compressor

Abstract

To provide a compressor capable of ensuring reliability.SOLUTION: A compressor is equipped with a compression mechanism that has a piston rotor 41 changing the capacity of a compression chamber 423, and a crank portion 72 provided inside the piston rotor 41. The compression mechanism compresses a refrigerant sucked into the compression chamber 423 from a first space and discharges it to a second space if a rotary shaft rotates in a first rotating direction R1, and compresses a refrigerant sucked into the compression chamber 423 from the second space and discharges it to the first space if the rotary shaft rotates in a second rotating direction R2. The crank portion 72 is formed with a lead-out hole 742 leading out oil into a clearance between the piston rotor 41 and the load-out hole 742. A part opposite to the piston rotor 41 in the crank portion 72 is divided into a first area AR1 and a second area AR2 by a virtual line IL passing through an axis CL of the rotary shaft and a center Cr of the crank portion 72. At that time, the lead-out hole 742 opens to both the first area AR1 and the second area AR2.SELECTED DRAWING: Figure 18

Description

Technical Field

[0001] The present disclosure relates to a compressor that compresses and discharges a fluid.

Background Art

[0002] Conventionally, a rotary compressor capable of compressing a fluid in either the forward or reverse rotation direction is known (see, for example, Patent Document 1). The reversible rotary compressor described in this Patent Document 1 includes a cylinder, a piston rotor disposed inside the cylinder, a crank portion disposed inside the piston rotor and eccentric with respect to the rotation axis of the piston rotor, a slide vane, and the like.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In a compressor configured as in Patent Document 1, the piston rotor and the crank portion have a sliding structure. The inventors of the present invention considered forming an oil outlet hole in the crank portion and supplying oil to the gap between the piston rotor and the crank portion.

[0005] According to the study by the inventors of the present invention, it was found that depending on the opening position of the oil outlet hole in the crank portion, the oil outlet hole may be closed by the load acting on the piston rotor during compression of the refrigerant (hereinafter also referred to as the compression load). The blockage of the oil outlet hole inhibits the supply of oil to the gap between the piston rotor and the crank portion, which is a factor that reduces the reliability of the compressor, and thus is not preferable.

[0006] An object of the present disclosure is to provide a compressor capable of ensuring reliability.

Means for Solving the Problems

[0007] The invention described in claim 1 is, A compressor that compresses and discharges a fluid, A housing (20) having a first inlet / outlet section (831) and a second inlet / outlet section (832) through which fluid flows in and out, A rotating shaft (70) housed in a housing and rotatably supported, The device comprises an annular cylinder (42), a piston rotor (41) that changes the volume of a compression chamber (423) formed inside the cylinder as the rotating shaft rotates, and a compression mechanism (40) having a crank section (72) provided inside the piston rotor eccentrically with respect to the axis of the rotating shaft. The compression mechanism is such that the rotating shaft rotates in the first rotational direction. (R1) When it rotates, the fluid drawn into the compression chamber from the first inlet / outlet is compressed and discharged to the second inlet / outlet, and the rotating shaft rotates in the second direction opposite to the first direction of rotation. (R2) When it rotates, it compresses the fluid drawn into the compression chamber from the second inlet / outlet and discharges it to the first inlet / outlet. The crank section has an oil outlet hole (742) formed in it to guide oil into the gap between the crank section and the piston rotor. When the portion of the crank section facing the piston rotor is divided into a first region and a second region by an imaginary line passing through the axis of the rotating shaft and the center of the crank section, The oil outlet holes are open in both the first and second regions. The first inlet / outlet section contains a first oil reservoir for storing oil. (861) A system was established, The second inlet / outlet section contains a second oil reservoir for storing oil. (862) A system was established, The compression mechanism is configured such that when the rotating shaft rotates in the first rotational direction, oil stored in the second oil reservoir is supplied to the oil outlet hole, and when the rotating shaft rotates in the second rotational direction, oil stored in the first oil reservoir is supplied to the oil outlet hole.

[0008] As mentioned above, in this type of compressor, a compressive load acts due to changes in the refrigerant pressure in the compression chamber. This compressive load pushes the piston rotor toward either the first or second region in the crank section.

[0009] Specifically, the piston rotor is pressed against one region of the crank section when the rotating shaft rotates in the first rotational direction, and against the other region when the rotating shaft rotates in the second rotational direction. Therefore, if the oil outlet hole is open to only one of the first and second regions of the crank section, the oil outlet hole is more likely to become blocked when the rotating shaft rotates in the first rotational direction. Also, if the oil outlet hole is open to only the other of the first and second regions of the crank section, the oil outlet hole is more likely to become blocked when the rotating shaft rotates in the second rotational direction.

[0010] Taking these factors into consideration, the compressor of this disclosure has a structure in which the oil outlet hole opens to both the first and second regions of the crank section. This makes it less likely for the oil outlet hole to become blocked, thereby ensuring the reliability of the compressor.

[0011] The invention described in claim 6 is, A compressor that compresses and discharges a fluid, A housing (20) having a first inlet / outlet section (831) and a second inlet / outlet section (832) through which fluid flows in and out, A rotating shaft (70) housed in a housing and rotatably supported, The device comprises an annular cylinder (42), a piston rotor (41) that changes the volume of a compression chamber (423) formed inside the cylinder as the rotating shaft rotates, and a compression mechanism (40) having a crank section (72) provided inside the piston rotor eccentrically with respect to the axis of the rotating shaft. The compression mechanism is such that the rotating shaft rotates in the first rotational direction. (R1) When it rotates, the fluid drawn into the compression chamber from the first inlet / outlet is compressed and discharged to the second inlet / outlet, and the rotating shaft rotates in the second direction opposite to the first direction of rotation. (R2)When it rotates to [specific direction], it has a structure that compresses the fluid inhaled from the second inlet / outlet part into the compression chamber and discharges it to the first inlet / outlet part. In the crank part, a first discharge part (745) and a second discharge part (746) are formed as oil discharge holes (742) for discharging oil to a part facing the piston rotor. The first discharge part and the second discharge part open at different positions in the circumferential direction of the crank part. In the first inlet / outlet part, a first oil storage part for storing oil (861) is provided. In the second inlet / outlet part, a second oil storage part for storing oil (862) is provided. The compression mechanism is configured such that when the rotating shaft rotates in the first rotation direction, the oil stored in the second oil storage part is supplied to the oil discharge hole, and when the rotating shaft rotates in the second rotation direction, the oil stored in the first oil storage part is supplied to the oil discharge hole.

[0012] If it is configured like this, even if one of the first discharge hole and the second discharge hole is blocked by the piston rotor, the oil supply between the piston rotor and the crank part can be continued through the other of the first discharge hole and the second discharge hole. Therefore, according to the compressor of the present disclosure, the reliability of the compressor can be ensured.

[0013] The reference numerals with parentheses attached to each component etc. show an example of the correspondence relationship between the component etc. and the specific components etc. described in the embodiments described later.

Brief Description of the Drawings

[0014] [Figure 1] It is a schematic configuration diagram showing the state in the heating mode of a refrigeration cycle device according to the first embodiment. [Figure 2] It is a schematic configuration diagram showing the state in the cooling mode of a refrigeration cycle device according to the first embodiment. [Figure 3] It is a schematic axial cross-sectional view of a compressor according to the first embodiment. [Figure 4] It is a cross-sectional view taken along line IV-IV of FIG. 3. [Figure 5] It is a cross-sectional view taken along line V-V of FIG. 3. [Figure 6] It is a cross-sectional view taken along line VI-VI of FIG. 3. [Figure 7] It is a cross-sectional view taken along line VII-VII of FIG. 3. [Figure 8] It is a cross-sectional view taken along line VIII-VIII of FIG. 7. [Figure 9] It is a cross-sectional view taken along line IX-IX of FIG. 7. [Figure 10] It is a cross-sectional view taken along line X-X of FIG. 3. [Figure 11] It is a cross-sectional view taken along line XI-XI of FIG. 3. [Figure 12] It is a cross-sectional view taken along line XII-XII of FIG. 3. [Figure 13] It is a cross-sectional view taken along line XIII-XIII of FIG. 3. [Figure 14] It is a schematic cross-sectional view of the compression mechanism of the comparative example of the first embodiment. [Figure 15] It is an enlarged view of a part of FIG. 14. [Figure 16] It is an explanatory diagram for explaining the compression load acting on the piston rotor when the rotating shaft is rotated in the first rotation direction in the compression mechanism of the comparative example. [Figure 17] It is an explanatory diagram for explaining the compression load acting on the piston rotor when the rotating shaft is rotated in the second rotation direction in the compression mechanism of the comparative example. [Figure 18] It is a schematic cross-sectional view of the compression mechanism of the first embodiment. [Figure 19] It is an explanatory diagram for explaining the compression load acting on the piston rotor when the rotating shaft is rotated in the first rotation direction in the compression mechanism of the first embodiment. [Figure 20] It is an explanatory diagram for explaining the compression load acting on the piston rotor when the rotating shaft is rotated in the second rotation direction in the compression mechanism of the first embodiment. [Figure 21] It is a schematic cross-sectional view of the compression mechanism of the second embodiment. [Figure 22]This is a schematic side view of the crank section of the second embodiment. [Figure 23] This is an explanatory diagram illustrating the compression load acting on the piston rotor when the rotating shaft is rotated in the first rotational direction in the compression mechanism of the second embodiment. [Figure 24] This is an explanatory diagram illustrating the compression load acting on the piston rotor when the rotating shaft is rotated in the second rotational direction in the compression mechanism of the second embodiment. [Figure 25] This is a schematic cross-sectional view of a compression mechanism which is a first modified example of the second embodiment. [Figure 26] This is a schematic side view of the crank section, which is a second modified example of the second embodiment. [Figure 27] This is a schematic side view of the crank section, which is a third modified example of the second embodiment. [Figure 28] This is a cross-sectional view of XXVIII-XXVIII in Figure 27. [Figure 29] This is an explanatory diagram illustrating the compression load acting on the piston rotor during cooling mode. [Figure 30] This is an explanatory diagram illustrating the compressive load acting on the piston rotor during heating mode. [Figure 31] This is a schematic cross-sectional view of the compression mechanism of the third embodiment. [Figure 32] This is a schematic cross-sectional view of a compression mechanism which is a modified example of the third embodiment. [Figure 33] This is a schematic cross-sectional view of the compression mechanism of the fourth embodiment. [Figure 34] This is an explanatory diagram illustrating the compression load acting on the piston rotor when the rotating shaft is rotated in the first rotational direction in the compression mechanism of the fourth embodiment. [Figure 35] This is an explanatory diagram illustrating the compression load acting on the piston rotor when the rotating shaft is rotated in the second rotational direction in the compression mechanism of the fourth embodiment. [Figure 36] This is a schematic axial cross-sectional view of the compressor according to the fifth embodiment. [Modes for carrying out the invention]

[0015] Embodiments of this disclosure will be described below with reference to the drawings. In the following embodiments, parts that are the same as or equivalent to those described in the prior embodiments will be denoted by the same reference numerals, and their descriptions may be omitted. Also, if only a part of a component is described in an embodiment, the components described in the prior embodiments can be applied to the other parts of that component. The following embodiments can be partially combined with each other, even if not explicitly stated, as long as it does not impede the combination.

