JP5825367B2 - Vane type compressor - Google Patents

Description

  The present invention relates to a vane type compressor.

  For example, in the vane type compressor disclosed in Patent Document 1, as shown in FIG. 5, a housing 101 of the vane type compressor 100 includes a rear housing 102 and a front housing joined to the front end surface of the rear housing 102. 103. A cylinder block 104 is accommodated in the rear housing 102. In the rear housing 102, a front side plate 105 is joined to the front end face of the cylinder block 104, and a rear side plate 106 is joined to the rear end face of the cylinder block 104. A discharge is provided between the outer peripheral surface of the cylinder block 104, the inner peripheral surface of the rear housing 102 facing the outer peripheral surface, and one end surface of the front side plate 105 and the rear side plate 106 facing the cylinder block 104. A chamber 107 is partitioned. A rotating shaft 108 is rotatably supported by the front side plate 105 and the rear side plate 106, and the rotating shaft 108 passes through the cylinder block 104.

  As shown in FIG. 6, in the cylinder block 104, a rotor 109 is fixed to the rotary shaft 108 so as to be integrally rotatable with the rotary shaft 108. On the outer peripheral surface of the rotor 109, vane grooves 110 are formed radially at a plurality of locations, and vanes 111 are accommodated in the respective vane grooves 110 so as to be able to appear and retract. These vanes 111 define a plurality of compression chambers 112 in the cylinder block 104. The cylinder block 104 is formed with a discharge port 113 that allows the compression chamber 112 and the discharge chamber 107 to communicate with each other. The refrigerant gas compressed in the compression chamber 112 pushes the discharge valve 114 away and is discharged into the discharge chamber 107 through the discharge port 113.

  As shown in FIG. 5, a suction port 115 is formed in the upper part of the front housing 103. A suction chamber 116 communicating with the suction port 115 is formed in the front housing 103. Further, a suction port 117 communicating with the suction chamber 116 is formed in the front side plate 105. The cylinder block 104 is formed with a suction passage 118 that penetrates the cylinder block 104 in the entire axial direction. The compression chambers 112 and the suction chambers 116 in the suction stroke are communicated with each other via a suction port 117 and a suction passage 118, respectively.

  A discharge port 119 is formed in the upper part of the rear housing 102. A discharge region 120 is defined by a rear side plate 106 on the rear side of the rear housing 102. The discharge region 120 is provided with an oil separator 121 that separates the lubricating oil contained in the refrigerant gas. The oil separator 121 includes an oil separation chamber 122 and an oil separation cylinder 123 provided on the upper portion of the oil separation chamber 122. In the discharge region 120, an oil storage chamber 124 is defined outside the oil separator 121. Further, a discharge passage 125 that connects the discharge chamber 107 and the oil separation chamber 122 is formed in the rear side plate 106, and the discharge chamber 107 and the oil separator 121 are connected via the discharge passage 125. Further, the rear side plate 106 is formed with an oil supply passage 126 for guiding the lubricating oil stored in the oil storage chamber 124 to the vane groove 110.

  When the rotating shaft 108 rotates, the rotor 109 rotates, and the refrigerant gas is sucked from the suction chamber 116 through the suction port 117 and the suction passage 118 into each compression chamber 112 during the suction stroke. The refrigerant gas sucked into each compression chamber 112 is compressed by the volume reduction of the compression chamber 112 during the compression stroke. The compressed refrigerant gas is discharged from each compression chamber 112 to the discharge chamber 107 through the discharge port 113. The refrigerant gas discharged into the discharge chamber 107 is discharged to the discharge region 120 through the discharge passage 125. The refrigerant gas discharged to the discharge region 120 is blown to the outer peripheral surface of the oil separation cylinder 123 and guided to the lower side of the oil separation chamber 122 while turning the outer peripheral surface of the oil separation cylinder 123. At this time, the lubricating oil is separated from the refrigerant gas by centrifugal separation. The lubricating oil separated from the refrigerant gas is stored in the oil storage chamber 124 via the oil separation chamber 122. The lubricating oil stored in the oil storage chamber 124 is guided to the vane groove 110 through the oil supply passage 126, and the sliding portion between the vane 111 and the vane groove 110 is lubricated by the lubricating oil. On the other hand, the refrigerant gas from which the lubricating oil has been separated moves upward in the oil separation cylinder 123 and is discharged to the outside (for example, an external refrigerant circuit) via the discharge port 119.

