JP2016125402A - Vane type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane type compressor capable of achieving improved compressing performance.SOLUTION: Storage parts 42, 43 are formed in at least one end face of a rotor 41. The storage parts 42, 43 store transmission members 110, 120 to be guided in a reciprocative manner in the ejecting/retracting directions of the first and second vanes 51, 52, respectively, the former including energizing means 115A having a first thrust part 110A on one end side where it abuts on a first vane 51 and a second thrust part 110B on the other end side where it abuts on a second vane 52, for energizing the first thrust part 110A and the second thrust part 110B to be isolated from each other in the ejecting/retracting directions. The transmission member 110 ejects the second vane 52 from a second vane groove 41B when the first vane 51 is pushed against an inner peripheral face 31S of a cylinder chamber 31 and stored in a first vane groove 41A, and ejects the first vane 51 from the first vane groove 41A when the second vane 52 is likewise stored in the second vane groove 41B.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a vane type compressor.

  Patent Documents 1 and 2 disclose conventional vane type compressors or pumps. These vane type compressors or pumps are provided with a housing, a rotating shaft, a rotor, and four vanes. A cylinder chamber is formed in the housing. The rotating shaft is rotatably provided on the housing. The rotor is rotatably provided with the rotation shaft in the cylinder chamber. Four vane grooves are formed in the rotor. Each vane is provided in the vane groove so that it can appear and disappear.

  More specifically, in Patent Documents 1 and 2, two vane grooves that form a pair with the rotation axis of the rotation shaft interposed therebetween are referred to as a first vane groove and a second vane groove. A vane provided in the first vane groove so as to be able to appear and disappear is referred to as a first vane. A vane provided in the second vane groove so as to be able to appear and disappear is referred to as a second vane. The other pair of vane grooves and the pair of vanes provided in the vane grooves so as to be capable of appearing and retracting are the same as the first and second vane grooves and the first and second vanes, and thus the description thereof is omitted.

  According to FIG. 2 of Patent Document 1, FIG. 8 of Patent Document 2, and the like, the cross-sectional shape of the outer peripheral surface of the rotor is a perfect circle centered on the rotation axis. The cross-sectional shape of the inner peripheral surface of the cylinder chamber is such that the first end portion on the inner peripheral side of the first vane and the second end portion on the inner peripheral side of the second vane are substantially constant regardless of the rotation of the rotor. It is set to be separated.

  In the pump disclosed in Patent Document 1, an operating rod is provided between the first vane and the second vane. The operating rod is inserted into a through hole intersecting the rotation axis so as to be reciprocally movable. One end of the operating rod is in contact with the first end of the first vane via a coil spring. The other end of the operating rod is in contact with the second end of the second vane via a coil spring.

  In this pump, the displacement when the first vane is buried is transmitted to the second vane by the operating rod, the displacement when the second vane is buried is transmitted to the first vane, and the first and second vanes are transferred to the first vane. Make it appear and disappear with respect to the 1 and 2 vane grooves. In short, in this pump, pressure loss is suppressed by adopting a configuration in which the first and second vanes protrude and retract with respect to the first and second vane grooves without using back pressure.

  In the compressor disclosed in Patent Document 2, the first vane and the second vane are one member connected by a connecting piece. The connecting piece has an annular portion that bypasses the rotating shaft. Sliders that are in sliding contact with the connecting pieces are supported on the front and rear surfaces of the housing. The slider can rotate at a position eccentric from the rotational axis. The rotor is formed with a housing portion that houses the connecting piece and the slider.

  In this compressor, with the rotation of the rotor, the connecting piece slides into contact with the slider, so that the first and second vanes appear and disappear with respect to the first and second vane grooves. At this time, the connecting piece holds the first and second vanes on the same plane. In short, this compressor employs a configuration in which the first and second vanes are projected and retracted with respect to the first and second vane grooves without using back pressure, thereby suppressing pressure loss and thus improving compression performance. I am trying.