[0016] (First Embodiment) This embodiment will be described with reference to Figures 1 to 20. In this embodiment, an example will be described in which the compressor 10 and the refrigeration cycle device 1 including the compressor 10 of this disclosure are applied to a seat air conditioning system mounted in a vehicle. The seat air conditioning system is a device that is located inside or below the seat of a vehicle and supplies warm or cold air to the front side of the seat where the occupant sits.

[0017] The refrigeration cycle device 1 is a vapor compression type refrigeration cycle and is configured as a heat pump cycle that can switch between a heating mode, which supplies warm air toward the front side of the sheet, and a cooling mode, which supplies cold air toward the front side of the sheet.

[0018] As shown in Figures 1 and 2, the refrigeration cycle device 1 includes a compressor 10, a first heat exchanger 11, a throttling device 12, a second heat exchanger 13, refrigerant piping 14, and a control device (not shown). The refrigeration cycle device 1 employs fluorocarbon refrigerants such as R134a and R1234yf, or natural refrigerants such as carbon dioxide, as refrigerants.

[0019] Here, the compressor 10 needs to be lubricated appropriately because the clearance around the bearings of the compression mechanism 40 and the parts forming the compression chamber 423 is small and contact is likely to occur. Taking this into consideration, the refrigerant is mixed with oil to lubricate the sliding parts of the compressor 10. A portion of the oil circulates within the cycle together with the refrigerant.

[0020] The compressor 10 compresses and discharges a refrigerant fluid. The compressor 10 is a bidirectional compressor capable of compressing the fluid in either forward or reverse rotation. The compressor 10 is an electric compressor comprising a housing 20 that forms the outer shell, a compression mechanism 40 that compresses the refrigerant, and an electric motor 30 that drives the compression mechanism 40. The housing 20 has a first connection port 81 and a second connection port 82 to which the refrigerant piping 14 is connected. The first connection port 81 and the second connection port 82 constitute the inlet and outlet of the refrigerant. Specifically, as shown in Figure 1, in heating mode, the first connection port 81 becomes the refrigerant outlet (i.e., discharge port), and the second connection port 82 becomes the refrigerant inlet (i.e., suction port). Also, as shown in Figure 2, in cooling mode, the first connection port 81 becomes the refrigerant inlet (i.e., suction port), and the second connection port 82 becomes the refrigerant outlet (i.e., discharge port). Details of the compressor 10 will be described later.

[0021] The first heat exchanger 11 is connected to the first connection port 81 via the refrigerant piping 14. The first heat exchanger 11 is a user-side heat exchanger located inside the air conditioning case 15. The first heat exchanger 11 exchanges heat between the refrigerant and the air blown from the blower 16 located in the air conditioning case 15. In heating mode, the first heat exchanger 11 functions as a heat radiator that dissipates heat by exchanging heat between the high-pressure refrigerant discharged from the compressor 10 and the blown air, and in cooling mode, it functions as a heat absorber that absorbs heat by exchanging heat between the low-pressure refrigerant, which has been reduced in pressure by the throttling device 12, and the blown air.

[0022] The second heat exchanger 13 is connected to the second connection port 82 via the refrigerant piping 14. The second heat exchanger 13 is an external heat exchanger located outside the air conditioning case 15. The second heat exchanger 13 exchanges heat between the refrigerant and the air outside the air conditioning case 15. In cooling mode, the second heat exchanger 13 functions as a heat radiator that dissipates heat by exchanging high-pressure refrigerant with the air outside the air conditioning case 15, and in heating mode, it functions as a heat absorber that absorbs heat by exchanging low-pressure refrigerant with the air outside the air conditioning case 15.

[0023] The throttling device 12 is a pressure reducing device that reduces the pressure of the refrigerant that has been heated by the first heat exchanger 11 or the second heat exchanger 13. The throttling device 12 is composed of a fixed throttling device such as a capillary tube or an orifice. However, the throttling device 12 may be composed of a variable throttling device.

[0024] In the refrigeration cycle device 1 configured in this way, during heating mode, the air blown from the blower 16 is heated in the first heat exchanger 11 until it becomes warm air, and this warm air is supplied to the surface side of the sheet. In addition, during cooling mode, the refrigeration cycle device 1 cools the air blown from the blower 16 in the first heat exchanger 11 until it becomes cold air, and this cold air is supplied to the surface side of the sheet.

[0025] Next, the details of the compressor 10 will be explained with reference to Figure 3, etc. Figure 3 is an axial cross-sectional view obtained by cutting the compressor 10 vertically along the axis CL of the rotating shaft 70. The arrows indicating vertical in Figure 3, etc., indicate the vertical direction when the compressor 10 is mounted on a vehicle. As shown in Figure 3, the compressor 10 is positioned such that the axis CL of the rotating shaft 70 is approximately coincided with the horizontal direction. Hereinafter, the direction extending along the axis CL of the rotating shaft 70 will be referred to as the axial direction DRa. In this specification, the rotation angle of the rotating shaft 70 is defined as the angle with respect to the top dead center. Regarding the rotation angle of the rotating shaft 70, the rotation angle of the rotating shaft 70 when rotating in the first rotation direction R1 may be indicated by a positive angle, and the rotation angle of the rotating shaft 70 when rotating in the second rotation direction R2 may be indicated by a negative angle.

[0026] The housing 20 includes a main housing 21 and a sub-housing 22 positioned at both ends of the axial DRa, as well as a first middle housing 23, a second middle housing 24, and a third middle housing 25 positioned between them. The housing 20 has a sealed container structure in which the main housing 21, sub-housing 22, first middle housing 23, second middle housing 24, and third middle housing 25 are hermetically fastened together by fastening means such as bolts (not shown).

[0027] The main housing 21 is positioned on one side of the axial direction DRa. The main housing 21 has a closed-bottom cylindrical shape with the other side of the axial direction DRa open. A second connection port 82 is formed at the bottom of the main housing 21. An electric motor 30 is housed inside the main housing 21.

[0028] The main housing 21 has an inner diameter that gradually increases as it approaches the opening, from the electric motor 30 to the opening, so that the refrigerant can easily flow toward the compression mechanism 40.

[0029] The sub-housing 22 is positioned on the other side of the axial DRa. That is, the sub-housing 22 is positioned on the opposite side of the compression mechanism 40 from the main housing 21. The sub-housing 22 is plate-shaped. A first connection port 81 is formed in the sub-housing 22.

[0030] The first middle housing 23 is positioned adjacent to the main housing 21 so as to cover the entire opening of the main housing 21. A rotating shaft 70 passes through the approximately central part of the first middle housing 23. A sealing member 29 is positioned between the inner surface of the first middle housing 23 and the rotating shaft 70.

[0031] The second middle housing 24 is positioned between the sub-housing 22 and the compression mechanism 40. The second middle housing 24 has a through-hole formed in its approximate central portion through which the rotating shaft 70 passes. A first sliding bearing 431 that rotatably supports the rotating shaft 70 is positioned in this through-hole. The second middle housing 24 has a first space 831 that communicates with the first connection port 81. The first space 831 communicates with the first connection port 81 by a first connection flow path 833, and refrigerant flows in or out through the first connection flow path 833 and the first connection port 81. In this embodiment, the first space 831 constitutes a first inlet / outlet section in the housing 20 through which fluid flows in and out.

[0032] The third middle housing 25 is positioned between the first middle housing 23 and the compression mechanism 40. The third middle housing 25 has a through hole formed in its approximate central portion through which the rotating shaft 70 passes. A second sliding bearing 432 that rotatably supports the rotating shaft 70 is positioned in this through hole. The third middle housing 25 has a second space 832 that communicates with the second connection port 82. The second space 832 communicates with the second connection port 82 by a second connection flow path 834, and refrigerant flows in or out through the second connection flow path 834 and the second connection port 82. In this embodiment, the second space 832 constitutes a second inflow / outflow section in the housing 20 through which fluid flows in and out.

[0033] The rotating shaft 70 is housed in the housing 20. The rotating shaft 70 is rotatably supported by a first sliding bearing 431 and a second sliding bearing 432 located inside the housing 20.

[0034] The rotating shaft 70 is composed of a cylindrical main shaft 71 centered on the axis CL, and a crank section 72 provided midway along the main shaft 71 and eccentric with respect to the axis CL. The main shaft 71 is supported by a first sliding bearing 431 and a second sliding bearing 432. The crank section 72 is an eccentric shaft and is a compression mechanism 40 It is located inside the cylinder 42. The crank section 72 functions as part of the compression mechanism 40. The axis CL of the rotating shaft 70 is the axis of rotation of the main shaft 71.

