JP5708573B2 - Tandem vane compressor - Google Patents

Description

  The present invention relates to a tandem vane compressor.

  Patent Document 1 discloses a conventional tandem vane compressor. In this tandem vane compressor, a suction chamber, a discharge chamber, and a compression chamber are formed in a housing, and a drive shaft is rotatably supported. Further, in the housing, the rotation of the drive shaft causes the compression chamber to suck the refrigerant gas from the suction chamber, the compression stroke to compress the refrigerant gas in the compression chamber, and the refrigerant gas in the compression chamber to be discharged to the discharge chamber. A plurality of compression mechanisms for performing the discharge stroke are tandemly coupled.

  Each compression mechanism includes a first compression mechanism and a second compression mechanism. The first compression mechanism has a first cylinder chamber formed in the housing, and a first rotor that is rotatably provided in the first cylinder chamber by a drive shaft. A plurality of first vane grooves are formed in the first rotor. In addition, the first compression mechanism is provided so as to be able to appear and retract in each first vane groove, and forms a first compression chamber that is a compression chamber positioned forward together with the inner surface of the first cylinder chamber and the outer surface of the first rotor. Has vanes.

  Similarly to the first compression mechanism, the second compression mechanism also includes a second cylinder chamber formed in the housing and a second rotor that is rotatably provided in the second cylinder chamber by a drive shaft. A plurality of second vane grooves are also formed in the second rotor. The second compression mechanism is also provided so as to be able to protrude and retract in each second vane groove, and forms a second compression chamber which is a compression chamber located rearward together with the inner surface of the second cylinder chamber and the outer surface of the second rotor. Has vanes.

  The housing includes a shell, a first side plate, a second side plate, a third side plate, a first cylinder block, and a second cylinder block.

  The shell forms an outer shell and is formed with a suction port and a discharge port connected to the outside. The first side plate is housed in the shell and forms a suction chamber that communicates with the suction port together with the shell. The second side plate is housed in the shell and partitions the first compression mechanism and the second compression mechanism. The third side plate is housed in the shell and forms a discharge chamber that communicates with the discharge port together with the shell. The first cylinder block is sandwiched between the first side plate and the second side plate and accommodated in the shell to form a first cylinder chamber. The second cylinder block is sandwiched between the second side plate and the third side plate and accommodated in the shell to form a second cylinder chamber.

  As shown in FIG. 1 and FIG. 2 of Patent Document 1, a first discharge region communicated with the first compression chamber in the discharge stroke of the first compression mechanism between the shell and the first cylinder block. Is provided. Further, as shown in FIGS. 1 and 3 of Patent Document 1, the second compression chamber communicates with the second compression chamber in the discharge stroke of the second compression mechanism between the shell and the second cylinder block. A discharge region is provided.

  When this tandem vane compressor is used in an air conditioner such as a vehicle, the drive shaft is rotationally driven through an electromagnetic clutch, for example. 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 and compressed in the first and second compression chambers. Then, the compressed refrigerant gas is discharged into the discharge chamber through the first and second discharge regions. The high-pressure refrigerant gas discharged into the discharge chamber is supplied to the refrigeration circuit of the air conditioner.

  Thus, in the tandem vane type compressor, 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.

Japanese Utility Model Publication No. 3-118294

  By the way, in the conventional tandem type vane compressor, when the discharge path of the refrigerant gas from the first compression mechanism and the second compression mechanism is made common, the first discharge area and the second discharge area are connected by the discharge communication path. It is possible to communicate. In addition, in order to reduce the pulsation of refrigerant gas discharged intermittently from the first compression chamber and the second compression chamber to the discharge chamber, the first outer peripheral discharge chamber communicated with the first compression chamber via the first discharge region. It is conceivable to provide a second outer peripheral discharge chamber that communicates with the second compression chamber via the second discharge region. In this case, the refrigerant gas discharged from the first compression chamber flows through the first discharge region and the first outer peripheral discharge chamber, and after passing through the discharge communication path, the refrigerant gas from the second compression chamber in the second discharge region Merge and discharge to the discharge chamber via the second outer peripheral discharge chamber. When the refrigerant gas from the first compression chamber and the second compression chamber is discharged via such a discharge path, the lubricating oil is separated from the refrigerant gas until reaching the discharge chamber, and the lubricating oil is separated from the first outer periphery. It tends to collect below the discharge chamber and the second outer peripheral discharge chamber.

  Then, the volume of the first outer peripheral discharge chamber and the volume of the second outer peripheral discharge chamber are reduced by the amount of the accumulated lubricating oil. If it does so, the pulsation reduction effect of the discharge refrigerant gas by the 1st perimeter discharge chamber and the 2nd perimeter discharge chamber will fall, and it will become easy to be transmitted to a discharge chamber. As a result, this tandem vane compressor tends to generate abnormal noise and vibration, and has a problem with quietness.

  In this case, the accumulated lubricating oil does not contribute to the lubrication of the compressor. As a result, in this tandem vane type compressor, there is a concern that the lubrication performance will deteriorate.

  In order to solve these problems, by increasing the communication area of the discharge communication path that connects the first discharge region and the second discharge region, the first outer peripheral discharge chamber that communicates with the first discharge region, and the second discharge region It is conceivable to move the lubricating oil accumulated in the second outer peripheral discharge chamber communicating with the region to the discharge chamber. However, in this case, the pulsation of the discharged refrigerant gas is easily transmitted to the discharge chamber due to the discharge communication path having a large communication area. As a result, even in this case, the problem of quietness still remains.

  This invention is made | formed in view of the said conventional situation, Comprising: It is set as the problem which should be solved to provide the tandem-type vane type compressor which can exhibit the outstanding quietness and lubrication performance.

