CN114026328B - Scroll compressor and air conditioner using the same - Google Patents

Abstract

The scroll compressor includes a fixed scroll, an orbiting scroll engaged with the fixed scroll to form a suction chamber or a compression chamber, a first space provided on the center side of the back surface of the orbiting scroll and having a pressure close to a discharge pressure, and a second space provided on the outer peripheral side of the first space and having an intermediate pressure. The present invention further includes: a circumferential groove formed in at least one of a cover plate surface of the fixed scroll, which is a sliding surface, and a cover plate surface of the orbiting scroll, which is a sliding surface, and extending in a circumferential direction; and a passage provided in the cover plate of the orbiting scroll for supplying the lubricant oil in the first space to the circumferential groove, wherein the circumferential groove is provided at a position where the cover plate of the orbiting scroll is most strongly abutted against the cover plate surface of the fixed scroll in the vicinity of a crank angle where a load acting on the orbiting scroll is maximum, and a length in a circumferential direction of the circumferential groove is within a range of approximately ±90 degrees including the position where the cover plate is most strongly abutted.

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 same.

Background

A scroll compressor for an air conditioner or the like is provided with a fixed scroll having a spiral wrap standing on a platen and an orbiting scroll having a spiral wrap standing on a cover plate, wherein the scrolls of the two scrolls are engaged with each other while facing inward. In addition, the orbiting scroll is configured to perform orbiting motion to sequentially reduce the volumes of a plurality of compression chambers formed between the two scrolls, thereby compressing the working gas.

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

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

However, this pressing force causes sliding friction between the platen of the fixed scroll and the sliding surface (cover plate surface) of the cover plate of the orbiting scroll, and when the pressing force is excessive, the sliding surface causes a burning phenomenon or the like, which deteriorates the reliability of the compressor.

Accordingly, the conventional scroll compressor has been modified as follows: the lubrication state of the sliding surface is improved by adopting a structure of supplying lubrication oil to the sliding surface (cover plate surface) of the fixed scroll and the orbiting scroll.

For example, in the scroll compressor described in japanese patent application laid-open No. 2008-2422 (patent document 1), a groove is provided in a cover plate surface of a orbiting scroll or a fixed scroll, a passage communicating with a first space (high pressure chamber) is provided in a cover plate of the orbiting scroll, and high-pressure lubricating oil in the first space is supplied to a sliding surface (cover plate surface) by communicating the groove with the passage. This structure provides lubrication oil to the sliding surfaces of the fixed scroll and orbiting scroll, thereby improving the lubrication state of the sliding surfaces.

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

Prior art literature

Patent literature

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

Patent document 2: japanese patent laid-open publication 2016-17484

Disclosure of Invention

Problems to be solved by the invention

The patent document 1 does not describe the position of the groove for introducing the high-pressure lubricating oil and the length of the groove. Therefore, when the groove is short, the effect of improving the lubrication state of the sliding surface (cover plate surface) is reduced, and the reliability of the compressor is lowered. On the other hand, if the groove is too long, the leakage amount of the lubricant oil from the groove to the suction chamber increases, and the heating loss caused by the lubricant oil heating the refrigerant gas increases. Further, since the pressing force increases, there is also a problem that the vortex plate is easily separated.

The above-mentioned patent document 2 uses an oil tank having a plurality of oil supply points, and uses an annular or C-shaped oil tank having a length of the tank exceeding half a turn, and the oil tank has a long shape, so that the leakage amount of the lubricating oil from the tank to the suction chamber increases, and the heating loss increases due to the heating of the refrigerant gas by the lubricating oil. Further, since the pressing force increases, there is also a problem that the vortex plate is easily separated.

The present invention provides a scroll compressor which can improve the lubricity of the sliding surface of a fixed scroll and an orbiting scroll while suppressing the increase of heating loss, and which is high in efficiency and reliability, and an air conditioner using the scroll compressor.

Solution for solving the problem

In order to achieve the above object, the present invention provides a scroll compressor comprising: a fixed scroll plate on which a spiral scroll is vertically arranged; a vortex scroll vertically arranged on the cover plate, meshed with the fixed scroll and performing a rotary motion to form a suction chamber or a compression chamber; a first space provided on the center side of the back surface of the swirl disk and having a pressure close to the discharge pressure; and a second space provided on the back surface of the orbiting scroll and on the outer peripheral side of the first space, and having an intermediate pressure which is a pressure between a discharge pressure and a suction pressure, wherein the scroll compressor includes: a circumferential groove formed in at least one of a cover plate surface of the fixed scroll, which is a sliding surface, and a cover plate surface of the orbiting scroll, which is a sliding surface, and extending in a circumferential direction; and a passage provided in the 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 the vicinity of a crank angle at which a load acting on the orbiting scroll is maximum, the cover plate of the orbiting scroll is most strongly abutted against the cover plate surface of the fixed scroll, and a length in a circumferential direction of the circumferential groove is a length in which both ends of the circumferential groove are arranged in 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 a refrigerant pipe to form a refrigeration cycle, wherein the scroll compressor is used as the scroll compressor.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the present invention, it is possible to obtain a scroll compressor that improves lubricity of a sliding surface between a fixed scroll and an orbiting scroll while suppressing an increase in heating loss, and that is highly efficient and highly reliable, and an air conditioner using the scroll compressor.

Drawings

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

Fig. 2 is a bottom view of the fixed scroll shown in fig. 1, showing the wrap of the orbiting scroll in section.

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

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

Fig. 5 is a graph illustrating the change in load versus crank angle for one revolution of the scroll compressor.

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

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

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

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

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

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

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

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

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

Detailed Description

Hereinafter, a specific embodiment of a scroll compressor and an air conditioner using the same 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 a scroll compressor according to 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 the scroll compressor according to embodiment 1, fig. 2 is a bottom view of the fixed scroll shown in fig. 1, and a cross section of the wrap of the orbiting scroll is shown.

The scroll compressor 1 is configured by housing the compression mechanism unit 2, the motor unit 16, and the like in a closed casing (housing) 9.

The compression mechanism 2 includes a frame 17, a fixed scroll 7 fixed to the frame 17, and a orbiting scroll 8 fixed between the frame 17 and the fixed scroll 7 and engaged with the fixed scroll 7 to form a compression chamber 13.

The fixed scroll 7 includes a disk-shaped platen 7a, a scroll 7b provided in a spiral manner to stand on the platen 7a, and a support portion 7d, and the support portion 7d is provided on the outer peripheral side of the platen 7a, has a cover surface 7e having substantially the same height as the tip surface of the scroll 7b, and is provided in a cylindrical shape so as to surround the scroll 7 b. The surface of the platen 7a on which the above-described scroll 7b is vertically provided is referred to as a tooth root 7c because it is located between the scrolls 7 b. The cover plate surface 7e of the support portion 7d of the fixed scroll 7 is a sliding surface that contacts the cover plate 8a of the orbiting scroll 8.

The fixed scroll 7 is fixed to the frame 17 by bolts or the like, and the frame 17 integrally coupled to the fixed scroll 7 is fixed to the sealed container 9 by a fixing method such as welding.