[0035] The rotating shaft 70 has a compression mechanism 40An oil supply passage 74 is formed to supply oil to the sliding parts. The oil supply passage 74 has a main supply hole 741 extending along the axis CL of the rotating shaft 70, an outlet hole 742 opening to the outside of the rotating shaft 70 and communicating with the main supply hole 741, a first inlet hole 743, and a second inlet hole 744. The first inlet hole 743 opens to the part of the rotating shaft 70 facing the first sliding bearing 431. The second inlet hole 744 opens to the part of the rotating shaft 70 facing the second sliding bearing 432. The outlet hole 742 opens to the part of the rotating shaft 70 facing the piston rotor 41. In this embodiment, the outlet hole 742 constitutes an oil outlet hole that leads oil into the gap between the crank section 72 and the piston rotor 41. Details of the outlet hole 742 will be described later.

[0036] The electric motor 30 is housed in the main housing 21. The electric motor 30 has a stator 31 and a movable element 32. The electric motor 30 is a bidirectional motor that can change the direction of rotation of the movable element 32 by changing the energization configuration of the stator 31. The electric motor 30 is an inner rotor type motor. Specifically, the stator 31 is fixed to the inner wall of the housing 20. The movable element 32 is fixed to the rotating shaft 70 inside the stator 31.

[0037] In the electric motor 30 configured in this way, when power is supplied to the stator 31 from an inverter (not shown), a rotating magnetic field is generated that rotates the movable element 32, and this rotating magnetic field causes the movable element 32 and the rotating shaft 70 to rotate together.

[0038] The compression mechanism 40 is located between the second middle housing 24 and the third middle housing 25. Specifically, the compression mechanism 40 is located between the first space 831 and the second space 832 so as to be aligned with the axial DRa of the rotating shaft 70.

[0039] The compression mechanism 40 has a rolling piston type structure in which the compression chamber 423 is separated into high-pressure and low-pressure zones by vanes 43 installed on the cylinder 42 side. As shown in Figures 3, 4, and 5, the compression mechanism 40 is composed of a piston rotor 41, a cylinder 42, vanes 43, and a biasing spring 44.

[0040] The piston rotor 41 functions as a rolling piston. The piston rotor 41 is fitted onto the crank portion 72 of the rotating shaft 70. Like the crank portion 72, the piston rotor 41's central axis is eccentric with respect to the axis CL of the rotating shaft 70. The piston rotor 41 revolves around the inner surface of the cylinder 42 in response to the rotation of the rotating shaft 70.

[0041] The cylinder 42 has a compression chamber 423 formed inside it for compressing the refrigerant. The cylinder 42 has a cylinder body 42a with a cylindrical hole formed therein, and a pair of side plates 42b and 42c that close the cylindrical hole formed in the cylinder body 42a. The compression chamber 423 is partitioned by the cylinder body 42a and the pair of side plates 42b and 42c.

[0042] As shown in Figures 6, 7, and 8, the cylinder 42 has a first communication section 421 that connects the compression chamber 423 to the first space 831. Also, as shown in Figures 11 and 12, the cylinder 42 has a second communication section 422 that connects the compression chamber 423 to the second space 832. The first communication section 421 and the second communication section 422 are formed at different locations on the cylinder 42 so that they do not communicate with each other.

[0043] The first connecting portion 421 and the second connecting portion 422 are closed by the side of the piston rotor 41 when the piston rotor 41 is at top dead center, and are opened when the piston rotor 41 is in a position away from top dead center. Top dead center is the state in which the center Cr of the piston rotor 41 is closest to the vane groove 424. Bottom dead center is the state in which the center Cr of the piston rotor 41 is furthest from the vane groove 424.

[0044] As shown in Figure 8, the first communication portion 421 is formed in the cylinder 42 in a portion that overlaps with the compression chamber 423 and the first space 831 in the axial direction DRa. The first communication portion 421 extends linearly along the axial direction DRa. Specifically, the first communication portion 421 is composed of a through hole that penetrates the side plate 42b and a bottomed hole provided in the cylinder body 42a.

[0045] The second communication section 422 is formed in the cylinder 42 at a point where it overlaps with the compression chamber 423 and the second space 832 in the axial direction DRa. The second communication section 422 extends linearly along the axial direction DRa. Specifically, the second communication section 422 is composed of a through hole that penetrates the side plate 42c and a bottomed hole provided in the cylinder body 42a.

[0046] As shown in Figures 4 and 5, the cylinder 42 has a vane groove 424 formed therein that slidably receives the vane 43. The vane groove 424 is formed in the upper wall portion of the inner wall that forms the compression chamber 423 in the cylinder 42. The vane groove 424 extends vertically so that the vane 43 can slide vertically.

[0047] In the cylinder 42, a pressure chamber 425 is formed by the inner wall of the vane groove 424 and the rear end surface of the vane 43. A biasing spring 44 is positioned in the pressure chamber 425 to bias the front surface of the vane 43 toward the piston rotor 41.

[0048] Furthermore, the cylinder 42 has a first communication passage 841 that connects the pressure chamber 425 and the first space 831, and a second communication passage 842 that connects the pressure chamber 425 and the second space 832. The first communication passage 841 and the second communication passage 842 are formed at different locations in the cylinder 42 so that they do not communicate with each other.

[0049] As shown in Figures 4, 6, 9, and 10, the pressure chamber 425 and the first space 831 are connected by a first communication passage 841. As shown in Figure 9, a first check valve 851 is provided in the middle of the first communication passage 841. The first communication passage 841 allows the flow of refrigerant from the first space 831 to the pressure chamber 425, while prohibiting the flow of refrigerant from the pressure chamber 425 to the first space 831. This first check valve 851 is a reed valve that opens in only one direction. The maximum opening degree of the first check valve 851 is restricted by a stopper 853 provided adjacent to the first check valve 851. The first check valve 851 and the stopper 853 are fixed to the housing 20 by fastening members 855 such as bolts.

[0050] As shown in Figures 5, 11, 12, and 13, the pressure chamber 425 and the second space 832 are connected by a second communication passage 842. A second check valve 852 is provided in the middle of the second communication passage 842. The second check valve 852 allows the flow of refrigerant from the second space 832 to the pressure chamber 425, while prohibiting the flow of refrigerant from the pressure chamber 425 to the second space 832. This second check valve 852 is a reed valve that opens in only one direction. The maximum opening degree of the second check valve 852 is restricted by a stopper 854 provided adjacent to the second check valve 852. The second check valve 852 and the stopper 854 are fixed to the housing 20 by fastening members such as bolts.

[0051] With this structure, regardless of the rotation direction of the rotating shaft 70, high-pressure refrigerant generated by the compression mechanism 40 is introduced into the pressure chamber 425 from either the first communication passage 841 or the second communication passage 842. As a result, the vanes 43 are biased toward the piston rotor 41 by the pressure in the pressure chamber 425, in addition to the biasing force from the biasing spring 44.

[0052] The vane 43 is a separating member that separates the compression chamber 423 into a first chamber 423a communicating with a first communication section 421 and a second chamber 423b communicating with a second communication section 422. The vane 43 seals the first chamber 423a and the second chamber 423b by the pressure in the pressure chamber 425 into which the refrigerant generated by the operation of the compression mechanism 40 is introduced. The vane 43 has a tip surface that contacts the piston rotor 41. The vane 43 is housed in a vane groove 424 and is displaceable in a direction toward the axis CL of the rotating shaft 70 and in a direction toward the axis CL. The vane 43 is displaced to the position furthest from the axis CL when the piston rotor 41 is at top dead center and to the position closest to the axis CL when the piston rotor 41 is at bottom dead center.

[0053] Here, as shown in Figures 7 and 8, a first discharge valve 531 is located in the first space 831. The first discharge valve 531 allows the flow of refrigerant from the first space 831 of the compression chamber 423 to the first communication section 421 when the pressure in the first space 831 of the compression chamber 423 rises to a predetermined first valve opening pressure, while preventing the flow of refrigerant from the first communication section 421 to the compression chamber 423. In other words, the first discharge valve 531 has a backflow prevention function that prevents the flow of refrigerant from the first communication section 421 to the compression chamber 423.

[0054] The first discharge valve 531 is a reed valve that opens in only one direction. The maximum opening of the first discharge valve 531 is restricted by a first stopper 521 provided adjacent to the first discharge valve 531. The first discharge valve 531 is fixed to the first movable member 541 together with the first stopper 521.

[0055] The first movable member 541 is partially exposed to the first space 831 and is subjected to the pressure of the first space 831, and is also subjected to the pressure of the second space 832 introduced through the second pressure introduction hole 892, thereby allowing it to be displaced in the axial direction DRa of the rotating shaft 70.

[0056] Specifically, the first movable member 541 is inserted into a bottomed first recess 426 formed on one end face of the cylinder 42, located on the other side of the axial direction DRa, so as to be displaceable in the axial direction DRa. A guide pin 543 is integrally connected to the first movable member 541 to prevent rotation of the first movable member 541. This guide pin 543 is inserted into a first pin groove 427 provided in the cylinder 42.

[0057] A second pressure introduction hole 892 is formed at the bottom of the first groove 426, connecting the first groove 426 and the second space 832. The second pressure introduction hole 892 extends along the axial direction DRa of the rotating shaft 70. A first biasing member 551 is positioned in the first groove 426 to bias the first discharge valve 531 toward a position where the backflow prevention function of the first discharge valve 531 is not activated. The first biasing member 551 displaces the first discharge valve 531 to a position where the backflow prevention function of the first discharge valve 531 is not activated when the rotating shaft 70 is stopped. The position where the backflow prevention function of the first discharge valve 531 is not activated is the position where the first discharge valve 531 is separated from the cylinder 42. The position where the backflow prevention function of the first discharge valve 531 is activated is the position where the first discharge valve 531 is in contact with the cylinder 42.

[0058] As shown in Figure 12, a second discharge valve 532 is located in the second space 832. The second discharge valve 532 allows refrigerant to flow from the second space 832 to the second communication section 422 of the compression chamber 423 when the pressure in the second space 832 of the compression chamber 423 rises to a predetermined second valve opening pressure, while preventing refrigerant from flowing from the second communication section 422 to the compression chamber 423. In other words, the second discharge valve 532 has a backflow prevention function that prevents refrigerant from flowing from the second communication section 422 to the compression chamber 423. The second valve opening pressure may be the same as or different from the first valve opening pressure.

