技术领域Technical Field
本发明涉及制冷设备技术领域，尤其是涉及一种压缩机构、一种压缩机、一种制冷循环装置和一种空调器。The present invention relates to the technical field of refrigeration equipment, and in particular to a compression mechanism, a compressor, a refrigeration cycle device and an air conditioner.
背景技术Background Art
在冬季由于室内外温差大，空调系统在低温环境下制热能力将大幅度衰减，无法达到用户需热量的需求。原因如下：第一，低温环境下，压缩机吸气口处制冷剂密度较小，导致制冷剂吸入量降低，进而影响空调系统的制热量；第二，由于室内外温差较大，空调系统蒸发温度与冷凝温度差异悬殊，节流后会闪发出大量气体，导致蒸发器不同流路间制冷剂分配不均匀，影响蒸发器换热效率，同时由于这些闪发气体进入蒸发器吸收的热量较小，而挤占蒸发器管道空间却很大，使管道很大表面积失去液体传导的功能，进一步影响了蒸发器的换热效率。In winter, due to the large temperature difference between indoor and outdoor, the heating capacity of the air conditioning system will be greatly reduced in low temperature environment, and it will not be able to meet the heat demand of users. The reasons are as follows: First, in low temperature environment, the refrigerant density at the compressor suction port is small, resulting in a decrease in the amount of refrigerant suction, which in turn affects the heating capacity of the air conditioning system; second, due to the large temperature difference between indoor and outdoor, the evaporation temperature and condensation temperature of the air conditioning system are very different, and a large amount of gas will be flashed after throttling, resulting in uneven distribution of refrigerant between different flow paths of the evaporator, affecting the heat exchange efficiency of the evaporator. At the same time, since the heat absorbed by these flash gases entering the evaporator is small, but the space occupied by the evaporator pipe is large, a large surface area of the pipe loses the function of liquid conduction, further affecting the heat exchange efficiency of the evaporator.
为了解决该难题，相关技术中，一种方式是将气体冷媒喷射方式应用在压缩机和冷冻循环上，运用双缸旋转压缩机。但是采用双缸式压缩机进行喷射技术压缩机成本增加明显，假如能效或制热能力提升不明显的话则会导致性价比低下；另一种方式是提出了独立压缩结构，增加一个独立的滑片压缩腔，即第二工作腔，从第二工作腔吸入中间压力的气体，一方面可以回收一部分膨胀功，另一方面降低了进入蒸发器低压制冷剂干度，提高蒸发器的换热效率，但是，目前独立压缩结构阀板通常采用顶丝固定，顶丝打紧后经常会出现滑片槽变形，进而导致滑片卡死的问题，严重影响了压缩机的可靠性。In order to solve this problem, one of the related technologies is to apply the gas refrigerant injection method to the compressor and refrigeration cycle, using a two-cylinder rotary compressor. However, the use of a two-cylinder compressor for injection technology will significantly increase the compressor cost. If the energy efficiency or heating capacity is not significantly improved, it will lead to low cost performance; another way is to propose an independent compression structure, add an independent vane compression chamber, that is, the second working chamber, and suck the gas of intermediate pressure from the second working chamber. On the one hand, it can recover part of the expansion work, and on the other hand, it reduces the dryness of the low-pressure refrigerant entering the evaporator and improves the heat exchange efficiency of the evaporator. However, the valve plate of the independent compression structure is usually fixed with a top screw. After the top screw is tightened, the vane groove often deforms, which leads to the problem of the vane getting stuck, seriously affecting the reliability of the compressor.
发明内容Summary of the invention
本发明旨在至少解决现有技术或相关技术中存在的技术问题之一。The present invention aims to solve at least one of the technical problems existing in the prior art or related art.
为此，本发明的第一方面提出一种压缩机构。To this end, a first aspect of the present invention provides a compression mechanism.
本发明的第二方面提出一种压缩机。A second aspect of the present invention provides a compressor.
本发明的第三方面提出一种制冷循环装置。A third aspect of the present invention provides a refrigeration cycle device.
本发明的第二方面提出一种空调器。A second aspect of the present invention provides an air conditioner.
有鉴于此，本发明的第一方面提供了一种压缩机构，包括：气缸，气缸上由气缸的中心轴线至气缸的外侧壁之间依次设置有滑片槽、安装槽及螺纹孔，滑片槽与安装槽相通，螺纹孔与安装槽相通；阀板，设置在安装槽内；螺纹紧固件，螺纹紧固件与螺纹孔配合连接，并对阀板施加挤压力；其中，螺纹紧固件的中心轴线至滑片槽任一轴向截面的距离，由滑片槽靠近气缸中心轴线的一端至滑片槽远离气缸中心轴线一端逐渐增大。In view of this, the first aspect of the present invention provides a compression mechanism, including: a cylinder, on which a vane groove, a mounting groove and a threaded hole are sequentially arranged from the central axis of the cylinder to the outer wall of the cylinder, the vane groove is communicated with the mounting groove, and the threaded hole is communicated with the mounting groove; a valve plate, arranged in the mounting groove; a threaded fastener, the threaded fastener is matched with the threaded hole and applies an extrusion force to the valve plate; wherein the distance from the central axis of the threaded fastener to any axial section of the vane groove gradually increases from the end of the vane groove close to the central axis of the cylinder to the end of the vane groove away from the central axis of the cylinder.
根据本发明的压缩机构，将螺纹紧固件的中心轴线至滑片槽任一轴向截面的距离设置为由滑片槽靠近气缸中心轴线的一端至滑片槽远离气缸中心轴线一端逐渐增大，即自气缸中心一侧的滑片槽的内端向外端方向逐渐增大，使得螺钉紧固件对阀板的作用力分解为垂直及平行阀板方向的两个作用力，垂直阀板方向的作用力将阀板紧固在安装槽的安装端面上，并使滑片槽向变窄方向变形，平行于阀板方向的作用力使得阀板对气缸产生反作用力，使滑片槽向变宽方向变形，两个作用力产生的变形相互抵消，最终的综合效果使得滑片槽变形大大减小，有效改善了压缩机的可靠性。According to the compression mechanism of the present invention, the distance from the center axis of the threaded fastener to any axial section of the vane groove is set to gradually increase from the end of the vane groove close to the center axis of the cylinder to the end of the vane groove away from the center axis of the cylinder, that is, gradually increase from the inner end to the outer end of the vane groove on the side of the cylinder center, so that the force of the screw fastener on the valve plate is decomposed into two forces in the directions perpendicular to and parallel to the valve plate. The force in the direction perpendicular to the valve plate fastens the valve plate to the mounting end face of the mounting groove and deforms the vane groove in a narrowing direction. The force parallel to the direction of the valve plate causes the valve plate to generate a reaction force on the cylinder, causing the vane groove to deform in a widening direction. The deformations caused by the two forces offset each other, and the final combined effect greatly reduces the deformation of the vane groove, effectively improving the reliability of the compressor.
另外，本发明提供的上述技术方案中的压缩机构还可以具有如下附加技术特征：In addition, the compression mechanism in the above technical solution provided by the present invention may also have the following additional technical features:
在上述技术方案中，优选地，螺纹紧固件的中心轴线与滑片槽任一轴向截面之间的夹角的取值范围为大于等于15°，小于等于60°。In the above technical solution, preferably, the angle between the central axis of the threaded fastener and any axial cross section of the sliding vane groove is in the range of greater than or equal to 15° and less than or equal to 60°.
在该技术方案中，通过将螺纹紧固件的中心轴线与滑片槽任一轴向截面之间的夹角的取值范围设置在15°至60°之间，可以缩小滑片槽的变形波动，以保证压缩机运行的可靠性。In this technical solution, by setting the angle between the central axis of the threaded fastener and any axial section of the vane groove to a value range of 15° to 60°, the deformation fluctuation of the vane groove can be reduced to ensure the reliability of the compressor operation.
在上述任一技术方案中，优选地，螺纹孔的数量为偶数个，均匀分布在滑片槽的两侧。In any of the above technical solutions, preferably, the number of the threaded holes is an even number and is evenly distributed on both sides of the sliding plate groove.
在该技术方案中，将螺纹孔设置于滑片槽两侧，从而保证安装槽的安装端面的密封，通常设置2个或4个螺纹孔。设置4个螺纹孔时，其位置分别对应阀板四个角部区域，由于螺纹紧固件数量较大，密封可靠性较好；设置2个螺纹孔时，其沿气缸腔轴线方向的位置位于阀板中部，由于螺纹紧固件数量相对较少，可以采用较大的直径和较大的打紧扭矩。In this technical solution, threaded holes are set on both sides of the sliding plate groove to ensure the sealing of the mounting end surface of the mounting groove. Usually, 2 or 4 threaded holes are set. When 4 threaded holes are set, their positions correspond to the four corner areas of the valve plate respectively. Since the number of threaded fasteners is large, the sealing reliability is better; when 2 threaded holes are set, their positions along the axis direction of the cylinder cavity are located in the middle of the valve plate. Since the number of threaded fasteners is relatively small, a larger diameter and a larger tightening torque can be used.
