JP2016156335A - Swash plate compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the resonance of discharge pulsation from generated by the annular shape of a discharge chamber.SOLUTION: A discharge chamber 32 is constructed by at least part of a peripheral wall 15b, and at least part of the discharge chamber 32 is formed between partition walls 15c neighboring each other in the peripheral direction of a rotating shaft 17 while extending from an inner peripheral face 15r of a rear housing 15 in the inward direction of the rear housing 15. Thus, the discharge chamber 32 is free from an annular shape. This prevents the resonance of discharge pulsation from generated by the annular shape of the discharge chamber 32.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a swash plate compressor.

  For example, as disclosed in Patent Document 1, a housing of a swash plate compressor includes a cylinder block, a front housing joined to one end of the cylinder block, and a valve / port formation body at the other end of the cylinder block. And a rear housing to be joined. A rotating shaft is rotatably supported in the housing. A swash plate chamber is defined between the cylinder block and the front housing. The swash plate chamber houses a swash plate that rotates by obtaining a driving force from a rotating shaft. A plurality of pistons are moored on the outer periphery of the swash plate. In the cylinder block, a plurality of cylinder bores in which the pistons are accommodated so as to reciprocate are formed around the rotation shaft.

  A suction chamber and a discharge chamber communicating with each cylinder bore are defined between the rear housing and the valve / port forming body. The discharge chamber is provided on the outer peripheral side of the suction chamber so as to extend around the suction chamber in an annular shape. Then, the refrigerant is sucked into each cylinder bore from the suction chamber by movement from the top dead center to the bottom dead center side in each piston, and the refrigerant in each cylinder bore by the movement from the bottom dead center to the top dead center side in each piston. Are compressed in each cylinder bore and discharged into the discharge chamber.

JP 2011-169259 A

  However, as in Patent Document 1, when the discharge chamber is formed in an annular shape on the outer peripheral side of the suction chamber, the discharge pulsation based on the pressure fluctuation of the refrigerant is resonated by the annular shape, and the discharge pulsation increases. End up.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a swash plate compressor that can prevent resonance of discharge pulsation generated by the annular shape of the discharge chamber. is there.

  A swash plate compressor that solves the above problems includes a housing having a cylinder block and a housing structure coupled to the cylinder block via a valve / port formation body, and is rotatably supported in the housing. A rotating shaft, a swash plate that rotates by obtaining a driving force from the rotating shaft, a swash plate chamber that is partitioned in the housing and accommodates the swash plate, and a plurality of pistons moored to the swash plate; A plurality of cylinder bores which are formed around the rotation shaft of the cylinder block and each piston is accommodated so as to be reciprocally movable; a suction chamber and a discharge chamber which are defined in the housing structure and communicate with the cylinder bores; The housing structure includes a bottom wall and the bottom wall toward the cylinder block. A plurality of partition walls extending from the bottom wall toward the valve / port forming body and forming the suction chamber therein. The partition walls are spaced apart from each other, and the discharge chamber is constituted by at least a part of the peripheral wall, and at least a part of the discharge chamber is formed between adjacent partition walls.

  According to this, since at least a part of the discharge chamber is formed between the adjacent partition walls, the discharge chamber can be eliminated from the annular shape. Therefore, resonance of discharge pulsation caused by the annular shape of the discharge chamber can be prevented.

In the swash plate compressor, the discharge chamber preferably covers the entire circumference of each partition wall.
According to this, compared with the case where the discharge chamber does not cover a part around each partition wall, the volume of the discharge chamber can be increased. As a result, the discharge pulsation can be effectively reduced by utilizing the muffler effect by the discharge chamber.

  In the swash plate compressor, the suction chamber overlaps with a part of a pair of cylinder bores adjacent to each other in the circumferential direction of the rotating shaft when viewed from a direction along the central axis of the rotating shaft. One is preferably arranged for each set of cylinder bores.

  According to this, for example, when the suction chambers are arranged so as to overlap three or more cylinder bores when viewed from the direction along the central axis of the rotation shaft, the volume of each suction chamber is reduced. Can be small. Therefore, since the volume of the discharge chamber can be increased in the housing structure, the discharge pulsation can be effectively reduced by utilizing the muffler effect by the discharge chamber.

