JPWO2012133669A1 - Swash plate compressor - Google Patents

Abstract

In the double-headed piston swash plate compressor 10, a front suction chamber 17 is formed separately from the swash plate chamber 25 so as to be positioned between the front cylinder bores 28 arranged in the circumferential direction. A suction chamber communication passage 50a is formed to communicate the suction chamber 17 and the shaft hole 11a. Further, the cylinder block 11 is formed with a plurality of front-side bore communication passages 50b for individually communicating the plurality of front-side cylinder bores 28 with the shaft holes 11a. The rotary shaft 22 is provided with a front rotary valve RF in which an introduction groove 22a is formed to sequentially communicate the suction chamber communication passage 50a and the front bore communication passage 50b while rotating integrally with the rotation shaft 22. Thereby, a small swash plate type compressor is provided while suppressing a decrease in pulsation and suction efficiency.

Description

  The present invention relates to a swash plate type compression in which a cylinder block is formed with a shaft hole through which a rotating shaft is inserted, and a plurality of cylinder bores that are formed so as to be circumferentially arranged around the shaft hole and into which pistons are inserted. Related to the machine.

  As this type of swash plate type compressor, there is a double-headed piston type swash plate type compressor which employs a double-headed piston as a piston. As shown in FIG. 11, in the swash plate compressor 80 of Patent Document 1, three cylinder bores 81a are formed in the cylinder block 81, and a double-headed piston 82 is accommodated in each cylinder bore 81a. The cylinder block 81 is formed so that one suction chamber 83 is positioned between two adjacent cylinder bores 81a, and one discharge chamber 84 is positioned between two adjacent cylinder bores 81a. Is formed. The suction chamber 83 and the discharge chamber 84 in which the capacity necessary for suppressing the pulsation is secured by effectively using the space between the adjacent cylinder bores 81a for forming the suction chamber 83 and the discharge chamber 84 is provided in the cylinder block 81. Therefore, an increase in the size of the swash plate compressor 80 is suppressed.

  By the way, although not shown, in the swash plate compressor 80 of Patent Document 1, the refrigerant is sucked from the suction chamber into the cylinder bore 81a when the reed valve type suction valve opens the suction port. In the suction system using such a suction valve, the suction valve opens and closes based on the pressure difference between the cylinder bore 81a and the suction chamber, and the suction valve is not opened until the pressure in the cylinder bore 81a has decreased to a predetermined pressure. The suction valve may not open at a desired timing without being opened, and the suction efficiency may be deteriorated.

  Therefore, a rotary valve in which the cylinder bore and the suction chamber are in mechanical communication is employed in order to prevent the deterioration of the suction efficiency with respect to the swash plate compressor 80 disclosed in Patent Document 1 in which the size of the body is suppressed. It is effective.

JP 9-317633 A JP 2007-138925 A JP 2007-270790 A

  As shown in FIG. 12, in the swash plate compressor 90 disclosed in Patent Document 2 as a compressor employing a rotary valve, the refrigerant is accommodated from the swash plate chamber 99 to the accommodation chamber 93 a on the front housing 93 side via the communication groove 98. It has reached the suction chamber once. For this reason, in order to introduce the refrigerant into the suction passage 96 communicating with the cylinder bore 97, the refrigerant on the front housing 93 side (accommodating chamber 93a) is guided to the cylinder block 91 side by the supply passage 92a. That is, a supply passage 92a extending from the front housing 93 to the cylinder block 91 must be formed in the rotating shaft 92, and the supply passage 92a is elongated in the axial direction. Therefore, in the swash plate compressor 90 of Patent Document 2, the physique of the swash plate compressor 90 is enlarged in the axial direction by forming the supply passage 92a.

  As shown in FIG. 13, in the swash plate compressor 100 disclosed in Patent Document 3 as a compressor that similarly employs a rotary valve, a supply passage 102 is formed in the rotating shaft 101, and the inside of the supply passage 102 is formed. An introduction hole 101 a that communicates with the outside of the rotating shaft 101 is formed. In the cylinder block 104, a suction recess 105 is formed around the rotation shaft 101, and the introduction hole 101 a can communicate with the swash plate chamber 106 and the supply passage 102 via the suction recess 105.

  In Patent Document 3, when the suction recess 105 and the introduction hole 101a communicate with the swash plate chamber 106, the refrigerant in the swash plate chamber 106 is introduced from the suction recess 105 into the supply passage 102 via the introduction hole 101a. It is introduced into the cylinder bore 108 from the supply passage 102 through the rotary valve 107. Also in Patent Document 3, the introduction hole 101 a is formed in the rotation shaft 101, so that the rotation shaft 101 is elongated in the axial direction and the suction recess 105 is formed in the cylinder block 104. The physique has grown in the axial direction. Further, with respect to the supply passage 102, it is necessary to increase the diameter of the rotating shaft 101 in order to ensure the strength of the rotating shaft 101. As a result, the size of the swash plate compressor 100 has increased in the radial direction. .

  As described above, the swash plate compressors 90 and 100 adopting the conventional rotary valve use the swash plate chambers 99 and 106 as they are as the suction chambers, so that the shape of the rotary valve 107 becomes complicated and large, resulting in the swash plate compression. The size of the machines 90 and 100 is increased.

  An object of the present invention is to provide a compact swash plate compressor while suppressing a decrease in pulsation and suction efficiency.

  In order to achieve the above object, a swash plate compressor according to an aspect of the present invention includes a cylinder block, a swash plate, a plurality of pistons, a rotating shaft, and a rotary valve. The cylinder block has a shaft hole, a plurality of cylinder bores, a swash plate chamber, and a suction chamber. The shaft hole extends through the cylinder block. The plurality of cylinder bores are arranged along the circumferential direction around the shaft hole. The suction chamber is provided between the adjacent cylinder bores so as to be isolated from the swash plate chamber. The swash plate is stored in the swash plate chamber. The plurality of pistons are moored to the swash plate and inserted into the plurality of cylinder bores, respectively. The rotating shaft is inserted into the shaft hole and rotates integrally with the swash plate. The rotary valve is provided on the rotation shaft so as to rotate integrally with the rotation shaft. The cylinder block includes a suction chamber communication path that communicates the suction chamber and the shaft hole, and a plurality of bore communication paths. The plurality of bore passages individually communicate the plurality of cylinder bores with the shaft hole. The rotary valve causes the suction chamber communication passage to sequentially communicate with the plurality of bore communication passages by rotating integrally with the rotary shaft.

