JP5874600B2 - Tandem vane compressor - Google Patents

Description

  The present invention relates to a tandem vane compressor.

  Patent Documents 1 to 5 disclose conventional tandem vane compressors. In these tandem vane compressors, a suction chamber, a discharge chamber, a first cylinder chamber, and a second cylinder chamber are formed in a housing, and a drive shaft is rotatably supported. These tandem vane compressors are provided with a first compression mechanism and a second compression mechanism.

  The first compression mechanism is rotatably provided in the first cylinder chamber by a drive shaft, is provided with a first rotor having a plurality of first vane grooves, and is provided so as to be able to protrude and retract in each first vane groove. And a first vane that forms a first compression chamber positioned forward together with the inner surface of the cylinder chamber and the outer surface of the first rotor.

  Further, the second compression mechanism is provided rotatably in the second cylinder chamber by a drive shaft, is provided with a second rotor formed with a plurality of second vane grooves, and can be projected and retracted in each second vane groove, And a second vane that forms a second compression chamber located rearward together with the inner surface of the second cylinder chamber and the outer surface of the second rotor.

  When these tandem vane compressors are used in an air conditioner such as a vehicle, the drive shaft is rotationally driven through, for example, an electromagnetic clutch. As a result, the first and second compression mechanisms operate. That is, the first and second rotors rotate, and the first and second compression chambers perform a suction stroke, a compression stroke, and a discharge stroke. For this reason, the refrigerant gas is sucked into the first and second compression chambers from the suction chamber, compressed in the first and second compression chambers, and discharged into the discharge chamber. The high-pressure refrigerant gas discharged into the discharge chamber is supplied to the refrigeration circuit of the air conditioner.

  Thus, in these tandem vane compressors, the first and second compression mechanisms perform the suction stroke, the compression stroke, and the discharge stroke, respectively, so that the discharge capacity per one rotation of the drive shaft can be increased.

  In addition, in order to increase the discharge capacity, simply increasing the axial length of a single cylinder type vane compressor having a single cylinder chamber and a rotor makes it easy for each vane to tilt forward and backward. It is likely that refrigerant gas leaks and the slidability of each vane deteriorates. In this respect, in these tandem vane type compressors, the first and second vanes are not easily tilted forward and backward, and there is little leakage of refrigerant gas from the first and second compression chambers. It seems to have excellent mobility. For this reason, it seems that these tandem type vane type compressors can exhibit excellent mechanical efficiency.

  Furthermore, since these tandem vane compressors can have the same barrel diameter as that of the single cylinder vane compressor, they can also exhibit excellent mountability.

Japanese Utility Model Publication No.59-90086 JP 58-144687 A Japanese Utility Model Publication No. 3-102086 Japanese Utility Model Publication No. 60-39793 Japanese Utility Model Publication No. 3-118294

  However, the conventional tandem vane type compressor has a first back pressure chamber formed between a bottom surface of each first vane and each first vane groove, a bottom surface of each second vane, and each second vane. There is no structure in which high-pressure lubricating oil can be supplied together with the second back pressure chamber formed between the grooves. Therefore, in these tandem type vane compressors, the first and second vanes are not pressed against the inner surfaces of the first and second cylinder chambers while the first and second compression mechanisms perform the compression stroke and the discharge stroke, respectively. There is concern about leakage of refrigerant gas from the first and second compression chambers. For this reason, it is difficult for these tandem vane compressors to reliably exhibit high mechanical efficiency.

  Therefore, the first back pressure chamber is defined between the bottom surface of each first vane and each first vane groove, and the second back pressure chamber is defined between the bottom surface of each second vane and each second vane groove. It is conceivable to form a back pressure supply path in the housing. The back pressure supply path communicates the discharge chamber with each first back pressure chamber and each second back pressure chamber. In this case, since each of the first and second vanes is suitably pressed against the inner surfaces of the first and second cylinder chambers by the high-pressure lubricant in the discharge chamber while the first and second compression mechanisms perform the compression stroke and the discharge stroke, respectively. Leakage of refrigerant gas from the first and second compression chambers is reduced. For this reason, this tandem vane type compressor can reliably exhibit high mechanical efficiency.

  However, the tandem vane compressor has a front side plate, a front housing, a center side plate, a first cylinder block, a rear side plate, a second cylinder block, and a rear housing. When the suction chamber is formed and the discharge chamber is formed by the rear housing and the rear side plate, the pressure between the front side plate and the drive shaft is low, and the pressure between the rear side plate and the drive shaft is high. In the tandem vane compressor, the first supply path that communicates the discharge chamber and each first back pressure chamber, and the discharge chamber and each second back pressure chamber, of the back pressure supply path, communicate with each other. A second supply path is formed in the center side plate.

  In this case, since the lubricating oil supplied to the first supply path reaches the first back pressure chamber and then the pressure between the front side plate and the drive shaft is low, the differential pressure causes the first back pressure chamber to enter the first back pressure chamber. It flows in one direction toward the front. Next, the lubricating oil in the first back pressure chamber reaches the suction chamber through the space between the front side plate and the drive shaft. For this reason, it is possible to release the back pressure in the first back pressure chamber. Further, a front bearing that can be provided between the front side plate and the drive shaft is lubricated.

  However, since the lubricating oil supplied to the second supply passage reaches the second back pressure chamber and then has a high pressure between the rear side plate and the drive shaft, the second back pressure chamber is moved backward in the second back pressure chamber. It is difficult to flow in the direction. The center side plate and the drive shaft are at a high pressure close to the discharge pressure because the back pressure supply path is formed in the center side plate. For this reason, the back pressure in the second back pressure chamber cannot be released, the back pressure in the second back pressure chamber becomes excessively high, and the power loss increases.

  The present invention has been made in view of the above-described conventional situation, and can increase the discharge capacity per one rotation of the drive shaft, has excellent mountability, and has excellent mechanical efficiency and reduction of power loss. Providing a tandem vane type compressor that can be demonstrated is an issue to be solved.

