技术领域Technical field
本发明涉及涡旋压缩机及使用了该涡旋压缩机的空调机。The present invention relates to a scroll compressor and an air conditioner using the scroll compressor.
背景技术Background technique
用于空调机等的涡旋压缩机具备在台板竖立设置有旋涡状的涡卷的固定涡盘和在盖板竖立设置有旋涡状的涡卷的回旋涡盘，使两涡盘的涡卷互相朝向内侧并啮合。另外，构成为，通过使回旋涡盘进行回旋运动，使形成于两涡卷间的多个压缩室的容积依次缩小，由此压缩工作气体。Scroll compressors used in air conditioners and the like include a fixed scroll with a spiral scroll erected on a base plate and an orbiting scroll with a vortex-shaped scroll erected on a cover plate. The scrolls of the two scrolls are facing each other inwards and engaging. Furthermore, the working gas is compressed by causing the orbiting scroll to orbit, thereby sequentially reducing the volumes of the plurality of compression chambers formed between the two scrolls.
由于这样的压缩作用，产生要使固定涡盘和回旋涡盘互相分离的轴向力。当两涡盘要分离时，在涡卷的齿顶与齿根之间产生间隙，压缩室的密闭性恶化，压缩机的效率降低。Due to such compression, an axial force is generated to separate the fixed scroll and the orbiting scroll from each other. When the two scrolls are about to separate, a gap is created between the tooth tops and the tooth roots of the scrolls, which deteriorates the tightness of the compression chamber and reduces the efficiency of the compressor.
在涡旋压缩机中，为了使两涡盘不分离，在回旋涡盘的盖板的背面中央侧设置大致成为吐出压力的第一空间(高压室)，还在上述第一空间的外周侧的盖板背面形成成为吐出压力与吸入压力之间的压力(中间压力)的第二空间(背压室)，通过这些第一、第二空间的压力，产生将回旋涡盘向固定涡盘推压的推压力。In a scroll compressor, in order to prevent the two scrolls from being separated, a first space (high-pressure chamber) with approximately the discharge pressure is provided on the back center side of the cover plate of the orbiting scroll, and a first space (high-pressure chamber) on the outer peripheral side of the first space is provided. A second space (back pressure chamber) is formed on the back surface of the cover plate to produce a pressure (intermediate pressure) between the discharge pressure and the suction pressure. The pressure in these first and second spaces causes the orbiting scroll to be pushed toward the fixed scroll. of pushing force.
但是，由于该推压力，在固定涡盘的台板与回旋涡盘的盖板的滑动面(盖板面)产生滑动摩擦，在推压力过大的情况下，上述滑动面产生烧熔现象等，使压缩机的可靠性受损。However, due to this pressing force, sliding friction occurs between the sliding surface (cover surface) of the base plate of the fixed scroll and the cover plate of the orbiting scroll. If the pressing force is too large, a phenomenon such as burning may occur on the sliding surface. , which damages the reliability of the compressor.
因此，在现有的涡旋压缩机中进行了如下改良：采用向固定涡盘与回旋涡盘的滑动面(盖板面)供给润滑油的结构，提高上述滑动面的润滑状态。Therefore, improvements have been made in conventional scroll compressors by adopting a structure in which lubricating oil is supplied to the sliding surfaces (cover surfaces) of the fixed scroll and the orbiting scroll to improve the lubrication state of the sliding surfaces.
例如，在日本特开2008－2422号公报(专利文献1)记载的涡旋压缩机中，在回旋涡盘或固定涡盘的盖板面设置槽，在回旋涡盘的盖板内设置与第一空间(高压室)连通的通路，通过使上述槽和上述通路连通，将第一空间内的高压的润滑油供给至滑动面(盖板面)。由此，构成为，向固定涡盘与回旋涡盘的滑动面进行润滑油供给，提高上述滑动面的润滑状态。For example, in the scroll compressor described in Japanese Patent Application Laid-Open No. 2008-2422 (Patent Document 1), a groove is provided on the cover surface of the orbiting scroll or the fixed scroll, and a groove is provided in the cover plate of the orbiting scroll. A passage communicating with a space (high-pressure chamber) supplies the high-pressure lubricating oil in the first space to the sliding surface (cover surface) by connecting the groove and the passage. Accordingly, the lubricating oil is supplied to the sliding surfaces of the fixed scroll and the orbiting scroll to improve the lubricated state of the sliding surfaces.
另外，在日本特开2016－17484号公报(专利文献2)记载的涡旋压缩机中，在与回旋涡盘滑动的固定涡盘的滑动面(盖板面)以沿轴向延伸的方式形成有油槽。另外，构成为，在固定涡盘设有用于向上述油槽供给润滑油的多个油导入路和给油点，将来自壳体内部的高压空间的润滑油供给至上述给油点。In addition, in the scroll compressor described in Japanese Patent Application Laid-Open No. 2016-17484 (Patent Document 2), the sliding surface (cover surface) of the fixed scroll that slides with the orbiting scroll is formed to extend in the axial direction. There is an oil tank. In addition, the fixed scroll is provided with a plurality of oil introduction passages and oil supply points for supplying lubricating oil to the oil groove, and the lubricating oil from the high-pressure space inside the casing is supplied to the oil supply points.
现有技术文献existing technical documents
专利文献patent documents
专利文献1：日本特开2008－2422号公报Patent Document 1: Japanese Patent Application Publication No. 2008-2422
专利文献2：日本特开2016－17484号公报Patent Document 2: Japanese Patent Application Publication No. 2016-17484
发明内容Contents of the invention
发明所要解决的课题The problem to be solved by the invention
上述专利文献1中未记载导入高压的润滑油的上述槽的位置、上述槽的长度。因此，在上述槽较短的情况下，提高滑动面(盖板面)的润滑状态的效果降低，压缩机的可靠性降低。另一方面，若上述槽过长，则从槽向吸入室的润滑油的漏出量增多，润滑油加热制冷剂气体所引起的加热损失增大。另外，由于下压力增大，因此也存在回旋涡盘容易脱离的问题。The above-mentioned Patent Document 1 does not describe the position of the groove into which high-pressure lubricating oil is introduced or the length of the groove. Therefore, when the groove is short, the effect of improving the lubrication state of the sliding surface (cover surface) is reduced, and the reliability of the compressor is reduced. On the other hand, if the groove is too long, the amount of lubricating oil leaking from the groove to the suction chamber increases, and the heating loss caused by the lubricating oil heating the refrigerant gas increases. In addition, due to the increased downforce, there is also a problem that the orbiting scroll is easily detached.
上述专利文献2采用具有多个给油点的油槽，且采用槽的长度超过半圈的圆环状、C字形状的油槽，由于槽为较长的形状，因此从槽向吸入室的润滑油的漏出量增多，润滑油加热制冷剂气体为导致加热损失增大。另外，由于下压力增大，因此也存在回旋涡盘容易脱离的问题。The above-mentioned Patent Document 2 uses an oil groove with a plurality of oil supply points, and uses an annular or C-shaped oil groove with a length of more than half a circle. Since the groove is long, the lubricating oil from the groove to the suction chamber is The amount of leakage increases, and the lubricating oil heats the refrigerant gas, resulting in increased heating losses. In addition, due to the increased downforce, there is also a problem that the orbiting scroll is easily detached.
本发明的目的在于得到一种涡旋压缩机及使用了该涡旋压缩机的空调机，该涡旋压缩机在抑制加热损失的增大的同时，提高固定涡盘与回旋涡盘的滑动面的润滑性，效率高且可靠性高。An object of the present invention is to obtain a scroll compressor that improves the sliding surface between a fixed scroll and an orbiting scroll while suppressing an increase in heating loss, and an air conditioner using the scroll compressor. Excellent lubricity, high efficiency and high reliability.
用于解决问题的方案solutions to problems
为了实现上述目的，本发明提供一种涡旋压缩机，其具备：在台板竖立设置有旋涡状的涡卷的固定涡盘；在盖板竖立设置有旋涡状的涡卷，且通过与上述固定涡盘啮合并进行回旋运动，形成吸入室或压缩室的回旋涡盘；设于上述回旋涡盘的背面中心侧且具有与吐出压力接近的压力的第一空间；以及设于上述回旋涡盘的背面且上述第一空间的外周侧，并具有作为吐出压力与吸入压力之间的压力的中间压力的第二空间，上述涡旋压缩机的特征在于，具备：周向槽，其形成于上述固定涡盘的成为滑动面的盖板面及上述回旋涡盘的成为滑动面的盖板面的至少任一方且沿周向延伸；以及通路，其设于上述回旋涡盘的盖板，且用于将上述第一空间内的润滑油供给至上述周向槽，上述周向槽设于在作用于上述回旋涡盘的载荷成为最大的曲柄角的附近，回旋涡盘的盖板最强力地抵接于固定涡盘的盖板面的位置，而且，上述周向槽的周向上的长度为其周向槽的两端配置于包括上述最强力地抵接的位置的大致±90度的范围内的长度。In order to achieve the above object, the present invention provides a scroll compressor, which is provided with: a fixed scroll with a spiral scroll erected on a base plate; a spiral scroll erected on a cover plate; An orbiting scroll in which the fixed scroll engages and performs orbiting motion to form a suction chamber or a compression chamber; a first space provided on the back center side of the orbiting scroll and having a pressure close to the discharge pressure; and an orbiting scroll provided in the above-mentioned orbiting scroll The back surface and the outer peripheral side of the first space have a second space having an intermediate pressure that is a pressure between the discharge pressure and the suction pressure. The scroll compressor is characterized in that it is provided with a circumferential groove formed in the above-mentioned first space. At least one of the cover surface serving as the sliding surface of the fixed scroll and the cover surface serving as the sliding surface of the orbiting scroll extends in the circumferential direction; and a passage provided on the cover plate of the orbiting scroll and used for When lubricating oil in the first space is supplied to the circumferential groove, and the circumferential groove is provided near the crank angle at which the load acting on the orbiting scroll becomes the largest, the cover plate of the orbiting scroll is most powerful. The position in contact with the cover plate surface of the fixed scroll, and the length in the circumferential direction of the circumferential groove is such that both ends of the circumferential groove are located approximately ±90 degrees including the position where the strongest contact is made length within the range.
本发明的另一特征为一种空调机，将涡旋压缩机、四通阀、室外侧热交换器、膨胀阀、室内侧热交换器通过制冷剂配管依次连接构成冷冻循环，该空调机的特征在于，上述涡旋压缩机采用了上述的涡旋压缩机。Another feature of the present invention is an air conditioner in which a scroll compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger are sequentially connected through refrigerant piping to form a refrigeration cycle. It is characterized in that the above-mentioned scroll compressor is used as the above-mentioned scroll compressor.
发明的效果Effect of the invention
根据本发明，能够得到一种涡旋压缩机及使用了该涡旋压缩机的空调机，该涡旋压缩机在抑制加热损失的增大的同时，提高固定涡盘与回旋涡盘的滑动面的润滑性，效率高且可靠性高。According to the present invention, it is possible to obtain a scroll compressor that improves the sliding surface between the fixed scroll and the orbiting scroll while suppressing an increase in heating loss, and an air conditioner using the scroll compressor. Excellent lubricity, high efficiency and high reliability.
附图说明Description of the drawings
图1是表示本发明的涡旋压缩机的实施例1的纵剖视图。FIG. 1 is a longitudinal sectional view showing Embodiment 1 of the scroll compressor of the present invention.
图2是图1所示的固定涡盘的仰视图，是用截面表示回旋涡盘的涡卷的图。FIG. 2 is a bottom view of the fixed scroll shown in FIG. 1 , and is a cross-sectional view showing the wraps of the orbiting scroll.
图3是说明现有的涡旋压缩机的回旋涡盘盖板面上的压力分布的图。FIG. 3 is a diagram illustrating the pressure distribution on the orbiting scroll cover surface of the conventional scroll compressor.
图4是说明本发明的实施例1的回旋涡盘盖板面上的压力分布的图。4 is a diagram illustrating pressure distribution on the orbiting scroll cover surface according to Embodiment 1 of the present invention.
图5是说明涡旋压缩机旋转一圈中的载荷相对于曲柄角的变化的图表。FIG. 5 is a graph illustrating a change in load relative to the crank angle during one rotation of the scroll compressor.
图6是说明涡旋压缩机的曲柄角与压缩室内压力的变化的关系的图表。FIG. 6 is a graph illustrating the relationship between the crank angle of the scroll compressor and changes in pressure within the compression chamber.
图7是表示本发明的涡旋压缩机的实施例2的图，是相当于图2的图。FIG. 7 is a diagram showing Embodiment 2 of the scroll compressor of the present invention, and is equivalent to FIG. 2 .
图8是表示本发明的涡旋压缩机的实施例3的图，是相当于图2的图。FIG. 8 is a diagram showing a third embodiment of the scroll compressor of the present invention, and is equivalent to FIG. 2 .
图9是说明本发明的涡旋压缩机的实施例4的回旋涡盘的俯视图。9 is a plan view illustrating an orbiting scroll of Example 4 of the scroll compressor of the present invention.
图10是说明本发明的涡旋压缩机的实施例5的固定涡盘的仰视图。FIG. 10 is a bottom view illustrating the fixed scroll of the scroll compressor according to Embodiment 5 of the present invention.