The tandem vane type compressor of the present invention has a suction chamber, a discharge chamber, and a compression chamber formed in a housing, and a drive shaft is rotatably supported in the housing. The compression chamber performs a suction stroke for sucking refrigerant gas from the suction chamber, a compression stroke for compressing the refrigerant gas in the compression chamber, and a discharge stroke for discharging the refrigerant gas in the compression chamber to the discharge chamber. Multiple compression mechanisms are combined in tandem,
Each of the compression mechanisms includes a first cylinder chamber formed in the housing, a first rotor provided in the first cylinder chamber so as to be rotatable by the drive shaft, and having a plurality of first vane grooves, A first vane which is provided in each first vane groove so as to be able to appear and retract, and forms a first compression chamber which is the compression chamber positioned forward together with an inner surface of the first cylinder chamber and an outer surface of the first rotor; A first compression mechanism;
A second cylinder chamber formed in the housing; a second rotor rotatably provided in the second cylinder chamber by the drive shaft; and a plurality of second vane grooves formed therein; and each second vane groove And a second compression mechanism having a second vane that forms a second compression chamber, which is a compression chamber located rearward together with the inner surface of the second cylinder chamber and the outer surface of the second rotor. In the provided tandem vane compressor,
The housing forms a shell, a shell in which a suction port and a discharge port connected to the outside are formed, and a first side plate that is housed in the shell and forms the suction chamber that communicates with the suction port together with the shell. And a second side plate that is housed in the shell and partitions the first compression mechanism and the second compression mechanism, and the discharge chamber that is housed in the shell and communicates with the discharge port together with the shell. A third side plate to be formed, a first cylinder block sandwiched between the first side plate and the second side plate and housed in the shell and forming the first cylinder chamber, and the second side plate And a second cylinder block sandwiched between the third side plate and housed in the shell and forming the second cylinder chamber,
Between the shell and the first cylinder block, a first discharge region communicating with the first compression chamber in the discharge stroke of the first compression mechanism, communicating with the first discharge region, and the first A first outer discharge chamber that circulates around the cylinder block,
Between the shell and the second cylinder block, a second discharge region that communicates with the second compression chamber in the discharge stroke of the second compression mechanism, a second discharge region that communicates with the second discharge region, and the second A second outer peripheral discharge chamber that circulates around the cylinder block,
The first discharge region and the second discharge region communicate with each other through a discharge communication path,
Wherein the discharge chamber to the lower side of the first outer peripheral discharge chamber, without passing through the second outer peripheral discharge chamber, communicating with the oil discharge passage can be discharged to the discharge chamber the lubricating oil of the first outside inner discharge chamber it shall be the feature of the being.

In the tandem vane type compressor of the present invention, the first discharge area and the second discharge area are communicated with each other by a discharge communication path. The discharge chamber and the lower side of the first outer peripheral discharge chamber communicates with the oil discharge passage. Oil discharge passage is the passage for discharging the discharged refrigerant gas from the first compression chamber to the discharge chamber is an independent route.

  When the lower part of the first outer peripheral discharge chamber communicates with the discharge chamber through the oil discharge passage, even if the lubricating oil contained in the refrigerant gas is separated in the first discharge region and accumulates in the first outer peripheral discharge chamber, Lubricating oil accumulated in the first outer peripheral discharge chamber is discharged to the discharge chamber by the oil passage. Further, even if the lubricating oil contained in the refrigerant gas is separated in the second discharge region and collected in the second outer peripheral discharge chamber, the accumulated lubricating oil is discharged from the first compression chamber into the second outer peripheral discharge chamber. By entering, it tends to be pushed away from the second outer peripheral discharge chamber together with the discharged refrigerant gas. For this reason, it is difficult for the volume of the first outer peripheral discharge chamber and the volume of the second outer peripheral discharge chamber to decrease.

  In this way, the volume of the first outer peripheral discharge chamber and the second outer peripheral discharge chamber are unlikely to decrease due to the oil drainage path, and thus the pulsation reduction effect of the discharged refrigerant gas by the first outer peripheral discharge chamber and the second outer peripheral discharge chamber is suitably achieved It can be maintained and pulsation is difficult to be transmitted to the discharge chamber. Further, the lubricating oil discharged to the discharge chamber by the oil drainage path again contributes to lubrication of the parts constituting the compressor and the refrigeration circuit.

  In the tandem vane compressor, by increasing the communication area of the discharge communication path that connects the first discharge region and the second discharge region, a first outer peripheral discharge chamber that communicates with the first discharge region; The lubricating oil accumulated in the second outer peripheral discharge chamber communicating with the second discharge region is not moved to the discharge chamber. For this reason, depending on the discharge communication path, the pulsation of the discharged refrigerant gas is difficult to be transmitted to the discharge chamber.

  Therefore, the tandem vane compressor of the present invention can exhibit excellent quietness and lubrication performance. Further, in this tandem vane compressor, the volume of the first outer peripheral discharge chamber and the volume of the second outer peripheral discharge chamber are difficult to decrease, so that over compression of the refrigerant gas can be prevented and power loss can be reduced.

  In the tandem vane compressor of the present invention, the compression mechanism may include another compression mechanism in addition to the first compression mechanism and the second compression mechanism. Further, the shell can be composed of a front housing and a rear housing. A cylindrical center housing may be provided between the front housing and the rear housing.

The third side plate is preferably formed with a discharge passage that communicates each second discharge region and the discharge chamber. The oil discharge passage, the second side plate is formed continuously to the second cylinder block and the third side plate, it is not preferable in communication with the lower and the discharge passage of the first outer peripheral discharge chamber. In this case, the oil discharge path can be easily formed as a path independent of the path for discharging the refrigerant gas discharged from the first compression chamber and the refrigerant gas discharged from the second compression chamber into the discharge chamber.

In the above case, oil discharge passage, it is not preferable in communication under the first outer peripheral discharge chamber by cut-out recess in the bottom of the first cylinder block. In this case, the oil discharge passage can be easily communicated with the lower part of the first outer peripheral discharge chamber by a simple recess.

