Compressors and refrigeration equipment

Abstract

To propose a compressor capable of suppressing deterioration in slidability of a bush.SOLUTION: A compressor (CMP) comprises a back pressure space (55, 75) provided in a cylinder (50, 70). The back pressure space (55, 75) has a radially inner end part connected to a radially outer end part of a blade space (52, 72), and communicates with a cylinder chamber (150, 170) and the blade space, where a blade (51b, 71b) moves forward and backward. While an opening of the back pressure space (55, 75) on a first end plate (40) side is sealed by the first end plate (40), an opening of the back pressure space (55, 75) on a second end plate (80) side is sealed by the second end plate (80).SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present disclosure relates to a compressor and a refrigeration device including the compressor. [Background technology]

[0002] 2. Description of the Related Art Conventionally, there has been a compressor that includes a sealed container and a cylinder that is housed in the sealed container and has a blade space and a back pressure space (see, for example, Japanese Patent Application Laid-Open No. 2008-45415 (Patent Document 1)).

[0003] The back pressure space communicates with a cylinder chamber defined by the inner circumferential surface of the cylinder via a blade space. A pair of bushes are disposed in the blade space, and a blade extending from the cylinder chamber through the blade space to the back pressure space is sandwiched between the pair of bushes. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2008-45415 A Summary of the Invention [Problem to be solved by the invention]

[0005] In the compressor, oil accumulates in the lower space within the sealed container. When a through hole communicating with the back pressure space is provided in the lower end plate of the cylinder and an oil supply pipe extending from the end plate to the lower space within the sealed container is connected to the through hole, the oil accumulated in the lower space within the sealed container flows into the back pressure space via the oil supply pipe, and the oil flowing into the back pressure space is supplied to the bushing.

[0006] Therefore, when a compressor having the oil supply pipe is enlarged, depending on the operating conditions, the supply of oil to the bushing may be insufficient, possibly reducing the sliding properties of the bushing.

[0007] An object of the present disclosure is to propose a compressor that can suppress a decrease in the sliding performance of the bush. [Means for solving the problem]

[0008] The compressor according to the first aspect of the present disclosure includes: A cylinder; A first end plate disposed on one side of the cylinder in the axial direction; A second end plate disposed on the other axial side of the cylinder; a cylinder chamber defined by an inner circumferential surface of the cylinder; a piston housed in the cylinder chamber and adapted to oscillate along an inner circumferential surface of the cylinder; a blade which, together with the piston, divides the cylinder chamber into a high pressure region and a low pressure region; a blade space provided in the cylinder, the blade space having a radially inner end connected to the cylinder chamber and communicating with the cylinder chamber, the blade moving forward and backward; a back pressure space provided in the cylinder, the radially inner end being connected to the radially outer end of the blade space and communicating with the cylinder chamber and the blade space, through which the blade advances and retreats; a first bush and a second bush disposed in the blade space and sandwiching the blade; Equipped with An opening of the back pressure space on the first end plate side is sealed by the first end plate, while an opening of the back pressure space on the second end plate side is sealed by the second end plate.

[0009] According to the above configuration, the opening of the back pressure space on the first end plate side is sealed by the first end plate, while the opening of the back pressure space on the second end plate side is sealed by the second end plate. This makes it possible to make the pressure in the back pressure space lower than the pressure inside the sealed container (discharge pressure), thereby suppressing a decrease in the sliding properties of the bush.

[0010] The compressor according to the second aspect of the present disclosure is In the compressor according to the first aspect, a high pressure side region of the cylinder chamber communicates with a region of the blade space on the first bush side, while a low pressure side region of the cylinder chamber communicates with a region of the blade space on the second bush side, The second bush has a peripheral surface on the opposite side to the blade, the peripheral surface being provided with a groove extending in the circumferential direction.

[0011] According to the above configuration, the second bush has a groove extending in the circumferential direction on its peripheral surface opposite to the blade, which facilitates the flow of oil from the back pressure space to the low pressure area, thereby suppressing the increase in pressure in the back pressure space.

[0012] A compressor according to a third aspect of the present disclosure includes: In the compressor according to the first or second aspect, a casing that accommodates the cylinder, the first end plate, and the second end plate; an oil reservoir provided within the casing in which oil is stored; a rotating shaft that is inserted through the cylinder, the first end plate, and the second end plate and has a first oil passage that communicates with the oil reservoir; Equipped with The oil in the oil reservoir is supplied to the first and second bushings through the first oil passage.

[0013] According to the above configuration, since oil in the oil reservoir is supplied to the first and second bushes via the first oil passage, it is possible to reliably supply oil to the first and second bushes.

[0014] A compressor according to a fourth aspect of the present disclosure includes: In the compressor according to the third aspect, the cylinder includes a first cylinder closer to the first end plate than the second end plate, and a second cylinder closer to the second end plate than the first end plate; An intermediate plate disposed between the first cylinder and the second cylinder is provided with a second oil passage that guides oil from the first oil passage to the first and second bushings.

[0015] According to the above configuration, a second oil passage is provided in the intermediate plate disposed between the first cylinder and the second cylinder to guide oil from the first oil passage to the first and second bushings, thereby preventing the structure from becoming complicated.

[0016] A compressor according to a fifth aspect of the present disclosure includes: In the compressor according to the first aspect, a casing that accommodates the cylinder, the first end plate, and the second end plate; an oil reservoir provided within the casing for storing oil; Equipped with a high pressure side region of the cylinder chamber communicates with a region of the blade space on the first bush side, while a low pressure side region of the cylinder chamber communicates with a region of the blade space on the second bush side, the first bushing has a first opposing surface opposing the blade, The first opposing surface is provided with a first oil groove that extends from the second end plate side toward the first end plate side and to which oil from the oil reservoir is supplied.

[0017] According to the above configuration, in the first opposing surface of the first bushing, the first oil groove extends from the second end plate side toward the first end plate side, so that oil easily spreads along the extending direction of the first oil groove.

[0018] A compressor according to a sixth aspect of the present disclosure includes: In the compressor according to the fifth aspect, A second oil groove is provided in a portion of the first opposing surface closer to the back pressure space than the first oil groove, the second oil groove extending from the high pressure side region toward the back pressure space.

[0019] According to the above configuration, in a portion of the first opposing surface closer to the back pressure space than the first oil groove, the second oil groove extends from the high pressure side region side toward the back pressure space side, so that oil easily spreads along the direction in which the second oil groove extends.

[0020] A compressor according to a seventh aspect of the present disclosure includes: In the compressor according to the fifth or sixth aspect, the second bushing has a second opposing surface opposing the blade, The second opposing surface is provided with a third oil groove extending from the back pressure space side toward the low pressure side area side.

[0021] According to the above configuration, in the second opposing surface of the second bushing, the third oil groove extends from the back pressure space side toward the low pressure side area side, so that oil easily spreads along the extending direction of the third oil groove.

[0022] A compressor according to an eighth aspect of the present disclosure includes: In the compressor according to the seventh aspect, An end of the second opposing surface on the low pressure side region side is closer to the low pressure side region than an end of the third oil groove on the low pressure side region side.

[0023] According to the above configuration, the end of the second opposing surface on the low pressure side region side is closer to the low pressure side region than the end of the third oil groove on the low pressure side region side, so that oil can be prevented from flowing from the third oil groove into the low pressure side region.

[0024] A compressor according to a ninth aspect of the present disclosure includes: In any one of the compressors according to the fifth to eighth aspects, the cylinder includes a first cylinder closer to the first end plate than the second end plate, and a second cylinder closer to the second end plate than the first end plate; An intermediate plate disposed between the first cylinder and the second cylinder is provided with a third oil passage that guides oil in the oil reservoir to the first oil groove.

[0025] According to the above configuration, a third oil passage is provided in the intermediate plate disposed between the first cylinder and the second cylinder to guide oil in the oil reservoir to the first oil groove, thereby preventing the structure from becoming complicated.

[0026] A refrigeration device according to a tenth aspect of the present disclosure includes: The compressor includes any one of the compressors according to the first aspect to the ninth aspect.

