CN114026328A - Scroll compressor and air conditioner using the same - Google Patents

Abstract

Translated fromChinese

涡旋压缩机具备固定涡盘、与固定涡盘啮合形成吸入室或压缩室的回旋涡盘、设于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、以及设于上述第一空间的外周侧且具有中间压力的第二空间。另外，具备：周向槽，其形成于固定涡盘的成为滑动面的盖板面及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，上述周向槽在作用于回旋涡盘的载荷成为最大的曲柄角的附近，设于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包括上述最强力地抵接的位置的大致±90度的范围内。

The scroll compressor includes a fixed scroll, an orbiting scroll that meshes with the fixed scroll to form a suction chamber or a compression chamber, a first space provided on the center side of the back of the orbiting scroll and having a pressure close to the discharge pressure, and a first space provided in the orbiting scroll. A second space having an intermediate pressure on the outer peripheral side of the first space. In addition, a circumferential groove extending in the circumferential direction is provided on at least one of a cover surface serving as a sliding surface of the fixed scroll and a cover surface serving as a sliding surface of the orbiting scroll, and a passage provided in A cover plate of the orbiting scroll for supplying the lubricating oil in the first space to the circumferential groove, which is provided in the orbiting scroll in the vicinity of the crank angle at which the load acting on the orbiting scroll becomes the largest The position where the cover plate of the disk most strongly abuts on the cover plate surface of the fixed scroll, and the length of the circumferential groove in the circumferential direction is within a range of approximately ±90 degrees including the position where the most strongly abuts. Inside.

Description

Scroll compressor and air conditioner using the same

Technical Field

The present invention relates to a scroll compressor and an air conditioner using the scroll compressor.

Background

A scroll compressor for use in an air conditioner or the like includes a fixed scroll having a scroll wrap standing on a base plate and an orbiting scroll having a scroll wrap standing on a cover plate, wherein the wraps of the scrolls are engaged with each other so as to face inward. Further, the orbiting scroll is made to perform an orbiting motion, and the volumes of a plurality of compression chambers formed between the two wraps are sequentially reduced, thereby compressing the working gas.

Due to such a compression action, an axial force to separate the fixed scroll and the orbiting scroll from each other is generated. When the two scrolls are separated from each other, a gap is formed between the tip and the root of the wrap, and the sealing performance of the compression chamber is deteriorated, thereby reducing the efficiency of the compressor.

In a scroll compressor, in order to prevent the two scrolls from separating, a first space (high pressure chamber) which is approximately a discharge pressure is provided on the center side of the back surface of a cover plate of an orbiting scroll, a second space (back pressure chamber) which is a pressure (intermediate pressure) between the discharge pressure and a suction pressure is formed on the back surface of the cover plate on the outer peripheral side of the first space, and a pressing force which presses the orbiting scroll against a fixed scroll is generated by the pressures of the first and second spaces.

However, due to this pressing force, sliding friction occurs between a sliding surface (cover plate surface) of a base plate of the fixed scroll and a cover plate of the orbiting scroll, and when the pressing force is too large, a seizure phenomenon or the like occurs on the sliding surface, which deteriorates reliability of the compressor.

Therefore, the following improvements have been made in the conventional scroll compressor: a structure for supplying lubricating oil to a sliding surface (cover plate surface) of a fixed scroll and a revolving scroll is adopted, and the lubricating state of the sliding surface is improved.

For example, in a scroll compressor described in japanese patent application laid-open No. 2008-2422 (patent document 1), a groove is provided on a cover plate surface of an orbiting scroll or a fixed scroll, a passage communicating with a first space (high-pressure chamber) is provided in the cover plate of the orbiting scroll, and the groove and the passage are communicated with each other, whereby high-pressure lubricant oil in the first space is supplied to a sliding surface (cover plate surface). Thereby, the lubricating oil is supplied to the sliding surface of the fixed scroll and the orbiting scroll, and the lubricating state of the sliding surface is improved.

Further, in the scroll compressor described in japanese patent application laid-open No. 2016 and 17484 (patent document 2), an oil groove is formed in a sliding surface (cover plate surface) of the fixed scroll that slides on the orbiting scroll so as to extend in the axial direction. Further, the fixed scroll is provided with a plurality of oil introduction passages and oil feed points for supplying the lubricating oil to the oil groove, and the lubricating oil from the high-pressure space inside the casing is supplied to the oil feed points.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open No. 2008-2422

Patent document 2: japanese patent laid-open publication No. 2016-17484

Disclosure of Invention

Problems to be solved by the invention

Patent document 1 does not describe the position of the groove into which the high-pressure lubricating oil is introduced and the length of the groove. Therefore, if the groove is short, the effect of improving the lubrication state of the sliding surface (the cover plate surface) is reduced, and the reliability of the compressor is reduced. On the other hand, if the groove is too long, the amount of lubricant leaking from the groove into the suction chamber increases, and the heating loss due to the refrigerant gas heated by the lubricant increases. Further, since the downward pressure is increased, there is also a problem that the orbiting scroll is easily detached.

In theabove patent document 2, an oil groove having a plurality of oil feed points is used, and an annular or C-shaped oil groove having a groove length exceeding a half turn is used, and since the groove is long, the amount of leakage of the lubricating oil from the groove to the suction chamber increases, and the heating loss increases because the lubricating oil heats the refrigerant gas. Further, since the downward pressure is increased, there is also a problem that the orbiting scroll is easily detached.

The invention aims to obtain a scroll compressor and an air conditioner using the scroll compressor, wherein the scroll compressor suppresses the increase of heating loss, improves the lubricating property of a sliding surface between a fixed scroll and a rotary scroll, and has high efficiency and high reliability.

Means for solving the problems

In order to achieve the above object, the present invention provides a scroll compressor including: a fixed scroll disk with a spiral scroll is vertically arranged on the bedplate; a rotary vortex disk which is vertically provided with a vortex-shaped scroll on the cover plate and forms a suction chamber or a compression chamber by engaging with the fixed vortex disk and performing rotary motion; a first space provided on a back center side of the orbiting scroll and having a pressure close to a discharge pressure; and a second space provided on a rear surface of the orbiting scroll and on an outer peripheral side of the first space, the second space having an intermediate pressure between a discharge pressure and a suction pressure, the scroll compressor including: a circumferential groove formed on at least one of a cover plate surface of the fixed scroll which becomes a sliding surface and a cover plate surface of the orbiting scroll which becomes a sliding surface, the circumferential groove extending in a circumferential direction; and a passage provided in a cover plate of the orbiting scroll and configured to supply the lubricant oil in the first space to the circumferential groove, wherein the circumferential groove is provided in a vicinity of a crank angle at which a load acting on the orbiting scroll becomes maximum, the cover plate of the orbiting scroll is most strongly abutted against a cover plate surface of the fixed scroll, and a length of the circumferential groove in a circumferential direction is a length at which both ends of the circumferential groove are arranged within a range of approximately ± 90 degrees including the most strongly abutted position.

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 connected in this order by refrigerant pipes to form a refrigeration cycle, wherein the scroll compressor is used as the scroll compressor.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, a scroll compressor capable of improving the lubricity of the sliding surface between the fixed scroll and the orbiting scroll while suppressing an increase in heating loss, and having high efficiency and high reliability, and an air conditioner using the scroll compressor can be obtained.

Drawings

Fig. 1 is a longitudinal sectional view showing a scroll compressor according toembodiment 1 of the present invention.

Fig. 2 is a bottom view of the fixed scroll shown in fig. 1, and is a cross-sectional view of the wrap of the orbiting scroll.

Fig. 3 is a diagram illustrating a pressure distribution on an orbiting scroll cover plate surface of a conventional scroll compressor.

Fig. 4 is a diagram illustrating a pressure distribution on the orbiting scroll cover plate surface in example 1 of the present invention.

Fig. 5 is a graph illustrating a variation of a load with respect to a crank angle in one rotation of the scroll compressor.

Fig. 6 is a graph illustrating a relationship between a crank angle of the scroll compressor and a change in pressure in the compression chamber.

Fig. 7 is a view showingembodiment 2 of the scroll compressor according to the present invention, and corresponds to fig. 2.

Fig. 8 is a view showingembodiment 3 of the scroll compressor according to the present invention, and corresponds to fig. 2.