In the above case, the first cylinder block may have a pair of first discharge regions that are symmetrical with respect to the axis of the drive shaft and that may be formed horizontally or substantially horizontally. In the second cylinder block, the pair of second discharge regions are symmetrical with respect to the axis and can be formed horizontally or substantially horizontally. And yet preferably be in communication with each of the respective first discharge region and the second discharge region the discharge communication passage. In this case, the pair of first discharge regions, the pair of second discharge regions, and the discharge communication path are located in the middle in the up-down direction of the compressor. For this reason, the lubricating oil separated from the refrigerant gas moves below the first outer peripheral discharge chamber and hardly accumulates in each first discharge region, each second discharge region, and each discharge communication path.

The discharge chamber communicates with the discharge passage, the lubricating oil separated from the refrigerant gas discharged from the second discharge region, it is not preferable that the separator for storing lubricating oil in the discharge chamber. If the lubricating oil is discharged directly to the oil storage area below the discharge chamber by the oil drainage passage, the oil surface is disturbed by the falling of the lubricating oil on the oil surface of the discharge chamber, and the lubricating oil is mixed with the refrigerant gas again. End up. In this regard, according to the above configuration, the lubricating oil discharged to the discharge chamber through the oil discharge passage is first transferred to the separator via the discharge passage. Then, since the lubricating oil is separated from the refrigerant gas by the separator and then stored in the discharge chamber, it is possible to prevent the lubricating oil from being mixed with the refrigerant gas again.

The separator has a cylindrical guide surface and a cylindrical separation cylinder which is provided on the inner side of the guide surface and is substantially coaxial with the guide surface, and separates the refrigerant gas discharged from each second discharge region from the guide surface. by circulating the separation chamber between the outer peripheral surface of the cylindrical separating lubricating oil, it is not preferable is to discharge to the outside of the compressor led refrigerant gas into the separation barrel. In this case, the lubricating oil is reliably separated by circulating the refrigerant gas mixed with the lubricating oil in the separator separation chamber.

It is preferable that the separator has a separator member that is in contact with the third side plate via a gasket. The oil discharge passage is not preferable to have an oil discharge groove formed in the gasket. In this case, the oil drainage passage can be easily formed by forming the oil drainage groove in the gasket that is easy to groove.

In the tandem vane compressor of the present invention, the shell is formed with a suction port, a front housing that forms a suction chamber with the first side plate, a discharge port, and a discharge chamber with the third side plate. And a rear housing. Then, a first cylinder block and the second cylinder block common, first rotor and the second rotor in common, the first vane and the second vane have preferable that the common. In this case, it is possible to reduce the manufacturing cost by sharing the parts.

  The tandem vane type compressor of the present invention can exhibit excellent quietness and lubricating performance.

1 is a cross-sectional view of a tandem vane compressor of Example 1. FIG. FIG. 2 is a cross-sectional view showing the AA cross section of FIG. 1 according to the tandem vane type compressor of the first embodiment. FIG. 2 is a cross-sectional view showing a BB cross section 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 CC of FIG. 1 according to the tandem vane type compressor of the first embodiment. 3 is a cross-sectional view of a tandem vane type compressor according to Embodiment 2. FIG. FIG. 6 is a cross-sectional view showing a DD cross section of FIG. 5 according to the tandem vane type compressor of Example 2. It is sectional drawing of the tandem type vane type compressor of a reference example . FIG. 9 is a cross-sectional view showing a EE cross section of FIG. 7 according to a tandem vane type compressor of a reference example . FIG. 8 is a cross-sectional view showing a FF cross section of FIG. 7 according to a tandem vane type compressor of a reference example .

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

Example 1
As shown in FIG. 1, the tandem vane compressor according to the first embodiment includes a first side plate 11, a first cylinder block 5, a second side plate 13 in a front housing 1 and a rear housing 3 that are coupled to each other. The second cylinder block 7 and the third side plate 15 are fixed in a accommodated state. The front housing 1 and the rear housing 3 are shells 9. The first and second cylinder blocks 5 and 7 have the same outer shape. In this embodiment, the front housing 1 side is the front side of the tandem vane compressor, and the rear housing 3 side is the rear side of the tandem vane compressor. Further, the upper side of the drawing in each figure is the upper side of the tandem vane compressor, and the lower side of the drawing in each drawing is the lower side of the tandem vane compressor.

  As shown in FIG. 2, the first cylinder block 5 is formed with an elliptical first cylinder chamber 5 a in the direction perpendicular to the axis. As shown in FIG. 3, 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 first side plate 11 and a second side plate 13 and stored in a shell 9. The front and rear of the first cylinder chamber 5a are closed by a first side plate 11 and a second side plate 13, respectively.

  Further, the second cylinder block 7 is sandwiched between the second side plate 13 and the third side plate 15 and stored in the shell 9. The front and rear of the second cylinder chamber 7a are closed by the second side plate 13 and the third side plate 15, respectively. The shell 9, the first and second cylinder blocks 5, 7 and the first to third side plates 11, 13, 15 correspond to the housing.

  The first to third side plates 11, 13, 15 are respectively provided with shaft holes 11a, 13a, 15a. Sliding bearings 17, 19, and 21 are press-fitted into the shaft holes 11a, 13a, and 15a. The front housing 1 is also provided with a shaft hole 1a. A shaft seal device 23 is press-fitted into the shaft hole 1a. The drive shaft 25 is rotatably held by the shaft seal device 23 and the sliding bearings 17, 19, 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 drive shaft 25 by an engine or a motor of the vehicle via an electromagnetic clutch or a pulley. The drive shaft 25 rotates in the clockwise direction toward the plane of FIG. 2 and FIG.

  Further, 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. The second rotor 29 is disposed in the second cylinder chamber 7a.

  As shown in FIG. 2, five first vane grooves 27a are formed in the outer circumferential surface of the first rotor 27 in the radial direction. A first vane 31 is accommodated in each first vane groove 27a so as to be able to appear and retract. A first back pressure chamber 33 is formed between the bottom surface of each first vane 31 and each first vane groove 27a. Two adjacent first vanes 31, 31, the outer peripheral surface of the first rotor 27, the inner peripheral surface of the first cylinder block 5, the rear surface of the first side plate 11, and the front surface of the second side plate 13, A first compression chamber 35 is formed.