JP 2010-38144 A

  Incidentally, in the vane type compressor 100 of Patent Document 1, a suction chamber 116 is formed in the front housing 103. That is, since the suction chamber 116 is formed at a position aligned with the cylinder block 104 in the axial direction of the rotary shaft 108, the suction chamber 116 makes the physique of the vane compressor 100 in the axial direction of the rotary shaft 108. It was a factor to increase the size. Further, since the suction chamber 116 is arranged at a position aligned with the cylinder block 104 in the axial direction of the rotary shaft 108, the suction port 115 formed in the upper part of the front housing 103 to the compression chamber 112 in the cylinder block 104 is arranged. Since the path is long and bent and is heated while passing through the path, the suction efficiency is reduced.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a vane type compressor that can improve the suction efficiency and can be downsized in the axial direction of the rotating shaft. is there.

In the vane type compressor that solves the above-described problems, a cylindrical cylinder block is accommodated in a housing, and a rotor having a vane is accommodated in the cylinder block so as to be rotatable along with the rotation of a rotating shaft. A compression chamber is defined by an inner wall of the cylinder block and the vane, and the housing is a vane type compressor provided with a suction port and a suction chamber communicating with the suction port. chamber, said extending in a circumferential direction of the rotary shaft between the cylinder block and said housing, said suction chamber and said suction port is disposed to overlap with the compression chamber in the radial direction of the rotary shaft A discharge chamber into which the refrigerant compressed in the compression chamber is discharged is formed between the cylinder block and the housing, and the suction chamber and the discharge chamber are formed. Chamber and is arranged in the axial direction of the rotary axis between the cylinder block housing.

According to this, since the suction chamber and the suction port are arranged so as to overlap the compression chamber in the radial direction of the rotation shaft, they are formed at positions aligned with the cylinder block as in the prior art in the axial direction of the rotation shaft. Can be abolished or reduced. As a result, the vane compressor can be downsized in the axial direction of the rotary shaft. Furthermore, by arranging the suction port, the suction chamber, and the compression chamber so as to overlap in the radial direction, the refrigerant is not heated by the heat in the vane compressor, and the suction path is bent. Therefore, since it is sucked into the compression chamber, the suction efficiency can be improved. Further, the suction chamber can be formed at a desired position in the circumferential direction of the cylinder block. For example, when a vane type compressor is mounted on a vehicle, the arrangement position of the suction port is uniquely determined to avoid interference with auxiliary machines arranged around the installation space of the vane type compressor. May be. Even in such a case, the suction chamber can be formed at a position corresponding to the position where the suction port is arranged, and the design freedom of the vane type compressor can be improved.
In the vane type compressor that solves the above-described problems, a cylindrical cylinder block is accommodated in a housing, and a rotor having a vane is accommodated in the cylinder block so as to be rotatable along with the rotation of a rotating shaft. A compression chamber is defined by an inner wall of the cylinder block and the vane, and the housing is a vane type compressor provided with a suction port and a suction chamber communicating with the suction port. A chamber extends between the cylinder block and the housing in a circumferential direction of the rotating shaft, and the suction chamber and the suction port are arranged to overlap the compression chamber in the radial direction of the rotating shaft. The cylinder block is formed with two suction ports communicating with the suction chamber, and the refrigerant in the suction chamber is sucked into the compression chamber through the suction ports. , Each inlet port, the length of the path of the coolant leading to the suction port through the suction chamber from the suction port is arranged at a position the same length, respectively.
According to this, the suction efficiency can be further improved. Further, the refrigerant sucked into the suction chamber from the suction port can be made to flow evenly to the respective suction ports. Therefore, it is possible to prevent the suction pulsation from occurring due to the refrigerant sucked in one of the suction ports.

