JP2017014980A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane type compressor capable of exerting high quietness.SOLUTION: A vane type compressor is provided with a first transmission pin 110, a second transmission pin 120, and a first coil spring 91 as an elastic member, in a first insertion hole 61. The first and second transmission pins 110, 120 transmit mutual displacements of the first vane 51 and the second vane 52. The first coil spring 91 energizes the first vane 51 and the second vane 52 in directions separating from each other through the first and second transmission pins 110, 120. The first transmission pin 110 is pressed and supported to the first vane 51. The second transmission pin 120 is pressed and supported to the second vane 52, and extended toward the first vane 51 so as to face the first transmission pin 110 with a clearance S1.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a vane type compressor.

  Patent Document 1 discloses a conventional vane type compressor. This vane type compressor includes a housing, a rotor, and four vanes. A cylinder chamber is formed in the housing. The rotor is provided in the cylinder chamber so as to be rotatable around the rotation axis. The rotor includes two first vane grooves extending toward the rotation axis, and two second vane grooves extending toward the rotation axis and symmetric with each first vane with respect to the rotation axis. Is formed. A first vane is provided in each first vane groove so as to be able to appear and appear, and a second vane is provided in each second vane groove so as to be able to appear and appear.

  The rotor is formed with two communicating holes extending in the radial direction. The first vane groove and the second vane groove communicate with each other through one communication hole, and the other first vane groove and the second vane groove communicate with each other through one communication hole. Further, an operating rod extending in the radial direction of the rotor from one end side to the other end side is inserted into each communication hole.

  A first coil spring is accommodated in the first vane groove, and a second coil spring is accommodated in the second vane groove. Specifically, the first coil spring is disposed between the bottom surface of the first vane and one end side of the operating rod, and biases the first vane and the operating rod away from each other. The second coil spring is disposed between the bottom surface of the second vane and the other end side of the operating rod, and urges the second vane and the operating rod away from each other.

  In this vane type compressor, the displacement of the first vane buried in the first vane groove is transmitted to the second vane through the operating rod and the first and second coil springs. The displacement of the second vane buried in the second vane groove is transmitted to the first vane through the operating rod and the first and second coil springs. Here, the fluctuation of the distance between the first vane and the second vane when the first vane appears and disappears with respect to the first vane groove and the second vane appears and disappears with respect to the second vane groove is as follows. It is absorbed by the expansion and contraction of the coil spring.

  Thereby, in this vane type compressor, each first vane is caused to appear and disappear relative to the first vane groove, and each second vane is indicated relative to the second vane groove. Thus, in this vane type compressor, a compression chamber is formed by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and two vanes adjacent to each other around the rotation axis. The The fluid is sucked into the compression chamber and compressed by the rotation of the rotor.

Japanese Utility Model Publication No. 49-26104

  However, in the above conventional vane type compressor, since the first vane and the operating rod are arranged apart from each other, when the first vane appears and disappears with respect to the first vane groove, There is a risk of collision with one end of the operating rod. The same applies to the second vane and the operating rod. In these cases, noise due to hitting sounds is intermittently generated as the rotor rotates.

  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 vane type compressor which can exhibit high silence.

The vane type compressor of the present invention includes a housing in which a cylinder chamber is formed,
A rotor provided in the cylinder chamber so as to be rotatable around a rotation axis, and formed with an even number of vane grooves;
A vane provided so as to be able to appear and disappear in each of the vane grooves,
A vane type compression in which a compression chamber is formed by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and the two vanes adjacent to each other around the rotation axis. In the machine
Each of the vane grooves includes a first vane groove and a second vane groove extending in the extending direction of the first vane groove.
Each vane includes a first vane provided in the first vane groove and a second vane provided in the second vane groove,
The rotor is formed with a communication hole that communicates the first vane groove and the second vane groove,
The communication hole includes a first transmission pin, a second transmission pin, and an elastic member that urges the first vane and the second vane away from each other via the first transmission pin and the second transmission pin. And
The first transmission pin is pressed and supported against the first vane,
The second transmission pin is supported by pressing against the second vane and extends toward the first vane so as to face the first transmission pin with a gap.

  In the vane type compressor of the present invention, the elastic member biases the first vane via the first transmission pin and biases the second vane via the second transmission pin. Accordingly, the displacement of the first vane buried in the first vane groove is transmitted to the second vane through the first and second transmission pins and the elastic member. Further, the displacement of the second vane buried in the second vane groove is transmitted to the first vane through the first and second transmission pins and the elastic member.

  Here, the first transmission pin and the second transmission pin are arranged facing each other with a gap. For this reason, when the first vane is raised and lowered with respect to the first vane groove and the second vane is raised and lowered with respect to the second vane groove, the first transmission pin and the second transmission pin are the first vane and the second vane. It can absorb the fluctuation of the distance. Therefore, in this vane type compressor, the first vane and the second vane can be suitably pressed against the inner peripheral surface of the cylinder chamber, and the first transmission pin and the second transmission pin rotate the rotor during operation. There is no hindrance.

  In this vane type compressor, the first transmission pin is pressed and supported by the elastic member, so that it is not separated from the first vane. For this reason, there is no hitting sound caused by the collision between the first transmission pin and the first vane during operation. Similarly, the second transmission pin is not separated from the second vane by being pressed and supported by the elastic member. For this reason, the hitting sound by the 2nd transmission pin and the 2nd vane colliding at the time of operation does not arise.

  Therefore, the vane type compressor of the present invention of the present invention can exhibit high silence.

  The elastic member is preferably provided in a compressed state. In this case, the elastic member can favorably bias the first vane and the second vane via the first transmission pin and the second transmission pin.

  Further, the second vane can protrude from the second vane groove by the pressing force with which the first vane is buried in the first vane groove. And it is preferable that a 1st vane protrudes from the inside of a 1st vane groove | channel by the pressing force by which a 2nd vane embeds in a 2nd vane groove | channel. In this case, the displacement of the first vane relative to the first vane groove can be suitably transmitted to the second vane, and the displacement of the second vane relative to the second vane groove can be favorably transmitted to the first vane. it can.

  The first vane may be formed with a first recess that is recessed from the bottom surface on the rotational axis side. In addition, the second vane may be formed with a second recess that is recessed from the bottom surface on the rotation axis side. Further, the first transmission pin includes a first loosely fitted portion loosely fitted in the first recess, a first shaft portion extending in a direction opposite to the first loosely fitted portion, a first loosely fitted portion and a first shaft. 1st flange part which is formed between the parts and contact | abuts the bottom face in which the 1st hollow part was recessedly provided. The second transmission pin includes a second loosely fitting portion loosely fitted in the second hollow portion, a second shaft portion extending in a direction opposite to the second loosely fitting portion, a second loosely fitting portion and a second shaft. And a second flange portion that is formed between the first and second portions and abuts the bottom surface in which the second depression is provided. Further, the communication hole can communicate the first dent part and the second dent part. The elastic member is preferably a coil spring supported by the first shaft portion and the second shaft portion, with one end abutting on the first flange portion and the other end abutting on the second flange portion.

  In this case, the first transmission pin of the first transmission pin is loosely fitted into the first recess portion, whereby the first transmission pin is assembled to the first vane while being positioned. Further, the second transmission pin of the second transmission pin is loosely fitted into the second recess, so that the second transmission pin is assembled to the second vane while being positioned. Therefore, the first transmission pin can be easily assembled to the first vane, and the second transmission pin can be easily assembled to the second vane. Moreover, the structure of an elastic member can be simplified by making an elastic member into a coil spring. For these reasons, the vane compressor can be easily manufactured.

  The coil spring is supported by the first shaft portion of the first transmission pin and the second shaft portion of the second transmission pin, respectively. For this reason, the coil spring can suitably bias the first vane via the first transmission pin and can favorably bias the second vane via the second transmission pin.

  Further, the first flange portion of the first transmission pin comes into contact with the bottom surface of the first vane. Further, the second flange portion of the second transmission pin comes into contact with the bottom surface of the second vane. The first flange portion is kept in contact with the bottom surface of the first vane by being pressed and supported by the coil spring, and the second flange portion is kept in contact with the bottom surface of the second vane. . For this reason, even if it does not press-fit a 1st transmission pin in a 1st hollow part, it can be set as the state which a 1st transmission pin does not separate from the bottom face of a 1st vane. Similarly, even if the second transmission pin is not press-fitted into the second recess, the second transmission pin can be kept away from the bottom surface of the second vane. For this reason, the deformation | transformation of the 1st vane, the 2nd vane, etc. by press-fitting the 1st and 2nd transmission pin in the 1st and 2nd hollow parts do not arise. For these reasons, manufacturing can be facilitated.