在上述任一技术方案中，优选地，沿气缸的径向，位于滑片槽两侧并靠近滑片槽相对的两个螺纹孔之间的距离与安装槽的宽度之间的比值大于等于0.5。In any of the above technical solutions, preferably, along the radial direction of the cylinder, the ratio of the distance between two threaded holes located on both sides of the sliding vane groove and close to the sliding vane groove and opposite to the width of the mounting groove is greater than or equal to 0.5.
在该技术方案中，螺纹孔的位置对滑片槽变形也有较大影响，气缸螺纹孔距离滑片槽中心越近，则螺纹紧固件对安装槽的安装端面的等效作用力与安装槽侧面的距离越远，即作用力的作用力臂越大，产生的滑片槽变形也越大，表现为滑片槽变窄，可见随着位于滑片槽两侧的两个螺纹孔之间的距离S与安装槽的宽度L之间比值的增大，滑片槽变形减小，当S/L≥0.5时，变形变化相对较为缓慢。In this technical solution, the position of the threaded hole also has a great influence on the deformation of the vane groove. The closer the cylinder threaded hole is to the center of the vane groove, the farther the distance between the equivalent force of the threaded fastener on the mounting end face of the mounting groove and the side of the mounting groove, that is, the greater the force arm of the force, the greater the deformation of the vane groove produced, which is manifested as a narrowing of the vane groove. It can be seen that as the ratio of the distance S between the two threaded holes on both sides of the vane groove and the width L of the mounting groove increases, the deformation of the vane groove decreases. When S/L≥0.5, the deformation change is relatively slow.
在上述任一技术方案中，优选地，压缩机构还包括：凹槽，设置在气缸上，位于阀板与螺纹紧固件的配合处；凹槽沿气缸的径向截面形状为锥形。In any of the above technical solutions, preferably, the compression mechanism further comprises: a groove, which is arranged on the cylinder and is located at the matching position of the valve plate and the threaded fastener; and the groove has a conical shape along the radial cross-section of the cylinder.
在该技术方案中，螺纹紧固件接触部位设置了截面形状为锥形的凹槽，该锥形槽凹槽可以只是位于与螺纹紧固件接触的局部，也可以沿气缸腔中心轴线方向贯穿阀板。由于该锥形凹槽的存在，解决了垂直于滑片槽方向作用力受摩擦系数限制的问题。从而通过优化设置螺纹紧固件的中心轴线与滑片槽的轴向界面之间的夹角θ，大大改善螺纹紧固件装配导致的滑片槽变形。In this technical solution, a groove with a conical cross-section is provided at the contact part of the threaded fastener. The conical groove can be located only at the part in contact with the threaded fastener, or can penetrate the valve plate along the central axis of the cylinder cavity. Due to the existence of the conical groove, the problem of the force acting in the direction perpendicular to the sliding vane groove being limited by the friction coefficient is solved. Therefore, by optimizing the angle θ between the central axis of the threaded fastener and the axial interface of the sliding vane groove, the deformation of the sliding vane groove caused by the assembly of the threaded fastener is greatly improved.
需要说明的是，凹槽沿气缸的径向截面形状也可以设置为方形、圆形、由直线或弧线构成的其他截面形状等，均可以达到相同的目的，不应作为对本发明的限制。It should be noted that the radial cross-sectional shape of the groove along the cylinder can also be set to square, circular, or other cross-sectional shapes consisting of straight lines or arcs, etc., which can achieve the same purpose and should not be used as a limitation to the present invention.
在上述任一技术方案中，优选地，阀板的朝向安装槽侧的外侧面形成有倒角平面，螺纹紧固件与倒角平面配合，以对阀板施加挤压力。In any of the above technical solutions, preferably, a chamfered surface is formed on the outer side of the valve plate facing the mounting groove, and the threaded fastener cooperates with the chamfered surface to apply an extrusion force to the valve plate.
在上述任一技术方案中，优选地，倒角平面与螺纹紧固件的轴线相垂直。In any of the above technical solutions, preferably, the chamfered plane is perpendicular to the axis of the threaded fastener.
在该技术方案中，将螺纹紧固件接触位置设置于阀板外侧面位于滑片槽两侧边缘形成的倒角平面上，且所述倒角平面与螺纹紧固件轴线垂直，保证螺纹紧固件预紧力始终沿其轴线方向。In this technical solution, the contact position of the threaded fastener is set on the chamfered plane formed by the edges of both sides of the sliding groove on the outer side of the valve plate, and the chamfered plane is perpendicular to the axis of the threaded fastener to ensure that the preload force of the threaded fastener is always along its axial direction.
在上述任一技术方案中，优选地，压缩机构还包括：滑片，滑片可滑动地设置在滑片槽内，滑片槽内位于滑片和阀板之间形成有第二工作腔。In any of the above technical solutions, preferably, the compression mechanism further comprises: a sliding vane, which is slidably disposed in a sliding vane groove, and a second working chamber is formed in the sliding vane groove between the sliding vane and the valve plate.
在上述任一技术方案中，优选地，压缩机构还包括：In any of the above technical solutions, preferably, the compression mechanism further comprises:
滚子，滚子可滚动地设在气缸的气缸腔内，滑片的一端与滚子相连接，气缸腔的内周面、滚子的外周面以及滑片之间形成有第一工作腔。The roller is rotatably arranged in the cylinder cavity of the cylinder, one end of the sliding plate is connected to the roller, and a first working cavity is formed between the inner circumference of the cylinder cavity, the outer circumference of the roller and the sliding plate.
在该技术方案中，滑片在滑片槽内可内外滑动，滚子套设在曲轴偏心部上，可随曲轴的旋转而偏心转动，此外，滚子还可绕自身轴线发生自转，滑片内端抵在滚子上。气缸腔的内周面、滚子的外周面以及滑片之间形成为第一工作腔，其上下端面由上轴承和下轴承密封。第一工作腔与第一吸气孔相连部分为第一吸气腔，与第一排气孔相连部分为第一压缩腔。随着曲轴的旋转，第一吸气腔容积不断增大，从而不断吸入冷媒，第一压缩腔容积不断减小，腔内冷媒压力不断升高，达到排气压力时将第一排气阀片顶开，从第一排气口将高压冷媒排出，第一限位器对第一排气阀片的升程进行限制，防止发生断裂等可靠性问题。In this technical solution, the vane can slide inside and outside in the vane groove, and the roller sleeve is arranged on the eccentric part of the crankshaft, and can rotate eccentrically with the rotation of the crankshaft. In addition, the roller can also rotate around its own axis, and the inner end of the vane is against the roller. The inner circumference of the cylinder cavity, the outer circumference of the roller and the vane form a first working chamber, and its upper and lower end surfaces are sealed by an upper bearing and a lower bearing. The part of the first working chamber connected to the first suction hole is the first suction chamber, and the part connected to the first exhaust hole is the first compression chamber. With the rotation of the crankshaft, the volume of the first suction chamber continues to increase, thereby continuously inhaling refrigerant, the volume of the first compression chamber continues to decrease, and the refrigerant pressure in the chamber continues to increase. When the exhaust pressure is reached, the first exhaust valve plate is pushed open, and the high-pressure refrigerant is discharged from the first exhaust port. The first limiter limits the lift of the first exhaust valve plate to prevent reliability problems such as breakage.
滑片槽内位于滑片和阀板之间形成为第二工作腔，其上下端面由上轴承和下轴承密封。滑片内端与滚子通过铰接方式连接，保证二者在任何情形下不发生脱离，随着曲轴的旋转，滑片在滑片槽内进行直线往复运动。当滑片向内运动时(朝向气缸腔轴线)，第二工作腔容积增大，增大到一定程度吸气阀片打开，吸入中间压力冷媒(压力高于第一工作腔吸气压力)；当滑片向外运动时(远离气缸腔轴线)，第二工作腔容积减小，冷媒被压缩，压力不断升高，达到排气压力时将第二排气阀片顶开，从第二排气口将高压冷媒排出，类似地，第二限位器对第二排气阀片的升程进行限制。通过采用双工作腔结构，提升压缩机的工作效率，以提升用户对空调器的使用体验。The second working chamber is formed between the vane and the valve plate in the vane groove, and its upper and lower end surfaces are sealed by the upper bearing and the lower bearing. The inner end of the vane is connected to the roller by a hinge to ensure that the two will not be separated under any circumstances. As the crankshaft rotates, the vane performs linear reciprocating motion in the vane groove. When the vane moves inward (toward the axis of the cylinder chamber), the volume of the second working chamber increases. When it increases to a certain extent, the suction valve plate opens and sucks in the intermediate pressure refrigerant (the pressure is higher than the suction pressure of the first working chamber); when the vane moves outward (away from the axis of the cylinder chamber), the volume of the second working chamber decreases, the refrigerant is compressed, and the pressure continues to increase. When the exhaust pressure is reached, the second exhaust valve plate is pushed open and the high-pressure refrigerant is discharged from the second exhaust port. Similarly, the second limiter limits the lift of the second exhaust valve plate. By adopting a dual working chamber structure, the working efficiency of the compressor is improved, so as to enhance the user experience of the air conditioner.