  In the vane type compressor, a discharge chamber into which the refrigerant compressed in the compression chamber is discharged is formed between the cylinder block and the housing, and the suction chamber and the discharge chamber are the cylinder It is preferable that they are arranged side by side in the axial direction of the rotating shaft between the block and the housing.

In the vane compressor, the suction chamber is preferably formed over the entire circumference in the circumferential direction of the cylinder block.
According to this, as compared with the case where the suction chamber is not formed over the entire circumference of the cylinder block, the volume of the suction chamber can be secured as much as possible.

  In the vane type compressor, a discharge chamber into which the refrigerant compressed in the compression chamber is discharged is formed between the cylinder block and the housing, and the suction chamber and the discharge chamber are the cylinder It is preferable that the block and the housing are arranged side by side in the circumferential direction of the cylinder block by being separated by a partition extending in the axial direction of the rotating shaft.

According to this, the volume ratio of the suction chamber and the discharge chamber can be adjusted by adjusting the position of the partition wall in the circumferential direction of the cylinder block.
In the vane type compressor, a shaft seal device is interposed between the housing and the rotary shaft, and the shaft seal device is housed in a housing chamber formed in the housing, and the suction chamber It is preferable that the housing chamber communicates with the communication passage.

  According to this, a part of the refrigerant sucked into the suction chamber can be introduced into the storage chamber via the communication passage. As a result, the shaft seal device can be cooled by the refrigerant introduced into the storage chamber, and lubrication of the sliding portion between the rotating shaft and the shaft seal device can be improved.

  In the vane type compressor, the cylinder block is preferably formed with a plurality of suction ports communicating with the suction chamber, and the refrigerant in the suction chamber is sucked into the compression chamber through the suction port. .

In the above SL vane compressor, said cylinder block, said intake port are two forms, each inlet port, the length of the refrigerant path extending through said suction chamber from said intake port to each inlet It is preferable that the lengths are arranged at positions having the same length.

  According to the present invention, it is possible to improve the suction efficiency and reduce the size in the axial direction of the rotating shaft.

A side sectional view showing a vane type compressor in an embodiment. FIG. 1 is a sectional view taken along line 1-1 in FIG. FIG. 2 is a sectional view taken along line 2-2 in FIG. 1. The longitudinal cross-sectional view of the vane type compressor in another embodiment. The sectional side view which shows the vane type compressor in a prior art example. FIG. 6 is a sectional view taken along line 3-3 in FIG. 5.

Hereinafter, an embodiment embodying the present invention will be described with reference to FIGS.
As shown in FIG. 1, the housing 11 of the vane compressor 10 is formed of a rear housing 12 and a front housing 13 joined to a front end surface (one end surface) of the rear housing 12. The front housing 13 has a cylindrical cylinder block 14 accommodated in the rear housing 12 (housing 11). Therefore, in this embodiment, the cylinder block 14 is integrated with the front housing 13.

  A side plate 15 is joined to the rear end surface of the cylinder block 14. A rotary shaft 16 is rotatably supported by the front housing 13 and the side plate 15, and the rotary shaft 16 passes through the cylinder block 14. A lip seal type shaft seal device 17 a is interposed between the front housing 13 and the rotary shaft 16. The shaft seal device 17 a is accommodated in an accommodation chamber 17 formed in the front housing 13. The shaft seal device 17 a prevents the refrigerant gas from leaking along the peripheral surface of the rotating shaft 16. In the cylinder block 14, a cylindrical rotor 18 is fixed to the rotary shaft 16 so as to be integrally rotatable with the rotary shaft 16. The rotor 18 has a front end face (one end face) facing the end face of the front housing 13 and a rear end face (other end face) facing the side plate 15.