  According to this, in the cylinder block, the suction chamber and the cylinder bore are arranged in the circumferential direction around the rotary valve. As a result, even if a rotary valve is used for the suction system, the size of the rotary valve in the axial direction and the radial direction, and thus the size of the swash plate compressor, does not increase. And since the rotary valve is adopted as the suction method instead of the suction valve, it is possible to prevent the deterioration of the suction efficiency as compared with the suction valve.

  Preferably, the suction chamber includes a plurality of suction chambers each positioned between adjacent cylinder bores. The suction chamber communication path includes a plurality of suction chamber communication paths that individually communicate the plurality of suction chambers with the shaft hole.

  According to this, in the cylinder block, the suction chamber and the cylinder bore are alternately arranged in the circumferential direction around the rotary valve. For this reason, in order to connect the cylinder bore and the suction chamber with the rotary valve, the supply passage only needs to be formed in a shape extending in a part of the circumferential direction of the rotary valve. Therefore, the shape of the rotary valve formed on the rotating shaft can be simplified, and the length in the axial direction can be further shortened.

  Preferably, the cylinder block has a plurality of discharge chambers positioned between adjacent cylinder bores.

  According to this, even if the cylinder block is thermally expanded by the high-temperature refrigerant discharged into the discharge chamber, the portions of thermal expansion are evenly distributed in the circumferential direction of the housing. As a result, the influence of each cylinder bore and piston due to thermal expansion can be reduced.

  Preferably, the plurality of discharge chambers are arranged outside the suction chamber in the radial direction of the cylinder block.

  Preferably, the cylinder block has a suction port to which an external pipe is connected, and a suction passage that communicates the suction port and the suction chamber, and the suction passage is provided separately from the swash plate chamber.

  According to this, although the rotary shaft having the rotary valve has heat due to sliding friction accompanying rotation, in the refrigerant suction path from the suction port to the suction chamber and further to the cylinder bore, the refrigerant can only be passed through the rotary valve. , Heat exchange with the rotating shaft. Furthermore, since the rotary valve is shortened in the axial direction, the heating of the refrigerant in the rotary valve is suppressed as much as possible, and the suction efficiency is increased.

  Preferably, the suction chamber communication passage is configured by a recess formed in an inner wall of the shaft hole, and the recess has an open end communicating with the swash plate chamber. A thrust bearing is disposed between the swash plate and the opening end of the recess, and the thrust bearing closes the opening end of the recess.

  According to this, when the cylinder block is cast, the suction chamber communication path can be formed at the same time. Therefore, there is no need to cut the suction chamber communication passage with a drill or the like after the cylinder block is cast, and the labor for manufacturing the cylinder block can be saved.

  Preferably, the suction chamber communication passage is formed in an inner wall of the suction chamber and has a first recess having an opening end opened in an end surface in the axial direction of the cylinder block, and an inner wall of the shaft hole. And a second recess having an open end communicating with the swash plate chamber. A thrust bearing is disposed between the swash plate and the opening end of the second recess, and the thrust bearing closes the opening end of the second recess.

  According to this, when casting the cylinder block, not only can the suction chamber communication path be formed at the same time, but also the opening of the suction chamber communication path and the swash plate chamber can be reduced in size, so that the thrust bearing as the closing member can be reduced in size. Can be

  Preferably, the plurality of cylinder bores are three cylinder bores.

  According to this, in the cylinder block, a large cylinder bore capacity can be secured, and pulsation can be further reduced.

  ADVANTAGE OF THE INVENTION According to this invention, a small swash plate type compressor can be provided, suppressing the fall of a pulsation and suction efficiency.

Sectional drawing which followed the 1-1 line | wire of FIG. 3 which shows the double-headed piston type swash plate type compressor which concerns on the 1st Embodiment of this invention. Sectional drawing which followed the 2-2 line of FIG. 3 which shows the double-headed piston type swash plate type compressor of 1st Embodiment. Sectional drawing along the 3-3 line of FIG. 1 which shows a front side discharge chamber and a front side suction chamber. FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. 1 showing the front cylinder bore, the front suction chamber, and the front discharge chamber. The fragmentary sectional view which shows the double-headed piston type swash plate type compressor which concerns on the 2nd Embodiment of this invention. FIG. 6 is a development view showing the rotary valve and the shaft hole in FIG. 5. 5A is a cross-sectional view taken along line 7a-7a in FIG. 5 showing the cylinder block of FIG. 5 from the front suction chamber side, and FIG. 5B is a line of 7b-7b in FIG. 5 showing the cylinder block from the shaft hole side. FIG. The fragmentary sectional view which shows the double-headed piston type swash plate type compressor of another example. Sectional drawing which shows the double-headed piston type swash plate type compressor of another example. The expanded view which shows the front side rotary valve of another example. The figure which shows the patent document 1. FIG. The figure which shows the patent document 2. FIG. The figure which shows the patent document 3. FIG.

(First embodiment)
A first embodiment in which the swash plate compressor of the present invention is embodied as a double-headed piston swash plate compressor 10 will be described with reference to FIGS.

  As shown in FIGS. 1 and 2, in a housing H of a double-headed piston type swash plate compressor 10 (hereinafter simply referred to as a compressor 10), of a pair of cylinder blocks 11 and 12 joined, the front side ( A front housing 13 is joined to the cylinder block 11 on the left side in FIG. 1 via a front side valve / port forming body 15. A rear housing 14 is joined to the cylinder block 12 on the rear side (right side in FIG. 1) via a rear side valve / port forming body 16. The housing H is formed with a pair of cylinder blocks 11 and 12 interposed between the front housing 13 and the rear housing 14.