本发明第二方面提供了一种压缩机，包括如上述任一技术方案的压缩机构。A second aspect of the present invention provides a compressor, comprising a compression mechanism as described in any of the above technical solutions.
本发明提供的压缩机，包括上述任一技术方案所述的压缩机构，因此具有压缩机构的全部有益效果，在此不再赘述。The compressor provided by the present invention includes the compression mechanism described in any of the above technical solutions, and therefore has all the beneficial effects of the compression mechanism, which will not be repeated here.
本发明第三方面提供了一种制冷循环装置，包括：如上述任一技术方案的压缩机构；或如上述技术方案的压缩机。A third aspect of the present invention provides a refrigeration cycle device, comprising: a compression mechanism as in any of the above technical solutions; or a compressor as in the above technical solution.
本发明提供的制冷循环装置，包括上述任一技术方案所述的压缩机构，或上述技术方案的压缩机，因此具有压缩机构和压缩机的全部有益效果，在此不再赘述。The refrigeration cycle device provided by the present invention includes the compression mechanism described in any of the above technical solutions, or the compressor of the above technical solution, and therefore has all the beneficial effects of the compression mechanism and the compressor, which will not be repeated here.
本发明第三方面提供了一种空调器，包括：如上述技术方案的制冷循环装置。A third aspect of the present invention provides an air conditioner, comprising: a refrigeration cycle device as described in the above technical solution.
本发明提供的空调器，包括上述技术方案的制冷循环装置，因此具有上述制冷循环装置的全部有益效果，在此不再赘述。The air conditioner provided by the present invention includes the refrigeration cycle device of the above technical solution, and therefore has all the beneficial effects of the above refrigeration cycle device, which will not be described in detail here.
本发明的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本发明的实践了解到。Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention.
附图说明BRIEF DESCRIPTION OF THE DRAWINGS
本发明的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：The above and/or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:
图1是现有独立压缩结构的工作腔及阀板固定结构示意图；FIG1 is a schematic diagram of a working chamber and a valve plate fixing structure of an existing independent compression structure;
图2是现有独立压缩结构高度方向剖视图；FIG2 is a cross-sectional view of a conventional independent compression structure in the height direction;
图3是现有阀板固定结构滑片槽变形原理说明图；FIG3 is a diagram illustrating the deformation principle of the slide slot of the existing valve plate fixing structure;
图4是根据本发明一个实施例的压缩机构的结构示意图；FIG4 is a schematic structural diagram of a compression mechanism according to an embodiment of the present invention;
图5是图4所示实施例的压缩机构改善原理说明图；FIG5 is a diagram illustrating the principle of improvement of the compression mechanism of the embodiment shown in FIG4;
图6是滑片槽变形与夹角θ曲线示意图；FIG6 is a schematic diagram of a curve showing the deformation of a sliding vane groove and an angle θ;
图7是滑片槽变形-气缸螺纹孔距离S/气缸安装槽宽度L曲线示意图；7 is a schematic diagram of a curve of vane groove deformation-cylinder threaded hole distance S/cylinder mounting groove width L;
图8是根据本发明再一个实施例的压缩机构的结构示意图；FIG8 is a schematic structural diagram of a compression mechanism according to yet another embodiment of the present invention;
图9是根据本发明又一个实施例的压缩机构的结构示意图；FIG9 is a schematic structural diagram of a compression mechanism according to yet another embodiment of the present invention;
图10是根据本发明一个实施例的制冷循环装置结构示意图。FIG. 10 is a schematic structural diagram of a refrigeration cycle device according to an embodiment of the present invention.
其中，图1至图3中的附图标记与部件名称之间的对应关系为：The corresponding relationship between the reference numerals and component names in FIGS. 1 to 3 is as follows:
1’气缸，2’曲轴，3’滚子，4’滑片，42’滑片槽，5’上轴承，6’下轴承，7’螺纹孔，8’安装槽，82’阀板，9’吸气阀片，10’第二工作腔，11’第一吸气孔，12’第一排气孔，14’第二限位器，15’第二排气阀片，16’第二排气孔，17’顶丝。1’ cylinder, 2’ crankshaft, 3’ roller, 4’ vane, 42’ vane groove, 5’ upper bearing, 6’ lower bearing, 7’ threaded hole, 8’ mounting groove, 82’ valve plate, 9’ intake valve plate, 10’ second working chamber, 11’ first intake hole, 12’ first exhaust hole, 14’ second limiter, 15’ second exhaust valve plate, 16’ second exhaust hole, 17’ top screw.
图4至图10中的附图标记与部件名称之间的对应关系为：The corresponding relationship between the reference numerals and component names in FIGS. 4 to 10 is as follows:
1气缸，12滑片槽，122滑片，14安装槽，142阀板，144吸气阀片，146凹槽，148倒角平面，16螺纹孔，162螺纹紧固件，18第一吸气孔，10第一工作腔，20第二工作腔，30压缩机，40四通阀，50室外换热器，60第一节流元件，70闪蒸器，80第二节流元件，90室内换热器。1 cylinder, 12 vane groove, 122 vane, 14 mounting groove, 142 valve plate, 144 suction valve plate, 146 groove, 148 chamfered plane, 16 threaded hole, 162 threaded fastener, 18 first suction hole, 10 first working chamber, 20 second working chamber, 30 compressor, 40 four-way valve, 50 outdoor heat exchanger, 60 first throttling element, 70 flash evaporator, 80 second throttling element, 90 indoor heat exchanger.
具体实施方式DETAILED DESCRIPTION
为了能够更清楚地理解本发明的上述目的、特征和优点，下面结合附图和具体实施方式对本发明进行进一步的详细描述。需要说明的是，在不冲突的情况下，本申请的实施例及实施例中的特征可以相互组合。In order to more clearly understand the above-mentioned purpose, features and advantages of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features in the embodiments can be combined with each other without conflict.
在下面的描述中阐述了很多具体细节以便于充分理解本发明，但是，本发明还可以采用其他不同于在此描述的其他方式来实施，因此，本发明的保护范围并不受下面公开的具体实施例的限制。In the following description, many specific details are set forth to facilitate a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the protection scope of the present invention is not limited to the specific embodiments disclosed below.
下面参照图4至图10描述根据本发明一些实施例所述压缩机构、压缩机、制冷循环装置和空调器。The compression mechanism, the compressor, the refrigeration cycle device and the air conditioner according to some embodiments of the present invention are described below with reference to FIGS. 4 to 10 .
如图4至图9所示，本发明的一个实施例提供了一种压缩机构，包括：气缸1，气缸1上由气缸1的中心轴线至气缸1的外侧壁之间依次设置有滑片槽12、安装槽14及螺纹孔16，滑片槽12与安装槽14相通，螺纹孔16与安装槽14相通；阀板142，设置在安装槽14内；螺纹紧固件162，螺纹紧固件162与螺纹孔16配合连接，并对阀板142施加挤压力；其中，螺纹紧固件162螺纹孔16的中心轴线至滑片槽12任一轴向截面的距离，由滑片槽12靠近气缸1中心轴线的一端至滑片槽12远离气缸1中心轴线一端逐渐增大。As shown in Figures 4 to 9, an embodiment of the present invention provides a compression mechanism, including: a cylinder 1, on which a vane groove 12, a mounting groove 14 and a threaded hole 16 are sequentially arranged from the central axis of the cylinder 1 to the outer side wall of the cylinder 1, the vane groove 12 is communicated with the mounting groove 14, and the threaded hole 16 is communicated with the mounting groove 14; a valve plate 142, which is arranged in the mounting groove 14; a threaded fastener 162, which is cooperated and connected with the threaded hole 16 and applies an extrusion force to the valve plate 142; wherein, the distance from the central axis of the threaded hole 16 of the threaded fastener 162 to any axial section of the vane groove 12 gradually increases from one end of the vane groove 12 close to the central axis of the cylinder 1 to the end of the vane groove 12 away from the central axis of the cylinder 1.