Fig. 9 is a plan view illustrating an orbiting scroll of embodiment 4 of the scroll compressor of the present invention.

Fig. 10 is a bottom view illustrating a fixed scroll ofembodiment 5 of the scroll compressor of the present invention.

Fig. 11 is a longitudinal sectional view illustrating an orbiting scroll of example 6 of a scroll compressor of the present invention.

Fig. 12 is a plan view illustrating an orbiting scroll ofembodiment 7 of the scroll compressor of the present invention.

Fig. 13 is a bottom view illustrating a fixed scroll ofembodiment 8 of the scroll compressor of the present invention.

Fig. 14 is a refrigeration cycle configuration diagram illustrating an example of an air conditioner using a scroll compressor of the present invention.

Detailed Description

Hereinafter, specific examples of the scroll compressor and the air conditioner using the scroll compressor according to the present invention will be described with reference to the drawings. In the drawings, the same reference numerals denote the same or equivalent parts.

Embodiment 1 of the scroll compressor of the present invention will be described with reference to fig. 1 to 6.

First, the overall structure of a scroll compressor to which the present embodiment is applied will be described with reference to fig. 1 and 2. Fig. 1 is a longitudinal sectional view of a scroll compressor according to example 1, and fig. 2 is a bottom view of the fixed scroll shown in fig. 1, showing a wrap of the orbiting scroll in cross section.

Thescroll compressor 1 is configured by accommodating thecompression mechanism section 2, themotor section 16, and the like in a closed container (casing) 9.

Thecompression mechanism 2 includes aframe 17, afixed scroll 7 fixed to theframe 17, and anorbiting scroll 8 fixed between theframe 17 and thefixed scroll 7 and engaged with thefixed scroll 7 to form acompression chamber 13.

Thefixed scroll 7 includes a disc-shaped base plate 7a, awrap 7b standing up on the base plate 7a in a spiral shape, and asupport portion 7d, and thesupport portion 7d is located on the outer peripheral side of the base plate 7a, has acover plate surface 7e having substantially the same height as the front end surface of thewrap 7b, and is provided in a cylindrical shape so as to surround thewrap 7 b. The surface of the platen 7a on which the above-describedlap 7b is erected is referred to as aroot 7c because it is located between thelaps 7 b. Acover plate surface 7e of thesupport portion 7d of thefixed scroll 7 is a sliding surface contacting thecover plate 8a of the orbitingscroll 8.

Thefixed scroll 7 is fixed to thesupport portion 7d by bolts or the like to theframe 17, and theframe 17 integrated with thefixed scroll 7 is fixed to the sealed container 9 by a fixing method such as welding.

The orbitingscroll 8 is disposed to face thefixed scroll 7, and awrap 7b of thefixed scroll 7 and awrap 8b of the orbitingscroll 8 are engaged with each other and disposed in aframe 17 so as to be able to orbit. The orbitingscroll 8 includes a disk-shaped cover plate 8a, aspiral wrap 8b standing from aroot 8c of the surface of thecover plate 8a, and a boss (orbiting boss) 8d provided at the center of the back surface of thecover plate 8 a. The surface of the outer peripheral portion of thecover 8a that contacts thefixed scroll 7 is acover surface 8e of the orbitingscroll 8.

A tip end portion (wrap tip) of thewrap 8b of the orbitingscroll 8 is configured to face thetooth root 7c of thefixed scroll 7 with a slight gap therebetween. Similarly, the tip end (wrap tip) of thewrap 7b of thefixed scroll 7 is also configured to face thetooth root 8c of theorbiting scroll 8 with a slight gap therebetween.

Themotor 16 includes arotor 16a and astator 16b, and a crankshaft (rotating shaft) 10 is integrally fixed to therotor 16 a.

Theorbiting scroll 8 is driven by amotor unit 16 via thecrankshaft 10, and theorbiting scroll 8 is made to perform an orbiting motion, thereby performing a compression operation in which the volume of thecompression chamber 13 is gradually reduced.

In accordance with this compression operation, the working fluid such as a refrigerant flowing through the refrigeration cycle is sucked into the suction chamber 20 (see fig. 2) from thesuction port 14, and the sucked working fluid is discharged from thedischarge port 15 to the discharge space 54 in the closed casing 9 through the compression stroke in thecompression chamber 13. The working fluid discharged into the discharge space 54 flows into themotor chamber 52 through a passage (not shown) formed between the outer periphery of the fixedscroll 7 and the outer periphery of theframe 17, and is then discharged from thedischarge pipe 6 to the outside of the sealed container 9.

Thecrankshaft 10 is rotatably supported by amain bearing 5 provided in theframe 17, and a central axis of thecrankshaft 10 is coaxial with a central axis O1 of the fixedscroll 7. An eccentric crankportion 10a is provided at a tip end portion (upper end portion) of thecrankshaft 10, and thecrank portion 10a is inserted into a rotary bearing 11 provided at arotary boss portion 8d of therotary scroll 8. Accordingly, theorbiting scroll 8 is configured to perform an orbiting motion by an eccentric motion of thecrank portion 10a when thecrankshaft 10 is rotated.

The center axis O2 of theorbiting scroll 8 is eccentric by a predetermined distance from the center axis of the fixedscroll 7.Wrap 8b of orbitingscroll 8 overlaps wrap 7b offixed scroll 7 at a predetermined angle (generally 180 degrees) in the circumferential direction. Further, anoldham ring 12 for relatively performing an orbiting motion of theorbiting scroll 8 with respect to the fixedscroll 7 while being restrained in a non-orbiting manner is provided between the orbitingscroll 8 and theframe 17.

The engagement state of the fixedscroll 7 and theorbiting scroll 8 will be described with reference to fig. 2. In fig. 2, awrap 8b of theorbiting scroll 8 is shown in a sectional view, and a portion corresponding to the outer periphery of acover plate 8a of theorbiting scroll 8 is shown in a phantom line drawing with two-dot chain lines. As shown in fig. 2, a plurality of crescent-shaped compression chambers 13 (inner orbiting lineside compression chamber 13a and outer orbiting lineside compression chamber 13b) are formed between thewrap 7b of the fixedscroll 7 and thewrap 8b of theorbiting scroll 8, and when theorbiting scroll 8 is made to perform an orbiting motion, the volumes of thecompression chambers 13 are continuously reduced as they move toward the center.

Reference numeral 20 denotes a suction chamber, which is a space on the way of sucking fluid. Thesuction chamber 20 serves as thecompression chamber 13 from the time when the phase of the orbiting motion of theorbiting scroll 8 advances to complete the sealing of the fluid.

As shown in fig. 1 and 2, thesuction port 14 is provided in the fixedscroll 7, and thesuction port 14 is formed on the outer peripheral side of the base plate 7a of the fixedscroll 7 so as to communicate with thesuction chamber 20.

Thedischarge port 15 is provided near the center of the vortex of the base plate 7a of the fixedscroll 7, and is configured to communicate with thedischarge port 15 immediately when the compression in theinnermost compression chamber 13 is performed.

When thecrankshaft 10 is rotated by themotor unit 16 shown in fig. 1, theorbiting scroll 8 performs an orbiting motion with a predetermined distance of an orbiting radius around the central axis of the fixedscroll 7. As a result, working gas (for example, refrigerant gas circulating in a refrigeration cycle) is sucked from thesuction port 14, sequentially compressed in thecompression chambers 13, and compressed working gas (hereinafter, referred to as compressed gas) is discharged from thedischarge port 15 to the discharge space 54. Thereafter, the compressed gas, for example, themotor chamber 52 is supplied to the refrigeration cycle and the like outside thescroll compressor 1 through thedischarge pipe 6.

Next, the flow of the lubricating oil in the scroll compressor (hereinafter, simply referred to as a compressor) 1 shown in fig. 1 will be described. Anoil reservoir 53 for storing lubricating oil (refrigerating machine oil) is provided at the bottom of the closed casing 9 in which thecompression mechanism 2, themotor 16, and the like are housed. A positive displacement type or centrifugal typeoil feed pump 21 is provided at the lower end of thecrankshaft 10, and theoil feed pump 21 rotates with the rotation of thecrankshaft 10, thereby sucking the lubricating oil stored in theoil reservoir 53 at the bottom of the hermetic container 9 and supplying the lubricating oil to the oil feed hole (through hole) 3 formed in thecrankshaft 10 in the axial direction.