图11是说明本发明的涡旋压缩机的实施例6的回旋涡盘的纵剖视图。FIG. 11 is a longitudinal sectional view illustrating an orbiting scroll of a scroll compressor according to Embodiment 6 of the present invention.
图12是说明本发明的涡旋压缩机的实施例7的回旋涡盘的俯视图。FIG. 12 is a plan view illustrating the orbiting scroll of the scroll compressor according to Embodiment 7 of the present invention.
图13是说明本发明的涡旋压缩机的实施例8的固定涡盘的仰视图。13 is a bottom view illustrating the fixed scroll of the scroll compressor according to Embodiment 8 of the present invention.
图14是说明使用了本发明的涡旋压缩机的空调机的一例的冷冻循环结构图。Fig. 14 is a refrigeration cycle structural diagram illustrating an example of an air conditioner using the scroll compressor of the present invention.
具体实施方式Detailed ways
以下，使用附图对本发明的涡旋压缩机及使用了该涡旋压缩机的空调机的具体的实施例进行说明。此外，在各图中，标注相同符号的部分表示相同或等同的部分。Hereinafter, specific examples of the scroll compressor of the present invention and the air conditioner using the scroll compressor will be described using the drawings. In addition, in each drawing, the part attached with the same symbol shows the same or equivalent part.
使用图1～图6，对本发明的涡旋压缩机的实施例1进行说明。Embodiment 1 of the scroll compressor of the present invention will be described using FIGS. 1 to 6 .
首先，使用图1及图2对应用本实施例的涡旋压缩机的整体结构进行说明。图1表示本实施例1的涡旋压缩机的纵剖视图，图2是图1所示的固定涡盘的仰视图，是用截面表示回旋涡盘的涡卷的图。First, the overall structure of the scroll compressor to which this embodiment is applied will be described using FIGS. 1 and 2 . FIG. 1 is a longitudinal sectional view of the scroll compressor according to the first embodiment of the present invention. FIG. 2 is a bottom view of the fixed scroll shown in FIG. 1 and is a cross-sectional view showing the wraps of the orbiting scroll.
涡旋压缩机1通过在密闭容器(壳体)9内容纳压缩机构部2及马达部16等而构成。The scroll compressor 1 is configured by housing the compression mechanism unit 2, the motor unit 16, and the like in a sealed container (casing) 9.
上述压缩机构部2具备框架17、固定于框架17的固定涡盘7、以及固定于上述框架17与固定涡盘7之间且与上述固定涡盘7啮合形成压缩室13的回旋涡盘8。The compression mechanism unit 2 includes a frame 17 , a fixed scroll 7 fixed to the frame 17 , and an orbiting scroll 8 fixed between the frame 17 and the fixed scroll 7 and meshed with the fixed scroll 7 to form the compression chamber 13 .
上述固定涡盘7具备圆板状的台板7a、以旋涡状竖立设置于台板7a的涡卷7b、以及支撑部7d，支撑部7d位于上述台板7a的外周侧，具有与上述涡卷7b的前端面大致相同的高度的盖板面7e，且以包围上述涡卷7b的方式设置成筒状。竖立设置有上述涡卷7b的台板7a的表面由于位于涡卷7b之间而称为齿根7c。固定涡盘7的支撑部7d的盖板面7e为与回旋涡盘8的盖板8a相接的滑动面。The fixed scroll 7 includes a disc-shaped base plate 7a, a scroll 7b erected in a spiral shape on the base plate 7a, and a support portion 7d. The front end surface of 7b is substantially the same height as the cover surface 7e, and is provided in a cylindrical shape so as to surround the above-mentioned scroll 7b. The surface of the base plate 7a on which the above-mentioned scrolls 7b are erected is located between the scrolls 7b and is called a tooth root 7c. The cover surface 7e of the support portion 7d of the fixed scroll 7 is a sliding surface in contact with the cover 8a of the orbiting scroll 8.
另外，固定涡盘7通过螺栓等将上述支撑部7d固定于上述框架17，与固定涡盘7结合成一体的上述框架17通过焊接等固定方法固定于上述密闭容器9。In addition, the fixed scroll 7 fixes the support portion 7d to the frame 17 with bolts and the like, and the frame 17 integrated with the fixed scroll 7 is fixed to the sealed container 9 by a fixing method such as welding.
上述回旋涡盘8与固定涡盘7对置配置，固定涡盘7的涡卷7b和回旋涡盘8的涡卷8b啮合，可回旋地配置于框架17内。该回旋涡盘8具有圆板状的盖板8a、从作为该盖板8a的表面的齿根8c竖立设置的旋涡状的涡卷8b、以及设于上述盖板8a的背面中央的凸起部(回旋凸起部)8d。另外，盖板8a的外周部的与固定涡盘7相接的表面为回旋涡盘8的盖板面8e。The above-mentioned orbiting scroll 8 is arranged to face the fixed scroll 7. The wrap 7b of the fixed scroll 7 meshes with the wrap 8b of the orbiting scroll 8, and is arranged in the frame 17 so as to be orbitable. The orbiting scroll 8 has a disk-shaped cover plate 8a, a spiral wrap 8b standing upright from a tooth base 8c as the surface of the cover plate 8a, and a convex portion provided in the center of the back surface of the cover plate 8a. (Swivel convex portion) 8d. In addition, the surface of the outer peripheral portion of the cover plate 8 a that is in contact with the fixed scroll 7 is the cover surface 8 e of the orbiting scroll 8 .
上述回旋涡盘8的涡卷8b的前端部(涡卷齿顶)构成为与上述固定涡盘7的齿根7c隔开微小的间隙地对置。同样地，固定涡盘7的涡卷7b的前端部(涡卷齿顶)也构成为与上述回旋涡盘8的齿根8c隔开微小间隙地对置。The front end portion (wrap tip) of the wrap 8b of the orbiting scroll 8 is configured to face the tooth base 7c of the fixed scroll 7 with a slight gap therebetween. Similarly, the front end portion (wrap tip) of the wrap 7b of the fixed scroll 7 is also configured to face the tooth root 8c of the orbiting scroll 8 with a slight gap therebetween.
上述马达部16由转子16a和定子16b构成，在上述转子16a一体地固定有曲轴(旋转轴)10。The motor unit 16 is composed of a rotor 16a and a stator 16b, and a crankshaft (rotating shaft) 10 is integrally fixed to the rotor 16a.
经由该曲轴10通过马达部16驱动上述回旋涡盘8，使回旋涡盘8进行回旋运动，由此进行使上述压缩室13的容积逐渐减小的压缩动作。The orbiting scroll 8 is driven by the motor unit 16 via the crankshaft 10 to orbit the orbiting scroll 8, thereby performing a compression operation in which the volume of the compression chamber 13 is gradually reduced.
随着该压缩动作，在冷冻循环流动的制冷剂等工作流体从吸入口14被吸入吸入室20(参照图2)，吸入的工作流体经过在压缩室13的压缩行程，从吐出口15吐出至密闭容器9内的吐出空间54。构成为，吐出到上述吐出空间54的工作流体通过形成于上述固定涡盘7的外周和上述框架17的外周的通路(未图示)流到马达室52，然后从吐出管6吐出到密闭容器9外。Along with this compression operation, working fluid such as refrigerant flowing in the refrigeration cycle is sucked into the suction chamber 20 (see FIG. 2 ) from the suction port 14 . The sucked working fluid passes through the compression stroke in the compression chamber 13 and is discharged from the discharge port 15 to The discharge space 54 in the airtight container 9 is sealed. The working fluid discharged into the discharge space 54 flows to the motor chamber 52 through a passage (not shown) formed on the outer periphery of the fixed scroll 7 and the outer periphery of the frame 17 , and is then discharged from the discharge pipe 6 to a sealed container. 9 outside.
上述曲轴10旋转自如地支撑于在上述框架17所设置的主轴承5，且构成为该曲轴10的中心轴线和固定涡盘7的中心轴线O1同轴。另外，在上述曲轴10的前端部(上端部)设有偏心的曲柄部10a，该曲柄部10a插入设于上述回旋涡盘8的回旋凸起部8d的回旋轴承11。由此，上述回旋涡盘8构成为，当曲轴10旋转时，通过上述曲柄部10a的偏心运动进行回旋运动。The crankshaft 10 is rotatably supported by a main bearing 5 provided on the frame 17 , and the central axis of the crankshaft 10 and the central axis O1 of the fixed scroll 7 are coaxial. In addition, an eccentric crank portion 10 a is provided at the front end portion (upper end portion) of the crankshaft 10 , and the orbiting bearing 11 provided in the orbiting boss portion 8 d of the orbiting scroll 8 is inserted into the crank portion 10 a. Thereby, the orbiting scroll 8 is configured to perform an orbiting motion due to the eccentric motion of the crank portion 10 a when the crankshaft 10 rotates.
上述回旋涡盘8的中心轴线O2为相对于上述固定涡盘7的中心轴线偏心规定距离的状态。另外，回旋涡盘8的涡卷8b相对于固定涡盘7的涡卷7b在周向上偏离规定角度(一般为180度)地重合。另外，在上述回旋涡盘8与上述框架17之间设有用于使回旋涡盘8相对于固定涡盘7一边以不能自转的方式约束一边相对地进行回旋动作的欧氏环12。The central axis O2 of the orbiting scroll 8 is eccentric to the central axis O2 of the fixed scroll 7 by a predetermined distance. In addition, the wrap 8b of the orbiting scroll 8 overlaps the wrap 7b of the fixed scroll 7 at a predetermined angle (generally 180 degrees) in the circumferential direction. Furthermore, an Oldham ring 12 is provided between the orbiting scroll 8 and the frame 17 for causing the orbiting scroll 8 to orbit relative to the fixed scroll 7 while constraining it from rotating.
根据图2，对上述固定涡盘7与回旋涡盘8的啮合状态进行说明。在该图2中，用剖视图示出了回旋涡盘8的涡卷8b，另外，用两点划线的假想线图示出相当于回旋涡盘8的盖板8a的外周的部分。如该图2所示，在固定涡盘7的涡卷7b与回旋涡盘8的涡卷8b之间形成有月牙状的多个压缩室13(回旋内线侧压缩室13a、回旋外线侧压缩室13b)，当使回旋涡盘8进行回旋运动时，各压缩室13随着向中央部移动而容积连续地缩小。The meshing state of the fixed scroll 7 and the orbiting scroll 8 will be described based on FIG. 2 . In FIG. 2 , the wrap 8 b of the orbiting scroll 8 is shown in a cross-sectional view, and a portion corresponding to the outer periphery of the cover plate 8 a of the orbiting scroll 8 is shown in a phantom line diagram of two-dot chain lines. As shown in FIG. 2, a plurality of crescent-shaped compression chambers 13 (the orbiting inner side compression chamber 13a, the orbiting outer side compression chamber 13a) are formed between the wrap 7b of the fixed scroll 7 and the wrap 8b of the orbiting scroll 8. 13b), when the orbiting scroll 8 is caused to orbit, the volume of each compression chamber 13 is continuously reduced as it moves toward the center.
20是吸入室，是吸入流体的途中的空间。自回旋涡盘8的回旋运动的相位前进而完成了流体的封入的时刻起，该吸入室20成为压缩室13。20 is a suction chamber, which is a space on the way to suck fluid. The suction chamber 20 becomes the compression chamber 13 from the time when the phase of the orbiting motion of the orbiting scroll 8 advances and sealing of the fluid is completed.
如图1、图2所示，上述吸入口14设于固定涡盘7，该吸入口14以与上述吸入室20连通的方式形成于固定涡盘7的台板7a的外周侧。As shown in FIGS. 1 and 2 , the suction port 14 is provided in the fixed scroll 7 , and is formed on the outer peripheral side of the base plate 7 a of the fixed scroll 7 so as to communicate with the suction chamber 20 .
上述吐出口15设于上述固定涡盘7的台板7a的旋涡中心附近，且构成为，当最内周侧的压缩室13的压缩进行时，马上与上述吐出口15连通。The discharge port 15 is provided near the swirl center of the platen 7a of the fixed scroll 7, and is configured to communicate with the discharge port 15 immediately when compression of the innermost compression chamber 13 proceeds.
当通过图1所示的马达部16使曲轴10旋转时，回旋涡盘8以固定涡盘7的中心轴线为中心以规定距离的回旋半径进行回旋运动。由此，工作气体(例如，在冷冻循环中循环的制冷剂气体)从上述吸入口14被吸入，在上述的各压缩室13内依次被压缩，进行了压缩的工作气体(以下，称为压缩气体)从吐出口15吐出至吐出空间54。之后，上述压缩气体例如马达室52，由此经由吐出管6供给至涡旋压缩机1的外部的冷冻循环等。When the crankshaft 10 is rotated by the motor unit 16 shown in FIG. 1 , the orbiting scroll 8 orbits with a predetermined distance around the central axis of the fixed scroll 7 at a radius of orbit. Thereby, the working gas (for example, the refrigerant gas circulating in the refrigeration cycle) is sucked in from the suction port 14 and is sequentially compressed in each of the compression chambers 13. The compressed working gas (hereinafter referred to as compressed gas) Gas) is discharged from the discharge port 15 to the discharge space 54 . Thereafter, the compressed gas is supplied to the refrigeration cycle outside the scroll compressor 1 via the discharge pipe 6 , for example, in the motor chamber 52 .