  A rotary shaft 22 is inserted into the shaft holes 11a and 12a formed through the cylinder blocks 11 and 12, and the rotary shaft 22 is rotated by a seal peripheral surface formed on the inner peripheral surfaces of the shaft holes 11a and 12a. Supported as possible. The rotary shaft 22 is inserted so as to pass through insertion holes 15 d and 16 d formed at the center of the front side valve / port forming body 15 and the rear side valve / port forming body 16. At the projecting end of the rotary shaft 22 from the front side valve / port forming body 15, there is a lip seal type shaft between the inner peripheral surface of the front housing 13 and the peripheral surface of the rotary shaft 22 facing the inner peripheral surface. The sealing device 23 is hermetically sealed. The shaft seal device 23 is accommodated in an accommodation chamber 13 c defined between the inner peripheral surface of the front housing 13 and the peripheral surface of the rotary shaft 22.

  A swash plate 24 that rotates integrally with the rotary shaft 22 is fixed to the rotary shaft 22. The swash plate 24 is located inside the cylinder blocks 11 and 12 and is housed in a swash plate chamber 25 defined between the cylinder blocks 11 and 12. A thrust bearing 26 is interposed between the end face of the front cylinder block 11 and the annular base 24 a of the swash plate 24. A thrust bearing 27 is interposed between the end face of the rear cylinder block 12 and the base 24 a of the swash plate 24. The thrust bearings 26 and 27 restrict movement of the swash plate 24 along the central axis L direction of the swash plate 24 across the swash plate 24, and the thrust bearings 26 and 27 are shaft holes in the cylinder blocks 11 and 12, respectively. It is pressed against the open end faces of 11a and 12a.

  As shown in FIG. 4, the front cylinder block 11 has three front cylinder bores 28 arranged around the rotary shaft 22 so as to surround the rotary shaft 22. As shown in FIG. 1, the rear cylinder block 12 has three rear cylinder bores 29 arranged around the rotary shaft 22 so as to surround the rotary shaft 22. The front cylinder bore 28 and the rear cylinder bore 29 make a pair in the axial direction (front-rear direction) in which the central axis L extends, and a double-headed piston 30 as a piston is inserted into both the cylinder bores 28 and 29. The front side cylinder bore 28 is closed by the front side valve / port forming body 15 and the double-headed piston 30, and the rear side cylinder bore 29 is closed by the rear side valve / port forming body 16 and the double-headed piston 30.

  The rotational movement of the swash plate 24 that rotates integrally with the rotary shaft 22 is transmitted to the double-headed piston 30 via a pair of shoes 31 provided with the swash plate 24 interposed therebetween, and the double-headed piston 30 is in contact with the front cylinder bore 28 and the rear cylinder bore. It reciprocates back and forth in 29. A front-side compression chamber 28a is defined in the front-side cylinder bore 28 by a double-headed piston 30 and a front-side valve / port forming body 15, and a double-headed piston 30 and a rear-side valve are placed in the rear-side cylinder bore 29. The rear compression chamber 29 a is partitioned by the port forming body 16.

  In the front housing 13 and the cylinder block 11, three front suction chambers 17 surround the rotating shaft 22 and are formed through the front valve / port forming body 15. As shown in FIG. 4, the three front side suction chambers 17 are arranged one by one between the front side cylinder bores 28 adjacent in the circumferential direction around the shaft hole 11a. The three front suction chambers 17 are arranged at equal intervals on the outer peripheral side of the shaft hole 11a.

  As shown in FIGS. 1 and 2, of the three front side suction chambers 17, one front side suction chamber 17 is closer to the axial direction of the rotary shaft 22 than the other two front side suction chambers 17. Along the length, the volume increases. As shown in FIG. 3, in the front housing 13, each of the three front suction chambers 17 communicates with the storage chamber 13c, and the three front suction chambers 17 communicate with each other around the storage chamber 13c. , It is a connected space.

  As shown in FIGS. 1 and 3, a front-side discharge chamber 28 b is partitioned between the front housing 13 and the front-side valve / port forming body 15 so as to surround the rotating shaft 22. The front discharge chamber 28 b is a space in which refrigerant from the three front compression chambers 28 a is discharged, and is annularly defined on the outer peripheral side of the front housing 13.

  In the front side discharge chamber 28b, a portion facing each front side compression chamber 28a through the front side valve / port forming body 15 is opened. In the front-side discharge chamber 28b, the spaces facing the front-side compression chambers 28a communicate with each other through a passage, forming a continuous space.

  As shown in FIGS. 3 and 4, the cylinder block 11 has three front side discharge chambers 40 communicating with the front side discharge chamber 28 b. The front-side discharge chamber 40 extends through the front-side valve / port forming body 15 to the front-side cylinder block 11. The front-side discharge chambers 40 formed at three locations are arranged around the rotating shaft 22 and are formed one by one between the front-side cylinder bores 28 adjacent to each other in the circumferential direction of the shaft hole 11a. Each front discharge chamber 40 is formed outside the front suction chamber 17 in the radial direction of the cylinder block 11.

  As shown in FIGS. 1 and 3, the front side valve / port forming body 15 has a discharge port 15a formed at a position corresponding to each front cylinder bore 28, and a discharge port corresponding to the discharge port 15a. A valve 15b is formed. Further, the front side valve / port forming body 15 is formed with a retainer 15c for regulating the opening degree of the discharge valve 15b.

  Next, the configuration on the rear side will be described.

  As shown in FIGS. 1 and 2, the rear housing 14 and the cylinder block 12 have three rear suction chambers 18 arranged around the rotation shaft 22 (shaft hole 12a) and a rear valve / port formation. It is formed through the body 16. Similar to the front side, the three rear side suction chambers 18 are arranged one by one between the rear side cylinder bores 29 adjacent to each other in the circumferential direction of the shaft hole 12a. Of the three rear suction chambers 18, one rear suction chamber 18 is longer in the axial direction of the rotary shaft 22 than the other two rear suction chambers 18. The volume is large.

  A rear housing side suction chamber 19 is defined between the center of the rear housing 14 and the rear side valve / port forming body 16. Three rear suction chambers 18 communicate with the rear housing side suction chamber 19, and the three rear suction chambers 18 are connected together with the rear housing side suction chamber 19 as a center. And the front side suction chamber 17 and the rear side suction chamber 18 are arrange | positioned so that one by one may make a pair in the front-back direction where the central axis L extends. A front suction chamber 17 and a rear suction chamber 18 are formed in the cylinder blocks 11 and 12 with a swash plate 24 interposed therebetween.