The tandem vane compressor of the present invention includes a housing in which a suction chamber, a discharge chamber, a first cylinder chamber and a second cylinder chamber are formed,
A drive shaft rotatably supported by the housing;
A first rotor provided in the first cylinder chamber so as to be rotatable by the drive shaft and formed with a plurality of first vane grooves, and provided in the first vane grooves so as to be able to project and retract, the first cylinder chamber. A first compression mechanism having a first vane that forms a first compression chamber located forward together with an inner surface of the first rotor and an outer surface of the first rotor;
A second rotor provided in the second cylinder chamber so as to be rotatable by the drive shaft and having a plurality of second vane grooves; And a second compression mechanism having a second vane that forms a second compression chamber positioned rearward together with the inner surface of the second rotor and the outer surface of the second rotor,
A space between the bottom surface of each first vane and each first vane groove is a first back pressure chamber,
A space between the bottom surface of each second vane and each second vane groove is a second back pressure chamber,
The housing is provided with a back pressure supply passage that communicates the discharge chamber with the first back pressure chamber and the second back pressure chamber,
The housing extends in a radial direction with respect to the drive shaft, a front side plate that pivotally supports the drive shaft, a front housing that forms the suction chamber together with the front side plate, and a radial direction with respect to the drive shaft Extending in the radial direction with respect to the drive shaft, a center side plate that pivotally supports the drive shaft, a first cylinder block that forms the first cylinder chamber together with the front side plate and the center side plate, A rear side plate that pivotally supports the drive shaft; a second cylinder block that forms the second cylinder chamber together with the center side plate and the rear side plate; and a rear housing that forms the discharge chamber together with the rear side plate. ,
The back pressure supply path is formed in the center side plate, and is formed in the center side plate, the first supply path communicating the discharge chamber and the first back pressure chamber, and the discharge chamber and the A second supply path communicating with the second back pressure chamber;
The housing includes a low pressure chamber that houses a rear end portion of the drive shaft, and a low pressure passage that communicates the suction chamber and the low pressure chamber (Claim 1).

  In the tandem vane type compressor of the present invention, a space between the bottom surface of each first vane and each first vane groove serves as a first back pressure chamber, and a space between each bottom surface of each second vane and each second vane groove. Is a second back pressure chamber, and a back pressure supply path is formed in the housing. The back pressure supply path communicates the discharge chamber with each of the first back pressure chambers and each of the second back pressure chambers. Therefore, while the first and second compression mechanisms perform the compression stroke and the discharge stroke, respectively, The two vanes are suitably pressed against the inner surfaces of the first and second cylinder chambers by the high-pressure lubricant in the discharge chamber. For this reason, in this tandem type vane type compressor, leakage of the refrigerant gas from the first and second compression chambers is reduced, and high mechanical efficiency can be reliably exhibited.

  In the tandem vane compressor, the housing includes a front side plate, a front housing, a center side plate, a first cylinder block, a rear side plate, a second cylinder block, and a rear housing. The suction chamber is formed by the rear housing, and the discharge chamber is formed by the rear housing and the rear side plate. On the other hand, the housing is formed with a low pressure chamber that houses the rear end portion of the drive shaft, and a low pressure passage that communicates the suction chamber and the low pressure chamber. For this reason, the pressure between the front side plate and the drive shaft is low, and the pressure between the rear side plate and the drive shaft is also low. And in this tandem type vane type compressor, among the back pressure supply paths, the first supply path that communicates the discharge chamber and each first back pressure chamber, and the discharge chamber and each second back pressure chamber communicate. A second supply path is formed in the center side plate.

  For this reason, since the lubricating oil supplied to the first supply passage reaches the first back pressure chamber and then the pressure between the front side plate and the drive shaft is low, the differential pressure causes the first back pressure chamber to enter the first back pressure chamber. It flows in one direction toward the front. Next, the lubricating oil in the first back pressure chamber reaches the suction chamber through the space between the front side plate and the drive shaft. For this reason, it is possible to release the back pressure in the first back pressure chamber. Further, a front bearing that can be provided between the front side plate and the drive shaft is lubricated.

  In addition, since the lubricating oil supplied to the second supply passage reaches the second back pressure chamber and the pressure between the rear side plate and the drive shaft is low, the second back pressure chamber is moved rearward by the differential pressure. Flows in one direction. Next, the lubricating oil in the second back pressure chamber reaches the suction chamber through the low pressure chamber and the low pressure passage between the rear side plate and the drive shaft. For this reason, the back pressure in the second back pressure chamber can be released. For this reason, the back pressure in the second back pressure chamber is not excessively high, and power loss is unlikely to occur. The center bearing that can be provided between the center side plate and the drive shaft is lubricated by lubricating oil that exists behind the first back pressure chamber and in front of the second back pressure chamber. Further, the rear sliding bearing that can be provided between the rear side plate and the drive shaft is lubricated by the lubricating oil existing behind the second back pressure chamber.

  Therefore, in this tandem type vane compressor, the discharge capacity per one rotation of the drive shaft can be increased, and it is possible to exhibit excellent mechanical efficiency and reduction of power loss while being excellent in mountability.

  The housing has a first suction passage that communicates the suction chamber and the first compression chamber during the suction stroke of the first compression mechanism, and a second that communicates the suction chamber and the second compression chamber during the suction stroke of the second compression mechanism. A suction passage may be formed. A front suction hole that communicates with the suction chamber may be formed in the front side plate. A first suction space that communicates with the front suction hole may be formed in the first cylinder block. A center suction hole communicating with the first suction space may be formed in the center side plate. A second suction space that communicates with the center suction hole may be formed in the second cylinder block. In this case, the first suction passage may include a front suction hole and a first suction space. Further, the second suction passage may include a front suction hole, a first suction space, a center suction hole, and a second suction space (claim 2). With this configuration, it is not necessary to separately form the first suction passage and the second suction passage in the housing, and the manufacturing cost can be reduced.

  In the above case, it is preferable that the rear side plate is formed with a low pressure chamber and a low pressure passage communicating with the second suction space. In this case, it is not necessary to separately form the low pressure chamber and the low pressure passage in the housing, and the manufacturing cost can be reduced.

  The housing communicates the first discharge passage that communicates the first compression chamber and the discharge chamber during the discharge stroke of the first compression mechanism, and the second compression chamber and the discharge chamber during the discharge stroke of the second compression mechanism. A second discharge passage may be formed. A rear discharge hole that communicates with the discharge chamber can be formed in the rear side plate. A second discharge space communicating with the rear discharge hole can be formed in the second cylinder block. A center discharge hole that communicates with the second discharge space may be formed in the center side plate. A first discharge space communicating with the center discharge hole may be formed in the first cylinder block. In this case, the second discharge passage can include a second discharge space and a rear discharge hole. In addition, the first discharge passage may include a first discharge space, a center discharge hole, a second discharge space, and a rear discharge hole. If comprised in this way, it is not necessary to form a 1st discharge path and a 2nd discharge path separately in a housing, and reduction in manufacturing cost is realizable.

  The back pressure supply path can include an upper flow path, a first lower flow path, and a second lower flow path. The upper flow path is formed in the rear side plate, the second cylinder block, and the center side plate, and communicates with the discharge chamber. The first lower flow path is formed in the center side plate and communicates the upper flow path and the first back pressure chamber. The second lower flow path is formed in the center side plate and communicates the upper flow path and the second back pressure chamber. In this case, the first supply path includes an upper flow path and a first lower flow path. The second supply path includes an upper flow path and a second lower flow path (Claim 5). If comprised in this way, it is not necessary to form a 1st supply path and a 2nd supply path in a housing separately, and reduction in manufacturing cost is realizable.