  Further, as shown in FIG. 3, five second vane grooves 29 a are also formed in the outer peripheral surface of the second rotor 29 in the radial direction. A second vane 37 is also accommodated in each second vane groove 29a so as to be able to appear and retract. A second back pressure chamber 39 is formed between the bottom surface of each second vane 37 and each second vane groove 29a. 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 second side plate 13, and the front surface of the third side plate Two compression chambers 41 are 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.

  As shown in FIG. 1, a suction chamber 43 is formed between the front housing 1 and the first 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. The first side plate 11 is provided with two suction holes 11 b communicating with the suction chamber 43.

  As shown in FIGS. 1 and 2, the first cylinder block 5 has two first suction areas 5b. As shown in FIG. 1, each suction hole 11b communicates with the first suction region 5b. As shown in FIG. 2, each first suction region 5b communicates with the first compression chamber 35 in the suction stroke by a suction port 5c.

  Further, as shown in FIG. 2, between the first cylinder block 5 and the rear housing 3, there are two first discharge areas 5d and a first outer peripheral discharge chamber 81 communicating with each first discharge area 5d. Is formed.

  Each first discharge region 5 d is a space formed by being recessed from the outer peripheral surface of the first cylinder block 5 toward the axis X <b> 1 of the drive shaft 25. One first discharge region 5d and the other first discharge region 5d are symmetric with respect to the axis X1 of the drive shaft 25. In addition, one first discharge region 5d and the other first discharge region 5d are arranged substantially horizontally with the axis X1 in between. Although not shown in FIG. 1, one first discharge region 5 d and the other first discharge region 5 d are located on the front side of the paper surface of FIG. 1 and the back surface of FIG. 1 with respect to the first rotor 27. Located on the side and.

  As shown in FIGS. 1 and 2, the outer diameter of the first cylinder block 5 is made smaller than the inner diameter of the rear housing 3. Further, the outer peripheral surface of the first cylinder block 5 is slightly bulged at the center in the front-rear direction. The first outer discharge chamber 81 is a substantially cylindrical space that is sandwiched between the outer peripheral surface of the first cylinder block 5 and the inner peripheral surface of the rear housing 3 and circulates around the first cylinder block 5.

  The two compression chambers 35 in the discharge stroke and each first discharge region 5d are communicated with each other by a discharge port 5e. As shown in FIG. 2, a discharge valve 45 that closes each discharge port 5e and a retainer 47 that regulates the lift amount of each discharge valve 45 are provided in each first discharge region 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 and 2, the second side plate 13 is provided with two suction communication paths 13 d communicating with the first suction areas 5 b of the first cylinder block 5.

  As shown in FIGS. 1 and 3, the second cylinder block 7 has two second suction regions 7b. As shown in FIG. 1, each suction communication path 13d communicates with the second suction region 7b. As shown in FIG. 3, each second suction region 7b communicates with the second compression chamber 41 in the suction stroke by a suction port 7c.

  As shown in FIG. 3, between the second cylinder block 7 and the rear housing 3, two second discharge regions 7d and a second outer peripheral discharge chamber 82 communicating with each second discharge region 7d are formed. Has been.

  Each second discharge region 7 d is also a space formed by being recessed from the outer peripheral surface of the second cylinder block 7 toward the axis X <b> 1 of the drive shaft 25. One second discharge region 7d and the other second discharge region 7d are symmetric with respect to the axis X1 of the drive shaft 25. Further, one second discharge region 7d and the other second discharge region 7d are arranged substantially horizontally with the axis X1 interposed therebetween. Although not shown in FIG. 1, one second ejection region 7 d and the other second ejection region 7 d are located on the front side of FIG. 1 and the rear side of FIG. 1 with respect to the first rotor 27. Located on the side and.

  As shown in FIGS. 1 and 3, the outer diameter of the second cylinder block 7 is made smaller than the inner diameter of the rear housing 3, similar to the first cylinder block 5. In addition, the outer peripheral surface of the second cylinder block 7 is slightly swelled in the center in the front-rear direction, like the first cylinder block 5. The second outer peripheral discharge chamber 82 is a substantially cylindrical space that is sandwiched between the outer peripheral surface of the second cylinder block 7 and the inner peripheral surface of the rear housing 3 and circulates around the second cylinder block 7.

  As shown in FIG. 2, the second side plate 13 is provided with two discharge communication paths 13e. Each discharge communication path 13e is a round hole extending in the front-rear direction. One discharge communication path 13e and the other discharge communication path 13e are arranged substantially horizontally with the axis X1 in between. Although not shown in FIG. 1, one discharge communication path 13e and the other discharge communication path 13e are located on the front side of the paper surface of FIG. 1 and the back side of the paper surface of FIG. positioned.

  One discharge communication path 13e has a front end communicating with one first discharge region 5d and a rear end communicating with one second discharge region 7d. The other discharge communication path 13e has a front end communicating with the other first discharge region 5d and a rear end communicating with the other second discharge region 7d.

  As shown in FIGS. 1 and 3, the two compression chambers 41 in the discharge stroke and each second discharge region 7d communicate with each other by a discharge port 7e. As shown in FIG. 3, a discharge valve 49 that closes each discharge port 7e and a retainer 51 that regulates the lift amount of each discharge valve 49 are provided in each second discharge region 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 FIG. 1, a discharge chamber 53 is formed between the third side plate 15 and the rear housing 3. A centrifugal separator 55 is fixed in the discharge chamber 53. The separator 55 has a separator member 57 and a separation cylinder 59.

  The separator member 57 is in contact with the rear surface of the third side plate 15 via a gasket 69. The separator member 57 is formed with a cylindrical guide surface 57b extending vertically. The separation cylinder 59 is fixed to the inside of the guide surface 57b, and extends in a cylindrical shape up and down substantially coaxially with the guide surface 57b. A space between the guide surface 57b and the outer peripheral surface of the separation cylinder 59 is a separation chamber 57a.