[0059] The second discharge valve 532 is a reed valve that opens in only one direction. The maximum opening of the second discharge valve 532 is restricted by a second stopper 522 provided adjacent to the second discharge valve 532. The second discharge valve 532 is fixed to the second movable member 542 together with the second stopper 522.

[0060] The second movable member 542 is partially exposed to the second space 832 and is subjected to the pressure of the second space 832, and is also subjected to the pressure of the first space 831 introduced through the first pressure introduction hole 891, thereby allowing it to be displaced in the axial direction DRa of the rotating shaft 70.

[0061] Specifically, the second movable member 542 is inserted into a bottomed second groove 428 formed on the other end face of the cylinder 42, which is located on one side in the axial direction DRa, so as to be displaceable in the axial direction DRa. A guide pin 544 is integrally connected to the second movable member 542 to prevent rotation of the second movable member 542. This guide pin 544 is inserted into a second pin groove 429 provided in the cylinder 42.

[0062] A first pressure introduction hole 891 is formed at the bottom of the second groove 428, connecting the second groove 428 and the first space 831. The first pressure introduction hole 891 extends along the axial DRa of the rotating shaft 70. A second biasing member 552 is positioned in the second groove 428 to bias the second discharge valve 532 toward a position where the backflow prevention function of the second discharge valve 532 is not activated. The second biasing member 552 is positioned so that the backflow prevention function of the second discharge valve 532 is not activated when the rotating shaft 70 is stopped. Second discharge valve 532 This displaces the second discharge valve 532. The position in which the backflow prevention function of the second discharge valve 532 is not performed is when the second discharge valve 532 is separated from the cylinder 42. The position in which the backflow prevention function of the second discharge valve 532 is performed is when the second discharge valve 532 is in contact with the cylinder 42.

[0063] In the compressor 10 of this embodiment, the first movable member 541, the second movable member 542, the first biasing member 551, and the second biasing member 552 constitute a function switching unit 54 that switches the backflow prevention function of the first discharge valve 531 and the backflow prevention function of the second discharge valve 532 on and off.

[0064] In a compressor 10 capable of rotation in both directions, the discharge port during forward rotation becomes the intake port during reverse rotation. Therefore, if each of the discharge valves 531 and 532 functions even during reverse rotation, it becomes impossible to draw refrigerant from the intake port. In contrast, the compressor 10 of this embodiment is equipped with a function switching unit 54, which allows refrigerant to be drawn in from the intake port even if each of the discharge valves 531 and 532 is provided.

[0065] Here, the first space 831 is provided with a first oil reservoir 861 on its lower side for storing oil. This first oil reservoir 861 communicates with the oil supply passage 74 and the sliding portion of the compression mechanism 40 via the first oil passage 871 and the gap between the first sliding bearing 431 and the rotating shaft 70.

[0066] The first oil passage 871 is formed between the sub-housing 22 and the second middle housing 24. The first oil passage 871 extends from the first oil reservoir 861 to a through hole 241 in the second middle housing 24 through which the rotating shaft 70 passes.

[0067] The gap between the first sliding bearing 431 and the rotating shaft 70 is a fine throttling passage with a smaller passage area for oil passage compared to the first oil passage 871. The gap between the first sliding bearing 431 and the rotating shaft 70 constitutes a first pressure reduction section that reduces the pressure of the oil flowing from the first oil reservoir 861 toward the sliding part of the compression mechanism 40. By having a structure that allows oil to pass through the gap between the first sliding bearing 431 and the rotating shaft 70 in this way, it is possible to supply oil to the first sliding bearing 431 while suppressing the flow of refrigerant from the first oil reservoir 861 into the compression chamber 423.

[0068] Furthermore, the second space 832 is provided with a second oil reservoir 862 located below it, which stores oil. This second oil reservoir 862 communicates with the oil supply passage 74 and the sliding portion of the compression mechanism 40 via the second oil passage 872 and the gap between the second sliding bearing 432 and the rotating shaft 70.

[0069] The second oil passage 872 is formed between the first middle housing 23 and the third middle housing 25. The second oil passage 872 extends from the second oil reservoir 862 to a through hole 251 in the third middle housing 25 through which the rotating shaft 70 passes.

[0070] The gap between the second sliding bearing 432 and the rotating shaft 70 is a fine throttling passage with a smaller passage area for oil passage compared to the second oil passage 872. The gap between the second sliding bearing 432 and the rotating shaft 70 constitutes a second pressure reduction section that reduces the pressure of the oil flowing from the second oil reservoir 862 toward the sliding part of the compression mechanism 40. By structuring the gap between the second sliding bearing 432 and the rotating shaft 70 in this way, it is possible to supply oil to the second sliding bearing 432 while suppressing the flow of refrigerant from the second oil reservoir 862 into the compression chamber 423.

[0071] The oil stored in each oil reservoir 861 and 862 is guided to the main supply hole 741 of the oil supply passage 74 through the inlet holes 743 and 744 located inside each sliding bearing 431 and 432. The oil guided to the main supply hole 741 is supplied to the gap between the piston rotor 41 and the crank section 72 through the outlet hole 742. This suppresses wear caused by sliding between the piston rotor 41 and the crank section 72.

[0072] The inventors diligently studied the supply of oil to the gap between the piston rotor 41 and the crank section 72 during the operation of the compression mechanism 40 in order to ensure smooth sliding between the piston rotor 41 and the crank section 72. Their studies revealed that, depending on the opening position of the outlet hole 742 in the crank section 72, the load acting on the piston rotor 41 during refrigerant compression (hereinafter also referred to as the compression load) can cause the outlet hole 742 to close.

[0073] The closure of the outlet hole 742 will be explained below with reference to Figures 14 to 17. Figures 14 to 17 show the schematic cross-sectional shape of a compression mechanism CE that is a comparative example of this embodiment. For ease of understanding, in Figures 14 to 17, components of the comparative example compression mechanism CE that correspond to the compression mechanism 40 of this embodiment are denoted by the same reference numerals as the compression mechanism 40 of this embodiment.

[0074] As shown in Figure 14, the comparative example compression mechanism CE has a single outlet hole OH formed in the crank portion 72. The outlet hole OH extends from the outer surface of the crank portion 72 toward the center Cr of the crank portion 72.

[0075] In the comparative example compression mechanism CE, a compressive load Fc acts on the piston rotor 41 due to the pressure difference between the first chamber 423a and the second chamber 423b of the compression chamber 423 formed when the refrigerant is compressed. This compressive load Fc acts from the high-pressure side to the low-pressure side of the first chamber 423a and the second chamber 423b. When the compressive load Fc acts on the piston rotor 41, for example, as shown in Figure 15, the gap between the part of the piston rotor 41 facing the second space 832, which is at low pressure, and the crank section 72 expands.

[0076] In this embodiment, the portion of the crank section 72 facing the piston rotor 41 is divided into two regions, a first region AR1 and a second region AR2, by a virtual line IL passing through the axis CL of the rotating shaft 70 and the center Cr of the crank section 72. Of the pair of intersections where the portion of the crank section 72 facing the piston rotor 41 intersects with the virtual line IL, the intersection furthest from the axis CL of the rotating shaft 70 is designated as the first intersection CP1, and the intersection closer to the axis CL of the rotating shaft 70 is designated as the second intersection CP2. The first region AR1 is the portion of the crank section 72 facing the piston rotor 41, extending from the second intersection CP2 along the first rotation direction R1 to the first intersection CP1. The second region AR2 is the portion of the crank section 72 facing the piston rotor 41, extending from the first intersection CP1 along the first rotation direction R1 to the second intersection CP2.

[0077] When the rotating shaft 70 rotates in the first rotational direction R1, the compressive load Fc acts to press the piston rotor 41 against the second region AR2 of the crank section 72, as shown in Figure 16. Therefore, when the rotating shaft 70 rotates in the first rotational direction R1, the gap between the piston rotor 41 and the crank section 72 is more likely to widen in the first region AR1 than in the second region AR2.

[0078] Taking these factors into consideration, in the comparative example compression mechanism CE, the oil outlet hole OH is provided on the crank section 72 so as to open into the first region AR1 of the crank section 72. With this configuration, when the rotating shaft 70 is rotated in the first rotational direction R1, oil can be supplied to the gap between the crank section 72 and the piston rotor 41 via the outlet hole OH.

[0079] However, if the compression mechanism CE of the comparative example is configured to allow fluid compression in either the forward or reverse rotation direction, the outlet hole OH may become blocked on the inner surface of the piston rotor 41 when the rotating shaft 70 rotates in the second rotation direction R2, which is opposite to the first rotation direction R1. This is because the compression load Fc when the rotating shaft 70 rotates in the second rotation direction R2 acts to press the piston rotor 41 against the first region AR1 of the crank section 72, as shown in Figure 17. Blockage of the outlet hole OH is undesirable because it hinders the supply of oil to the gap between the piston rotor 41 and the crank section 72, which reduces the reliability of the compressor 10.

[0080] Taking these factors into consideration, the compression mechanism 40 of this embodiment, as shown in Figure 18, has a first outlet section 745 and a second outlet section 746 formed as outlet holes 742 for guiding oil out at the portion of the crank section 72 facing the piston rotor 41. The first outlet section 745 and the second outlet section 746 open at different positions in the circumferential direction of the crank section 72.

[0081] In this embodiment, the first outlet portion 745 opens into the first region AR1 of the crank portion 72, and the second outlet portion 746 opens into the second region AR2 of the crank portion 72. Thus, the outlet hole 742 in this embodiment includes the first outlet portion 745 that opens into the first region AR1 of the crank portion 72 and the second outlet portion 746 that opens into the second region AR2.