The orbiting scroll 8 is disposed to face the fixed scroll 7, and the scroll 7b of the fixed scroll 7 and the scroll 8b of the orbiting scroll 8 are engaged with each other and rotatably disposed in the frame 17. The orbiting scroll 8 includes a disk-shaped cover plate 8a, an orbiting scroll 8b erected from a tooth root 8c which is a surface of the cover plate 8a, and a boss (orbiting boss) 8d provided in the center of the rear surface of the cover plate 8 a. The surface of the outer peripheral portion of the cover plate 8a that contacts the fixed scroll 7 is a cover plate surface 8e of the orbiting scroll 8.

The tip end portion (tip end) of the scroll 8b of the orbiting scroll 8 is opposed to the root 7c of the fixed scroll 7 with a slight gap therebetween. Similarly, the tip portion (tip portion) of the fixed scroll 7b is also configured to face the root 8c of the orbiting scroll 8 with a slight gap therebetween.

The motor unit 16 is composed of a rotor 16a and a stator 16b, and a crankshaft (rotary shaft) 10 is integrally fixed to the rotor 16 a.

The orbiting scroll 8 is driven by the motor 16 through the crankshaft 10, and the orbiting scroll 8 performs an orbiting motion, thereby performing a compression operation in which the volume of the compression chamber 13 gradually decreases.

With this compression operation, the working fluid such as the refrigerant flowing in the refrigeration cycle is sucked into the suction chamber 20 from the suction port 14 (see fig. 2), and the sucked working fluid is discharged from the discharge port 15 to the discharge space 54 in the closed casing 9 through the compression stroke in the compression chamber 13. The working fluid discharged into the discharge space 54 flows into the motor chamber 52 through passages (not shown) formed in the outer periphery of the fixed scroll 7 and the outer periphery of the frame 17, and is discharged from the discharge pipe 6 to the outside of the sealed container 9.

The crankshaft 10 is rotatably supported by a main bearing 5 provided in the frame 17, and the center axis of the crankshaft 10 is coaxial with the center axis O1 of the fixed scroll 7. An eccentric crank portion 10a is provided at a front end portion (upper end portion) of the crankshaft 10, and the crank portion 10a is inserted into a swirl bearing 11 provided in a swirl boss portion 8d of the swirl disk 8. Thus, the orbiting scroll 8 is configured to perform orbiting motion by the eccentric motion of the crank part 10a when the crankshaft 10 rotates.

The center axis O2 of the orbiting scroll 8 is eccentric a predetermined distance from the center axis of the fixed scroll 7. The scroll 8b of the orbiting scroll 8 is overlapped with the scroll 7b of the fixed scroll 7 at a predetermined angle (typically 180 degrees) in the circumferential direction. Further, an euclidean ring 12 for causing the orbiting scroll 8 to orbit relative to the fixed scroll 7 while being restrained so as not to rotate is provided between the orbiting scroll 8 and the frame 17.

The engagement state of the fixed scroll 7 and the orbiting scroll 8 will be described with reference to fig. 2. In fig. 2, the scroll 8b of the orbiting scroll 8 is shown in a cross-sectional view, and a portion corresponding to the outer periphery of the cover plate 8a of the orbiting scroll 8 is shown in a phantom line drawing of a two-dot chain line. As shown in fig. 2, a plurality of crescent-shaped compression chambers 13 (a swirl inner-line side compression chamber 13a and a swirl outer-line side compression chamber 13 b) are formed between the scroll 7b of the fixed scroll 7 and the scroll 8b of the orbiting scroll 8, and when the orbiting scroll 8 is caused to perform a swirl motion, the volumes of the compression chambers 13 continuously decrease as they move toward the center.

Reference numeral 20 denotes a suction chamber, which is a space in the middle of sucking fluid. The suction chamber 20 becomes the compression chamber 13 from the time when the phase of the orbiting motion of the orbiting scroll 8 advances to complete the sealing of the fluid.

As shown in fig. 1 and 2, the suction port 14 is provided in the fixed scroll 7, and the suction port 14 is formed on the outer peripheral side of the platen 7a of the fixed scroll 7 so as to communicate with the suction chamber 20.

The discharge port 15 is provided near the center of the vortex of the platen 7a of the fixed scroll 7, and is configured to communicate with the discharge port 15 immediately when the compression chamber 13 on the innermost side is compressed.

When the crankshaft 10 is rotated by the motor unit 16 shown in fig. 1, the orbiting scroll 8 performs orbiting motion with an orbiting radius of a predetermined distance around the central axis of the fixed scroll 7. As a result, the working gas (for example, the refrigerant gas circulated in the refrigeration cycle) is sucked through the suction port 14, and the compressed working gas (hereinafter, referred to as compressed gas) is sequentially compressed in the compression chambers 13, and is discharged from the discharge port 15 to the discharge space 54. Thereafter, the compressed gas is supplied to, for example, the motor chamber 52, and is thereby supplied to a refrigeration cycle or the like outside the scroll compressor 1 via the discharge pipe 6.

Next, a flow of lubricating oil in the scroll compressor (hereinafter, simply referred to as a compressor) 1 shown in fig. 1 will be described. An oil reservoir 53 for storing lubricating oil (refrigerating machine oil) is provided at the bottom of the closed casing 9 accommodating the compression mechanism 2, the motor 16, and the like. A volumetric or centrifugal oil feed pump 21 is provided at the lower end of the crankshaft 10, and the oil feed pump 21 rotates in accordance with the rotation of the crankshaft 10, and sucks and feeds the lubricating oil stored in the oil reservoir 53 at the bottom of the closed casing 9 to an oil feed hole (through hole) 3 formed in the crankshaft 10 in the axial direction.

The lubricant in the oil reservoir 53 is sucked through the lubricant inlet 25 provided in the oil pump housing 22, and is discharged through the discharge port 28 of the oil pump 21. The discharged lubricating oil is fed to the upper end of the crankshaft 10 through the oil feed hole 3.

At this time, a part of the lubricating oil flowing through the oil feed hole 3 is sent to the sub-bearing 23 via the transverse hole 24 provided in the crankshaft 10, and after lubricating the sub-bearing 23, the lubricating oil returns to the oil reservoir 53 at the bottom of the closed casing 9. The lubricating oil flowing through the oil feed hole 3 reaches the space inside the swirl boss 8d at the upper end of the crank portion 10a of the crankshaft 10, and lubricates the swirl bearing 11 through the oil groove 57 provided in the outer peripheral surface of the Qu Bingbu a. After lubricating the main bearing 5 provided at the lower portion of the orbiting bearing 11, the lubricating oil returns to the oil reservoir 53 at the bottom of the closed casing 9 through the oil return passage formed by the oil drain hole 26a and the oil drain pipe 26 b.