Japanese Utility Model Publication No. 49-26104 Japanese Patent Application Laid-Open No. 60-147591

  However, the vane type compressor or pump disclosed in Patent Literatures 1 and 2 employs a special arrangement in which the first vane groove, the second vane groove, and the rotating shaft are aligned. In this regard, many vane compressors employ a configuration in which the first vane groove and the second vane groove extend in parallel to opposite directions in the radial direction of the rotor and the extending direction is deviated. Therefore, it is difficult to apply the operating rods related to the pump disclosed in Patent Document 1 and the connecting pieces related to the compressor disclosed in Patent Document 2, and the compression performance is improved by using these operating rods and connecting pieces. There is a problem that it is difficult to plan.

  This invention is made | formed in view of the said conventional condition, Comprising: It is set as the problem which should be solved to provide the vane type compressor which can implement | achieve the improvement of compression performance.

The vane type compressor of the present invention includes a housing in which a discharge chamber and a cylinder chamber are formed,
A rotating shaft rotatably provided in the housing;
A rotor provided in the cylinder chamber so as to be rotatable together with the rotating shaft, and formed with a first vane groove and a second vane groove;
A first vane provided in the first vane groove so as to be able to appear and disappear;
A second vane provided in the second vane groove so as to be able to appear and disappear,
A vane type compressor in which a compression chamber is formed by a front surface of the cylinder chamber, an inner peripheral surface of the cylinder chamber, a rear surface of the cylinder chamber, an outer peripheral surface of the rotor, the first vane and the second vane;
The first vane groove and the second vane groove extend in parallel to opposite directions in the radial direction of the rotor, the extending direction is shifted, and are symmetric in the rotation axis of the rotation shaft,
On at least one end surface of the rotor, a housing portion that is recessed while the rotating shaft is contained is formed,
The accommodating portion is in contact with the first vane at a first pressing portion provided on one end side, and is in contact with the second vane at a second pressing portion provided on the other end side. And a transmission member guided so as to reciprocate in the protruding and retracting directions of the first vane and the second vane. Has been
The transmission member causes the second vane to protrude from the second vane groove when the first vane is pressed against the inner peripheral surface of the cylinder chamber and accommodated in the first vane groove, and the second vane groove protrudes from the second vane groove. When the vane is pressed against the inner peripheral surface of the cylinder chamber and accommodated in the second vane groove, the first vane and the second vane are protruded from the first vane groove. It is configured to transmit movement.

  In the vane type compressor of the present invention, the first vane groove and the second vane groove extend in parallel to opposite directions in the radial direction of the rotor, the extending directions are shifted, and the rotational axis of the rotating shaft is symmetric. The first vane is pressed against the inner peripheral surface of the cylinder chamber by the transmission member including the first pressing portion, the second pressing portion, and the urging means, which is the above-described configuration, so that the first vane is in the first vane groove. When received, the second vane protrudes from the second vane groove, and when the second vane is pressed against the inner peripheral surface of the cylinder chamber and received in the second vane groove, the first vane protrudes from the first vane groove. Can be made. For this reason, in this compressor, even if back pressure is not used or back pressure is weakened, the first and second vanes can be moved in and out of the first and second vane grooves, so that pressure loss is suppressed. it can. In particular, in this compressor, since it is difficult for rattling to occur between the first vane and the first pressing part or between the second vane and the second pressing part, the pressure loss can be reliably suppressed by the urging means. .

  Therefore, in the vane type compressor of the present invention, improvement in compression performance can be realized. Further, in this compressor, chattering of each vane is suppressed by the biasing means because it is difficult for rattling to occur between the first vane and the first pressing portion or between the second vane and the second pressing portion. can do.

  It is desirable that the transmission member has a substantially rectangular shape that is long in the protruding and retracting direction when viewed from the rotational axis direction. And it is desirable for the 1st press part to contact | abut to a 1st vane in the corner | angular part side of the outer surface of the short side facing the 1st vane in a transmission member. Moreover, it is desirable that the second pressing portion abuts on the second vane on the corner portion side of the outer surface on the short side facing the second vane in the transmission member. In this case, while maintaining simplification and miniaturization of the shape of the transmission member, the state in which the transmission member is in contact with the first vane by the first pressing portion and is in contact with the second vane by the second pressing portion is reliably maintained. it can.