The lubricating oil in theoil reservoir 53 is sucked from the lubricatingoil suction port 25 provided in the oilfeed pump case 22 and discharged from thedischarge port 28 of theoil feed pump 21. The discharged lubricating oil is delivered to the upper end of thecrankshaft 10 through theoil feed hole 3.

At this time, a part of the lubricating oil flowing through theoil feed hole 3 is sent to the sub-bearing 23 through thetransverse hole 24 provided in thecrankshaft 10, lubricates the sub-bearing 23, and then returns to theoil reservoir 53 at the bottom of the closed casing 9. Most of the lubricating oil flowing through theoil supply hole 3 reaches the space inside the orbitingboss 8d at the upper end of thecrank portion 10a of thecrankshaft 10, and lubricates the orbiting bearing 11 through anoil groove 57 provided on the outer peripheral surface of thecrank portion 10 a. The lubricating oil is then returned to theoil reservoir 53 at the bottom of the sealed container 9 through an oil return passage formed by theoil drain hole 26a and theoil drain pipe 26b after lubricating themain bearing 5 provided at the lower portion of the orbitingbearing 11.

The space inside the orbitingboss 8d (the space at the upper end of the crankpart 10a, the space formed by the gap between the orbitingbearing 11 and thecrankshaft 10, and the oil groove 57), the space located on the outer peripheral side of theorbiting boss 8d (the space formed by the orbitingboss 8d, the back surface of thecover plate 8a, theseal member 32, and the frame 17), and the space for housing the main bearing 5 (the space formed by theframe 17, thecrankshaft 10, and the frame seal 56) are collectively referred to as afirst space 33. Thefirst space 33 is a space having a pressure close to the discharge pressure.

Most of the lubricating oil flowing into thefirst space 33 to lubricate themain bearing 5 and the orbiting bearing 11 is returned to theoil reservoir 53 at the bottom of the sealed container 9 through the return passage of theoil drain hole 26a and theoil drain pipe 26 b. Further, a part of the lubricating oil flows into a back pressure chamber (second space) 18 through an oil leakage unit provided between the upper end surface of theseal member 32 and the back surface of thecover plate 8a, and theback pressure chamber 18 is provided on the outer circumferential side of thefirst space 33 and is a pressure between the discharge pressure and the suction pressure (intermediate pressure, hereinafter also referred to as back pressure). The lubricating oil that has flowed into theback pressure chamber 18 is used for lubrication of theoldham ring 12, lubrication of sliding portions between thecover surfaces 7e and 8e of the fixedscroll 7 and theorbiting scroll 8, sealing (sealing) of a gap between thewraps 7b and 8b, and the like. Accordingly, the oil leakage means is configured to allow the amount of lubricating oil necessary for the lubrication and sealing to flow into theback pressure chamber 18.

Theseal member 32 is provided in anannular groove 31 provided in a surface of theframe 17 facing the back surface of thecover plate 8a, together with a wave spring (not shown). Theseal member 32 partitions thefirst space 33 at the discharge pressure and the back pressure chamber (second space) 18 at an intermediate pressure between the suction pressure and the discharge pressure.

The oil leakage means is constituted by, for example, one or more slit-shapedshallow grooves 58 provided on the back surface of thecover plate 8a and theseal member 32. Theshallow groove 58 is disposed across theseal member 32 by the orbiting motion of theorbiting scroll 8, and intermittently communicates thefirst space 33 and theback pressure chamber 18. With this configuration, the lubricant oil can be caused to flow from thefirst space 33 into theback pressure chamber 18 through theshallow groove 58, which is a minute gap, by the pressure difference between thefirst space 33 and theback pressure chamber 18.

Instead of theshallow grooves 58, one or more oil pockets (holes serving as oil reservoirs, for example, circular grooves) may be provided on the back surface of thecover plate 8a, and the oil pockets may perform a circular motion across theseal member 32 in accordance with the orbiting motion of theorbiting scroll 8. With this configuration, the oil pocket moves between thefirst space 33 and theback pressure chamber 18, and the lubricating oil in thefirst space 33 can be stored in the oil pocket and intermittently transferred to theback pressure chamber 18, and the lubricating oil in thefirst space 33 can be supplied to theback pressure chamber 18.

The lubricating oil introduced into theback pressure chamber 18 lubricates the sliding portion of theoldham ring 12, and a portion of the lubricating oil passes through a small gap between thefixed scroll 7 and thecover plate surfaces 7e and 8e of theorbiting scroll 8 while lubricating, and flows into thesuction chamber 20 or thecompression chamber 13. When the pressure (back pressure) in the back pressure chamber becomes high, the other lubricating oil flows into thecompression chamber 13 through theback pressure hole 35 that communicates theback pressure chamber 18 and thecompression chamber 13. Theback pressure hole 35 is a hole for adjusting the pressure in theback pressure chamber 18.

The lubricant oil that has flowed into thesuction chamber 20 and thecompression chamber 13 is used for sealing and lubricating the gap between thewrap 7b of the fixedscroll 7 and thewrap 8 of theorbiting scroll 8, and then discharged from thedischarge port 15 into the discharge space 54. Part of the discharged oil is discharged from thedischarge pipe 6 to the refrigeration cycle together with the refrigerant gas, and the remaining part is separated from the refrigerant gas in the closed casing 9 and is stored in theoil reservoir 53 at the bottom of the closed casing 9.

As described above, by providing thefirst space 33, theback pressure chamber 18, and the oil leakage means, the amount of oil supply to each bearing and the amount of oil supply to theback pressure chamber 18 can be independently controlled, and therefore, a scroll compressor with high efficiency can be obtained.

Next, the function of theback pressure chamber 18 will be described. In thescroll compressor 1, due to the compression action thereof, an axial force (separation force) is generated to separate thefixed scroll 7 and theorbiting scroll 8 from each other. When the so-called separation phenomenon of theorbiting scroll 8 in which the two scrolls are separated from each other occurs due to the axial force, the sealing property of thecompression chamber 13 is deteriorated, and the compressor efficiency is lowered.

Therefore, aback pressure chamber 18 that is a pressure between the discharge pressure and the suction pressure is provided on the back surface side of thecover plate 8a of theorbiting scroll 8, and theorbiting scroll 8 is pressed against the fixedscroll 7 while the separating force is cancelled by the pressure (intermediate pressure) of theback pressure chamber 18 and the discharge pressure of thefirst space 33.

At this time, if the pressing force is too large, the sliding loss between thecover surface 8e of theorbiting scroll 8 and thecover surface 7e of the fixedscroll 7 increases, the compressor efficiency decreases, and problems such as abrasion, seizure, or seizure occur in thecover surfaces 7e and 8e, which lowers the reliability of the compressor. That is, the pressing force has an optimum value, and when it is too small, the sealing property of the compression chamber is deteriorated, and the thermal fluid loss is increased, and when it is too large, the sliding loss is increased. Therefore, maintaining the pressing force at an optimum value is important for improving the performance and reliability of the compressor.

The above is the basic configuration of thescroll compressor 1. Here, the diameter of the orbiting bearing 11 may be increased for the reason of, for example, improving the reliability of the orbitingbearing 11. In this case, the diameter of the sealingmember 32 disposed outside the sealing member is also increased, and thefirst space 33 having a pressure close to the discharge pressure is increased. Therefore, the area of discharge pressure acting on the back surface ofcover plate 8a of orbitingscroll 8 is also expanded, and the above-described pressing force is increased. If this increase in pressing force is too large, the sliding loss between thecover plate surface 7e and thecover plate surface 8e increases, and problems such as abrasion, seizure, or seizure occur, which lowers the reliability of the compressor. In particular, under a high pressure ratio condition in which thescroll compressor 1 is operated at a high pressure ratio, the above-described pressing force is excessively large, and seizure, burn-out, and the like occur on the cover plate surface, which tends to reduce the reliability of the compressor.