  A rear-side discharge chamber 29 b is annularly defined between the rear housing 14 and the rear-side valve / port forming body 16 so as to surround the rotating shaft 22. The rear side discharge chamber 29 b is a space in which refrigerant from the three rear side compression chambers 29 a is discharged, and is partitioned on the outer peripheral side of the rear housing side suction chamber 19. In the rear side discharge chamber 29b, a portion facing each rear side cylinder bore 29 via the rear side valve / port forming body 16 opens with the same size as the circular shape of the rear side compression chamber 29a. In the rear-side discharge chamber 29b, spaces facing the respective rear-side cylinder bores 29 communicate with each other through a passage and form a continuous space.

  The cylinder block 12 is integrally formed with three rear side discharge chambers 42 communicating with the rear side discharge chamber 29b. The rear side discharge chamber 42 extends from the rear housing 14 through the rear side valve / port forming body 16 to the cylinder block 12 on the rear side. The rear side discharge chambers 42 formed at three locations are arranged around the shaft hole 12a and are formed one by one between the rear cylinder bores 29 adjacent to each other in the circumferential direction of the shaft hole 12a. Each rear discharge chamber 42 is formed outside the rear suction chamber 18 in the radial direction of the cylinder block 12. Further, the front-side discharge chamber 28b and the rear-side discharge chamber 29b are arranged so that one pair is formed in the front-rear direction in which the central axis L extends.

  As shown in FIG. 1, the rear side valve / port forming body 16 has a discharge port 16a formed at a position corresponding to each rear side discharge chamber 29b, and a discharge valve 16b at a position corresponding to the discharge port 16a. Is formed. Further, the rear side valve / port forming body 16 is formed with a retainer 16c for regulating the opening degree of the discharge valve 16b.

  A suction passage 43 is formed in the cylinder blocks 11, 12. The suction passage 43 communicates with the front suction chamber 17 having the largest volume among the three front suction chambers 17. The rear-side opening communicates with the rear-side suction chamber 18 having the largest volume among the three rear-side suction chambers 18. Further, a suction port 44 is formed in the front cylinder block 11. One end of the suction port 44 opens on the outer peripheral surface of the cylinder block 11, and the other end opens on the inner peripheral surface of the suction passage 43. An external pipe 32 of an external refrigerant circuit disposed outside the compressor 10 is connected to one end opening of the suction port 44. The suction passage 43 is formed in the cylinder blocks 11 and 12 and is isolated from the swash plate chamber 25.

  The suction passage 43 is formed so as to communicate the suction chambers 17 and 18 having the largest volume on the front side and the rear side. Therefore, the suction passage 43 is formed at a position sandwiched in the axial direction by the front-side discharge chamber 40 and the rear-side discharge chamber 42 located on the outer peripheral side of the suction chambers 17 and 18.

  As shown in FIG. 2, the cylinder blocks 11 and 12 are provided with a discharge passage 45, and the discharge passage 45 has one of the three front-side discharge chambers 40 having a front opening. The rear side opening communicates with one of the three rear side discharge chambers 42. Further, a discharge port 46 is formed in the cylinder block 11. One end of the discharge port 46 opens to the outer surface of the cylinder block 11, and the other end opens to the inner peripheral surface of the discharge passage 45. The discharge port 46 is connected to an external pipe 33 of an external refrigerant circuit disposed outside the compressor 10.

  As shown in FIG. 3, the discharge passage 45 is formed in the cylinder blocks 11 and 12 at a position shifted in the circumferential direction of the cylinder blocks 11 and 12 from the position where the suction passage 43 is formed. Specifically, the front side discharge chamber 40 and the rear side discharge chamber 42 that sandwich the suction passage 43 in the axial direction are sandwiched in the axial direction by the front side discharge chamber 40 and the rear side discharge chamber 42 that are shifted in the circumferential direction. A discharge passage 45 is formed at the position.

  When the refrigeration cycle for vehicle air conditioning is configured using the compressor 10, the external refrigerant circuit connects the discharge port 46 and the suction port 44 of the compressor 10 via the external pipes 32 and 33. The external refrigerant circuit has a condenser (condenser), an expansion valve (expansion valve), and an evaporator (evaporator), which are arranged in this order from the discharge port 46 of the compressor 10 on the external refrigerant circuit. The

  Next, the suction structure in the compressor 10 will be described.

  First, the suction structure on the front side will be described. As shown in FIG. 4, the cylinder block 11 is formed with a suction chamber communication passage 50a for communicating each front suction chamber 17 with the shaft hole 11a. One end of the suction chamber communication passage 50a opens to the front suction chamber 17, and the other end opens on the seal peripheral surface of the shaft hole 11a. Further, the suction chamber communication passage 50 a extends while being slightly inclined along the radial direction of the cylinder block 11, and is formed in the cylinder block 11.

  The cylinder block 11 is formed with a front-side bore communication passage 50b that allows the shaft hole 11a and the front-side cylinder bores 28 to communicate with each other. One end of the front-side bore communication passage 50 b opens on the seal circumferential surface of the shaft hole 11 a, and the other end opens on the front-side cylinder bore 28. The suction chamber communication passage 50a and the front bore communication passage 50b are alternately arranged in the circumferential direction of the shaft hole 11a.

  As shown in FIGS. 1 and 4, an introduction groove 22 a is formed on the front peripheral surface of the rotating shaft 22. The introduction groove 22a is recessed in the circumferential surface on the front housing 13 side of the rotary shaft 22 that is a solid shaft. The introduction groove 22a opens toward the seal peripheral surface of the shaft hole 11a, and can communicate with the suction chamber communication passage 50a and the front bore communication passage 50b individually. Then, the position of the introduction groove 22a is changed with the rotation of the rotary shaft 22, so that the suction chamber communication path 50a and the front bore communication path 50b with which the introduction groove 22a communicates are mechanically switched. It has become.

  Therefore, the portion of the rotating shaft 22 surrounded by the seal peripheral surface is a front-side rotary valve RF formed integrally with the rotating shaft 22. The introduction groove 22a allows one suction chamber communication passage 50a and one front-side bore communication passage 50b located adjacent to each other in the circumferential direction of the shaft hole 11a to communicate with each other. Then, the rotation of the rotary shaft 22 causes the suction chamber communication passage 50a and the front bore communication passage 50b to individually communicate with each other through the introduction groove 22a, so that the front cylinder bore 28 adjacent to the front suction chamber 17 is adjacent. The refrigerant is inhaled. Therefore, in the present embodiment, the introduction groove 22a serves as a supply passage for communicating the front cylinder bore 28 and the front suction chamber 17 with the front rotary valve RF.