  In the swash plate compressor, refrigerant is sucked into the swash plate chamber, and the swash plate chamber and each suction chamber are communicated with each other through a suction passage that penetrates the cylinder block and the valve / port formation body. preferable.

  According to this, for example, the suction pipes for sucking the refrigerant from the external refrigerant circuit to the respective suction chambers are respectively arranged, and the refrigerant is sucked into the respective suction chambers through the respective suction pipes. It is possible to avoid a complicated configuration around the plate compressor. In addition, since the refrigerant is once sucked into the swash plate chamber, which is a relatively large space with respect to each suction chamber, before the refrigerant is sucked into each suction chamber, the suction pulsation is effectively utilized by utilizing the muffler effect of the swash plate chamber. Can be reduced.

  In the swash plate compressor, a link mechanism that allows a change in the inclination angle of the swash plate with respect to a direction orthogonal to the direction along the central axis of the rotation shaft, and a rotation mechanism that is integrally rotatable with the rotation shaft in the swash plate chamber. A partitioned body, a moving body that moves in the direction along the central axis with respect to the partitioned body, and changes the tilt angle; and the partition body and the moving body, and the refrigerant in the discharge chamber And a control mechanism for controlling the pressure of the control pressure chamber, the control pressure chamber being provided in the housing structure, and from the control mechanism to the control pressure chamber. It is preferable that a part of the passage of the refrigerant to be supplied is formed in the partition wall. This configuration is suitable as a variable capacity swash plate compressor.

  According to the present invention, resonance of discharge pulsation caused by the annular shape of the discharge chamber can be prevented.

A side sectional view showing a swash plate type compressor in an embodiment. The longitudinal cross-sectional view of a swash plate type compressor. The sectional side view which shows a swash plate type compressor when the inclination of a swash plate is a maximum inclination. (A) And (b) is a longitudinal cross-sectional view of the swash plate type compressor in another embodiment.

Hereinafter, an embodiment embodied in a variable capacity swash plate compressor will be described with reference to FIGS. The swash plate compressor is used for a vehicle air conditioner.
As shown in FIG. 1, the housing 11 of the swash plate compressor 10 includes a cylinder block 12, a front housing 13 connected to one end (the left end in FIG. 1) of the cylinder block 12, and the other end ( It is composed of a rear housing 15 as a housing component connected to the right end in FIG. 1 via a valve / port forming body 14. The rear housing 15 has a bottom wall 15 a and a cylindrical peripheral wall 15 b extending from the bottom wall 15 a toward the cylinder block 12.

  The cylinder block 12, the front housing 13, and the rear housing 15 are fastened together by a plurality of bolts B (only one is shown in FIG. 1). Each bolt B is inserted into a bolt through hole 11 h formed in the cylinder block 12, the front housing 13 and the rear housing 15, and a threaded portion (not shown) formed at the tip of the bolt B is screwed into the rear housing 15. It has come to be.

  In the housing 11, a swash plate chamber 16 is defined in a space surrounded by the cylinder block 12 and the front housing 13. A rotating shaft 17 is rotatably supported in the housing 11. In the rotary shaft 17, one end side along the direction in which the central axis L extends (the axial direction of the rotary shaft 17), and the front end portion located on the front side (one side) of the housing 11 penetrates the front housing 13. The shaft hole 13h is inserted. The front end of the rotating shaft 17 protrudes from the front housing 13. Further, in the rotating shaft 17, the rear end portion located on the other end side along the direction in which the central axis L extends and located on the rear side (the other side) of the housing 11 is a shaft hole 12 h penetrating the cylinder block 12. Is inserted.

  A first sliding bearing B1 is disposed in the shaft hole 13h, and a front end portion of the rotating shaft 17 is rotatably supported by the front housing 13 via the first sliding bearing B1. A second sliding bearing B2 is disposed in the shaft hole 12h, and the rear end portion of the rotating shaft 17 is rotatably supported by the cylinder block 12 via the second sliding bearing B2. A lip seal type shaft seal device 18 is interposed between the front housing 13 and the rotary shaft 17. A vehicle engine E as an external drive source is connected to the front end of the rotating shaft 17 via a power transmission mechanism PT. In the present embodiment, the power transmission mechanism PT is a constant transmission type clutchless mechanism (for example, a combination of a belt and a pulley).