  The center side plate may have a center shaft hole through which the drive shaft is inserted. A center bearing may be provided between the center shaft hole and the drive shaft. The upper flow path may include an annular path that is recessed in the center shaft hole in the radially outward direction and circulates around the center shaft hole in an annular shape. The first lower flow path may communicate with the annular path and extend forward. The second lower flow path can communicate with the annular path and extend rearward. A first center communication groove that communicates with the plurality of first back pressure chambers may be formed in the front surface of the center side plate. In addition, it is preferable that a second center communication groove communicating with the plurality of second back pressure chambers is recessed on the rear surface of the center side plate.

  In this case, the first and second center communication grooves allow the first and second vanes to be connected to the first and second cylinders even after high-pressure lubricating oil is supplied to the first and second back pressure chambers through the back pressure supply passage. The first and second back pressure chambers are maintained at a predetermined pressure so as to be kept pressed against the inner surface of the chamber. Further, the first and second center communication grooves formed on the front surface and the rear surface of the center side plate mainly function to maintain the postures of the first and second vanes. Then, the upper flow path, the first and second lower flow paths, and the first and second center communication grooves can be formed only by processing the center side plate, and the manufacturing cost can be reliably reduced. It is preferable that there are two first and second lower flow paths. The first and second center communication grooves preferably have a fan shape around the axis of the drive shaft. It is also possible to provide first and second chattering prevention valves for preventing chattering of the first and second compression mechanisms in the first and second communication grooves.

  The front side plate may have a front shaft hole through which the drive shaft is inserted. A front bearing may be provided between the front shaft hole and the drive shaft. On the rear surface of the front side plate, a front communication groove that communicates with the plurality of first back pressure chambers and the same phase as the first lower flow path, and the high-pressure lubricant supplied to each first back pressure chamber It is preferable that the first damper groove for relieving the impact caused by is recessed.

  In this case, the lubricating oil that has flowed toward the front side plate via the first back pressure chamber is collected in a front communication groove formed on the rear surface of the front side plate, and spreads from the high pressure side to the low pressure side. Further, each front vane is pressurized from the front side and the rear side by the front communication groove formed on the rear surface of the front side plate and the first center communication groove formed on the front surface of the center side plate. The posture of the first vane can be maintained. Furthermore, the impact caused by the high-pressure lubricant supplied to each first back pressure chamber can be mitigated by the first damper groove. The number of first damper grooves is preferably two. The front communication groove preferably has an arc shape around the axis of the drive shaft.

  The rear side plate may have a rear shaft hole through which the drive shaft is inserted. A rear bearing may be provided between the rear shaft hole and the drive shaft. The front side of the rear side plate is positioned in the same phase as the rear communication groove communicating with the plurality of second back pressure chambers and the second lower flow path, and is caused by the high-pressure lubricant supplied to each second back pressure chamber. It is preferable that the third damper groove for reducing the impact is recessed.

  In this case, the lubricating oil that has flowed toward the rear side plate via the second back pressure chamber is collected in a rear communication groove formed on the front surface of the rear side plate, and spreads from the high pressure side to the low pressure side. In addition, the second center communication groove formed on the rear surface of the center side plate and the rear communication groove formed on the front surface of the rear side plate apply pressure to each second vane from the front side and the rear side, so that each of the second vanes has good balance. A two-vane posture can be maintained. Furthermore, the impact caused by the high-pressure lubricant supplied to each second back pressure chamber can be mitigated by the second damper groove. The number of second damper grooves is preferably two. The rear communication groove preferably has an arc shape around the axis of the drive shaft.

  A separator for separating the lubricating oil from the refrigerant gas discharged from the rear discharge hole and storing the lubricating oil in the discharge chamber may be provided in the discharge chamber. A sealing member that seals the low-pressure chamber from the discharge chamber is preferably provided between the rear side plate and the separator. In this case, lubricating oil can be reliably supplied to the first and second back pressure chambers and the respective bearings. Further, leakage of refrigerant gas and lubricating oil from the discharge chamber to the low pressure chamber can be prevented, and high mechanical efficiency can be reliably exhibited.

  Further, a separator that separates the lubricating oil from the refrigerant gas discharged from the rear discharge hole and stores the lubricating oil in the discharge chamber may be provided in the discharge chamber. The rear side plate preferably includes a separator (claim 10). In this case, lubricating oil can be reliably supplied to the first and second back pressure chambers and the respective bearings. Further, leakage of refrigerant gas and lubricating oil from the discharge chamber to the low pressure chamber can be reliably prevented, and high mechanical efficiency can be reliably exhibited. In addition, there is no need for a dedicated part for the separator, and the manufacturing cost can be further reduced by reducing the number of parts.

  As the separator, in addition to a centrifugal separator, a separator other than a centrifugal separator such as a collision type can be employed. For example, the separator may have a cylindrical guide surface and a cylindrical separation cylinder provided inside the guide surface and substantially coaxial with the guide surface. The separator circulates the refrigerant gas discharged from the rear discharge hole between the guide surface and the outer peripheral surface of the separation cylinder to separate the lubricating oil, and guides the refrigerant gas to the inside of the separation cylinder to the outside of the compressor. Discharge. Preferably, the guide surface is formed on the rear side plate. In this case, the separator is a centrifugal separator. Thereby, reduction of a number of parts and size reduction can be implement | achieved easily.

  A suction port communicating with the suction chamber may be formed in the front housing, and a discharge port communicating with the discharge chamber may be formed in the rear housing. The front housing and the rear housing can be shells. The first cylinder block and the second cylinder block can be common except for the upper flow path. The first rotor and the second rotor may be common. The first vane and the second vane can be common. In these cases, it is possible to further reduce the manufacturing cost by sharing parts.

  The tandem vane type compressor of the present invention can increase the discharge capacity per one rotation of the drive shaft, and is excellent in mountability and can exhibit excellent mechanical efficiency and reduction of power loss.

1 is a cross-sectional view of a tandem vane compressor of Example 1. FIG. FIG. 2 is a cross-sectional view taken along the line AA in FIG. 1 according to the tandem vane type compressor of the first embodiment. FIG. 5 is a cross-sectional view taken along the line BB in FIG. 1 according to the tandem vane type compressor of the first embodiment. FIG. 2 is a cross-sectional view taken along the line CC of FIG. 1 according to the tandem vane type compressor of the first embodiment. FIG. 2 is a cross-sectional view taken along the line DD in FIG. 1 according to the tandem vane type compressor of the first embodiment. FIG. 2 is a cross-sectional view taken along the line EE in FIG. 1 according to the tandem vane type compressor of the first embodiment. FIG. 5 is a cross-sectional view taken along the line FF in FIG. 1 according to the tandem vane type compressor of the first embodiment. 1. It is a GG arrow sectional drawing of FIG. 1 regarding the tandem-type vane type compressor of Example 1. FIG. 1 is a schematic cross-sectional view of a tandem vane compressor of Example 1. FIG. 3 is a cross-sectional view of a tandem vane type compressor according to Embodiment 2. FIG.

  Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings.

Example 1
As shown in FIG. 1, the tandem vane compressor of the first embodiment includes a front side plate 11, a first cylinder block 5, a center side plate 13, a second side in a front housing 1 and a rear housing 3 that are coupled to each other. The cylinder block 7 and the rear side plate 15 are fixed in a housed state. The front housing 1 and the rear housing 3 are shells 9. The shell 9 has the same body diameter as that of the single cylinder vane compressor. The first and second cylinder blocks 5 and 7 have the same outer shape. The shell 9, the first and second cylinder blocks 5, 7, the front side plate 11, the center side plate 13, and the rear side plate 15 correspond to the housing.

  As shown in FIG. 3, the first cylinder block 5 is formed with an elliptical first cylinder chamber 5 a in a direction perpendicular to the axis. As shown in FIG. 6, the second cylinder block 7 is formed with a second cylinder chamber 7a having the same shape as the first cylinder chamber 5a. The first and second cylinder blocks 5 and 7 are fixed so that the first and second cylinder chambers 5a and 7a have the same phase.

  As shown in FIG. 1, the first cylinder block 5 is sandwiched between a front side plate 11 and a center side plate 13 and stored in a shell 9. The front and rear of the first cylinder chamber 5a are closed by a front side plate 11 and a center side plate 13, respectively. The second cylinder block 7 is held between the center side plate 13 and the rear side plate 15 and accommodated in the shell 9. The front and rear of the second cylinder chamber 7a are closed by a center side plate 13 and a rear side plate 15, respectively.

  A front shaft hole 11a is formed through the front side plate 11, a center shaft hole 13a is formed through the center side plate 13, and a rear shaft hole 15a is formed through the rear side plate 15. A front slide bearing 17 is press-fitted into the front shaft hole 11a, a center slide bearing 19 is press-fitted into the center shaft hole 13a, and a rear slide bearing 21 is press-fitted into the rear shaft hole 15a. A shaft hole 1a is also provided through the front housing 1, and a shaft seal device 23 is press-fitted into the shaft hole 1a. A drive shaft 25 is rotatably held by the shaft seal device 23, the front slide bearing 17, the center slide bearing 19, and the rear slide bearing 21. An electromagnetic clutch or pulley (not shown) is fixed to the tip of the drive shaft 25 exposed from the front housing 1. A driving force is transmitted to the electromagnetic clutch or pulley by the engine or motor of the vehicle.

  The drive shaft 25 is press-fitted with first and second rotors 27 and 29 having a circular cross section. The first rotor 27 is disposed in the first cylinder chamber 5a, and the second rotor 29 is disposed in the second cylinder chamber 7a.

  As shown in FIGS. 1 and 3, five first vane grooves 27 a are formed in the radial direction on the outer peripheral surface of the first rotor 27, and each first vane groove 27 a has a first vane. 31 is accommodated so that it can appear and disappear. A first back pressure chamber 33 is formed between the bottom surface of each first vane 31 and each first vane groove 27a. The first back pressure chamber 33 extends from the rear surface of the front side plate 11 to the front surface of the center side plate 13. Five first compressions are performed by two adjacent first vanes 31, 31, an outer peripheral surface of the first rotor 27, an inner peripheral surface of the first cylinder block 5, a rear surface of the front side plate 11, and a front surface of the center side plate 13. A chamber 35 is formed.

  Further, as shown in FIGS. 1 and 6, five second vane grooves 29a are also formed in the radial direction on the outer peripheral surface of the second rotor 29, and each second vane groove 29a has a second one. Two vanes 37 are stored so that they can appear and disappear. A second back pressure chamber 39 is formed between the bottom surface of each second vane 37 and each second vane groove 29a. The second back pressure chamber 39 extends from the rear surface of the center side plate 13 to the front surface of the rear side plate 15. Two adjacent second vanes 37, 37, the outer peripheral surface of the second rotor 29, the inner peripheral surface of the second cylinder block 7, the rear surface of the center side plate 13 and the front surface of the rear side plate 15 provide five second compression chambers. 41 is formed.

  The first rotor 27 and the second rotor 29 are the same component. The first vane 31 and the second vane 37 are the same parts. These are those employed in single cylinder vane compressors.

  As shown in FIG. 1, a suction chamber 43 is formed between the front housing 1 and the front side plate 11. In the front housing 1, a suction port 1 b for connecting the suction chamber 43 to the outside is opened upward. As shown in FIG. 2, the front side plate 11 is provided with two front suction holes 11 b communicating with the suction chamber 43. As shown in FIG. 3, each front suction hole 11 b communicates with each first suction space 5 b of the first cylinder block 5. Each first suction space 5b communicates with the first compression chamber 35 in the suction stroke by a suction port 5c. Each front suction hole 11b and each first suction space 5b are first suction passages.

  As shown in FIGS. 1 and 3, two first discharge spaces 5 d are formed between the first cylinder block 5 and the rear housing 3. Each first discharge space 5d communicates with the first compression chamber 35 in the discharge stroke by a discharge port 5e. A discharge valve 45 that closes the discharge port 5e and a retainer 47 that regulates the lift amount of the discharge valve 45 are provided in each first discharge space 5d. The drive shaft 25, the first cylinder block 5, the first rotor 27, the first vanes 31, the discharge valve 45, the retainer 47, and the like constitute the first compression mechanism 1C.

  As shown in FIGS. 1, 4, and 5, the center side plate 13 is provided with two center suction holes 13 b communicating with the first suction spaces 5 b of the first cylinder block 5. Each center suction hole 13b communicates with each second suction space 7b of the second cylinder block 7 as shown in FIG. Each second suction space 7b communicates with the second compression chamber 41 in the suction stroke by a suction port 7c. Each front suction hole 11b, each first suction space 5b, each center suction hole 13b, and second suction space 7b are second suction passages.

  As shown in FIGS. 1, 4 and 5, the center side plate 13 is formed with two center discharge holes 13e communicating with the first discharge spaces 5d. Further, as shown in FIG. 6, a second discharge space 7d communicating with each center discharge hole 13e is formed between the second cylinder block 7 and the rear housing 3. Each second discharge space 7d communicates with the compression chamber 41 in the discharge stroke by a discharge port 7e. A discharge valve 49 that closes the discharge port 7e and a retainer 51 that regulates the lift amount of the discharge valve 49 are provided in each second discharge space 7d. The drive shaft 25, the second cylinder block 7, the second rotor 29, each second vane 37, the discharge valve 49, the retainer 51, and the like constitute the second compression mechanism 2C.