  It is desirable that the transmission member has a substantially rectangular shape that is long in the protruding and retracting direction when viewed from the rotational axis direction. The pair of outer surfaces on the long side of the transmission member are preferably slidably contacted with the housing portion, so that the transmission member is guided so as to reciprocate in the protruding and retracting direction. In this case, the pair of outer surfaces on the long side suppresses the inclination of the transmission member with respect to the protruding and retracting direction, so that the transmission member comes into contact with the first vane by the first pressing portion and hits the second vane by the second pressing portion. The contact state can be reliably maintained.

  It is desirable that a hole through which the rotating shaft is inserted is provided in the transmission member. And it is desirable for the hole to be made into an ellipse shape long in the direction of appearance. In this case, the transmission member can smoothly reciprocate in the housing portion without interfering with the rotation shaft by the hole.

  It is desirable that the housing portion includes a first housing portion formed on one end surface of the rotor and a second housing portion formed on the other end surface of the rotor. And it is desirable for a transmission member to consist of a 1st transmission member accommodated in a 1st accommodating part, and a 2nd transmission member accommodated in a 2nd accommodating part. In this case, the first and second transmission members press the one end side and the other end side in the rotational axis direction of the first and second vanes, so the first and second vanes are not easily twisted in the first and second vane grooves. Become. For this reason, in this compressor, the 1st and 2nd vanes can be made to appear and disappear smoothly with respect to the 1st and 2nd vane grooves.

  It is desirable that a space between the bottom surface of the first vane and the first vane groove is a first back pressure chamber. It is desirable that a space between the bottom surface of the second vane and the second vane groove is a second back pressure chamber. And it is desirable for the rotating shaft and the rotor to be formed with a back pressure flow path that communicates the discharge chamber with the first back pressure chamber and the second back pressure chamber. In this case, the first and second vanes can be pressed against the inner peripheral surface of the cylinder chamber by the back pressure of the first and second back pressure chambers in addition to the pressing of the first and second vanes by the transmission member. At this time, the back pressure can be made weaker than before by the transmission member. For this reason, in this compressor, compression performance can be improved while chattering of each vane is suppressed.

  In the vane type compressor of the present invention, the compression performance can be improved.

FIG. 1 is a cross-sectional view of the vane type compressor according to the first embodiment. FIG. 2 is a cross-sectional view showing the AA cross section of FIG. 1 according to the vane type compressor of the first embodiment. FIG. 3 is a cross-sectional view of the vane type compressor according to the first embodiment, showing a cross section taken along the line BB of FIG. FIG. 4 is a cross-sectional view similar to FIG. 3 according to the vane type compressor of the first embodiment. FIG. 5 is a schematic diagram illustrating the first distance between the first and second end portions of the first and second vanes according to the vane type compressor of the first embodiment. FIG. 6 is a perspective view illustrating the relative relationship between the first and second vanes and the transmission member in the vane type compressor according to the first embodiment. FIG. 7 is a partial cross-sectional view of the vane type compressor according to the second embodiment. FIG. 8 is a schematic side view illustrating a rotor, first and second vanes, a transmission member, and the like according to the vane type compressor of the third embodiment. FIG. 9 is a schematic side view illustrating a rotor, first and second vanes, a transmission member, and the like according to the vane type compressor of the fourth embodiment. FIG. 10 is a schematic side view illustrating a rotor, first and second vanes, a transmission member, and the like according to the vane type compressor of the fifth embodiment. FIG. 11 is a schematic side view illustrating a rotor, first and second vanes, a transmission member, and the like according to the vane type compressor of the sixth embodiment. FIG. 12 is a schematic side view illustrating a rotor, first and second vanes, a transmission member, and the like according to the vane type compressor of the seventh embodiment. FIG. 13 is a schematic side view illustrating a rotor, first and second vanes, a transmission member, and the like according to the vane type compressor of the eighth embodiment.

  Hereinafter, Embodiments 1 to 8 embodying the present invention will be described 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 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. A bulging portion 1E is formed on the upper portion of the cylindrical portion 1D. The bulging portion 1E bulges outward in the radial direction of the rotation axis X1. A suction port 1 </ b> F that communicates the outside with the motor chamber 1 </ b> C is formed in a portion located on the front side and the lower side of the cylindrical portion 1 </ b> D. An evaporator of a vehicle air conditioner is connected to the suction port 1F by a pipe (not shown).