  A seal ring 12 s is provided between the cylinder block 12 and the rotating shaft 17. The seal ring 12s seals the space between the pressure adjusting chamber 30a and the swash plate chamber 16, which is a space closer to the valve / port forming body 14 than the seal ring 12s in the shaft hole 12h.

  The swash plate chamber 16 accommodates a swash plate 19 that rotates by obtaining a driving force from the rotary shaft 17 and that can tilt in the axial direction with respect to the rotary shaft 17. The swash plate 19 is formed with an insertion hole 19a through which the rotary shaft 17 can be inserted. The swash plate 19 is attached to the rotating shaft 17 by inserting the rotating shaft 17 into the insertion hole 19a.

  In the cylinder block 12, a plurality of cylinder bores 12 a formed so as to penetrate in the axial direction of the cylinder block 12 are arranged around the rotating shaft 17. In this embodiment, six cylinder bores 12a are formed in the cylinder block 12, and only one cylinder bore 12a is shown in FIG. The plurality of cylinder bores 12 a are arranged at equal intervals in the circumferential direction of the rotating shaft 17. Each cylinder bore 12a accommodates a piston 20 that can reciprocate between a top dead center position and a bottom dead center position. Both openings of each cylinder bore 12a are closed by a valve / port forming body 14 and a piston 20, and a compression chamber 21 whose volume changes according to the reciprocation of the piston 20 is defined in each cylinder bore 12a. Each piston 20 is anchored to the outer periphery of the swash plate 19 via a pair of shoes 22. Then, the rotational movement of the swash plate 19 accompanying the rotation of the rotating shaft 17 is converted into the reciprocating linear movement of the piston 20 via the shoe 22.

  As shown in FIG. 2, the bottom wall 15 a of the rear housing 15 is provided with a plurality (three in this embodiment) of cylindrical partition walls 15 c extending toward the valve / port forming body 14. The plurality of partition walls 15 c extend linearly from the bottom wall 15 a toward the valve / port forming body 14. The plurality of partition walls 15c are spaced from each other in the circumferential direction of the rotary shaft 17, and are separated from the inner peripheral surface 15r of the rear housing 15 (the peripheral wall 15b).

  The tip of each partition wall 15 c is in contact with the valve / port forming body 14. Each partition 15 c cooperates with the valve / port forming body 14 to partition the suction chamber 31 inside. Therefore, a plurality (three in this embodiment) of suction chambers 31 are formed in the rear housing 15. Each suction chamber 31 is formed in a perfect circle shape in a cross-sectional view orthogonal to the axial direction of the rotating shaft 17. When viewed from the direction along the central axis L of the rotary shaft 17, the suction chamber 31 is arranged in the circumferential direction of the rotary shaft 17 so as to overlap a part of the pair of cylinder bores 12 a adjacent in the circumferential direction of the rotary shaft 17. Are arranged one by one with respect to a pair of adjacent cylinder bores 12a.

  A discharge chamber 32 is formed around each suction chamber 31 in the rear housing 15. The discharge chamber 32 is configured by at least a part of the peripheral wall 15b. At least a portion of the discharge chamber 32 is formed between the partition walls 15 c extending from the inner peripheral surface 15 r of the rear housing 15 toward the inner side of the rear housing 15 and adjacent in the circumferential direction of the rotary shaft 17. Further, the discharge chamber 32 covers the entire circumference of each suction chamber 31.

  The valve / port forming body 14 is formed with a suction port 31h and a discharge port 32h corresponding to each cylinder bore 12a. The suction port 31h and the discharge port 32h are opened and closed by a suction reed valve (not shown) and a discharge reed valve 32v (shown in FIG. 1) formed in the valve / port forming body 14. Each suction chamber 31 and each cylinder bore 12a (compression chamber 21) communicate with each other via each suction port 31h, and each cylinder bore 12a (compression chamber 21) and each discharge chamber 32 communicate with each other via each discharge port 32h. doing. Further, the swash plate chamber 16 and each suction chamber 31 communicate with each other by a suction passage 12 b that penetrates the cylinder block 12 and the valve / port formation body 14. In FIG. 2, for convenience of explanation, only the suction port 31 h, the discharge port 32 h, and the suction passage 12 b are shown in the valve / port formation body 14, and the other configurations are not shown.