The space inside the swirl boss 8d (the space in the upper end portion of the crank portion 10a, the space formed by the clearance between the swirl bearing 11 and the crankshaft 10, and the oil groove 57), the space located on the outer peripheral side of the swirl boss 8d (the space formed by the swirl boss 8d, the back surface of the cover plate 8a, the seal member 32, and the frame 17), and the space in which the main bearing 5 is housed (the space formed by the frame 17, the crankshaft 10, and the frame seal 56) are collectively referred to as a first space 33. The first space 33 is a space having a pressure close to the discharge pressure.

Most of the lubricating oil flowing into the first space 33 for lubricating the main bearing 5 and the orbiting bearing 11 is returned to the oil reservoir 53 at the bottom of the closed casing 9 through the return passage of the oil drain hole 26a and the oil drain pipe 26 b. A part of the lubricating oil flows into a back pressure chamber (second space) 18 via an oil drain means provided between an upper end surface of the seal member 32 and a rear surface of the cover plate 8a, and the back pressure chamber 18 is provided on an outer peripheral side of the first space 33 and is a pressure between a discharge pressure and a suction pressure (intermediate pressure, hereinafter also referred to as back pressure). The lubricating oil flowing into the back pressure chamber 18 is used for lubrication of the euclidean ring 12, lubrication of sliding portions between the cover surfaces 7e and 8e of the fixed scroll 7 and the orbiting scroll 8, sealing (sealing) of gaps between the scrolls 7b and 8b, and the like. Thus, the oil drain means is configured to allow the amount of lubricating oil necessary for lubrication and sealing to flow into the back pressure chamber 18.

The seal member 32 is provided with a wave spring (not shown) on an annular groove 31 provided on a surface of the frame 17 facing the rear surface of the cover plate 8 a. The seal member 32 separates the first space 33, which is the discharge pressure, from the back pressure chamber (second space) 18, which is the intermediate pressure between the suction pressure and the discharge pressure.

The oil drain unit is constituted by, for example, one or more slit-shaped shallow grooves 58 provided on the back surface of the cover plate 8a and the seal member 32. The shallow groove 58 is configured to intermittently communicate the first space 33 and the back pressure chamber 18 so as to be disposed across the seal member 32 by the orbiting motion of the orbiting scroll 8. According to this configuration, the lubricant oil can flow from the first space 33 into the back pressure chamber 18 via the shallow groove 58 as a minute gap by the pressure difference between the first space 33 and the back pressure chamber 18.

Instead of the shallow groove 58, one or more pockets (holes serving as oil storage portions, for example, circular grooves) may be provided on the back surface of the cover plate 8a, and the pockets may perform circular movement across the seal member 32 in accordance with the circular movement of the orbiting scroll 8. With this configuration, the oil pocket moves between the first space 33 and the back pressure chamber 18, and the lubricating oil in the first space 33 can be stored in the oil pocket and intermittently transferred to the back pressure chamber 18, so that the lubricating oil in the first space 33 can be supplied to the back pressure chamber 18.

The lubricant oil introduced into the back pressure chamber 18 lubricates the sliding portion of the euclidean ring 12, and a part thereof passes through the minute gap between the cover surfaces 7e and 8e of the fixed scroll 7 and the orbiting scroll 8 while being lubricated, and flows into the suction chamber 20 or the compression chamber 13. When the pressure (back pressure) of the back pressure chamber becomes high, the other lubricating oil flows into the compression chamber 13 through the back pressure hole 35 that communicates the back pressure chamber 18 and the compression chamber 13. The back pressure hole 35 is a hole for adjusting the pressure in the back pressure chamber 18.

The lubricant oil flowing into the suction chamber 20 and the compression chamber 13 is sealed and lubricated in the gap between the scroll 7b of the fixed scroll 7 and the scroll 8 of the orbiting scroll 8, and then discharged from the discharge port 15 to the discharge space 54. Part of the discharged oil is discharged from the discharge pipe 6 to the refrigeration cycle together with the refrigerant gas, and the remaining part is separated from the refrigerant gas in the sealed container 9 and stored in the oil storage portion 53 at the bottom of the sealed container 9.

As described above, by providing the first space 33, the back pressure chamber 18, and the oil drain means, the amount of oil supply required for each bearing portion and the amount of oil supply to the back pressure chamber 18 can be independently controlled, and therefore, a scroll compressor with high efficiency can be obtained.

Next, the function of the back pressure chamber 18 will be described. In the scroll compressor 1, an axial force (separation force) is generated to separate the fixed scroll 7 and the orbiting scroll 8 from each other due to the compression action thereof. When the separation phenomenon of the so-called orbiting scroll 8 separating the two scrolls occurs due to the axial force, the sealing performance of the compression chamber 13 is deteriorated, and the compressor efficiency is lowered.

Therefore, a back pressure chamber 18 is provided on the back surface side of the cover plate 8a of the orbiting scroll 8, which is a pressure between the discharge pressure and the suction pressure, and the separation force is canceled by the pressure (intermediate pressure) of the back pressure chamber 18 and the discharge pressure of the first space 33, and the orbiting scroll 8 is pressed against the fixed scroll 7.

At this time, if the pressing force is excessively large, the sliding loss between the cover plate surface 8e of the orbiting scroll 8 and the cover plate surface 7e of the fixed scroll 7 increases, the compressor efficiency decreases, and problems such as abrasion, seizure, or burning occur in the cover plate surfaces 7e and 8e, and the reliability of the compressor decreases. That is, the pressing force has an optimum value, and if the pressing force is too small, the sealing property of the compression chamber is deteriorated, and if the pressing force is too large, the sliding loss is increased. Therefore, maintaining the pressing force at the optimum value is important for the high performance and high reliability of the compressor.

The above is a basic configuration of the scroll compressor 1. Here, for example, the diameter of the swivel bearing 11 may be increased for the reason of improving the reliability of the swivel bearing 11. In this case, the diameter of the seal member 32 disposed outside thereof also increases, and the first space 33 having a pressure close to the discharge pressure increases. Therefore, the area of the discharge pressure acting on the back surface of the cover plate 8a of the orbiting scroll 8 is also enlarged, and the pressing force is increased. If the pressing force increases excessively, the sliding loss between the cover plate surface 7e and the cover plate surface 8e increases, and problems such as abrasion, seizure, or burning occur, which reduces the reliability of the compressor. In particular, under high pressure ratio conditions in which the scroll compressor 1 is operated at a high pressure ratio, the pressing force is excessively large, and seizure, burning, or the like occurs on the cover plate surface, which tends to reduce the reliability of the compressor.

Therefore, in the present embodiment, the following structure is adopted: at least one of the cover plate surface 7e of the fixed scroll 7, which is a sliding surface, and the cover plate surface 8e of the orbiting scroll 8, which is a sliding surface, is formed with a circumferential groove extending in the circumferential direction, and a passage for supplying the lubricating oil in the first space 33 to the circumferential groove is provided in the cover plate 8a of the orbiting scroll 8. The circumferential groove is provided in the vicinity of a crank angle at which a load acting on the orbiting scroll is maximum, and the cover plate of the orbiting scroll is most strongly abutted against the cover plate surface of the fixed scroll.