  As shown in FIGS. 2 and 3, the inner peripheral surface of the cylinder block 14 is formed in an elliptical shape. On the outer peripheral surface of the rotor 18, vane grooves 18 a are formed radially at a plurality of locations, and vanes 19 are accommodated in the respective vane grooves 18 a so as to be able to appear and retract. Lubricating oil is supplied to each vane groove 18a.

  When the tip surface of the vane 19 comes into contact with the inner peripheral surface of the cylinder block 14 due to the rotation of the rotor 18 accompanying the rotation of the rotating shaft 16, the outer peripheral surface of the rotor 18, the inner wall of the cylinder block 14, and the adjacent vane 19 A plurality of compression chambers 21 are defined between the front housing 13 and the side plate 15. In the vane type compressor 10, a stroke in which the compression chamber 21 increases in volume with respect to the rotation direction of the rotor 18 is a suction stroke, and a stroke in which the compression chamber 21 decreases in volume is a compression stroke.

  As shown in FIG. 1, a suction port 22 is formed in the upper portion of the rear housing 12. A recess 14 a is formed on the outer peripheral surface of the cylinder block 14 over the entire circumference in the circumferential direction of the cylinder block 14. A suction chamber 20 communicating with the suction port 22 is defined by the recess 14 a and the inner peripheral surface of the rear housing 12. Therefore, the suction chamber 20 extends in the circumferential direction of the rotary shaft 16 between the cylinder block 14 and the rear housing 12. The suction chamber 20 and the suction port 22 are disposed so as to overlap the compression chamber 21 in the radial direction of the rotating shaft 16.

  As shown in FIG. 2, the cylinder block 14 is formed with a pair of suction ports 23 that communicate with the suction chamber 20. That is, in the present embodiment, the cylinder block 14 is formed with two suction ports 23. Each suction port 23 is disposed at a position where the lengths of the refrigerant gas paths from the suction port 22 through the suction chamber 20 to the suction ports 23 are the same. The compression chambers 21 and the suction chambers 20 during the suction stroke are communicated with each other via the suction ports 23.

  As shown in FIG. 3, a concave portion 14 b that is recessed from the outer peripheral surface of the cylinder block 14 is formed on each outer peripheral surface of the cylinder block 14 that sandwiches the rotating shaft 16. Each recess 14b is formed of an extending surface 141b extending from the outer peripheral surface of the cylinder block 14 toward the rotating shaft 16, and an attachment surface 142b extending toward the outer peripheral surface of the cylinder block 14 while intersecting the extending surface 141b. Has been. A pair of discharge chambers 30 are defined by the extended surfaces 141b, the mounting surfaces 142b, and the inner peripheral surface of the rear housing 12. Therefore, each discharge chamber 30 is formed between the cylinder block 14 and the rear housing 12 in the radial direction of the rotating shaft 16.

  The cylinder block 14 is formed with a discharge port 31 that opens to each mounting surface 142b and communicates the compression chamber 21 and the discharge chamber 30 during the compression stroke. Each discharge port 31 can be opened and closed by a discharge valve 32 attached to the attachment surface 142b. Then, the refrigerant gas compressed in the compression chamber 21 pushes out the discharge valve 32 and is discharged into the discharge chamber 30 through the discharge port 31.

  As shown in FIG. 1, each discharge chamber 30 is located closer to the side plate 15 than the suction chamber 20. The suction chamber 20 and each discharge chamber 30 are arranged side by side in the axial direction of the rotary shaft 16 between the cylinder block 14 and the rear housing 12 in the radial direction of the rotary shaft 16. In addition, a communication passage 25 that connects the suction chamber 20 and the storage chamber 17 is formed in the front housing 13.