  As shown in FIG. 1, a suction port 13 s is formed on the peripheral wall of the front housing 13. The suction port 13s is connected to an external refrigerant circuit. Then, the refrigerant gas sucked into the swash plate chamber 16 from the external refrigerant circuit through the suction port 13s is sucked into the suction chambers 31 through the suction passages 12b. Therefore, the suction chamber 31 and the swash plate chamber 16 are in the suction pressure region, and the pressures are almost equal.

  A lug plate 23 as a partition is fixed in front of the swash plate 19 on the rotating shaft 17. The lug plate 23 has a disc shape and can rotate integrally with the rotary shaft 17. Between the lug plate 23 and the swash plate 19, a bottomed cylindrical moving body 24 that is movable in the axial direction of the rotary shaft 17 with respect to the lug plate 23 is disposed.

  The moving body 24 includes a first cylindrical portion 24a having an insertion hole 24e through which the rotating shaft 17 is inserted, and a second cylindrical portion 24b extending in the axial direction of the rotating shaft 17 and having a diameter larger than that of the first cylindrical portion 24a. The first cylindrical portion 24a and the second cylindrical portion 24b are formed from an annular connecting portion 24c. The tip of the second cylindrical portion 24b is slidable with respect to the surface of the guide groove 23a facing the outer peripheral surface of the second cylindrical portion 24b in an annular guide groove 23a formed in the lug plate 23. ing. Thereby, the moving body 24 can rotate integrally with the rotary shaft 17 via the lug plate 23. A seal member 25 seals between the outer peripheral surface of the second cylindrical portion 24b and the surface of the guide groove 23a facing the outer peripheral surface of the second cylindrical portion 24b. The space between the insertion hole 24 e and the rotary shaft 17 is sealed by a seal member 26. A control pressure chamber 27 is defined between the lug plate 23 and the moving body 24.

  A convex portion 19 b is projected from a portion of the swash plate 19 that faces the moving body 24. The surface of the first cylindrical portion 24a that faces the convex portion 19b forms a pressing portion 24d that contacts the convex portion 19b and presses the swash plate 19.

  The lug plate 23 is provided with a pair of arms 23 b that project toward the swash plate 19. On the upper end side (the upper side in FIG. 1) of the swash plate 19, a projection 19c is provided so as to project toward the lug plate 23. The protrusion 19c is inserted between the pair of arms 23b, and is movable between the pair of arms 23b while being sandwiched between the pair of arms 23b. An inclined surface 23c is formed at the bottom portion between the pair of arms 23b, and the tip of the protrusion 19c can slide on the inclined surface 23c. The swash plate 19 can be tilted in the axial direction of the rotating shaft 17 by the linkage of the projection 19c sandwiched between the pair of arms 23b and the inclined surface 23c, and the driving force of the rotating shaft 17 is transmitted via the pair of arms 23b. The swash plate 19 is rotated by being transmitted to the protrusion 19c. When the swash plate 19 tilts in the axial direction of the rotary shaft 17, the protrusion 19c slides on the inclined surface 23c. The protrusion 19 c and the inclined surface 23 c constitute a link mechanism that allows a change in the inclination angle of the swash plate 19 with respect to a direction orthogonal to the direction along the central axis L of the rotating shaft 17.

  Further, on the rotary shaft 17, a regulating ring 28 is fixedly attached to the cylinder block 12 side from the swash plate 19. A spring 29 is mounted around the rotation shaft 17 between the regulating ring 28 and the swash plate 19. The spring 29 urges the swash plate 19 so that the swash plate 19 tilts toward the lug plate 23.