Therefore, in the present embodiment, the following structure is adopted: a circumferential groove extending in the circumferential direction is formed in at least one of acover surface 7e serving as a sliding surface of the fixedscroll 7 and acover surface 8e serving as a sliding surface of theorbiting scroll 8, and a passage for supplying the lubricant oil in thefirst space 33 to the circumferential groove is provided in thecover 8a of theorbiting scroll 8. The circumferential groove is provided in the vicinity of a crank angle at which a load acting on the orbiting scroll becomes maximum, and the cover plate of the orbiting scroll is configured to be in most strong contact with the cover plate surface of the fixed scroll.

With such a configuration, since the discharge pressure can act on the sliding surface between thecover surface 7e of the fixedscroll 7 and thecover surface 8e of theorbiting scroll 8, a force in the direction of separating theorbiting scroll 8 from the fixedscroll 7, that is, a downward pressure can be applied. Therefore, excessive pressing force can be avoided.

In the present embodiment, the circumferential length of the circumferential groove is configured such that one end of the circumferential groove is disposed within a range of +70 to +100 degrees from the most strongly abutting position, and the other end of the circumferential groove is disposed within a range of-70 to-100 degrees from the most strongly abutting position. Therefore, the amount of leakage of the lubricating oil from the circumferential groove to thesuction chamber 20 can be reduced, and the heating loss of the refrigerant gas heated by the lubricating oil can be reduced. Further, it is possible to prevent the above-described downward pressure from being excessively large, and to ensure the downward pressure at a position where thecover plate 8a of theorbiting scroll 8 most strongly abuts on thecover plate surface 7e of the fixedscroll 7.

The length of the circumferential groove in the circumferential direction is not limited to the above range, and one end of the circumferential groove may be disposed within a range of +20 to +100 degrees from the position where the circumferential groove most strongly abuts, and the other end may be disposed within a range of-20 to-100 degrees from the position where the circumferential groove most strongly abuts. For example, one end of the circumferential groove may be disposed within a range of +20 to +40 degrees from the most strongly contacting position, and the other end may be disposed within a range of-20 to-40 degrees from the most strongly contacting position.

Hereinafter, specific embodiments of the scroll compressor according to the present invention will be described with reference to the drawings. As shown in fig. 1 and 2, inembodiment 1, acircumferential groove 36 is provided in the fixedscroll 7. As shown in fig. 1, apassage 37 having one end communicating with thefirst space 33 is provided in thecover plate 8a of theorbiting scroll 8. Thepassage 37 is used to supply the lubricating oil (hereinafter, also referred to as oil) in thefirst space 33 to thecircumferential groove 36.

In order to receive the lubricating oil from thepassage 37, as shown in fig. 2, acircular groove portion 36a is formed at one end portion or a part of thecircumferential groove 36. Thecircular groove 36a is formed in a circle having a radius equal to or greater than the turning radius so as to communicate with the end of thepassage 37 over the entire range of the turning motion of the end of thepassage 37 opened in thegroove 36 a. Acircle 45 shown by a chain line in fig. 2 indicates a locus of movement of thepassage 37 with respect to the fixedscroll 7 when theorbiting scroll 8 orbits.

Further, thecircumferential groove 36 except for thegroove portion 36a is formed to have a width smaller than the diameter of thegroove portion 36a and to be longer than the diameter of thegroove portion 36a in the circumferential direction. Thegroove 36a is not limited to a circular shape, and may be formed in another shape such as an elliptical shape or a rectangular shape as long as it communicates with thegroove 36a over the entire range of the end of thepassage 37 performing the turning motion.

Thepassage 37 communicates with thecircular groove 36a, so that the lubricating oil in thefirst space 33 is supplied to the space of thecircular groove 36a, and the oil is supplied from thecircular groove 36a to thecircumferential groove 36. By supplying high-pressure oil to thecircumferential groove 36, the pressure in thecircumferential groove 36 is a pressure close to the discharge pressure, similarly to the pressure in thefirst space 33.

Here, the pressure distribution on the cover plate surface of theorbiting scroll 8 of the conventional scroll compressor will be described with reference to fig. 3, and the pressure distribution on the cover plate surface of theorbiting scroll 8 of the scroll compressor of the present embodiment will be described with reference to fig. 4.

As shown in fig. 3, in the pressure distribution on the cover plate surface of theorbiting scroll 8 of the conventional scroll compressor, the pressure on the side facing the back pressure chamber 18 (outer peripheral side of the cover plate) is the back pressure, and the pressure on the side facing thesuction chamber 20 or the compression chamber 13 (see fig. 2) (inner peripheral side of the cover plate and any side of thewrap 8 b) is the suction pressure or the pressure in the compression chamber.

In contrast, in thescroll compressor 1 of the present embodiment, since thecircumferential groove 36 is provided, oil at discharge pressure is introduced into thecircumferential groove 36. Therefore, as shown by the pressure distribution on the orbiting scroll cover surface shown on the right side in fig. 4, the oil of the discharge pressure is introduced into thecircumferential groove 36, and the force pressing theorbiting scroll 8 downward is increased by thearea 38 indicated by oblique lines in fig. 4. Therefore, an increase in the pressing force at a position where the cover plate of theorbiting scroll 8 most strongly abuts against the cover plate surface of the fixed scroll can be suppressed.

Further, the lubricating oil that has flowed into thecircumferential groove 36 flows through a small gap between thecover plate surface 7e of the fixedscroll 7 and thecover plate surface 8e of theorbiting scroll 8 while lubricating, and flows toward theback pressure chamber 18, thesuction chamber 20, or thecompression chamber 13, so that the lubrication state at thecover plate surfaces 7e, 8e is good, and reliability can be improved.

Next, a force acting on theorbiting scroll 8 in a direction perpendicular to the axial direction and a change in the force during one revolution will be described with reference to fig. 3 to 6.

Due to the compression action, theorbiting scroll 8 in the operation of thescroll compressor 1 generates not only axial force but also tangential and radial forces. The resultant force of these forces in the direction orthogonal to the axial direction at a certain phase of the orbiting scroll is represented by Fg in fig. 3 and 4. Further, a force Fr for causing theorbiting scroll 8 to orbit, which is a reaction force of Fg, acts on the orbitingbearing 11.

Here, Fg and Fr are opposite to each other, and their points of action are separated in the axial direction, so that a moment is generated in theorbiting scroll 8 as indicated by an arrow M. The moment M is a so-called tilting moment to tilt theorbiting scroll 8. Due to this upsetting moment, thecover surface 8e of theorbiting scroll 8 is locally strongly pressed against thecover surface 7e of the fixedscroll 7. When the moment M acts as shown in fig. 3 and 4, the position of the strong pressing is the right side of the cover plate.

Further, as theorbiting scroll 8 orbits, the orientation and magnitude of Fg and Fr change, and therefore the direction and magnitude of the overturning moment also change. This is the reason for the so-called orbiting motion of the orbiting scroll. Further, the position and the size of thecover plate surface 8e of theorbiting scroll 8 which is locally strongly pressed also vary during one revolution.

Fig. 5 is a graph illustrating a change in the crank angle of the load Fg per rotation of the scroll compressor, and fig. 6 is a graph illustrating a relationship between the crank angle of the scroll compressor and a change in the pressure in the compression chamber.

An example of the change in the load Fg during one rotation is shown by acurve 46 in fig. 5, and in the example of fig. 5, Fg is the largest at aposition 47 where the crank angle is substantially 180 degrees. In fig. 5, theposition 47 at which the load Fg reaches the maximum crank angle is generally determined by the number of wraps of the scroll wrap, the discharge start angle, and the like.

For example, fig. 6 shows the relationship between the crank angle of a specific scroll compressor, which is determined by the number of wraps of the scroll wrap and the discharge start angle, and thepressure 50a in the inner-orbiting lineside compression room 13a and thepressure 50b in the outer-orbiting lineside compression room 13 b. In the example shown in fig. 6, an example of a so-called asymmetric scroll in which the number of turns of the inner coilside compression room 13a and the outer coilside compression room 13b is different is shown, and an example of an operation condition in which the maximum value of the load Fg becomes the maximum and the high pressure ratio is shown among all the operation conditions. Further, the timing at which the whirling outer lineside compression room 13b completes the suction is set to 0 degree in crank angle.