  As shown in FIGS. 1, 3, and 4, the third side plate 15 is formed with two discharge passages 15b communicating with the respective second discharge regions 7d. Each discharge passage 15b extends in a round hole shape from the front surface of the third side plate 15 toward the rear surface, and then extends in a groove shape obliquely upward on the rear surface side of the third side plate 15.

  As shown in FIG. 1, the upper end of each discharge passage 15 b communicates with the separation chamber 57 a via a discharge passage 69 e penetrating the gasket 69 and a discharge passage 57 e penetrating the separator member 57. Yes.

  At the lower end of the separator member 57, a communication port 57 c that allows the bottom surface of the separation chamber 57 a to communicate with the discharge chamber 53 is formed. The rear housing 3 has 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 separation cylinder 59.

  An oil drain groove 13 f is recessed in the front surface of the second side plate 13. The oil drain groove 13 f communicates with the first back pressure chamber 33 in the suction stroke or the like by the rotation of the first rotor 27. Although not shown, the second side plate 13 is provided with a chattering prevention valve for preventing chattering of the first compression mechanism 1C.

  An oil drain groove 15 f is also recessed in the front surface of the third side plate 15. The oil drain groove 15 f communicates with the second back pressure chamber 39 in the suction stroke or the like by the rotation of the second rotor 29. Although illustration is omitted, the third side plate 15 is also provided with a chattering prevention valve for preventing chattering of the second compression mechanism 2C.

  The bottom of the discharge chamber 53 communicates with the first back pressure chamber 33 and the second back pressure chamber 39 in the compression stroke and the discharge stroke by a lubricating oil supply passage (not shown).

  As shown in FIGS. 1 and 2, a recess 62 a is formed on the rear surface of the first cylinder block 5. The recess 62a is located directly below the axis X1 and is cut out small from the lowermost rear end side of the outer peripheral surface of the first cylinder block 5 upward.

  As shown in FIGS. 1 to 4, the second side plate 13, the second cylinder block 7, and the third side plate 15 are positioned just below the axis X1 and extend in the front-rear direction parallel to the axis X1. A hole 62b is provided. The front end of the pore 62 b opens into the recess 62 a, and the rear end of the pore 62 b stops midway in the third side plate 15.

  As shown in FIGS. 1 and 4, the third side plate 15 is provided with a pore 62c extending in a direction orthogonal to the axis X1 and communicating with the rear end of the pore 62b and one discharge passage 15b. It has been.

  The oil drainage path 62 is configured by the recess 62a and the pores 62b and 62c. The oil discharge passage 62 communicates the first outer peripheral discharge chamber 81 and the inside of the separator 55 through the discharge passages 15b, 69e, and 57e. The oil discharge passage 62 is a route that is independent of the passage for discharging the discharge refrigerant gas from the first compression chamber 35 and the discharge refrigerant gas from the second compression chamber 41 to the discharge chamber 53.

Drive shaft 25, sliding bearing 17, 19, 21, first side plate 11, the first cylinder block 5, the first vane 31, the discharge valve 45, the retainer 47, the second side plate 13, the second cylinder block 7, the The second vane 37, the discharge valve 49, the retainer 51, the third side plate 15, and the separator 55 are assembled as a sub-assembly.

  An O-ring is attached to the sub-assembly, 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. And the several volt | bolt 71 shown in FIGS. 2-4 is fastened. Thus, the tandem vane type compressor of Example 1 is assembled.

  In the 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 evaporation The vessel is connected to the inlet 1b by piping. 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 suction hole 11b, each first suction region 5b, and each suction port 5c. The refrigerant gas in each first suction region 5b is sucked into the second compression chamber 41 via each suction communication path 13d, each second suction region 7b, and each suction port 7c.

  The refrigerant gas compressed in the first compression chamber 35 is discharged to each first discharge region 5d through the discharge port 5e. The high-pressure refrigerant gas in each first discharge region 5d moves through the first outer discharge chamber 81 and reaches each second discharge region 7d via each discharge communication path 13e. The refrigerant gas compressed in the second compression chamber 41 is discharged to each second discharge region 7d through the discharge port 7e. The high-pressure refrigerant gas in each second discharge region 7d moves in the second outer peripheral discharge chamber 82 and is discharged toward the guide surface 57b of the separator 50 through the discharge passages 15b, 69e, and 57e. For this reason, the refrigerant gas circulates in the separation chamber 57a, and the lubricating oil is centrifuged. The refrigerant gas from which the lubricating oil has been separated is guided into the separation cylinder 59 and discharged from the discharge port 3a toward the condenser.

  The separated lubricating oil is stored in the discharge chamber 53 from the separation chamber 57a through the communication port 57c. Since the discharge chamber 53 has a high pressure, the lubricating oil in the discharge chamber 53 passes through the above-described lubricating oil supply passage (not shown), and the first back pressure chamber 33 and the second back pressure in the compression stroke and the discharge stroke. It is supplied to the pressure chamber 39. For this reason, in this tandem type vane compressor, the high-pressure lubricating oil in each first back pressure chamber 33 and each second back pressure chamber 39 while the first and second compression mechanisms 1C and 2C perform the compression strokes, respectively. Thus, the first and second vanes 31 and 37 are suitably pressed against the inner surfaces of the first and second cylinder chambers 5a and 7a. Thereby, leakage of the refrigerant gas from the first and second compression chambers 35 and 41 is suppressed.

  The lubricating oil supplied to each first back pressure chamber 33 is caused by sliding between the first vane 31 and the first vane groove 27a, and between the first rotor 27, the first side plate 11, and the second side plate 13. This contributes to lubrication such as sliding and sliding between the sliding bearings 17 and 19 and the drive shaft 25. Further, the lubricating oil supplied to each second back pressure chamber 39 is slid between the second vane 37 and the second vane groove 29a, and the second rotor 29, the second side plate 13 and the third side plate 15 are in contact with each other. This contributes to lubrication such as sliding and sliding between the sliding bearings 19 and 21 and the drive shaft 25.