  The rotation shaft 17 is formed with a first in-axis passage 17 a extending along the axial direction of the rotation shaft 17. The rear end of the first in-axis passage 17a opens to the pressure adjustment chamber 30a. Further, the rotary shaft 17 is formed with a second in-axis passage 17 b extending along the radial direction of the rotary shaft 17. One end of the second in-shaft passage 17 b communicates with the tip of the first in-shaft passage 17 a, and the other end opens to the control pressure chamber 27. Therefore, the control pressure chamber 27 and the pressure adjustment chamber 30a communicate with each other via the first in-axis passage 17a and the second in-axis passage 17b.

  The valve / port forming body 14 is formed with a throttling portion 14 s communicating therewith. In addition, a communication portion 12r that communicates the pressure adjusting chamber 30a and the throttle portion 14s is recessed in the end face of the cylinder block 12 on the valve / port forming body 14 side. The control pressure chamber 27 and the suction chamber 31 communicate with each other via the second in-shaft passage 17b, the first in-shaft passage 17a, the pressure adjustment chamber 30a, the communication portion 12r, and the throttle portion 14s. Therefore, the second in-shaft passage 17b, the first in-shaft passage 17a, the pressure adjustment chamber 30a, the communication portion 12r, and the throttle portion 14s form an extraction passage from the control pressure chamber 27 to the suction chamber 31. Then, the opening degree of the extraction passage is reduced by the throttle portion 14s.

  Control of the pressure in the control pressure chamber 27 is performed by supplying refrigerant gas from the discharge chamber 32 to the control pressure chamber 27 and discharging refrigerant gas from the control pressure chamber 27 to the suction chamber 31. Therefore, the refrigerant gas supplied to the control pressure chamber 27 is a control gas that controls the pressure of the control pressure chamber 27. The moving body 24 moves in the axial direction of the rotary shaft 17 with respect to the lug plate 23 in accordance with the pressure difference between the control pressure chamber 27 and the swash plate chamber 16. An electromagnetic capacity control valve 35 is provided in the rear housing 15 as a control mechanism for controlling the pressure in the control pressure chamber 27.

  The capacity control valve 35 and the suction chamber 31 communicate with each other via a communication path 36. The capacity control valve 35 of this embodiment has its valve opening adjusted by sensing the pressure (suction pressure) of the refrigerant supplied from the suction chamber 31 to the capacity control valve 35 via the communication path 36. The capacity control valve 35 and the discharge chamber 32 communicate with each other via a communication passage 37. Further, the capacity control valve 35 and the pressure adjusting chamber 30a communicate with each other by a passage 38 (see FIG. 2) passing through the partition wall 15c and the valve / port forming body 14. Therefore, a part of the passage 38 is formed in the partition wall 15c. The discharge chamber 32 and the pressure adjusting chamber 30a communicate with each other via a communication passage 37, a capacity control valve 35, and a passage 38. Therefore, the communication passage 37, the passage 38, the pressure adjustment chamber 30a, the first in-shaft passage 17a, and the second in-shaft passage 17b form an air supply passage from the discharge chamber 32 to the control pressure chamber 27, and the capacity control The valve 35 is provided on the supply passage.

  As shown in FIG. 3, when the valve opening of the capacity control valve 35 is decreased, the communication passage 37, the passage 38, the pressure adjustment chamber 30a, the first in-shaft passage 17a, and the second in-shaft passage 17b are moved from the discharge chamber 32. Thus, the flow rate of the refrigerant gas supplied to the control pressure chamber 27 is reduced. Then, the refrigerant gas is discharged from the control pressure chamber 27 to the suction chamber 31 through the second in-shaft passage 17b, the first in-shaft passage 17a, the pressure adjusting chamber 30a, the communication portion 12r, and the throttle portion 14s. The pressure in the pressure chamber 27 approaches the pressure in the suction chamber 31.

  As the pressure in the control pressure chamber 27 approaches the pressure in the suction chamber 31 and the pressure difference between the control pressure chamber 27 and the swash plate chamber 16 decreases, the first cylindrical portion 24a of the moving body 24 approaches the lug plate 23. The moving body 24 moves. Then, the swash plate 19 is urged toward the lug plate 23 by the urging force of the spring 29, and the protrusion 19c slides on the inclined surface 23c in a direction away from the rotary shaft 17, thereby causing the swash plate to move. The inclination angle 19 increases, the stroke of the piston 20 increases, and the discharge capacity increases.