接下来，对图1所示的涡旋压缩机(以下，简称为压缩机)1中的润滑油的流进行说明。在容纳有压缩机构部2及马达部16等的密闭容器9的底部设有贮存润滑油(冷冻机油)的贮油部53。在曲轴10的下端设有容积型或离心式的给油泵21，随着上述曲轴10的旋转，给油泵21也旋转，将贮存于上述密闭容器9底部的贮油部53的润滑油吸入并供给至在上述曲轴10内沿轴向形成的给油孔(贯通孔)3。Next, the flow of lubricating oil in the scroll compressor (hereinafter simply referred to as compressor) 1 shown in FIG. 1 will be described. An oil storage portion 53 for storing lubricating oil (refrigeration oil) is provided at the bottom of the sealed container 9 accommodating the compression mechanism unit 2, the motor unit 16, and the like. A positive displacement or centrifugal oil feed pump 21 is provided at the lower end of the crankshaft 10. As the crankshaft 10 rotates, the oil feed pump 21 also rotates to suck in and supply the lubricating oil stored in the oil storage portion 53 at the bottom of the sealed container 9. to the oil supply hole (through hole) 3 formed in the axial direction in the above-mentioned crankshaft 10.
贮油部53的润滑油从设于给油泵壳体22的润滑油吸入口25吸入，并从上述给油泵21的吐出口28吐出。吐出的润滑油通过上述给油孔3输送至曲轴10的上端。The lubricating oil in the oil reservoir 53 is sucked in from the lubricating oil suction port 25 provided in the oil feed pump housing 22 and discharged from the discharge port 28 of the oil feed pump 21 . The discharged lubricating oil is delivered to the upper end of the crankshaft 10 through the above-mentioned oil supply hole 3 .
此时，流通于上述给油孔3的润滑油的一部分经由设于上述曲轴10的横孔24输送至副轴承23，在对副轴承23进行润滑后，返回密闭容器9底部的上述贮油部53。流通于上述给油孔3的其它大部分的润滑油达到上述曲轴10的曲柄部10a上端的回旋凸起部8d的内侧空间，通过设于上述曲柄部10a的外周面的油槽57对回旋轴承11进行润滑。该润滑油之后在对设于上述回旋轴承11的下部的上述主轴承5进行润滑后，通过由排油孔26a及排油管26b构成的回油通路返回到密闭容器9底部的贮油部53。At this time, part of the lubricating oil flowing through the oil supply hole 3 is transported to the auxiliary bearing 23 through the transverse hole 24 provided in the crankshaft 10 , and after lubricating the auxiliary bearing 23 , is returned to the oil storage portion at the bottom of the sealed container 9 53. Most of the other lubricating oil flowing through the oil supply hole 3 reaches the inner space of the orbiting boss 8d at the upper end of the crank portion 10a of the crankshaft 10, and passes through the oil groove 57 provided on the outer peripheral surface of the crank portion 10a to contact the orbiting bearing 11. Lubricate. The lubricating oil then lubricates the main bearing 5 provided at the lower part of the revolving bearing 11 and then returns to the oil storage portion 53 at the bottom of the sealed container 9 through the oil return passage composed of the oil drain hole 26 a and the oil drain pipe 26 b.
将上述回旋凸起部8d的内侧空间(曲柄部10a上端部的空间、由回旋轴承11与曲轴10的间隙、油槽57形成的空间)、位于上述回旋凸起部8d的外周侧的空间(由回旋凸起部8d、盖板8a背面、密封部件32以及框架17形成的空间)、以及收纳上述主轴承5的空间(由框架17、曲轴10以及框架密封件56形成的空间)合起来称为第一空间33。该第一空间33是具有接近吐出压力的压力的空间。The inner space of the above-mentioned revolving boss 8d (the space at the upper end of the crank part 10a, the space formed by the gap between the revolving bearing 11 and the crankshaft 10, and the oil groove 57) and the space located on the outer peripheral side of the above-mentioned revolving boss 8d (the space formed by the gap between the revolving bearing 11 and the crankshaft 10, The space formed by the revolving boss 8d, the back surface of the cover plate 8a, the sealing member 32, and the frame 17), and the space in which the main bearing 5 is accommodated (the space formed by the frame 17, the crankshaft 10, and the frame seal 56) are collectively called First Space33. The first space 33 is a space having a pressure close to the discharge pressure.
为了润滑上述主轴承5及上述回旋轴承11而流入到上述第一空间33的润滑油的大部分通过上述排油孔26a及上述排油管26b的回通路返回到密闭容器9底部的贮油部53。另外，上述润滑油的一部分经由设于上述密封部件32的上端面与上述盖板8a的背面之间的油漏出单元流入背压室(第二空间)18，该背压室18设于比上述第一空间33靠外周侧，且为吐出压力与吸入压力之间的压力(中间压力。以下也称为背压)。流入到该背压室18的润滑油用于上述欧氏环12的润滑、上述固定涡盘7与回旋涡盘8的盖板面7e、8e间的滑动部的润滑、涡卷7b、8b间的间隙的密封(密闭)等。从而，以使上述润滑、密封所需的润滑油量流入上述背压室18的方式构成上述油漏出单元。Most of the lubricating oil that flows into the first space 33 in order to lubricate the main bearing 5 and the revolving bearing 11 returns to the oil storage portion 53 at the bottom of the sealed container 9 through the return passage of the oil drain hole 26 a and the oil drain pipe 26 b. . In addition, a part of the lubricating oil flows into the back pressure chamber (second space) 18 provided at a position larger than the above-mentioned position via an oil leakage unit provided between the upper end surface of the sealing member 32 and the back surface of the cover plate 8 a. The first space 33 is located on the outer peripheral side and has a pressure between the discharge pressure and the suction pressure (intermediate pressure. Hereinafter also referred to as back pressure). The lubricating oil flowing into the back pressure chamber 18 is used for lubrication of the Oldham ring 12, lubrication of the sliding portion between the cover surfaces 7e and 8e of the fixed scroll 7 and the orbiting scroll 8, and between the scrolls 7b and 8b. The sealing (sealing) of the gap, etc. Therefore, the oil leakage unit is configured so that the amount of lubricating oil required for the lubrication and sealing flows into the back pressure chamber 18 .
上述密封部件32与波状弹簧(未图示)一起设于在上述框架17的与上述盖板8a的背面对置的面所设置的圆环槽31。该密封部件32分隔成为吐出压力的上述第一空间33和成为吸入压力与吐出压力的中间压力的上述背压室(第二空间)18。The sealing member 32 is provided together with a wave spring (not shown) in an annular groove 31 provided in a surface of the frame 17 facing the back surface of the cover plate 8 a. This sealing member 32 partitions the first space 33 that becomes a discharge pressure and the back pressure chamber (second space) 18 that becomes an intermediate pressure between the suction pressure and the discharge pressure.
上述油漏出单元例如由设于上述盖板8a的背面的一个或多个狭缝状的浅槽58和上述密封部件32构成。上述浅槽58构成为，以通过上述回旋涡盘8的回旋运动而横跨上述密封部件32的方式配置，将上述第一空间33和上述背压室18间歇地连通。根据这样的结构，通过上述第一空间33与上述背压室18的压力差，能够使润滑油经由作为微小间隙的上述浅槽58从上述第一空间33流入到上述背压室18。The oil leakage unit is composed of, for example, one or a plurality of slit-shaped shallow grooves 58 provided on the back surface of the cover plate 8 a and the sealing member 32 . The shallow groove 58 is disposed across the sealing member 32 due to the orbiting motion of the orbiting scroll 8, and is configured to intermittently communicate with the first space 33 and the back pressure chamber 18. According to such a structure, the lubricating oil can flow from the first space 33 into the back pressure chamber 18 via the shallow groove 58 which is a minute gap due to the pressure difference between the first space 33 and the back pressure chamber 18 .
另外，也可以构成为，取代上述浅槽58，而在上述盖板8a的背面设置一个或多个油兜(成为贮油部的孔，例如，圆形的槽)，该油兜随着回旋涡盘8的回旋运动进行横跨上述密封部件32的圆运动。当这样构成时，上述油兜在上述第一空间33与上述背压室18之间移动，能够将上述第一空间33的润滑油贮存于油兜而间歇性地移送到上述背压室18，能够将第一空间33内的润滑油供给至背压室18。Alternatively, instead of the shallow groove 58, one or more oil pockets (holes serving as oil storage portions, for example, circular grooves) may be provided on the back surface of the cover plate 8a, and the oil pockets may return as they return. The swirling motion of the scroll 8 makes a circular motion across the sealing member 32 . With this structure, the oil pocket moves between the first space 33 and the back pressure chamber 18, and the lubricating oil in the first space 33 can be stored in the oil pocket and intermittently transferred to the back pressure chamber 18. The lubricating oil in the first space 33 can be supplied to the back pressure chamber 18 .
进入到上述背压室18的润滑油润滑欧氏环12的滑动部，并且其一部在上述固定涡盘7与回旋涡盘8的盖板面7e、8e间的微小间隙一边润滑一边通过，并流入吸入室20或压缩室13。其它润滑油在背压室的压力(背压)变高时，通过连通背压室18和压缩室13的背压孔35流入压缩室13。该背压孔35是用于调整背压室18内的压力的孔。The lubricating oil that has entered the back pressure chamber 18 lubricates the sliding portion of the Oldham ring 12, and a part of the lubricating oil passes through the minute gap between the cover surfaces 7e and 8e of the fixed scroll 7 and the orbiting scroll 8 while being lubricated. And flows into the suction chamber 20 or the compression chamber 13. When the pressure (back pressure) of the back pressure chamber becomes high, other lubricating oil flows into the compression chamber 13 through the back pressure hole 35 connecting the back pressure chamber 18 and the compression chamber 13 . This back pressure hole 35 is a hole for adjusting the pressure in the back pressure chamber 18 .
流入到吸入室20、压缩室13的润滑油在用于上述固定涡盘7的涡卷7b与回旋涡盘8的涡卷8之间的间隙的密封、润滑后，从上述吐出口15向吐出空间54吐出。该吐出的油的一部分与制冷剂气体一起从上述吐出管6向冷冻循环吐出，剩余部分在密闭容器9内与制冷剂气体分离，并贮存于密闭容器9底部的贮油部53。The lubricating oil flowing into the suction chamber 20 and the compression chamber 13 is used to seal and lubricate the gap between the wrap 7 b of the fixed scroll 7 and the wrap 8 of the orbiting scroll 8 , and then is discharged from the discharge port 15 to the discharge port 15 . Space 54 spat out. Part of the discharged oil is discharged into the refrigeration cycle from the discharge pipe 6 together with the refrigerant gas, and the remaining part is separated from the refrigerant gas in the sealed container 9 and stored in the oil storage portion 53 at the bottom of the sealed container 9 .
如上述地，通过设置上述第一空间33、上述背压室18以及上述油漏出单元，能够独立控制各轴承部所需的给油量和向背压室18的给油量，因此，能够得到高效率的涡旋压缩机。As described above, by providing the first space 33 , the back pressure chamber 18 and the oil leakage unit, the oil supply amount required for each bearing part and the oil supply amount to the back pressure chamber 18 can be independently controlled. Therefore, a high oil supply amount can be obtained. Efficient scroll compressor.
接下来，对上述背压室18的功能进行说明。在涡旋压缩机1中，由于其压缩作用，产生要使固定涡盘7和回旋涡盘8互相分离的轴向的力(分离力)。若由于该轴向的力而产生上述两涡盘分离的所谓的回旋涡盘8的脱离现象，则压缩室13的密闭性恶化，压缩机效率降低。Next, the function of the back pressure chamber 18 will be described. In the scroll compressor 1, due to its compression action, an axial force (separating force) is generated to separate the fixed scroll 7 and the orbiting scroll 8 from each other. If this axial force causes a so-called detachment phenomenon of the orbiting scroll 8 in which the two scrolls are separated, the airtightness of the compression chamber 13 will deteriorate and the compressor efficiency will decrease.
因此，在回旋涡盘8的盖板8a的背面侧设置成为吐出压力与吸入压力之间的压力的背压室18，通过该背压室18的压力(中间压力)和上述第一空间33的吐出压力，抵消上述分离力，并且将回旋涡盘8向固定涡盘7推压。Therefore, a back pressure chamber 18 having a pressure between the discharge pressure and the suction pressure is provided on the back side of the cover plate 8 a of the orbiting scroll 8 , and the pressure in the back pressure chamber 18 (intermediate pressure) and the pressure in the first space 33 are passed The discharge pressure cancels out the separation force and presses the orbiting scroll 8 toward the fixed scroll 7 .
此时，若推压力过大，则回旋涡盘8的盖板面8e与固定涡盘7的盖板面7e的滑动损失增大，压缩机效率降低，并且在盖板面7e、8e产生磨损、咬合、或者烧熔等问题等，压缩机的可靠性降低。也就是，上述推压力存在最佳值，若过小，则压缩室的密闭性恶化，热流体损失增大，若过大，则滑动损失增大。因此，将推压力维持为最佳值对于压缩机的高性能化、高可靠性化是重要的。At this time, if the pushing force is too large, the sliding loss between the cover surface 8e of the orbiting scroll 8 and the cover surface 7e of the fixed scroll 7 increases, the compressor efficiency decreases, and wear occurs on the cover surfaces 7e and 8e. , seizure, or melting problems, etc., the reliability of the compressor will be reduced. That is, there is an optimal value for the above-mentioned pressing force. If it is too small, the tightness of the compression chamber will deteriorate and the thermal fluid loss will increase. If it is too large, the sliding loss will increase. Therefore, maintaining the pushing force at an optimal value is important for improving the performance and reliability of the compressor.