  Here, in the tandem vane compressor according to the first embodiment, the lubricating oil contained in the refrigerant gas is separated in the first discharge region 5 d and collected in the first outer peripheral discharge chamber 81. However, in the tandem vane compressor, each first discharge region 5d, each second discharge region 7d, and each discharge communication path 13e are located in the middle in the up-down direction of the compressor. Therefore, the lubricating oil separated from the refrigerant gas in each first discharge region 5d moves below the first outer peripheral discharge chamber 81, and each first discharge region 5d and each second discharge region located in the middle in the vertical direction. It is difficult to collect in 7d and each discharge communication path 13e. The accumulated lubricating oil is transferred into the discharge chamber 53 through the oil discharge passage 62 as follows.

  That is, the refrigerant gas discharged from each second discharge region 7d and transferred to the separation chamber 57a of the separator 50 is throttled when passing through the discharge passages 15b, 69e, 57e, and the pressure is reduced. For this reason, the pressure in the separation chamber 57 a is lower than the pressure in the first outer peripheral discharge chamber 81. Here, if the lubricating oil is directly discharged to the oil storage area below the discharge chamber 53 by the oil drain passage 62, the oil surface is disturbed by the falling of the lubricating oil on the oil surface of the discharge chamber 53, and the refrigerant gas is changed to the refrigerant gas. Lubricant is mixed again. In this regard, in this embodiment, the lubricating oil discharged to the discharge chamber 53 by the oil discharge passage 62 is first transferred to the separation chamber 57a of the separator 50 via the discharge passages 15b, 69e, 57e, and the lubricating oil is used as the refrigerant. Since it isolate | separates from gas and is stored in the discharge chamber 53, it can suppress that lubricating oil mixes with refrigerant gas again.

  The recess 62a on the front end side of the oil discharge passage 62 is located at the lowermost position of the first outer peripheral discharge chamber 81 where the lubricating oil separated from the refrigerant gas is likely to accumulate, and is a pore on the rear end side of the oil discharge passage 62. 62c extends upward from below and communicates with the discharge passage 15b. Further, the pressure on the recess 62a side is higher than the pressure on the separation chamber 57a side of the separator 55. As a result, the lubricating oil accumulated below the first outer peripheral discharge chamber 81 flows into the pores 62b and 62c from the lowermost portion of the first outer peripheral discharge chamber 81 through the recess 62a. Then, the lubricating oil is transferred into the separation chamber 57a through the discharge passages 15b, 69e, and 57e, and is discharged into the discharge chamber 53 through the communication port 57c.

Further, even if the lubricating oil contained in the refrigerant gas is separated in each second discharge region 7d and is accumulated in the second outer peripheral discharge chamber 82, the accumulated lubricating oil is discharged from the first compression chamber 35 by the first refrigerant gas. By entering the second outer peripheral discharge chamber 82, it is easily pushed away from the second outer peripheral discharge chamber 82 together with the discharged refrigerant gas. For this reason, the volume of the second outer peripheral discharge chamber 82 is unlikely to decrease.

  In this way, in this tandem type vane compressor, the volume of the first outer peripheral discharge chamber 81 and the volume of the second outer peripheral discharge chamber 82 are difficult to decrease. Therefore, the refrigerant discharged by the first outer peripheral discharge chamber 81 and the second outer peripheral discharge chamber 82 The gas pulsation reducing effect can be suitably maintained, and the pulsation is hardly transmitted to the discharge chamber 53. In addition, the lubricating oil is transferred from the first outer peripheral discharge chamber 81 to the discharge chamber 53 by the oil discharge passage 62, and then the first back pressure chamber 33 and the second back pressure chamber 33 in the compression stroke and the discharge stroke by a lubricating oil supply passage (not shown). It contributes to the lubrication of the compressor again by being supplied to the back pressure chamber 39.

  Further, in this tandem vane compressor, each first discharge region is increased by increasing the communication area of the two discharge communication paths 13e that respectively connect the first discharge regions 5d and the second discharge regions 7d. The lubricating oil accumulated in the first outer peripheral discharge chamber 81 communicating with 5d and the second outer peripheral discharge chamber 82 communicating with each second discharge region 7d is not moved to the discharge chamber 53. For this reason, it is difficult for the pulsation of the discharged refrigerant gas to be transmitted to the discharge chamber 53 depending on each discharge communication path 13e.

  Further, in the first outer peripheral discharge chamber 81, there is no entry of the discharged refrigerant gas from other places, and the lubricating oil is easily accumulated as compared with the second outer peripheral discharge chamber 82. For this reason, the oil drainage passage 62 which connects the lower part of the 1st outer periphery discharge chamber 81 and the discharge chamber 53 can exhibit a remarkable effect.

  Therefore, the tandem vane compressor of the first embodiment can exhibit excellent quietness and lubrication performance. Further, in this tandem vane compressor, since the volume of the first outer peripheral discharge chamber 81 and the volume of the second outer peripheral discharge chamber 82 are difficult to decrease, over compression of the refrigerant gas can be prevented and power loss can be reduced.

  Further, in this tandem type vane compressor, the first cylinder block 5 and the second cylinder block 7 are common, the first rotor 27 and the second rotor 29 are common, and the first vane 31 and the second vane 37. Therefore, it is possible to reduce the manufacturing cost by sharing parts.

(Example 2)
As shown in FIGS. 5 and 6, the tandem vane compressor of the second embodiment employs an oil discharge passage 262 instead of the oil discharge passage 62 in the tandem vane compressor of the first embodiment. . Other configurations of the second embodiment are the same as those of the first embodiment. For this reason, about the same structure as Example 1, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  As shown in FIG. 5, a recess 262 a is formed on the rear surface of the first cylinder block 5. The recess 262a has the same configuration as the recess 62a of the first embodiment.

  As shown in FIGS. 5 and 6, the second side plate 13, the second cylinder block 7 and the third side plate 15 are positioned below the axis X1 and extend in the front-rear direction parallel to the axis X1. A hole 262b is provided. The front end of the pore 262b opens to the recess 262a, and the rear end of the pore 262b opens to the rear surface of the third side plate 15.