In addition, the crank angle is originally 0 to 360 degrees, but in the case of a scroll compressor, usually, one rotation or more is performed from the completion of suction to the start of discharge in one compression chamber. In the case of the asymmetric wrap, the inner orbiting lineside compression room 13a finishes the suction at a position where the crank angle advances by substantially 180 degrees after the outer orbiting lineside compression room 13b finishes the suction, and starts the compression. Therefore, for convenience of explanation, the crank angle on the horizontal axis in fig. 6 is set to 0 to 720 degrees.

As shown in fig. 6, when the crank angle changes, the pressure in each compression chamber also changes. As shown in fig. 2, thescroll compressor 1 has a plurality ofcompression chambers 13, and the pressure in eachcompression chamber 13 changes as shown in fig. 6. Further, the pressure in each of thecompression chambers 13 acts on thelap 8b of theorbiting scroll 8. The resultant force of these is the load Fg (gas load) which changes as shown by thecurve 46 in fig. 5.

In the example shown in fig. 5, Fg is maximized at a crank angle of 180 degrees at which the orbiting inner wireside compression chamber 13a starts to discharge (in fig. 6, a position where 360 degrees +180 degrees is 540 degrees corresponds to a position where the crank angle of 180 degrees starts to discharge), and accordingly, the overturning moment is maximized.

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 described with reference to fig. 2 to 4. Fig. 2 is a diagram showing a state where the crank angle is 180 degrees, and fig. 3 and 4 are vertical sectional views showing a state where the load acting on the orbiting scroll is maximized when the crank angle is 180 degrees. As is clear from the moment M generated by the directions of the forces Fg and Fr shown in fig. 3 and 4, the position where the cover plate of theorbiting scroll 8 most strongly abuts against the cover plate surface of the fixedscroll 7 is the position on the right side of the cover plate surface.

This position corresponds approximately to the range indicated by thebroken line 44 in fig. 2. That is, by providing thecircumferential groove 36 at this position, it is possible to supply high-pressure lubricant oil at a pressure that is approximately equal to the discharge pressure to a position where thecover plate 8a of theorbiting scroll 8 is most strongly pressed against thecover plate surface 7e of the fixedscroll 7 during one revolution of the compressor. Accordingly, the problems such as abrasion, seizure, or seizure of thecover plates 7e and 8e can be prevented, and the reliability of the compressor can be improved.

The position where thecircumferential groove 36 is provided is as described above.

Next, a preferred shape of thecircumferential groove 36 will be described. When the shape of the circumferential groove, that is, the circumferential length exceeds half a turn, for example, like an annular shape or a C-shape, the downward pressure may become excessive, and a separation phenomenon may occur in which theorbiting scroll 8 separates from the fixedscroll 7. Further, the amount of oil supplied to thecircumferential groove 36 leaking into thesuction chamber 20 and thecompression chamber 13 increases. That is, since the flow path area of the oil leakage is expressed by the product of the length of thecircumferential groove 36 and the length of the small gap between thecover plates 7e and 8e, the longer the circumferential groove is, the larger the amount of lubricating oil flowing into thesuction chamber 20 and thecompression chamber 13 becomes, the refrigerant gas is heated, and the heating loss increases.

Therefore, in the present embodiment, thecircumferential groove 36 is formed of a portion of a substantially circular arc, and both ends thereof are in a shape within a range of substantially ± 90 degrees (within a range ofθ 1 in fig. 2) including a position where thecover plate 8a of theorbiting scroll 8 is most strongly pressed when the load Fg shown in fig. 5 is maximized. This makes it possible to arrange thecircumferential groove 36 so as to effectively supply oil to the portion where the pressing force is strong and lubrication is most necessary, and to make the length of thecircumferential groove 36 shorter. Accordingly, the occurrence of the detachment phenomenon and the heating loss can be suppressed, the increase in the pressing force can be suppressed, the problems such as abrasion, seizure, and seizure of thecover plates 7e and 8e can be prevented, and the reliability of the compressor can be improved.

Thesection 48 shown in fig. 5 shows a range of approximately ± 90 degrees including theposition 47 of the crank angle at which the load Fg becomes the maximum, and a range in which the value of the load Fg can be significantly larger than the average value can be covered by thesection 48. Therefore, thecircumferential groove 36 is provided at a position corresponding to thecover surface 7e or 8e of thesection 48. That is, thecircumferential groove 36 is provided at a position of thecover surface 7e or 8e in a region where thecover 8a of theorbiting scroll 8 is strongly pressed against thecover surface 7e of the fixedscroll 7. This makes it possible to supply the lubricating oil to the area of the lid surface where the pressing force is significantly larger than the average value.

As described above, according to the present embodiment, since thecircumferential groove 36 is provided at the position of the cover plate surface in the region where thecover plate 8a of theorbiting scroll 8 is strongly pressed against thecover plate surface 7e of the fixedscroll 7, it is possible to supply the lubricating oil to the region of the cover plate surface where the pressing force is significantly larger than the average value. Accordingly, oil can be effectively supplied to a portion where the pressing force is strong and lubrication is most required, so that the length of thecircumferential groove 36 can be further shortened, the occurrence of a separation phenomenon and a heating loss can be suppressed, the increase in the pressing force can be suppressed, the wear, the seizure, and the like of the cover plate surface can be prevented, and the reliability of the compressor can be improved.

Example 2

Embodiment 2 of the scroll compressor according to the present invention will be described with reference to fig. 5 and fig. 7. Fig. 7 is a diagram showing a scroll compressor ofembodiment 2, and corresponds to fig. 2. In fig. 7, the same or corresponding portions are denoted by the same reference numerals as in fig. 1 to 6, and the same portions as in example 1 are not described, and the portions different from example 1 will be mainly described.

As a characteristic of the scroll compressor under the high pressure ratio operation condition, in acurve 46 in fig. 5, an inclination of aleft side 46a (a side where a crank angle which is a direction in which the rotation of theorbiting scroll 8 is delayed is small, hereinafter referred to as a delay angle side) and an inclination of aright side 46b (a side where a crank angle which is a direction in which the rotation of theorbiting scroll 8 is advanced is large, hereinafter referred to as an advance angle side) with respect to aposition 47 at which a crank angle at which a load Fg becomes maximum are generally gentle. This is because, under the operating conditions of a high pressure ratio at which compression into uncompressed state is insufficient due to only a decrease in the volume of thecompression chamber 13, after discharge is started, the refrigerant gas flows backward from the discharge pressure space (discharge space 54), the pressure in the compression chamber rapidly increases to the discharge pressure, and then the refrigerant gas increased to the discharge pressure is gradually discharged into the discharge space 54 as the crank angle advances.

Therefore, as shown in fig. 5 and 7, inembodiment 2, thecircumferential groove 36 is formed so that a portion corresponding to thesection 48b is longer than a portion corresponding to thesection 48 a. Specifically, as shown in fig. 7, thecircumferential groove 36 is formed as follows: aposition 47A (see fig. 7) of the cover plate surface (a position where the cover plate of the orbiting scroll most strongly abuts on the cover plate surface of the fixed scroll) where the pressing force is significantly larger than the average value corresponds to a position 47 (see fig. 5) of the crank angle at which the load Fg acting on theorbiting scroll 8 becomes the maximum, and a side θ 1b in which the crank angle is large (advance angle side) in the rotational advance direction of theorbiting scroll 8 is longer than aside θ 1a in which the crank angle is small (retard angle side) in the direction in which the rotation of theorbiting scroll 8 is retarded.

With such a configuration, in a range where the value of the load Fg is significantly larger than the average value, that is, in a case where the lengths of thecircumferential grooves 36 are the same, an effect is obtained that the lubricating oil can be supplied more reliably to the region of the lid surface where the pressing force is significantly larger than the average value. As described above, according toembodiment 2, it is possible to further suppress the heating loss due to the lubricating oil supplied to thecircumferential groove 36, and to cover a range in which the value of the load Fg is significantly larger than the average value.

The other structure is the same as inembodiment 1 described above.

Example 3

Embodiment 3 of the scroll compressor according to the present invention will be described with reference to fig. 5 and fig. 8. Fig. 8 is a diagram showing a scroll compressor according toembodiment 3, and corresponds to fig. 2. In fig. 8, the same or corresponding portions are denoted by the same reference numerals as in fig. 1 to 6, and the same portions as in example 1 will be omitted from description, and the portions different from example 1 will be mainly described.