以上是涡旋压缩机1的基本的构造。在此，由于例如要提高上述回旋轴承11的可靠性等理由，有时增大回旋轴承11的径。这样的情况下，配置于其外侧的上述密封部件32的径也增大，具有接近吐出压力的压力的上述第一空间33变大。因此，作用于回旋涡盘8的盖板8a的背面的吐出压力的领域也扩大，上述推压力增加。若该推压力的增加过大，则盖板面7e与盖板面8e的滑动损失增大，并且产生磨损、咬合、或者烧熔等问题，使压缩机的可靠性降低。特别是在涡旋压缩机1以高压力比运转的高压力比条件下，上述推压力过大，在盖板面产生咬合、烧熔等，压缩机的可靠性容易降低。The above is the basic structure of the scroll compressor 1 . Here, for reasons such as improving the reliability of the orbiting bearing 11, the diameter of the orbiting bearing 11 may be increased. In this case, the diameter of the sealing member 32 arranged outside the sealing member 32 also increases, and the first space 33 having a pressure close to the discharge pressure becomes larger. Therefore, the range of the discharge pressure acting on the back surface of the cover plate 8a of the orbiting scroll 8 also expands, and the above-mentioned pressing force increases. If the pressing force increases too much, the sliding loss between the cover plate surface 7e and the cover plate surface 8e will increase, and problems such as wear, seizure, or melting will occur, reducing the reliability of the compressor. Especially under high pressure ratio conditions in which the scroll compressor 1 operates at a high pressure ratio, the above-mentioned pressing force is too large, causing seizures, melting, etc. on the cover surface, and the reliability of the compressor is easily reduced.
因此，在本实施例中，采用如下结构：在固定涡盘7的成为滑动面的盖板面7e、及回旋涡盘8的成为滑动面的盖板面8e的至少任意一个形成沿周向延伸的周向槽，在上述回旋涡盘8的盖板8a设有用于将上述第一空间33内的润滑油供给至上述周向槽的通路。另外，构成为，上述周向槽设于在作用于上述回旋涡盘的载荷成为最大的曲柄角的附近，回旋涡盘的盖板最强力地抵接于固定涡盘的盖板面的位置。Therefore, in this embodiment, a structure is adopted in which at least one of the cover surface 7e serving as the sliding surface of the fixed scroll 7 and the cover surface 8e serving as the sliding surface of the orbiting scroll 8 has a formation extending in the circumferential direction. The cover plate 8a of the orbiting scroll 8 is provided with a passage for supplying the lubricating oil in the first space 33 to the circumferential groove. In addition, the circumferential groove is provided at a position near a crank angle at which the load acting on the orbiting scroll becomes maximum, and the cover plate of the orbiting scroll most strongly abuts against the cover surface of the fixed scroll. .
通过这样地构成，能够对固定涡盘7的盖板面7e与回旋涡盘8的盖板面8e的滑动面作用吐出压力，因此，能够赋予将回旋涡盘8从固定涡盘7分离的方向的力、即下压力。因此，能够避免推压力过大。With this configuration, the discharge pressure can act on the sliding surface between the cover surface 7e of the fixed scroll 7 and the cover surface 8e of the orbiting scroll 8. Therefore, a direction to separate the orbiting scroll 8 from the fixed scroll 7 can be provided. force, that is, downforce. Therefore, excessive pushing force can be avoided.
另外，在本实施例中，将上述周向槽的周向上的长度构成为，上述周向槽的一端配置于相距上述最强力地抵接的位置+70～+100度的范围内，将上述周向槽的另一端配置于相距上述最强力地抵接的位置－70～－100度的范围内。从而，能够降低从上述周向槽向吸入室20的润滑油的漏出量，降低润滑油加热制冷剂气体的加热损失。进一步地，能够防止上述下压力过大，并且确保回旋涡盘8的盖板8a最强力地抵接于固定涡盘7的盖板面7e的位置处的下压力。In addition, in this embodiment, the length of the circumferential groove in the circumferential direction is configured such that one end of the circumferential groove is disposed within a range of +70 to +100 degrees from the position where the strongest contact is made. The other end of the circumferential groove is disposed within a range of -70 to -100 degrees from the position of strongest contact. Therefore, the leakage amount of the lubricating oil from the circumferential groove to the suction chamber 20 can be reduced, and the heating loss of the refrigerant gas heated by the lubricating oil can be reduced. Furthermore, it is possible to prevent the above-mentioned downward force from being excessively large and ensure the downward force at the position where the cover plate 8 a of the orbiting scroll 8 most strongly abuts the cover plate surface 7 e of the fixed scroll 7 .
此外，上述周向槽的周向上的长度不限于上述的范围，只要将上述周向槽的一端配置于相距上述最强力地抵接的位置+20～+100度的范围内，且将另一端配置于相距上述最强力地抵接的位置－20～－100度的范围内即可。例如，也可以构成为，将上述周向槽的一端配置于相距上述最强力地抵接的位置+20～+40度的范围内，将另一端配置于相距上述最强力地抵接的位置－20～－40度的范围内。In addition, the length of the circumferential groove in the circumferential direction is not limited to the above range, as long as one end of the circumferential groove is arranged within the range of +20 to +100 degrees from the position of strongest contact, and the other end is One end may be arranged within the range of -20 to -100 degrees from the above-mentioned position of strongest contact. For example, the circumferential groove may be configured such that one end of the circumferential groove is disposed within a range of +20 to +40 degrees from the position where the strongest contact is made, and the other end is disposed apart from the position where the strongest contact is made. The position is within the range of -20 to -40 degrees.
以下，使用附图对本发明的涡旋压缩机的具体的实施例进行说明。如图1、图2所示，本实施例1中，在固定涡盘7设有周向槽36。另外，如图1所示，在回旋涡盘8的盖板8a设有一端与第一空间33连通的通路37。该通路37用于将上述第一空间33内的润滑油(以下，也称为油)供给至上述周向槽36。Hereinafter, specific examples of the scroll compressor of the present invention will be described using the drawings. As shown in FIGS. 1 and 2 , in the first embodiment, the fixed scroll 7 is provided with a circumferential groove 36 . In addition, as shown in FIG. 1 , the cover plate 8 a of the orbiting scroll 8 is provided with a passage 37 whose one end communicates with the first space 33 . This passage 37 is used to supply the lubricating oil (hereinafter, also referred to as oil) in the first space 33 to the circumferential groove 36 .
为了接收来自上述通路37的润滑油，如图2所示，在上述周向槽36的一端部或其一部分形成有圆形的槽部36a。上述圆形的槽部36a以在上述通路37的在槽部36a开口的端部进行回旋运动的全范围内与上述通路37的端部连通的方式形成为回旋半径以上的半径的大小的圆。图2中用点划线示出的圆45表示回旋涡盘8回旋运动时上述通路37相对于固定涡盘7运动的轨迹。In order to receive the lubricating oil from the passage 37, as shown in FIG. 2, a circular groove portion 36a is formed at one end of the circumferential groove 36 or a part thereof. The circular groove 36a is formed as a circle with a radius equal to or larger than the radius of gyration so as to communicate with the end of the passage 37 over the entire range of the gyration motion of the end of the passage 37 where the groove 36a opens. The circle 45 shown by the dotted line in FIG. 2 represents the trajectory of the movement of the passage 37 relative to the fixed scroll 7 when the orbiting scroll 8 orbits.
此外，上述周向槽36中的除了槽部36a的部分形成为比槽部36a的径窄的宽度，而且形成为在周向比上述槽部36a的径长。另外，上述槽部36a不限于圆形，只要形成为在上述通路37的端部进行回旋运动的全范围内与上述槽部36a连通即可，也可以是椭圆形、矩形等其它形状。In addition, the portion of the circumferential groove 36 excluding the groove portion 36a is formed to have a width narrower than the diameter of the groove portion 36a, and is formed to be longer than the diameter of the groove portion 36a in the circumferential direction. In addition, the groove portion 36a is not limited to a circular shape, as long as it is formed to communicate with the groove portion 36a over the entire range of the swing motion of the end portion of the passage 37, and may be an elliptical, rectangular or other shape.
上述通路37与上述圆形的槽部36a连通，由此第一空间33内的润滑油被供给至圆形的槽部36a的空间，从该圆形的槽部36a向上述周向槽36供给油。通过向周向槽36供给高压的油，周向槽36内的压力与第一空间33内的压力同样地为接近吐出压力的压力。The passage 37 communicates with the circular groove 36a, whereby the lubricating oil in the first space 33 is supplied to the space of the circular groove 36a, and is supplied from the circular groove 36a to the circumferential groove 36. Oil. By supplying high-pressure oil to the circumferential groove 36 , the pressure in the circumferential groove 36 becomes a pressure close to the discharge pressure like the pressure in the first space 33 .
在此，通过图3说明现有的涡旋压缩机的回旋涡盘8的盖板面上的压力分布，通过图4说明本实施例的涡旋压缩机的回旋涡盘8的盖板面上的压力分布。Here, the pressure distribution on the cover surface of the orbiting scroll 8 of the conventional scroll compressor will be described with reference to FIG. 3 , and the pressure distribution on the cover surface of the orbiting scroll 8 of the scroll compressor of the present embodiment will be described with reference to FIG. 4 . pressure distribution.
如图3所示，就现有的涡旋压缩机的回旋涡盘8的盖板面上的压力分布而言，面向背压室18的侧(盖板的外周侧)的压力为背压，面向吸入室20或压缩室13(参照图2)的侧(盖板的内周侧，且涡卷8b的某侧)的压力为吸入压力或压缩室内压力。As shown in FIG. 3 , regarding the pressure distribution on the cover plate surface of the orbiting scroll 8 of the conventional scroll compressor, the pressure on the side facing the back pressure chamber 18 (the outer peripheral side of the cover plate) is the back pressure. The pressure on the side facing the suction chamber 20 or the compression chamber 13 (see FIG. 2 ) (the inner peripheral side of the cover plate and one side of the scroll 8 b ) is the suction pressure or the compression chamber pressure.
与之相对，在本实施例的涡旋压缩机1中，由于设有上述的周向槽36，因此向上述周向槽36内导入吐出压力的油。因此，如图4中的右侧所示的回旋涡盘盖板面上的压力分布所示地，在设有周向槽36的侧，通过被导入吐出压力的油，将回旋涡盘8向下方下压的力增大与图4中用斜线示出的区域38相应的量。因此，能够抑制回旋涡盘8的盖板最强力地抵接于固定涡盘的盖板面的位置处的推压力的增加。On the other hand, in the scroll compressor 1 of this embodiment, since the above-mentioned circumferential groove 36 is provided, oil at discharge pressure is introduced into the circumferential groove 36 . Therefore, as shown in the pressure distribution on the orbiting scroll cover plate shown on the right side in FIG. 4 , the orbiting scroll 8 is pushed toward the side where the circumferential groove 36 is provided by the oil having discharge pressure introduced thereto. The downward pressing force increases by an amount corresponding to the area 38 indicated by hatching in FIG. 4 . Therefore, it is possible to suppress an increase in the pressing force at the position where the cover plate of the orbiting scroll 8 most strongly abuts the cover plate surface of the fixed scroll.
另外，流入到周向槽36内的润滑油在固定涡盘7的盖板面7e与回旋涡盘8的盖板面8e之间的微小的间隙一边润滑一边通过，并流向背压室18、吸入室20或压缩室13，因此，盖板面7e、8e处的润滑状态良好，能够提高可靠性。In addition, the lubricating oil flowing into the circumferential groove 36 passes while lubricating the minute gap between the cover surface 7e of the fixed scroll 7 and the cover surface 8e of the orbiting scroll 8, and flows to the back pressure chamber 18, Because the suction chamber 20 or the compression chamber 13 is in a good lubrication state at the cover surfaces 7e and 8e, reliability can be improved.
接下来，使用图3～图6，对作用于回旋涡盘8的与轴向正交的方向的力、以及该力在旋转一圈中的变化进行说明。Next, the force acting on the orbiting scroll 8 in a direction orthogonal to the axial direction and the change of the force during one rotation will be described using FIGS. 3 to 6 .
由于压缩作用，在涡旋压缩机1的运转中的回旋涡盘8不仅轴向的力，还产生切线方向及半径方向的力。回旋涡盘的某位相处的这些与轴向正交的方向的力的合力用图3、图4中的Fg表示。另外，作为Fg的反作用力的使回旋涡盘8回旋运动的力Fr作用于回旋轴承11。Due to the compression effect, the orbiting scroll 8 during operation of the scroll compressor 1 generates not only axial force but also tangential and radial force. The resultant force of these forces in directions orthogonal to the axial direction at a certain position of the orbiting scroll is represented by Fg in Figures 3 and 4. In addition, the force Fr that causes the orbiting scroll 8 to orbit as a reaction force of Fg acts on the orbiting bearing 11 .