[0082] In this embodiment, the first outlet portion 745 opens in the crank portion 72 at the point where the greatest load is applied to the piston rotor 41 when the rotating shaft 70 is rotating in the first rotational direction R1, and the outlet portion 746 opens in the crank portion 72 at the point where the greatest load is applied to the piston rotor 41 when the rotating shaft 70 is rotating in the second rotational direction R25 opens in the crank portion 72 at the point where the greatest load is applied to the piston rotor 41.

[0083] Specifically, the first outlet portion 745 opens on the opposite side of the center Cr of the crank portion 72 from the portion of the crank portion 72 where the load from the piston rotor 41 is greatest when the rotating shaft 70 is rotating in the first rotational direction R1. The second outlet portion 746 is formed to be symmetrical to the first outlet portion 745 with respect to the imaginary line IL. Furthermore, the first outlet portion 745 and the second outlet portion 746 are formed in the approximate central portion of the axial direction DRa of the crank portion 72.

[0084] Next, the operation of the refrigeration cycle device 1 and the compressor 10 will be explained with reference to Figures 1, 2, 19, 20, etc.

[0085] [Cooling mode] In the refrigeration cycle device 1, during cooling mode, the rotary shaft 70 of the compressor 10 is rotated in the first rotational direction R1. As a result, as shown in Figure 2, the refrigerant compressed in the compressor 10 to high temperature and pressure flows into the second heat exchanger 13 for heat dissipation. After passing through the second heat exchanger 13, the refrigerant is reduced to a desired pressure by the throttling device 12 and then flows into the first heat exchanger 11. The refrigerant flowing into the first heat exchanger 11 absorbs heat from the air blown from the blower 16 and evaporates. At this time, the air blown from the blower 16 is cooled and supplied to the surface side of the sheet. The refrigerant evaporated in the first heat exchanger 11 is then drawn back into the compressor 10. hand It will be compressed.

[0086] Specifically, in cooling mode, when the compressor 10 is powered by the electric motor 30, the rotating shaft 70 rotates from the top dead center position shown in Figure 19 in the first rotation direction R1, and refrigerant is drawn from the first space 831 through the first communication section 421 into the first chamber 423a of the compression chamber 423. The suction process of drawing refrigerant into the first chamber 423a is completed when the piston rotor 41 rotates again to the top dead center position. After the completion of the refrigerant suction process, when the rotating shaft 70 rotates in the first rotation direction R1, the refrigerant is compressed in the second chamber 423b. The refrigerant compressed in the second chamber 423b is discharged into the second space 832 through the second communication section 422. The refrigerant discharged into the second space 832 is then discharged from the second connection port 82 towards the second heat exchanger 13 via the second connection passage 834 which constitutes the motor chamber.

[0087] In cooling mode, the first space 831 becomes a low-pressure space, and the second space 832 becomes a high-pressure space. As the second space 832 becomes more high-pressure than the first space 831, the first movable member 541 and the second movable member 542 are displaced to the other side of the axial DRa. As a result, in cooling mode, the first discharge valve 531 is displaced to a position away from the cylinder 42 where the backflow prevention function is not performed, and the second discharge valve 532 is displaced to a position in contact with the cylinder 42 where the backflow prevention function is performed.

[0088] Furthermore, in cooling mode, the second space 832 becomes high pressure, and the refrigerant in the second space 832 is introduced into the pressure chamber 425 via the second communication passage 842. Also, since the first check valve 851 is provided in the first communication passage 841, the refrigerant in the pressure chamber 425 does not flow into the first space 831. As a result, the pressure chamber 425 is maintained at high pressure, and the vane 43 is biased toward the piston rotor 41 by the pressure in the pressure chamber 425 in addition to the biasing force from the biasing spring 44.

[0089] Furthermore, in cooling mode, the oil stored in the second oil reservoir 862 of the second space 832 flows into the oil supply passage 74 via the second oil passage 872 and the gap between the second sliding bearing 432 and the rotating shaft 70. At this time, the gap between the second sliding bearing 432 and the rotating shaft 70 becomes a second pressure reduction section, so the oil supply passage 74 has an intermediate pressure lower than that of the second space 832. The oil that flows into the oil supply passage 74 is supplied to the gap between the piston rotor 41 and the crank section 72 via the outlet hole 742.

[0090] In cooling mode, as shown in Figure 19, the compression load Fc acts to press the piston rotor 41 against the second region AR2 of the crank section 72. As a result, the second outlet section 746 may be blocked by the piston rotor 41, but the first outlet section 745 is separated from the piston rotor 41, so oil is supplied to the gap between the crank section 72 and the piston rotor 41 via the first outlet section 745.

[0091] The oil supplied to the gap between the crankshaft 72 and the piston rotor 41 flows to the low-pressure side of the compression chamber 423 through a gap formed inside the compression mechanism 40. This lubricates the components that make up the compression chamber 423. The oil that flows into the compression chamber 423 is compressed again with the refrigerant and returns to the second space 832, where it is stored in the second oil reservoir 862.

[0092] [Heating mode] In heating mode, the refrigeration cycle unit 1 rotates the compressor 10's rotating shaft 70 in the second rotation direction R2. As a result, as shown in Figure 1, the refrigerant compressed in the compressor 10 to high temperature and pressure flows into the first heat exchanger 11 and condenses by releasing heat into the air blown from the blower 16. At this time, the air blown from the blower 16 is heated and supplied to the surface side of the sheet. After passing through the first heat exchanger 11, the refrigerant is reduced to a desired pressure by the throttling device 12 and then flows into the second heat exchanger 13. The refrigerant that flows into the second heat exchanger 13 absorbs heat from outside the air conditioning case 15 and evaporates. The refrigerant evaporated in the second heat exchanger 13 is then drawn back into the compressor 10. hand It will be compressed.

[0093] Specifically, in heating mode, when the compressor 10 is rotated by the electric motor 30, the rotating shaft 70 rotates from the top dead center position shown in Figure 20 in the second rotation direction R2, and refrigerant is drawn from the second space 832 to the second chamber 423b of the compression chamber 423 via the second communication section 422. The suction process of drawing refrigerant into the second chamber 423b is completed when the piston rotor 41 rotates again to the top dead center position. After the completion of the refrigerant suction process, when the rotating shaft 70 rotates in the second rotation direction R2, the refrigerant is compressed in the first chamber 423a. The refrigerant compressed in the first chamber 423a is discharged to the first space 831 via the first communication section 421. The refrigerant discharged to the first space 831 is then discharged from the first connection port 81 towards the first heat exchanger 11 via the first connection flow path 833.

[0094] In heating mode, the first space 831 becomes a high-pressure space, and the second space 832 becomes a low-pressure space. As the first space 831 becomes more high-pressure than the second space 832, the first movable member 541 and the second movable member 542 are displaced to one side in the axial direction DRa. As a result, in heating mode, the first discharge valve 531 is displaced to a position where it contacts the cylinder 42 and the backflow prevention function is activated, and the second discharge valve 532 is displaced to a position where it moves away from the cylinder 42 and the backflow prevention function is not activated.

[0095] Furthermore, in heating mode, the first space 831 becomes high pressure, and the refrigerant in the first space 831 is introduced into the pressure chamber 425 via the first communication passage 841. In addition, since the second check valve 852 is provided in the second communication passage 842, the refrigerant in the pressure chamber 425 does not flow into the second space 832. As a result, the pressure chamber 425 is maintained at high pressure, and the vane 43 is biased toward the piston rotor 41 by the pressure in the pressure chamber 425 in addition to the biasing force from the biasing spring 44.

[0096] Furthermore, in heating mode, the oil stored in the first oil reservoir 861 of the first space 831 flows into the oil supply passage 74 through the first oil passage 871 and the gap between the first sliding bearing 431 and the rotating shaft 70. At this time, the gap between the first sliding bearing 431 and the rotating shaft 70 becomes the first pressure reduction section, so the oil supply passage 74 has an intermediate pressure lower than that of the first space 831. The oil that flows into the oil supply passage 74 is supplied to the gap between the piston rotor 41 and the crank section 72 through the outlet hole 742.

[0097] In heating mode, as shown in Figure 20, the compression load Fc acts to press the piston rotor 41 against the first region AR1 of the crank section 72. As a result, the first outlet 745 may be blocked by the piston rotor 41, but the second outlet 746 is separated from the piston rotor 41, so oil is supplied to the gap between the crank section 72 and the piston rotor 41 via the second outlet 746.

[0098] The oil supplied to the gap between the crankshaft 72 and the piston rotor 41 flows to the low-pressure side of the compression chamber 423 through a gap formed inside the compression mechanism 40. This lubricates the components that make up the compression chamber 423. The oil that flows into the compression chamber 423 is compressed again with the refrigerant and returns to the first space 831, where it is stored in the first oil reservoir 861.

[0099] [Service suspended] When the refrigeration cycle device 1 is stopped, the rotating shaft 70 of the compressor 10 stops rotating, and the first space 831 and the second space 832 communicate with each other via the refrigerant piping 14 and the inside of the compression mechanism 40, etc., and the pressure in the first space 831 and the second space 832 is equalized. In this state, the compressor 10 is displaced such that the first movable member 541 is displaced to the other side of the axial DRa by the first biasing member 551, and the second movable member 542 is displaced to one side of the axial DRa by the second biasing member 552. As a result, when the rotating shaft 70 is stopped, the first discharge valve 531 and the second discharge valve 532 are displaced to a position where they are separated from the cylinder 42 and the backflow prevention function is not performed.

[0100] The compressor 10 described above includes a compression mechanism 40. The compression mechanism 40 is structured to compress the refrigerant drawn into the compression chamber 423 from the first communication section 421 when the rotating shaft 70 rotates in the first rotational direction R1, and discharge it to the second communication section 422. The compression mechanism 40 is also structured to compress the refrigerant drawn into the compression chamber 423 from the second communication section 422 when the rotating shaft 70 rotates in the second rotational direction R2, which is opposite to the first rotational direction R1, and discharge it to the first communication section 421. Furthermore, the crank section 72 has an outlet hole 742 formed in the gap between the crank section 72 and the piston rotor 41 for guiding oil out. This outlet hole 742 opens into both the first region AR1 and the second region AR2 of the crank section 72. This makes it less likely for the outlet hole 742 to become blocked, thus ensuring the reliability of the compressor 10.