[0027] According to the above configuration, a refrigeration system can be realized in which the maintenance interval for the compressor can be extended. [Brief description of the drawings]

[0028] [Figure 1] FIG. 1 is a vertical sectional view of a compressor according to a first embodiment of the present disclosure. [Diagram 2] FIG. 4 is a top view of a first cylinder and a first rocker in the first embodiment. [Diagram 3] FIG. 4 is a top view for explaining the oscillation of a first oscillator in the first embodiment. [Figure 4] FIG. 4 is a top view for explaining the oscillation of a first oscillator in the first embodiment. [Diagram 5] FIG. 3 is a perspective view of a first bush and a second bush of a first cylinder in the first embodiment. [Figure 6] FIG. 4 is a top view of a second cylinder and a second rocker in the first embodiment. [Figure 7] FIG. 4 is a perspective view of a first bush and a second bush of a second cylinder in the first embodiment. [Figure 8] FIG. 4 is a schematic diagram for explaining the flow of lubricating oil around a first bush and a second bush of the first cylinder. [Figure 9] FIG. 4 is a schematic diagram for explaining the flow of lubricating oil around a first bush and a second bush of the second cylinder. [Figure 10] FIG. 4 is a cross-sectional view for illustrating the supply of lubricating oil from an oil reservoir to a first cylinder and a second cylinder in the first embodiment. [Figure 11] FIG. 11 is a perspective view of a second bush of a first cylinder according to a second embodiment of the present disclosure. [Figure 12] FIG. 11 is a perspective view of a second bush of a second cylinder in the second embodiment. [Figure 13] FIG. 11 is a circuit diagram of an air conditioner according to a third embodiment of the present disclosure. [Figure 14]11 is a schematic vertical cross-sectional view of a main portion of a compressor according to a fourth embodiment of the present disclosure. [Figure 15] FIG. 13 is a schematic plan view of a first blade and its surrounding area in the fourth embodiment. [Figure 16] FIG. 13 is a schematic plan view of a second blade and its surrounding area according to the fourth embodiment; [Figure 17] FIG. 11 is a schematic vertical cross-sectional view of the periphery of a first bush of a compression mechanism part of the fourth embodiment. [Figure 18] FIG. 11 is a schematic vertical cross-sectional view of the periphery of a second bush of the compression mechanism part of the fourth embodiment. [Figure 19] 13 is a schematic vertical cross-sectional view of the periphery of a first bush of a compression mechanism section of a fifth embodiment of the present disclosure. FIG. [Figure 20] 13 is a schematic vertical cross-sectional view of a second bush and its periphery in a compression mechanism section of a sixth embodiment of the present disclosure. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0029] Hereinafter, an embodiment will be described. In the drawings, the same reference numerals represent the same or corresponding parts. In addition, the dimensions in the drawings, such as length, width, thickness, depth, etc., are appropriately changed from the actual scale for clarity and simplification of the drawings, and do not represent the actual relative dimensions.

[0030] [First embodiment] Fig. 1 is a vertical cross-sectional view of a compressor CMP according to a first embodiment of the present disclosure. Note that in Fig. 1, a first oscillator 51 and a second oscillator 71 are omitted from the illustration.

[0031] The compressor CMP is an example of a two-cylinder swing piston type rotary compressor. The compressor CMP includes a sealed container 1, a compression mechanism 2, and a motor 3. The sealed container 1 is an example of a casing.

[0032] The sealed container 1 has a cylindrical body 11, a top 12 that closes the opening at the upper end of the body 11, and a bottom 13 that closes the opening at the lower end of the body 11. The top 12 and the bottom 13 are each welded to the body 11.

[0033] The compression mechanism 2 is housed in the sealed container 1. More specifically, the compression mechanism 2 includes a front head 40 attached to the inner surface of the sealed container 1, a first cylinder 50 attached to the lower surface of the front head 40, and a partition plate 60 attached to the lower surface of the first cylinder 50. The first cylinder 50, the front head 40, and the partition plate 60 form a first cylinder chamber 150. The front head 40 is an example of a first end plate. The first cylinder 50 is an example of a cylinder. The partition plate 60 is an example of an intermediate plate.

[0034] The front head 40 is an end plate disposed on one axial side of the first cylinder 50. The front head 40 has a cylindrical boss portion 41 on its inner periphery. The rotating shaft 20 is inserted into the boss portion 41.

[0035] The first cylinder 50 sucks in a portion of the refrigerant gas that has flowed into the flow distributor 4 via the first suction pipe 5. In other words, a portion of the refrigerant gas in the flow distributor 4 is guided to the first suction pipe 5 and flows into the first cylinder chamber 150. The outer periphery of this first cylinder chamber 150 is defined by the inner periphery of the first cylinder 50. The first cylinder chamber 150 is an example of a cylinder chamber.

[0036] The refrigerant gas is obtained by controlling a compressor CMP, a condenser, an expansion mechanism, and an evaporator (not shown). The compressor CMP, the condenser, the expansion mechanism, and the evaporator constitute the main parts of an air conditioner as an example of a refrigeration device.

[0037] The partition plate 60 is an annular plate disposed between the first cylinder 50 and the second cylinder 70. To explain in more detail, the partition plate 60 is formed with a first oil supply passage 61 and a second oil supply passage 62 located radially outward from the first oil supply passage 61. The first oil supply passage 61 extends from the inner peripheral surface of the partition plate 70 in the radial direction of the partition plate 70. In other words, the first oil supply passage 61 communicates with a space surrounded by the inner peripheral surface of the partition plate 60 through an end portion on the radial inner side. The first oil supply passage 61 also communicates with the second oil supply passage 62 through an end portion on the radial outer side. On the other hand, the second oil supply passage 62 extends from the upper surface to the lower surface of the partition plate 60 and penetrates the partition plate 70 in the thickness direction of the partition plate 70. The first oil supply passage 61 and the second oil supply passage 62 are examples of second oil passages.

[0038] Furthermore, lubricating oil flows into the space surrounded by the inner peripheral surface of the partition plate 60 from an oil reservoir 14, which will be described later. The lubricating oil that flows into the space flows through a first oil supply passage 61 and a second oil supply passage 62. As a result, a portion of the lubricating oil is supplied to a first blade space 52 (shown in Figs. 2 to 4) of the first cylinder 50, while another portion of the lubricating oil is supplied to a second blade space 72 (shown in Fig. 6) of a second cylinder 70, which will be described later. The first blade space 52 and the second blade space 72 are examples of blade spaces.

[0039] The compression mechanism 2 also includes a second cylinder 70 attached to the underside of the partition plate 60, and a rear head 80 attached to the underside of the second cylinder 70. The second cylinder 70, the partition plate 60, and the rear head 80 form a second cylinder chamber 170. The second cylinder 70 is an example of a cylinder. The rear head 80 is an example of a second end plate.

[0040] The second cylinder 70 sucks in another portion of the refrigerant gas that has flowed into the flow distributor 4 through the second suction pipe 6. In other words, another portion of the refrigerant gas in the flow distributor 4 is guided to the second suction pipe 6 and flows into the second cylinder chamber 170. The outer peripheral edge of this second cylinder chamber 170 is defined by the inner peripheral surface of the second cylinder 70. The second cylinder chamber 170 is an example of a cylinder chamber.

[0041] The rear head 80 is an end plate located on the other axial side of the second cylinder 70. The rear head 80 has a cylindrical boss portion 81 on its inner periphery and a wall portion 82 on its outer periphery. The rotating shaft 20 is inserted into the boss portion 81. The wall portion 82 is provided around the entire outer periphery of the rear head 80 and surrounds the boss portion 81.

[0042] In addition, the first cylinder 50 is disposed closer to the front head 40 than to the rear head 80. In other words, the distance from the first cylinder 50 to the front head 40 is shorter than the distance from the rear head 80 to the front head 40.

[0043] In addition, the second cylinder 70 is disposed closer to the rear head 80 than to the front head 40. In other words, the distance from the second cylinder 70 to the rear head 80 is shorter than the distance from the front head 40 to the rear head 80.

[0044] A cup-shaped muffler 30 is attached to the upper surface of the front head 40 so as to cover a first discharge valve (not shown) provided on the front head 40. The muffler 30 is fixed to the front head 40 by bolts (not shown) or the like. A boss portion 41 of the front head 40 is inserted into the muffler 30. A first muffler chamber 130 is formed by the muffler 30 and the front head 40.

[0045] Meanwhile, a sheet metal muffler 90 is attached to the underside of the rear head 80 so as to cover a second discharge valve (not shown) provided on the rear head 80. This sheet metal muffler 90 is fixed to the rear head 80 with a plurality of bolts (not shown). An oil feed pump 120 attached to the lower end of the rotating shaft 20 is inserted through the sheet metal muffler 90. A second muffler chamber 190 is formed by the rear head 80 and the sheet metal muffler 90.