在此，Fg及Fr彼此为反向，而且其作用点在轴向上分离，因此如箭头M所示地，在回旋涡盘8产生力矩。该力矩M为要使回旋涡盘8倾斜的所谓的颠覆力矩。由于该颠覆力矩，回旋涡盘8的盖板面8e被局部性地强力推压于固定涡盘7的盖板面7e。在力矩M如图3、图4所示地作用的情况下，该强力推压的位置为盖板的右侧。Here, Fg and Fr are in opposite directions to each other, and their action points are separated in the axial direction. Therefore, as shown by arrow M, a moment is generated in the orbiting scroll 8 . This moment M is a so-called overturning moment that causes the orbiting scroll 8 to tilt. Due to this overturning moment, the cover surface 8e of the orbiting scroll 8 is locally strongly pressed against the cover surface 7e of the fixed scroll 7. When the moment M acts as shown in FIGS. 3 and 4 , the position of this strong push is on the right side of the cover plate.
此外，随着回旋涡盘8的回旋运动，Fg及Fr的朝向及大小变化，因此颠覆力矩的方向和大小也变化。这就是所谓的回旋涡盘的摆动运动的原因。另外，回旋涡盘8的盖板面8e被局部性地强力推压的位置及其大小在旋转一圈中也变化。In addition, as the orbiting scroll 8 rotates, the directions and sizes of Fg and Fr change, so the direction and size of the overturning moment also change. This is the cause of the so-called oscillating motion of the orbiting scroll. In addition, the position where the cover surface 8e of the orbiting scroll 8 is strongly pressed locally and its size also change during one rotation.
图5是说明涡旋压缩机旋转一圈中的载荷Fg相对于曲柄角的变化的图表，图6是说明涡旋压缩机的曲柄角与压缩室内压力的变化的关系的图表。FIG. 5 is a graph illustrating the change in load Fg with respect to the crank angle during one rotation of the scroll compressor, and FIG. 6 is a graph illustrating the relationship between the crank angle of the scroll compressor and changes in the compression chamber pressure.
图5中的曲线46示出了旋转一圈中的载荷Fg的变化的一例，该图5的例中，在曲柄角为大致180度的位置47，Fg最大。此外，图5是一例，载荷Fg成为最大的曲柄角的位置47一般由涡盘涡卷的卷数、吐出开始角度等决定。Curve 46 in FIG. 5 shows an example of change in load Fg during one rotation. In the example of FIG. 5 , Fg is maximum at position 47 where the crank angle is approximately 180 degrees. In addition, FIG. 5 is an example. The crank angle position 47 at which the load Fg reaches the maximum is generally determined by the number of scroll wraps, the discharge start angle, and the like.
例如，图6示出了涡盘涡卷的卷数和吐出开始角度决定的某特定的涡旋压缩机中的曲柄角与回旋内线侧压缩室13a的压力50a及回旋外线侧压缩室13b的压力50b的关系。此外，图6所示的例中示出了回旋内线侧压缩室13a和回旋外线侧压缩室13b的圈数不同的所谓的非对称涡卷下的例，另外，示出了所有运转条件中载荷Fg的最大值成为最大的高压力比的运转条件下的例。进一步地，将回旋外线侧压缩室13b完成吸入的时刻设为曲柄角0度。For example, FIG. 6 shows the crank angle, the pressure 50a of the orbiting inner side compression chamber 13a, and the pressure of the orbiting outer side compression chamber 13b in a specific scroll compressor determined by the number of scroll wraps and the discharge start angle. 50b relationship. In addition, the example shown in FIG. 6 shows an example of a so-called asymmetric scroll in which the number of turns of the orbiting inner side compression chamber 13a and the orbiting outer side compression chamber 13b is different, and also shows the load under all operating conditions. The maximum value of Fg becomes the largest example under the operating condition of high pressure ratio. Furthermore, the time when suction of the orbiting outer line side compression chamber 13b is completed is set to 0 degrees of crank angle.
此外，曲柄角原本为0度至360度，但在涡旋压缩机的情况下，通常从一个压缩室完成吸入到开始吐出为旋转一圈以上。另外，在非对称涡卷的情况下，回旋内线侧压缩室13a在回旋外线侧压缩室13b完成吸入后曲柄角前进大致180度的位置完成吸入并开始压缩。因此，为了便于说明，图6的横轴的曲柄角设为0度至720度。In addition, the crank angle is originally 0 degrees to 360 degrees, but in the case of a scroll compressor, it usually takes more than one rotation from the completion of suction to the start of discharge in one compression chamber. In the case of an asymmetric scroll, the orbiting inner side compression chamber 13a completes suction and starts compression at a position where the crank angle advances by approximately 180 degrees after the orbiting outer side compression chamber 13b completes suction. Therefore, for convenience of explanation, the crank angle of the horizontal axis in FIG. 6 is set to 0 degrees to 720 degrees.
如图6所示，当曲柄角变化时，各压缩室内的压力也变化。如图2所示，涡旋压缩机1具有多个压缩室13，各个压缩室13的压力如图6那样变化。另外，这些各压缩室13内的压力作用于回旋涡盘8的涡卷8b。它们的合力为上述载荷Fg(气体载荷)，该Fg如图5中的曲线46那样变化。As shown in Figure 6, when the crank angle changes, the pressure in each compression chamber also changes. As shown in FIG. 2 , the scroll compressor 1 has a plurality of compression chambers 13 , and the pressure in each compression chamber 13 changes as shown in FIG. 6 . In addition, the pressure in each of these compression chambers 13 acts on the wrap 8 b of the orbiting scroll 8 . Their resultant force is the above-mentioned load Fg (gas load), and this Fg changes like the curve 46 in FIG. 5 .
在该图5所示的例中，在回旋内线侧压缩室13a开始吐出的曲柄角180度(图6中，360度+180度＝540度的位置相当于开始吐出的曲柄角180度的位置)，Fg成为最大，与之相伴地，颠覆力矩也成为最大。In the example shown in FIG. 5 , the crank angle of 180 degrees at which discharge starts in the swirling inner line side compression chamber 13 a (in FIG. 6 , the position of 360 degrees + 180 degrees = 540 degrees corresponds to the position of 180 degrees at crank angle at which discharge starts). ), Fg becomes the largest, and along with it, the overturning moment also becomes the largest.
通过图2～图4说明在作用于回旋涡盘的载荷成为最大的上述曲柄角下，回旋涡盘的盖板最强力地抵接于固定涡盘的盖板面的位置。图2是表示曲柄角为180度的状态的图，图3、图4示出了曲柄角180度时的纵剖视图，是作用于回旋涡盘的载荷成为最大的状态的图。如根据由图3、图4所示的Fg及Fr的力的方向产生的力矩M可知地，回旋涡盘8的盖板最强力地抵接于固定涡盘7的盖板面的位置为盖板面的右侧的位置。The position where the cover plate of the orbiting scroll most strongly abuts the cover plate surface of the fixed scroll at the crank angle at which the load acting on the orbiting scroll becomes maximum will be explained with reference to FIGS. 2 to 4 . FIG. 2 is a diagram showing a state where the crank angle is 180 degrees. FIGS. 3 and 4 are longitudinal cross-sectional views when the crank angle is 180 degrees, and are diagrams showing the maximum load acting on the orbiting scroll. As can be seen from the moment M generated by the directions of the forces Fg and Fr shown in FIGS. 3 and 4 , the position where the cover plate of the orbiting scroll 8 most strongly abuts the cover surface of the fixed scroll 7 is: The position on the right side of the cover.
该位置大致相当于图2中虚线44表示的范围。也就是，通过在该位置设置上述周向槽36，能够向压缩机旋转一圈中回旋涡盘8的盖板8a被最强力地推压于固定涡盘7的盖板面7e的位置供给大致吐出压力的高压的润滑油。从而，能够防止盖板面7e、8e产生磨损、咬合、或烧熔等问题，能够提高压缩机的可靠性。This position roughly corresponds to the range indicated by the dotted line 44 in FIG. 2 . That is, by providing the circumferential groove 36 at this position, supply can be supplied to the position where the cover plate 8a of the orbiting scroll 8 is most strongly pressed against the cover plate surface 7e of the fixed scroll 7 during one revolution of the compressor. High-pressure lubricating oil that discharges roughly the pressure. Therefore, it is possible to prevent problems such as wear, seizure, or burning of the cover surfaces 7e and 8e, thereby improving the reliability of the compressor.
设置上述周向槽36的位置如以上所述。The position at which the circumferential groove 36 is provided is as described above.
接下来，对上述周向槽36优选的形状进行说明。周向槽的形状、即周向的长度在例如如圆环状、C字形状等那样超过半圈的情况下，有可能下压力过大，产生回旋涡盘8从固定涡盘7分离的脱离现象。另外，供给到上述周向槽36的油向吸入室20、压缩室13泄漏的量也增多。即，由于油泄漏的流路面积表示为周向槽36的长度与盖板面7e、8e间的微小间隙的长度的积，因此周向槽越长，越向吸入室20、压缩室13流入过大量的润滑油，加热制冷剂气体，使加热损失越增大。Next, a preferred shape of the circumferential groove 36 will be described. If the shape of the circumferential groove, that is, the length in the circumferential direction exceeds half a turn, for example, such as an annular shape or a C-shaped shape, the downward force may be too great, causing the orbiting scroll 8 to separate from the fixed scroll 7 . Phenomenon. In addition, the oil supplied to the circumferential groove 36 leaks into the suction chamber 20 and the compression chamber 13 in an increased amount. That is, since the flow path area of oil leakage is expressed as the product of the length of the circumferential groove 36 and the length of the minute gap between the cover surfaces 7e and 8e, the longer the circumferential groove is, the more oil flows into the suction chamber 20 and the compression chamber 13. Excessive lubricating oil will heat the refrigerant gas and increase the heating loss.
因此，在本实施例中，将上述周向槽36设为由大致圆弧的一部分构成，且其两端处于包括在图5所示的载荷Fg成为最大时回旋涡盘8的盖板8a被最强力地推压的位置在内大致±90度的范围内(图2中的θ1的范围内)的形状。由此，能够以向推压力强且最需要润滑的部位有效地给油的方式配置周向槽36，能够使周向槽36的长度更短。从而，能够抑制脱离现象、加热损失的发生，并且抑制推压力的增加，防止盖板面7e、8e产生磨损、咬合、或烧熔等问题，可以提高压缩机的可靠性。Therefore, in this embodiment, the circumferential groove 36 is formed as a substantially arcuate part, and both ends thereof are positioned so that the cover plate 8a of the orbiting scroll 8 is included when the load Fg shown in FIG. 5 becomes the maximum. A shape that is roughly within a range of ±90 degrees (within the range of θ1 in Figure 2) from the position where the most powerful force is pressed. Thereby, the circumferential groove 36 can be arranged so that oil can be effectively supplied to the part which requires the most lubrication with strong pressing force, and the length of the circumferential groove 36 can be made shorter. Therefore, the occurrence of detachment and heating loss can be suppressed, and the increase in pressing force can be suppressed to prevent problems such as wear, seizure, or melting of the cover surfaces 7e and 8e, thereby improving the reliability of the compressor.
此外，图5所示的区间48示出了包括载荷Fg成为最大的曲柄角的位置47的大致±90度的范围、通过该区间48能够覆盖能够载荷Fg的值比平均值显著大的范围。从而，在相当于该区间48的盖板面7e或8e的位置设置上述周向槽36。即，在回旋涡盘8的盖板8a被强力地推压于固定涡盘7的盖板面7e的区域的盖板面7e或8e的位置设置上述周向槽36。由此，能够向推压力比平均值显著大的盖板面的区域供给润滑油。In addition, the interval 48 shown in FIG. 5 shows a range of approximately ±90 degrees including the crank angle position 47 where the load Fg becomes the maximum. This interval 48 can cover a range in which the value of the load Fg can be significantly larger than the average value. Therefore, the circumferential groove 36 is provided at a position corresponding to the cover surface 7e or 8e of the section 48. That is, the circumferential groove 36 is provided at a position on the cover surface 7e or 8e in a region where the cover plate 8a of the orbiting scroll 8 is strongly pressed against the cover surface 7e of the fixed scroll 7. This allows lubricating oil to be supplied to the area of the cover surface where the pressing force is significantly larger than the average value.
这样，根据上述的本实施例，在回旋涡盘8的盖板8a被强力地推压于固定涡盘7的盖板面7e的区域的盖板面的位置设置周向槽36，因此能够向推压力比平均值显著大的盖板面的区域供给润滑油。从而，能够向推压力强且最需要润滑的部位有效给油,因此，能够进一步缩短周向槽36的长度，能够抑制脱离现象、加热损失的发生，并且抑制推压力的增加，防止盖板面发生磨损、咬合、烧熔等，提高压缩机的可靠性。In this way, according to the present embodiment described above, the circumferential groove 36 is provided at the position of the cover surface of the area where the cover plate 8a of the orbiting scroll 8 is strongly pressed against the cover surface 7e of the fixed scroll 7, so that it is possible to Lubricating oil is supplied to the area of the cover plate where the pushing force is significantly greater than the average. Therefore, oil can be effectively supplied to the parts where the pressing force is strong and most need lubrication. Therefore, the length of the circumferential groove 36 can be further shortened, the occurrence of detachment phenomenon and heating loss can be suppressed, and the increase of the pressing force can be suppressed to prevent the cover plate surface from cracking. The occurrence of wear, seizure, melting, etc. will improve the reliability of the compressor.