  Next, the rear suction structure will be described.

  As shown in FIGS. 1 and 2, the cylinder block 12 is formed with a rear side introduction passage 51 for communicating each rear side cylinder bore 29 and the shaft hole 12a. One end of the rear side introduction passage 51 opens to each rear side cylinder bore 29, and the other end opens on the seal peripheral surface of the shaft hole 12a. Further, a supply path 22 b is formed on the peripheral surface on the rear side of the rotating shaft 22. One end of the supply path 22 b opens into the rear housing side suction chamber 19 in the rear housing 14. Further, the other end of the rear side introduction passage 51 can communicate with the other end side of the supply passage 22b. Then, by changing the position of the supply path 22b with the rotation of the rotary shaft 22, the rear side introduction path 51 with which the supply path 22b communicates is mechanically switched. Therefore, the portion of the rotating shaft 22 surrounded by the seal peripheral surface is a rear-side rotary valve RR formed integrally with the rotating shaft 22.

  Next, the operation of the compressor 10 having the above configuration will be described.

  The refrigerant is sucked into the suction passage 43 through the suction port 44 and supplied to the front suction chambers 17 and the rear suction chambers 18. When the front cylinder bore 28 shifts to the suction stroke, as shown in FIG. 4, one suction chamber communication passage 50a and the suction chamber communication passage 50a are provided via the introduction groove 22a of the front rotary valve RF. And the front-side bore communication passage 50b adjacent to each other. Then, the refrigerant is sucked into the front cylinder bore 28 from the front suction chamber 17 via the front rotary valve RF.

  As the rotary shaft 22 rotates, the introduction groove 22a is disconnected from the suction chamber communication passage 50a, the communication between the suction chamber communication passage 50a and the front bore communication passage 50b is released, and the front side When the cylinder bore 28 is shut off, the front side cylinder bore 28 shifts to the compression stroke and the discharge stroke. Then, the refrigerant in the front side compression chamber 28a pushes the discharge valve 15b away from the discharge port 15a and is discharged into the front side discharge chamber 28b. Then, the refrigerant discharged to the front discharge chamber 28b flows out from the front discharge chamber 40 through the discharge passage 45 and the discharge port 46 to the external refrigerant circuit.

  On the other hand, on the rear side, when the refrigerant is supplied to the rear housing side suction chamber 19 and the rear cylinder bore 29 shifts to the suction stroke, a supply path communicating with the rear housing side suction chamber 19 in the rear side rotary valve RR. 22 b communicates with one or two rear side introduction passages 51. Then, the refrigerant is supplied to the rear side introduction passage 51 from the rear housing side suction chamber 19 via the rear side rotary valve RR, and the refrigerant is sucked into the rear side cylinder bore 29 communicating with the rear side introduction passage 51. The

  As the rotary shaft 22 rotates, the supply passage 22b is disconnected from the rear side introduction passage 51, the communication between the rear side introduction passage 51 and the rear housing side suction chamber 19 is released, and the rear side cylinder bore 29 is When shut off, the rear cylinder bore 29 shifts to the compression stroke and the discharge stroke. Then, the refrigerant in the rear side compression chamber 29a pushes the discharge valve 16b away from the discharge port 16a and is discharged into the rear side discharge chamber 29b. Then, the refrigerant discharged to the rear side discharge chamber 29b flows out from the rear side discharge chamber 42 through the discharge passage 45 and the discharge port 46 to the external refrigerant circuit.

  Therefore, according to the present embodiment, the following advantages can be obtained.

  (1) In the double-headed piston type swash plate compressor 10, three front side cylinder bores 28 are formed around the shaft hole 11 a in the cylinder block 11, and the front side suction chamber 17 is interposed between the adjacent front side cylinder bores 28. Were placed one by one. That is, the front cylinder bore 28 and the front suction chamber 17 are alternately arranged around the shaft hole 11a. In addition, the cylinder block 11 is formed with a suction chamber communication passage 50a for communicating each front suction chamber 17 and the shaft hole 11a, and a front bore communication passage 50b for communicating the front cylinder bore 28 and the shaft hole 11a. The suction chamber communication passage 50a and the front bore communication passage 50b are alternately arranged in the circumferential direction of the shaft hole 11a. The refrigerant in each front suction chamber 17 is directly introduced into the introduction groove 22a via the suction chamber communication passage 50a in the cylinder block 11, and then the front cylinder bore 28 via the front bore communication passage 50b. Inhaled. Therefore, in order to connect the front side cylinder bore 28 and the front side suction chamber 17 adjacent to each other in the circumferential direction by the front side rotary valve RF, it is only necessary to form the introduction groove 22a in a shape extending in a part in the circumferential direction of the rotary valve RF. Good. Therefore, since the shape of the front side rotary valve RF can be simplified, the length of the front side rotary valve RF in the axial direction can be shortened. As a result, even if the front rotary valve RF is adopted as the suction method of the compressor 10 having the front suction chamber 17 in the cylinder block 11, the size of the compressor 10 is not easily increased in size in the axial direction or the radial direction. As a suction method, a rotary valve is used instead of a suction valve, and the front side cylinder bore 28 and the front side suction chamber 17 are mechanically communicated with each other, so that deterioration of suction efficiency is prevented as compared with the suction valve. be able to. In addition, since three front-side suction chambers 17 are formed in the cylinder block 11, a sufficient volume of the suction chamber can be secured and pulsation can be suppressed.

  (2) One front suction chamber 17 is formed between the front cylinder bores 28 adjacent to each other in the circumferential direction of the shaft hole 11a. In addition, a suction chamber communication passage 50a is formed in the cylinder block 11 for communicating each front suction chamber 17 with the introduction groove 22a of the front rotary valve RF. The refrigerant in each front-side suction chamber 17 can be directly introduced into the introduction groove 22a through the suction chamber communication passage 50a. Accordingly, since it is not necessary to introduce the refrigerant into the suction pressure region of the front housing 13 once, there is no need to form the introduction groove 22 a extending from the front housing 13 to the cylinder block 11 on the rotating shaft 22. Therefore, the rotating shaft 22 is supported by the shaft hole 11a (seal peripheral surface) before and after the introduction groove 22a in the axial direction, and the bearing area of the rotating shaft 22 can be secured and the wear resistance can be improved.