Inembodiment 1 shown in fig. 2, acircumferential groove 36 is provided in acover plate surface 7e of the fixedscroll 7, and acircular groove portion 36a is provided at one end portion thereof. Further, theorbiting scroll 8 is provided with apassage 37 for supplying the lubricating oil in thefirst space 33 to thecircumferential groove 36, and an end portion of thepassage 37 is communicated with thecircular groove portion 36 a. The end of thepassage 37 performs a revolving motion with its revolving radius in accordance with the revolving motion of the revolvingscroll 8. Therefore, thecircular groove 36a forms a circle having a radius equal to or larger than the turning radius so as to communicate with the entire range of turning motion at the end of thepassage 37. In addition, thecircumferential groove 36 except for thegroove portion 36a is formed to have a width smaller than the diameter of thegroove portion 36 a.

In contrast, inembodiment 3, the section in which thepassage 37 provided in theorbiting scroll 8 communicates with thecircumferential groove 36 is configured to be within a range of approximately ± 90 degrees including the crank angle at which the load Fg becomes the maximum. This communicated section corresponds to thesection 48 shown in fig. 5. That is, while the lubricating oil is supplied from thepassage 37 to thecircumferential groove 36 at all times in the configuration ofembodiment 1, the lubricating oil is intermittently supplied to thecircumferential groove 36 only at a timing when the value of the load Fg is significantly larger than the average value inembodiment 3.

A specific configuration for realizing the above-described case is explained with reference to fig. 8. Thepassage 37 that performs the circling motion at one end portion of thecircumferential groove 36 is formed with an arc-shapedgroove portion 39 that intermittently communicates only at a timing when the value of the load Fg is significantly larger than the average value. The arc-shapedgroove portion 39 is configured to communicate with the end portion of thepassage 37 only in a range of approximately ± 90 degrees including a crank angle at which the load Fg becomes maximum when theorbiting scroll 8 performs an orbiting motion. The arc-shapedgroove portion 39 is preferably formed as an arc having a groove center with a radius equal to the turning radius of theorbiting scroll 8, but the shape of thegroove portion 39 is not limited to the arc-shaped groove portion, and may be circular, rectangular, or the like as long as thegroove portion 39 is formed so that the end portion of thepassage 37 communicates with thegroove portion 39 only within a range of approximately ± 90 degrees including the crank angle at which Fg becomes the maximum.

Here, acircle 45 indicated by a chain line in fig. 8 indicates a trajectory of thepassage 37 when theorbiting scroll 8 performs an orbiting motion. Thepassage 37 communicates with thecircumferential groove 36 via thegroove portion 39 only in a range ofθ 2, which is a range of approximately ± 90 degrees on the locus.

While thepassage 37 is always in communication with thecircumferential groove 36, a pressing force is always applied, according toembodiment 3, lubricating oil can be supplied to the most strongly pressed position only at the timing when thecover plate 8a of theorbiting scroll 8 is most strongly pressed against thecover plate surface 7e of the fixedscroll 7 during one revolution. Therefore, the lubricant oil can be efficiently supplied only to a desired portion at a desired timing, and therefore, the occurrence of the separation phenomenon and the heating loss can be further suppressed, and the orbiting motion of the orbiting scroll can be suppressed.

In example 3, thecircumferential groove 36 is formed to have a width smaller than the turning radius of theorbiting scroll 8 except for the arc-shapedgroove portion 39.

Example 4

Embodiment 4 of the scroll compressor according to the present invention will be described with reference to fig. 9. Fig. 9 is a plan view illustrating the orbiting scroll of embodiment 4. In fig. 9, the same or corresponding portions are denoted by the same reference numerals as in fig. 1 to 6, and the same portions as in example 1 are not described, and the portions different from example 1 will be mainly described.

In example 4, similar to example 1, acircumferential groove 36 is formed in the cover plate surface of the fixedscroll 7, acircular groove 36a is formed on one end side thereof, and apassage 37 for supplying the lubricant oil in the first space 33 (see fig. 1) to thecircumferential groove 36 is provided in thecover plate 8a of theorbiting scroll 8.

Further, in example 4, as shown in fig. 9, a slit (oil leakage means) 40 as means for leaking the lubricating oil supplied to thecircumferential groove 36 to thesuction chamber 20 or thecompression chamber 13 shown in fig. 2 is provided on thecover plate surface 8e of theorbiting scroll 8. Theslit 40 communicates thecircumferential groove 36 with thesuction chamber 20 or thecompression chamber 13 at all times or intermittently.

When theslits 40 are always in communication with each other, the positions and lengths of theslits 40 may be determined so that thecircumferential groove 36 and thesuction chamber 20 or thecompression chamber 13 are always in communication with each other even when theorbiting scroll 8 performs an orbiting motion. In the case of intermittent communication, the position and length of theslit 40 may be determined so that a part of theslit 40 intermittently communicates with thecircumferential groove 36 or a part of theslit 40 intermittently communicates with thesuction chamber 20 or thecompression chamber 13 in accordance with the orbiting motion of theorbiting scroll 8.

In addition, although one slit 40 is provided in the present embodiment, a plurality of slits may be provided. Instead of theslit 40, one or more oil pockets (oil leaking means) may be provided on thecover plate surface 8e of the orbiting scroll as oil leaking means, the oil pockets (oil leaking means) moving between thecircumferential groove 36 and thesuction chamber 20 or thecompression chamber 13, and the lubricating oil supplied into thecircumferential groove 36 may be intermittently transferred to thesuction chamber 20 or thecompression chamber 13.

The other structure is the same as inembodiment 1 described above.

According to the structure of embodiment 4, the oil supplied to thecircumferential groove 36 can be smoothly discharged to thesuction chamber 20 and thecompression chamber 13 through theslit 40 and the oil pocket. Thus, the following effects can be obtained: the oil supplied to thecircumferential groove 36 is suppressed from staying in thecircumferential groove 36, and can flow out to thesuction chamber 20 and thecompression chamber 13 before being heated to a high temperature by heat generation due to sliding of thecover plate surfaces 7e and 8 e. Further, new lubricating oil can be smoothly supplied from thepassage 37 to thecircumferential groove 36. Further, a part of the oil supplied to thecircumferential groove 36 lubricates a small gap between thecover plates 7e and 8e, and then flows out to thesuction chamber 20 and thecompression chamber 13.

In the present embodiment, since the flow rate of the lubricating oil can be controlled by the depth of theslit 40, the volume of the oil pocket, and the number of the oil pockets, an amount of oil that can ensure a good lubrication state of thelid surfaces 7e and 8e can be supplied to thecircumferential groove 36 while suppressing an increase in heating loss.

Example 5

Embodiment 5 of the scroll compressor according to the present invention will be described with reference to fig. 10. Fig. 10 is a bottom view illustrating the fixed scroll ofembodiment 5. In fig. 10, the same or corresponding portions are denoted by the same reference numerals as in fig. 1 to 6, and the same portions as in example 1 will be omitted from description, and the portions different from example 1 will be mainly described.

In example 5, as in example 4, oil leakage means for leaking the lubricating oil supplied to thecircumferential groove 36 to thesuction chamber 20 or thecompression chamber 13 is provided. In example 4, an example in which theslit 40 serving as oil leakage means is provided on thecover surface 8e of theorbiting scroll 8 has been described, but in example 5, theslit 41 serving as oil leakage means for leaking the lubricant oil supplied to thecircumferential groove 36 to thesuction chamber 20 or thecompression chamber 13 is provided on thecover surface 7e of the fixedscroll 7.

That is, as shown in fig. 10, in the present embodiment, acircumferential groove 36 is provided in acover plate surface 7e of the fixedscroll 7, and acircular groove portion 36a is provided on one end portion side of thecircumferential groove 36. Further, in the present embodiment, aslit 41 communicating with the side of thecircumferential groove 36 opposite to thegroove portion 36a is provided in thecover plate surface 7e of the fixedscroll 7. Theslit 41 is configured to communicate with thesuction chamber 20 or thecompression chamber 13.

The other structure is the same as inembodiment 1 described above. The number ofslits 41 is not limited to one, and a plurality of slits may be provided along thecircumferential groove 36.