实施例2Example 2
引用图5，并且使用图7，对本发明的涡旋压缩机的实施例2进行说明。图7是表示本实施例2的涡旋压缩机的图，是相当于图2的图。此外，在图7中，标注了与图1～图6相同的符号的部分表示相同或相当的部分，对与实施例1相同的部分省略说明，以与实施例1不同的部分为中心进行说明。Embodiment 2 of the scroll compressor of the present invention will be described with reference to FIG. 5 and using FIG. 7 . FIG. 7 is a diagram showing the scroll compressor according to the second embodiment, and is equivalent to FIG. 2 . In addition, in FIG. 7 , parts marked with the same reference numerals as in FIGS. 1 to 6 represent the same or equivalent parts. The description of the parts that are the same as those in Embodiment 1 will be omitted, and the description will focus on the parts that are different from Embodiment 1. .
作为高压力比的运转条件下的涡旋压缩机的特性，就图5中的曲线46而言，相对于载荷Fg成为最大的曲柄角的位置47，相比其左侧46a(回旋涡盘8的旋转滞后的方向即曲柄角小的侧，以下称为滞后角侧)，右侧46b(回旋涡盘8的旋转前进的方向即曲柄角大的侧，以下成为前进角侧)的倾斜度通常较缓和。这是因为，在仅通过压缩室13的容积减少进行的压缩成未压缩不足的高压力比的运转条件下，吐出开始后，制冷剂气体从吐出压力空间(吐出空间54)逆流，压缩室内的压力急剧上升至吐出压力，之后，随着曲柄角前进，将上升至吐出压力的制冷剂气体逐渐向吐出空间54排出。As a characteristic of the scroll compressor under the operating condition of a high pressure ratio, the curve 46 in FIG. 5 shows that the position 47 at which the crank angle becomes the largest with respect to the load Fg is smaller than the position 46a on the left side (the orbiting scroll 8 The inclination of the right side 46b (the direction in which the rotation of the orbiting scroll 8 advances, that is, the side with a large crank angle, hereinafter referred to as the advance angle side) is the direction in which the rotation retards, that is, the side with a small crank angle, hereinafter referred to as the retarded angle side. More moderate. This is because under operating conditions in which compression is performed only by reducing the volume of the compression chamber 13 to a high pressure ratio that is not sufficiently compressed, after the discharge is started, the refrigerant gas flows backward from the discharge pressure space (discharge space 54), and the refrigerant gas in the compression chamber 13 flows backward. The pressure rises sharply to the discharge pressure, and then, as the crank angle advances, the refrigerant gas that has risen to the discharge pressure is gradually discharged into the discharge space 54 .
因此，如图5、图7所示，在本实施例2中，以相当于区间48b的部分比相当于区间48a的部分长的方式形成上述周向槽36。具体而言，如图7所示，以如下方式形成上述周向槽36：相对于与作用于回旋涡盘8的载荷Fg成为最大的曲柄角的位置47(参照图5)对应地推压力比平均值显著大的盖板面的位置(回旋涡盘的盖板最强力地抵接于固定涡盘的盖板面的位置)47A(参照图7)，回旋涡盘8的旋转前进方向即曲柄角大的侧(前进角侧)θ1b比回旋涡盘8的旋转滞后的方向即曲柄角小的侧(滞后角侧)θ1a长。Therefore, as shown in FIGS. 5 and 7 , in the second embodiment, the circumferential groove 36 is formed such that the portion corresponding to the section 48 b is longer than the section corresponding to the section 48 a. Specifically, as shown in FIG. 7 , the circumferential groove 36 is formed such that the pressing force ratio corresponds to the position 47 (see FIG. 5 ) at which the load Fg acting on the orbiting scroll 8 becomes the maximum crank angle. The position 47A of the cover surface where the average value is significantly larger (the position where the cover plate of the orbiting scroll most strongly contacts the cover surface of the fixed scroll) 47A (see FIG. 7 ), the direction of rotation of the orbiting scroll 8 is The side with a large crank angle (advance angle side) θ1b is longer than the direction in which the rotation of the orbiting scroll 8 lags, that is, the side with a small crank angle (retarded angle side) θ1a.
通过这样地构成，在载荷Fg的值比平均值显著大的范围、即将周向槽36的长度设为相同的情况下，可以得到能够向推压力比平均值显著大的盖板面的区域更可靠地供给润滑油的效果。这样，根据本实施例2，能够进一步抑制因向周向槽36供给的润滑油而引起的加热损失，并且更广地覆盖载荷Fg的值比平均值显著大的范围。By configuring in this way, in a range where the value of the load Fg is significantly larger than the average value, that is, when the lengths of the circumferential grooves 36 are made the same, it is possible to obtain a region of the cover surface where the pressing force is significantly larger than the average value. Reliable supply of lubricant. In this way, according to the second embodiment, it is possible to further suppress the heating loss caused by the lubricating oil supplied to the circumferential groove 36 and to cover a wider range in which the value of the load Fg is significantly larger than the average value.
其它结构与上述的实施例1相同。Other structures are the same as the above-mentioned Embodiment 1.
实施例3Example 3
引用图5，并且使用图8对本发明的涡旋压缩机的实施例3进行说明。图8是表示本实施例3的涡旋压缩机的图，是相当于图2的图。此外，图8中，标注了与图1～图6相同的符号的部分表示相同或相当的部分，对于与实施例1相同的部分，省略说明，以与实施例1不同的部分为中心进行说明。Embodiment 3 of the scroll compressor of the present invention will be described with reference to FIG. 5 and using FIG. 8 . FIG. 8 is a diagram showing the scroll compressor according to the third embodiment, and is equivalent to FIG. 2 . In addition, in FIG. 8 , parts marked with the same symbols as in FIGS. 1 to 6 represent the same or equivalent parts. Descriptions of the parts that are the same as those in Embodiment 1 will be omitted, and the description will focus on parts that are different from Embodiment 1. .
图2所示的实施例1中，在固定涡盘7的盖板面7e设置周向槽36，并且在其一端部设置圆形的槽部36a。另外，在回旋涡盘8设置用于将第一空间33内的润滑油供给至上述周向槽36的通路37，且使该通路37的端部与上述圆形的槽部36a连通。上述通路37的端部随着回旋涡盘8的回旋运动以其回旋半径进行回旋运动。因此，上述圆形的槽部36a以在上述通路37的端部进行回旋运动的全范围连通的方式构成上述回旋半径以上的半径的大小的圆。另外，上述周向槽36中的除了槽部36a的部分形成为比槽部36a的径小的宽度。In Embodiment 1 shown in FIG. 2 , a circumferential groove 36 is provided on the cover plate surface 7 e of the fixed scroll 7 and a circular groove portion 36 a is provided on one end portion thereof. In addition, the orbiting scroll 8 is provided with a passage 37 for supplying the lubricating oil in the first space 33 to the circumferential groove 36, and an end portion of the passage 37 is communicated with the circular groove portion 36a. The end portion of the passage 37 makes an orbiting motion according to the orbiting radius of the orbiting scroll 8 . Therefore, the circular groove portion 36a forms a circle having a radius equal to or greater than the radius of gyration so as to communicate with the end portion of the passage 37 over the entire range of the gyration motion. In addition, the portion of the circumferential groove 36 except the groove portion 36a is formed to have a width smaller than the diameter of the groove portion 36a.
与之相对，在本实施例3中构成为，设于回旋涡盘8的通路37与上述周向槽36连通的区间仅在包括载荷Fg成为最大的曲柄角的大致±90度的范围内。该连通的区间相当于图5所示的区间48。即，在上述实施例1中构成，始终从上述通路37向上述周向槽36供给润滑油，而在本实施例3中，仅在上述载荷Fg的值比平均值显著大的定时间歇性地向周向槽36供给润滑油。On the other hand, in the third embodiment, the section in which the passage 37 provided in the orbiting scroll 8 communicates with the circumferential groove 36 is only within a range of approximately ±90 degrees including the crank angle at which the load Fg becomes the maximum. This connected section corresponds to section 48 shown in FIG. 5 . That is, in the first embodiment, the lubricating oil is always supplied from the passage 37 to the circumferential groove 36 . However, in the third embodiment, the lubricating oil is supplied intermittently only at the timing when the value of the load Fg is significantly larger than the average value. Lubricating oil is supplied to the circumferential groove 36 .
通过图8说明实现上述情况的具体的结构。在周向槽36的一端部以进行回旋运动的上述通路37仅在载荷Fg的值比平均值显著大的定时间歇性地连通的方式形成有圆弧状的槽部39。该圆弧状的槽部39构成为，在回旋涡盘8进行回旋运动时，仅在包括载荷Fg成为最大的曲柄角的大致±90度的范围内与上述通路37的端部连通。圆弧状的上述槽部39优选形成为其槽中心具有与回旋涡盘8的回旋半径相同的半径的圆弧，但只要以上述通路37的端部仅在包括Fg成为最大的曲柄角的大致±90度的范围内与上述槽部39连通的方式形成上述槽部39即可，槽部39的形状不限于圆弧状的槽部，也可以采用圆形、矩形等形状。A specific structure for realizing the above situation will be described with reference to FIG. 8 . An arc-shaped groove portion 39 is formed at one end portion of the circumferential groove 36 so that the passage 37 that performs rotational motion communicates intermittently only at timings when the value of the load Fg is significantly larger than the average value. The arc-shaped groove portion 39 is configured to communicate with the end portion of the passage 37 only within a range of approximately ±90 degrees including the crank angle at which the load Fg becomes maximum when the orbiting scroll 8 performs the orbiting motion. The arc-shaped groove portion 39 is preferably formed as an arc with the groove center having the same radius as the orbiting radius of the orbiting scroll 8. However, as long as the end portion of the passage 37 is only approximately at the maximum crank angle including Fg. The groove portion 39 may be formed so as to communicate with the groove portion 39 within a range of ±90 degrees. The shape of the groove portion 39 is not limited to an arc-shaped groove portion, and may also be circular, rectangular, or other shapes.
在此，用图8中的点划线表示的圆45表示回旋涡盘8进行回旋运动时的上述通路37的轨迹。仅在该轨迹中的大致±90度的范围内即θ2的范围，上述通路37经由上述槽部39连通于上述周向槽36。Here, a circle 45 represented by a chain line in FIG. 8 represents the trajectory of the passage 37 when the orbiting scroll 8 performs orbiting motion. The passage 37 communicates with the circumferential groove 36 via the groove portion 39 only within a range of approximately ±90 degrees in this trajectory, that is, a range of θ2.
在上述通路37始终与上述周向槽36连通的情况下，始终作用下压力，与之相对，根据本实施例3，在旋转一圈中，仅在回旋涡盘8的盖板8a被最强力地推压于固定涡盘7的盖板面7e的定时能够向该被最强力地推压的位置供给润滑油。从而，能够仅在所需的定时仅向所需的部位高效地供给润滑油，因此能够进一步抑制脱离现象的发生、加热损失，并且能够抑制回旋涡盘的摆动运动。When the passage 37 is always connected to the circumferential groove 36 , downward pressure is always applied. On the other hand, according to the third embodiment, only the cover plate 8 a of the orbiting scroll 8 is pressed the strongest during one rotation. The timing of strongly pressing the cover plate surface 7e of the fixed scroll 7 enables lubricating oil to be supplied to the most strongly pressed position. Therefore, the lubricating oil can be efficiently supplied only to the required parts at the required timing, so that the occurrence of the detachment phenomenon and the heating loss can be further suppressed, and the oscillating motion of the orbiting scroll can be suppressed.
此外，在本实施例3中，上述周向槽36中的除了圆弧状的槽部39的部分，形成为比回旋涡盘8的回旋半径小的宽度。Furthermore, in the third embodiment, the portion of the circumferential groove 36 except the arc-shaped groove portion 39 is formed to have a width smaller than the orbiting radius of the orbiting scroll 8 .
实施例4Example 4
使用图9对本发明的涡旋压缩机的实施例4进行说明。图9是说明本实施例4的回旋涡盘的俯视图。此外，在图9中，标注了与图1～图6相同的符号的部分表示相同或相当的部分，对与实施例1相同的部分省略说明，以与实施例1不同的部分为中心进行说明。Embodiment 4 of the scroll compressor of the present invention will be described using FIG. 9 . FIG. 9 is a plan view illustrating the orbiting scroll of the fourth embodiment. In addition, in FIG. 9 , parts marked with the same reference numerals as in FIGS. 1 to 6 represent the same or equivalent parts. The description of the parts that are the same as those in Embodiment 1 will be omitted, and the description will focus on the parts that are different from Embodiment 1. .
在本实施例4中，与实施例1同样的点在于，在固定涡盘7的盖板面形成周向槽36，在其一端部侧形成圆形的槽部36a，在回旋涡盘8的盖板8a设有将第一空间33(参照图1)内的润滑油供给至上述周向槽36的通路37。In the fourth embodiment, the same point as in the first embodiment is that a circumferential groove 36 is formed on the cover surface of the fixed scroll 7, a circular groove portion 36a is formed on one end side, and a circumferential groove 36 is formed on the cover surface of the orbiting scroll 8. The cover plate 8a is provided with a passage 37 for supplying lubricating oil in the first space 33 (see FIG. 1 ) to the circumferential groove 36 .
进一步地，在本实施例4中，如图9所示，将作为用于将供给至上述周向槽36的润滑油向图2所示的吸入室20或压缩室13漏出的单元的狭缝(油漏出单元)40设于回旋涡盘8的盖板面8e。该狭缝40将上述周向槽36和吸入室20或压缩室13始终或间歇地连通。Furthermore, in the fourth embodiment, as shown in FIG. 9 , a slit is used as a unit for leaking the lubricating oil supplied to the circumferential groove 36 to the suction chamber 20 or the compression chamber 13 shown in FIG. 2 (Oil leakage unit) 40 is provided on the cover surface 8e of the orbiting scroll 8. The slit 40 communicates the circumferential groove 36 with the suction chamber 20 or the compression chamber 13 either always or intermittently.