  As shown in FIG. 6, on the front surface of the gasket 69, that is, the surface that contacts the rear surface of the third side plate 15 facing the back side in FIG. 269s is recessed. The oil drain groove 269s communicates the rear end of the pore 262b and the one discharge passage 15b.

  The oil drainage path 262 is configured by the recess 262a, the pore 262b, and the oil drain groove 269s. The oil drain passage 262 communicates the first outer peripheral discharge chamber 81 and the separator 55 via the discharge passages 15b, 69e, and 57e. The oil discharge path 262 is a path that is independent from the path for discharging the discharge refrigerant gas from the first compression chamber 35 and the discharge refrigerant gas from the second compression chamber 41 to the discharge chamber 53.

  This tandem vane compressor can also achieve the same effects as the tandem vane compressor of the first embodiment.

  Further, in this tandem vane compressor, the oil drain passage 262 can be easily formed by forming the oil drain groove 269s in the gasket 69 that is easy to groove.

(Reference example)
As shown in FIGS. 7 to 9, the tandem vane compressor of the reference example includes two first discharge areas 5 d and two second discharge areas 7 d in the tandem vane compressor of the first embodiment. Instead of the oil discharge path 62 and the two discharge communication paths 13e, the first discharge area 5f, the first discharge area 5g, the second discharge area 7f, the second discharge area 7g, the oil discharge path 362, and the single discharge communication The road 313e is employed. Other configurations of the reference example are the same as those of the first embodiment. For this reason, about the same structure as Example 1, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  The first discharge area 5f shown in FIG. 8 has the same configuration as that of the first discharge area 5d located on the right side in FIG. The first discharge area 5g shown in FIG. 8 has the same configuration as the other first discharge area 5d located on the left side of FIG. The second discharge region 7f shown in FIG. 9 has the same configuration as one second discharge region 7d located on the right side of the sheet of FIG. The second discharge area 7g shown in FIG. 9 has the same configuration as that of the other second discharge area 7d located on the left side of FIG.

  As shown in FIGS. 7 and 9, a recess 362 a is formed on the rear surface of the second cylinder block 7. The recessed portion 362a is located directly below the axis X1 and is cut out small from the lowermost rear end side of the outer peripheral surface of the second cylinder block 7 upward.

  The third side plate 15 is provided with pores 362b that are located directly below the axis X1 and extend in the front-rear direction parallel to the axis X1. The front end of the pore 362 b opens into the recess 362 a, and the rear end of the pore 362 b stops in the middle of the third side plate 15.

  As shown in FIG. 7, the third side plate 15 is provided with a pore 362c that extends in a direction orthogonal to the axis X1 and communicates the rear end of the pore 362b and one discharge passage 15b.

  The oil drainage path 362 is constituted by the recess 362a and the pores 362b and 362c. The oil discharge passage 362 communicates the second outer peripheral discharge chamber 82 and the inside of the separator 55 via the discharge passages 15b, 69e, and 57e. The oil discharge path 362 is a path that is independent of a path for discharging the discharge refrigerant gas from the first compression chamber 35 and the discharge refrigerant gas from the second compression chamber 41 to the discharge chamber 53.

  As shown in FIG. 8, the second side plate 13 is provided with a single discharge communication path 313e. The discharge communication path 313e is a round hole extending in the front-rear direction. The discharge communication path 313e is arranged substantially horizontally with the axis X1. Although not shown in FIG. 7, the discharge communication path 313 e is located on the front side of the sheet of FIG. 7 with respect to the drive shaft 25.

  As shown in FIGS. 8 and 9, only the first discharge region 5f and the second discharge region 7f communicate with each other by a single discharge communication path 313e. On the other hand, the first discharge region 5g and the second discharge region 7g are not in direct communication with each other through the discharge communication path. The first discharge region 5g communicates with the second discharge regions 7f and 7g and the second outer discharge chamber 82 via the first outer discharge chamber 81, the first discharge region 5f, and the discharge communication path 313e.

Further, in this tandem type vane compressor, as shown in FIG. 8, the refrigerant gas discharged from the first compression chamber 35 to the first discharge region 5g by the discharge stroke performed intermittently in the first compression mechanism 1C. Moves along the first outer peripheral discharge chamber 81 to the first discharge region 5f. Then, the refrigerant gas moves to the second discharge region 7f and the second outer peripheral discharge chamber 82 via the discharge communication path 313e. At this time, by forcibly flowing the refrigerant gas below the first outer peripheral discharge chamber 81, the lubricating oil accumulated below the first outer peripheral discharge chamber 81 is wound up by the refrigerant gas, and along the first outer peripheral discharge chamber 81. To the first discharge region 5f, and move to the second discharge region 7f and the second outer peripheral discharge chamber 82 via the discharge communication path 313e. Further, since the pressure in the separation chamber 57a of the separator 55 is lower than the pressure in the second outer peripheral discharge chamber 82, it is separated from the refrigerant gas in the second discharge regions 7f and 7g and accumulated in the second outer peripheral discharge chamber 82. Lubricating oil or lubricating oil moved from the first outer peripheral discharge chamber 81 to the second outer peripheral discharge chamber 82 via the discharge communication path 313e enters the discharge passage 15b via the recessed portion 362a and the pores 362b and 362c located below. Then, it is reliably transferred to the discharge chamber 53.

  This tandem vane compressor can also achieve the same effects as the tandem vane compressors of the first and second embodiments.

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.

  For example, the pore 362c of the oil drain passage 262 of the second embodiment is eliminated, the pore 362b is opened on the rear surface of the third side plate 15, and the oil drain groove similar to the oil drain groove 269s of the second embodiment is formed in the gasket 69. The pores 362b and the discharge passage 15b may be communicated with each other by the oil drain groove.

  The present invention can be used for an air conditioner such as a vehicle.