With this configuration, since the discharge pressure can be applied to the sliding surface between the cover surface 7e of the fixed scroll 7 and the cover surface 8e of the orbiting scroll 8, a force in the direction of separating the orbiting scroll 8 from the fixed scroll 7, that is, a pressing force can be applied. Therefore, the pressing force can be prevented from being excessively large.

In this embodiment, the length of the circumferential groove in the circumferential direction is set so that one end of the circumferential groove is disposed in a range of +70 to +100 degrees from the position where the circumferential groove is most strongly abutted, and the other end of the circumferential groove is disposed in a range of-70 to-100 degrees from the position where the circumferential groove is most strongly abutted. Accordingly, the leakage amount of the lubricant oil from the circumferential groove to the suction chamber 20 can be reduced, and the heating loss of the lubricant oil heating refrigerant gas can be reduced. Further, the above-described pressing force can be prevented from being excessively large, and the pressing force at the position where the cover plate 8a of the orbiting scroll 8 most strongly abuts against the cover plate surface 7e of the fixed scroll 7 can be ensured.

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 in a range of +20 to +100 degrees from the position where the circumferential groove is most strongly abutted, and the other end may be disposed in a range of-20 to-100 degrees from the position where the circumferential groove is most strongly abutted. For example, one end of the circumferential groove may be disposed in a range of +20 to +40 degrees from the position where the circumferential groove is most strongly abutted, and the other end may be disposed in a range of-20 to-40 degrees from the position where the circumferential groove is most strongly abutted.

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, in embodiment 1, a circumferential groove 36 is provided in the fixed scroll 7. As shown in fig. 1, a passage 37 having one end communicating with the first space 33 is provided in the cover plate 8a of the orbiting scroll 8. The passage 37 is used to supply lubricating oil (hereinafter also referred to as oil) in the first space 33 to the circumferential groove 36.

In order to receive the lubricating oil from the passage 37, a circular groove 36a is formed at one end or a part of the circumferential groove 36 as shown in fig. 2. The circular groove 36a is formed as a circle having a radius equal to or larger than the radius of revolution so as to communicate with the end of the passage 37 over the entire range of the opening of the groove 36a of the passage 37. A circle 45 shown by a chain line in fig. 2 indicates a locus of movement of the passage 37 with respect to the fixed scroll 7 when the orbiting scroll 8 moves in an orbiting manner.

Further, the portion of the circumferential groove 36 other than the groove 36a is formed to have a width smaller than the diameter of the groove 36a, and is formed to be longer than the diameter of the groove 36a in the circumferential direction. The groove 36a is not limited to a circular shape, and may be formed so as to communicate with the groove 36a over the entire range of the end of the passage 37 for the rotational movement, and may have other shapes such as an elliptical shape and a rectangular shape.

The passage 37 communicates with the circular groove 36a, and thus the lubricant in the first space 33 is supplied to the space of the circular groove 36a, and the lubricant is supplied from the circular groove 36a to the circumferential groove 36. By supplying the high-pressure oil to the circumferential groove 36, the pressure in the circumferential groove 36 is close to the discharge pressure as is the case with the pressure in the first space 33.

Here, the pressure distribution on the cover plate surface of the orbiting scroll 8 of the conventional scroll compressor will be described with reference to fig. 3, and the pressure distribution on the cover plate surface of the orbiting 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 the orbiting scroll 8 of the conventional scroll compressor, the pressure on the side facing the back pressure chamber 18 (the outer peripheral side of the cover plate) is the back pressure, and the pressure on the side facing the suction chamber 20 or the compression chamber 13 (see fig. 2) (the inner peripheral side of the cover plate, and the certain side of the wrap 8 b) is the suction pressure or the pressure in the compression chamber.

In contrast, in the scroll compressor 1 of the present embodiment, since the circumferential groove 36 is provided, oil having discharge pressure is introduced into the circumferential groove 36. Therefore, as shown by the pressure distribution on the orbiting scroll cover surface shown on the right side in fig. 4, the force of pressing down the orbiting scroll 8 by the oil introduced with the discharge pressure increases by an amount corresponding to the region 38 shown by oblique lines in fig. 4 on the side where the circumferential groove 36 is provided. Therefore, an increase in the pressing force at the position where the cover plate of the orbiting scroll 8 most strongly abuts against the cover plate surface of the fixed scroll can be suppressed.

In addition, since the lubricating oil flowing into the circumferential groove 36 passes through the minute gap between the cover plate surface 7e of the fixed scroll 7 and the cover plate surface 8e of the orbiting scroll 8 while lubricating, and flows into the back pressure chamber 18, the suction chamber 20, or the compression chamber 13, the lubricating state at the cover plate surfaces 7e, 8e is good, and the reliability can be improved.

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

Due to the compression action, the orbiting scroll 8 generates forces in the tangential direction and the radial direction in addition to the axial force during the operation of the scroll compressor 1. The resultant force of these forces in the direction perpendicular to the axial direction at a certain phase of the orbiting scroll is denoted by Fg in fig. 3 and 4. In addition, a force Fr that causes the orbiting disk 8 to orbit as a reaction force of Fg acts on the orbiting bearing 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 orbiting scroll 8 as indicated by arrow M. This moment M is a so-called tilting moment to tilt the orbiting scroll 8. Due to this tilting moment, the cover plate surface 8e of the orbiting scroll 8 is locally strongly pressed against the cover plate surface 7e of the fixed scroll 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.

In addition, the direction and magnitude of the overturning moment change as the direction and magnitude of Fg and Fr change with the swirling motion of the swirling disk 8. This is the cause of the so-called orbiting scroll's oscillating movement. The position where the cover surface 8e of the orbiting scroll 8 is locally strongly pressed and the size thereof also change in one rotation.

Fig. 5 is a graph illustrating a change in the load Fg with respect to the crank angle in one 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.

The curve 46 in fig. 5 shows an example of a change in the load Fg in one rotation, and Fg is maximum at a position 47 where the crank angle is approximately 180 degrees in the example of fig. 5. In fig. 5, the position 47 at which the load Fg is 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 in a specific scroll compressor, which is determined by the number of wraps of the scroll and the discharge start angle, and the pressure 50a of the inner-orbiting-line side compression chamber 13a and the pressure 50b of the outer-orbiting-line side compression chamber 13 b. In the example shown in fig. 6, the case of so-called asymmetric scroll in which the number of turns of the outer-orbiting-wire side compression chamber 13a and the outer-orbiting-wire side compression chamber 13b are different is shown, and the case of the operation condition in which the maximum value of the load Fg is the maximum pressure ratio is shown. Further, the timing at which the intake of the outside-rotation-side compression chamber 13b is completed is set to 0 degrees crank angle.

In addition, the crank angle is originally 0 to 360 degrees, but in the case of a scroll compressor, it is usual to complete suction to start discharge from one compression chamber by one rotation or more. In the case of the asymmetric scroll, the compression is started after the intake of the outer-line side compression chamber 13b is completed and the crank angle is advanced by approximately 180 degrees. Therefore, for convenience of explanation, the crank angle of the horizontal axis of fig. 6 is set to 0 degrees to 720 degrees.