在始终连通的情况下，只要以即使回旋涡盘8进行回旋运动，狭缝40也始终使周向槽36和吸入室20或压缩室13连通的方式决定上述狭缝40的位置和长度即可。另外，在间歇性连通的情况下，只要以随着回旋涡盘8的回旋运动，上述狭缝40的一部分与上述周向槽36间歇性地连通、或者上述狭缝40的一部分与吸入室20或压缩室13间歇性地连通的方式决定上述狭缝40的位置和长度即可。In the case of constant communication, the position and length of the slit 40 may be determined so that the slit 40 always communicates with the circumferential groove 36 and the suction chamber 20 or the compression chamber 13 even if the orbiting scroll 8 performs an orbiting motion. . In addition, in the case of intermittent communication, as long as a part of the slit 40 is intermittently communicated with the circumferential groove 36 or a part of the slit 40 is connected with the suction chamber 20 in accordance with the orbiting motion of the orbiting scroll 8 Or the position and length of the slit 40 may be determined in such a manner that the compression chamber 13 is intermittently connected.
此外，在本实施例中设置了一个上述狭缝40，但是也可以设置多个。另外，也可以构成为，作为油漏出单元，取代上述狭缝40而将一个以上的油兜设于回旋涡盘的盖板面8e，该油兜(油漏出单元)在上述周向槽36与吸入室20或压缩室13之间移动，将供给到上述周向槽36内的润滑油间歇性地移送到吸入室20或压缩室13。In addition, in this embodiment, one slit 40 is provided, but a plurality of slits 40 may be provided. In addition, as an oil leakage unit, one or more oil pockets may be provided on the cover surface 8e of the orbiting scroll instead of the slits 40, and the oil pockets (oil leakage units) may be formed between the circumferential groove 36 and the circumferential groove 36. The lubricating oil supplied to the circumferential groove 36 is intermittently transferred to the suction chamber 20 or the compression chamber 13 by moving between the suction chamber 20 or the compression chamber 13 .
其它结构与上述的实施例1相同。Other structures are the same as the above-mentioned Embodiment 1.
根据本实施例4的结构，能够使供给到周向槽36的油经由上述狭缝40、上述油兜顺畅地流出到吸入室20、压缩室13。从而，可得到如下效果：抑制供给到周向槽36的油在周向槽36滞留，能够在被因盖板面7e、8e的滑动而产生的发热加热为高温之前流出到上述吸入室20、压缩室13。另外，可以从上述通路37向上述周向槽36顺畅地供给新的润滑油。此外，供给到上述周向槽36的油的一部分对上述盖板面7e、8e间的微小间隙进行润滑后，流出到上述吸入室20、压缩室13。According to the structure of the fourth embodiment, the oil supplied to the circumferential groove 36 can smoothly flow out to the suction chamber 20 and the compression chamber 13 through the slit 40 and the oil pocket. Therefore, the following effect can be obtained: the oil supplied to the circumferential groove 36 is suppressed from being retained in the circumferential groove 36 and can flow out to the suction chamber 20 or 20 before being heated to a high temperature by the heat generated by the sliding of the cover surfaces 7e, 8e. Compression chamber 13. In addition, new lubricating oil can be smoothly supplied from the passage 37 to the circumferential groove 36 . In addition, part of the oil supplied to the circumferential groove 36 lubricates the minute gap between the cover surfaces 7e and 8e, and then flows out into the suction chamber 20 and the compression chamber 13.
本实施例中，能够利用上述狭缝40的深度、上述油兜的容积、个数来控制润滑油的流量，因此能够抑制加热损失的增大，并且能够向周向槽36供给能够确保盖板面7e、8e的良好的润滑状态的油量。In this embodiment, the depth of the slit 40 and the volume and number of the oil pockets can be used to control the flow rate of the lubricating oil. Therefore, the increase in heating loss can be suppressed, and the supply to the circumferential groove 36 can ensure the cover plate. The amount of oil in the good lubrication state of surfaces 7e and 8e.
实施例5Example 5
使用图10，对本发明的涡旋压缩机的实施例5进行说明。图10是说明本实施例5的固定涡盘的仰视图。此外，在图10中，标注了与图1～图6相同的符号的部分表示相同或相当的部分，对与实施例1相同的部分省略说明，以与实施例1不同的部分为中心进行说明。Embodiment 5 of the scroll compressor of this invention is demonstrated using FIG. 10. FIG. 10 is a bottom view illustrating the fixed scroll of the fifth embodiment. In addition, in FIG. 10 , parts marked with the same reference numerals as in FIGS. 1 to 6 represent the same or equivalent parts. The description of the parts that are the same as those in Embodiment 1 will be omitted, and the description will focus on the parts that are different from Embodiment 1. .
本实施例5也与上述实施例4同样地设有使供给到周向槽36的润滑油向吸入室20或压缩室13漏出的油漏出单元。在上述实施例4中对在回旋涡盘8的盖板面8e设置作为油漏出单元的狭缝40的例进行了说明，但在本实施例5中，在固定涡盘7的盖板面7e设置作为使供给到上述周向槽36的润滑油向吸入室20或压缩室13漏出的油漏出单元的狭缝41。This Embodiment 5 is also provided with an oil leakage unit for leaking the lubricating oil supplied to the circumferential groove 36 into the suction chamber 20 or the compression chamber 13, similarly to the above-mentioned Embodiment 4. In the above-mentioned Embodiment 4, the example in which the slit 40 as the oil leakage means is provided on the cover surface 8e of the orbiting scroll 8 has been described. However, in the present Embodiment 5, the cover surface 7e of the fixed scroll 7 is provided. The slit 41 is provided as an oil leakage means for causing the lubricating oil supplied to the circumferential groove 36 to leak into the suction chamber 20 or the compression chamber 13 .
即，如图10所示，在本实施例中，在固定涡盘7的盖板面7e设有周向槽36，在该周向槽36的一端部侧设有圆形的槽部36a。进一步地，在本实施例中，在固定涡盘7的盖板面7e设有与上述周向槽36的与上述槽部36a相反的侧连通的狭缝41。上述狭缝41构成为还与吸入室20或压缩室13连通。That is, as shown in FIG. 10 , in this embodiment, the circumferential groove 36 is provided on the cover surface 7 e of the fixed scroll 7 , and the circular groove portion 36 a is provided on one end side of the circumferential groove 36 . Furthermore, in this embodiment, the cover plate surface 7e of the fixed scroll 7 is provided with a slit 41 communicating with the side of the circumferential groove 36 opposite to the groove portion 36a. The slit 41 is configured to communicate with the suction chamber 20 or the compression chamber 13 as well.
其它结构与上述的实施例1相同。此外，上述狭缝41不限于一个，也可以沿周向槽36设置多个。Other structures are the same as the above-mentioned Embodiment 1. In addition, the above-mentioned slit 41 is not limited to one, and a plurality of slits 41 may be provided along the circumferential groove 36 .
即使如本实施例5地构成为将作为油漏出单元的狭缝41设于固定涡盘7的盖板面7e，也能够使供给到周向槽36的油顺畅地向吸入室20或压缩室13漏出，因此能够得到与上述的实施例4同样的效果。Even if the slit 41 as the oil leakage means is provided on the cover plate surface 7e of the fixed scroll 7 as in the fifth embodiment, the oil supplied to the circumferential groove 36 can be smoothly transported to the suction chamber 20 or the compression chamber. 13 leaks out, the same effect as that of the above-mentioned Embodiment 4 can be obtained.
实施例6Example 6
使用图11对本发明的涡旋压缩机的实施例6进行说明。图11是说明本实施例6的回旋涡盘的纵剖视图。此外，在图11中，标注了与图1～图6相同的符号的部分表示相同或相当的部分，对与实施例1相同的部分省略说明，以与实施例1不同的部分为中心进行说明。Embodiment 6 of the scroll compressor of the present invention will be described using FIG. 11 . Fig. 11 is a longitudinal sectional view illustrating the orbiting scroll of the sixth embodiment. In addition, in FIG. 11 , parts marked with the same reference numerals as in FIGS. 1 to 6 represent the same or equivalent parts. The description of the parts that are the same as those in Embodiment 1 will be omitted, and the description will focus on the parts that are different from Embodiment 1. .
在本实施例6的涡旋压缩机中，与图1所示的实施例1同样地，在回旋涡盘8的盖板8a具备用于将第一空间33内的润滑油供给至周向槽36的通路37。本实施例6中，除了实施例1的结构，还如图11所示地以使上述通路37的一部分的通路截面积变小的方式设置节流部件42。In the scroll compressor of Embodiment 6, similarly to Embodiment 1 shown in FIG. 1 , the cover plate 8 a of the orbiting scroll 8 is provided with a device for supplying the lubricating oil in the first space 33 to the circumferential groove. 36 passage 37. In the sixth embodiment, in addition to the structure of the first embodiment, a throttling member 42 is provided so as to reduce the passage cross-sectional area of a part of the passage 37 as shown in FIG. 11 .
通过在上述通路37设置节流部件42，从第一空间33引导至通路37的润滑油通过因上述节流部件42而通路截面积小的部分时，发生压力损失，压力降低。因此，供给到周向槽36的润滑油的压力为比作为吐出压力的第一空间33的压力低的压力。By providing the throttle member 42 in the passage 37 , when the lubricating oil guided from the first space 33 to the passage 37 passes through a portion of the passage with a small cross-sectional area due to the throttle member 42 , pressure loss occurs and the pressure decreases. Therefore, the pressure of the lubricating oil supplied to the circumferential groove 36 is lower than the pressure of the first space 33 which is the discharge pressure.
在当将第一空间33内的吐出压力的润滑油经由通路37直接供给到上述周向槽36时，下压回旋涡盘8的力过大的情况下，也可以应用本实施例6。即，通过在上述通路37设置节流部件42，能够将向周向槽36供给的润滑油的压力抑制为比吐出压力低，因此能够避免下压回旋涡盘8的力过大，能够将回旋涡盘8以合适的推压力推压于固定涡盘。This Embodiment 6 can also be applied when the force for depressing the orbiting scroll 8 is too large when the lubricating oil at the discharge pressure in the first space 33 is directly supplied to the circumferential groove 36 via the passage 37 . That is, by providing the throttling member 42 in the passage 37, the pressure of the lubricating oil supplied to the circumferential groove 36 can be suppressed to be lower than the discharge pressure. Therefore, excessive force for depressing the orbiting scroll 8 can be avoided, and the return force can be reduced. The scroll 8 is pressed against the fixed scroll with an appropriate pressing force.
其它结构与上述的实施例1相同。Other structures are the same as the above-mentioned Embodiment 1.
实施例7Example 7
使用图12对本发明的涡旋压缩机的实施例7进行说明。图12是说明本实施例7的回旋涡盘的俯视图。此外，在图12中，标注了与图1～图6相同的符号的部分表示相同或相当的部分，对与实施例1相同的部分省略说明，以与实施例1不同的部分为中心进行说明。Embodiment 7 of the scroll compressor of the present invention will be described using FIG. 12 . FIG. 12 is a plan view illustrating the orbiting scroll of the seventh embodiment. In addition, in FIG. 12 , parts marked with the same reference numerals as in FIGS. 1 to 6 represent the same or equivalent parts. The description of the parts that are the same as those in Embodiment 1 will be omitted, and the description will focus on the parts that are different from Embodiment 1. .
在上述的实施例1中，在固定涡盘7的盖板面设置周向槽36，经由设于回旋涡盘8的盖板8a的通路37将第一空间33内的润滑油供给至上述周向槽36。In the above-described Embodiment 1, the circumferential groove 36 is provided on the cover plate surface of the fixed scroll 7, and the lubricating oil in the first space 33 is supplied to the circumferential surface through the passage 37 provided in the cover plate 8a of the orbiting scroll 8. To slot 36.
与之相对，在本实施例7中，将上述周向槽36不是形成于固定涡盘7的盖板面7e，而是形成于回旋涡盘8的盖板面8e。另外，关于用于向设于回旋涡盘8的上述周向槽36引导第一空间33内的润滑油的通路37，与实施例1同样地设于回旋涡盘8的盖板8a。此外，上述通路37的第一空间33侧与实施例同样地在回旋凸起部8d的内侧开口，但上述通路37的周向槽36侧与该周向槽36直接连通。On the other hand, in the seventh embodiment, the circumferential groove 36 is formed not on the cover surface 7e of the fixed scroll 7 but on the cover surface 8e of the orbiting scroll 8. In addition, the passage 37 for guiding the lubricating oil in the first space 33 to the circumferential groove 36 provided in the orbiting scroll 8 is provided in the cover plate 8 a of the orbiting scroll 8 in the same manner as in the first embodiment. In addition, the first space 33 side of the passage 37 opens inside the convoluted boss 8 d as in the embodiment, but the circumferential groove 36 side of the passage 37 is directly connected to the circumferential groove 36 .