  (3) Similarly to the front suction chamber 17, one rear suction chamber 18 is formed between the adjacent rear cylinder bores 29 so as to surround the rotating shaft 22. For this reason, the suction chambers 17 and 18 are provided in the radial direction of the cylinder blocks 11 and 12 on the front side and the rear side, and an increase in size of the compressor 10 in the axial direction can be suppressed.

  (4) A front-side discharge chamber 28b is formed in the front housing 13, a rear-side discharge chamber 29b is formed in the rear housing 14, and three front-side discharge chambers 40 communicate with the front-side discharge chamber 28b. Three rear discharge chambers 42 communicate with the rear discharge chamber 29b. Each discharge chamber 40, 42 is arranged one by one between the adjacent cylinder bores 28, 29. For this reason, in the cylinder blocks 11 and 12, the capacity | capacitance of each discharge chamber 40 and 42 can be ensured large, and a pulsation can be reduced more.

  (5) The discharge chambers 40 and 42 are disposed outside the suction chambers 17 and 18 in the radial direction of the cylinder blocks 11 and 12. For this reason, even if the cylinder blocks 11 and 12 are thermally expanded by the high-temperature refrigerant discharged into the discharge chambers 40 and 42, the thermal expansion locations are evenly distributed in the radial direction of the cylinder blocks 11 and 12. As a result, the influence of the double-headed piston 30 due to thermal deformation of the cylinder bores 28 and 29 can be reduced.

  (6) The discharge chambers 40 and 42 are arranged one by one between the cylinder bores 28 and 29. For this reason, even if the cylinder blocks 11 and 12 are thermally expanded by the high-temperature refrigerant discharged into the discharge chambers 40 and 42, the thermal expansion locations are evenly distributed in the circumferential direction of the cylinder blocks 11 and 12. As a result, the influence of the double-headed piston 30 due to thermal deformation of the cylinder bores 28 and 29 can be reduced.

  (7) A suction port 44 is formed in the cylinder block 11, and a suction passage 43 communicating with the front suction chamber 17 and the rear suction chamber 18 is formed in the cylinder blocks 11 and 12. For this reason, when the refrigerant is sucked into the suction chambers 17 and 18, the refrigerant does not pass through the swash plate chamber 25. Therefore, it is possible to prevent the refrigerant sucked into the suction chambers 17 and 18 from being heated by the high-temperature blow-by gas flowing into the swash plate chamber 25 or the rotating shaft 22 heated by sliding friction.

  (8) The front suction chamber 17 and the rear suction chamber 18 are paired in the axial direction, and the front discharge chamber 40 and the rear discharge chamber 42 are paired in the axial direction. Further, a front-side rotary valve RF is adopted as a suction method to the front-side cylinder bore 28, and a rear-side rotary valve RR is adopted as a suction method to the rear-side cylinder bore 29. For this reason, since the suction structure is the same on the front side and the rear side, it is possible to suppress the occurrence of vibration and noise due to the difference in the suction structure between the front side and the rear side.

  (9) One front-side suction chamber 17 is formed between the front-side cylinder bores 28 adjacent in the circumferential direction so as to surround the shaft hole 11a. Further, a suction chamber communication passage 50a for communicating each front suction chamber 17 and the introduction groove 22a of the front rotary valve RF to the cylinder block 11, and a front bore for communicating the introduction groove 22a and the front cylinder bore 28. A communication passage 50b was formed. The refrigerant in each front suction chamber 17 can be sucked into the front cylinder bore 28 via the suction chamber communication passage 50a, the introduction groove 22a, and the front bore communication passage 50b. The refrigerant suction from the front suction chamber 17 to the front cylinder bore 28 can be completed. Therefore, the contact area between the refrigerant and the introduction groove 22a can be shortened as compared with the case where the air is sucked into the front cylinder bore 28 through the groove extending into the front housing 13 and the swash plate chamber 25. As a result, it is possible to reduce the increase in suction overheating accompanying the increase in the contact area between the refrigerant and the introduction groove 22a, and to prevent the suction efficiency from deteriorating.

  (10) Although the rotary shaft 22 has heat due to sliding friction with the shaft holes 11a, 12a, etc., in the refrigerant suction path from the suction port 44 to the front side suction chamber 17 and further to the front side cylinder bore 28, the refrigerant is When passing through the introduction groove 22a, heat is exchanged with the rotary shaft 22 via the front rotary valve RF. However, since the introduction groove 22a is shortened in the axial direction, the heating of the refrigerant at the front rotary valve RF is suppressed as much as possible, and the suction efficiency is increased.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. In addition, the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description thereof is omitted or simplified.

    As shown in FIGS. 5 and 7 (a), the first recess 60 is located on the front end of the cylinder block 11 on the front housing 13 side and is located outside the shaft hole 11a. It is formed corresponding to the side suction chamber 17. The first recess 60 is formed in the cylinder block 11 so as to extend in the radial direction from the inner wall of each front suction chamber 17. One end of the first recess 60 opens to the first end surface 11 b that is the surface of the cylinder block 11 in the axial direction, and is connected to the opening of each front-side suction chamber 17. The other end of the first recess 60 is located in the middle of the axial length of the front suction chamber 17 and does not penetrate the cylinder block 11 in the axial direction. Moreover, the 1st recessed part 60 is recessedly provided toward the 2nd end surface 11c from the 1st end surface 11b.

    As shown in FIGS. 5 and 7B, a second recess 61 is formed corresponding to each front suction chamber 17 on the second end surface 11c which is the surface of the cylinder block 11 on the swash plate chamber 25 side in the axial direction. Has been. The second recess 61 is formed in the cylinder block 11 so as to extend in the radial direction from the inner wall of the shaft hole 11a. One end of the second recess 61 opens to the second end surface 11c of the cylinder block 11 and is connected to the opening of the shaft hole 11a. The other end of the second recess 61 is located in the middle of the axial length of the shaft hole 11a and does not penetrate the cylinder block 11 in the axial direction. Moreover, the 2nd recessed part 61 is recessedly provided toward the 1st end surface 11b from the 2nd end surface 11c. The opening on the second end face 11 c side (swash plate chamber 25 side) in the second recess 61 is closed by the thrust bearing 26.