[0046] Further, a first oil supply passage 21, a second oil supply passage 22, and a third oil supply passage 23 are formed inside the rotating shaft 20. The first oil supply passage 21, the second oil supply passage 22, and the third oil supply passage 23 are oil supply passages for supplying the lubricating oil sucked up from the oil reservoir 14 to the sliding parts of the compression mechanism 2. The first oil supply passage 21 and the third oil supply passage 23 are an example of a first oil passage.

[0047] The first oil supply passage 21 extends along the axial direction of the rotating shaft 20 from the lower end of the rotating shaft 20 to the vicinity of the front head 40. The lubricating oil sucked up from the oil reservoir 14 is supplied to the second oil supply passage 22 and the third oil supply passage 23 via the first oil supply passage 21.

[0048] The second oil supply passage 22 extends from the upper end of the first oil supply passage 21 to the vicinity of the motor 3 along the axial direction of the rotating shaft 20. The diameter of the second oil supply passage 22 is set to be smaller than the diameter of the first oil supply passage 21. In other words, the second oil supply passage 22 is a passage narrower than the first oil supply passage 21.

[0049] The third oil supply passage 23 is a passage narrower than the second oil supply passage 22. The third oil supply passage 23 is formed in a portion of the rotating shaft 20 facing the inner circumferential surface of the partition plate 60. The third oil supply passage 23 extends from the inner circumferential surface to the outer circumferential surface of the rotating shaft 20 along the radial direction of the rotating shaft 20. As a result, the first oil supply passage 21 communicates with a space on the radial inside of the partition plate 60 (a space surrounded by the inner circumferential surface of the partition plate 60) via the third oil supply passage 23.

[0050] An oil supply pump 120 is attached to the lower end of the first oil supply passage 21 of the rotating shaft 20. The oil supply pump 120 has a tube member 121 made of, for example, iron, and a propeller-shaped pump member 122, most of which is housed within the tube member 121. An opening 123 having a diameter smaller than the inner diameter of the tube member 121 is provided at the lower end of the tube member 121. When the rotating shaft 20 rotates, the pump member 122 sucks up the lubricating oil in the oil reservoir 14 through the opening 123 and sends it to the first oil supply passage 21. Note that the oil supply pump 120 may be one disclosed in, for example, JP 2010-242625 A.

[0051] The motor 3 is an example of an inner rotor type motor. The motor 3 is disposed in an upper region inside the sealed container 1, and drives the compression mechanism section 2. The motor 3 also has an annular stator 31 fixed to the inner circumferential surface of the body section 11 of the sealed container 1, and a rotor 32 disposed radially inside the stator 31 and fixed to the rotating shaft 20. When the rotor 32 rotates, the rotating shaft 20 rotates together with the rotor 32, thereby driving the compression mechanism section 2.

[0052] In addition, in the compressor CMP, compressed high-temperature, high-pressure refrigerant gas (discharge gas) is discharged from the compression mechanism 2 to fill the inside of the sealed container 1, passes through the gap between the stator 31 and the rotor 32, cools the motor 3, and is then discharged to the outside from the discharge pipe 7 provided above the motor 3.

[0053] In addition, within the sealed container 1, a part of the region below the compression mechanism unit 2 serves as an oil reservoir 14 in which lubricating oil is stored. This lubricating oil is sent from the oil reservoir 14 to the first oil supply passage 61 and the second oil supply passage 62 of the partition plate 60 via the first oil supply passage 21 and the third oil supply passage 23 of the rotating shaft 20.

[0054] 2 is a diagram showing the first cylinder 50 and the first oscillator 51 as viewed from above. Note that the rotating shaft 20 is omitted in FIG.

[0055] The compressor CMP includes a first oscillator 51 having a first piston 51a accommodated in a first cylinder chamber 150 and a first blade 51b integrally formed with the first piston 51a. The first oscillator 51 oscillates inside the first cylinder 50. The first oscillator 51 divides the first cylinder chamber 150 into a suction chamber 150a (low pressure side region) and a compression chamber 150b (high pressure side region). In other words, the first cylinder chamber 150 is divided into the suction chamber 150a and the compression chamber 150b by the first piston 51a and the first blade 51b. The suction chamber 150a is formed on the right side of the first blade 51b, while the compression chamber 150b is formed on the left side of the first blade 51b. The right side corresponds to the right side when the first cylinder 50 is viewed from the motor 3 side. The left side corresponds to the left side when the first cylinder 50 is viewed from the motor 3 side. The first piston 51a is an example of a piston. The first blade 51b is an example of a blade. The first blade space 1052 is an example of a blade space. The first back pressure space 1055 is an example of a back pressure space. The suction chamber 1150a is an example of a low pressure side region.

[0056] Further, a first suction port 111 is formed in the first cylinder 50 on the right side (the suction chamber 150a side) of the first blade 51b, penetrating from the outer peripheral surface to the inner peripheral surface of the first cylinder 50. The first suction port 111 opens into the suction chamber 150a on the right side of the first blade 51b. The first suction pipe 5 (shown in FIG. 1) is connected to the radially outer end of the first suction port 111 via a first inlet tube 9 (shown in FIG. 1).

[0057] Further, a first discharge port (not shown) penetrating from the upper surface to the lower surface of the front head 40 (shown in FIG. 1) is in communication with the compression chamber 150b of the first cylinder 50. This first discharge port is opened and closed by the first discharge valve.

[0058] The first cylinder 50 is provided with a first blade space 52 located radially outward from the first cylinder chamber 150, and a first back pressure space 55 located radially outward from the first blade space 52. The first blade space 52 and the first back pressure space 55 are each a through hole penetrating from the upper surface to the lower surface of the first cylinder 50. The first back pressure space 55 is an example of a back pressure space.

[0059] The first blade space 52 is connected to the first cylinder chamber 150 at its radially inner end, and is in communication with the first blade space 52. The first blade 51b advances and retreats in this first blade space 52. In other words, while inserted in the first blade space 52, the first blade 51b alternately repeats movement in the radially outward direction and movement in the radially outward direction.

[0060] The first back pressure space 55 has a radially inner end connected to a radially outer end of the first blade space 52, and communicates with the first cylinder chamber 150 and the first blade space 52. An upper opening (front head 40 side) of the first back pressure space 55 is sealed by the front head 40. Meanwhile, a lower opening (partition plate 60 side) of the first back pressure space 55 communicates with a through hole 63 of the partition plate 60. Also, the first blade 51b advances and retreats in the first back pressure space 55.

[0061] A first bush 53 and a second bush 54 are arranged to be able to swing in the first blade space 52. The first bush 53 and the second bush 54 sandwich the first blade 51b from both sides and support the first blade 51b so that the first blade 51b can move forward and backward. Lubricating oil is supplied from a second oil supply passage 62 of the partition plate 60 between the first bush 53 and the first blade 51b and between the second bush 54 and the first blade 51b.

[0062] Further, the region of the first blade space 52 on the first bush 53 side communicates with the compression chamber 150b of the first cylinder chamber 150, while the region of the first blade space 52 on the second bush 54 side communicates with the suction chamber 150a of the first cylinder chamber 150. The region of the first blade space 52 on the first bush 53 side can be rephrased as the region between the left side surface of the first blade 51b (opposite the first suction port 111 side) and the left inner circumferential surface of the first blade space 52. The region of the first blade space 52 on the second bush 54 side can be rephrased as the region between the right side surface of the first blade 51b (the first suction port 111 side) and the right inner circumferential surface of the first blade space 52.

[0063] As shown in FIG. 1, the rotating shaft 20 has a first eccentric portion 20a disposed in the first cylinder chamber 150. The first eccentric portion 20a is provided eccentrically with respect to the central axis of the rotating shaft 20. The first eccentric portion 20a rotates eccentrically with the clockwise rotation of the rotating shaft 20, and the first piston 51a fitted to the first eccentric portion 20a oscillates along the inner circumferential surface of the first cylinder chamber 150 as shown in FIGS. 3 and 4. With the oscillating motion of the first piston 51a, low-pressure refrigerant gas is sucked into the suction chamber 150a from the first suction port 111, compressed to high pressure in the compression chamber 150b, and then discharged from the first discharge port. The high-pressure refrigerant gas discharged from the first discharge port is then discharged from the discharge pipe 7 to the outside of the compressor CMP.

[0064] FIG. 5 is a view of the first bush 53 and the second bush 54 used in the first cylinder 50, viewed obliquely from above.