当如本实施例地在回旋涡盘8的盖板面8e形成周向槽36时，周向槽36随着回旋涡盘8的回旋运动而移动，因此能够使润滑油扩散到盖板面7e、8e的更广的范围，能够使润滑状态更良好。When the circumferential groove 36 is formed in the cover surface 8e of the orbiting scroll 8 as in this embodiment, the circumferential groove 36 moves with the orbiting motion of the orbiting scroll 8, so that the lubricating oil can be diffused to the cover surface 7e , the wider range of 8e can make the lubrication condition better.
其它结构与上述的实施例1相同。Other structures are the same as the above-mentioned Embodiment 1.
实施例8Example 8
使用图13对本发明的涡旋压缩机的实施例8进行说明。图13是说明本实施例8的固定涡盘的仰视图。此外，图13中，标注了与图1～图6相同的符号的部分表示相同或相当的部分，对与实施例1相同的部分省略说明，以与实施例1不同的部分为中心进行说明。Embodiment 8 of the scroll compressor of the present invention will be described using FIG. 13 . FIG. 13 is a bottom view illustrating the fixed scroll of the eighth embodiment. In addition, in FIG. 13 , parts marked with the same reference numerals as in FIGS. 1 to 6 represent the same or equivalent parts. The description of the parts that are the same as those in Embodiment 1 will be omitted, and the description will focus on the parts that are different from Embodiment 1.
在本实施例8中，在设有周向槽36的固定涡盘7的盖板面7e上的设有上述周向槽36的范围以外的区域(图13中的θ1c以外的范围的盖板面7e)设有与背压室(第二空间)18连通的至少一个背压槽43。如图13所示，上述背压槽43形成为在设有周向槽36的用上述θ1c表示的区域以外的区域沿周向延伸。上述背压室18为吐出压力与吸入压力之间的压力(中间压力)，能够将该背压室18的润滑油引导至固定涡盘7的盖板面7e。此外，上述背压槽43不限于一条，也可以设置多条。In the eighth embodiment, on the cover surface 7e of the fixed scroll 7 provided with the circumferential groove 36, the area other than the range in which the circumferential groove 36 is provided (the cover plate in the range other than θ1c in FIG. 13 Surface 7e) is provided with at least one back pressure groove 43 communicating with the back pressure chamber (second space) 18. As shown in FIG. 13 , the back pressure groove 43 is formed to extend in the circumferential direction in an area other than the area indicated by θ1c where the circumferential groove 36 is provided. The back pressure chamber 18 has a pressure (intermediate pressure) between the discharge pressure and the suction pressure, and can guide the lubricating oil in the back pressure chamber 18 to the cover surface 7 e of the fixed scroll 7 . In addition, the above-mentioned back pressure groove 43 is not limited to one, and a plurality of back pressure grooves 43 may be provided.
通过形成本实施例的结构，对于回旋涡盘8的盖板8a最强力地抵接于固定涡盘7的盖板面7e的位置，由上述周向槽36赋予适当的下压力，并且能够进行设有周向槽36的盖板面附近的润滑。另外，由于设有上述背压槽43，因此向设有上述周向槽36的部分以外的盖板面的区域也能够供给背压室18内的润滑油，能够将盖板面整体的润滑状态保持良好。By forming the structure of this embodiment, the circumferential groove 36 can impart an appropriate downward force to the position where the cover plate 8a of the orbiting scroll 8 most strongly abuts against the cover plate surface 7e of the fixed scroll 7, and can Lubrication is performed near the cover surface where the circumferential groove 36 is provided. In addition, since the back pressure groove 43 is provided, the lubricating oil in the back pressure chamber 18 can also be supplied to the area of the cover surface other than the portion where the circumferential groove 36 is provided, and the lubricating state of the entire cover surface can be improved. keep great.
其它结构与上述的实施例1相同。Other structures are the same as the above-mentioned Embodiment 1.
实施例9Example 9
使用图14对本发明的实施例9进行说明。图14是说明使用了本发明的涡旋压缩机的空调机的一例的冷冻循环结构图。Example 9 of the present invention will be described using FIG. 14 . Fig. 14 is a refrigeration cycle structural diagram illustrating an example of an air conditioner using the scroll compressor of the present invention.
图14中，1是涡旋压缩机，60是四通阀，61是室外侧热交换器(制冷运转时为冷凝器，制热运转时为蒸发器)，62是由电子膨胀阀等构成的膨胀阀，63是室内侧热交换器(冷房运转时为蒸发器，制热运转时为冷凝器)，这些设备通过制冷剂配管64依次连接，构成空调机的冷冻循环。In Figure 14, 1 is a scroll compressor, 60 is a four-way valve, 61 is an outdoor heat exchanger (condenser during cooling operation, evaporator during heating operation), and 62 is composed of an electronic expansion valve, etc. The expansion valve 63 is an indoor heat exchanger (evaporator during cooling operation and condenser during heating operation). These devices are connected in sequence through refrigerant pipes 64 to form the refrigeration cycle of the air conditioner.
上述涡旋压缩机1使用了上述的实施例1～8的任一个记载的涡旋压缩机。通过在如图14所示的空调机组装高效率且高可靠性的本发明的各实施例记载的涡旋压缩机，能够提高空调机的运转效率。从而，能够大幅提高空调机的全年能量消费效率，能够得到全年的耗电量小且可靠性高的空调机。The scroll compressor 1 described above uses the scroll compressor described in any one of the above-described Examples 1 to 8. By incorporating the highly efficient and highly reliable scroll compressor described in each embodiment of the present invention into the air conditioner shown in FIG. 14 , the operating efficiency of the air conditioner can be improved. Therefore, the energy consumption efficiency of the air conditioner can be greatly improved throughout the year, and an air conditioner with low power consumption and high reliability throughout the year can be obtained.
如以上说明地，根据本发明的各实施例，在回旋涡盘8的盖板8a被强力地推压于固定涡盘7的盖板面7e的区域的盖板面的位置设有周向槽36，因此能够向推压力显著增大的盖板面的区域供给润滑油。从而，能够向推压力强且最需要润滑的部位有效地给油，能够进一步缩短周向槽36的长度，能够抑制脱离现象、加热损失的发生，并且抑制推压力的增加，从而能够得到效率高且可靠性高的涡旋压缩机。另外，通过将该涡旋压缩机应用于空调机，能够得到高效率且可靠性高的空调机。As explained above, according to each embodiment of the present invention, the circumferential groove is provided at the position of the cover surface of the area where the cover plate 8a of the orbiting scroll 8 is strongly pressed against the cover surface 7e of the fixed scroll 7 36, therefore, lubricating oil can be supplied to the area of the cover surface where the pressing force is significantly increased. Therefore, oil can be effectively supplied to the parts where the pressing force is strong and most need lubrication, the length of the circumferential groove 36 can be further shortened, the occurrence of detachment phenomenon and heating loss can be suppressed, and the increase of the pressing force can be suppressed, thereby achieving high efficiency. And highly reliable scroll compressor. In addition, by applying this scroll compressor to an air conditioner, an air conditioner with high efficiency and high reliability can be obtained.
此外，本发明不限于上述的实施例，包括各种变形例。另外，可以将某实施例的结构的一部分置换成其它实施例的结构，也可以在某实施例的结构追加其它实施例的结构。In addition, the present invention is not limited to the above-described embodiment, and includes various modifications. In addition, a part of the structure of a certain embodiment may be replaced with the structure of another embodiment, or a structure of another embodiment may be added to the structure of a certain embodiment.
进一步地，上述的实施例是为了容易理解地说明本发明而详细说明的例子，并非限定于必须具备说明的全部的结构。另外，对于各实施例的结构的一部分，可以进行其它结构的追加、削除、置换。Furthermore, the above-described embodiments are examples described in detail in order to easily understand the present invention, and are not necessarily limited to having all the structures described. In addition, a part of the structure of each embodiment may be added, deleted, or replaced with other structures.
符号说明Symbol Description
1—涡旋压缩机，2—压缩机构部，3—给油孔(贯通孔)，5—主轴承，6—吐出管，7—固定涡盘，7a—台板，7b—涡卷，7c—齿根，7d—支撑部，7e—盖板面，8—回旋涡盘，8a—盖板，8b—涡卷，8c—齿根，8d—凸起部(回旋凸起部)，8e—盖板面，9—密闭容器(壳体)，10—曲轴(旋转轴)，10a—曲柄部，11—回旋轴承，12—欧氏环，13—压缩室，13a—回旋内线侧压缩室，13b—回旋外线侧压缩室，14—吸入口，15—吐出口，16—马达部，16a—转子，16b—定子，17—框架，18—背压室(第二空间)，20—吸入室，21—给油泵，22—给油泵壳体，23—副轴承，24—横孔，25—润滑油吸入口，26a—排油孔，26b—排油管，28—吐出口，31—圆环槽，32—密封部件，33—第一空间，35—背压孔，36—周向槽，36a—槽部，37—通路，38—区域，39—槽部，40，41—狭缝(油漏出单元)，42—节流部件，43—背压槽，45—圆，46—曲线，47—载荷Fg最大的曲柄角的位置，47A—推压力比平均值显著增大的盖板面的位置，48—区间，50a—内线侧压缩室的压力，50b—外线侧压缩室的压力，52—马达室，53—贮油部，54—吐出空间，56—框架密封件，57—油槽，58—浅槽，60—四通阀，61—室外侧热交换器，62—膨胀阀，63—室内侧热交换器，64—制冷剂配管。1—Scroll compressor, 2—Compression mechanism part, 3—Oil feed hole (through hole), 5—Main bearing, 6—Discharge pipe, 7—Fixed scroll, 7a—Table plate, 7b—Scroll, 7c —Tooth root, 7d—support portion, 7e—cover surface, 8—orbiting scroll, 8a—cover plate, 8b—scroll, 8c—tooth root, 8d—convex portion (orbiting convex portion), 8e— Cover surface, 9—airtight container (casing), 10—crankshaft (rotating shaft), 10a—crank portion, 11—gyration bearing, 12—Euclidean ring, 13—compression chamber, 13a—gyration inner line side compression chamber, 13b—Swivel outer line side compression chamber, 14—Suction port, 15—Discharge port, 16—Motor part, 16a—Rotor, 16b—Stator, 17—Frame, 18—Back pressure chamber (second space), 20—Suction chamber , 21—oil feed pump, 22—oil feed pump housing, 23—auxiliary bearing, 24—transverse hole, 25—lubricating oil suction port, 26a—oil drain hole, 26b—oil drain pipe, 28—discharge port, 31—ring Groove, 32—sealing component, 33—first space, 35—back pressure hole, 36—circumferential groove, 36a—groove portion, 37—passage, 38—region, 39—groove portion, 40, 41—slit ( Oil leakage unit), 42—throttle component, 43—back pressure groove, 45—circle, 46—curve, 47—position of crank angle with maximum load Fg, 47A—cover plate surface where pushing force is significantly greater than the average value position, 48—interval, 50a—pressure of the inner line side compression chamber, 50b—pressure of the outer line side compression chamber, 52—motor room, 53—oil storage part, 54—discharge space, 56—frame seal, 57—oil tank , 58—shallow groove, 60—four-way valve, 61—outdoor heat exchanger, 62—expansion valve, 63—indoor heat exchanger, 64—refrigerant piping.
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2019/026291WO2021001923A1 (en) | 2019-07-02 | 2019-07-02 | Scroll compressor and air conditioner using same |
| Publication Number | Publication Date |
|---|---|
| CN114026328A CN114026328A (en) | 2022-02-08 |
| CN114026328Btrue CN114026328B (en) | 2023-11-10 |
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980098031.6AActiveCN114026328B (en) | 2019-07-02 | 2019-07-02 | Scroll compressor and air conditioner using the scroll compressor |
| Country | Link |
|---|---|
| JP (1) | JP6701469B1 (en) |
| CN (1) | CN114026328B (en) |
| WO (1) | WO2021001923A1 (en) |
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| JP7213382B1 (en) | 2022-05-24 | 2023-01-26 | 日立ジョンソンコントロールズ空調株式会社 | Scroll compressor and refrigeration cycle device |
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| JP7731484B1 (en)* | 2024-08-29 | 2025-08-29 | 日立ジョンソンコントロールズ空調株式会社 | Scroll compressor and refrigeration cycle device |
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| CN103189650A (en)* | 2010-11-01 | 2013-07-03 | 大金工业株式会社 | scroll compressor |
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN1782398A (en)* | 2004-11-30 | 2006-06-07 | 日立家用电器公司 | Turbine compressor |
| JP2009013882A (en)* | 2007-07-05 | 2009-01-22 | Hitachi Appliances Inc | Scroll compressor |
| JP2009174500A (en)* | 2008-01-28 | 2009-08-06 | Hitachi Appliances Inc | Hermetic scroll compressor |
| CN101672276A (en)* | 2008-09-12 | 2010-03-17 | 日立空调·家用电器株式会社 | Scroll compressor |
| CN101725526A (en)* | 2008-10-15 | 2010-06-09 | Lg电子株式会社 | Scoroll compressor and refrigerator having the same |
| CN103189650A (en)* | 2010-11-01 | 2013-07-03 | 大金工业株式会社 | scroll compressor |
| JP2012102708A (en)* | 2010-11-12 | 2012-05-31 | Daikin Industries Ltd | Scroll type compressor |
| Publication number | Publication date |
|---|---|
| JPWO2021001923A1 (en) | 2021-09-13 |
| CN114026328A (en) | 2022-02-08 |
| WO2021001923A1 (en) | 2021-01-07 |
| JP6701469B1 (en) | 2020-05-27 |
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| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
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