  As shown in FIGS. 1 and 7, the rear side plate 15 is provided with two low-pressure passages 15 b communicating with the second suction spaces 7 b of the second cylinder block 7. Further, the rear side plate 15 is provided with two rear discharge holes 15c communicating with the second discharge spaces 7d. Each second discharge space 7d and each rear discharge hole 15c are second discharge passages. Each first discharge space 5d, each center discharge hole 13e, each second discharge space 7d, and each rear discharge hole 15c are first discharge passages.

  As shown in FIGS. 1 and 8, a discharge chamber 53 is formed between the rear side plate 15 and the rear housing 3. As shown in FIG. 1, a centrifugal separator 55 is fixed in the discharge chamber 53 by being sandwiched between the rear side plate 15 and the rear housing 3. The separator 55 includes an end frame 57 and a cylindrical member 59 that is fixed in the end frame 57 and extends vertically.

  The end frame 57 is formed with an oil separation chamber 57a that extends vertically in a cylindrical shape. A cylindrical member 59 is press-fitted into the upper end of the oil separation chamber 57a. For this reason, a part of the oil separation chamber 57 a serves as a guide surface 57 b for circulating the refrigerant gas around the outer peripheral surface of the cylindrical member 59. Both rear discharge holes 15c communicate with the cylindrical member 59 and the guide surface 57b. A communication port 57 c is formed at the lower end of the end frame 57 to allow the bottom surface of the oil separation chamber 57 a to communicate with the discharge chamber 53. The rear housing 3 is formed with a discharge port 3a for connecting the upper end of the discharge chamber 53 to the outside. The discharge port 3 a is located above the cylindrical member 59.

  A low pressure chamber 61 is formed between the rear side plate 15 and the end frame 57. The rear end portion of the drive shaft 25 is accommodated in the low pressure chamber 61. Each low pressure passage 15 b communicates with the low pressure chamber 61. An O-ring 62 that seals the low-pressure chamber 61 against the discharge chamber 53 is provided between the rear side plate 15 and the end frame 57. The O-ring 62 is a sealing member.

  As shown in FIGS. 1 and 2, a pair of front communication grooves 11 c having a circular arc shape are formed in the rear surface of the front side plate 11. Both front communication grooves 11 c are point-symmetric with respect to the axis of the drive shaft 25. Each front communication groove 11 c communicates with the first back pressure chamber 33 in the suction stroke or the like by the rotation of the first rotor 27. In addition, a pair of first damper grooves 11 d that form a circle are recessed in the rear surface of the front side plate 11. Both first damper grooves 11 d are also point-symmetric with respect to the axis of the drive shaft 25. Each first damper groove 11d is located on the rear side in the rotational direction of the first rotor 27 with respect to the front communication groove 11c.

  As shown in FIGS. 1 and 5 to 8, the rear side plate 15, the second cylinder block 7, and the center side plate 13 have an axial flow path 69 a that extends in the front-rear direction and communicates with the discharge chamber 53. As shown in FIGS. 1, 4 and 5, the center side plate 13 is formed with a radial flow path 69b extending in the axial direction of the drive shaft 25 from the front end of the axial flow path 69a. Further, the center side plate 13 is provided with an annular passage 69c that goes around the center shaft hole 13a. The upper end of the radial flow path 69b communicates with the annular path 69c. The axial flow path 69a, the radial flow path 69b, and the annular path 69c are the upper flow paths.

  As shown in FIGS. 1 and 4, the center side plate 13 has two first lower flow paths 69d communicating with the annular path 69c extending forward in the axial direction. Both first lower flow paths 69d are positioned in the same phase as the first damper groove 11d. As shown in FIGS. 1 and 5, the center side plate 13 has two second lower flow paths 69e communicating with the annular path 69c extending rearward in the axial direction. Both the second lower flow paths 69e are located in the same phase as the first damper groove 11d and the first lower flow path 69d.

  That is, each first lower flow path 69d communicates with the first back pressure chamber 33 in the compression stroke and the discharge stroke by the rotation of the first rotor 27. Further, each second lower flow path 69e communicates with the second back pressure chamber 39 in the compression stroke and the discharge stroke by the rotation of the second rotor 29. The axial flow path 69a, the radial flow path 69b, the annular path 69c, and the first and second lower flow paths 69d and 69e are back pressure supply paths. An axial flow path 69a, a radial flow path 69b, an annular path 69c, and a first lower flow path 69d are first supply paths, and an axial flow path 69a, a radial flow path 69b, an annular path 69c, and a second lower flow path 69d. Is the second supply path.

  As shown in FIGS. 1 and 4, a pair of first center communication grooves 13 c having a fan shape are formed in the front surface of the center side plate 13. Each first center communication groove 13c is located in the same phase as the front communication groove 11c. As shown in FIGS. 1 and 5, a pair of second center communication grooves 13 d having a fan shape are also provided in the rear surface of the center side plate 13. Each second center communication groove 13d is positioned in the same phase as the front communication groove 11c and the first center communication groove 13c.

  As shown in FIGS. 1 and 7, a pair of rear communication grooves 15 d having an arc shape are also recessed on the front surface of the rear side plate 15 in the same manner as the rear surface of the front side plate 11. Both rear communication grooves 15d are positioned in the same phase as the front communication groove 11c, the first center communication groove 13c, and the second center communication groove 13d. A pair of second damper grooves 15e having a circular shape are recessed in the front surface of the rear side plate 15 in the same manner as the rear surface of the front side plate 11. Both the second damper grooves 15e are positioned in the same phase as the first damper groove 11d and the first and second lower flow paths 69d and 69e.

  The first rotor 27 and the second rotor 29 are connected to the drive shaft 25 by the first and second vane grooves 27a and 29a, the first center communication groove 13c, the second center communication groove 13d, the front communication groove 11c, and the rear communication groove 15d. The first and second lower flow paths 69d and 69e and the first and second damper grooves 11d and 15e are fixed so as to have the same phase.

  As shown in FIG. 1, the drive shaft 25, the front slide bearing 17, the center slide bearing 19 and the rear slide bearing 21, the front side plate 11, the first cylinder block 5, each first vane 31, the discharge valve 45, the retainer 47, The center side plate 13, the second cylinder block 7, each second vane 37, the discharge valve 49, the retainer 51, the rear side plate 15, and the separator 55 are assembled as a sub assembly SA. An O-ring is attached to the sub-assembly SA, and this is inserted into the rear housing 3. Next, an O-ring is mounted on the rear housing 3 and the front housing 1 is put on the O-ring. Then, a plurality of bolts 71 shown in FIGS. Thus, the tandem vane type compressor of Example 1 is assembled.