[0065] The first bush 53 is made of, for example, a metal material and has a substantially semi-cylindrical shape. The first bush 53 has a first side surface 53a facing the left side surface of the first blade 51b (shown in FIG. 2) and a second side surface 53b facing the left inner circumferential surface of the first blade space 52 (shown in FIG. 2).

[0066] The first side surface 53a is formed to fit along the left side surface of the first blade 51b. When the first piston 51a oscillates, the left side surface of the first blade 51b slides on the first side surface 53a. In addition, a groove 53c is formed in the first side surface 53a, which extends from the upper surface 53d to the lower surface 53e of the first bush 53.

[0067] The second side surface 53b is formed along the inner circumferential surface on the left side of the first blade space 52. No groove extending in the radial or circumferential direction is formed on this second side surface 53b.

[0068] The second bush 54 is made of, for example, a metal material and has a substantially semi-cylindrical shape, similar to the first bush 53. The second bush 54 has a first side surface 54a facing the right side surface of the first blade 51b (shown in FIG. 2) and a second side surface 54b facing the right inner circumferential surface of the first blade space 52 (shown in FIG. 2).

[0069] The first side surface 54a is formed to fit along the right side surface of the first blade 51b. When the first piston 51a oscillates, the right side surface of the first blade 51b slides on the first side surface 54a. Also, a groove 54c is formed in the first side surface 54a, extending from the upper surface 54d to the lower surface 54e of the second bushing 54.

[0070] The second side surface 54b is formed along the inner circumferential surface on the right side of the first blade space 52. No grooves extending in the radial and circumferential directions are formed on this second side surface 54b.

[0071] Fig. 6 is a diagram showing the second cylinder 70 and the second oscillator 71 as viewed from above. Note that the rotating shaft 20 is omitted in Fig. 6.

[0072] The compressor CMP includes a second oscillator 71 having a second piston 71a accommodated in a second cylinder chamber 170 and a second blade 71b integrally formed with the second piston 71a. The second oscillator 71 oscillates inside the second cylinder 70. The second oscillator 71 divides the second cylinder chamber 170 into a suction chamber 170a (low pressure side region) and a compression chamber 170b (high pressure side region). In other words, the second cylinder chamber 170 is divided into the suction chamber 170a and the compression chamber 170b by the second piston 71a and the second blade 71b. The suction chamber 170a is formed on the right side of the second blade 71b, while the compression chamber 170b is formed on the left side of the second blade 71b. The right side corresponds to the right side when the second cylinder 70 is viewed from the motor 3 side. The left side corresponds to the left side when the second cylinder 70 is viewed from the motor 3 side. The second piston 71a is an example of a piston. The second blade 71b is an example of a blade.

[0073] Further, a second suction port 112 is formed in the second cylinder 70 on the right side (the suction chamber 170a side) of the second blade 71b, penetrating from the outer peripheral surface to the inner peripheral surface of the second cylinder 70. The second suction port 112 opens into the suction chamber 170a on the right side of the second blade 71b. The first suction pipe 5 (shown in FIG. 1) is connected to the radially outer end of the second suction port 112 via the second inlet tube 10 (shown in FIG. 1).

[0074] Further, a first discharge port (not shown) penetrating from the upper surface to the lower surface of the front head 40 (shown in FIG. 1) is in communication with the compression chamber 170b of the second cylinder 70. This first discharge port is opened and closed by the first discharge valve.

[0075] The second cylinder 70 is provided with a second blade space 72 located radially outward from the second cylinder chamber 170, and a second back pressure space 75 located radially outward from the second blade space 72. The second blade space 72 and the second back pressure space 75 are each a through hole penetrating from the upper surface to the lower surface of the second cylinder 70. The second back pressure space 75 is an example of a back pressure space.

[0076] The second blade space 72 is connected to the second cylinder chamber 170 at its radially inner end, and is in communication with the second blade space 72. The second blade 71b advances and retreats in this second blade space 72. In other words, while inserted in the second blade space 72, the second blade 71b alternately repeats movement in the radially outward direction and movement in the radially outward direction.

[0077] The second back pressure space 75 has a radially inner end connected to a radially outer end of the second blade space 72, and communicates with the second cylinder chamber 170 and the second blade space 72. The opening on the lower side (the rear head 80 side) of the second back pressure space 75 is sealed by the rear head 80. Meanwhile, the opening on the lower side (the partition plate 60 side) of the second back pressure space 75 communicates with the through hole 63 of the partition plate 60. In the second back pressure space 75, the second blade 71b advances and retreats.

[0078] A first bush 73 and a second bush 74 are arranged to be able to swing in the second blade space 72. The first bush 73 and the second bush 74 sandwich the second blade 71b from both sides and support the second blade 71b so that the second blade 71b can move forward and backward. Lubricating oil is supplied from the second oil supply passage 62 of the partition plate 60 between the first bush 73 and the second blade 71b and between the second bush 74 and the second blade 71b.

[0079] Further, the region of the second blade space 72 on the first bush 73 side communicates with the compression chamber 170b of the second cylinder chamber 170, while the region of the second blade space 72 on the second bush 74 side communicates with the suction chamber 170a of the second cylinder chamber 170. The region of the second blade space 72 on the first bush 73 side can be rephrased as the region between the left side surface of the second blade 71b (opposite the second suction port 112 side) and the left inner circumferential surface of the second blade space 72. The region of the second blade space 72 on the second bush 73 side can be rephrased as the region between the right side surface of the second blade 71b (the second suction port 112 side) and the right inner circumferential surface of the second blade space 72.

[0080] As shown in FIG. 1, the rotating shaft 20 has a second eccentric portion 20b disposed in the second cylinder chamber 170. The second eccentric portion 20b is provided eccentrically with respect to the central axis of the rotating shaft 20. The second eccentric portion 20b rotates eccentrically with the clockwise rotation of the rotating shaft 20, and the second piston 71a fitted to the second eccentric portion 20b oscillates along the inner circumferential surface of the second cylinder chamber 170, similar to the second piston 71a (shown in FIG. 6) of the second oscillating body 71. At this time, the refrigerant gas sucked into the suction chamber 170a from the second suction port 112 with the oscillating motion of the second piston 71a is compressed in the compression chamber 170b to become high pressure, and then discharged from the second discharge port. The high-pressure refrigerant gas discharged from the second discharge port is then discharged from the discharge pipe 7 to the outside of the compressor CMP.

[0081] FIG. 7 is a view of the first bush 73 and the second bush 74 used in the second cylinder 70, viewed obliquely from above.

[0082] The first bush 73 is made of, for example, a metal material and has a semi-cylindrical shape. The first bush 73 has a first side surface 73a facing the left side surface of the second blade 71b (shown in FIG. 6) and a second side surface 73b facing the left inner circumferential surface of the second blade space 72 (shown in FIG. 6).

[0083] The first side surface 73a is formed to fit along the left side surface of the second blade 71b. When the first piston 51a oscillates, the left side surface of the second blade 71b slides on the first side surface 73a. Also, a groove 73c is formed on the first side surface 73a, which extends from the upper surface 73d to the lower surface 73e of the first bush 73.

[0084] The second side surface 73b is formed along the inner circumferential surface on the left side of the second blade space 72. No groove extending in the radial or circumferential direction is formed on this second side surface 73b.

[0085] The second bush 74 is formed of, for example, a metal material and has a semi-cylindrical shape, similar to the first bush 73. The second bush 74 has a first side surface 74a facing the right side surface of the second blade 71b (shown in FIG. 6) and a second side surface 74b facing the right inner circumferential surface of the second blade space 72 (shown in FIG. 6).

[0086] The first side surface 74a is formed to fit along the right side surface of the second blade 71b. When the first piston 51a oscillates, the right side surface of the second blade 71b slides on the first side surface 74a. Also, a groove 74c is formed on the first side surface 74a, which extends from the upper surface 74d to the lower surface 74e of the second bushing 74.

[0087] The second side surface 74b is formed along the inner circumferential surface on the right side of the second blade space 72. No grooves extending in the radial and circumferential directions are formed on this second side surface 74b.