As shown in fig. 6, when the crank angle is changed, the pressure in each compression chamber is also changed. As shown in fig. 2, the scroll compressor 1 has a plurality of compression chambers 13, and the pressure of each compression chamber 13 varies as shown in fig. 6. The pressure in each compression chamber 13 acts on the scroll 8b of the orbiting scroll 8. The resultant force is the load Fg (gas load) described above, which varies as shown by curve 46 in fig. 5.

In the example shown in fig. 5, fg is maximized at a crank angle of 180 degrees (in fig. 6, a position of 360 degrees+180 degrees=540 degrees corresponds to a position of 180 degrees at which discharge starts) at which discharge of the swirl inner-line side compression chamber 13a starts, and accordingly, the overturning moment is maximized.

The position where the cover plate of the orbiting scroll most strongly abuts against the cover plate surface of the fixed scroll at the above crank angle at which the load acting on the orbiting scroll is maximized will be described with reference to fig. 2 to 4. Fig. 2 is a view 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 maximum 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 the orbiting scroll 8 most strongly contacts the cover plate surface of the fixed scroll 7 is the right position of the cover plate surface.

This position corresponds approximately to the range indicated by the dashed line 44 in fig. 2. That is, by providing the circumferential groove 36 at this position, it is possible to supply high-pressure lubricating oil having a substantially discharge pressure to the position where the cover plate 8a of the orbiting scroll 8 is most strongly pressed against the cover plate surface 7e of the fixed scroll 7 in one revolution of the compressor. Accordingly, the cover plates 7e and 8e can be prevented from being worn, caught, burned, or the like, and the reliability of the compressor can be improved.

The circumferential groove 36 is located as described above.

Next, a preferred shape of the circumferential groove 36 will be described. If the circumferential groove has a shape, i.e., a circumferential length, exceeding a half turn, such as an annular shape or a C-shape, there is a possibility that the depressing force is excessively large, and a detachment phenomenon occurs in which the orbiting scroll 8 is separated from the fixed scroll 7. In addition, the amount of oil supplied to the circumferential groove 36 leaks into the suction chamber 20 and the compression chamber 13. That is, since the flow path area of the oil leakage is expressed as the product of the length of the circumferential groove 36 and the length of the minute gap between the cover plates 7e and 8e, the longer the circumferential groove is, the larger the amount of lubricating oil flows into the suction chamber 20 and the compression chamber 13, the larger the heating loss is due to heating of the refrigerant gas.

Therefore, in the present embodiment, the circumferential groove 36 is formed of a part of a substantially circular arc, and both ends thereof are in a shape within a range of approximately ±90 degrees (within a range of θ1 in fig. 2) including a position where the cover plate 8a of the orbiting scroll 8 is pressed most strongly when the load Fg shown in fig. 5 becomes maximum. Thus, the circumferential groove 36 can be disposed so as to effectively supply oil to the portion that has a high pressing force and requires lubrication at the most, and the length of the circumferential groove 36 can be made shorter. Accordingly, the occurrence of detachment and heating loss can be suppressed, the increase in the pressing force can be suppressed, and the problems such as abrasion, biting, or burning of the cover plates 7e and 8e can be prevented, thereby improving the reliability of the compressor.

The section 48 shown in fig. 5 shows a range of approximately ±90 degrees including the position 47 at which the load Fg is the maximum crank angle, and a range in which the value of the load Fg can be significantly larger than the average value can be covered by the section 48. Thus, the circumferential groove 36 is provided at a position corresponding to the cover surface 7e or 8e of the section 48. That is, the circumferential groove 36 is provided at a position of the cover plate surface 7e or 8e where the cover plate 8a of the orbiting scroll 8 is strongly pressed against the cover plate surface 7e of the fixed scroll 7. This makes it possible to supply lubricating oil to the area of the cover surface where the pressing force is significantly larger than the average value.

As described above, according to the present embodiment, since the circumferential groove 36 is provided at the position of the cover plate surface of the orbiting scroll 8 where the cover plate 8a is strongly pressed against the cover plate surface 7e of the fixed scroll 7, it is possible to supply the lubricating oil to the area of the cover plate surface where the pressing force is significantly larger than the average value. Therefore, since oil can be effectively supplied to the portion that is strong in the pressing force and most in need of lubrication, the length of the circumferential groove 36 can be further shortened, the occurrence of the detachment phenomenon and the heating loss can be suppressed, the increase in the pressing force can be suppressed, the occurrence of wear, seizure, burning, 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 of the present invention will be described with reference to fig. 5, and with reference to fig. 7. Fig. 7 is a view showing the scroll compressor according to embodiment 2, and corresponds to fig. 2. In fig. 7, the same reference numerals as those in fig. 1 to 6 denote the same or corresponding parts, and the parts identical to those in embodiment 1 will be omitted from the description, and the parts different from embodiment 1 will be mainly described.

As characteristics of the scroll compressor under the high pressure ratio operation condition, the inclination of the left side 46a (the side where the rotation of the orbiting scroll 8 is retarded, i.e., the crank angle is small, hereinafter referred to as the retarded side) and the right side 46b (the side where the rotation of the orbiting scroll 8 is advanced, i.e., the crank angle is large, hereinafter referred to as the advanced side) is generally gentle with respect to the position 47 where the load Fg is the largest crank angle in fig. 5. This is because, under the high pressure ratio operation condition in which compression is performed only by the volume reduction of the compression chamber 13 to be insufficient, after the start of discharge, the refrigerant gas flows back 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 having increased to the discharge pressure is gradually discharged to the discharge space 54 as the crank angle advances.

Therefore, as shown in fig. 5 and 7, in embodiment 2, the circumferential groove 36 is formed so that a portion corresponding to the section 48b is longer than a portion corresponding to the section 48 a. Specifically, as shown in fig. 7, the circumferential groove 36 is formed as follows: the side (advance angle side) θ1b on which the rotational advance direction of the orbiting scroll 8 is larger than the side (retard angle side) θ1a on which the rotational retard direction of the orbiting scroll 8 is smaller than the crank angle is longer than the side (retard angle side) θ1a on which the rotational retard direction of the orbiting scroll 8 is smaller than the position 47 (see fig. 5) on which the cover plate surface of the orbiting scroll is most strongly abutted against the cover plate surface of the fixed scroll, in which the pressing force is significantly larger than the average value, corresponding to the position 47 (see fig. 5) on which the load Fg acting on the orbiting scroll 8 is the largest crank angle.

With this configuration, when the length of the circumferential groove 36 is the same in a range where the value of the load Fg is significantly larger than the average value, the lubricating oil can be supplied more reliably to the region of the cover plate surface where the pressing force is significantly larger than the average value. In this way, according to embodiment 2, it is possible to further suppress the heating loss due to the lubricating oil supplied to the circumferential groove 36, and to cover a range in which the value of the load Fg is significantly larger than the average value.

Other structures are the same as those of embodiment 1 described above.