  In this tandem vane compressor, although not shown, the discharge port 3a is connected to the condenser by piping, the condenser is connected to the expansion valve by piping, the expansion valve is connected to the evaporator by piping, and the evaporator Is connected to the inlet 1b by a pipe. A tandem vane compressor, a condenser, an expansion valve, an evaporator, and piping constitute a refrigeration circuit. This refrigeration circuit constitutes a vehicle air conditioner.

  In the tandem vane compressor, when the drive shaft 25 is driven by an engine or the like, the first and second compression mechanisms 1C and 2C repeat the suction stroke, the compression stroke, and the discharge stroke, respectively.

  That is, the first and second rotors 27 and 29 rotate in synchronization with the drive shaft 25, and the first and second compression chambers 35 and 41 undergo volume changes. For this reason, the refrigerant gas having passed through the evaporator is sucked into the suction chamber 43 from the suction port 1b. The refrigerant gas in the suction chamber 43 is sucked into the first compression chamber 35 through the front suction hole 11b, the first suction space 5b, and the suction port 5c. The refrigerant gas in the first suction space 5b is sucked into the second compression chamber 41 through the center suction hole 13b, the second suction space 7b, and the suction port 7c.

  The refrigerant gas compressed in the first compression chamber 35 is discharged to the first discharge space 5d through the discharge port 5e. The high-pressure refrigerant gas in the first discharge space 5d reaches the second discharge space 7d through the center discharge hole 13e. The refrigerant gas compressed in the second compression chamber 41 passes through the discharge port 7e and is discharged into the second discharge space 7d. The high-pressure refrigerant gas in the second discharge space 7d is discharged toward the guide surface 57b of the separator 50 through the rear discharge hole 15c. For this reason, the refrigerant gas circulates around the guide surface 57b, and the lubricating oil is centrifuged. The refrigerant gas from which the lubricating oil has been separated is discharged from the discharge port 3a toward the condenser. Thus, in this tandem vane type compressor, the discharge capacity per rotation of the drive shaft 25 is doubled compared to the single cylinder type vane compressor.

  Further, in this tandem type vane compressor, the first and second vanes 31 and 37 each have a short shaft length employed in the single cylinder type vane compressor, so that it is difficult to tilt forward and backward. For this reason, leakage of the refrigerant gas from the first and second compression chambers 35 and 41 is small, and the slidability of the first and second vanes 31 and 37 is excellent.

  The separated lubricating oil is stored in the discharge chamber 53 from the oil separation chamber 57a through the communication port 57c. The lubricating oil in the discharge chamber 53 reaches the annular path 69c through the axial flow path 69a and the radial flow path 69b because the discharge chamber 53 has a high pressure. Lubricating oil in the annular passage 69c is supplied from the first lower passage 69d to the first back pressure chambers 33 in the compression stroke and the discharge stroke. Further, the lubricating oil in the annular passage 69c is supplied to the second back pressure chambers 39 in the compression stroke and the discharge stroke. For this reason, in the tandem vane type compressor, while the first and second compression mechanisms 1C and 2C perform the compression stroke and the discharge stroke, the first and second vanes 31 and 37 are respectively connected to the first and second cylinders 5a and 7a. The refrigerant gas is suitably pressed against the inner surface of the chamber, and the leakage of refrigerant gas from the first and second compression chambers 35 and 41 is small. Therefore, these tandem vane compressors can reliably exhibit high mechanical efficiency.

  In the tandem vane compressor, as shown in FIG. 1, the housing is a front side plate 11, a front housing 1, a center side plate 13, a first cylinder block 5, a rear side plate 15, a second cylinder block 7, and A rear housing 3 is provided. The front housing 1 and the front side plate 11 form a suction chamber 43, and the rear housing 3 and the rear side plate 15 form a discharge chamber 53. On the other hand, a low pressure chamber 61 is formed by the rear side plate 15 and the end frame 57, and a low pressure passage 15 b is formed in the rear side plate 15. For this reason, as shown in FIG. 9, the space between the front side plate 11 and the drive shaft 25 communicates with the suction chamber 43 through the clearance to become a low pressure LP, and the clearance between the rear side plate 15 and the drive shaft 25 is also cleared. The low-pressure chamber 61 is communicated with the low-pressure LP via the. In the tandem vane compressor, first and second lower flow paths 69d and 69e communicating with the discharge chamber 53 by the axial flow path 59a, the radial flow path 69b, and the annular path 69c are formed in the center side plate 13. Therefore, the first and second back pressures are provided between the center side plate 13 and the drive shaft 25 via the clearance between the center side plate 13 and the first and second rotors 27 and 29 and the center communication grooves 13c and 13d. The high pressure HP communicates with the chambers 33 and 39 and is close to the discharge pressure.

  For this reason, the lubricating oil supplied to the first lower flow path 69d reaches the inside of the first back pressure chamber 33, and then the high pressure HP is formed between the center side plate 13 and the drive shaft 25. Since the space between the drive shaft 25 and the drive shaft 25 is a low pressure LP, it flows in one direction toward the front in the first back pressure chamber 33. Next, part of the lubricating oil in the first back pressure chamber 33 reaches the suction chamber 43 through the space between the front side plate 11 and the drive shaft 25. For this reason, the back pressure in the first back pressure chamber 33 can be released. Further, the front sliding bearing 17 provided between the front side plate 11 and the drive shaft 25 is lubricated.

  In addition, after the lubricating oil supplied to the second lower flow path 69e reaches the second back pressure chamber 39, the high pressure HP exists between the center side plate 13 and the drive shaft 25, and the rear side plate 15 and the drive shaft 25 Since it is a low pressure LP, it flows in the second back pressure chamber 39 in one direction toward the rear. Next, part of the lubricating oil in the second back pressure chamber 39 reaches the low pressure chamber 61 through the space between the rear side plate 15 and the drive shaft 25. For this reason, the back pressure in the second back pressure chamber 39 can be released. For this reason, the back pressure in the second back pressure chamber 39 is not excessively high, and power loss is unlikely to occur. Further, the rear sliding bearing 21 provided between the rear side plate 15 and the drive shaft 25 is configured such that a part of the lubricating oil in the second back pressure chamber 39 is connected to the rear communication groove 15d, the rear side plate 15 and the second rotor 29. By flowing around the drive shaft 25 through the clearance, lubrication is achieved. The center sliding bearing 19 provided between the center side plate 13 and the drive shaft 25 has a part of the lubricating oil in the first and second back pressure chambers 33 and 39 and the center communication grooves 13c and 13d and the center side. Lubrication is achieved by flowing around the drive shaft 25 through the clearance between the plate 13 and the first and second rotors 27 and 29.