[0088] In the compressor CMP having the above-mentioned configuration, the upper opening of the first back pressure space 55 in the first cylinder 50 is sealed by the front head 40, while the lower opening of the second back pressure space 75 in the second cylinder 70 is sealed by the rear head 80. As a result, the high-pressure refrigerant gas in the sealed container 1 does not flow into the first back pressure space 55 from the upper opening of the first back pressure space 55, and does not flow into the second back pressure space 75 from the lower opening of the second back pressure space 75. Also, as shown in FIG. 8, even if a part of the lubricating oil supplied from the oil reservoir 14 to the grooves 53c and 54c flows along the dotted arrows A11 and A21 and flows into the first back pressure space 55, it then flows along the dotted arrow A22 and flows into the suction chamber 150a. 9, even if a part of the lubricating oil supplied from the oil reservoir 14 to the grooves 73c, 74c flows along the dotted arrows A31, A41 and flows into the second back pressure space 75, it then flows along the dotted arrow A42 and flows into the suction chamber 170a. As a result, the pressure in the first back pressure space 55 and the second back pressure space 75 can be lowered below the pressure in the sealed container 1 (the pressure of the refrigerant gas discharged from the first discharge port and the second discharge port into the sealed container 1). Therefore, by preventing the pressure difference between the suction chamber 150a of the first cylinder chamber 150 and the first back pressure space 55 and the pressure difference between the suction chamber 170a of the second cylinder chamber 170 and the second back pressure space 75 from becoming large, the load applied to the second bushes 54, 74 can be reduced, and the deterioration of the slidability of the second bushes 54, 74 can be suppressed.

[0089] If the upper opening of the first back pressure space 55 is not sealed and is open to the sealed container 1, or if the lower opening of the second back pressure space 75 is not sealed and is open to the sealed container 1, the high-pressure refrigerant gas in the sealed container 1 flows from the upper opening of the first back pressure space 55 into the first back pressure space 55 and the second back pressure space 75, or flows from the lower opening of the second back pressure space 75 into the first back pressure space 55 and the second back pressure space 75. In this case, the pressure difference between the suction chamber 150a of the first cylinder chamber 150 and the first back pressure space 55, and the pressure difference between the suction chamber 170a of the second cylinder chamber 170 and the second back pressure space 75 become large. This increase in pressure difference leads to an increase in the load on the second bushes 54, 74, which leads to a decrease in the sliding properties of the second bushes 54, 74.

[0090] Furthermore, if the upper opening of the first back pressure space 55 is sealed by the front head 40, but the upper end of a pipe is connected to the lower opening of the second back pressure space 75 and the lower end of this pipe is disposed in the oil reservoir 9, high pressure lubricating oil will be supplied to the first back pressure space 55 and the second back pressure space 75 through the pipe. This also leads to a decrease in the sliding properties of the second bushes 54, 74.

[0091] As shown in FIG. 8, another part of the lubricating oil supplied from the oil reservoir 14 to the grooves 53c and 54c flows along the dotted arrows A13 and A23 and flows into the compression chamber 150b and the suction chamber 150a. To explain in more detail, the pressure in the compression chamber 150b changes from low pressure to high pressure (discharge pressure) according to the change in the position of the piston 51a. As a result, another part of the lubricating oil supplied from the oil reservoir 14 to the groove 53c flows along the dotted arrow A13 and also flows into the compression chamber 150b. As the pressure in the compression chamber 150b changes, the lubricating oil flows from the compression chamber 150b to the first back pressure space 55 and from the first back pressure space 55 to the compression chamber 150b along the dotted arrow A12. On the other hand, another portion of the lubricating oil supplied from the oil reservoir 14 to the groove 54c does not pass through the first back pressure space 55, but flows along the dotted arrow A23 and into the suction chamber 150a.

[0092] As shown in FIG. 9, another part of the lubricating oil supplied from the oil reservoir 14 to the grooves 73c and 74c flows along the dotted arrows A33 and A43 and flows into the compression chamber 170b and the suction chamber 170a. To explain in more detail, the pressure in the compression chamber 170b changes from low pressure to high pressure (discharge pressure) according to the change in the position of the piston 71a. As a result, another part of the lubricating oil supplied from the oil reservoir 14 to the groove 73c flows along the dotted arrow A33 and also flows into the compression chamber 170b. As the pressure in the compression chamber 170b changes, the lubricating oil flows from the compression chamber 170b to the second back pressure space 75 and from the second back pressure space 75 to the compression chamber 170b along the dotted arrow A32. On the other hand, another portion of the lubricating oil supplied from the oil reservoir 14 to the groove 74c does not pass through the second back pressure space 75, but flows along the dotted arrow A43 and into the suction chamber 170a.

[0093] 10, the lubricating oil in the oil reservoir 14 flows toward the first cylinder 50 and the second cylinder 70. At this time, the lubricating oil in the oil reservoir 14 is supplied to the grooves 53c, 73c of the first bushings 53, 73 and the grooves 54c, 74c of the second bushings 54, 74 via the first oil supply passage 21 and the third oil supply passage 23 of the rotating shaft 20, so that the first bushings 53, 73 and the second bushings 54, 74 can be reliably oiled.

[0094] In the above first embodiment, the refrigerant gas is supplied from the flow divider 4 to the compression mechanism 2, but the refrigerant gas may be supplied from an accumulator to the compression mechanism 2. In other words, an accumulator may be used instead of the flow divider 4.

[0095] In the first embodiment, the compressor CMP is a two-cylinder swing piston type rotary compressor, but may be a one-cylinder swing piston type rotary compressor. When the compressor CMP is a one-cylinder swing piston type rotary compressor, an oil supply passage that plays a role similar to that of the first oil supply passage 61 and the second oil supply passage 62 may be provided in the front head or the rear head.

[0096] In the first embodiment described above, the first oil supply passage 21 and the third oil supply passage 23 are provided in the rotating shaft 20, while the first oil supply passage 61 and the second oil supply passage 62 are provided in the partition plate 60. However, the first oil supply passage 21 and the third oil supply passage 23 may not be provided in the rotating shaft 20, and the first oil supply passage 61 and the second oil supply passage 62 may not be provided in the partition plate 60. Even in this case, the deterioration of the slidability of the second bushes 54, 74 can be suppressed.

[0097] In the first embodiment, the first piston 51a and the first blade 51b are integrally formed, but the first piston 51a and the first blade 51b may be formed separately. Similarly, the second piston 71a and the second blade 71b may be formed separately.

[0098] In the first embodiment, the lower opening of the first back pressure space 55 is not sealed by the partition plate 60, but it may be sealed by the partition plate 60.

[0099] In the first embodiment, the upper opening of the second back pressure space 75 is not sealed by the partition plate 60, but it may be sealed by the partition plate 60.

[0100] Second Embodiment Fig. 11 is a view of the second bush 254 used in the first cylinder 50 according to the second embodiment of the present disclosure, as viewed obliquely from above. Also, Fig. 12 is a view of the second bush 274 used in the second cylinder 70 according to the second embodiment of the present disclosure, as viewed obliquely from above.

[0101] The compressor of the second embodiment differs from the compressor CMP of the first embodiment only in that the compressor CMP of the second embodiment includes second bushings 254, 274 instead of the second bushings 54, 74.

[0102] The second bush 254, 274 is formed of, for example, a metal material and has a semi-cylindrical shape. The second bush 254, 274 has a second side surface 254b, 274b facing the right inner peripheral surface of the second blade space 72 (shown in Figs. 2 and 6). A groove 254f, 274f extending along the circumferential direction of the second bush 254, 274 is provided in the portion of the second side surface 254b, 274b on the suction chamber 150a, 170a side. The second side surface 254b, 274b is the peripheral surface of the second bush 254, 274 on the opposite side to the first blade 51b, 71b (shown in Figs. 2 and 6).

[0103] The compressor having the above configuration has a similar configuration to that of the first embodiment, and therefore provides the same effects as those of the first embodiment.

[0104] In addition, the grooves 254f, 274f are provided in the second side surfaces 254b, 274b on the suction chamber 150a, 170a side, so that the lubricating oil can easily flow from the first and second back pressure spaces 55, 75 to the suction chambers 150a, 170a. As a result, the increase in pressure in the first and second back pressure spaces 55, 75 can be suppressed.

[0105] In the second embodiment, one groove 254f is provided in the portion of the second side surface 254b on the side of the suction chamber 150a, but multiple grooves may be provided. For example, the multiple grooves may extend parallel to each other and extend along the circumferential direction of the second bushing 254. Furthermore, the multiple grooves may have the same or different circumferential lengths.

[0106] In the second embodiment, a single circumferentially extending groove 274f is provided in a portion of the second side surface 274b on the suction chamber 170a side. The multiple grooves may extend, for example, parallel to one another and along the circumferential direction of the second bushing 254. The multiple grooves may have the same or different circumferential lengths.

[0107] Third Embodiment 11 is a circuit diagram of an air conditioner as an example of a refrigeration device including a refrigerant circuit RC according to a third embodiment of the present disclosure. This refrigerant circuit RC uses the compressor CMP according to the first embodiment.