Example 3

Embodiment 3 of the scroll compressor of the present invention will be described with reference to fig. 5, and with reference to fig. 8. Fig. 8 is a view showing the scroll compressor according to embodiment 3, and corresponds to fig. 2. In fig. 8, the same reference numerals as those in fig. 1 to 6 denote the same or corresponding parts, and the parts similar to those in embodiment 1 will be omitted from the description, and the parts different from embodiment 1 will be mainly described.

In embodiment 1 shown in fig. 2, a circumferential groove 36 is provided in a cover plate surface 7e of the fixed scroll 7, and a circular groove portion 36a is provided at one end portion thereof. A passage 37 for supplying the lubricating oil in the first space 33 to the circumferential groove 36 is provided in the orbiting scroll 8, and an end of the passage 37 communicates with the circular groove 36a. The end of the passage 37 performs a swirling motion with a swirling radius of the swirling disc 8. Therefore, the circular groove 36a is formed as a circle having a radius equal to or larger than the turning radius so as to communicate with the entire range of the turning motion at the end of the passage 37. In addition, the portions of the circumferential groove 36 other than the groove portion 36a are formed to have a smaller width than the diameter of the groove portion 36a.

In contrast, in embodiment 3, the section where the passage 37 provided in the orbiting scroll 8 communicates with the circumferential groove 36 is formed only within a range of approximately ±90 degrees including the crank angle at which the load Fg is maximum. The communicated section corresponds to the section 48 shown in fig. 5. That is, in the configuration of the embodiment 1, the lubricating oil is always supplied from the passage 37 to the circumferential groove 36, whereas in the present embodiment 3, the lubricating oil is intermittently supplied to the circumferential groove 36 only at a timing when the value of the load Fg is significantly larger than the average value.

A specific structure for realizing the above-described situation is described with reference to fig. 8. The circular arc-shaped groove portion 39 is formed at one end portion of the circumferential groove 36 so that the passage 37 performing the swirling motion intermittently communicates only at a timing when the value of the load Fg is significantly larger than the average value. The arcuate groove 39 is configured to communicate with the end of the passage 37 only within a range of approximately ±90 degrees including the crank angle at which the load Fg is maximum when the orbiting scroll 8 performs the orbiting motion. The arc-shaped groove 39 is preferably formed as an arc having a radius equal to the radius of revolution of the orbiting scroll 8 at the groove center, but the groove 39 may be formed so that the end of the passage 37 communicates with the groove 39 only within a range including approximately ±90 degrees of the crank angle at which Fg is maximum, and the shape of the groove 39 is not limited to the arc-shaped groove, but may be circular, rectangular, or the like.

Here, a circle 45 indicated by a chain line in fig. 8 indicates the locus of the passage 37 when the orbiting scroll 8 performs the orbiting motion. The passage 37 communicates with the circumferential groove 36 via the groove 39 only within a range of approximately ±90 degrees, that is, within a range of θ2 in the locus.

In contrast to this, according to embodiment 3, when the passage 37 is always in communication with the circumferential groove 36, the pressure is always applied, and the lubricating oil can be supplied to the position where the cover plate 8a of the orbiting scroll 8 is pressed most strongly against the cover plate surface 7e of the fixed scroll 7 only at the timing when the cover plate is pressed most strongly in one revolution. Accordingly, since the lubricant can be efficiently supplied only to the desired portion at only the desired timing, occurrence of the detachment phenomenon and heating loss can be further suppressed, and the oscillating motion of the orbiting scroll can be suppressed.

In embodiment 3, the circumferential groove 36 is formed to have a width smaller than the radius of revolution of the orbiting scroll 8 except for the arcuate groove portion 39.

Example 4

Embodiment 4 of the scroll compressor of the present invention will be described with reference to fig. 9. Fig. 9 is a plan view illustrating the swirling disc of this example 4. In fig. 9, the same reference numerals as those in fig. 1 to 6 denote the same or corresponding parts, and the parts identical to those in embodiment 1 will be omitted from the description, and the parts different from embodiment 1 will be mainly described.

In this embodiment 4, the same point as in embodiment 1 is that a circumferential groove 36 is formed in the cover plate surface of the fixed scroll 7, a circular groove portion 36a is formed on one end side thereof, and a passage 37 for supplying the lubricating oil in the first space 33 (see fig. 1) to the circumferential groove 36 is provided in the cover plate 8a of the orbiting scroll 8.

Further, in this embodiment 4, as shown in fig. 9, a slit (oil leakage means) 40 as a means for leaking the lubricating oil supplied to the circumferential groove 36 to the suction chamber 20 or the compression chamber 13 shown in fig. 2 is provided on the cover plate surface 8e of the orbiting scroll 8. The slit 40 communicates the circumferential groove 36 with the suction chamber 20 or the compression chamber 13 all the time or intermittently.

In the case of the constant communication, the position and length of the slit 40 may be determined so that the slit 40 always communicates the circumferential groove 36 with the suction chamber 20 or the compression chamber 13 even when the orbiting scroll 8 performs the orbiting motion. In the case of intermittent communication, the position and length of the slit 40 may be determined so that a part of the slit 40 intermittently communicates with the circumferential groove 36 or a part of the slit 40 intermittently communicates with the suction chamber 20 or the compression chamber 13 in accordance with the swirling motion of the swirling disc 8.

In addition, one slit 40 described above is provided in the present embodiment, but a plurality may be provided. Further, instead of the slit 40, one or more oil pockets may be provided on the cover plate surface 8e of the orbiting scroll, and the oil pockets (oil leakage means) may be moved between the circumferential groove 36 and the suction chamber 20 or the compression chamber 13, so that the lubricating oil supplied into the circumferential groove 36 may be intermittently transferred to the suction chamber 20 or the compression chamber 13.

Other structures are the same as those of embodiment 1 described above.

According to the structure of embodiment 4, the oil supplied to the circumferential groove 36 can be smoothly discharged to the suction chamber 20 and the compression chamber 13 via the slit 40 and the oil pocket. Thus, the following effects can be obtained: the oil supplied to the circumferential groove 36 is prevented from stagnating in the circumferential groove 36, and can flow out to the suction chamber 20 and the compression chamber 13 before being heated to a high temperature by heat generated by sliding of the cover plate surfaces 7e and 8 e. Further, new lubricating oil can be smoothly supplied from the passage 37 to the circumferential groove 36. Further, a part of the oil supplied to the circumferential groove 36 lubricates the minute gap between the cover surfaces 7e and 8e, and then flows out to the suction chamber 20 and the compression chamber 13.

In this embodiment, since the flow rate of the lubricating oil can be controlled by the depth of the slit 40, the volume of the oil pocket, and the number of oil pockets, the increase in heating loss can be suppressed, and the amount of oil that can ensure a good lubrication state of the cover surfaces 7e and 8e can be supplied to the circumferential groove 36.

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 of the present embodiment 5. In fig. 10, the same reference numerals as those in fig. 1 to 6 denote the same or corresponding parts, and the parts identical to those in embodiment 1 will be omitted from the description, mainly the parts different from those in embodiment 1.