    And in the cylinder block 11, the 1st recessed part 60 and the 2nd recessed part 61 are connected, and the communication path 62 for suction chambers is formed by connecting. One end of the suction chamber communication passage 62 is formed by an opening on the front suction chamber 17 side in the first recess 60, and the other end of the suction chamber communication passage 62 is formed by an opening on the shaft hole 11 a side in the second recess 61. Is formed. The suction chamber communication path 62 allows the front suction chamber 17 and the introduction groove 22a to communicate with each other. In the suction chamber communication path 62, the opening end on the swash plate chamber 25 side is closed by the thrust bearing 26, and the space between the suction chamber communication path 62 and the swash plate chamber 25 is sealed. The first recess 60 and the second recess 61 are formed together with the front suction chamber 17 when the cylinder block 11 is manufactured by casting.

  FIG. 6 is a diagram in which the front-side rotary valve RF is developed in the circumferential direction, and shows the peripheral surface of the front-side rotary valve RF and the shaft hole 11a through which the front-side rotary valve RF is inserted and supported by the outline shown by the solid line. . An introduction groove 22a is shown in these outlines. 6 shows a front-side bore communication passage 50b that opens to the shaft hole 11a and communicates with each front-side cylinder bore 28 by a two-dot chain line in FIG. 6, and opens to the shaft hole 11a and has each front-side suction chamber. 17 shows a suction chamber communication passage 62 (a region where the first concave portion 60 and the second concave portion 61 overlap with each other).

    As shown in FIG. 6, the front bore communication passages 50b and the suction chamber communication passages 62 are alternately arranged along the circumferential direction of the shaft hole 11a. In order to connect the suction chamber communication passage 62 and the front bore communication passage 50b through the introduction groove 22a, the introduction groove 22a only needs to be formed to extend partly in the circumferential direction of the rotary shaft 22. .

    Therefore, according to the second embodiment, in addition to the same advantages as (1) to (10) described in the first embodiment, the following advantages can be obtained.

    (11) Since the suction chamber communication passage 62 has a rectangular shape that is long in the axial direction, the suction chamber communication passage 62 and the front bore communication passage 50b can be sealed in the shaft hole 11a. They are lined up alternately in the circumferential direction. Therefore, in order to connect the front cylinder bore 28 and the front suction chamber 17 adjacent to each other in the circumferential direction by the front rotary valve RF, the front bore communication passage 50b and the suction chamber communication passage 62 adjacent to each other in the circumferential direction are provided. It is only necessary to communicate with the introduction groove 22a. Therefore, the introduction groove 22a only needs to be formed in the front side rotary valve RF so as to extend in a part of the front side rotary valve RF in the circumferential direction. Therefore, the shape of the front-side rotary valve RF formed on the rotating shaft 22 can be simplified, and the length in the axial direction can be shortened. As a result, even if the front rotary valve RF is adopted as the suction method of the compressor 10 having the front suction chamber 17 in the cylinder block 11, the size does not increase in the axial direction.

    (12) The suction chamber communication passage 62 is formed together with the front suction chamber 17 when the cylinder block 11 is cast. Therefore, compared with the case where the suction chamber communication passage 62 is cut by a drill or the like after the cylinder block 11 is cast, labor for manufacturing the cylinder block 11 can be saved.

    (13) The suction chamber communication passage 62 is formed by connecting the first recess 60 extending from the first end surface 11b and the second recess 61 extending from the second end surface 11c. This makes it possible to reduce the opening area of the second recess 61 compared to the case where the suction chamber communication path is formed only by the second recess 61, and the opening of the second recess 61 is made by the relatively small thrust bearing 26. It can be closed.

  In addition, you may change the said embodiment as follows.

  In the embodiment, the suction chamber communication passage 62 is formed by connecting the first recess 60 extending from the first end surface 11b of the cylinder block 11 and the second recess 61 extending from the second end surface 11c, but the present invention is not limited thereto. As shown in FIG. 8, if the outer diameter of the thrust bearing 26 is sufficiently large, the suction chamber communication path may be formed only by the second recess 66 extending from the second end surface 11 c of the cylinder block 11. The second recess 66 allows the front suction chamber 17 and the introduction groove 22a to communicate directly.

  As a suction path for the refrigerant gas to the front cylinder bore 28, in addition to a path from the suction chamber communication path 62 to the front bore communication path 50b by the front rotary valve RF, as shown in FIG. A route via an in-shaft passage 65 communicating with the chamber 19 may be provided. In this case, the refrigerant is sucked into the front cylinder bore 28 only from the rear housing side suction chamber 19 via the in-shaft passage 65, and compared with the configuration in which the refrigerant is sucked into the front side cylinder bore 28 via the suction chamber communication passage 62. However, since the refrigerant is sucked into the front cylinder bore 28, the diameter of the in-shaft passage 65 can be reduced. Therefore, the rotary shaft 22 and the rotary valve RF can be reduced in size in the radial direction, and the overall size of the compressor 10 can be reduced.

  In the embodiment, the rotary valve is employed as the suction method on the front side and the rear side, but the suction method on the rear side may be based on the suction valve instead of the rotary valve.

  In the embodiment, on the rear side, the refrigerant in the rear side suction chamber 18 is collected in the rear housing side suction chamber 19 and sucked from the rear housing side suction chamber 19 into the rear side cylinder bore 29 via the rear side rotary valve RR. Not limited to. Also on the rear side, each rear side suction chamber 18 and the shaft hole 12a are individually communicated with each other through an introduction groove through a communication path, and the shaft hole 12a and the rear side cylinder bore 29 are individually communicated with each other through an introduction path. The refrigerant may be sucked into the rear cylinder bore 29 from the rear suction chamber 18 via the introduction groove and introduction passage of the rear rotary valve RR.

  In the embodiment, the suction port 44 is formed in the front cylinder block 11. However, for example, the suction port 44 may be formed in another part of the housing H such as the rear cylinder block 12.