根据本发明的压缩机构，将螺纹紧固件162螺纹孔16的中心轴线至滑片槽12任一轴向截面的距离设置为由滑片槽12靠近气缸1中心轴线的一端至滑片槽12远离气缸1中心轴线一端逐渐增大，即自气缸1中心一侧的滑片槽12的内端向外端方向逐渐增大，使得螺钉紧固件对阀板142的作用力分解为垂直及平行阀板142方向的两个作用力，垂直阀板142方向的作用力将阀板142紧固在安装槽14的安装端面上，并使滑片槽12向变窄方向变形，平行于阀板142方向的作用力使得阀板142对气缸1产生反作用力，使滑片槽12向变宽方向变形，两个作用力产生的变形相互抵消，最终的综合效果使得滑片槽12变形大大减小，有效改善了压缩机的可靠性。According to the compression mechanism of the present invention, the distance from the center axis of the threaded hole 16 of the threaded fastener 162 to any axial section of the vane groove 12 is set to gradually increase from the end of the vane groove 12 close to the center axis of the cylinder 1 to the end of the vane groove 12 away from the center axis of the cylinder 1, that is, gradually increase from the inner end of the vane groove 12 on the center side of the cylinder 1 to the outer end, so that the force of the screw fastener on the valve plate 142 is decomposed into two forces in the directions perpendicular to and parallel to the valve plate 142. The force perpendicular to the direction of the valve plate 142 fastens the valve plate 142 to the mounting end face of the mounting groove 14 and deforms the vane groove 12 in the narrowing direction. The force parallel to the direction of the valve plate 142 causes the valve plate 142 to generate a reaction force on the cylinder 1, causing the vane groove 12 to deform in the widening direction. The deformations caused by the two forces offset each other. The final comprehensive effect greatly reduces the deformation of the vane groove 12, effectively improving the reliability of the compressor.
在本发明的一些实施例中，螺纹紧固件162采用顶丝。In some embodiments of the present invention, the threaded fastener 162 is a jackscrew.
相关技术中，如图1至图3所示，现有独立压缩结构的压缩机泵体，包括：气缸1’、曲轴2’、滚子3’、滑片4’、上轴承5’、下轴承6’、第一排气阀片、第一限位器(第一排气阀片和第一限位器图中未示出，位于上轴承5’或下轴承6’上)、阀板82’、吸气阀片9’、第二排气阀片15’、第二限位器14’和顶丝17’。气缸1’上形成有圆柱形气缸1’腔、第一吸气孔11’、第一排气孔12’、滑片槽42’、安装槽8’和螺纹孔7’，安装槽8’设在滑片槽42’的外端且与滑片槽42’连通，安装槽8’与滑片槽42’相连的连通口的表面构成安装端面，螺纹孔7’设置于安装槽8’外端并与安装槽8’连通。这里，需要说明的是，圆柱形的气缸1’腔具有轴线，滑片槽42’的内端指的是滑片槽42’的朝向该轴线的一端，滑片槽42’的外端指的是滑片槽42’的远离该轴线的一端。In the related art, as shown in Figures 1 to 3, the compressor pump body of the existing independent compression structure includes: a cylinder 1', a crankshaft 2', a roller 3', a vane 4', an upper bearing 5', a lower bearing 6', a first exhaust valve plate, a first stopper (the first exhaust valve plate and the first stopper are not shown in the figure, and are located on the upper bearing 5' or the lower bearing 6'), a valve plate 82', an air intake valve plate 9', a second exhaust valve plate 15', a second stopper 14' and a top screw 17'. A cylindrical cylinder 1' cavity, a first air intake hole 11', a first exhaust hole 12', a vane groove 42', a mounting groove 8' and a threaded hole 7' are formed on the cylinder 1'. The mounting groove 8' is arranged at the outer end of the vane groove 42' and is connected to the vane groove 42'. The surface of the connecting port connecting the mounting groove 8' and the vane groove 42' constitutes a mounting end surface. The threaded hole 7' is arranged at the outer end of the mounting groove 8' and is connected to the mounting groove 8'. Here, it should be noted that the cylindrical cylinder 1' cavity has an axis, the inner end of the vane groove 42' refers to the end of the vane groove 42' facing the axis, and the outer end of the vane groove 42' refers to the end of the vane groove 42' away from the axis.
滑片4’在滑片槽42’内可内外滑动，滚子3’套设在曲轴2’偏心部上，可随曲轴2’的旋转而偏心转动，此外，滚子3’还可绕自身轴线发生自转，滑片4’内端抵在滚子3’上。气缸1’腔的内周面、滚子3’的外周面以及滑片4’之间形成为第一工作腔，其上下端面由上轴承5’和下轴承6’密封。第一工作腔与第一吸气孔11’相连部分为第一吸气腔，与第一排气孔12’相连部分为第一压缩腔。随着曲轴2’的旋转，第一吸气腔容积不断增大，从而不断吸入冷媒，第一压缩腔容积不断减小，腔内冷媒压力不断升高，达到排气压力时将第一排气阀片顶开，从第一排气孔12’将高压冷媒排出，第一限位器对第一排气阀片的升程进行限制，防止发生断裂等可靠性问题。The vane 4' can slide inside and outside in the vane groove 42', and the roller 3' is sleeved on the eccentric part of the crankshaft 2' and can rotate eccentrically with the rotation of the crankshaft 2'. In addition, the roller 3' can also rotate around its own axis, and the inner end of the vane 4' is against the roller 3'. The inner circumference of the cylinder 1' cavity, the outer circumference of the roller 3' and the vane 4' form a first working chamber, and its upper and lower end surfaces are sealed by the upper bearing 5' and the lower bearing 6'. The part of the first working chamber connected to the first suction hole 11' is the first suction chamber, and the part connected to the first exhaust hole 12' is the first compression chamber. With the rotation of the crankshaft 2', the volume of the first suction chamber continues to increase, thereby continuously inhaling refrigerant, the volume of the first compression chamber continues to decrease, and the refrigerant pressure in the chamber continues to increase. When the exhaust pressure is reached, the first exhaust valve plate is pushed open, and the high-pressure refrigerant is discharged from the first exhaust hole 12'. The first limiter limits the lift of the first exhaust valve plate to prevent reliability problems such as breakage.
滑片槽42’内位于滑片4’和阀板82’之间形成为第二工作腔10’，其上下端面由上轴承5’和下轴承6’密封。滑片4’内端与滚子3’通过铰接方式连接，保证二者在任何情形下不发生脱离，随着曲轴2’的旋转，滑片4’在滑片槽42’内进行直线往复运动。当滑片4’向内运动时(朝向气缸1’腔轴线)，第二工作腔10’容积增大，增大到一定程度吸气阀片9’打开，吸入中间压力冷媒(压力高于第一工作腔吸气压力)；当滑片4’向外运动时(远离气缸1’腔轴线)，第二工作腔10’容积减小，冷媒被压缩，压力不断升高，达到排气压力时将第二排气阀片15’顶开，从第二排气孔16’将高压冷媒排出，类似地，第二限位器14’对第二排气阀片15’的升程进行限制。The second working chamber 10' is formed between the vane 4' and the valve plate 82' in the vane groove 42', and its upper and lower end surfaces are sealed by the upper bearing 5' and the lower bearing 6'. The inner end of the vane 4' is connected to the roller 3' by a hinged manner to ensure that the two will not be separated under any circumstances. As the crankshaft 2' rotates, the vane 4' performs linear reciprocating motion in the vane groove 42'. When the vane 4' moves inward (toward the axis of the cylinder 1' cavity), the volume of the second working chamber 10' increases, and when it increases to a certain extent, the suction valve plate 9' opens and sucks in the intermediate pressure refrigerant (the pressure is higher than the suction pressure of the first working chamber); when the vane 4' moves outward (away from the axis of the cylinder 1' cavity), the volume of the second working chamber 10' decreases, the refrigerant is compressed, and the pressure continues to increase. When the exhaust pressure is reached, the second exhaust valve plate 15' is pushed open, and the high-pressure refrigerant is discharged from the second exhaust hole 16'. Similarly, the second limiter 14' limits the lift of the second exhaust valve plate 15'.
阀板82’、吸气阀片9’与气缸1’安装槽8’的安装端面配合，为了保证密封，通常采用顶丝17’进行预紧，即顶丝17’安装在气缸1’安装槽8’外端的螺纹孔7’内，如图1和图3所示，顶丝17’轴线与滑片槽42’平行，将阀板82’和吸气阀片9’压紧在所述安装端面上。顶丝17’结构具有结构简单、安装方便、预紧力可调等优点，因而成为安装端面密封方式的首选，但该结构压缩机在顶丝17’预紧后经常出现滑片槽42’变形大导致滑片4’卡死的问题，严重影响了压缩机的可靠性，成为该结构应用的瓶颈问题。The valve plate 82', the air intake valve plate 9' and the mounting end surface of the cylinder 1' mounting groove 8' are matched. In order to ensure sealing, a top screw 17' is usually used for pre-tightening, that is, the top screw 17' is installed in the threaded hole 7' at the outer end of the cylinder 1' mounting groove 8'. As shown in Figures 1 and 3, the axis of the top screw 17' is parallel to the vane groove 42', and the valve plate 82' and the air intake valve plate 9' are pressed against the mounting end surface. The top screw 17' structure has the advantages of simple structure, convenient installation, and adjustable pre-tightening force, so it has become the first choice for the mounting end face sealing method. However, the compressor of this structure often has the problem of large deformation of the vane groove 42' causing the vane 4' to get stuck after the top screw 17' is pre-tightened, which seriously affects the reliability of the compressor and becomes a bottleneck problem in the application of this structure.