  Further, in this vane type compressor, since the first and second loose fitting portions are loosely fitted in the first and second hollow portions, respectively, the dimensions of the first and second loose fitting portions and the first and second hollow portions. Accuracy can be relaxed. Therefore, the degree of freedom in designing the first and second transmission pins and the first and second vanes can be increased. Thereby, for example, in the first transmission pin, the first loosely fitting portion and the first shaft portion can be formed to have different diameters. The same applies to the second transmission pin.

  The first shaft portion may be formed with a first reduced diameter portion that decreases in diameter toward the second transmission pin. And it is preferable that the 2nd reduced diameter part which diameter-reduces toward the 1st transmission pin is formed in the 2nd axial part. In this case, it is possible to suppress the coil spring from being sandwiched between the first shaft portion and the second shaft portion. For this reason, a coil spring can energize the 1st vane and the 2nd vane suitably.

  The first flange portion and the second flange portion preferably have a smaller diameter than the communication hole. In this case, it can prevent that a 1st flange part and a 2nd flange part contact with the inner wall of a communicating hole. Accordingly, the first vane can be made to appear and disappear suitably with respect to the first vane groove, and the second vane can be made to appear and appear suitably with respect to the second vane groove.

  A discharge chamber may be formed in the housing. Further, a space between the bottom surface of the first vane and the bottom surface of the first vane groove can be a first back pressure chamber. Further, a space between the bottom surface of the second vane and the bottom surface of the second vane groove can be a second back pressure chamber. In addition, a rotation shaft that extends in the direction of the rotation axis and is rotatably supported by the housing can be press-fitted into the rotor. And it is preferable that the back pressure flow path which connects a discharge chamber, a 1st back pressure chamber, and a 2nd back pressure chamber is formed in the rotating shaft and the rotor.

  In this case, the elastic member presses and supports the first vane and the second vane against the inner peripheral surface of the cylinder chamber, and the first back pressure chamber and the second back pressure chamber also cause the first pressure. The vane and the second vane can be pressed against the inner peripheral surface of the cylinder chamber. For this reason, while being able to press a 1st vane and a 2nd vane suitably to the internal peripheral surface of a cylinder chamber, it can make it more difficult to leak a fluid from a compression chamber.

  Moreover, it is preferable that a communicating hole penetrates a rotating shaft and is used as a part of back pressure flow path. In this case, the communication hole can function as a back pressure channel, and the configuration of the back pressure channel can be simplified.

  The first vane and the second vane can have the same shape. The first transmission pin and the second transmission pin preferably have the same shape. In this case, the first vane and the second vane can be shared, and the first transmission pin and the second transmission pin can be shared. For this reason, manufacture of a vane type compressor can be facilitated and manufacturing cost can be reduced.

  The vane type compressor of the present invention of the present invention can exhibit high silence.

FIG. 1 is a cross-sectional view of the vane type compressor according to the first embodiment. FIG. 2 is an enlarged cross-sectional view of a main part illustrating the rotor, the first vane, the second vane, the first transmission pin, the second transmission pin, the coil spring, and the like according to the vane type compressor of the first embodiment. FIG. 3 is a cross-sectional view showing the AA cross section of FIG. 1 according to the vane type compressor of the first embodiment. FIG. 4 is a cross-sectional view similar to FIG. 3 according to the vane type compressor of the first embodiment. FIG. 5 is an enlarged cross-sectional view of a main part showing a region Q1 in FIG. 2 according to the vane type compressor of the first embodiment. FIG. 6 is a partial cross-sectional view of the vane type compressor according to the second embodiment. FIG. 7 is a partial cross-sectional view of the vane type compressor according to the third embodiment. FIG. 8 is a partial cross-sectional view of the vane compressor according to the fourth embodiment.

  Embodiments 1 to 4 embodying the present invention will be described below with reference to the drawings.

Example 1
As shown in FIG. 1, the electric vane compressor (hereinafter simply referred to as “compressor”) according to the first embodiment is an example of a specific aspect of the vane compressor of the present invention. The compressor includes a motor housing 1, a motor mechanism 3, a first side plate 4, a second side plate 5, a cylinder block 7, a cover 9, and a compression mechanism 13. The motor housing 1, the first and second side plates 4, 5, the cylinder block 7 and the cover 9 are examples of the “housing” of the present invention.

  In the following description, the motor housing 1 side on the left side of FIG. 1 is the front side of the compressor, and the cover 9 side on the right side of FIG. 1 is the rear side of the compressor. Further, the upper side of the page of FIG. 1 is the upper side of the compressor, and the lower side of the page of FIG. 1 is the lower side of the compressor. In FIG. 2 and subsequent figures, the front-rear direction and the vertical direction are displayed in correspondence with FIG. In addition, the front-back direction and the up-down direction in Example 1 are examples. The mounting posture of the compressor of the present invention is appropriately changed in accordance with the vehicle or the like to be mounted.

  The motor housing 1 extends in the axial direction from the front end side to the rear end side, has a bottomed cylindrical shape with the front end side closed by a bottom wall 1A and an opening 1B on the rear end side. The motor housing 1 forms a motor chamber 1C that also serves as a suction chamber. The motor housing 1 has a cylindrical portion 1D. The cylindrical portion 1D has a substantially cylindrical shape with the rotation axis X1 of the rotation shaft 19 as the central axis. The front peripheral edge of the cylindrical portion 1D is connected to the outer peripheral edge of the bottom wall 1A. The cylindrical portion 1D is formed with a suction port 1E that communicates the outside with the motor chamber 1C. An evaporator of a vehicle air conditioner is connected to the suction port 1E by a pipe (not shown). Further, a shaft support 1G protrudes from the bottom wall 1A. A bearing device 21 is provided on the shaft support 1G.

  The motor mechanism 3 includes a stator 15 and a motor rotor 17. The stator 15 is fixed to the inner peripheral surface of the cylindrical portion 1D. Further, the lead wire 16C and the cluster block 16 are accommodated in the cylindrical portion 1D.

  The cluster block 16 has connection terminals 16A and 16B. The connection terminal 16A protrudes outside through the bottom wall 1A. The connection terminal 16B is connected to the stator 15 via the lead wire 16C. Thereby, the stator 15 is appropriately supplied with power from the power supply device (not shown) via the cluster block 16 and the lead wire 16C.

  The motor rotor 17 is disposed in the stator 15. The motor rotor 17 is inserted through a rotation shaft 19 having a rotation axis X1 extending in the front-rear direction as an axis. A front end portion of the rotating shaft 19 is pivotally supported by a bearing device 21.

  A cover 9 is fixed to the rear end of the motor housing 1 by a plurality of bolts (not shown). The cover 9 has a bottomed cylindrical shape in which the rear end side is closed by the bottom wall 9D and the front end side has an opening 9E. The opening 9E of the cover 9 is in contact with the opening 1B of the motor housing 1, and the motor housing 1 and the cover 9 are closed. A gasket 22 is provided between the opening 1 </ b> B of the motor housing 1 and the opening 9 </ b> E of the cover 9.

  A first step portion 9F is formed on the opening 9E side of the cover 9 and is recessed in an annular shape coaxial with the rotation axis X1 of the rotation shaft 19. The first side plate 4 is fitted to the first step portion 9F. On the opening 1 </ b> B side of the motor housing 1, a second step portion 1 </ b> H is formed that is recessed in an annular shape coaxial with the rotation axis X <b> 1 of the rotation shaft 19. The first side plate 4 is also fitted to the second step portion 1H. The first side plate 4 is a flat plate member extending in the radial direction orthogonal to the rotational axis X1. The outer peripheral edge of the first side plate 4 is sandwiched from the front and rear by the second step portion 1H of the motor housing 1 and the first step portion 9F of the cover 9.

  An O-ring 23 is provided between the outer peripheral surface of the first side plate 4 and the inner peripheral surface of the first step portion 9F. The first side plate 4 is provided with a shaft hole 4A through which the rotary shaft 19 is inserted. In the shaft hole 4A, plating (not shown) for suitably sliding the rotating shaft 19 is formed.

  A cylinder block 7, a second side plate 5, and a block 35 are accommodated in the cover 9. The cylinder block 7 and the second side plate 5 are assembled to the rear surface of the first side plate 4 by bolts 25A to 25D shown in FIGS. As shown in FIG. 1, the cylinder block 7 is sandwiched between the first side plate 4 and the second side plate 5 from the front and rear.

  The second side plate 5 is fitted to the inner peripheral surface of the cover 9. The second side plate 5 is a flat plate member extending in the radial direction orthogonal to the rotation axis X1. An O-ring 24 is provided between the outer peripheral surface of the second side plate 5 and the inner peripheral surface of the cover 9.