[0108] The air conditioner of the third embodiment comprises an indoor unit U1 installed in a room to be air-conditioned, and an outdoor unit U2 installed outdoors.

[0109] <Configuration of indoor unit U1> The indoor unit U1 of the air conditioner includes an indoor heat exchanger 1004, one end of which is connected to refrigerant pipe L4 (communication pipe) and the other end of which is connected to refrigerant pipe L5 (communication pipe), and an indoor fan 1006 that supplies air to the indoor heat exchanger 1004. The indoor fan 1006 blows out the air, the temperature of which has been adjusted by the indoor heat exchanger 1004, toward the room.

[0110] <Configuration of outdoor unit U2> The outdoor unit U2 of the above-mentioned air conditioner has a compressor CMP, a four-way switching valve 1001, an outdoor heat exchanger 1002, an expansion valve 1003 as an example of an expansion mechanism, a diverter 4, and an outdoor fan 1005 that sends air to the outdoor heat exchanger 1002.

[0111] The discharge side of the compressor CMP is connected to a first port a of a four-way switching valve 1001 via a refrigerant pipe L1. A second port b of the four-way switching valve 1001 is connected to one end of an outdoor heat exchanger 1002 via a refrigerant pipe L2. The other end of the outdoor heat exchanger 1002 is connected to one end of an expansion valve 1003 via a refrigerant pipe L3, and the other end of the expansion valve 1003 is connected to one end of a refrigerant pipe L4 (communication pipe). One end of the refrigerant pipe L5 (communication pipe) is connected to a third port c of the four-way switching valve 1001. A fourth port d of the four-way switching valve 1001 is connected to the suction side of the compressor CMP via a refrigerant pipe L6, a flow divider 4, a first suction pipe 5, and a second suction pipe 6.

[0112] The refrigerant flowing through the outdoor heat exchanger 1002 exchanges heat with air drawn in by the outdoor fan 1005 .

[0113] The expansion valve 1003 is, for example, an electrically operated valve whose opening degree is adjustable, and the opening degree changes in response to a signal from a control device (not shown).

[0114] <Configuration of refrigerant circuit RC> The refrigerant circuit RC of the air conditioner is made up of an indoor heat exchanger 1004, a compressor CMP, a four-way switching valve 1001, an outdoor heat exchanger 1002, an expansion valve 1003, a flow divider 4, refrigerant pipes L1 to L6, a first suction pipe 5, and a second suction pipe 6. This constitutes a circular refrigerant circuit RC.

[0115] In cooling operation, as shown in FIG. 11, the four-way switching valve 1001 is switched to the switching position shown by the solid line, and in heating operation, the four-way switching valve 1001 is switched to the switching position shown by the dotted line, and the compressor CMP is driven to circulate the refrigerant through the refrigerant circuit RC.

[0116] According to the air conditioner configured as above, by providing the refrigerant circuit RC using the compressor CMP, it is possible to realize an air conditioner in which the maintenance interval for the compressor CMP can be extended.

[0117] In the above third embodiment, an air conditioner has been described as the refrigeration apparatus, but the refrigeration apparatus including the refrigerant circuit RC using the compressor CMP is not limited to an air conditioner and may be a refrigeration apparatus of another configuration.

[0118] In the above third embodiment, the compressor CMP of the first embodiment is used in the refrigerant circuit RC. In the refrigerant circuit RC, for example, a compressor according to a modification of the first embodiment, a compressor according to the second embodiment, or a compressor according to a modification of the second embodiment may be used.

[0119] [Fourth embodiment] FIG. 14 is a schematic vertical cross-sectional view of a main portion of a compressor CMP' according to the fourth embodiment of the present disclosure.

[0120] The compressor CMP' is an example of a two-cylinder oscillating piston type rotary compressor. The compressor CMP' includes a sealed container 1, a compression mechanism 1102, and a motor (not shown). The motor is configured similarly to the motor 3 of the first embodiment, and drives a rotary shaft 1020.

[0121] The compression mechanism 1102 has first and second cylinders 1050 and 1070, a partition plate 1060, a front head 1040, a rear head 1080, and first and second cup-shaped mufflers 1030 and 1090. When the compressor CMP' is driven, the liquid level of the lubricating oil stored in the oil reservoir 14 is higher than the upper surface of the rear head 1080. The first and second cylinders 1050 and 1070 are an example of a cylinder. The partition plate 1060 is an example of an intermediate plate. The front head 1040 is an example of a first end plate. The rear head 1080 is an example of a second end plate.

[0122] The first and second cylinders 1050, 1070 are formed to have smaller outer diameters than the first and second cylinders 50, 70 of the first embodiment. The first cylinder 1050 is closer to the front head 1040 than the rear head 1080. The second cylinder 1070 is closer to the rear head 1080 than the front head 1040. That is, the first cylinder 1050 is disposed relatively on the upper side, while the second cylinder 1070 is disposed relatively on the lower side.

[0123] The partition plate 1060 differs from the partition plate 60 of the first embodiment in that it does not have a passage for guiding the lubricating oil from the rotating shaft 1020 in the radial direction of the partition plate 1060 .

[0124] The front head 1040 and the rear head 1080 have different external shapes from the front head 40 and the rear head 80 of the first embodiment.

[0125] Fig. 15 is a schematic diagram of the first blade 51b and its surrounding area as viewed from above. Note that the arrows in Fig. 15 indicate the flow of lubricating oil when the compressor CMP' is in operation.

[0126] The first cylinder 1050 is provided with a first cylinder chamber 1150, a first blade space 1052, and a first back pressure space 1055, similar to the first cylinder 50. The first cylinder chamber 1150 is divided into a suction chamber 1150a (shown in FIG. 18) and a compression chamber 1150b (shown in FIG. 17) by the first piston 51a and the first blade 51b. The upper opening of the first back pressure space 1055 is sealed by the front head 1040. On the other hand, the lower opening of the first back pressure space 1055 is sealed by the partition plate 1060. The first blade space 1052 is an example of a blade space. The first back pressure space 1055 is an example of a back pressure space. The suction chamber 1150a is an example of a low pressure side region. The compression chamber 1150b is an example of a high pressure side region.

[0127] The first bush 53 and the second bush 1054 are arranged to be able to swing in the first blade space 1052. The area of ​​the first blade space 1052 on the first bush 53 side communicates with the compression chamber 1150b of the first cylinder chamber 1150. On the other hand, the area of ​​the first blade space 1052 on the second bush 1054 side communicates with the suction chamber 1150a of the first cylinder chamber 1150.

[0128] The first backpressure space 1055 communicates with a region of the first blade space 1052 on the first bush 53 side. The first backpressure space 1055 also communicates with a region of the first blade space 1052 on the second bush 1054 side.

[0129] A first side surface 53a (shown in FIG. 17) of the first bushing 53 faces the first blade 51b. A groove 53c is provided in the first side surface 53a, extending from the rear head 1080 side toward the front head 1040 side. When the compressor CMP' is driven, lubricating oil in the oil reservoir 14 is supplied to the groove 53c. The first side surface 53a is an example of a first opposing surface. The groove 53c is an example of a first oil supply groove.

[0130] The second bush 1054 is formed of, for example, a metal material, similar to the second bush 54 of the first embodiment. This second bush 1054 has a first side surface 1054a (shown in FIG. 18) facing the first blade 51b. The first side surface 1054a is a flat surface. That is, the second bush 1054 is different from the second bush 54 of the first embodiment only in that it has a flat first side surface 1054a.

[0131] Fig. 16 is a schematic diagram of the second blade 71b and its surrounding area as viewed from above. Note that the arrows in Fig. 16 indicate the flow of lubricating oil when the compressor CMP' is in operation.

[0132] The second cylinder 1070 is provided with a second cylinder chamber 1170, a second blade space 1072, and a second back pressure space 1075, similar to the second cylinder 70. The second cylinder chamber 1170 is divided into a suction chamber 1170a (shown in FIG. 18) and a compression chamber 1170b (shown in FIG. 17) by the second piston 71a and the second blade 71b. The upper opening of the second back pressure space 75 is sealed by the partition plate 1060. Meanwhile, the lower opening of the second back pressure space 1075 is sealed by the rear head 1080. The second blade space 1072 is an example of a blade space. The second back pressure space 1075 is an example of a back pressure space. The suction chamber 1170a is an example of a low pressure side region. The compression chamber 1170b is an example of a high pressure side region.