  A discharge port 34 is formed in the upper portion of the rear housing 12. A discharge region 35 is defined by a side plate 15 on the rear side of the rear housing 12. An oil separator 36 for separating lubricating oil contained in the refrigerant gas is disposed in the discharge region 35. The oil separator 36 has a bottomed cylindrical case 36a, and a cylindrical oil separation cylinder 36b is fitted and fixed to the opening side of the case 36a. An oil passage 36c that connects the inside of the case 36a and the bottom side of the discharge region 35 is formed in the lower portion of the case 36a. The side plate 15 and the case 36a are formed with a communication passage 37 that allows the discharge chamber 30 to communicate with the inside of the case 36a. Further, the side plate 15 is formed with an oil supply passage 15d for guiding the lubricating oil stored on the bottom side of the discharge region 35 to the vane groove 18a.

Next, the operation of this embodiment will be described.
When the rotating shaft 16 rotates, the rotor 18 and the vane 19 rotate, and the refrigerant gas is sucked into the suction chamber 20 from the outside of the vane compressor 10 (for example, an external refrigerant circuit) through the suction port 22. The refrigerant gas sucked into the suction chamber 20 is sucked into the compression chambers 21 during the suction stroke through the suction ports 23. The refrigerant gas sucked into each compression chamber 21 is compressed by the volume reduction of the compression chamber 21 during the compression stroke. The compressed refrigerant gas is discharged from the compression chambers 21 to the discharge chambers 30 through the discharge ports 31.

  The refrigerant gas in each discharge chamber 30 flows out into the case 36a through the communication passage 37 and is sprayed on the outer peripheral surface of the oil separation cylinder 36b, and in the case 36a while turning around the outer peripheral surface of the oil separation cylinder 36b. It is led below. At this time, the lubricating oil is separated from the refrigerant gas by centrifugation. The lubricating oil separated from the refrigerant gas moves to the bottom side of the case 36a and is stored at the bottom of the discharge region 35 through the oil passage 36c. The lubricating oil stored at the bottom of the discharge region 35 is guided from the oil supply passage 15d to the vane groove 18a, and pushes the vane 19 to the outer peripheral side as back pressure. And the compression chamber 21 is divided by the vane 19 pushed out to the outer peripheral side. In addition, the sliding portion between the vane 19 and the vane groove 18a is lubricated by the lubricating oil guided to the vane groove 18a. On the other hand, in the oil separator 36, the refrigerant gas from which the lubricating oil has been separated moves upward in the oil separation cylinder 36b, and to the outside of the vane compressor 10 (for example, an external refrigerant circuit) via the discharge port 34. Discharged.

  A part of the refrigerant gas sucked into the suction chamber 20 from the suction port 22 is introduced into the storage chamber 17 through the communication passage 25. The shaft sealing device 17a is cooled by the refrigerant gas introduced into the storage chamber 17, and the sliding portion between the rotating shaft 16 and the shaft sealing device 17a is well lubricated.

  In the vane type compressor 10 configured as described above, the suction chamber 20 is formed between the cylinder block 14 and the rear housing 12 in the radial direction of the rotary shaft 16. Therefore, unlike the prior art, there is no need to form the suction chamber 20 at a position aligned with the cylinder block 14 in the axial direction of the rotary shaft 16, and the vane compressor 10 is downsized in the axial direction of the rotary shaft 16. Is done. Furthermore, by arranging the suction port 22, the suction chamber 20, and the compression chamber 21 so as to overlap in the radial direction, the refrigerant gas is not heated by the heat in the vane compressor 10, and The suction path is sucked into the compression chamber 21 without being bent.