  The motor mechanism 3 includes a stator 15 and a motor rotor 17 in the motor chamber 1C. The stator 15 is fixed to the inner peripheral surface of the cylindrical portion 1 </ b> D of the motor housing 1. A lead wire 16 </ b> C and a cluster block 16 are accommodated in the bulging portion 1 </ b> E of the motor housing 1.

  The cluster block 16 has a connection terminal 16A that protrudes from the front end portion to the front side, and a connection terminal 16B that is accommodated in the rear end portion. The connection terminal 16 </ b> A protrudes outside through the bottom wall 1 </ b> A of the motor housing 1. Between the connection terminal 16A and the bottom wall 1A, the motor chamber 1C is sealed so as to be hermetically sealed.

  The front end side of the lead wire 16C is connected to the cluster block 16 via the connection terminal 16B. The rear end side of the lead wire 16 </ b> C is connected to the stator 15. The stator 15 is appropriately supplied with power from a power supply device (not shown) through the connection terminal 16A, 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 shaft support portion 1G projects from the bottom wall 1A of the motor housing 1 in the axial direction. A bearing device 21 is provided on the shaft support 1G. 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 a plurality of bolts 25 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. 1, the cylinder block 7 extends in a cylindrical shape in the direction of the rotation axis X1. The cylinder block 7 forms a cylinder chamber 31 together with the first and second side plates 4 and 5. As shown in FIGS. 2 and 3, 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 in this embodiment. The first and second vanes 51 and 52 are provided with plating (not shown) so as to slide with the front surface, the inner peripheral surface 31S and the rear surface of the cylinder chamber 31 and the rotor 41 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. As shown in FIGS. 1 to 3, the cylinder block 7 is formed with a suction passage 33 </ b> B communicating with the suction passage 33 </ b> A. 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. In the present embodiment, as shown in FIGS. 5A and 5B, a reference line SL1 perpendicular to the rotation axis X1 is defined for the rotor 41. A direction in which the reference line SL1 extends is defined as a first direction W1. The first direction W1 is an example of the “protrusion direction” in the present invention. Further, as shown in FIGS. 5A and 5B and FIG. 6, a reference plane S1 including a rotation axis X1 and a reference line SL1 is defined for the rotor 41. When the rotor 41 rotates around the rotation axis X1, the reference line SL1 and the reference plane S1 also rotate around the rotation axis X1. FIG. 5A corresponds to the positions of the rotor 41 and the first and second vanes 51 and 52 shown in FIG. FIG. 5B corresponds to the positions of the rotor 41 and the first and second vanes 51 and 52 shown in FIG.

  As shown in FIGS. 1 to 4, the rotor 41 is provided in the cylinder chamber 31 so as to be able to rotate synchronously with the rotary shaft 19. As shown in FIGS. 2 to 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 parallel to the opposite direction in the radial direction of the rotor 41, the extending directions are shifted, and the rotation axis X1 of the rotation shaft 19 is the axis of symmetry. They are arranged so as to be line symmetric. Specifically, as shown in FIGS. 5A and 5B, the first vane groove 41A is separated from the reference plane S1 by a distance D41 in the direction opposite to the rotation direction R1 of the rotor 41, and the reference plane S1. It extends in parallel. The second vane groove 41B is separated from the reference plane S1 by a distance D41 in the direction opposite to the rotation direction R1 of the rotor 41, and extends in parallel with the reference plane S1. That is, the first vane groove 41A and the second vane groove 41B are separated from the reference plane S1 by an equal distance D41, and are located downstream from the reference plane S1 in the rotation direction R1 of the rotor 41.

  As shown in FIGS. 2 to 4, a flat plate-like first vane 51 is provided in the first vane groove 41 </ b> A so as to be able to appear and retract. A flat plate-like second vane 52 is provided in the second vane groove 41B so as to appear and retract. The first and second vanes 51 and 52 are brought into and out of the first and second vane grooves 41 </ b> A and 41 </ b> B by bringing their tip portions into sliding contact with the inner peripheral surface 31 </ b> S of the cylinder chamber 31 as the rotor 41 rotates. To do. As shown in FIG. 6, the front end corner and the rear end corner on the inner peripheral side of the first vane 51 are first end portions 47A and 47A. The front end corner portion and the rear end corner portion on the inner peripheral side of the second vane 52 are second end portions 48A and 48A.