  As shown in FIG. 1, when the valve opening of the capacity control valve 35 is increased, the communication passage 37, the passage 38, the pressure adjustment chamber 30a, the first in-shaft passage 17a, and the second in-shaft passage 17b are moved from the discharge chamber 32. Thus, the flow rate of the refrigerant gas supplied to the control pressure chamber 27 increases. Therefore, the pressure in the control pressure chamber 27 approaches the pressure in the discharge chamber 32.

  As the pressure in the control pressure chamber 27 approaches the pressure in the discharge chamber 32 and the pressure difference between the control pressure chamber 27 and the swash plate chamber 16 increases, the first cylindrical portion 24a of the moving body 24 moves away from the lug plate 23. Thus, the moving body 24 moves. Then, the pressing portion 24 d presses the convex portion 19 b, and the swash plate 19 is pressed in a direction away from the lug plate 23 against the urging force of the spring 29. Then, the protrusion 19c slides on the inclined surface 23c in a direction approaching the rotating shaft 17, whereby the inclination angle of the swash plate 19 is reduced, the stroke of the piston 20 is reduced, and the discharge capacity is reduced.

Next, the operation of this embodiment will be described.
As shown in FIG. 2, the discharge chamber 32 is configured by at least a part of the peripheral wall 15 b, and at least a part of the discharge chamber 32 is directed from the inner peripheral surface 15 r of the rear housing 15 toward the inner side of the rear housing 15. It extends between the partition walls 15 c that are adjacent to each other in the circumferential direction of the rotating shaft 17. For this reason, the discharge chamber 32 is not in an annular shape. Therefore, resonance of the discharge pulsation caused by the annular shape of the discharge chamber 32 is prevented. The refrigerant gas is once sucked into the swash plate chamber 16 which is a relatively large space with respect to each suction chamber 31 before being sucked into each suction chamber 31. For this reason, the suction pulsation is effectively reduced by utilizing the muffler effect by the swash plate chamber 16.

In the above embodiment, the following effects can be obtained.
(1) The discharge chamber 32 is configured by at least a part of the peripheral wall 15b, and at least a part of the discharge chamber 32 extends from the inner peripheral surface 15r of the rear housing 15 toward the inner side of the rear housing 15 and rotates. It is formed between the partition walls 15c adjacent to each other in the 17 circumferential direction. According to this, the discharge chamber 32 can be eliminated from an annular shape. Therefore, resonance of discharge pulsation caused by the annular shape of the discharge chamber 32 can be prevented.

  (2) The discharge chamber 32 covers the entire circumference of each suction chamber 31. According to this, the volume of the discharge chamber 32 can be increased as compared with the case where the discharge chamber 32 does not cover a part around each suction chamber 31. As a result, the discharge pulsation can be effectively reduced by utilizing the muffler effect by the discharge chamber 32.

  (3) When the suction chamber 31 is viewed from the direction along the central axis L of the rotary shaft 17, a set of cylinder bores 12 a adjacent to each other in the circumferential direction of the rotary shaft 17 is overlapped. One for each cylinder bore 12a. According to this, for example, when compared with the case where the suction chamber 31 is arranged so as to overlap with three or more cylinder bores 12a when viewed from the direction along the central axis L of the rotation shaft 17, each suction chamber 31 is arranged. The volume of the chamber 31 can be reduced. Therefore, since the volume of the discharge chamber 32 can be increased in the rear housing 15, the discharge pulsation can be effectively reduced by utilizing the muffler effect by the discharge chamber 32.

  (4) The swash plate chamber 16 and each suction chamber 31 communicate with each other through each suction passage 12b. According to this, for example, a suction pipe for sucking the refrigerant gas from the external refrigerant circuit to each suction chamber 31 is arranged, and the refrigerant gas is sucked into each suction chamber 31 through each suction pipe. Thus, it can avoid that the structure around the swash plate compressor 10 becomes complicated. Further, since the refrigerant gas is once sucked into the swash plate chamber 16 which is a relatively large space with respect to each suction chamber 31 before being sucked into each suction chamber 31, the muffler effect by the swash plate chamber 16 is used. Inhalation pulsation can be effectively reduced.