  In particular, in this tandem vane compressor, since the O-ring 62 is provided between the rear side plate 15 and the end frame 57, leakage of refrigerant gas and lubricating oil from the discharge chamber 53 to the low pressure chamber 61 is prevented. be able to.

  In the tandem vane compressor, the first and second compression mechanisms C1 and C2 perform the suction stroke, the compression stroke, and the discharge stroke, respectively. Therefore, the discharge capacity per rotation of the drive shaft 25 may be increased. it can. Further, in this tandem vane type compressor, the first and second vanes 31 and 37 are not easily tilted forward and backward, the refrigerant gas leaks from the first and second compression chambers 35 and 41, and the first, The slidability of the two vanes 31 and 37 is excellent. For this reason, this tandem vane type compressor can exhibit excellent mechanical efficiency. Furthermore, since this tandem vane compressor can have the same barrel diameter as that of the single cylinder vane compressor, it can also exhibit excellent mountability.

  Therefore, in this tandem type vane compressor, the discharge capacity per rotation of the drive shaft 25 can be increased, and it is possible to exhibit excellent mechanical efficiency and reduction of power loss while being excellent in mountability.

  In the tandem vane compressor, the first suction passage is composed of each front suction hole 11b and each first suction space 5b, and the second suction passage is each front suction hole 11b, each first suction space 5b, It consists of a center suction hole 13b and each second suction space 7b. For this reason, it is not necessary to separately form the first suction passage and the second suction passage in the housing, and the manufacturing cost can be reduced.

  In particular, the rear side plate 15 is formed with a low pressure chamber 61 and a low pressure passage 15b communicating with the second suction space 7b. For this reason, it is not necessary to separately form the low-pressure chamber 61 and the low-pressure passage 15b in the housing, and the manufacturing cost can be reduced.

  Further, in this tandem vane compressor, the first discharge passage is composed of each second discharge space 7d and each rear discharge hole 15c, and the second discharge passage is each first discharge space 5d, each center discharge hole 13e, each each It consists of a second discharge space 7d and each rear discharge hole 15c. For this reason, it is not necessary to separately form the first discharge passage and the second discharge passage in the housing, and the manufacturing cost can be reduced.

  Further, in this tandem vane type compressor, the first supply path includes an axial flow path 69a, a radial flow path 69b, an annular path 69c, and a first lower flow path 69d. The second supply path includes an axial flow path 69a, a radial flow path 69b, an annular path 69c, and a second lower flow path 69e. For this reason, it is not necessary to separately form the first supply path and the second supply path in the housing, and the manufacturing cost can be reduced.

  In the tandem vane type compressor, the first and second center communication grooves 13c and 13d are provided in the first and second back pressure chambers 33 and 39 through the first and second lower flow paths 69d and 69e. Even after being supplied, the first and second back pressure chambers 33, 37 are maintained so that the first and second vanes 31, 37 are pressed against the inner surfaces of the first and second cylinder chambers 5a, 7a. The inside of 39 is kept at a predetermined pressure. The first and second center communication grooves 13 c and 13 d formed on the front and rear surfaces of the center side plate mainly function to maintain the postures of the first and second vanes 31 and 37.

  The lubricating oil that has flowed toward the front side plate 11 through the first back pressure chamber 33 is collected in the front communication groove 11c and spreads from the high pressure side to the low pressure side. In addition, the front communication groove 11c and the first center communication groove 13c apply pressure to the first vanes 31 from the front side and the rear side, so that the postures of the first vanes 31 can be maintained with good balance. Further, the impact caused by the high-pressure lubricant supplied to each first back pressure chamber 33 can be mitigated by the first damper groove 11d.

  The lubricating oil that has flowed toward the rear side plate 15 via the second back pressure chamber 39 is collected in the rear communication groove 15d and spreads from the high pressure side to the low pressure side. Further, the second center communication groove 13d and the rear communication groove 15d apply pressure to the second vanes 37 from the front side and the rear side, so that the postures of the second vanes 37 can be maintained with good balance. Further, the impact caused by the high-pressure lubricant supplied to each second back pressure chamber 39 can be mitigated by the second damper groove 15e.

(Example 2)
In the tandem vane compressor of the second embodiment, the rear side plate 16 includes a separator 55 as shown in FIG. Specifically, in this tandem vane compressor, the rear side plate 16 serves as the rear side plate 15 and the end frame 57 of the first embodiment. For this reason, the low pressure chamber 61 is also formed by the rear side plate 16 and does not have the O-ring 62 as in the first embodiment. Other configurations are the same as those of the first embodiment.

  In this tandem type vane compressor, leakage of refrigerant gas and lubricating oil from the discharge chamber 53 to the low pressure chamber 61 can be reliably prevented, and high mechanical efficiency can be reliably exhibited. In addition, an end frame dedicated to the separator is not required, and the manufacturing cost can be further reduced by reducing the number of parts. Other functions and effects are the same as those of the first embodiment.

  In the above, the present invention has been described with reference to the first and second embodiments. However, the present invention is not limited to the first and second embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  The present invention is applicable to a vehicle air conditioner.

43 ... Suction chamber 53 ... Discharge chamber 5a ... First cylinder chamber 7a ... Second cylinder chamber 1, 3, 9, 11, 13, 15, 16 ... Housing 25 ... Drive shaft 27a ... First vane groove 27 ... First rotor 35 ... 1st compression chamber 31 ... 1st vane 1C ... 1st compression mechanism 29a ... 2nd vane groove | channel 29 ... 2nd rotor 41 ... 2nd compression chamber 37 ... 2nd vane 2C ... 2nd compression mechanism 33 ... 1st back Pressure chamber 39 ... Second back pressure chamber 69a, 69b, 69c, 69d, 69e ... Back pressure supply path 11 ... Front side plate 1 ... Front housing 13 ... Center side plate 5 ... First cylinder block 15, 16 Rear side plate 7 ... 2nd cylinder block 3 ... Rear side plate 11b ... Front suction hole 5b ... First suction space 13b ... Center suction hole 7b ... Second suction space 61 ... Low pressure chamber 1 5b ... Low pressure passage 15c ... Rear discharge hole 5d ... First discharge space 13e ... Center discharge hole 7d ... Second discharge space 69a, 69b, 69c ... Upper flow path (69a ... Axial flow path, 69b ... Radial flow path, 69c ... circular road)
69d: First lower flow path 69e: Second lower flow path 13a: Center shaft hole 19: Center sliding bearing (center bearing)
13c ... 1st center communicating groove 13d ... 2nd center communicating groove 11a ... Front shaft hole 17 ... Front sliding bearing (front bearing)
11c ... Front communication groove 11d ... First damper groove 15a ... Rear shaft hole 21 ... Rear sliding bearing (rear bearing)
15d ... Rear communication groove 15e ... Second damper groove 55 ... Separator 62 ... O-ring (sealing member)
57b ... Guide surface 59 ... Separating cylinder