[0101] Furthermore, the compressor 10 of this embodiment has the following features.

[0102] (1) The outlet hole 742 includes a first outlet portion 745 that opens into the first region AR1 and a second outlet portion 746 that opens into the second region AR2. With this configuration, even if one of the first outlet portion 745 and the second outlet portion 746 is blocked by the piston rotor 41, the supply of oil between the piston rotor 41 and the crankshaft 72 can be continued through the other of the first outlet portion 745 and the second outlet portion 746.

[0103] (2) The first outlet section 745 opens at a point in the crank section 72 where the greatest load is applied to the piston rotor 41 when the rotating shaft 70 is rotating in the first rotational direction R1, and the outlet section 746 opens at a point in the crank section 72 where the greatest load is applied to the piston rotor 41 when the rotating shaft 70 is rotating in the second rotational direction R2, and the outlet section 746 opens at a point in the crank section 72 where the outlet section 746 opens at a point in the crank section 72 where the greatest load is applied to the piston rotor 41 when the rotating shaft 70 is rotating in the first rotational direction R1. With this configuration, when the rotating shaft 70 is rotating in the first rotational direction R1, the supply of oil between the piston rotor 41 and the crank section 72 can be continued through the first outlet section 745. Furthermore, when the rotating shaft 70 is rotating in the second rotational direction R2, the supply of oil between the piston rotor 41 and the crank section 72 can be continued through the second outlet section 746.

[0104] (3) The first outlet 745 and the second outlet 746 open at different positions in the circumferential direction of the crank section 72. In this configuration, even if one of the outlets 745 or 746 is blocked by the piston rotor 41, the supply of oil between the piston rotor 41 and the crank section 72 can be continued through the other outlet 745 or 746.

[0105] (4) The compressor 10 includes a first discharge valve 531, a second discharge valve 532, and a function switching unit 54 that switches between enabling and disabling the backflow prevention function of the first discharge valve 531 and the backflow prevention function of the second discharge valve 532. The function switching unit 54 enables the backflow prevention function of the second discharge valve 532 and disables the backflow prevention function of the first discharge valve 531 when the rotating shaft 70 rotates in the first rotation direction R1. The function switching unit 54 also enables the backflow prevention function of the first discharge valve 531 and disables the backflow prevention function of the second discharge valve 532 when the rotating shaft 70 rotates in the second rotation direction R2.

[0106] With this configuration, refrigerant can be drawn into the compression chamber 423 from one of the two communication sections, the first communication section 421 and the second communication section 422, where the backflow prevention function is disabled. The refrigerant, pressurized to the desired pressure in the compression chamber 423, can then be discharged to the other communication section where the backflow prevention function is enabled. Therefore, a compressor 10 capable of compressing refrigerant in both forward and reverse rotation directions can be realized with a simple structure without omitting the discharge valves 531 and 532.

[0107] (5) The function switching unit 54 includes a first movable member 541 that is displaced by the pressure difference of the refrigerant generated by the operation of the compression mechanism 40, and a second movable member 542 that is displaced by the pressure difference of the refrigerant generated by the operation of the compression mechanism 40. The first movable member 541 is connected to the first discharge valve 531. The first movable member 541 displaces the first discharge valve 531 to a position where the backflow prevention function is not activated when the rotating shaft 70 rotates in the first rotation direction R1, and displaces the first discharge valve 531 to a position where the backflow prevention function is activated when it rotates in the second rotation direction R2. The second movable member 542 is connected to the second discharge valve 532. The second movable member 542 displaces the second discharge valve 532 to a position where the backflow prevention function is activated when the rotating shaft 70 rotates in the first rotation direction R1, and displaces the second discharge valve 532 to a position where the backflow prevention function is not activated when it rotates in the second rotation direction R2.

[0108] In this way, by utilizing the pressure difference generated by the operation of the compression mechanism 40, the backflow prevention function of each discharge valve 531, 532 can be switched on and off without adding a dedicated actuator or the like.

[0109] (6) The compression mechanism 40 is positioned between the first space 831 and the second space 832 so as to be aligned with the axial DRa of the rotating shaft 70. The first movable member 541 is partially exposed to the first space 831 and receives pressure from the first space 831, and is also displaceable in the axial DRa of the rotating shaft 70 by receiving pressure from the second space 832 introduced through the second pressure introduction hole 892. The second movable member 542 is partially exposed to the second space 832 and receives pressure from the second space 832, and is also displaceable in the axial DRa of the rotating shaft 70 by receiving pressure from the first space 831 introduced through the first pressure introduction hole 891.

[0110] In this way, by arranging the compression mechanism 40 between the first space 831 and the second space 832, the pressure inlet holes 891 and 892 are less likely to interfere with each other, thus ensuring flexibility in the installation position of each pressure inlet hole 891 and 892.

[0111] (7) The first pressure inlet hole 891 and the second pressure inlet hole 892 extend along the axial DRa of the rotating shaft 70. By constructing each pressure inlet hole 891 and 892 as a straight hole in this way, the structure is simple and processing costs can be reduced.

[0112] (8) When the rotating shaft 70 is stopped, the function switching unit 54 disables the backflow prevention function of the first discharge valve 531 and the backflow prevention function of the second discharge valve 532, respectively. By disabling the backflow prevention function of the first discharge valve 531 and the backflow prevention function of the second discharge valve 532 when the rotating shaft 70 is stopped, it is possible to promote the equalization of the refrigerant pressure inside the compressor 10 when the compressor 10 is stopped. This contributes, for example, to shortening the time required to switch the rotation direction of the compressor 10.

[0113] (9) The function switching unit 54 includes a first biasing member 551 that biases the first discharge valve 531 toward a position where the backflow prevention function is not performed, and a second biasing member 552 that biases the second discharge valve 532 toward a position where the backflow prevention function is not performed. The first biasing member 551 displaces the first discharge valve 531 toward a position where the backflow prevention function is not performed when the rotating shaft 70 is stopped. The second biasing member 552 also displaces the second discharge valve 532 toward a position where the backflow prevention function is not performed when the rotating shaft 70 is stopped. With this configuration, the deactivation of the backflow prevention function of the first discharge valve 531 and the backflow prevention function of the second discharge valve 532 when the rotating shaft 70 is stopped can be achieved with a simple configuration.

[0114] (10) The compression mechanism 40 includes vanes 43 that separate the compression chamber 423 into a first chamber 423a communicating with a first communication section 421 and a second chamber 423b communicating with a second communication section 422. The vanes 43 seal the first chamber 423a and the second chamber 423b by the pressure of the pressure chamber 425 into which the refrigerant is introduced by the operation of the compression mechanism 40. The first space 831 communicates with the compression chamber 423 via the first communication section 421 and with the pressure chamber 425 via the first communication passage 841. The first communication passage 841 is configured by a first check valve 851 to allow the flow of refrigerant from the first space 831 to the pressure chamber 425 and to prevent the flow of refrigerant from the pressure chamber 425 to the first space 831. The second space 832 communicates with the compression chamber 423 via the second communication section 422 and with the pressure chamber 425 via the second communication passage 842. The second communication passage 842 is controlled by a second check valve 852, which allows the flow of refrigerant from the second space 832 to the pressure chamber 425 and prevents the flow of refrigerant from the pressure chamber 425 to the second space 832. When the rotating shaft 70 rotates in the first rotational direction R1, high-pressure refrigerant discharged from the compression chamber 423 to the second space 832 via the second communication section 422 is introduced into the pressure chamber 425 via the second communication passage 842. Also, when the rotating shaft 70 rotates in the second rotational direction R2, high-pressure refrigerant discharged from the compression chamber 423 to the first space 831 via the first communication section 421 is introduced into the pressure chamber 425 via the first communication passage 841.

[0115] According to this, when the rotating shaft 70 is rotating, high-pressure refrigerant is introduced into the pressure chamber 425 via the first communication passage 841 or the second communication passage 842. The presence of check valves 851 and 852 prevents the pressure in the pressure chamber 425 from escaping through the communication passage with lower pressure among the two communication passages 841 and 842. As a result, the pressure chamber 425 is maintained at a high pressure when the rotating shaft 70 is rotating, so that sufficient sealing performance between the first chamber 423a and the second chamber 423b by the vane 43 can be ensured.

[0116] In a rolling piston compressor, the vanes 43 must always be pressed against the piston rotor 41 during operation. As the piston rotor 41 oscillates, the vertical movement of the vanes 43 becomes more violent as the rotational speed increases. To overcome this and keep the vanes 43 pressed against the piston rotor 41 requires a large load, and relying solely on the biasing spring 44 may lead to increased size and excessive pressure on the vanes 43 at low rotational speeds, potentially causing wear on the tips of the vanes 43. In a unidirectional rolling piston compressor, the back portion of the vanes 43 is connected to a high-pressure space, and the differential pressure with the compression chamber 423 is used to press the vanes 43 against the piston rotor 41. However, if the compressor rotates in both directions, the high-pressure space during forward rotation becomes a low-pressure space during reverse rotation, making it impossible to adopt the same structure as a unidirectional rolling piston compressor. The same applies to slide vane compressors.

[0117] Therefore, in this embodiment, the spaces 831 and 832 are connected to the pressure chamber 425, which is the back portion of the vane 43, via the check valves 851 and 852, and the pressure of the high-pressure refrigerant is introduced into the pressure chamber 425, and the differential pressure with respect to the compression chamber 423 is used to press the vane 43 against the piston rotor 41. The presence of the check valves 851 and 852 suppresses refrigerant leakage from the compression chamber 423 to the low-pressure side.