  In the embodiment, the refrigerant that has passed through the suction port 44 is supplied to the front suction chamber 17 and the rear suction chamber 18 through the suction passage 43 formed in the cylinder blocks 11 and 12, but has passed through the suction port 44. The refrigerant may be supplied to the front suction chamber 17 and the rear suction chamber 18 via the swash plate chamber 25.

  In the embodiment, the three front-side discharge chambers 40 are arranged one by one between the adjacent front-side cylinder bores 28, but the front-side discharge chambers 40 may be formed in one or two places. In this case, as shown in FIG. 10, a part of the introduction groove 22 a is on the front side of the rotation shaft 22 so that the suction chamber communication passage 62 always communicates with the introduction groove 22 a regardless of the rotation angle of the rotation shaft 22. It is formed in an annular shape that goes around the peripheral surface of the.

  Three rear-side discharge chambers 42 are arranged one by one between the adjacent rear-side cylinder bores 29, but the rear-side discharge chambers 42 may be formed in one or two places.

  In the embodiment, three rear suction chambers 18 are formed, and the rear suction chambers 18 are arranged one by one between the adjacent rear cylinder bores 29. However, the present invention is not limited to this. The rear-side suction space may be the rear housing-side suction chamber 19 alone, or the rear-side suction chamber 18 may be formed in one place or two places.

  In the embodiment, the front suction chamber 17 communicating with the suction passage 43 has a larger volume than the other two front suction chambers 17, but the volume of the other two front suction chambers 17 is reduced to the suction passage 43. It may be larger than the volume of the front suction chamber 17 that communicates. When configured in this manner, the front-side suction chamber 17 communicating with the suction passage 43 is supplied with the refrigerant directly from the suction passage 43, so that the refrigerant is smoothly supplied to the front-side cylinder bore 28. Therefore, the volume is small. May be. On the other hand, in the other two front suction chambers 17, since the refrigerant once supplied to the storage chamber 13c is supplied to the front cylinder bore 28, in order to smoothly supply the refrigerant to the front cylinder bore 28, It is preferable to ensure a large volume and supply a large amount of refrigerant.

  The three front suction chambers 17 may have the same volume.

  In the embodiment, the front suction chamber 17 and the front discharge chamber 40 are formed across both the front housing 13 and the cylinder block 11, but may be formed only in the cylinder block 11.

  In the embodiment, the rear suction chamber 18 and the rear discharge chamber 42 are formed across both the rear housing 14 and the cylinder block 12, but may be formed only in the cylinder block 12.

  In the embodiment, the swash plate type compressor is embodied as a double-headed piston type swash plate type compressor. May be.

  RF: Front rotary valve as a rotary valve, 10: Double-head piston type swash plate compressor, 11, 12: Cylinder block, 11a, 12a ... Shaft hole, 17 ... Front suction chamber, 18 ... Rear suction chamber, 22 Rotating shaft, 22a ... introduction groove, 24 ... swash plate, 25 ... swash plate chamber, 26, 27 ... thrust bearing, 28 ... front side cylinder bore as cylinder bore, 28b ... front side discharge chamber as discharge chamber, 29 ... as cylinder bore Rear side cylinder bore, 29b ... rear side discharge chamber as discharge chamber, 30 ... double-ended piston, 32, 33 ... external piping, 40 ... front side discharge chamber as discharge chamber, 42 ... rear side discharge chamber as discharge chamber, 43 ... suction passage, 44 ... suction port, 50a ... suction chamber communication passage, 50b ... front bore communication passage, 60 ... first recess, 61, 6 ... second concave portion, 62 ... communicating passage for suction chamber.

Claims (8)

A cylinder block having a shaft hole, a plurality of cylinder bores, a swash plate chamber, and a suction chamber, the shaft hole extending through the cylinder block, and the plurality of cylinder bores circumferentially around the shaft hole The cylinder block, the suction chamber is provided separately from the swash plate chamber between the adjacent cylinder bores, and
A swash plate housed in the swash plate chamber;
A plurality of pistons moored to the swash plate and respectively inserted into the plurality of cylinder bores;
A rotating shaft that is inserted through the shaft hole and rotates integrally with the swash plate;
A rotary valve provided on the rotary shaft so as to rotate integrally with the rotary shaft,
The cylinder block has a suction chamber communication path that communicates the suction chamber and the shaft hole, and a plurality of bore communication paths that individually communicate the plurality of cylinder bores with the shaft hole,
The rotary valve is a swash plate type compressor that causes the suction chamber communication passage to sequentially communicate with the plurality of bore communication passages by rotating integrally with the rotary shaft. The suction chamber includes a plurality of suction chambers respectively positioned between adjacent cylinder bores,
2. The swash plate compressor according to claim 1, wherein the suction chamber communication path includes a plurality of suction chamber communication paths that individually communicate the plurality of suction chambers with the shaft hole.   The swash plate compressor according to claim 2, wherein the cylinder block has a plurality of discharge chambers that are respectively positioned between adjacent cylinder bores.   The swash plate compressor according to claim 3, wherein the plurality of discharge chambers are arranged outside the suction chamber in a radial direction of the cylinder block. The cylinder block has a suction port to which an external pipe is connected, and a suction passage that communicates the suction port and the suction chamber.
The swash plate compressor according to any one of claims 1 to 4, wherein the suction passage is provided separately from the swash plate chamber. The suction chamber communication passage is constituted by a recess formed in the inner wall of the shaft hole, and the recess has an open end communicating with the swash plate chamber,
A thrust bearing is disposed between the swash plate and the opening end of the recess,
The swash plate compressor according to any one of claims 1 to 5, wherein the thrust bearing closes an opening end of the recess. The suction chamber communication passage is formed in the inner wall of the suction chamber and has a first recess having an opening end that opens at an end surface in the axial direction of the cylinder block, and is formed in the inner wall of the shaft hole and the inclined wall. A second recess having an open end communicating with the plate chamber,
A thrust bearing is disposed between the swash plate and the open end of the second recess,
The swash plate compressor according to any one of claims 1 to 5, wherein the thrust bearing closes an opening end of the second recess.   The swash plate compressor according to any one of claims 1 to 7, wherein the plurality of cylinder bores are three cylinder bores.

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