针对该问题，如图4所示，本发明提出的压缩机构将螺纹紧固件162的中心轴线至滑片槽12任一轴向截面的距离，由滑片槽12靠近气缸1中心轴线的一端至滑片槽12远离气缸1中心轴线一端逐渐增大。当滑片槽12两侧均设置螺纹紧固件162时，至少一个螺纹紧固件162的中心轴线与滑片槽12的距离由滑片槽12的任一轴向截面的距离由滑片槽12的内端向外端方向逐渐增大。To solve this problem, as shown in FIG4 , the compression mechanism proposed by the present invention gradually increases the distance from the central axis of the threaded fastener 162 to any axial section of the vane slot 12 from the end of the vane slot 12 close to the central axis of the cylinder 1 to the end of the vane slot 12 away from the central axis of the cylinder 1. When the threaded fasteners 162 are arranged on both sides of the vane slot 12, the distance from the central axis of at least one threaded fastener 162 to the vane slot 12 gradually increases from the inner end to the outer end of the vane slot 12 from any axial section of the vane slot 12.
如图3和图5所示，可见根据本发明的提供的压缩机构，可有效改善装配滑片槽12变形的问题。具体对比如下：As shown in FIG. 3 and FIG. 5 , it can be seen that the compression mechanism provided by the present invention can effectively improve the problem of deformation of the assembly slide slot 12 . The specific comparison is as follows:
如图3，在现有顶丝17’结构设计下，顶丝17’轴线与滑片槽42’平行，在顶丝17’打紧后，顶丝17’将产生较大的预紧力，气缸1’安装槽8’安装端面相应地受到阀板82’、吸气阀片9’传递过来的压紧力作用。对于气缸1’和顶丝17’构成的整体而言，受到阀板82’对顶丝17’的反作用力，其大小与顶丝17’预紧力相同；同时，气缸1’安装槽8’安装端面还受到上述阀板82’、吸气阀片9’传递过来的压紧力作用，该压紧力实际是一个分布力，图中所示为该分布力的等效合力。阀板82’对顶丝17’的反作用力、吸气阀片9’传递过来的压紧力等效合力均与滑片槽42’平行。由于气缸1’安装槽8’的设置，滑片槽42’局部刚性严重减弱，主要在吸气阀片9’传递过来的压紧力作用下，气缸1’滑片槽42’将发生显著的变形，其变形后的形状如图4中虚线所示，即滑片槽42’外端显著变窄，而滑片槽42’内端略有变宽，该形状得到了理论及试验的同时验证。滑片槽42’变窄的幅度超过了滑片槽42’与滑片4’之间的宽度间隙，从而导致了滑片4’的卡死。As shown in Figure 3, under the existing top screw 17' structural design, the axis of the top screw 17' is parallel to the slide groove 42'. After the top screw 17' is tightened, the top screw 17' will generate a large pre-tightening force, and the mounting end face of the cylinder 1' mounting groove 8' will be correspondingly subjected to the compression force transmitted by the valve plate 82' and the air intake valve plate 9'. For the cylinder 1' and the top screw 17' as a whole, the valve plate 82' is subjected to the reaction force on the top screw 17', and its magnitude is the same as the pre-tightening force of the top screw 17'; at the same time, the mounting end face of the cylinder 1' mounting groove 8' is also subjected to the compression force transmitted by the above-mentioned valve plate 82' and the air intake valve plate 9'. The compression force is actually a distributed force, and the equivalent resultant force of the distributed force is shown in the figure. The reaction force of the valve plate 82' on the top screw 17' and the equivalent resultant force of the compression force transmitted by the air intake valve plate 9' are both parallel to the slide groove 42'. Due to the setting of the installation groove 8' of the cylinder 1', the local rigidity of the slide groove 42' is seriously weakened. Mainly under the pressing force transmitted by the air intake valve plate 9', the slide groove 42' of the cylinder 1' will be significantly deformed. The deformed shape is shown by the dotted line in Figure 4, that is, the outer end of the slide groove 42' is significantly narrowed, while the inner end of the slide groove 42' is slightly widened. This shape has been verified by both theory and experiment. The narrowing of the slide groove 42' exceeds the width gap between the slide groove 42' and the slide 4', which causes the slide 4' to get stuck.
滑片槽42’变形很大时，在大批量生产中由于各制造因素的波动，其变形的波动通常也很大，这意味着如果单纯增大滑片4’与滑片槽42’之间的宽度间隙，将导致部分压缩机在装配后滑片4’与滑片槽42’之间的实际宽度间隙过大，造成压缩机运行时通过该宽度间隙的泄漏显著增大，表现为性能显著恶化；同时滑片4’倾斜也会增大(滑片4’与滑片槽42’之间形成微小夹角)，会造成滑片4’侧面异常磨损，影响压缩机可靠性。因此，必须减小装配导致的滑片槽42’变形。When the vane slot 42' is greatly deformed, the deformation fluctuation is usually also large due to the fluctuation of various manufacturing factors in mass production. This means that if the width gap between the vane 4' and the vane slot 42' is simply increased, the actual width gap between the vane 4' and the vane slot 42' will be too large after assembly in some compressors, causing a significant increase in leakage through the width gap when the compressor is running, which is manifested as a significant deterioration in performance; at the same time, the inclination of the vane 4' will also increase (a small angle is formed between the vane 4' and the vane slot 42'), which will cause abnormal wear on the side of the vane 4' and affect the reliability of the compressor. Therefore, the deformation of the vane slot 42' caused by assembly must be reduced.
如图5所示，根据本发明提供的压缩机构，将螺纹紧固件162的中心轴线与滑片槽12的任一轴向截面的距离设置为由滑片槽12的内端向外端方向逐渐增大，此时螺纹紧固件162与气缸1构成的整体除受平行于滑片槽12方向的作用力F外，由于螺纹紧固件162预紧力与阀板142接触表面不垂直，还将产生平行于阀板142表面，即垂直于滑片槽12方向的作用力f。作用力F和f的合力为螺纹紧固件162预紧力的反作用力。平行于滑片槽12方向的作用力F导致的滑片槽12变形与图3类似，但在垂直于滑片槽12方向的作用力f的作用下，滑片槽12整体还将产生变宽的变形效果，其变形方向与作用力F相反，于是变形相互抵消。在二者的综合作用下，滑片槽12变形显著减小，其变形后的形状如图5中的虚线所示，表现为滑片槽12外端略有变窄，而内端略有变宽。在本发明的一个实施例中，顶丝预紧导致的滑片槽12变形由原有设计的12.5μm减小至本发明改善设计的1.7μm，滑片槽12改善幅度达到86.4％。As shown in FIG5 , according to the compression mechanism provided by the present invention, the distance between the central axis of the threaded fastener 162 and any axial section of the vane slot 12 is set to gradually increase from the inner end to the outer end of the vane slot 12. At this time, the whole formed by the threaded fastener 162 and the cylinder 1 is not only subjected to the force F parallel to the direction of the vane slot 12, but also generates a force f parallel to the surface of the valve plate 142, that is, perpendicular to the direction of the vane slot 12, because the pre-tightening force of the threaded fastener 162 is not perpendicular to the contact surface of the valve plate 142. The resultant force of the force F and f is the reaction force of the pre-tightening force of the threaded fastener 162. The deformation of the vane slot 12 caused by the force F parallel to the direction of the vane slot 12 is similar to that in FIG3 , but under the action of the force f perpendicular to the direction of the vane slot 12, the vane slot 12 as a whole will also produce a widening deformation effect, and its deformation direction is opposite to the force F, so the deformations cancel each other out. Under the combined effect of the two, the deformation of the vane slot 12 is significantly reduced, and its deformed shape is shown by the dotted line in Figure 5, which shows that the outer end of the vane slot 12 is slightly narrowed, while the inner end is slightly widened. In one embodiment of the present invention, the deformation of the vane slot 12 caused by the top screw pre-tightening is reduced from 12.5μm in the original design to 1.7μm in the improved design of the present invention, and the improvement of the vane slot 12 reaches 86.4%.
在本发明的一个实施例中，优选地，螺纹紧固件162螺纹孔16的中心轴线与滑片槽12任一轴向截面之间的夹角的取值范围为大于等于15°，小于等于60°。In one embodiment of the present invention, preferably, the angle between the central axis of the threaded hole 16 of the threaded fastener 162 and any axial cross section of the slide slot 12 is in the range of greater than or equal to 15° and less than or equal to 60°.