  The second side plate 5 is provided with a shaft hole 5A through which the rotary shaft 19 is inserted. The shaft hole 5A is formed with a plating (not shown) for suitably sliding the rotating shaft 19. The rear end portion of the rotation shaft 19 is supported by the shaft hole 5A. Thus, the rotating shaft 19 is pivotally supported at both ends by the bottom wall 1A of the motor housing 1 and the shaft hole 5A of the second side plate 5, and can rotate about the rotation axis X1.

  A discharge chamber 9 </ b> A is formed between the bottom wall 9 </ b> D side of the cover 9 and the rear surface of the second side plate 5. The cover 9 is formed with a discharge port 9B that communicates the outside with the discharge chamber 9A. A condenser of a vehicle air conditioner is connected to the discharge port 9B by a pipe (not shown).

  The block 35 is fixed to the rear surface of the second side plate 5. The block 35 is formed with an oil separation chamber 35 </ b> A that has a cylindrical shape and extends in a direction perpendicular to the axis. A cylindrical tube member 53 is fixed to the oil separation chamber 35A. The upper end of the cylindrical member 53 is open to the discharge chamber 9A. The lower end of the oil separation chamber 35A is opened to the discharge chamber 9A by an oil discharge port 35B. In the second side plate 5 and the block 35, passages 5B and 35C are formed. The passages 5B and 35C communicate between the oil separation chamber 35A and a discharge space 37 described later. These oil separation chambers 35A and the cylindrical member 53 constitute an oil separator.

  The portion surrounding the shaft hole 5 </ b> A on the rear surface of the second side plate 5, the rear end surface of the rotary shaft 19, and the front surface of the block 35 form an oil supply chamber 310.

  The second side plate 5 is formed with a first passage 5E that communicates with the bottom of the discharge chamber 9A and extends upward so as to approach the rotation axis X1. The second side plate 5 is formed with a second passage 5 </ b> F that communicates the upper end of the first passage 5 </ b> E with the oil supply chamber 310.

  As shown in FIG. 2, the cylinder block 7 extends in a cylindrical shape in the direction of the rotation axis X1. As shown in FIGS. 3 and 4, the cylinder block 7 forms a cylinder chamber 31 together with the first and second side plates 4 and 5. In the present embodiment, the cross-sectional shape of the inner peripheral surface 31S of the cylinder chamber 31 is a perfect circle that is eccentric with respect to the rotation axis X1. The front surface of the cylinder chamber 31 corresponds to “one surface of the cylinder chamber” in the present invention, and the rear surface of the cylinder chamber 31 corresponds to “other surface of the cylinder chamber” in the present invention. In addition to the front surface, the inner peripheral surface 31S, and the rear surface of the cylinder chamber 31, the first and second vanes 51 and 52 are provided with plating (not shown) so as to slide appropriately with the rotor 41. Details of the first and second vanes 51 and 52 and the rotor 41 will be described later.

  Further, as shown in FIG. 1, the first side plate 4 is formed with a suction passage 33A that opens in the axial direction and communicates with the motor chamber 1C. The cylinder block 7 is formed with a suction passage 33B communicating with the suction passage 33A. As shown in FIGS. 3 and 4, the suction passage 33 </ b> B communicates with the cylinder chamber 31 through a suction port 33 </ b> C that is recessed in the cylinder block 7.

  The cylinder block 7 is provided with a discharge space 37 that opens to the outer peripheral side. The discharge space 37 communicates with the cylinder chamber 31 by a discharge port 37 </ b> A that is recessed from the outer peripheral surface of the cylinder chamber 31. In the discharge space 37, a discharge reed valve 39 that opens and closes the discharge port 37A and a retainer 39A that regulates the opening degree of the discharge reed valve 39 are fixed to the cylinder block 7 by bolts 39B.

  The compression mechanism 13 includes a cylinder chamber 31, a rotor 41, and first and second vanes 51 and 52.

  As shown in FIG. 1, the rotary shaft 19 is press-fitted into the rotor 41. Thereby, the rotor 41 can rotate in synchronization with the rotary shaft 19 in the cylinder chamber 31. As shown in FIGS. 3 and 4, the cross-sectional shape of the outer peripheral surface 41 </ b> S of the rotor 41 is a perfect circle centered on the rotation axis X <b> 1. In this embodiment, the rotation direction R1 of the rotor 41 is counterclockwise toward the paper surface of FIGS.

  The rotor 41 is formed with a first vane groove 41A and a second vane groove 41B. The first vane groove 41A and the second vane groove 41B extend in the radial direction of the rotor 41 while passing through the rotation axis X1. Here, the second vane groove 41B extends in the extending direction of the first vane groove 41A, and the first vane groove 41A and the second vane groove 41B are symmetrical with respect to the rotation axis X1.

  A first vane 51 is provided in the first vane groove 41A. A second vane 52 is provided in the second vane groove 41B. As the rotor 41 rotates, the first vane 51 slides in and out of the first vane groove 41 </ b> A by bringing the tip portion into sliding contact with the inner peripheral surface 31 </ b> S of the cylinder chamber 31. As the rotor 41 rotates, the second vane 52 slides in and out of the second vane groove 41 </ b> B by sliding the tip of the second vane 52 on the inner peripheral surface 31 </ b> S of the cylinder chamber 31. The first vane 51 and the second vane 52 are both formed in a flat plate shape and have the same shape.

  As shown in FIG. 2, a recess 51 </ b> H and a recess 51 </ b> J are recessed in the bottom surface 51 </ b> S on the rotation axis X <b> 1 side in the first vane 51. The recess 51H and the recess 51J have the same shape, and extend from the bottom surface 51S in the radial direction of the rotor 41, respectively. Moreover, in the bottom face 51S, the hollow part 51J is located ahead of the hollow part 51H. These hollow part 51H and hollow part 51J correspond to the 1st hollow part in this invention.

  In the second vane 52, a recess 52H and a recess 52J are recessed in the bottom surface 52S on the rotation axis X1 side. The recess 52H and the recess 52J have the same shape, and extend from the bottom surface 52S in the radial direction of the rotor 41, respectively. Moreover, in the bottom face 52S, the hollow part 52J is located ahead of the hollow part 52H. These hollow part 52H and hollow part 52J correspond to the 2nd hollow part in this invention.

  As shown in FIGS. 3 and 4, the compression chamber 30 </ b> A is formed by the front surface of the cylinder chamber 31, the inner peripheral surface 31 </ b> S of the cylinder chamber 31, the rear surface of the cylinder chamber 31, the outer peripheral surface 41 </ b> S of the rotor 41, and the first and second vanes 51 and 52. And the compression chamber 30B is formed.

  As shown in FIG. 2, the rotor 41 and the rotating shaft 19 are formed with a first communication hole 61 and a second communication hole 63. The first communication hole 61 and the second communication hole 63 correspond to the communication holes in the present invention. As shown in FIG. 5, the diameter of the first communication hole 61 is set to a length L1. The same applies to the second communication hole 63.

  As shown in FIG. 2, both the first communication hole 61 and the second communication hole 63 extend in the radial direction of the rotor 41 while passing through the rotation shaft 19 and passing through the rotation axis X <b> 1. It communicates with the bottom surface of the first vane groove 41A and communicates with the bottom surface of the second vane groove 41B on the other end side. That is, the first vane groove 41 </ b> A and the second vane groove 41 </ b> B communicate with each other through the first communication hole 61 and the second communication hole 63. Here, the second communication hole 63 is located in front of the first communication hole 61. Thereby, the 1st communicating hole 61 is connected with the hollow part 51H of the 1st vane 51 on the one end side, and is connected with the hollow part 52H of the 2nd vane 52 on the other end side. The second communication hole 63 communicates with the recess 51J of the first vane 51 on one end side, and communicates with the recess 52J of the second vane 52 on the other end side.

  Two first transmission pins 110 and 130 are assembled to the first vane 51. In addition, two second transmission pins 120 and 140 are assembled to the second vane 52. These first and second transmission pins 110 to 140 have the same shape. The configuration of each of the first and second transmission pins 110 to 140 will be described later.

  The first transmission pin 110 and the second transmission pin 120 are provided in the first communication hole 61. At this time, the first transmission pin 110 and the second transmission pin 120 are arranged coaxially along the first communication hole 61. And in the 1st communicating hole 61, the 1st transmission pin 110 and the 2nd transmission pin 120 face each other while the mutual edge part which becomes the rotating shaft center X1 side has gap S1 between both. Are arranged as follows. A first coil spring 91 is provided in the first communication hole 61.

  On the other hand, the first transmission pin 130 and the second transmission pin 140 are provided in the second communication hole 63. At this time, the first transmission pin 130 and the second transmission pin 140 are coaxially arranged along the second communication hole 63. Then, in the second communication hole 63, the first transmission pin 130 and the second transmission pin 140 face each other while the end portions on the rotation axis X1 side have a gap S2 between them. Are arranged as follows. A second coil spring 93 is provided in the second communication hole 63. These first and second coil springs 91 and 93 correspond to the coil spring in the present invention.