In the above embodiment, the following effects can be obtained.
(1) The suction chamber 20 extends between the cylinder block 14 and the rear housing 12 in the circumferential direction of the rotary shaft 16, and the suction chamber 20 and the suction port 22 are connected to the compression chamber 21 in the radial direction of the rotary shaft 16. Arranged to overlap. According to this, the suction chamber 20 formed at a position aligned in the axial direction of the rotating shaft 16 with respect to the cylinder block 14 as in the prior art can be eliminated or reduced. As a result, the vane compressor 10 can be downsized in the axial direction of the rotary shaft 16. Furthermore, by arranging the suction port 22, the suction chamber 20, and the compression chamber 21 so as to overlap in the radial direction, the refrigerant gas is not heated by the heat in the vane compressor 10, and Since the suction path is sucked into the compression chamber 21 without being bent, the suction efficiency can be improved.

  (2) The suction chamber 20 and the discharge chamber 30 are arranged side by side in the axial direction of the rotary shaft 16 between the cylinder block 14 and the rear housing 12 in the radial direction of the rotary shaft 16. Accordingly, the suction chamber 20 can be formed at a desired position in the circumferential direction of the cylinder block 14. For example, when the vane compressor 10 is mounted on a vehicle, the arrangement position of the intake port 22 is unambiguous in order to avoid interference with auxiliary machines and the like arranged around the installation space of the vane compressor 10. May be determined. Even in such a case, the suction chamber 20 can be formed at a position corresponding to the position where the suction port 22 is arranged, and the design freedom of the vane compressor 10 can be improved.

  (3) The suction chamber 20 is formed over the entire circumference of the cylinder block 14. According to this, as compared with the case where the suction chamber 20 is not formed over the entire circumference of the cylinder block 14, the volume of the suction chamber 20 can be ensured as much as possible.

  (4) The suction chamber 20 and the storage chamber 17 are communicated with each other through the communication passage 25. According to this, a part of the refrigerant gas sucked into the suction chamber 20 can be introduced into the storage chamber 17 through the communication passage 25. As a result, the shaft seal device 17a can be cooled by the refrigerant gas introduced into the storage chamber 17, and lubrication of the sliding portion between the rotating shaft 16 and the shaft seal device 17a can be improved. .

(5) A pair of suction ports 23 communicating with the suction chamber 20 is formed in the cylinder block 14. According to this, the suction efficiency can be further improved.
(6) The suction ports 23 are arranged at positions where the lengths of the refrigerant gas paths from the suction port 22 through the suction chamber 20 to the suction ports 23 are the same. According to this, the refrigerant gas sucked into the suction chamber 20 from the suction port 22 can flow evenly to the respective suction ports 23. Therefore, it is possible to prevent the suction pulsation from occurring due to the refrigerant gas being sucked in bias toward one of the suction ports 23.

  (7) The suction chamber 20 is formed over the entire circumference of the cylinder block 14. According to this, the space on the opposite side of the suction port 22 from each suction port 23 in the suction chamber 20 can function as a muffler chamber. As a result, it is possible to further suppress the suction pulsation and to suppress noise.

  (8) Since the suction chamber 20 is formed over the entire circumference in the circumferential direction of the cylinder block 14, compared with the case where the suction chamber 20 is not formed over the entire circumference in the circumferential direction of the cylinder block 14. The temperature distribution of the cylinder block 14 due to the refrigerant gas sucked into the chamber 20 can be easily made uniform in the circumferential direction of the cylinder block 14. As a result, the temperature distribution of the cylinder block 14 becomes non-uniform in the circumferential direction of the cylinder block 14, so that the cylinder block 14 can be prevented from being distorted by the heat of the refrigerant gas.

  (9) In the present embodiment, the suction chamber 20 is formed between the cylinder block 14 and the rear housing 12 in the radial direction of the rotating shaft 16 and is as far away from the rotating shaft 16 as possible. The rotating shaft 16 is easy to have heat by rotating. However, since the suction chamber 20 is located as far as possible from the rotating shaft 16, the refrigerant gas sucked into the suction chamber 20 can be prevented from being heated by the heat from the rotating shaft 16.