在该实施例中，通过将螺纹紧固件162螺纹孔16的中心轴线与滑片槽12任一轴向截面之间的夹角的取值范围设置在15°至60°之间，可以缩小滑片槽12的变形波动，以保证压缩机运行的可靠性。In this embodiment, by setting the angle between the central axis of the threaded hole 16 of the threaded fastener 162 and any axial section of the vane slot 12 to between 15° and 60°, the deformation fluctuation of the vane slot 12 can be reduced to ensure the reliability of the compressor operation.
具体实施例中，如图6所示，螺纹紧固件162的中心轴线与滑片槽12的任一轴向截面之间的夹角对滑片槽12变形的改善效果有较大影响。图6中所示变形正值表示滑片槽12变窄，负值表示滑片槽12变宽，即正负符号表示变形方向，而数值表示变形大小。考虑到气缸1安装槽14安装端面的密封要求，该曲线是在平行于滑片槽12方向的作用力F保持不变的前提下得到的。同时，由图5可知，f＝F*tanθ，随着夹角θ的增大，作用力f逐渐增大，图6中曲线假定作用力f的增大不受其他因素的限制，即螺纹紧固件162预紧力始终沿着其轴向。当夹角θ小于45度时，螺纹紧固件162预紧后，平行于滑片槽12方向的作用力F较大，其作用更为显著，使滑片槽12表现为变窄，随着夹角θ的增大，滑片槽12变形迅速减小；相反，当夹角θ大于45度时，螺纹紧固件162预紧后，垂直于滑片槽12方向的作用力f较大，其作用更为显著，使滑片槽12表现为变宽，随着夹角θ的增大，作用力f迅速增大，导致滑片槽12变形迅速恶化。如前所述，滑片槽12变形过大(无论是变宽还是变窄)，会导致批量生产时变形波动也较大，因此较小的滑片槽12变形是较为理想的。由图6可知，夹角θ设置在15°至60°之间效果较好。In a specific embodiment, as shown in FIG6 , the angle between the central axis of the threaded fastener 162 and any axial section of the vane slot 12 has a great influence on the improvement effect of the deformation of the vane slot 12. The positive value of the deformation shown in FIG6 indicates that the vane slot 12 becomes narrower, and the negative value indicates that the vane slot 12 becomes wider, that is, the positive and negative symbols indicate the direction of deformation, and the numerical value indicates the magnitude of deformation. Considering the sealing requirements of the mounting end face of the mounting groove 14 of the cylinder 1, the curve is obtained under the premise that the force F parallel to the direction of the vane slot 12 remains unchanged. At the same time, it can be seen from FIG5 that f=F*tanθ, and as the angle θ increases, the force f gradually increases. The curve in FIG6 assumes that the increase of the force f is not limited by other factors, that is, the preload force of the threaded fastener 162 is always along its axial direction. When the angle θ is less than 45 degrees, after the threaded fastener 162 is pre-tightened, the force F parallel to the direction of the vane slot 12 is larger, and its effect is more significant, so that the vane slot 12 appears to be narrowed. As the angle θ increases, the deformation of the vane slot 12 decreases rapidly; on the contrary, when the angle θ is greater than 45 degrees, after the threaded fastener 162 is pre-tightened, the force f perpendicular to the direction of the vane slot 12 is larger, and its effect is more significant, so that the vane slot 12 appears to be widened. As the angle θ increases, the force f increases rapidly, causing the deformation of the vane slot 12 to deteriorate rapidly. As mentioned above, if the deformation of the vane slot 12 is too large (whether it is widened or narrowed), it will cause large deformation fluctuations during mass production, so a smaller deformation of the vane slot 12 is more ideal. As shown in Figure 6, it is better to set the angle θ between 15° and 60°.
在本发明的一个实施例中，优选地，螺纹孔16的数量为偶数个，均匀分布在滑片槽12的两侧。In one embodiment of the present invention, preferably, the number of the threaded holes 16 is an even number and is evenly distributed on both sides of the sliding vane slot 12 .
在该实施例中，将螺纹孔16设置于滑片槽12两侧，从而保证安装槽14的安装端面的密封，通常设置2个或4个螺纹孔16。设置4个螺纹孔16时，其位置分别对应阀板142四个角部区域，由于螺纹紧固件162数量较大，密封可靠性较好；设置2个螺纹孔16时，其沿气缸腔轴线方向的位置位于阀板142中部，由于螺纹紧固件162数量相对较少，可以采用较大的直径和较大的打紧扭矩。In this embodiment, threaded holes 16 are arranged on both sides of the slide groove 12 to ensure the sealing of the mounting end surface of the mounting groove 14. Usually, two or four threaded holes 16 are arranged. When four threaded holes 16 are arranged, their positions correspond to the four corner areas of the valve plate 142 respectively. Since the number of threaded fasteners 162 is large, the sealing reliability is good; when two threaded holes 16 are arranged, their positions along the axis direction of the cylinder chamber are located in the middle of the valve plate 142. Since the number of threaded fasteners 162 is relatively small, a larger diameter and a larger tightening torque can be used.
在本发明的一个实施例中，优选地，沿气缸1的径向，位于滑片槽12两侧并靠近滑片槽12相对的两个螺纹孔16之间的距离与安装槽14的宽度之间的比值大于等于0.5。In one embodiment of the present invention, preferably, along the radial direction of the cylinder 1 , the ratio between the distance between two threaded holes 16 located on both sides of the vane groove 12 and close to the vane groove 12 and opposite to the width of the mounting groove 14 is greater than or equal to 0.5.
在该实施例中，螺纹孔16的位置对滑片槽12变形也有较大影响，气缸1螺纹孔16距离滑片槽12中心越近，则螺纹紧固件162对安装槽14的安装端面的等效作用力与安装槽14侧面的距离越远，即作用力的作用力臂越大，产生的滑片槽12变形也越大，表现为滑片槽12变窄，如图7所示，可见随着位于滑片槽12两侧的两个螺纹孔16之间的距离S与安装槽14的宽度L之间比值的增大，滑片槽12变形减小，当S/L≥0.5时，变形变化相对较为缓慢。In this embodiment, the position of the threaded hole 16 also has a great influence on the deformation of the vane slot 12. The closer the threaded hole 16 of the cylinder 1 is to the center of the vane slot 12, the farther the distance between the equivalent force of the threaded fastener 162 on the mounting end face of the mounting slot 14 and the side face of the mounting slot 14, that is, the greater the force arm of the force, the greater the deformation of the vane slot 12 produced, which is manifested as the narrowing of the vane slot 12. As shown in FIG. 7, it can be seen that as the ratio of the distance S between the two threaded holes 16 located on both sides of the vane slot 12 and the width L of the mounting slot 14 increases, the deformation of the vane slot 12 decreases. When S/L ≥ 0.5, the deformation changes relatively slowly.
具体实施例中，如图4所示，螺纹紧固件162为顶丝，顶丝可以完全设置在气缸1的螺纹孔16内部，从而避免干涉问题。与顶丝前端接触的阀板142为平面，因此平行于阀板142表面的作用力f完全由摩擦力提供，顶丝前端与阀板142接触面积较小，局部可以产生一定的变形，从而有利于增大局部的静摩擦系数μ。在平行于滑片槽12的作用力F不变时，静摩擦力f的最大值完全取决于静摩擦系数：f＝μ*F，由图5可知，f＝F*tanθ，所以得出μ＝tanθ，θ＝arctanμ。在本实施例中摩擦系数μ通常在0.3至0.4之间，因此当夹角θ大于arctanμ时，即17°至22°时，静摩擦力f将不再增大。此后，如果夹角θ进一步增大，顶丝预紧力将偏离其轴线。由图6可知，由于静摩擦力f的限制，滑片槽12变形的改善幅度受到一定的限制，最终滑片槽12变形仍然表现为变窄。需要说明的是，顶丝作为螺纹紧固件162的一种，是一种比较便捷的设计，但在此基础上进行的一些变化，如将顶丝变换为其他形式的螺钉，且连接形式未发生本质上的变化，则不应视为对本专利的规避。In a specific embodiment, as shown in FIG4 , the threaded fastener 162 is a top screw, and the top screw can be completely set inside the threaded hole 16 of the cylinder 1, thereby avoiding interference problems. The valve plate 142 in contact with the front end of the top screw is a plane, so the force f parallel to the surface of the valve plate 142 is completely provided by friction. The front end of the top screw has a small contact area with the valve plate 142, and a certain deformation can be produced locally, which is conducive to increasing the local static friction coefficient μ. When the force F parallel to the slide groove 12 remains unchanged, the maximum value of the static friction force f depends entirely on the static friction coefficient: f=μ*F. As shown in FIG5 , f=F*tanθ, so μ=tanθ, θ=arctanμ. In this embodiment, the friction coefficient μ is usually between 0.3 and 0.4, so when the angle θ is greater than arctanμ, that is, 17° to 22°, the static friction force f will no longer increase. Thereafter, if the angle θ is further increased, the top screw preload will deviate from its axis. As can be seen from FIG6 , due to the limitation of the static friction force f, the improvement of the deformation of the slide slot 12 is limited to a certain extent, and the final deformation of the slide slot 12 still shows narrowing. It should be noted that the top screw, as a type of threaded fastener 162, is a relatively convenient design, but some changes made on this basis, such as changing the top screw to other forms of screws, and the connection form has not changed substantially, should not be regarded as circumvention of this patent.