In this embodiment 5, oil leakage means for leaking the lubricating oil supplied to the circumferential groove 36 to the suction chamber 20 or the compression chamber 13 is provided in the same manner as in the above embodiment 4. In the above-described embodiment 4, the case where the slit 40 as the oil leakage means is provided in the cover plate surface 8e of the orbiting scroll 8 has been described, but in the present embodiment 5, the slit 41 as the oil leakage means for leaking the lubricating oil supplied to the above-described circumferential groove 36 to the suction chamber 20 or the compression chamber 13 is provided in the cover plate surface 7e of the fixed scroll 7.

That is, as shown in fig. 10, in the present embodiment, a circumferential groove 36 is provided in the cover plate surface 7e of the fixed scroll 7, and a circular groove portion 36a is provided on one end side of the circumferential groove 36. Further, in the present embodiment, a slit 41 communicating with the side of the circumferential groove 36 opposite to the groove portion 36a is provided in the cover surface 7e of the fixed scroll 7. The slit 41 is also connected to the suction chamber 20 or the compression chamber 13.

Other structures are the same as those of embodiment 1 described above. The slit 41 is not limited to one slit, and may be provided in plural along the circumferential groove 36.

Even if the slit 41 as the oil leakage means is provided in the cover surface 7e of the fixed scroll 7 as in embodiment 5, the oil supplied to the circumferential groove 36 can be smoothly leaked to the suction chamber 20 or the compression chamber 13, and therefore the same effects as in embodiment 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 swirling disc of this example 6. In fig. 11, the same reference numerals as those in fig. 1 to 6 denote the same or corresponding parts, and the parts identical to those in embodiment 1 will be omitted from the description, and the parts different from embodiment 1 will be mainly described.

In the scroll compressor of embodiment 6, as in embodiment 1 shown in fig. 1, a passage 37 for supplying the lubricating oil in the first space 33 to the circumferential groove 36 is provided in the cover plate 8a of the orbiting scroll 8. In example 6, in addition to the structure of example 1, as shown in fig. 11, a throttle member 42 is provided so as to reduce the passage cross-sectional area of a part of the passage 37.

By providing the throttle member 42 in the passage 37, when the lubricating oil guided from the first space 33 to the passage 37 passes through a portion having a small passage cross-sectional area due to the throttle member 42, a pressure loss occurs, and the pressure decreases. Therefore, the pressure of the lubricating oil supplied to the circumferential groove 36 is a pressure lower than the pressure of the first space 33 as the discharge pressure.

When the lubricant oil at the discharge pressure in the first space 33 is directly supplied to the circumferential groove 36 via the passage 37, the present embodiment 6 can be applied even when the force for pressing down the orbiting scroll 8 is excessive. That is, by providing the throttle member 42 in the passage 37, the pressure of the lubricating oil supplied to the circumferential groove 36 can be suppressed to be lower than the discharge pressure, and thus, the excessive force of pressing down the orbiting scroll 8 can be avoided, and the orbiting scroll 8 can be pressed against the fixed scroll with an appropriate pressing force.

Other structures are the same as those of embodiment 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 swirling disc of this example 7. In fig. 12, the same reference numerals as those in fig. 1 to 6 denote the same or corresponding parts, and the parts identical to those in embodiment 1 will be omitted from the description, mainly the parts different from those in embodiment 1.

In embodiment 1 described above, the circumferential groove 36 is provided on the cover plate surface of the fixed scroll 7, and the lubricating oil in the first space 33 is supplied to the circumferential groove 36 through the passage 37 provided in the cover plate 8a of the orbiting scroll 8.

In contrast, in embodiment 7, the circumferential groove 36 is formed not in the cover plate surface 7e of the fixed scroll 7 but in the cover plate surface 8e of the orbiting scroll 8. The passage 37 for guiding the lubricant oil in the first space 33 to the circumferential groove 36 provided in the orbiting scroll 8 is provided in the cover plate 8a of the orbiting scroll 8 in the same manner as in the embodiment 1. The first space 33 side of the passage 37 is opened inside the swirl boss portion 8d as in the embodiment, but the circumferential groove 36 side of the passage 37 is directly communicated with the circumferential groove 36.

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

Other structures are the same as those of embodiment 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 of embodiment 8. In fig. 13, the same reference numerals as those in fig. 1 to 6 denote the same or corresponding parts, and the parts identical to those in embodiment 1 will be omitted from the description, and the parts different from embodiment 1 will be mainly described.

In embodiment 8, at least one back pressure groove 43 communicating with the back pressure chamber (second space) 18 is provided in a region (cover plate surface 7e of a region other than θ1c in fig. 13) other than the region where the circumferential groove 36 is provided on the cover plate surface 7e of the fixed scroll 7 where the circumferential groove 36 is provided. As shown in fig. 13, the back pressure groove 43 is formed to extend in the circumferential direction in a region other than the region indicated by θ1c in which the circumferential groove 36 is provided. The back pressure chamber 18 is a pressure (intermediate pressure) between the discharge pressure and the suction pressure, and the lubricating oil in the back pressure chamber 18 can be guided to the cover surface 7e of the fixed scroll 7. The back pressure groove 43 is not limited to one, and may be provided in plural.

By the configuration of this embodiment, the above-described circumferential groove 36 is given an appropriate downward pressure to the position where the cover plate 8a of the orbiting scroll 8 is most strongly abutted against the cover plate surface 7e of the fixed scroll 7, and lubrication in the vicinity of the cover plate surface where the circumferential groove 36 is provided can be performed. Further, since the back pressure groove 43 is provided, the lubricating oil in the back pressure chamber 18 can be supplied to the region of the cover plate surface other than the portion where the circumferential groove 36 is provided, and the lubricating state of the entire cover plate surface can be maintained well.

Other structures are the same as those of embodiment 1 described above.

Example 9

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

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

The scroll compressor 1 described above is used in any one of the above embodiments 1 to 8. The scroll compressor according to each embodiment of the present invention, which is assembled in the air conditioner shown in fig. 14, is highly efficient and reliable, and thus the operation efficiency of the air conditioner can be improved. Accordingly, the annual energy consumption efficiency of the air conditioner can be greatly improved, and an air conditioner with low annual power consumption and high reliability can be obtained.

As described above, according to the embodiments of the present invention, the circumferential groove 36 is provided at the position of the cover plate surface of the cover plate 8a of the orbiting scroll 8 that is strongly pressed against the area of the cover plate surface 7e of the fixed scroll 7, so that lubricating oil can be supplied to the area of the cover plate surface where the pressing force is significantly increased. Accordingly, oil can be effectively supplied to the portion that is strong in pressing force and most in need of lubrication, the length of the circumferential groove 36 can be further shortened, occurrence of a detachment phenomenon and a heating loss can be suppressed, and an increase in pressing force can be suppressed, so that a highly efficient and highly reliable scroll compressor can be obtained. In addition, 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 includes various modifications. In addition, 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 of the present invention described in detail for easy understanding, and are not limited to the configuration in which all the descriptions are necessarily provided. In addition, a part of the structure of each embodiment may be added, removed, or replaced with another structure.