  Here, the gap S1 is set to a distance at which the first transmission pin 110 and the second transmission pin 120 do not collide even when the first vane 51 and the second vane 52 are displaced. The gap S2 is set to a distance at which the first transmission pin 130 and the second transmission pin 140 do not collide even when the first vane 51 and the second vane 52 are displaced. More specifically, the gaps S1 and S2 are the variation width of the distance between the bottom surface 51S of the first vane 51 and the bottom surface 52S of the second vane 52 and the first and second vanes 51 and 52, respectively. It is set in consideration of tolerances such as the transmission pins 110 to 140, the first and second vanes 51 and 52, and the first and second vane grooves 41A and 41B.

  As shown in FIG. 5, the first transmission pin 110 is formed in a substantially cylindrical shape extending in the radial direction of the rotor 41, and includes a first loose fitting portion 111, a first flange portion 113, and a first shaft portion 115. And have. The first flange portion 113 is located between the first loose fitting portion 111 and the first shaft portion 115.

  The first loosely fitting portion 111 extends in the radial direction of the rotor 41 in a direction away from the rotation axis X1 from the first flange portion 113 side. The first loose fitting portion 111 is formed with a smaller diameter than the hollow portion 51H, and is loosely fitted into the hollow portion 51H. Further, the axial length of the first loosely fitting portion 111 is formed to be shorter than the depth of the recessed portion 51H.

  The first flange portion 113 is formed on the entire circumference of the first transmission pin 110 and protrudes in a hook shape between the first loose fitting portion 111 and the first shaft portion 115. The first flange portion 113 is formed with a first end surface 113T located on the first loose fitting portion 111 side and a second end surface 113S located on the first shaft portion 115 side. The first end surface 113T and the second end surface 113S are formed flat. The first flange portion 113 has a diameter set to a length L2 and is larger than the first loose fitting portion 111 and the first shaft portion 115. Here, the length L 2 of the diameter of the first flange portion 113 is smaller than the length L 1 of the diameter of the first communication hole 61. Thereby, the first flange portion 113 has a smaller diameter than the first communication hole 61.

  The first shaft portion 115 extends in the radial direction of the rotor 41 in a direction approaching the rotational axis X1 from the first flange portion 113 side, that is, in a direction opposite to the first loose fitting portion 111. The first shaft portion 115 is formed to have the same diameter as the first loose fitting portion 111. In addition, a first tapered surface 115 </ b> A that decreases in diameter toward the second transmission pin 120 is formed on the rotation shaft center X <b> 1 side of the first shaft portion 115. The first tapered surface 115A corresponds to the first reduced diameter portion in the present invention. In addition, you may form the 1st loose fitting part 111 and the 1st axial part 115 in a different diameter.

  Similar to the first transmission pin 110, the second transmission pin 120 is also formed in a substantially cylindrical shape extending in the radial direction of the rotor 41. The second transmission pin 120 includes a second loose fitting portion 121, a second flange portion 123, and a second shaft portion 125. The second flange portion 123 is located between the second loose fitting portion 121 and the first shaft portion 125.

  The second loosely fitting portion 121 extends in the radial direction of the rotor 41 in a direction away from the rotation axis X1 from the second flange portion 123 side. The second loose fitting portion 121 is formed to have a smaller diameter than the hollow portion 52H, and is loosely fitted into the hollow portion 52H. Further, the axial length of the second loosely fitting portion 121 is formed to be shorter than the depth of the recessed portion 52H.

  The second flange portion 123 is formed on the entire circumference of the second transmission pin 120 and protrudes in a hook shape between the second loose fitting portion 121 and the second shaft portion 125. The second flange portion 123 has a first end surface 123T located on the second loose fitting portion 121 side and a second end surface 123S located on the second shaft portion 125 side. The first end surface 123T and the second end surface 123S are also formed flat. The second flange portion 123 is formed with the same diameter as the first flange portion 113. Thereby, the second flange portion 123 also has a smaller diameter than the first communication hole 61.

  The second shaft portion 125 extends in the radial direction of the rotor 41 in a direction approaching the rotational axis X1 from the second flange portion 123 side, that is, in a direction opposite to the second loosely fitting portion 121. The second shaft portion 125 is formed to have the same diameter as the second loose fitting portion 121. A second taper surface 125 </ b> A that decreases in diameter toward the first transmission pin 110 is formed on the rotation shaft center X <b> 1 side of the second shaft portion 125. The second tapered surface 125A corresponds to the second reduced diameter portion in the present invention. Note that the second loosely fitting portion 121 and the second shaft portion 125 may also be formed with different diameters.

  The first transmission pin 130 includes a first loose fitting portion 131, a first flange portion 133, and a first shaft portion 135. The first flange portion 133 has a first end surface 133T and a second end surface 133S. The first shaft portion 135 is formed with a first tapered surface 135A. The first tapered surface 135A also corresponds to the first reduced diameter portion in the present invention. The configuration of the first transmission pin 130 including the first loose fitting portion 131, the first flange portion 133, and the first shaft portion 135 is the same as that of the first transmission pin 110. For this reason, the detailed description regarding the structure of the 1st transmission pin 130 is abbreviate | omitted.

  The second transmission pin 140 includes a second loose fitting portion 141, a second flange portion 143, and a second shaft portion 145. The second flange portion 143 has a first end surface 143T and a second end surface 143S. The second shaft portion 145 has a second tapered surface 145A. The second tapered surface 145A also corresponds to the second reduced diameter portion in the present invention. The configuration of the second transmission pin 140 including the second loose fitting portion 141, the second flange portion 143, and the second shaft portion 145 is the same as that of the second transmission pin 120. For this reason, the detailed description regarding the structure of the 2nd transmission pin 140 is also abbreviate | omitted.

  As shown in FIG. 5, the first transmission pin 110 is assembled while being positioned on the first vane 51 by loosely fitting the first loose fitting portion 111 into the recess 51 </ b> H of the first vane 51. Here, the clearance between the hollow portion 51H and the first loose fitting portion 111 in the radial direction of the first transmission pin 110 is the first loose fit before the first flange portion 113 contacts the first communication hole 61. The part 111 is set so as to abut the recessed part 51H. Specifically, the distance between the axial centers of the recess 51H and the first flange 113, the diameters of the first flange 113, the first communication hole 63, the recess 51H, and the first loose fitting 111, including tolerances, are included. By setting, an appropriate clearance is formed. The clearance between the hollow portion 51J and the first loose fitting portion 131 is set similarly. And since the axial length of the 1st loose fitting part 111 is shorter than the depth of the hollow part 51H as mentioned above, in the 1st transmission pin 110, the 1st end surface 113T of the 1st flange part 113 is the edge of the hollow part 51H. Surface contact is made with the part 51E. As shown in FIG. 2, the first transmission pin 130 is assembled while being positioned on the first vane 51 by loosely fitting the first loose fitting portion 131 to the recess 51 </ b> J of the first vane 51. Since the axial length of the first loose fitting portion 131 is also shorter than the depth of the recessed portion 51J, the first end surface 133T of the first flange portion 133 is also in surface contact with the edge portion 51F of the recessed portion 51J in the first transmission pin 130. To do.

  The second transmission pin 120 is assembled while being positioned on the second vane 51 by loosely fitting the second loose fitting portion 121 into the recess 52H of the second vane 52. At this time, since the axial length of the second loosely fitting portion 121 is shorter than the depth of the recessed portion 52H, in the second transmission pin 120, the first end surface 123T of the second flange portion 123 faces the edge portion 52E of the recessed portion 52H. Contact. The second transmission pin 140 is assembled while being positioned on the second vane 52 by loosely fitting the second loose fitting portion 141 into the recess 52J of the second vane 52. Since the axial length of the second loose fitting portion 141 is also shorter than the depth of the recessed portion 52J, the first end surface 143T of the second flange portion 143 is in surface contact with the edge portion 52F of the recessed portion 52J also in the second transmission pin 140. To do.

  The first coil spring 91 is disposed between the first transmission pin 110 and the second transmission pin 120 in the first communication hole 61. A first shaft 115 is inserted through one end of the first coil spring 91, and a second shaft 125 is inserted through the other end. As a result, the first coil spring 91 is supported by the first shaft portion 115 and the second shaft portion 125, and as shown in FIGS. 3 and 4, the first vane groove 41 </ b> A and the first It is possible to enter the 2-vane groove 41B.

  As shown in FIG. 2, one end of the first coil spring 91 is in contact with the second end surface 113 </ b> S of the first flange portion 113, and the other end is in contact with the second end surface 123 </ b> S of the second flange portion 123. It is in contact. Accordingly, the first coil spring 91 is provided in a compressed state between the first transmission pin 110 and the second transmission pin 120, and both ends are supported by the first and second flange portions 113 and 123. The first coil spring 91 presses and supports the first vane 51 and the second vane 52 through the first transmission pin 110 and the second transmission pin 120 in a direction away from each other.