在本发明的一个实施例中，优选地，压缩机构还包括：凹槽146，设置在气缸1上，位于阀板142与螺纹紧固件162的配合处；凹槽146沿气缸1的径向截面形状为锥形。In one embodiment of the present invention, preferably, the compression mechanism further comprises: a groove 146 , which is arranged on the cylinder 1 and is located at the matching position of the valve plate 142 and the threaded fastener 162 ; the groove 146 has a conical shape along the radial cross section of the cylinder 1 .
在该实施例中，如图8所示，螺纹紧固件162接触部位设置了截面形状为锥形的凹槽146，该锥形的凹槽146可以只是位于与螺纹紧固件162接触的局部，也可以沿气缸腔中心轴线方向贯穿阀板142。由于该锥形的凹槽146的存在，解决了垂直于滑片槽12方向作用力受摩擦系数限制的问题。从而通过优化设置螺纹紧固件162的中心轴线与滑片槽12的轴向界面之间的夹角θ，大大改善螺纹紧固件162装配导致的滑片槽12变形。In this embodiment, as shown in FIG8 , a groove 146 with a conical cross-section is provided at the contact part of the threaded fastener 162. The conical groove 146 may be located only at the part in contact with the threaded fastener 162, or may penetrate the valve plate 142 along the central axis of the cylinder chamber. Due to the existence of the conical groove 146, the problem of the force in the direction perpendicular to the slide vane groove 12 being limited by the friction coefficient is solved. Thus, by optimizing the angle θ between the central axis of the threaded fastener 162 and the axial interface of the slide vane groove 12, the deformation of the slide vane groove 12 caused by the assembly of the threaded fastener 162 is greatly improved.
需要说明的是，凹槽146沿气缸1的径向截面形状也可以设置为方形、圆形、由直线或弧线构成的其他截面形状等，均可以达到相同的目的，不应作为对本发明的限制。It should be noted that the radial cross-sectional shape of the groove 146 along the cylinder 1 can also be set to be square, circular, or other cross-sectional shapes composed of straight lines or arcs, etc., which can achieve the same purpose and should not be used as a limitation to the present invention.
在本发明的一个实施例中，优选地，阀板142的朝向安装槽14侧的外侧面形成有倒角平面148，螺纹紧固件162与倒角平面148配合，以对阀板142施加挤压力。In one embodiment of the present invention, preferably, a chamfered surface 148 is formed on the outer side of the valve plate 142 facing the mounting groove 14 , and the threaded fastener 162 cooperates with the chamfered surface 148 to apply a squeezing force to the valve plate 142 .
在本发明的一个实施例中，优选地，倒角平面148与螺纹紧固件162的轴线相垂直。In one embodiment of the present invention, the chamfered plane 148 is preferably perpendicular to the axis of the threaded fastener 162 .
在该实施例中，如图9所示，将螺纹紧固件162接触位置设置于阀板142外侧面位于滑片槽12两侧边缘形成的倒角平面148上，且所述倒角平面148与螺纹紧固件162轴线垂直，保证螺纹紧固件162预紧力始终沿其轴线方向。在本发明的一个实施例中，优选地，压缩机构还包括：滑片122，滑片122可滑动地设置在滑片槽12内，滑片槽12内位于滑片122和阀板142之间形成有第二工作腔20。In this embodiment, as shown in FIG9 , the contact position of the threaded fastener 162 is set on the chamfered plane 148 formed on the outer side of the valve plate 142 and located on the edges of both sides of the sliding plate groove 12, and the chamfered plane 148 is perpendicular to the axis of the threaded fastener 162, ensuring that the pre-tightening force of the threaded fastener 162 is always along its axial direction. In one embodiment of the present invention, preferably, the compression mechanism also includes: a sliding plate 122, the sliding plate 122 is slidably arranged in the sliding plate groove 12, and a second working chamber 20 is formed in the sliding plate groove 12 between the sliding plate 122 and the valve plate 142.
在本发明的一个实施例中，优选地，压缩机构还包括：In one embodiment of the present invention, preferably, the compression mechanism further comprises:
滚子，滚子可滚动地设在气缸1的气缸腔内，滑片122的一端与滚子相连接，气缸腔的内周面、滚子的外周面以及滑片122之间形成有第一工作腔10。The roller is rotatably disposed in the cylinder cavity of the cylinder 1 , one end of the sliding plate 122 is connected to the roller, and a first working chamber 10 is formed between the inner circumference of the cylinder cavity, the outer circumference of the roller and the sliding plate 122 .
在该实施例中，滑片122在滑片槽12内可内外滑动，滚子套设在曲轴偏心部上，可随曲轴的旋转而偏心转动，此外，滚子还可绕自身轴线发生自转，滑片122内端抵在滚子上。气缸腔的内周面、滚子的外周面以及滑片122之间形成为第一工作腔10，其上下端面由上轴承和下轴承密封。第一工作腔10与第一吸气孔18相连部分为第一吸气腔，与第一排气孔相连部分为第一压缩腔。随着曲轴的旋转，第一吸气腔容积不断增大，从而不断吸入冷媒，第一压缩腔容积不断减小，腔内冷媒压力不断升高，达到排气压力时将第一排气阀片顶开，从第一排气口将高压冷媒排出，第一限位器对第一排气阀片的升程进行限制，防止发生断裂等可靠性问题。In this embodiment, the vane 122 can slide inside and outside in the vane groove 12, and the roller sleeve is arranged on the eccentric part of the crankshaft, and can rotate eccentrically with the rotation of the crankshaft. In addition, the roller can also rotate around its own axis, and the inner end of the vane 122 is against the roller. The inner circumference of the cylinder cavity, the outer circumference of the roller and the vane 122 form a first working chamber 10, and its upper and lower end surfaces are sealed by an upper bearing and a lower bearing. The part of the first working chamber 10 connected to the first suction hole 18 is the first suction chamber, and the part connected to the first exhaust hole is the first compression chamber. With the rotation of the crankshaft, the volume of the first suction chamber increases continuously, thereby continuously sucking in the refrigerant, the volume of the first compression chamber decreases continuously, and the refrigerant pressure in the chamber increases continuously. When the exhaust pressure is reached, the first exhaust valve plate is pushed open, and the high-pressure refrigerant is discharged from the first exhaust port. The first limiter limits the lift of the first exhaust valve plate to prevent reliability problems such as breakage.
滑片槽12内位于滑片122和阀板142之间形成为第二工作腔20，其上下端面由上轴承和下轴承密封。滑片122内端与滚子通过铰接方式连接，保证二者在任何情形下不发生脱离，随着曲轴的旋转，滑片122在滑片槽12内进行直线往复运动。当滑片122向内运动时(朝向气缸腔轴线)，第二工作腔20容积增大，增大到一定程度吸气阀片144打开，吸入中间压力冷媒(压力高于第一工作腔10吸气压力)；当滑片122向外运动时(远离气缸腔轴线)，第二工作腔20容积减小，冷媒被压缩，压力不断升高，达到排气压力时将第二排气阀片顶开，从第二排气口将高压冷媒排出，类似地，第二限位器对第二排气阀片的升程进行限制。通过采用双工作腔结构，提升压缩机的工作效率，以提升用户对空调器的使用体验。The second working chamber 20 is formed between the vane 122 and the valve plate 142 in the vane slot 12, and its upper and lower end surfaces are sealed by the upper bearing and the lower bearing. The inner end of the vane 122 is connected to the roller by a hinged manner to ensure that the two do not separate under any circumstances. As the crankshaft rotates, the vane 122 performs linear reciprocating motion in the vane slot 12. When the vane 122 moves inward (toward the axis of the cylinder chamber), the volume of the second working chamber 20 increases, and when it increases to a certain extent, the suction valve plate 144 opens to inhale the intermediate pressure refrigerant (the pressure is higher than the suction pressure of the first working chamber 10); when the vane 122 moves outward (away from the axis of the cylinder chamber), the volume of the second working chamber 20 decreases, the refrigerant is compressed, and the pressure continues to increase. When the exhaust pressure is reached, the second exhaust valve plate is pushed open, and the high-pressure refrigerant is discharged from the second exhaust port. Similarly, the second limiter limits the lift of the second exhaust valve plate. By adopting a dual working chamber structure, the working efficiency of the compressor is improved, so as to enhance the user experience of the air conditioner.