DESCRIPTION OF SYMBOLS 1, 3, 5, 7, 9, 11, 13, 15 ... Housing 1 ... Front housing 3 ... Rear housing 5 ... 1st cylinder block 7 ... 2nd cylinder block 9 ... Shell 11 ... 1st side plate 13 ... 2nd Side plate 15 ... Third side plate 43 ... Suction chamber 53 ... Discharge chamber 35 ... First compression chamber 41 ... Second compression chamber 25 ... Drive shaft 1C ... First compression mechanism 2C ... Second compression mechanism 5a ... First cylinder chamber 27a ... 1st vane groove 27 ... 1st rotor 31 ... 1st vane 7a ... 2nd cylinder chamber 29a ... 2nd vane groove 29 ... 2nd rotor 37 ... 2nd vane 1b ... Inlet 3a ... Discharge port 5d, 5f, 5g ... 1st discharge area 81 ... 1st outer periphery discharge chamber 7d, 7f, 7g ... 2nd discharge area 82 ... 2nd outer periphery discharge chamber X1 ... Shaft center of drive shaft 13e, 313e ... Discharge communication path 62a, 62a ... concave portion 55 ... separator 62,262,362 ... oil discharge passage 57 b ... guide surface 59 ... separating cylinder 57a ... separation chamber 15b ... discharge passage 69 ... gasket 57 ... separator member 269S ... oil discharge groove

Claims (8)

A suction chamber, a discharge chamber, and a compression chamber are formed in the housing, and a drive shaft is rotatably supported. The rotation of the drive shaft causes the compression chamber to draw refrigerant gas from the suction chamber. A plurality of compression mechanisms that perform a suction stroke for suction, a compression stroke for compressing the refrigerant gas in the compression chamber, and a discharge stroke for discharging the refrigerant gas in the compression chamber to the discharge chamber are tandemly coupled,
Each of the compression mechanisms includes a first cylinder chamber formed in the housing, a first rotor provided in the first cylinder chamber so as to be rotatable by the drive shaft, and having a plurality of first vane grooves, A first vane which is provided in each first vane groove so as to be able to appear and retract, and forms a first compression chamber which is the compression chamber positioned forward together with an inner surface of the first cylinder chamber and an outer surface of the first rotor; A first compression mechanism;
A second cylinder chamber formed in the housing; a second rotor rotatably provided in the second cylinder chamber by the drive shaft; and a plurality of second vane grooves formed therein; and each second vane groove And a second compression mechanism having a second vane that forms a second compression chamber, which is a compression chamber located rearward together with the inner surface of the second cylinder chamber and the outer surface of the second rotor. In the provided tandem vane compressor,
The housing forms a shell, a shell in which a suction port and a discharge port connected to the outside are formed, and a first side plate that is housed in the shell and forms the suction chamber that communicates with the suction port together with the shell. And a second side plate that is housed in the shell and partitions the first compression mechanism and the second compression mechanism, and the discharge chamber that is housed in the shell and communicates with the discharge port together with the shell. A third side plate to be formed, a first cylinder block sandwiched between the first side plate and the second side plate and housed in the shell and forming the first cylinder chamber, and the second side plate And a second cylinder block sandwiched between the third side plate and housed in the shell and forming the second cylinder chamber,
Between the shell and the first cylinder block, a first discharge region communicating with the first compression chamber in the discharge stroke of the first compression mechanism, communicating with the first discharge region, and the first A first outer discharge chamber that circulates around the cylinder block,
Between the shell and the second cylinder block, a second discharge region that communicates with the second compression chamber in the discharge stroke of the second compression mechanism, a second discharge region that communicates with the second discharge region, and the second A second outer peripheral discharge chamber that circulates around the cylinder block,
The first discharge region and the second discharge region communicate with each other through a discharge communication path,
Wherein the discharge chamber to the lower side of the first outer peripheral discharge chamber, without passing through the second outer peripheral discharge chamber, communicating with the oil discharge passage can be discharged to the discharge chamber the lubricating oil of the first outside inner discharge chamber A tandem vane compressor characterized by In the third side plate, a discharge passage that connects each of the second discharge regions and the discharge chamber is formed,
The oil drainage passage is formed continuously with the second side plate, the second cylinder block, and the third side plate, and communicates with a lower portion of the first outer peripheral discharge chamber and the discharge passage. The tandem vane compressor according to 1.   3. The tandem vane compressor according to claim 2, wherein the oil discharge passage communicates with the lower portion of the first outer peripheral discharge chamber through a recess cut out in a lower portion of the first cylinder block. In the first cylinder block, the pair of first discharge areas are symmetrical with respect to the axis of the drive shaft and are formed horizontally or substantially horizontally,
In the second cylinder block, a pair of the second discharge regions are symmetrical with respect to the axis, and are formed horizontally or substantially horizontally.
4. The tandem vane compressor according to claim 2, wherein each of the first discharge areas and each of the second discharge areas communicate with each other through the discharge communication path. The discharge chamber is provided with a separator that communicates with the discharge passage, separates the lubricating oil from the refrigerant gas discharged from the second discharge region, and stores the lubricating oil in the discharge chamber. Item 5. The tandem vane compressor according to any one of Items 2 to 4 . The separator has a cylindrical guide surface and a cylindrical separation cylinder provided inside the guide surface and substantially coaxial with the guide surface, and the refrigerant gas discharged from each of the second discharge regions Circulates in a separation chamber between the guide surface and the outer peripheral surface of the separation cylinder to separate the lubricating oil, guide the refrigerant gas to the inside of the separation cylinder, and discharge it to the outside of the compressor. The tandem vane type compressor according to claim 5 . The separator is formed having a separator member that comes into contact with the third side plate via a gasket,
The tandem vane compressor according to claim 6 , wherein the oil drain passage has a drain groove formed in the gasket. The shell includes a front housing in which the suction port is formed and forms the suction chamber together with the first side plate, and a rear housing in which the discharge port is formed and forms the discharge chamber together with the third side plate. Become
The first cylinder block and the second cylinder block are common,
The first rotor and the second rotor are common,
The tandem vane compressor according to any one of claims 1 to 7 , wherein the first vane and the second vane are common.

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