  (10) In the present embodiment, unlike the prior art, it is not necessary to form the suction chamber 116 between the front housing 103 and the front side plate 105, and it is also necessary to form the suction passage 118 penetrating the cylinder block 104. Absent. Therefore, the front housing 103, the front side plate 105, and the cylinder block 104 can be formed by one member (front housing 13), and the number of parts can be reduced.

In addition, you may change the said embodiment as follows.
As shown in FIG. 4, the suction chamber 20A and the discharge chamber 30A are arranged side by side in the circumferential direction of the cylinder block 14A between the cylinder block 14A and the rear housing 12 in the radial direction of the rotating shaft 16. Also good. The inner peripheral surface of the cylinder block 14A is formed in a perfect circle shape. When the tip surface of the vane 19 comes into contact with the inner peripheral surface of the cylinder block 14A due to the rotation of the rotor 18 accompanying the rotation of the rotating shaft 16, the outer peripheral surface of the rotor 18 and the inner peripheral surface of the cylinder block 14A are adjacent to the vane. A compression chamber 21 </ b> A is defined between the front housing 13 and the side plate 15. In the vane type compressor 10, the stroke in which the compression chamber 21 </ b> A expands the volume with respect to the rotation direction of the rotor 18 is the suction stroke, and the stroke in which the compression chamber 21 </ b> A decreases the volume is the compression stroke.

  A pair of partition walls 40 projecting from the outer peripheral surface in the radial direction of the rotating shaft 16 and extending in the axial direction of the rotating shaft 16 are formed on the outer peripheral surface of the cylinder block 14A. Each partition wall 40 is disposed at a position 180 degrees away from each other in the circumferential direction of the cylinder block 14A. The suction chamber 20A and the discharge chamber 30A are arranged side by side in the circumferential direction of the cylinder block 14A by being separated by the partition walls 40 between the cylinder block 14A and the rear housing 12 in the radial direction of the rotating shaft 16. Has been.

  The cylinder block 14A has a suction port 23A communicating with the suction chamber 20A. The compression chamber 21A and the suction chamber 20A during the suction stroke are communicated with each other via the suction port 23A. A mounting surface 141A is formed on the outer peripheral surface of the cylinder block 14A, and a discharge port 31A that opens to the mounting surface 141A and communicates the compression chamber 21A and the discharge chamber 30A is formed in the cylinder block 14A. The discharge port 31A can be opened and closed by a discharge valve 32 attached to the attachment surface 141A. Then, the refrigerant gas compressed in the compression chamber 21A pushes out the discharge valve 32 and is discharged into the discharge chamber 30A through the discharge port 31A.

  According to the above configuration, the volume ratio between the suction chamber 20A and the discharge chamber 30A can be adjusted by adjusting the position of the partition wall 40 in the circumferential direction of the cylinder block 14A. Further, as in the case where the suction chamber 20A and the discharge chamber 30A are arranged side by side in the axial direction of the rotary shaft 16 between the cylinder block 14 and the rear housing 12 in the radial direction of the rotary shaft 16, The axial length of the rotating shaft 16 is not shortened by the amount corresponding to the suction chamber 20A. That is, for example, the length in the axial direction of the rotary shaft 16 in the discharge chamber 30A when the suction chamber 20A is formed at a position aligned with the cylinder block 14A in the axial direction of the rotary shaft 16 as in the prior art. The discharge valve 32 having the same length as that of the prior art can be used.

  In the embodiment, a suction chamber may be formed in the front housing 13 in addition to the suction chamber 20 between the cylinder block 14 and the rear housing 12. In this case, a larger suction space can be secured and suction pulsation can be reduced.

In the embodiment, the suction chamber 20 may be located on the side plate 15 side with respect to each discharge chamber 30.
In the embodiment, the suction chamber 20 may not be formed over the entire circumference of the cylinder block 14. For example, the suction chamber 20 may be formed over a range of 350 degrees in the circumferential direction of the cylinder block 14, and the range in which the suction chamber 20 is formed can be changed as appropriate.