本发明的再一个实施例提供了一种压缩机，包括如上述任一实施例的压缩机构。Yet another embodiment of the present invention provides a compressor, comprising a compression mechanism as described in any of the above embodiments.
本发明提供的压缩机，包括上述任一实施例所述的压缩机构，因此具有压缩机构的全部有益效果，在此不再赘述。The compressor provided by the present invention includes the compression mechanism described in any of the above embodiments, and therefore has all the beneficial effects of the compression mechanism, which will not be repeated here.
本发明的又一个实施例提供了一种制冷循环装置，包括：如上述任一实施例的压缩机构；或如上述实施例的压缩机。Yet another embodiment of the present invention provides a refrigeration cycle device, comprising: a compression mechanism as in any of the above embodiments; or a compressor as in the above embodiments.
本发明提供的制冷循环装置，包括上述任一实施例所述的压缩机构，或上述实施例的压缩机，因此具有压缩机构和压缩机的全部有益效果，在此不再赘述。The refrigeration cycle device provided by the present invention includes the compression mechanism described in any of the above embodiments, or the compressor of the above embodiments, and therefore has all the beneficial effects of the compression mechanism and the compressor, which will not be repeated here.
具体实施例中，如图10所示，制冷循环装置包括：压缩机30、四通阀40、室外换热器50、第一节流元件60、闪蒸器70、第二节流元件80和室内换热器90。四通阀40在图中状态下时制冷装置处于制冷模式，经第一工作腔10和第二工作腔20压缩的高压冷媒在压缩机30内部混合(也可以在压缩机30外部混合，不应视为对本发明制冷装置的限制)，一起流向室外换热器50进行冷凝，冷凝后的液态冷媒经节流元件节流至所需的中间压力，然后在闪蒸器70中进行分离，分离后的饱和液态冷媒再次进入节流元件节流，最终达到蒸发压力值进入室内换热器90进行蒸发。蒸发后的冷媒经过第一吸气孔18重新回到第一工作腔10进行压缩。而闪蒸器70中分离出来的中间压力的气体，则通过第二吸气孔重新回到第二工作腔20进行压缩。In a specific embodiment, as shown in FIG10 , the refrigeration cycle device includes: a compressor 30, a four-way valve 40, an outdoor heat exchanger 50, a first throttling element 60, a flash evaporator 70, a second throttling element 80 and an indoor heat exchanger 90. When the four-way valve 40 is in the state shown in the figure, the refrigeration device is in a refrigeration mode, and the high-pressure refrigerant compressed by the first working chamber 10 and the second working chamber 20 is mixed inside the compressor 30 (it can also be mixed outside the compressor 30, which should not be regarded as a limitation of the refrigeration device of the present invention), and flows to the outdoor heat exchanger 50 for condensation. The condensed liquid refrigerant is throttled to the required intermediate pressure by the throttling element, and then separated in the flash evaporator 70. The saturated liquid refrigerant after separation enters the throttling element again for throttling, and finally reaches the evaporation pressure value and enters the indoor heat exchanger 90 for evaporation. The evaporated refrigerant returns to the first working chamber 10 through the first air suction hole 18 for compression. The gas of the intermediate pressure separated in the flash evaporator 70 returns to the second working chamber 20 through the second air suction hole for compression.
通常制冷循环装置中冷媒节流膨胀所做的功完全浪费掉了，而本发明制冷循环装置中闪蒸器70分离出来的中间压力气体直接回到第二工作腔20压缩，相当于回收了一部分的膨胀功。此外，由于进入室内换热器90的为饱和液态冷媒，即降低了室内换热器90中冷媒的干度，从而提高了室内换热器90的换热效率。In general, the work done by the throttling expansion of the refrigerant in the refrigeration cycle device is completely wasted, while in the refrigeration cycle device of the present invention, the intermediate pressure gas separated by the flash evaporator 70 is directly returned to the second working chamber 20 for compression, which is equivalent to recovering a part of the expansion work. In addition, since the refrigerant entering the indoor heat exchanger 90 is saturated liquid refrigerant, the dryness of the refrigerant in the indoor heat exchanger 90 is reduced, thereby improving the heat exchange efficiency of the indoor heat exchanger 90.
制冷循环装置通过四通阀40可切换为制热模式，此时经第一工作腔10和第二工作腔20压缩的高压冷媒一起流向室内换热器90进行冷凝，冷凝后的液态冷媒经节流元件节流至所需的中间压力，然后在闪蒸器70中进行分离，分离后的饱和液态冷媒再次进入节流元件节流，最终达到蒸发压力值进入室外换热器50进行蒸发。蒸发后的冷媒经过第一吸气孔18重新回到第一工作腔10进行压缩。而闪蒸器70中分离出来的中间压力的气体，则通过第二吸气孔重新回到第二工作腔20进行压缩。The refrigeration cycle device can be switched to the heating mode through the four-way valve 40. At this time, the high-pressure refrigerant compressed by the first working chamber 10 and the second working chamber 20 flows to the indoor heat exchanger 90 for condensation. The condensed liquid refrigerant is throttled to the required intermediate pressure by the throttling element, and then separated in the flash evaporator 70. The saturated liquid refrigerant after separation enters the throttling element again for throttling, and finally reaches the evaporation pressure value and enters the outdoor heat exchanger 50 for evaporation. The evaporated refrigerant returns to the first working chamber 10 through the first air suction hole 18 for compression. The gas of the intermediate pressure separated in the flash evaporator 70 returns to the second working chamber 20 through the second air suction hole for compression.
在室内外温差大的情况下，本发明空调系统在低温环境下制热能力将大幅提升，可以有效达到用户对制热量的需求。When the temperature difference between indoor and outdoor is large, the heating capacity of the air-conditioning system of the present invention will be greatly improved in a low temperature environment, and the user's demand for heating amount can be effectively met.
可以理解的是，本发明压缩机构可用于单缸压缩机，也可以用于多缸压缩机。It can be understood that the compression mechanism of the present invention can be used in single-cylinder compressors as well as multi-cylinder compressors.
本发明的又一个提供了一种空调器，包括：如上述实施例的制冷循环装置。Still another aspect of the present invention provides an air conditioner, comprising: a refrigeration cycle device as described in the above embodiment.
本发明提供的空调器，包括上述实施例的制冷循环装置，因此具有上述制冷循环装置的全部有益效果，在此不再赘述。The air conditioner provided by the present invention includes the refrigeration cycle device of the above embodiment, and thus has all the beneficial effects of the above refrigeration cycle device, which will not be described in detail here.
另外，在本发明的描述中，术语“中心”、“长度”、“宽度”、“厚度”、“上”、“下”、“竖直”、“水平”、“顶”、“底”“内”、“外”、“轴向、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本发明和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，限定有“第一”、“第二”的特征可以明示或者隐含地包括一个或者更多个该特征。在本发明的描述中，除非另有说明，“多个”的含义是两个或两个以上。术语“连接”、“安装”、“固定”等均应做广义理解，例如，“连接”可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是直接相连，也可以通过中间媒介间接相连。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本发明中的具体含义。In addition, in the description of the present invention, the terms "center", "length", "width", "thickness", "up", "down", "vertical", "horizontal", "top", "bottom", "inside", "outside", "axial", "radial", "circumferential" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention. In addition, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, unless otherwise specified, "multiple" means two or more. The terms "connect", "install", "fix" and the like should be understood in a broad sense. For example, "connection" can be a fixed connection, a detachable connection, or an integral connection; it can be directly connected or indirectly connected through an intermediate medium. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.
在本发明的描述中，术语“一个实施例”、“一些实施例”、“具体实施例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或特点包含于本发明的至少一个实施例或示例中。在本发明中，对上述术语的示意性表述不一定指的是相同的实施例或实例。而且，描述的具体特征、结构、材料或特点可以在任何的一个或多个实施例或示例中以合适的方式结合。In the description of the present invention, the description of the terms "one embodiment", "some embodiments", "specific embodiments", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In the present invention, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811006105.2ACN110873050B (en) | 2018-08-30 | 2018-08-30 | Compression mechanism, compressor, refrigeration cycle device and air conditioner |
| Application Number | Priority Date | Filing Date | Title |
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| CN201811006105.2ACN110873050B (en) | 2018-08-30 | 2018-08-30 | Compression mechanism, compressor, refrigeration cycle device and air conditioner |
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| CN110873050A CN110873050A (en) | 2020-03-10 |
| CN110873050Btrue CN110873050B (en) | 2024-11-01 |
| Application Number | Title | Priority Date | Filing Date |
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| CN201811006105.2AActiveCN110873050B (en) | 2018-08-30 | 2018-08-30 | Compression mechanism, compressor, refrigeration cycle device and air conditioner |
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| CN208702693U (en)* | 2018-08-30 | 2019-04-05 | 广东美芝精密制造有限公司 | Compression mechanism, compressor, refrigerating circulatory device and air conditioner |
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