  The second coil spring 93 is disposed between the first transmission pin 130 and the second transmission pin 140 in the second communication hole 63. A first shaft 135 is inserted through one end of the second coil spring 93, and a second shaft 145 is inserted through the other end. Thus, the second coil spring 93 is also supported by the first shaft portion 135 and the second shaft portion 145, and as shown in FIGS. 3 and 4, the first vane groove 41A and the second vane spring 93 are rotated along with the rotation of the rotor 41. It is possible to enter the second vane groove 41B.

  Further, as shown in FIG. 2, one end of the second coil spring 93 is in contact with the second end surface 133 </ b> S of the first flange portion 133, and the other end is in contact with the second end surface 143 </ b> S of the second flange portion 143. It is in contact. Accordingly, the second coil spring 93 is provided in a compressed state between the first transmission pin 130 and the second transmission pin 140, and both ends thereof are supported by the first and second flange portions 133 and 143. The second coil spring 93 presses and supports the first vane 51 and the second vane 52 in directions away from each other via the first transmission pin 130 and the second transmission pin 140. Thus, the first vane 51 and the second vane 52 are pressed and supported by the first and second coil springs 91 and 93 in a direction away from each other in the radial direction of the rotor 41.

  Here, by being pressed and supported by the first coil spring 91, in the first transmission pin 110, the first end surface 113T of the first flange portion 113 is not separated from the edge portion 51E. Similarly, in the second transmission pin 120, the first end surface 123T of the second flange portion 123 is not separated from the edge portion 52E. Further, by being biased by the second coil spring 93, the first end surface 133 </ b> T of the first flange portion 133 is not separated from the edge portion 51 </ b> F also in the first transmission pin 130. Similarly, in the second transmission pin 140, the first end surface 143T of the second flange portion 143 is not separated from the edge portion 52F. That is, the first transmission pins 110 and 130 are not separated from the bottom surface 51S of the first vane 51. Further, the second transmission pins 120 and 140 are also not separated from the bottom surface 52S of the second vane 52.

  As shown in FIGS. 3 and 4, a first back pressure chamber 49A is defined between the bottom surface 51S of the first vane 51 and the first vane groove 41A. A space between the bottom surface 52S of the second vane 52 and the second vane groove 41B is a second back pressure chamber 49B.

  As shown in FIG. 1, a first communication path 5 </ b> G is formed in the rotating shaft 19. Further, a second communication path 5H is formed in the rotary shaft 19 and the rotor 41. The first communication path 5G extends from the rear end surface of the rotation shaft 19 toward the front side along the rotation axis X1. The first communication path 5G communicates with the first communication hole 61 and the second communication hole 63. The second communication path 5H extends vertically in the radial direction of the rotation axis X1, and communicates with the first back pressure chamber 49A and the second back pressure chamber 49B. The first and second passages 5E and 5F, the oil supply chamber 310, the first and second communication passages 5G and 5H, and the first and second communication holes 61 and 63 are examples of the “back pressure flow passage” in the present invention. As described above, when the first communication passage 5G communicates with the first and second communication holes 61 and 63, the formation of the second communication passage 5H may be omitted.

  In this compressor, when electric power is supplied to the stator 15 shown in FIG. 1, the motor mechanism 3 operates and the rotating shaft 19 rotates around the rotation axis X1. For this reason, the compression mechanism 13 operates and the rotor 41 rotates in the cylinder block 7. Thereby, each compression chamber 30A, 30B repeats expansion and contraction of the volume. Therefore, the compression chambers 30A and 30B perform a suction stroke for sucking low-pressure refrigerant gas from the motor chamber 1C through the suction passages 33A and 33B and the suction port 33C. Further, after the suction stroke, a compression stroke is performed in which the refrigerant gas is compressed in each of the compression chambers 30A and 30B. Further, after the compression stroke, a discharge stroke is performed in which high-pressure refrigerant gas in the compression chambers 30A and 30B is discharged to the discharge chamber 9A through the discharge port 37A, the discharge space 37, and the passages 5B and 35C. Thus, the air conditioning of the passenger compartment is performed.

  In this compressor, the high-pressure refrigerant gas discharged from the passages 5B and 35C to the oil separation chamber 35A separates the lubricating oil by centrifugal force. Lubricating oil is stored in the discharge chamber 9A. Since the discharge chamber 9A has a high pressure, the first and second back pressure chambers pass through the first and second passages 5E and 5F, the oil supply chamber 310, the first communication passage 5G and the second communication passage 5H. Supplied to 49A and 49B. The lubricating oil is also supplied to the first and second back pressure chambers 49A and 49B from the first communication passage 5G via the first communication hole 61 and the second communication hole 63.

  During this time, in this compressor, the rotor 41 rotates 90 degrees in the rotational direction R1 from the state shown in FIG. In the state shown in the figure, the second vane 52 is pushed by the inner peripheral surface 31S of the cylinder chamber 31 and begins to be buried in the second vane groove 41B. On the other hand, the first vane 51 starts to protrude from the first vane groove 41 </ b> A by being pushed out by the second vane buried in the second vane groove 41.

  That is, as the second vane groove 41B is buried, the second vane 52 causes the second transmission pins 120 and 140 to rotate against the urging force of the first and second coil springs 91 and 93, respectively. Press toward the side. Accordingly, the second vane 52 buried in the second vane groove 41B presses the first vane 51 so as to protrude from the first vane groove 41A. Thus, the displacement of the second vane 52 buried in the second vane groove 41B is transferred to the first vane 51 through the first transmission pins 110 and 130, the second transmission pins 120 and 140, and the first and second coil springs 91 and 93. Communicated. For this reason, the first vane 51 protrudes from the first vane groove 41 </ b> A by the amount of displacement of the second vane 52 and is in sliding contact with the inner peripheral surface 31 </ b> S of the cylinder chamber 31.

  In this compressor, when the rotor 41 further rotates 90 degrees from the state shown in FIG. 4, the positions of the first vane 51 and the second vane 52 are switched to the state shown in FIG. 3. When the rotor 41 further rotates than in this state, the first vane 51 is pushed by the inner peripheral surface 31S of the cylinder chamber 31 and begins to be buried in the first vane groove 41A. Thereby, similarly to the above case, the displacement of the first vane 51 buried in the first vane groove 41 </ b> A causes the first transmission pins 110 and 130, the second transmission pins 120 and 140, and the first and second coil springs 91 to move. , 93 to the second vane 52. Thus, in this compressor, the first and second vanes 51 and 52 repeatedly appear and appear as the rotor 41 rotates.

  Here, the first coil spring 91 is supported by the first shaft portion 115 of the first transmission pin 110 and the second shaft portion 125 of the second transmission pin 120. Similarly, the second coil spring 93 is supported by the first shaft portion 135 of the first transmission pin 130 and the second shaft portion 145 of the second transmission pin 140. Therefore, the postures of the first and second coil springs 91 and 93 are maintained in the first and second communication holes 61 and 63 and in the first and second vane grooves 41A and 41B. For this reason, the first and second coil springs 91 and 93 can suitably transmit the displacement of the first vane 51 to the second vane 52 together with the first transmission pins 110 and 130 and the second transmission pins 120 and 140. In addition, the displacement of the second vane 52 can be suitably transmitted to the first vane 51.

  Further, in this compressor, in the first communication hole 61, the first transmission pin 110 and the second transmission pin 120 are arranged to face each other with a gap S1. In the second communication hole 63, the first transmission pin 130 and the second transmission pin 140 are arranged facing each other with a gap S2. For these reasons, in this compressor, when the first vane 51 protrudes and retracts with respect to the first vane groove 41A and the second vane 52 protrudes and retracts with respect to the second vane groove 41B, the first and second coil springs 91, By the expansion and contraction of 93, the fluctuation in the distance between the first vane 51 and the second vane 52 can be absorbed. For this reason, in this compressor, the first and second transmission pins 110 and 120 do not collide with each other and the first and second transmission pins 130 and 140 do not collide with each other during operation. Accordingly, the first vane 51 and the second vane 52 can be suitably pressed against the inner peripheral surface 31S of the cylinder chamber 31, and the first and second transmission pins 110 to 140 prevent the rotor 41 from rotating during operation. There is no.

  Here, as shown in FIG. 4, in this compressor, in the state where the first vane 51 protrudes from the first vane groove 41A and the state where the second vane 52 protrudes from the second vane groove 41B, One end side of the coil springs 91 and 93 enters the first vane groove 41A, and the other end side enters the second vane groove 41B. On the other hand, as shown in FIG. 2, in a state where the first vane 51 is completely buried in the first vane groove 41A, one end portion side of the first coil spring 91 stops in the first communication hole 61, and the second coil spring. One end portion side of 93 also stops in the second communication hole 63. Although not shown, when the second vane 52 is completely buried in the second vane groove 41 </ b> B, the other end side of the first coil spring 91 stops in the first communication hole 61, and the second coil spring 93 The end portion also stops in the second communication hole 63.