  (5) A part of the refrigerant gas passage 38 supplied from the capacity control valve 35 to the control pressure chamber 27 is formed in the partition wall 15c. This configuration is suitable as the variable capacity swash plate compressor 10.

  (6) For example, by forming the discharge chamber 32 on the inner peripheral side of the suction chamber 31, the discharge chamber 32 can be eliminated from the annular shape. However, when the discharge chamber 32 is formed on the inner peripheral side of the suction chamber 31, the volume of the discharge chamber 32 becomes smaller than when the discharge chamber 32 is formed on the outer peripheral side of the suction chamber 31. The muffler effect cannot be fully utilized, and the discharge pulsation cannot be effectively reduced. Therefore, in the present embodiment, the discharge chamber 32 is configured by at least a part of the peripheral wall 15b, and at least a part of the discharge chamber 32 is directed from the inner peripheral surface 15r of the rear housing 15 toward the inner side of the rear housing 15. It extends between the partition walls 15 c that are adjacent to each other in the circumferential direction of the rotating shaft 17. Further, the discharge chamber 32 covers the entire circumference of each suction chamber 31. By doing so, the discharge chamber 32 can be eliminated from the annular shape while the volume of the discharge chamber 32 is increased as compared with the case where the discharge chamber 32 is formed on the inner peripheral side of the suction chamber 31.

  (7) For example, even if the discharge chamber 32 is formed on the outer peripheral side of the suction chamber 31, a standing wall that connects the inner peripheral surface 15r of the rear housing 15 and the partition that partitions the suction chamber 31 on the inner peripheral side is provided. By erecting, the discharge chamber 32 can be eliminated from the annular shape. However, the volume of the discharge chamber 32 is reduced by the amount of the standing wall, and the muffler effect by the discharge chamber 32 cannot be fully utilized, and the discharge pulsation cannot be effectively reduced. Therefore, in the present embodiment, the discharge chamber 32 is configured by at least a part of the peripheral wall 15b, and at least a part of the discharge chamber 32 is directed from the inner peripheral surface 15r of the rear housing 15 toward the inner side of the rear housing 15. It extends between the partition walls 15 c that are adjacent to each other in the circumferential direction of the rotating shaft 17. Further, the discharge chamber 32 covers the entire circumference of each suction chamber 31. By doing so, the discharge chamber 32 can be eliminated from the annular shape while securing the volume of the discharge chamber 32.

  (8) In this embodiment, since the pressure adjustment chamber 30a is not disposed in the rear housing 15, for example, the refrigerant gas in the pressure adjustment chamber 30a is cooled and liquefied by the refrigerant gas in the suction chamber 31. Can be prevented. As a result, the performance of the swash plate compressor 10 can be improved.

In addition, you may change the said embodiment as follows.
As shown in FIG. 4A, the suction chamber 31 may be disposed so as to overlap the three cylinder bores 12a when viewed from the direction along the central axis L of the rotating shaft 17. Each suction chamber 31 is formed in a semicircular shape in a cross-sectional view orthogonal to the axial direction of the rotating shaft 17. Further, as shown in FIG. 4B, each suction chamber 31 may be formed in an arc shape in a cross-sectional view orthogonal to the axial direction of the rotating shaft 17. In short, the shape of the suction chamber 31 is not particularly limited.

  In the embodiment, the refrigerant may not be configured to be sucked into each suction chamber 31 through the swash plate chamber 16. For example, a suction pipe for sucking the refrigerant from the external refrigerant circuit to each suction chamber 31 may be provided, and the refrigerant may be sucked into each suction chamber 31 via each suction pipe.

  In the embodiment, a part of the outer peripheral surface of each partition wall 15 c may be continuous with the inner peripheral surface 15 r of the rear housing 15, and the discharge chamber 32 does not cover a part around each suction chamber 31. It may be.