[0118] (11) The first space 831 is provided with a first oil reservoir 861 for storing oil mixed with the refrigerant. The first oil reservoir 861 is in communication with the sliding part of the compression mechanism 40 via a first pressure reduction section and a first oil passage 871. The second space 832 is provided with a second oil reservoir 862 for storing oil. The second oil reservoir 862 is in communication with the sliding part of the compression mechanism 40 via a second pressure reduction section and a second oil passage 872. When the rotating shaft 70 rotates in the first rotational direction R1, the oil stored in the second oil reservoir 862 is supplied to the sliding part of the compression mechanism 40 via the second pressure reduction section and the second oil passage 872 due to the pressure difference between the second space 832 and the compression chamber 423. Furthermore, oil stored in the first oil reservoir 861 is supplied to the sliding portion of the compression mechanism 40 via the first pressure reduction section and the first oil passage 871 due to the pressure difference between the first space 831 and the compression chamber 423 when the rotating shaft 70 rotates in the second rotation direction R2.

[0119] According to this, when the rotating shaft 70 is rotating, the oil stored in either the first oil reservoir 861 or the second oil reservoir 862 can be supplied to the sliding part of the compression mechanism 40 via either the first oil passage 871 or the second oil passage 872.

[0120] (12) The refrigeration cycle device 1 comprises the compressor 10 described above, a first heat exchanger 11 connected to a first connection port 81, a second heat exchanger 13 connected to a second connection port 82, and a throttling device 12 connected between the first heat exchanger 11 and the second heat exchanger 13. The refrigeration cycle device 1 also comprises refrigerant piping 14 connected to circulate the refrigerant between the compressor 10, the first heat exchanger 11, the throttling device 12, and the second heat exchanger 13.

[0121] According to this, a single compressor 10 can switch between a mode in which one heat exchanger acts as a heat absorber and the other as a heat radiator, and a mode in which one heat exchanger acts as a heat radiator and the other as a heat absorber, without adding a flow path switching valve to the cycle. This contributes to simplifying the cycle configuration.

[0122] (Modified version of the first embodiment) The first outlet portion 745 of the outlet hole 742 can be provided at any position in the first region AR1. The second outlet portion 746 of the outlet hole 742 can be provided at any position in the second region AR2.

[0123] The crank section 72 is not limited to having two openings as outlet holes 742, such as a first outlet section 745 and a second outlet section 746; for example, it may have three or more openings as outlet holes 742.

[0124] (Second Embodiment) Next, the second embodiment will be described with reference to Figures 21 to 24. This embodiment differs from the first embodiment in that a third outlet portion 747 is provided in the crank portion 72 as an outlet hole 742, instead of the first outlet portion 745 and the second outlet portion 746. In this embodiment, the differences from the first embodiment will be mainly described.

[0125] As shown in Figure 21, the crank section 72 has a single third outlet section 747 formed as an outlet hole 742 for guiding oil to the portion facing the piston rotor 41. The third outlet section 747 opens across both the first region AR1 and the second region AR2 of the crank section 72. In this embodiment, the third outlet section 747 opens at a position that includes the second intersection CP2 in the crank section 72.

[0126] Specifically, the third outlet portion 747 opens so as to span equally across both the first region AR1 and the second region AR2. As shown in Figure 22, the third outlet portion 747 is composed of a hole with a circular shape.

[0127] As shown in Figure 23, when the rotating shaft 70 rotates in the first rotational direction R1, the compressor 10 configured in this way has a compression load Fc that acts to press the piston rotor 41 against the second region AR2 of the crank section 72. Therefore, the second region AR2 side of the third outlet section 747 may be blocked by the piston rotor 41, but the first region AR1 side of the third outlet section 747 is separated from the piston rotor 41. Consequently, oil is supplied from the first region AR1 side of the third outlet section 747 to the gap between the crank section 72 and the piston rotor 41. The oil supplied to the gap between the crank section 72 and the piston rotor 41 flows to the low-pressure side of the compression chamber 423 through a gap formed inside the compression mechanism 40. This lubricates the components forming the compression chamber 423.

[0128] Furthermore, as shown in Figure 24, when the rotating shaft 70 of the compressor 10 rotates in the second rotation direction R2, the compression load Fc acts to press the piston rotor 41 against the first region AR1 of the crank section 72. As a result, the first region AR1 side of the third outlet section 747 may be blocked by the piston rotor 41, but the second region AR2 side of the third outlet section 747 is separated from the piston rotor 41. Therefore, oil is supplied from the second region AR2 side of the third outlet section 747 to the gap between the crank section 72 and the piston rotor 41. The oil supplied to the gap between the crank section 72 and the piston rotor 41 flows to the low-pressure side of the compression chamber 423 through a gap formed inside the compression mechanism 40. This lubricates the components forming the compression chamber 423.

[0129] Other aspects are the same as in the first embodiment. The compressor 10 of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a configuration common to or equivalent to that of the first embodiment.

[0130] Furthermore, the compressor 10 of this embodiment has the following features.

[0131] (1) The outlet hole 742 includes a third outlet portion 747 that opens across both the first region AR1 and the second region AR2. In this configuration, even if the portion of the third outlet portion 747 on the first region AR1 side is blocked by the piston rotor 41, oil can still be supplied between the piston rotor 41 and the crankshaft 72 through the portion on the second region AR2 side.

[0132] (2) Furthermore, the third outlet section 747 opens at a position that includes the second intersection CP2 in the crank section 72. Near the second intersection CP2, which is closer to the axis CL of the rotating shaft 70 among the pair of intersections in the crank section 72, the gap between the piston rotor 41 and the crank section 72 tends to widen due to the compression load Fc when the refrigerant is discharged from the compression chamber 423. For this reason, it is desirable that the third outlet section 747 opens near the second intersection CP1, CP2, which is closer to the axis CL of the rotating shaft 70 among the pair of intersections CP1 and CP2 with the imaginary line IL in the crank section 72.

[0133] (Modified version of the second embodiment) In the second embodiment, the details of the compression mechanism 40 were described, but the compression mechanism 40 is not limited to the one described above and can be modified as appropriate. For example, it can be modified as follows.

[0134] (First variation) The third outlet portion 747A may open at a position that includes the first intersection CP1 in the crank portion 72, rather than the second intersection CP2, as shown in Figure 25. Alternatively, the outlet hole 742 may be provided at a position that includes not only the first intersection CP1 in the crank portion 72, but also the second intersection CP2.

[0135] (Second variation) The third lead-out section 747B is composed of a hole with an elliptical shape, as shown in Figure 26, for example. This is also true when a lead-out hole 742 is provided at the second intersection CP2.

[0136] (Third variation) As shown in Figures 27 and 28, the crank section 72 has a D-shaped cross-section, and a flat section 748 is located at the opening of the third lead-out section 747. but It may be provided. If it is provided in this way, the blockage of the third outlet portion 747 by the piston rotor 41 can be prevented. However, if the gap between the piston rotor 41 and the crank portion 72 is too large near the third outlet portion 747, oil tends to accumulate in that gap, so it is desirable to keep the size of the flat portion 748 provided relative to the crank portion 72 to a minimum.

[0137] (Third embodiment) Next, a third embodiment will be described with reference to Figures 29 to 31. In this embodiment, the opening positions of the first outlet portion 745 and the second outlet portion 746 differ from those of the first embodiment. In this embodiment, the differences from the first embodiment will be mainly described.

[0138] In the refrigeration cycle device 1, the rotational speed of the compressor 10 is adjusted so that the refrigerant pressure on the suction side of the compressor 10 reaches a desired pressure during cooling mode. According to the inventors' calculations, for example, as shown in Figure 29, the refrigerant pressure is maximum when the rotation angle of the rotating shaft 70 with respect to top dead center is 238°. At this timing, the largest compressive load Fc (i.e., maximum load) acts on the piston rotor 41. When the rotation angle of the rotating shaft 70 in the first rotational direction R1 exceeds 238°, the area on the piston rotor 41 that receives the pressure of the discharged refrigerant decreases, and the compressive load Fc gradually decreases.

[0139] On the other hand, in heating mode, the rotational speed of the compressor 10 is adjusted so that the refrigerant pressure on the discharge side of the compressor 10 reaches a desired pressure. According to the inventors' calculations, for example, as shown in Figure 30, the refrigerant pressure is maximum when the rotation angle of the rotating shaft 70 in the second rotation direction R2 with respect to the top dead center is 265°. At this timing, the largest compressive load Fc (i.e., maximum load) acts on the piston rotor 41. When the rotation angle of the rotating shaft 70 exceeds 265°, the area on the piston rotor 41 that receives the pressure of the discharged refrigerant decreases, and the compressive load Fc gradually decreases.

[0140] Considering these factors, the first outlet section 745 of this embodiment opens at a position in the crank section 72 that is shifted 180° in the circumferential direction of the rotating shaft 70 from the position where the maximum load acts on the piston rotor 41 when the rotating shaft 70 is rotating in the first rotational direction R1. The second outlet section 746 opens at a position in the crank section 72 that is shifted 180° in the circumferential direction of the rotating shaft 70 from the position where the maximum load acts on the piston rotor 41 when the rotating shaft 70 is rotating in the second rotational direction R2. This allows for the proper and continuous supply of oil between the piston rotor 41 and the crank section 72 via either the first outlet section 745 or the second outlet section 746.

[0141] Specifically, the first derivation section 745 and the second derivation section 746 are formed asymmetrically on either side of the imaginary line IL, as shown in Figure 31. In other words, the rotation angle θa from the top dead center to the first derivation section 745 and the rotation angle θb from the top dead center to the second derivation section 746 do not coincide (θa > θb).

[0142] Other aspects are the same as in the first embodiment. The compressor 10 of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a configuration common to or equivalent to that of the first embodiment.

[0143] (Modified version of the third embodiment) As in the second embodiment, when the outlet hole 742 is composed of a third outlet portion 747, it is desirable that the third outlet portion 747 be opened such that the opening area of ​​the first region AR1 is larger than that of the second region AR2, for example, as shown in Figure 32.

[0144] (Fourth Embodiment) Next, the fourth embodiment will be described with reference to Figures 33 to 35. In this embodiment, the differences from the first embodiment will be mainly described.