Symbol description

1-scroll compressor, 2-compression mechanism part, 3-oil feed hole (through hole), 5-main bearing, 6-discharge pipe, 7-fixed scroll, 7A-platen, 7 b-scroll, 7 c-tooth root, 7 d-support part, 7 e-cover plate, 8-orbiting scroll, 8 a-cover plate, 8 b-scroll, 8 c-tooth root, 8 d-boss (orbiting boss), 8 e-cover plate surface, 9-closed vessel (housing), 10-crankshaft (rotation axis), 10 a-crank part, 11-orbiting bearing, 12-Euclidean ring, 13-compression chamber, 13 a-orbiting inner line side compression chamber, 13 b-orbiting outer line side compression chamber, 14-suction inlet, 15-discharge outlet, 16-motor part, 16 a-rotor, 16 b-stator, 17-frame, 18-back pressure chamber (second space), 20-suction chamber, 21-oil feed pump, 22-oil feed pump housing, 23-auxiliary bearing, 24-transverse hole, 25-lubricant suction port, 26 a-oil discharge hole, 26 b-oil discharge pipe, 28-discharge port, 31-annular groove, 32-seal 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 drain unit), 42-throttle member, 43-back pressure groove, 45-circle, 46-curve, 47-position of maximum crank angle of load Fg, 47A-position of cover plate surface where pressing force is significantly increased than average value, 48-region, 50 a-pressure of inner line side compression chamber, 50 b-pressure of outer line side compression chamber, 52-motor chamber, 53-oil storage portion, 54-discharge space, 56-frame seal, 57-oil groove, 58-shallow groove, 60-four-way valve, 61-outdoor side heat exchanger, 62-expansion valve, 63-indoor heat exchanger, 64-refrigerant piping.

Claims (14)

1. A scroll compressor is provided with: a fixed scroll plate on which a spiral scroll is vertically arranged; a vortex scroll vertically arranged on the cover plate, meshed with the fixed scroll and performing a rotary motion to form a suction chamber or a compression chamber; a first space provided on the center side of the back surface of the swirl disk and having a pressure close to the discharge pressure; and a second space provided on the back surface of the orbiting scroll and on the outer peripheral side of the first space, and having an intermediate pressure between the discharge pressure and the suction pressure,

the scroll compressor is characterized by comprising:

a circumferential groove formed in at least one of a cover plate surface of the fixed scroll, which is a sliding surface, and a cover plate surface of the orbiting scroll, which is a sliding surface, and extending in a circumferential direction; and

a passage provided in a cover plate of the orbiting scroll for supplying the lubricant oil in the first space to the circumferential groove,

the circumferential groove is provided in the vicinity of a crank angle at which a load acting on the orbiting scroll is maximum, and the cover plate of the orbiting scroll is most strongly abutted against the cover plate surface of the fixed scroll,

The length of the circumferential groove in the circumferential direction 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 most strongly abuts,

at least one back pressure groove communicating with the second space is provided in a region outside the range where the circumferential groove is provided on the cover plate surface where the circumferential groove is provided.

2. The scroll compressor of claim 1, wherein,

the circumferential groove is arranged on the cover plate surface of the fixed scroll,

the cover plate surface of the fixed scroll is provided with a groove part communicated with the circumferential groove and the passage.

3. The scroll compressor of claim 2, wherein,

the groove part communicated with the circumferential groove and the passage is a circular groove part,

the circular groove portion is formed to communicate with an end portion of the passage over a full range of a rotational movement of the end portion of the passage that is open to the groove portion.

4. The scroll compressor of claim 2, wherein,

the groove portion communicating with the circumferential groove and the passage is configured to intermittently communicate with the passage,

the angle at which the groove communicates with the passage is set to be within approximately + -90 degrees including the crank angle at which the load is maximum.

5. The scroll compressor of claim 4, wherein,

the groove part communicated with the circumferential groove and the passage is an arc-shaped groove part,

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 a crank angle at which a load becomes maximum when the orbiting scroll performs orbiting motion.

6. The scroll compressor of claim 1, wherein,

the circumferential groove is arranged on the cover plate surface of the vortex disc,

the passage provided in the cover plate of the orbiting scroll is directly connected to the circumferential groove.

7. The scroll compressor of claim 1, wherein,

the circumferential groove is formed so that a cover plate of the orbiting scroll is most strongly abutted against a cover plate surface of the fixed scroll in a position corresponding to a position of a crank angle at which a load acting on the orbiting scroll is maximum, and a side of the orbiting scroll in which a rotation advancing direction, that is, a crank angle is larger is longer than a side of the orbiting scroll in which a rotation retarding direction, that is, a crank angle is smaller.

8. The scroll compressor of claim 1, wherein,

an oil leakage means for leaking the lubricating oil supplied to the circumferential groove to the suction chamber or the compression chamber is provided on the cover plate surface of the orbiting scroll or the cover plate surface of the fixed scroll.

9. The scroll compressor of claim 8, wherein,

the oil leakage means is a slit or an oil pocket provided on the cover surface of the orbiting scroll.

10. The scroll compressor of claim 8, wherein,

the oil leakage means is a slit provided on the cover surface of the fixed scroll so as to communicate with the circumferential groove.

11. The scroll compressor of claim 1, wherein,

the throttle member for reducing the pressure of the lubricating oil guided from the first space and supplying the lubricating oil to the circumferential groove is provided in the passage provided in the cover plate of the orbiting scroll for supplying the lubricating oil to the circumferential groove.

12. 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 piping to form a refrigeration cycle, characterized in that,

the scroll compressor according to claim 1 is used as the scroll compressor.

13. A scroll compressor is provided with: a fixed scroll plate on which a spiral scroll is vertically arranged; a vortex scroll vertically arranged on the cover plate, meshed with the fixed scroll and performing a rotary motion to form a suction chamber or a compression chamber; a first space provided on the center side of the back surface of the swirl disk and having a pressure close to the discharge pressure; and a second space provided on the back surface of the orbiting scroll and on the outer peripheral side of the first space, and having an intermediate pressure between the discharge pressure and the suction pressure,

The scroll compressor is characterized by comprising:

a circumferential groove formed in at least one of a cover plate surface of the fixed scroll, which is a sliding surface, and a cover plate surface of the orbiting scroll, which is a sliding surface, and extending in a circumferential direction; 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, wherein a section in which the passage communicates with the circumferential groove is only within a range of approximately ±90 degrees including a crank angle at which a load of the orbiting scroll is maximum,

the circumferential groove is provided at a position where a cover plate of the orbiting scroll is most strongly abutted against a cover plate surface of the fixed scroll in the vicinity of a crank angle at which a load acting on the orbiting scroll is maximum,

the length in the circumferential direction of the circumferential groove is set to be only 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 most strongly abuts.

14. 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 piping to form a refrigeration cycle, characterized in that,

the scroll compressor according to claim 13 is used.