Even if the oil leakage means is constituted by providing theslit 41 on thecover plate surface 7e of the fixedscroll 7 as in example 5, the oil supplied to thecircumferential groove 36 can be smoothly leaked to thesuction chamber 20 or thecompression chamber 13, and therefore the same effect as in example 4 described above can be obtained.

Example 6

Embodiment 6 of the scroll compressor according to the present invention will be described with reference to fig. 11. Fig. 11 is a longitudinal sectional view illustrating the orbiting scroll ofembodiment 6. In fig. 11, the same or corresponding portions are denoted by the same reference numerals as in fig. 1 to 6, and the same portions as in example 1 are not described, and the portions different from example 1 will be mainly described.

In the scroll compressor according to example 6, as in example 1 shown in fig. 1, apassage 37 for supplying the lubricant oil in thefirst space 33 to thecircumferential groove 36 is provided in thecover plate 8a of theorbiting scroll 8. In example 6, in addition to the structure of example 1, as shown in fig. 11, athrottle member 42 is provided so as to reduce the passage cross-sectional area of a part of thepassage 37.

By providing theorifice member 42 in thepassage 37, when the lubricating oil introduced from thefirst space 33 to thepassage 37 passes through a portion having a small passage cross-sectional area due to theorifice member 42, pressure loss occurs, and the pressure is reduced. Therefore, the pressure of the lubricating oil supplied to thecircumferential groove 36 is lower than the pressure of thefirst space 33, which is the discharge pressure.

Embodiment 6 can also be applied to a case where the force for depressing theorbiting scroll 8 is excessively large when the lubricant oil at the discharge pressure in thefirst space 33 is directly supplied to thecircumferential groove 36 via thepassage 37. That is, since the pressure of the lubricating oil supplied to thecircumferential groove 36 can be suppressed to be lower than the discharge pressure by providing theorifice member 42 in thepassage 37, it is possible to avoid an excessive force for depressing theorbiting scroll 8, and to press theorbiting scroll 8 against the fixed scroll with an appropriate pressing force.

The other structure is the same as inembodiment 1 described above.

Example 7

Embodiment 7 of the scroll compressor according to the present invention will be described with reference to fig. 12. Fig. 12 is a plan view illustrating the orbiting scroll ofembodiment 7. In fig. 12, the same or corresponding portions are denoted by the same reference numerals as in fig. 1 to 6, and the same portions as in example 1 are not described, and the portions different from example 1 will be mainly described.

Inembodiment 1 described above, thecircumferential groove 36 is provided on the cover plate surface of the fixedscroll 7, and the lubricant oil in thefirst space 33 is supplied to thecircumferential groove 36 through thepassage 37 provided in thecover plate 8a of theorbiting scroll 8.

In contrast, inembodiment 7, thecircumferential groove 36 is formed not on thecover surface 7e of the fixedscroll 7 but on thecover surface 8e of theorbiting scroll 8. Further, apassage 37 for guiding the lubricant oil in thefirst space 33 to thecircumferential groove 36 provided in theorbiting scroll 8 is provided in thecover plate 8a of theorbiting scroll 8 in the same manner as inembodiment 1. Further, thefirst space 33 side of thepassage 37 is opened inside theswirl projection 8d as in the embodiment, but thecircumferential groove 36 side of thepassage 37 directly communicates with thecircumferential groove 36.

When thecircumferential groove 36 is formed in thecover plate surface 8e of theorbiting scroll 8 as in the present embodiment, thecircumferential groove 36 moves in accordance with the orbiting motion of theorbiting scroll 8, and therefore the lubricating oil can be spread over a wider range of thecover plate surfaces 7e, 8e, and the lubrication state can be made better.

The other structure is the same as inembodiment 1 described above.

Example 8

Embodiment 8 of the scroll compressor according to the present invention will be described with reference to fig. 13. Fig. 13 is a bottom view illustrating the fixed scroll ofembodiment 8. In fig. 13, the same or corresponding portions are denoted by the same reference numerals as in fig. 1 to 6, and the same portions as in example 1 are not described, and portions different from example 1 will be mainly described.

Inembodiment 8, at least oneback pressure groove 43 communicating with the back pressure chamber (second space) 18 is provided in a region (thecover surface 7e in a region other than the region θ 1c in fig. 13) where thecircumferential groove 36 is provided on thecover surface 7e of the fixedscroll 7 where thecircumferential groove 36 is provided. As shown in fig. 13, theback pressure groove 43 is formed to extend in the circumferential direction in a region other than the region indicated by θ 1c where thecircumferential groove 36 is provided. Theback pressure chamber 18 is a pressure (intermediate pressure) between the discharge pressure and the suction pressure, and the lubricating oil in theback pressure chamber 18 can be guided to thecover plate surface 7e of the fixedscroll 7. Theback pressure groove 43 is not limited to one, and a plurality of grooves may be provided.

By forming the configuration of the present embodiment, thecircumferential groove 36 can provide an appropriate downward pressure to the position where thecover plate 8a of theorbiting scroll 8 most strongly abuts on thecover plate surface 7e of the fixedscroll 7, and the vicinity of the cover plate surface provided with thecircumferential groove 36 can be lubricated. Further, since theback pressure groove 43 is provided, the lubricating oil in theback pressure chamber 18 can be supplied to the area of the lid plate surface other than the portion where thecircumferential groove 36 is provided, and the lubrication state of the entire lid plate surface can be maintained well.

The other structure is the same as inembodiment 1 described above.

Example 9

Embodiment 9 of the present invention will be described with reference to fig. 14. Fig. 14 is a refrigeration cycle configuration diagram illustrating an example of an air conditioner using a scroll compressor of the present invention.

In fig. 14,reference numeral 1 denotes a scroll compressor, 60 denotes a four-way valve, 61 denotes an outdoor heat exchanger (a condenser during cooling operation and an evaporator during heating operation), 62 denotes an expansion valve formed of an electronic expansion valve or the like, 63 denotes an indoor heat exchanger (an evaporator during cooling operation and a condenser during heating operation), and these devices are connected in order by arefrigerant pipe 64 to constitute a refrigeration cycle of the air conditioner.

Thescroll compressor 1 is the scroll compressor according to any one ofembodiments 1 to 8. The operation efficiency of the air conditioner can be improved by assembling the scroll compressor according to each embodiment of the present invention having high efficiency and high reliability to the air conditioner shown in fig. 14. Therefore, the annual energy consumption efficiency of the air conditioner can be greatly improved, and the air conditioner with low annual power consumption and high reliability can be obtained.

As described above, according to the embodiments of the present invention, since thecircumferential groove 36 is provided at the position of the cover plate surface in the region where thecover plate 8a of theorbiting scroll 8 is strongly pressed against thecover plate surface 7e of the fixedscroll 7, it is possible to supply the lubricating oil to the region of the cover plate surface where the pressing force is significantly increased. Accordingly, oil can be effectively supplied to a portion where the pressing force is strong and lubrication is most required, the length of thecircumferential groove 36 can be further shortened, the occurrence of a separation phenomenon and a heating loss can be suppressed, and an increase in the pressing force can be suppressed, so that a scroll compressor with high efficiency and high reliability can be obtained. Further, by applying the scroll compressor to an air conditioner, an air conditioner with high efficiency and high reliability can be obtained.

The present invention is not limited to the above-described embodiments, and various modifications are possible. Further, a part of the structure of one embodiment may be replaced with the structure of another embodiment, or the structure of another embodiment may be added to the structure of one embodiment.

The above-described embodiments are examples described in detail to facilitate understanding of the present invention, and are not limited to having all the configurations described. Further, some of the structures of the embodiments may be added, deleted, or replaced with other structures.