In the embodiment, the number of cylinder bores 12a is not particularly limited.
In the embodiment, the number of the suction chambers 31 is not particularly limited. In short, the discharge chamber 32 is constituted by at least a part of the peripheral wall 15b, and at least a part of the discharge chamber 32 extends from the inner peripheral surface 15r of the rear housing 15 toward the inner side of the rear housing 15 and rotates. What is necessary is just to be formed between the partition 15c adjacent in the circumferential direction of the axis | shaft 17.

  In the embodiment, a throttle portion is provided in the air supply passage that communicates the pressure adjustment chamber 30 a and the discharge chamber 32, and the capacity control valve 35 is provided on the extraction passage that communicates the pressure adjustment chamber 30 a and the suction chamber 31. The provided structure may be sufficient.

In the embodiment, a driving force may be obtained from an external driving source via a clutch.
In the embodiment, the swash plate compressor 10 may be a fixed capacity type.

(Circle) in embodiment, the swash plate type compressor 10 may not be used for a vehicle air conditioner, and may be used for another air conditioner.
Next, the technical idea that can be grasped from the above embodiments and other examples will be described below.

  (A) The suction chamber has a perfect circle shape in a cross-sectional view orthogonal to the axial direction of the rotation shaft.

  DESCRIPTION OF SYMBOLS 10 ... Swash plate type compressor, 11 ... Housing, 12 ... Cylinder block, 12a ... Cylinder bore, 12b ... Suction passage, 14 ... Valve / port formation body, 15 ... Rear housing as housing structure, 15a ... Bottom wall, 15b ... Peripheral wall, 15c ... partition wall, 16 ... swash plate chamber, 17 ... rotating shaft, 19 ... swash plate, 19c ... projection constituting the link mechanism, 20 ... piston, 23 ... lug plate as a partition, 23c ... constituting the link mechanism Inclined surface, 24 ... moving body, 27 ... control pressure chamber, 31 ... suction chamber, 32 ... discharge chamber, 35 ... capacity control valve as control mechanism, 38 ... passage.

Claims (5)

A housing having a cylinder block and a housing structure coupled to the cylinder block via a valve / port forming body;
A rotating shaft rotatably supported in the housing;
A swash plate that rotates by obtaining a driving force from the rotating shaft;
A swash plate chamber partitioned within the housing and containing the swash plate;
A plurality of pistons moored to the swash plate;
A plurality of cylinder bores that are formed around the rotation shaft of the cylinder block and each piston is accommodated so as to be capable of reciprocating;
A swash plate compressor that includes a suction chamber and a discharge chamber that are partitioned in the housing structure and communicate with the cylinder bore,
The housing structure includes a bottom wall and a peripheral wall extending from the bottom wall toward the cylinder block,
The bottom wall is provided with a plurality of partition walls extending from the bottom wall toward the valve / port forming body and forming the suction chamber therein, and the plurality of partition walls are spaced apart from each other. Has been
The discharge chamber is configured by at least a part of the peripheral wall, and at least a part of the discharge chamber is formed between adjacent partition walls.   The swash plate compressor according to claim 1, wherein the discharge chamber covers the entire circumference of each partition wall.   When viewed from the direction along the central axis of the rotating shaft, the suction chamber is positioned with respect to the set of cylinder bores so as to overlap a part of the set of adjacent cylinder bores in the circumferential direction of the rotating shaft. The swash plate compressor according to claim 1 or 2, wherein the compressors are arranged one by one.   The refrigerant is sucked into the swash plate chamber, and the swash plate chamber and each suction chamber communicate with each other through a suction passage that penetrates the cylinder block and the valve / port formation body. The swash plate type compressor according to claim 3. A link mechanism that allows a change in the inclination angle of the swash plate with respect to a direction orthogonal to a direction along the central axis of the rotation axis;
A partition provided in the swash plate chamber so as to be integrally rotatable with the rotary shaft;
A moving body that moves in a direction along the central axis relative to the partition body to change the tilt angle;
A control pressure chamber that is partitioned into the partition body and the movable body and moves the movable body by being supplied with a refrigerant in the discharge chamber;
A control mechanism that is provided in the housing structure and controls the pressure of the control pressure chamber,
The slant according to any one of claims 1 to 4, wherein a part of a passage of the refrigerant supplied from the control mechanism to the control pressure chamber is formed in the partition wall. Plate type compressor.