In the embodiment, the communication path 25 may be deleted.
In the embodiment, the cylinder block 14 may be a separate body from the front housing 13.

In the embodiment, the number of the suction ports 23 is not particularly limited.
In the embodiment, each of the suction ports 23 may be disposed at a position where the lengths of the refrigerant gas paths from the suction port 22 through the suction chamber 20 to the respective suction ports 23 are different from each other.

  DESCRIPTION OF SYMBOLS 10 ... Vane type compressor, 11 ... Housing, 14, 14A ... Cylinder block, 16 ... Rotating shaft, 17 ... Storage chamber, 17a ... Shaft seal device, 18 ... Rotor, 19 ... Vane, 20, 20A ... Suction chamber, 21 , 21A ... compression chamber, 22 ... suction port, 23, 23A ... suction port, 25 ... communication passage, 30, 30A ... discharge chamber, 40 ... partition wall.

Claims (8)

A cylindrical cylinder block is accommodated in the housing, and a rotor having a vane is accommodated in the cylinder block so as to be rotatable in accordance with the rotation of the rotation shaft, and the inner wall of the cylinder block and the vane A compression chamber is defined, and the housing is a vane compressor provided with a suction port and a suction chamber communicating with the suction port;
The suction chamber extends between the cylinder block and the housing in the circumferential direction of the rotation shaft, and the suction chamber and the suction port are arranged to overlap the compression chamber in the radial direction of the rotation shaft. and,
A discharge chamber for discharging the refrigerant compressed in the compression chamber is formed between the cylinder block and the housing;
The vane compressor, wherein the suction chamber and the discharge chamber are arranged side by side in the axial direction of the rotating shaft between the cylinder block and the housing . A cylindrical cylinder block is accommodated in the housing, and a rotor having a vane is accommodated in the cylinder block so as to be rotatable in accordance with the rotation of the rotation shaft, and the inner wall of the cylinder block and the vane A compression chamber is defined, and the housing is a vane compressor provided with a suction port and a suction chamber communicating with the suction port;
The suction chamber extends between the cylinder block and the housing in the circumferential direction of the rotation shaft, and the suction chamber and the suction port are arranged to overlap the compression chamber in the radial direction of the rotation shaft. and,
Two suction ports communicating with the suction chamber are formed in the cylinder block, and the refrigerant in the suction chamber is sucked into the compression chamber through the suction ports,
Each of the suction ports is arranged at a position where the lengths of the refrigerant paths from the suction port to the suction ports through the suction chamber are the same length . A discharge chamber for discharging the refrigerant compressed in the compression chamber is formed between the cylinder block and the housing;
The vane type compressor according to claim 2 , wherein the suction chamber and the discharge chamber are arranged side by side in the axial direction of the rotation shaft between the cylinder block and the housing. The suction chamber, a vane type compressor according to claim 1 or claim 3, characterized in that it is formed over the whole circumference of the cylinder block. A discharge chamber for discharging the refrigerant compressed in the compression chamber is formed between the cylinder block and the housing;
The suction chamber and the discharge chamber are arranged side by side in the circumferential direction of the cylinder block by being separated by a partition extending in the axial direction of the rotating shaft between the cylinder block and the housing. The vane type compressor according to claim 2 . A shaft seal device is interposed between the housing and the rotary shaft, and the shaft seal device is housed in a housing chamber formed in the housing,
The vane type compressor according to any one of claims 1 to 5 , wherein the suction chamber and the storage chamber communicate with each other through a communication passage. Said cylinder block, said plurality of suction ports communicating with the suction chamber is formed, refrigerant in the suction chamber, according to claim 1, characterized in that it is sucked into the compression chamber through the suction port Vane type compressor. Two suction ports are formed in the cylinder block,
8. The vane according to claim 7 , wherein the suction ports are arranged at positions where the lengths of the refrigerant paths from the suction port to the suction ports through the suction chamber are the same. Mold compressor.