Claims (11)

A housing in which a suction chamber, a discharge chamber, a first cylinder chamber and a second cylinder chamber are formed;
A drive shaft rotatably supported by the housing;
A first rotor provided in the first cylinder chamber so as to be rotatable by the drive shaft and formed with a plurality of first vane grooves, and provided in the first vane grooves so as to be able to project and retract, the first cylinder chamber. A first compression mechanism having a first vane that forms a first compression chamber located forward together with an inner surface of the first rotor and an outer surface of the first rotor;
A second rotor provided in the second cylinder chamber so as to be rotatable by the drive shaft and having a plurality of second vane grooves; And a second compression mechanism having a second vane that forms a second compression chamber positioned rearward together with the inner surface of the second rotor and the outer surface of the second rotor,
A space between the bottom surface of each first vane and each first vane groove is a first back pressure chamber,
A space between the bottom surface of each second vane and each second vane groove is a second back pressure chamber,
The housing is provided with a back pressure supply passage that communicates the discharge chamber with the first back pressure chamber and the second back pressure chamber,
The housing extends in a radial direction with respect to the drive shaft, a front side plate that pivotally supports the drive shaft, a front housing that forms the suction chamber together with the front side plate, and a radial direction with respect to the drive shaft Extending in the radial direction with respect to the drive shaft, a center side plate that pivotally supports the drive shaft, a first cylinder block that forms the first cylinder chamber together with the front side plate and the center side plate, A rear side plate that pivotally supports the drive shaft; a second cylinder block that forms the second cylinder chamber together with the center side plate and the rear side plate; and a rear housing that forms the discharge chamber together with the rear side plate. ,
The back pressure supply path is formed in the center side plate, and is formed in the center side plate, the first supply path communicating the discharge chamber and the first back pressure chamber, and the discharge chamber and the A second supply path communicating with the second back pressure chamber;
A tandem vane compressor characterized in that a low pressure chamber for housing a rear end portion of the drive shaft and a low pressure passage for communicating the suction chamber and the low pressure chamber are formed in the housing. The housing includes a first suction passage communicating the suction chamber and the first compression chamber during the suction stroke of the first compression mechanism, and the suction chamber and the second compression during the suction stroke of the second compression mechanism. A second suction passage communicating with the chamber is formed,
The front side plate is formed with a front suction hole communicating with the suction chamber,
The first cylinder block is formed with a first suction space communicating with the front suction hole,
A center suction hole communicating with the first suction space is formed in the center side plate,
The second cylinder block is formed with a second suction space communicating with the center suction hole,
The first suction passage is composed of the front suction hole and the first suction space,
2. The tandem vane compressor according to claim 1, wherein the second suction passage includes the front suction hole, the first suction space, the center suction hole, and the second suction space.   The tandem vane type compressor according to claim 2, wherein the rear side plate is formed with the low pressure chamber and the low pressure passage communicating with the second suction space. The housing includes a first discharge passage communicating the first compression chamber and the discharge chamber during a discharge stroke of the first compression mechanism, and the second compression chamber and the discharge during a discharge stroke of the second compression mechanism. A second discharge passage communicating with the chamber is formed,
A rear discharge hole communicating with the discharge chamber is formed in the rear side plate,
A second discharge space communicating with the rear discharge hole is formed in the second cylinder block,
A center discharge hole communicating with the second discharge space is formed in the center side plate,
A first discharge space communicating with the center discharge hole is formed in the first cylinder block,
The second discharge passage is composed of the second discharge space and the rear discharge hole,
4. The tandem vane compressor according to claim 1, wherein the first discharge passage includes the first discharge space, the center discharge hole, the second discharge space, and the rear discharge hole. 5. The back pressure supply path is formed in the rear side plate, the second cylinder block and the center side plate, and an upper flow path communicating with the discharge chamber;
A first lower flow path formed in the center side plate and communicating the upper flow path and the first back pressure chamber;
The center side plate is formed of a second lower flow path that communicates the upper flow path and the second back pressure chamber,
The first supply path includes the upper flow path and the first lower flow path,
The tandem vane compressor according to any one of claims 1 to 4, wherein the second supply path includes the upper flow path and the second lower flow path. The center side plate has a center shaft hole through which the drive shaft is inserted,
A center bearing is provided between the center shaft hole and the drive shaft,
The upper flow path includes an annular passage that is recessed in the center shaft hole in a radially outward direction and circulates around the center shaft hole in an annular shape,
The first lower flow path communicates with the annular path and extends forward;
The second lower flow path communicates with the annular path and extends rearward.
A first center communication groove communicating with the plurality of first back pressure chambers is recessed in the front surface of the center side plate,
The tandem vane type compressor according to claim 5, wherein a second center communication groove communicating with the plurality of second back pressure chambers is recessed on a rear surface of the center side plate. The front side plate has a front shaft hole through which the drive shaft is inserted,
A front bearing is provided between the front shaft hole and the drive shaft,
On the rear surface of the front side plate, a front communication groove communicating with the plurality of first back pressure chambers and the same phase as the first lower flow path, the high pressure supplied to each first back pressure chamber is provided. The tandem vane type compressor according to claim 6, wherein a first damper groove that relieves an impact caused by the lubricating oil is recessed. The rear side plate has a rear shaft hole through which the drive shaft is inserted,
A rear bearing is provided between the rear shaft hole and the drive shaft,
On the front surface of the rear side plate, a plurality of rear communication grooves communicating with the second back pressure chambers and the same phase as the second supply path are provided, and high-pressure lubrication supplied to the second back pressure chambers is provided. The tandem vane type compressor according to claim 6, wherein a second damper groove for reducing an impact caused by oil is recessed. In the discharge chamber, a separator that separates the lubricating oil from the refrigerant gas discharged from the rear discharge hole and stores the lubricating oil in the discharge chamber is provided.
The tandem vane compressor according to claim 3 or 4, wherein a sealing member for sealing the low-pressure chamber with respect to the discharge chamber is provided between the rear side plate and the separator. In the discharge chamber, a separator that separates the lubricating oil from the refrigerant gas discharged from the rear discharge hole and stores the lubricating oil in the discharge chamber is provided.
The tandem vane compressor according to claim 3 or 4, wherein the rear side plate includes the separator. The separator has a cylindrical guide surface and a cylindrical separation cylinder that is provided on the inner side of the guide surface and is substantially coaxial with the guide surface. The separator discharges the refrigerant gas discharged from the rear discharge hole. Circulate between the guide surface and the outer peripheral surface of the separation cylinder to separate the lubricating oil, guide the refrigerant gas into the separation cylinder and discharge it to the outside of the compressor;
The tandem vane compressor according to claim 10, wherein the guide surface is formed on the rear side plate.

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