Description of the symbols

1-scroll compressor, 2-compression mechanism section, 3-oil feed hole (through hole), 5-main bearing, 6-discharge pipe, 7-fixed scroll, 7 a-platen, 7 b-scroll, 7 c-tooth root, 7 d-support section, 7 e-deck, 8-orbiting scroll, 8 a-deck, 8 b-scroll, 8 c-tooth root, 8 d-boss (orbiting boss), 8 e-deck, 9-closed container (housing), 10-crankshaft (rotating shaft), 10 a-crank section, 11-orbiting bearing, 12-Oldham's ring, 13-compression chamber, 13 a-orbiting inner wire side compression chamber, 13 b-orbiting outer wire side compression chamber, 14-suction port, 15-discharge port, 16-motor section, 16 a-rotor, 16 b-stator, 17-frame, 18-back pressure chamber (second space), 20-suction chamber, 21-feed, 22-oil pump housing, 23-auxiliary bearing, 24-cross hole, 25-lubricating oil suction port, 26 a-oil discharge hole, 26 b-oil discharge pipe, 28-discharge port, 31-circular groove, 32-sealing member, 33-first space, 35-back pressure hole, 36-circumferential groove, 36 a-groove portion, 37-passage, 38-region, 39-groove portion, 40, 41-slit (oil leaking means), 42-throttle member, 43-back pressure groove, 45-circle, 46-curve, 47-position of crank angle at which load Fg is largest, 47A-position of cover plate surface at which pushing force is significantly larger than average value, 48-section, 50 a-pressure of inner line side compression chamber, 50 b-pressure of outer line side compression chamber, 52-motor chamber, 53-oil reservoir, 54-discharge space, 56-frame seal, 57-oil groove, 58-shallow groove, 60-four-way valve, 61-outer side heat exchanger, 62-expansion valve, 63-inner side heat exchanger, and 64, refrigerant piping.

Claims (13)

Translated fromChinese

1.一种涡旋压缩机，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，1. A scroll compressor comprising: a fixed scroll on which a vortex-shaped scroll is erected on a platen; An orbiting scroll that orbits to form a suction chamber or a compression chamber; a first space provided on the center side of the back of the orbiting scroll and having a pressure close to the discharge pressure; and a first space provided on the back of the orbiting scroll and the first space The outer peripheral side of the space has a second space that is an intermediate pressure between the discharge pressure and the suction pressure,上述涡旋压缩机的特征在于，具备：The above-mentioned scroll compressor is characterized in that it has: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a circumferential groove formed in at least one of a cover surface serving as a sliding surface of the fixed scroll and a cover surface serving as a sliding surface of the orbiting scroll and extending in the circumferential direction; and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，a passage, which is provided on the cover plate of the orbiting scroll and is used for supplying the lubricating oil in the first space to the circumferential groove,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，The circumferential groove is provided at a position near the crank angle at which the load acting on the orbiting scroll becomes the largest, and the cover plate of the orbiting scroll most strongly abuts on the cover plate surface of the fixed scroll, and,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。The length in the circumferential direction of the circumferential groove is a length in which both ends of the circumferential groove are disposed within a range of approximately ±90 degrees including the position where the circumferential groove is most strongly abutted.2.根据权利要求1所述的涡旋压缩机，其特征在于，2. The scroll compressor of claim 1, wherein上述周向槽设于固定涡盘的盖板面，The above-mentioned circumferential groove is arranged on the cover surface of the fixed scroll,在上述固定涡盘的盖板面设有连通于上述周向槽和上述通路的槽部。A groove portion communicating with the circumferential groove and the passage is provided on the cover surface of the fixed scroll.3.根据权利要求2所述的涡旋压缩机，其特征在于，3. The scroll compressor of claim 2, wherein连通于上述周向槽和上述通路的上述槽部为圆形的槽部，The groove portion communicating with the circumferential groove and the passage is a circular groove portion,上述圆形的槽部为在上述通路的在上述槽部开口的端部进行回旋运动的全范围内与上述通路的端部连通的形状。The said circular groove part is a shape which communicates with the end part of the said passage in the whole range of the swirling movement of the end part of the said passage which opens the said groove part.4.根据权利要求2所述的涡旋压缩机，其特征在于，4. The scroll compressor of claim 2, wherein连通于上述周向槽和上述通路的上述槽部构成为与上述通路间歇性地连通，The groove portion communicating with the circumferential groove and the passage is configured to intermittently communicate with the passage,上述槽部与上述通路连通的角度构成为包括上述载荷为最大的曲柄角的大致±90度以内。The angle at which the groove portion communicates with the passage is configured to be within approximately ±90 degrees including the crank angle at which the load becomes the largest.5.根据权利要求4所述的涡旋压缩机，其特征在于，5. The scroll compressor of claim 4, wherein连通于上述周向槽和上述通路的上述槽部为圆弧状的槽部，The groove portion communicating with the circumferential groove and the passage is an arc-shaped groove portion,上述圆弧状的槽部构成为，在回旋涡盘进行回旋运动时，仅在包括载荷成为最大的曲柄角的大致±90度的范围内与上述通路的端部连通。The arc-shaped groove portion is configured to communicate with the end portion of the passage only within a range of approximately ±90 degrees including the crank angle at which the load becomes the largest when the orbiting scroll orbits.6.根据权利要求1所述的涡旋压缩机，其特征在于，6. The scroll compressor of claim 1, wherein上述周向槽设于回旋涡盘的盖板面，The above-mentioned circumferential groove is arranged on the cover surface of the orbiting scroll,设于上述回旋涡盘的盖板的上述通路直接连通于上述周向槽。The passage provided in the cover plate of the orbiting scroll directly communicates with the circumferential groove.7.根据权利要求1所述的涡旋压缩机，其特征在于，7. The scroll compressor of claim 1, wherein将上述周向槽形成为，对于与作用于上述回旋涡盘的载荷为最大的曲柄角的位置而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，回旋涡盘的旋转前进的方向即曲柄角较大的一侧比回旋涡盘的旋转滞后的方向即曲柄角较小的一侧长。The circumferential groove is formed so that the cover plate of the orbiting scroll is most strongly abutted on the cover plate surface of the fixed scroll at the position where the crank angle of the load acting on the orbiting scroll becomes the largest. The direction in which the rotation of the orbiting scroll advances, that is, the side with the larger crank angle is longer than the direction in which the rotation of the orbiting scroll lags, that is, the side with the smaller crank angle.8.根据权利要求1所述的涡旋压缩机，其特征在于，8. The scroll compressor of claim 1, wherein在回旋涡盘的盖板面或固定涡盘的盖板面设有使供给到上述周向槽的润滑油向吸入室或压缩室漏出的油漏出单元。An oil leakage unit for leaking the lubricating oil supplied to the circumferential groove to the suction chamber or the compression chamber is provided on the cover surface of the orbiting scroll or the cover surface of the fixed scroll.9.根据权利要求8所述的涡旋压缩机，其特征在于，9. The scroll compressor of claim 8, wherein:上述油漏出单元是设于上述回旋涡盘的盖板面的狭缝或油兜。The said oil leakage means is a slit or an oil pocket provided in the cover surface of the said orbiting scroll.10.根据权利要求8所述的涡旋压缩机，其特征在于，10. The scroll compressor of claim 8, wherein:上述油漏出单元是以与上述周向槽连通的方式设于上述固定涡盘的盖板面的狭缝。The said oil leakage means is a slit provided in the cover surface of the said fixed scroll so that it may communicate with the said circumferential groove.11.根据权利要求1所述的涡旋压缩机，其特征在于，11. The scroll compressor of claim 1, wherein:在为了向上述周向槽供给润滑油而设于回旋涡盘的盖板的上述通路，设有用于使从上述第一空间引导来的润滑油的压力降低并供给上述周向槽的节流部件。In the passage provided in the cover plate of the orbiting scroll in order to supply the lubricating oil to the circumferential groove, a throttle member for reducing the pressure of the lubricating oil guided from the first space and supplying the circumferential groove is provided .12.根据权利要求1所述的涡旋压缩机，其特征在于，12. The scroll compressor of claim 1, wherein:在设有上述周向槽的盖板面的设有上述周向槽的范围以外的区域，设有与上述第二空间连通的至少一个背压槽。At least one back pressure groove that communicates with the second space is provided in a region other than the range in which the circumferential groove is provided on the cover surface on which the circumferential groove is provided.13.一种空调机，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而构成冷冻循环，上述空调机的特征在于，13. 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, wherein the air conditioner is characterized in that:上述涡旋压缩机采用了权利要求1～12中任一项所述的涡旋压缩机。The scroll compressor according to any one of claims 1 to 12 is used as the scroll compressor.

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