[0145] As shown in Figure 33, the lead hole 742 is formed by a single through hole, with the first lead portion 745A and the second lead portion 746A being formed by a single through hole. Specifically, the first lead portion 745A and the second lead portion 746A are formed by a single through hole extending in a direction perpendicular to the virtual line IL. The through hole constituting the first lead portion 745A and the second lead portion 746A extends through the center Cr of the crank portion 72.

[0146] As shown in Figure 34, when the rotating shaft 70 rotates in the first rotational direction R1, the compressor 10 configured in this way has a compressive load Fc that acts to press the piston rotor 41 against the second region AR2 of the crank section 72. At this time, the second outlet section 746A may be blocked by the piston rotor 41, but the first outlet section 745A moves away from the piston rotor 41. Therefore, oil is supplied from the first outlet section 745A to the gap between the crank section 72 and the piston rotor 41.

[0147] Furthermore, as shown in Figure 35, when the rotating shaft 70 of the compressor 10 rotates in the second rotational direction R2, the compression load Fc acts to press the piston rotor 41 against the first region AR1 of the crank section 72. At this time, the first outlet section 745A may be blocked by the piston rotor 41, but the second outlet section 746A moves away from the piston rotor 41. Therefore, oil is supplied from the second outlet section 746A into the gap between the crank section 72 and the piston rotor 41.

[0148] Other aspects are the same as in the first embodiment. The compressor 10 of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a configuration common to or equivalent to that of the first embodiment.

[0149] Furthermore, the compressor 10 of this embodiment has the following features.

[0150] (1) The first outlet section 745A and the second outlet section 746A are formed by a single through hole. With this configuration, the reliability of the compressor 10 can be ensured in a simple form.

[0151] (Fifth embodiment) Next, the fifth embodiment will be described with reference to Figure 36. In this embodiment, the differences from the first and second embodiments will be mainly described.

[0152] In the first and second embodiments, the crank portion 72 is exemplified as having one outlet hole 742 formed approximately in the center of the axial DRa of the crank portion 72, but the crank portion 72 is not limited to this.

[0153] For example, as shown in Figure 36, the crank section 72 may have two outlet holes 742A and 742B arranged in the axial direction DRa of the crank section 72. The crank section 72 may also have three or more outlet holes 742. In this configuration, even if some of the outlet holes 742 are blocked by the piston rotor 41, oil can still be supplied to the gap between the piston rotor 41 and the crank section 72 through the other outlet holes 742.

[0154] Other aspects are the same as in the first embodiment. The compressor 10 of this embodiment can obtain the same effects as in the first embodiment, which are achieved from a configuration common to or equivalent to that of the first embodiment.

[0155] (Other embodiments) While representative embodiments of this disclosure have been described above, this disclosure is not limited to the embodiments described above and can be modified in various ways, for example, as follows.

[0156] As described in the above embodiment, it is desirable that the outlet hole 742 opens into both the first region AR1 and the second region AR2 in the crank portion 72, but this is not required.

[0157] As described in the above embodiment, it is desirable that the compressor 10 has a structure in which the pressure of the high-pressure refrigerant is introduced into the pressure chamber 425 and the differential pressure with the compression chamber 423 is used to press the vanes 43 against the piston rotor 41, but the compressor 10 is not limited to this. The compressor 10 may also have a structure in which the vanes 43 are pressed against the piston rotor 41 by biasing springs 44 alone.

[0158] In the embodiments described above, an example was shown in which oil is stored in the first space 831 and the second space 832, but the compressor 10 is not limited thereto. The compressor 10 may, for example, have oil stored in an oil tank installed outside the housing 20.

[0159] As described in the above-described embodiment, the compression mechanism 40 preferably includes a first discharge valve 531 and a second discharge valve 532, but is not limited to this, and at least one of the first discharge valve 531 and the second discharge valve 532 may be omitted.

[0160] The housing 20 in the above-described embodiment includes, for example, a main housing 21, a sub-housing 22, a first middle housing 23, a second middle housing 24, a third middle housing 25, etc., but it may have a different configuration.

[0161] Although the electric motor 30 in the above-described embodiment was configured as an inner rotor type motor, it is not limited to this, and may be configured as an outer rotor type motor in which the movable element 32 is arranged outside the stator 31, for example.

[0162] The compression mechanism 40 in the above-described embodiment had a rolling piston type structure, but is not limited to this and may be composed of other structures. The compression mechanism 40 may be driven by the output of a prime mover other than the electric motor 30 that can rotate in both forward and reverse directions.

[0163] The embodiments described above illustrate the application of the compressor 10 of the present disclosure to a refrigeration cycle device 1, but the applications of the compressor 10 of the present disclosure are not limited to this. The compressor 10 of the present disclosure can also be applied to devices other than the refrigeration cycle device 1 (for example, devices that compress fluids other than refrigerants).

[0164] In the embodiments described above, it goes without saying that the elements constituting the embodiments are not necessarily essential, except in cases where they are explicitly stated to be essential or where they are clearly considered essential in principle.

[0165] In the embodiments described above, if numerical values ​​such as the number, numerical values, quantities, or ranges of the components of the embodiment are mentioned, the embodiment is not limited to those specific numbers unless explicitly stated as particularly essential or clearly limited to a specific number in principle.

[0166] In the embodiments described above, when referring to the shape, positional relationships, etc. of the components, the definition is not limited to those shapes, positional relationships, etc., unless otherwise specifically stated or when the definition is fundamentally limited to a particular shape, positional relationship, etc. [Explanation of symbols]

[0167] 10 Compressor 20 Housing 40 Compression mechanism 41 Piston Rotor 43 cylinders 70 rotation shaft 72 Crank section 742 Outlet hole (oil outlet hole) 831 First space (first inflow and outflow section) 832 Second space (second inflow and outflow section)

Claims

1. A compressor that compresses and discharges a fluid, A housing (20) having a first inlet / outlet section (831) and a second inlet / outlet section (832) through which the fluid flows in and out, A rotating shaft (70) housed in the aforementioned housing and rotatably supported, The device comprises an annular cylinder (42), a piston rotor (41) that changes the volume of a compression chamber (423) formed inside the cylinder as the rotating shaft rotates, and a compression mechanism (40) having a crank portion (72) provided inside the piston rotor eccentrically with respect to the axis of the rotating shaft, The compression mechanism is configured such that when the rotating shaft rotates in a first rotational direction (R1), it compresses the fluid drawn into the compression chamber from the first inlet / outlet and discharges it to the second inlet / outlet, and when the rotating shaft rotates in a second rotational direction (R2) opposite to the first rotational direction, it compresses the fluid drawn into the compression chamber from the second inlet / outlet and discharges it to the first inlet / outlet. The crank section has oil outlet holes (742, 742A, 742B) formed therein to guide oil into the gap between the crank section and the piston rotor. When the portion of the crank section facing the piston rotor is divided into a first region and a second region by a virtual line passing through the axis of the rotating shaft and the center of the crank section, The oil outlet hole is open to both the first region and the second region. The first inlet / outlet section is provided with a first oil storage section (861) for storing oil. The second inlet / outlet section is provided with a second oil storage section (862) for storing oil. The compression mechanism is configured such that when the rotating shaft rotates in the first rotational direction, oil stored in the second oil reservoir is supplied to the oil outlet hole, and when the rotating shaft rotates in the second rotational direction, oil stored in the first oil reservoir is supplied to the oil outlet hole.

2. The compressor according to claim 1, wherein the oil outlet hole includes an outlet portion (747) that opens across both the first region and the second region.

3. When a pair of intersections between the portion of the crank section facing the piston rotor and the imaginary line intersect, the intersection furthest from the axis of the rotating shaft is designated as the first intersection, and the intersection closer to the axis of the rotating shaft is designated as the second intersection, The compressor according to claim 2, wherein the outlet portion opens at a position including the second intersection in the crank portion.

4. The compressor according to claim 1, wherein the oil outlet hole includes a first outlet portion (745) opening into the first region and a second outlet portion (746) opening into the second region.

5. The first outlet portion opens in the crank portion at the point where the greatest compressive load acts on the piston rotor when the rotating shaft is rotating in the first rotational direction, and the portion is separated from the piston rotor. The compressor according to claim 4, wherein the second outlet portion opens at a part of the crank portion that separates from the piston rotor at the timing when the largest compressive load is applied to the piston rotor when the rotating shaft is rotating in the second rotational direction.

6. A compressor that compresses and discharges a fluid, A housing (20) having a first inlet / outlet section (831) and a second inlet / outlet section (832) through which the fluid flows in and out, A rotating shaft (70) housed in the aforementioned housing and rotatably supported, The device comprises an annular cylinder (42), a piston rotor (41) that changes the volume of a compression chamber (423) formed inside the cylinder as the rotating shaft rotates, and a compression mechanism (40) having a crank portion (72) provided inside the piston rotor eccentrically with respect to the axis of the rotating shaft, The compression mechanism is configured such that when the rotating shaft rotates in a first rotational direction (R1), it compresses the fluid drawn into the compression chamber from the first inlet / outlet and discharges it to the second inlet / outlet, and when the rotating shaft rotates in a second rotational direction (R2) opposite to the first rotational direction, it compresses the fluid drawn into the compression chamber from the second inlet / outlet and discharges it to the first inlet / outlet. The crank section has oil outlet holes (742, 742A, 742A) formed in the part facing the piston rotor, which are first outlet sections (745, 745A) and second outlet sections (746, 746A). The first outlet and the second outlet open at different positions in the circumferential direction of the crank portion. The first inlet / outlet section is provided with a first oil storage section (861) for storing oil. The second inlet / outlet section is provided with a second oil storage section (862) for storing oil. The compression mechanism is configured such that when the rotating shaft rotates in the first rotational direction, oil stored in the second oil reservoir is supplied to the oil outlet hole, and when the rotating shaft rotates in the second rotational direction, oil stored in the first oil reservoir is supplied to the oil outlet hole.

7. The compressor according to claim 4 or 6, wherein the first outlet (745A) and the second outlet (746A) are formed by a single through hole.

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