[0133] The first bush 73 and the second bush 1074 are arranged to be able to swing in the second blade space 1072. The area of ​​the second blade space 1072 on the first bush 73 side communicates with the compression chamber 1170b of the second cylinder chamber 1170. On the other hand, the area of ​​the second blade space 1072 on the second bush 1074 side communicates with the suction chamber 1170a of the second cylinder chamber 1170.

[0134] The second back pressure space 1075 communicates with a region of the second blade space 1072 on the first bush 73 side. The second back pressure space 1075 also communicates with a region of the second blade space 1072 on the second bush 1074 side.

[0135] A first side surface 73a (shown in FIG. 17) of the first bush 73 faces the second blade 71b. A groove 73c is provided in the first side surface 73a, extending from the rear head 1080 side toward the front head 1040 side. When the compressor CMP' is driven, lubricating oil in the oil reservoir 14 is supplied to the groove 73c. ​​The first side surface 73a is an example of a first opposing surface. The groove 73c is an example of a first oil supply groove.

[0136] The second bush 1074 is formed of, for example, a metal material, similar to the second bush 74 of the first embodiment. This second bush 1074 has a first side surface 1074a (shown in FIG. 18) facing the second blade 71b. The first side surface 1074a is a flat surface. That is, the second bush 1074 differs from the second bush 74 of the first embodiment only in that it has a flat first side surface 1074a.

[0137] A groove 1080a is provided on the upper surface of the rear head 1080 (see FIG. 17). One end of this groove 1080a is connected to the lower end of the groove 73c of the first bush 73. Meanwhile, the other end of the groove 1080a is connected to the outer periphery of the upper surface of the rear head 1080. That is, the rear head 1080 is formed so that the lubricating oil in the oil reservoir 14 can flow into the groove 73c of the first bush 73 via the groove 1080a of the rear head 1080.

[0138] Fig. 17 is a schematic vertical cross-sectional view of the periphery of first bushes 53, 73 of the compression mechanism part 1102. Fig. 18 is a schematic vertical cross-sectional view of the periphery of second bushes 1054, 1074 of the compression mechanism part 1102. The arrows in Figs. 17 and 18 indicate the flow of lubricating oil when the compressor CMP' is driven.

[0139] As shown in FIG. 17, the partition plate 1060 is provided with an oil passage 1060a that guides the lubricating oil in the oil reservoir 14 to the groove 53c of the first bush 53. More specifically, the oil passage 1060a is a hole that penetrates the partition plate 1060 in the vertical direction and is located between the region of the first blade space 1052 on the first bush 53 side and the region of the second blade space 1072 on the first bush 73 side. The upper end of the oil passage 1060a is connected to the lower end of the groove 53c of the first bush 53. On the other hand, the lower end of the oil passage 1060a is connected to the upper end of the groove 53c of the first bush 73. That is, the partition plate 1060 is formed so that the lubricating oil that flows from the oil reservoir 14 into the groove 73c of the first bush 73 can flow into the groove 53c of the first bush 53 through the oil passage 1060a of the partition plate 1060. The oil passage 1060a is an example of a third oil passage.

[0140] Further, as shown in FIG. 18, no through hole such as the oil passage 1060a is provided between the area of ​​the first blade space 1052 on the second bushing 1054 side and the area of ​​the second blade space 1072 on the second bushing 1074 side.

[0141] According to the compressor CMP' having the above configuration, as shown in FIG. 14, the upper opening of the first back pressure space 1055 is sealed by the front head 1040, while the lower opening of the second back pressure space 1075 is sealed by the rear head 1080, thereby achieving the same effects as those of the first embodiment.

[0142] Furthermore, when the compressor CMP' is driven, the lubricating oil in the oil reservoir 14 is supplied to the grooves 53c, 73c of the first bushings 53, 73 as shown in Fig. 17. Since the grooves 53c, 73c extend from the lower surface of the first bushings 53, 73 to the upper surface of the first bushings 53, 73, the lubricating oil easily spreads from the lower side to the upper side on the first side surfaces 53a, 73a of the first bushings 53, 73. As a result, the lubricating state of the first side surfaces 53a, 73a of the first bushings 53, 73 can be prevented from deteriorating.

[0143] Furthermore, the lubricating oil supplied to the grooves 53c, 73c of the first bushings 53, 73 flows toward the suction chambers 1150a, 1170a via the first and second back pressure spaces 1055, 1075 as shown in Figs. 15 to 18. This makes it easier for the lubricating oil to spread from the first and second back pressure spaces 1055, 1075 side to the suction chambers 1150a, 1170a side on the first side surfaces 1054a, 1074a of the second bushings 1054, 1074. As a result, it is possible to suppress deterioration of the lubricating state of the first side surfaces 1054a, 1074a of the second bushings 1054, 1074.

[0144] 17, the oil passage 1060a is provided in the partition plate 1060, so that the lubricating oil flows from the groove 73c of the first bushing 73 to the groove 53c of the first bushing 53. Therefore, the lubricating oil can be supplied from the groove 73c of the first bushing 73 to the groove 53c of the first bushing 53 with a simple structure.

[0145] In the above fourth embodiment, the grooves 53c and 73c are formed so as to extend along a direction parallel to the rotation axis 1020. However, for example, the grooves 53c and 73c may be formed so as to extend along a direction inclined with respect to the rotation axis 1020.

[0146] In the fourth embodiment, the number of each of the grooves 53c and 73c is one, but the number may be multiple.

[0147] In the fourth embodiment, the lubricating oil in the oil reservoir 14 may be supplied to the grooves 53c, 73c of the first bushes 53, 73 via the rotating shaft 1020 and the partition plate 1060. In this case, it is not necessary to provide the groove 1080a on the upper surface of the rear head 1080. Fifth embodiment Fig. 19 is a schematic diagram of a vertical cross section around the first bushes 1053, 1073 of the first and second cylinders 1050, 1070 according to the fifth embodiment of the present disclosure. Note that the arrows in Fig. 19 indicate the flow of lubricating oil when the compressor is driven.

[0148] The compressor of the fifth embodiment differs from the compressor CMP' of the fourth embodiment only in that the compressor CMP' of the fifth embodiment includes first bushes 1053, 1073 instead of the first bushes 53, 73.

[0149] The first bush 1053, 1073 corresponds to the first bush 53, 73 with the addition of grooves 1053f, 1073f. To explain in more detail, the first side surface 1053a, 1073a of the first bush 1053, 1073 faces the first blade 51b, 71b. The grooves 1053f, 1073f are provided in the vertical center of the first side surface 1053a, 1073a. The grooves 1053f, 1073f extend from the compression chambers 1150b, 1170b side toward the first and second back pressure spaces 1055, 1075 side. The extension direction of the grooves 1053f, 1073f is perpendicular to the extension direction of the grooves 1053c, 1073c. In other words, the extension direction of the grooves 1053f, 1073f is parallel to the upper and lower surfaces of the partition plate 1060. One end of the grooves 1053f, 1073f is connected to the grooves 53c, 73c. ​​Meanwhile, the other end of the grooves 1053f, 1073f is connected to the edge of the first side surface 1053a, 1073a on the side of the first and second back pressure spaces 1055, 1075. The first side surface 1053a, 1073a is an example of a first opposing surface. The grooves 1053f, 1073f are an example of a second oil groove.

[0150] The compressor having the above configuration has the same configuration as that of the fourth embodiment, and therefore provides the same effects as those of the fourth embodiment.

[0151] Furthermore, by providing the grooves 1053f, 1073f in the first side surfaces 1053a, 1073a, a part of the lubricating oil in the grooves 53c, 73c flows into the grooves 1053f, 1073f when the compressor is driven. As a result, the lubricating oil is more likely to spread from the compression chambers 1150b, 1170b toward the first and second back pressure spaces 1055, 1075.

[0152] In the above-described fifth embodiment, the grooves 1053f, 1073f are provided in the vertical center of the first side surfaces 1053a, 1073a, but they may be provided above (toward the front head 1040) the vertical center of the first side surfaces 1053a, 1073a. In this case, it is possible to increase the reliability of the supply of lubricating oil to the upper portions of the first side surfaces 1053a, 1073a.

[0153] In the fifth embodiment, the grooves 1053f, 1073f extend in parallel to the upper and lower surfaces of the partition plate 1060. However, the grooves 1053f, 1073f may extend in a direction inclined relative to the upper and lower surfaces of the partition plate 1060.