  In this compressor, the first transmission pins 110 and 130 are assembled to the first vane 51 as described above, so that the first flange portions 113 and 133 come into contact with the edge portions 51E and 51F, respectively. Similarly, when the second transmission pins 120 and 140 are assembled to the second vane 52, the second flange portions 123 and 143 come into contact with the edge portions 52E and 52F, respectively. In addition, a first coil spring 91 is provided in a compressed state between the first transmission pin 110 and the second transmission pin 120, and a second coil spring is provided between the first transmission pin 130 and the second transmission pin 140. A coil spring 93 is provided in a compressed state. Thus, in this compressor, the first and second transmission pins 110 to 140 are not separated from the bottom surfaces 51S and 52S of the first and second vanes 51 and 52, respectively. Movement of the rotor 41 in the radially outward direction is restricted. Thereby, in this compressor, in operation, in each of the first transmission pins 110 and 130, the first loosely fitting portions 111 and 131 collide with the bottom surfaces of the recessed portions 51H and 51J, respectively, to generate a hitting sound. There is no. Further, in each of the second transmission pins 120 and 140, the second loosely fitting portions 121 and 141 do not collide with the bottom surfaces of the recess portions 52H and 52J, respectively, to generate a hitting sound.

  Further, since the first and second transmission pins 110 to 140 are not separated from the bottom surfaces 51S and 52S of the first and second vanes 51 and 52, respectively, the first end surface 113T of the first flange portion 113 is By being pressed and supported by the one coil spring 91, the state of surface contact with the edge 51E is maintained. The first end surface 133T of the first flange portion 133 is also pressed and supported by the second coil spring 93, so that the surface contact with the edge portion 51J is maintained. For these reasons, in this compressor, the first flange portions 113 and 133 do not collide with the edge portions 51E and 51F, that is, the bottom surface 51S of the first vane 51 during operation, so that no hitting sound is generated. The same applies to the second flange portions 123 and 143.

  In this compressor, the first coil spring 91 is connected to the first vane 51 and the second vane 52 via the first flange portion 113 of the first transmission pin 110 and the second flange portion 123 of the second transmission pin 120. Are supported in a direction away from each other. Further, the second coil spring 93 separates the first vane 51 and the second vane 52 from each other via the first flange portion 133 of the first transmission pin 130 and the second flange portion 143 of the second transmission pin 140. Supports pressing.

  Here, the first end surface 113T of the first flange portion 113 is in surface contact with the edge portion 51E, and the first end surface 133T of the first flange portion 133 is also in surface contact with the edge portion 51F. . Further, the first end surface 123T of the second flange portion 123 is in surface contact with the edge portion 52E, and the first end surface 143T of the second flange portion 143 is also in surface contact with the edge portion 52F. For this reason, for example, in comparison with the case where the first and second coil springs 91 and 93 are in direct contact with both the first vane 51 and the second vane 52 to press and support them, The two coil springs 91 and 93 are easy to stably bias the first vane 51 and the second vane. Thereby, in this compressor, while being able to make the 1st vane 51 appear stably with respect to the 1st vane groove 41A, it is possible to make the 2nd vane 52 appear stably with respect to the 2nd vane groove 41B. Is possible. Therefore, in this compressor, the first vane 51 and the second vane 52 can be suitably pressed against the inner peripheral surface 31S of the cylinder chamber 31, and the refrigerant gas can be hardly leaked from the compression chambers 30A and 30B. It has become.

  Therefore, the compressor of Example 1 can exhibit high silence.

  Further, in this compressor, the first transmission pins 110 and 130 are assembled to the first vane 51 by loosely fitting the first loose fitting portions 111 and 131 into the recessed portions 51H and 51J, respectively. Further, the second transmission pins 120 and 140 are assembled to the second vane 52 by loosely fitting the second loose fitting portions 121 and 141 into the recess portions 52H and 52J, respectively. For this reason, for example, the first transmission pins 110 and 130 are press-fitted into the recesses 51H and 51J, and the second transmission pins 120 and 140 are pressed into the recesses 52H and 52J. The first transmission pins 110 and 130 can be easily assembled, and the second transmission pins 120 and 140 can be easily assembled to the second vane 52. Moreover, in this compressor, the deformation | transformation of the 1st, 2nd vanes 51 and 52 by press-fitting each 1st and 2nd transmission pins 110-140 to the hollow parts 51H, 51J, 52H, and 52J, respectively does not arise. For these reasons, the compressor can be easily manufactured.

  Furthermore, in this compressor, since each of the first and second loose fitting portions 111, 121, 131, 141 is configured to loosely fit into the hollow portions 51H, 51J, 52H, 52J, compared to the case of press-fitting, The dimensional accuracy of each of the first and second loose fitting portions 111, 121, 131, 141 and the recessed portions 51H, 51J, 52H, 52J can be relaxed. For this reason, in this compressor, it is possible to increase the degree of freedom in designing the first and second transmission pins 100 to 140 and the first and second vanes 51 and 52.

  The first transmission pin 110 has a first taper surface 115A, and the first transmission pin 130 has a first taper surface 135A. Similarly, the second transmission pin 120 is formed with a second tapered surface 125A, and the second transmission pin 140 is formed with a second tapered surface 145A. For this reason, in this compressor, it can suppress that the 1st coil spring 91 is pinched | interposed between the 1st axial part 115 of the 1st transmission pin 110, and the 2nd axial part 125 of the 2nd transmission pin 120. . Further, the second coil spring 93 can be prevented from being sandwiched between the first shaft portion 135 of the first transmission pin 130 and the second shaft portion 145 of the second transmission pin 140. For these reasons, the first and second coil springs 91 and 93 can suitably bias the first vane 51 and the second vane 52.

  Further, in this compressor, the first flange portions 113 and 133 are formed with a smaller diameter than the first and second communication holes 61 and 63, and the second flange portions 123 and 143 are formed in the first and second communication holes. The diameter is smaller than 61 and 63. Therefore, the first and second flange portions 113 and 123 can be prevented from contacting the inner wall of the first communication hole 61 during operation, and the first and second flange portions 133 and 143 are in contact with the inner wall of the second communication hole 63. Can be prevented. Also in this point, in this compressor, it is possible to make the first vane 51 appear and disappear appropriately with respect to the first vane groove 41A, and the second vane 52 is preferable with respect to the second vane groove 41B. It is possible to indulge in.

  Further, in this compressor, the first flange portion 113 is formed on the entire circumference of the first transmission pin 110, and the second flange portion 123 is formed on the entire circumference of the second transmission pin 120. For this reason, in this compressor, formation of the 1st and 2nd flange parts 113 and 123 and by extension, formation of the 1st and 2nd transmission pins 110 and 120 are easy. The same applies to the first and second transmission pins 130 and 140.

  Further, in this compressor, the high-pressure refrigerant in the discharge chamber 9A passes through the first and second passages 5E and 5F, the oil supply chamber 310, the first and second communication passages 5G and 5H, and the first and second communication holes 61 and 63. Gas is supplied to the first and second back pressure chambers 49A and 49B. Thereby, in this compressor, in addition to pressing the first and second vanes 51 and 52 against the inner peripheral surface 31S of the cylinder chamber 31 by the first and second coil springs 91 and 93 being pressed and supported, The first and second vanes 51 and 52 can be pressed against the inner peripheral surface 31S of the cylinder chamber 31 also by the back pressure of the pressure chamber 49A and the second back pressure chamber 49B. For this reason, in this compressor, the first vane 51 and the second vane 52 can be suitably pressed against the inner peripheral surface 31S of the cylinder chamber 31, and the refrigerant gas hardly leaks from the compression chambers 30A and 30B.

  Here, in this compressor, the first and second communication holes 61 and 63 are formed so as to penetrate the rotating shaft 19 and communicate with the first communication path 5G. Thereby, the 1st, 2nd communicating holes 61 and 63 can be functioned as a back pressure channel, and it becomes possible to simplify the composition of a back pressure channel.

  In this compressor, the first vane 51 and the second vane 52 have the same shape, and the first and second transmission pins 110 to 140 have the same shape. For this reason, the first vane 51 and the second vane 52 can be shared, and the first and second transmission pins 110 to 140 can be shared. For this reason, in this compressor, manufacture can be facilitated and manufacturing cost can be reduced.