[0154] In the fifth embodiment, the number of each of the grooves 1053f and 1073f is one, but there may be more than one. Sixth Embodiment Fig. 20 is a schematic diagram of a vertical cross section around the second bushes 2054, 2074 of the first and second cylinders 1050, 1070 according to the sixth embodiment of the present disclosure. Note that the arrows in Fig. 20 indicate the flow of lubricating oil when the compressor is driven.

[0155] The compressor of the sixth embodiment differs from the compressor CMP' of the fourth embodiment only in that the compressor CMP' of the sixth embodiment includes second bushes 2054, 2074 instead of the second bushes 1054, 1074.

[0156] The second bush 2054, 2074 corresponds to the second bush 1054, 1074 to which grooves 1054f, 2074f are added. More specifically, the first side surface 1054a, 1074a of the second bush 2054, 2074 faces the first blade 51b, 71b. The grooves 2054f, 2074f are provided in the vertical center of the first side surface 1054a, 1074a. The grooves 2054f, 2074f extend from the first and second back pressure spaces 1055, 1075 side toward the suction chambers 1150a, 1170a side. The extension direction of the grooves 2054f, 2074f is parallel to the upper and lower surfaces of the partition plate 1060. Also, one end of the groove 2054f, 2074f is connected to the edge of the first side surface 2054a, 2074a on the first and second back pressure spaces 2055, 2075 side. On the other hand, the other end of the groove 2054f, 2074f is not connected to the edge of the first side surface 2054a, 2074a on the suction chamber 1150a, 1170a side. In other words, the edge of the first side surface 2054a, 2074a on the suction chamber 1150a, 1170a side is closer to the suction chamber 1150a, 1170a than the other end of the groove 2054f, 2074f. Also, the other end of the groove 2054f, 2074f is located on the suction chamber 1150a, 1170a side with respect to the center in the width direction of the first side surface 2054a, 2074a. First side surfaces 2054a, 2074a are an example of a second opposing surface. Grooves 2054f, 2074f are an example of a third oil groove.

[0157] The compressor having the above configuration has the same configuration as that of the fourth embodiment, and therefore provides the same effects as those of the fourth embodiment.

[0158] Furthermore, by providing the grooves 2054f, 2074f on the first side surfaces 2054a, 2074a of the second bushings 2054, 2074, a portion of the lubricating oil in the first and second back pressure spaces 2055, 2075 flows into the grooves 2054f, 2074f when the compressor is in operation. As a result, the lubricating oil is more likely to spread from the first and second back pressure spaces 1055, 1075 toward the suction chambers 1150a, 1170a.

[0159] Furthermore, by not connecting the other ends of the grooves 2054f, 2074f to the edges of the first side surfaces 2054a, 2074a on the suction chambers 1150a, 1170a side, it is possible to prevent the lubricating oil in the grooves 2054f, 2074f from flowing into the suction chambers 1150a, 1170a.

[0160] In the sixth embodiment, the grooves 2054f, 2074f extend in a direction parallel to the upper and lower surfaces of the partition plate 1060. However, the grooves 2054f, 2074f may extend in a direction inclined toward the upper and lower surfaces of the partition plate 1060.

[0161] In the sixth embodiment, the number of each of the grooves 2054f and 2074f is one, but there may be more than one.

[0162] In the above sixth embodiment, the other ends of the grooves 2054f, 2074f were located on the suction chamber 1150a, 1170a side relative to the widthwise center of the first side surfaces 2054a, 2074a, but they may also be located on the first and second back pressure spaces 2055, 2075 side relative to the widthwise center of the first side surfaces 2054a, 2074a.

[0163] Although specific embodiments of the present disclosure have been described, the present disclosure is not limited to the above first to sixth embodiments, and various modifications can be made within the scope of the present disclosure. For example, an appropriate combination of the contents described in the above first to sixth embodiments may be one embodiment of the present disclosure.

[0164] More specifically, for example, similar to the modified example of the first embodiment, the compressor CMP' may be a swing piston type rotary compressor having a one-cylinder configuration.

[0165] Moreover, in the refrigerant circuit RC of the third embodiment, the compressor CMP' of the third embodiment may be used in place of the compressor CMP of the first embodiment.

[0166] Moreover, the compressor of the fifth embodiment may be provided with the second bushes 2054, 2074 of the sixth embodiment instead of the second bushes 1054, 1074. [Explanation of symbols]

[0167] 1. Airtight container 2,1102 Compression mechanism 3 Motor 4 Flow divider 5 1st suction pipe 6 Second suction pipe 7 Discharge pipe 14 Oil Reservoir 20,1020 Rotation axis 20a 1st eccentric part 20b 2nd eccentric part 21 1st oil supply path 22 2nd oil supply path 23 3rd oil supply path 31 Stator 32 Rotor 40,1040 Front Head 50,1050 No. 1 cylinder 60 Partition 70,1070 No. 2 cylinder 80 Rear Head 51 First oscillator 51a 1st piston 51b First Blade 52,1052 First blade space 53,73,1053,1073 1st Bush 53a,73a,1053a,1073a,2054a,2074a 1st side 53c,73c,1053f,1073f,2054f,2074f groove 54,74,1054,1074,2054,2074 2nd Bush 55,1055 First back pressure space 61 1st oil supply path 62 2nd oil supply path 71 Second oscillator 71a 2nd piston 71b 2nd Blade 72,1072 Second blade space 75,1075 Second back pressure space 150,1150 First cylinder chamber 150a,170a,1150a,1170a Suction chamber 150b,170b,150b,170b compression chamber 170,1170 Second cylinder chamber CMP, CMP' compressor RC refrigerant circuit

Claims

1. A cylinder (50, 70); a first end plate (40) disposed on one side of the cylinder (50, 70) in the axial direction; a second end plate (80) disposed on the other axial side of the cylinder (50, 70); a cylinder chamber (150, 170) defined by an inner peripheral surface of the cylinder (50, 70); a piston (51a, 71a) accommodated in the cylinder chamber (150, 170) and swinging along an inner circumferential surface of the cylinder (50, 70); a blade (51b, 71b) which, together with the piston (51a, 71a), divides the cylinder chamber (150, 170) into a high pressure side region (150b, 170b) and a low pressure side region (150a, 170a); a blade space (52, 72) provided in the cylinder (50, 70), the radially inner end of which is connected to the cylinder chamber (150, 170) and communicates with the cylinder chamber (150, 170), and through which the blade (51 b, 71 b) advances and retreats; a back pressure space (55, 75) provided in the cylinder (50, 70), having a radially inner end connected to a radially outer end of the blade space (52, 72) and communicating with the cylinder chamber (150, 170) and the blade space (52, 72), and through which the blade (51 b, 71 b) advances and retreats; first and second bushes (53, 73, 54, 74) disposed in the blade space (52, 72) and sandwiching the blade (51b, 71b); a casing (1) that houses the cylinder (50, 70), the first end plate (40) and the second end plate (80); an oil reservoir (14) provided within the casing (1) for storing oil; a rotating shaft (20) that is inserted through the cylinder (50, 70), the first end plate (40) and the second end plate (80) and has a first oil passage (21, 23) that communicates with the oil reservoir (14); Equipped with The opening of the back pressure space (55, 75) on the first end plate (40) side is sealed by the first end plate (40), while the opening of the back pressure space (55, 75) on the second end plate (80) side is sealed by the second end plate (80). The oil in the oil reservoir (14) is supplied to the first and second bushes (53, 73, 54, 74) through the first oil passages (21, 23), The cylinders (50, 70) include a first cylinder (50) that is closer to the first end plate (40) than the second end plate (80) and a second cylinder (70) that is closer to the second end plate (80) than the first end plate (40), In the compressor (CMP), an intermediate plate (60) disposed between the first cylinder (50) and the second cylinder (70) is provided with second oil passages (61, 62) for guiding oil from the first oil passages (21, 23) to the first and second bushes (53, 73, 54, 74).

2. 2. The compressor according to claim 1, a high-pressure side region (150b, 170b) of the cylinder chamber (150, 170) communicates with a region of the blade space (52, 72) on the side of the first bush (53, 73), while a low-pressure side region (150a, 170a) of the cylinder chamber (150, 170) communicates with a region of the blade space (52, 72) on the side of the second bush (54, 74), The compressor, wherein a groove (254f, 274f) extending in a circumferential direction is provided on a peripheral surface of the second bush (54, 74) opposite to the blade (51b, 71b).

3. Equipped with a compressor (CMP) according to claim 1 or 2, Refrigeration equipment.

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