(Example 2)
As shown in FIG. 6, in the compressor of the second embodiment, the communication path 5G in the compressor of the first embodiment is eliminated. On the rear surface of the first side plate 4, an annular groove 4C is formed in an annular shape around the rotation axis X1. On the front surface of the second side plate 5, an annular groove 5 </ b> C that makes a pair with the annular groove 4 </ b> C in the front-rear direction is recessed in an annular shape around the rotation axis X <b> 1. Further, the second side plate 5 is formed with a second passage 305F that communicates the upper end of the first passage 5E with the annular groove 5C. The second passage 305 </ b> F extends from the rear surface of the second side plate 5 toward the front and then extends toward the upper front side. 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.

  In the compressor according to the second embodiment, the lubricating oil stored in the discharge chamber 9A is supplied to the first back pressure chamber 49A and the second back pressure chamber 49B via the first and second passages 5E and 305F and the annular groove 5C. Is done. Further, the first back pressure chamber 49A and the second back pressure chamber 49B communicate with each other through the annular groove 4C, so that the pressure difference between the first back pressure chamber 49A and the second back pressure chamber 49B is adjusted. The compressor of Example 2 which is the said structure can also show | play the effect similar to the compressor of Example 1. FIG.

(Example 3)
As shown in FIG. 7, in the compressor of the third embodiment, the first transmission pins 310 and 330 are employed instead of the first transmission pins 110 and 130 of the first embodiment, and the second transmission pins 120 and 140 are replaced. The second transmission pins 320 and 340 are employed. These first and second transmission pins 310 to 340 also have the same shape.

  In the 1st communicating hole 61, the 1st transmission pin 310 and the 2nd transmission pin 320 are arrange | positioned so that the edge part which becomes the rotating shaft center X1 side may have a clearance gap S1 between both, and may face each other. Yes. Similarly, in the second communication hole 63, the first transmission pin 330 and the second transmission pin 340 face each other while the end on the rotation axis X1 side has a gap S2 between them. Has been placed.

  The first transmission pin 310 has a first loose fitting portion 311 and a first cylindrical portion 313. The first loosely fitting portion 311 has the same configuration as the first loosely fitting portion 111 of the first embodiment. The first cylindrical portion 313 has a bottomed cylindrical shape, and extends in the radial direction of the rotor 41 in the direction opposite to the first loosely fitting portion 311. The first cylindrical portion 313 is formed to have a larger diameter than the first loose fitting portion 311 and a smaller diameter than the first communication hole 61. The first cylindrical portion 313 is formed with a first end face 313T located on the first vane 51 side and a second end face 313S located on the opposite side of the first end face 313T. These first and second end faces 313T and 313S are both formed flat.

  The second transmission pin 320 has a second loose fitting part 321 and a second cylindrical part 323. The second loose fitting part 321 has the same configuration as the second loose fitting part 121 of the first embodiment. The second cylindrical portion 323 also has a bottomed cylindrical shape, and extends in the radial direction of the rotor 41 in the direction opposite to the second loosely fitting portion 321. The second cylindrical portion 323 is formed with a larger diameter than the second loose fitting portion 321 and a smaller diameter than the first communication hole 61. The second cylindrical portion 323 is formed with a first end face 323T located on the second vane 52 side and a second end face 323S located on the opposite side of the first end face 323T. The first and second end faces 323T and 323S are also formed flat.

  The first transmission pin 330 has a first loose fitting portion 331 and a first cylindrical portion 333. The first cylindrical portion 333 has a first end surface 333T and a second end surface 333S. The second transmission pin 340 includes a second loose fitting portion 341 and a second cylindrical portion 343. The second cylindrical portion 343 is formed with a first end surface 343T and a second end surface 343S. The configuration of the first transmission pin 330 is the same as that of the first transmission pin 310, and the configuration of the second transmission pin 340 is the same as that of the second transmission pin 320. For these reasons, detailed description of each configuration of the first and second transmission pins 330 and 340 is omitted.

  The first transmission pins 310 and 330 are assembled while being positioned on the first vane 51 by loosely fitting the first loose fitting portions 311 and 331 to the recess portions 51H and 51J of the first vane 51, respectively. Accordingly, the first end surface 313T of the first cylindrical portion 313 is in surface contact with the edge portion 51E of the recessed portion 51H, and the first end surface 333T of the first cylindrical portion 333 is in surface contact with the edge portion 51F of the recessed portion 51J. .

  Each of the second transmission pins 320 and 340 is assembled while being positioned on the second vane 52 by loosely fitting the second loose fitting portions 321 and 341 into the recesses 52H and 52J of the second vane 52, respectively. Accordingly, the first end surface 323T of the second cylindrical portion 323 is in surface contact with the edge portion 52E of the recessed portion 52H, and the first end surface 343T of the second cylindrical portion 343 is in surface contact with the edge portion 52F of the recessed portion 52J. .

  The first coil spring 91 is accommodated in the first cylindrical portion 313 of the first transmission pin 310 and in the second cylindrical portion 323 of the second transmission pin 320. One end of the first coil spring 91 is in contact with the second end surface 313S of the first cylindrical portion 313, and the other end is in contact with the second end surface 323S of the second cylindrical portion 323. Accordingly, the first coil spring 91 is provided in a compressed state between the first transmission pin 310 and the second transmission pin 320, and the first vane 51 and the first transmission pin 310 and 320 are connected to each other. The two vanes 52 are urged away from each other.

  The second coil spring 93 is accommodated in the first cylindrical portion 333 of the first transmission pin 330 and in the second cylindrical portion 343 of the second transmission pin 340. One end of the second coil spring 93 is in contact with the second end surface 333S of the first cylindrical portion 333, and the other end is in contact with the second end surface 343S of the second cylindrical portion 343. Accordingly, the second coil spring 93 is provided in a compressed state between the first transmission pin 330 and the second transmission pin 340, and the first vane 51 and the first transmission pin 330 are connected via the first and second transmission pins 330 and 340. The two vanes 52 are urged away from each other. Other configurations of the compressor of the third embodiment are the same as those of the compressor of the first embodiment.

  In this compressor, the displacement of the first vane 51 is transmitted to the second vane 52 through the first and second transmission pins 310 to 340 and the first and second coil springs 91 and 93, and the displacement of the second vane 52 is also transmitted. Is transmitted to the first vane 51. Also in this compressor, the first end face 313T of the first cylindrical portion 313 is in surface contact with the edge portion 51E in the first transmission pin 310 by being pressed and supported by the first coil spring 91. Similarly, in the second transmission pin 320, the first end surface 323T of the second cylindrical portion 323 is in surface contact with the edge portion 52E. Thus, the first transmission pin 310 is not separated from the bottom surface 51S of the first vane 51, and the second transmission pin 320 is not separated from the bottom surface 52S of the second vane 52. The same applies to the first and second transmission pins 330 and 340 biased by the second coil spring 93. Thus, this compressor can achieve the same effects as the compressor of the first embodiment.

Example 4
As shown in FIG. 8, in the compressor of Example 4, the first tapered pins 115A and 135A are not formed on the first transmission pins 110 and 130, respectively. Further, the second tapered pins 125A and 145A are not formed on the second transmission pins 120 and 140, respectively. Further, in this compressor, instead of the first and second coil springs 91 and 93, first and second rubber blocks 491 and 493 are employed. These first and second rubber blocks 491 and 493 correspond to the elastic member in the present invention.

  The first rubber block 491 is disposed in the first communication hole 61 and is movable in the first communication hole 61. The first rubber block 491 is located between the first shaft portion 115 of the first transmission pin 110 and the second shaft portion 125 of the second transmission pin 120. The first rubber block 491 is provided with a first engagement hole 491H and a second engagement hole 491J that extend opposite to each other.

  The second rubber block 493 is disposed in the second communication hole 63 and can move in the second communication hole 63. The second rubber block 493 is located between the first shaft portion 135 of the first transmission pin 130 and the second shaft portion 145 of the second transmission pin 140. The second rubber block 493 is also provided with a first engagement hole 493H and a second engagement hole 493J that extend opposite to each other.

  In the first transmission pin 110, the first loose fitting portion 111 is loosely fitted in the hollow portion 51 </ b> H of the first vane 51, and the first shaft portion 115 is inserted into the first engagement hole 491 </ b> H of the first rubber block 491. Has been. At this time, the tip of the first shaft portion 115 is in contact with the bottom surface 491S of the first engagement hole 491H. The second transmission pin 120 has the second loosely fitting portion 121 loosely fitted in the hollow portion 52H of the second vane 51 and the second shaft portion 125 having the second engagement hole 491J of the first rubber block 491. Has been inserted. At this time, the tip of the second shaft portion 125 is also in contact with the bottom surface 491T of the second engagement hole 491J.

  Similarly to the first transmission pin 110, the first shaft 135 is inserted into the first engagement hole 493 </ b> H of the second rubber block 493 for the first transmission pin 130. As for the second transmission pin 140, similarly to the second transmission pin 120, the second shaft portion 145 is inserted into the second engagement hole 493 </ b> J of the second rubber block 493. The tip of the first shaft portion 135 is in contact with the bottom surface 493S of the first engagement hole 493H, and the tip of the second shaft portion 145 is in contact with the bottom surface 493T of the second engagement hole 493J. It is in a state. Thus, the first and second rubber blocks 491 and 493 bias the first vane 51 and the second vane 52 away from each other via the first and second transmission pins 110 to 140.

  Here, the first rubber block 491 is disposed between the first transmission pin 110 and the second transmission pin 120 in a compressed state. The first transmission pin 110 and the second transmission pin 120 face each other with a gap S1 corresponding to the distance between the bottom surface of the first engagement hole 491H and the bottom surface of the second engagement hole 491J. Be placed. The same applies to the second rubber block 493, and the first transmission pin 130 and the second transmission pin 140 are arranged facing each other with a gap S2. Other configurations of the compressor of the fourth embodiment are the same as those of the compressors of the first and second embodiments.

  In this compressor, the displacement of the first vane 51 is transmitted to the second vane 52 through the first and second transmission pins 110 to 140 and the first and second rubber blocks 491 and 493, and the displacement of the second vane 52 is also transmitted. Is transmitted to the first vane 51. Also in this compressor, the first transmission pins 110 and 130 are supported by the first and second rubber blocks 491 and 493 so that the first transmission pins 110 and 130 are the bottom surface 51S of the first vane 51 as in the compressor of the first embodiment. The second transmission pins 120 and 140 are not separated from the bottom surface 52S of the second vane 52. Thus, this compressor can achieve the same effects as the compressor of the first embodiment.

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

  For example, in the first embodiment, between the first vane 51 and the second vane 52, two first transmission pins 110 and 130, two second transmission pins 120 and 140, and first and second coil springs 91 are provided. , 93 are provided. However, the present invention is not limited to this, and only the first transmission pin 110, the second transmission pin 120, and the first coil spring 91 may be provided between the first vane 51 and the second vane 52. Moreover, it is good also as a structure which provides 3 or more 1st transmission pins, 3 or more 2nd transmission pins, and 3 or more coil springs. The same applies to Examples 2 to 4.

  Further, in the first embodiment, the first transmission pins 110 and 130 are not separated from the first vane 51 by press-fitting the first transmission pins 110 and 130 into the recesses 51H and 51J of the first vane 51, respectively. It is also good. Further, the second transmission pins 120 and 140 may not be separated from the second vane 52 by press-fitting the second transmission pins 120 and 140 into the recesses 52H and 51J of the second vane 52, respectively. The same applies to Examples 2 to 4.

  In Examples 1, 2, and 4, the first flange portion 113 is in surface contact with the edge portion 51E of the recess portion 51H, and the second flange portion 123 is in surface contact with the edge portion 52E of the recess portion 52H. . However, the present invention is not limited thereto, and the first flange portion 113 abuts on the bottom surface 51S of the first vane 51 at a place other than the edge portion 51E, and the second flange portion 113 is located at a place other than the edge portion 52E. It is good also as a structure contact | abutted to the bottom face 52S of this. The same applies to the first and second flange portions 133 and 143. The same applies to the first and second cylindrical portions 313, 323, 333, and 343 of the third embodiment.

  Further, in the first to third embodiments, the first coil spring 91 may be divided into two coil springs. The same applies to the second coil spring 93.

  Moreover, you may comprise a compressor by combining suitably each structure of Examples 1-4.

  The present invention is applicable to an air conditioner such as a vehicle.

31 ... Cylinder chamber 1, 4, 7, 5, 9 ... Housing (1 ... Motor housing, 4 ... First side plate, 7 ... Cylinder block, 5 ... Second side plate, 9 ... Cover)
X1 ... Rotational axis 41 ... Rotor 30A, 30B ... Compression chamber 41A ... First vane groove 41B ... Second vane groove 51 ... First vane 51S ... Bottom surface of first vane 52 ... Second vane 52S ... Bottom surface of second vane 61, 63 ... communication hole (61 ... first communication hole, 63 ... second communication hole)
91, 93 ... coil spring (91 ... first coil spring, 93 ... second coil spring)
491, 493 ... elastic members (491 ... first rubber block, 493 ... second rubber block)
51H, 51J ... 1st hollow part 52H, 52J ... 2nd hollow part 51E, 51F, 52E, 52F ... Edge part 110, 130, 310, 330 ... 1st transmission pin 120, 140, 320, 340 ... 2nd transmission pin 111, 131, 311, 331 ... first loose fitting portion 113, 133 ... first flange portion 115, 135 ... first shaft portion S1, S2 ... gap 121, 141, 321, 341 ... second loose fitting portion 123, 143 ... 2nd flange part 125, 145 ... 2nd axial part 115A, 135A ... 1st taper surface (1st diameter reduction site | part)
125A, 145A ... 2nd taper surface (2nd diameter reduction part)
9A ... Discharge chamber 49A ... First back pressure chamber 49B ... Second back pressure chamber 19 ... Rotating shaft 5E, 5F, 310, 5G, 5H, 61, 63 ... Back pressure flow path (5E ... First passage, 5F ... Second (Passage, 310 ... refueling chamber, 5G ... first communication passage, 5H ... second communication passage, 61 ... first communication hole, 63 ... second communication hole)

Claims (9)

A housing in which a cylinder chamber is formed;
A rotor provided in the cylinder chamber so as to be rotatable around a rotation axis, and formed with an even number of vane grooves;
A vane provided so as to be able to appear and disappear in each of the vane grooves,
A vane type compression in which a compression chamber is formed by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and the two vanes adjacent to each other around the rotation axis. In the machine
Each of the vane grooves includes a first vane groove and a second vane groove extending in the extending direction of the first vane groove.
Each vane includes a first vane provided in the first vane groove and a second vane provided in the second vane groove,
The rotor is formed with a communication hole that communicates the first vane groove and the second vane groove,
The communication hole includes a first transmission pin, a second transmission pin, and an elastic member that urges the first vane and the second vane away from each other via the first transmission pin and the second transmission pin. And
The first transmission pin is pressed and supported against the first vane,
The vane-type compression, wherein the second transmission pin is pressed and supported against the second vane and extends toward the first vane so as to face the first transmission pin with a gap. Machine.   The vane compressor according to claim 1, wherein the elastic member is provided in a compressed state. The second vane protrudes from the second vane groove by a pressing force in which the first vane is buried in the first vane groove,
3. The vane compressor according to claim 1, wherein the first vane protrudes from the first vane groove by a pressing force with which the second vane is buried in the second vane groove. The first vane is formed with a first recess that is recessed from the bottom surface on the rotational axis side,
The second vane is formed with a second recess that is recessed from the bottom surface on the rotational axis side,
The first transmission pin includes a first loose-fit portion loosely fitted in the first recess, a first shaft portion extending in a direction opposite to the first loose-fit portion, the first loose-fit portion, and the A first flange portion formed between the first shaft portion and the bottom surface in which the first recess portion is recessed,
The second transmission pin includes a second loosely fitted portion loosely fitted in the second recessed portion, a second shaft portion extending in a direction opposite to the second loosely fitted portion, the second loosely fitted portion, and the A second flange portion formed between the second shaft portion and abutting against the bottom surface in which the second recess portion is recessed,
The communication hole communicates the first depression and the second depression,
The elastic member is a coil spring supported by the first shaft portion and the second shaft portion, one end of which is in contact with the first flange portion, and the other end of which is in contact with the second flange portion. The vane type compressor according to any one of claims 1 to 3. The first shaft portion is formed with a first reduced diameter portion that is reduced in diameter toward the second transmission pin,
5. The vane compressor according to claim 4, wherein the second shaft portion is formed with a second reduced diameter portion that decreases in diameter toward the first transmission pin.   The vane compressor according to claim 4 or 5, wherein the first flange portion and the second flange portion are smaller in diameter than the communication hole. A discharge chamber is formed in the housing,
A space between the bottom surface of the first vane and the bottom surface of the first vane groove is a first back pressure chamber,
A space between the bottom surface of the second vane and the bottom surface of the second vane groove is a second back pressure chamber,
The rotor is press-fitted with a rotation shaft that extends in the direction of the rotation axis and is rotatably supported by the housing,
The back shaft which connects the said discharge chamber, the said 1st back pressure chamber, and the said 2nd back pressure chamber in the said rotating shaft and the said rotor is formed in any one of Claim 1 thru | or 6. Vane type compressor.   The vane compressor according to claim 7, wherein the communication hole penetrates the rotating shaft and is a part of the back pressure flow path. The first vane and the second vane have the same shape,
The vane type compressor according to any one of claims 1 to 8, wherein the first transmission pin and the second transmission pin have the same shape.

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