  As shown in FIGS. 5A and 5B, distances between the first ends 47A and 47A of the first vane 51 and the second ends 48A and 48A of the second vane 52 in the first direction W1. Is the first distance D1.

  As described above, 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, and the cross-sectional shape of the outer peripheral surface 41S of the rotor 41 is centered on the rotation axis X1. It is a perfect circle. With this configuration, even if the first and second vanes 51 and 52 slide in and out of the first and second vane grooves 41A and 41B while being in sliding contact with the inner circumferential surface 31S of the cylinder chamber 31, in short, the rotation of the rotor 41 is affected. First, the first distance D1 has a substantially constant length.

  As shown in FIGS. 2 to 4, 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 Compression chambers 30A and 30B are formed.

  As shown in FIG. 1, a first accommodating portion 42 is formed on the front end surface of the rotor 41. The 1st accommodating part 42 is dented toward back, making the rotating shaft 19 internal. A second accommodating portion 43 is formed on the rear end surface of the rotor 41. The 2nd accommodating part 43 is dented toward the front, making the rotating shaft 19 internal. The first accommodation member 42 accommodates the first transmission member 110. The second transmission member 120 is accommodated in the second accommodation portion 43. The first and second accommodating portions 42 and 43 are examples of the “accommodating portion” in the present invention. The first and second transmission members 110 and 120 are examples of the “transmission member” in the present invention.

  The first housing part 42 and the first transmission member 110 on the front side and the second housing part 43 and the second transmission member 120 on the rear side have the same configuration. For this reason, in the following description, illustration and description of the first housing part 42 and the first transmission member 110 are mainly performed, and illustration and description of the second storage part 43 and the second transmission member 120 are omitted or simplified as appropriate. To do.

  As shown in FIGS. 3 and 4, the first accommodating portion 42 has a substantially rectangular shape that is long in the first direction W1 when viewed from the direction of the rotation axis X1. The first accommodating portion 42 overlaps a part of the first and second vane grooves 41A and 41B.

  The first transmission member 110 is a metal plate material, and has a substantially rectangular shape that is long in the first direction W1 when viewed from the direction of the rotation axis X1, as shown in FIGS. The first transmission member 110 is formed with a plating (not shown) so that the first transmission member 110 can slide on the bottom surface and the side wall surface of the first accommodating portion 42. The pair of inner wall surfaces on the long side of the first housing portion 42 are guide surfaces 42A and 42A. A bypass hole 110 </ b> C is provided through the center of the first transmission member 110. The bypass hole 110 </ b> C is a long hole that is long in the first direction W <b> 1 and passes through the rotation shaft 19. The bypass hole 110C is an example of the “hole through which the rotation shaft is inserted” in the present invention. Since a sufficient gap is secured between the bypass hole 110C and the rotary shaft 19, the rotary shaft 19 is prevented from contacting the bypass hole 110C. The plate thickness of the first transmission member 110 is set slightly smaller than the distance between the bottom surface of the first housing portion 42 and the front surface of the cylinder chamber 31. The pair of outer wall surfaces on the long side of the first transmission member 110 are slidable contact portions 110D and 110D. The sliding contact portions 110 </ b> D and 110 </ b> D can be in sliding contact with the guide surfaces 42 </ b> A and 42 </ b> A of the first housing portion 42.

  Thus, the first transmission member 110 is accommodated in the first accommodating portion 42 while bypassing the rotating shaft 19 and can reciprocate while slidingly contacting the first accommodating portion 42 in the first direction W1. Similarly to the first transmission member 110, the second transmission member 120 is accommodated in the second accommodation portion 43 while bypassing the rotation shaft 19, and can be reciprocated in the first direction W <b> 1 while being in sliding contact with the second accommodation portion 43. It has become.

  As shown in FIGS. 3, 4, and 6, the first transmission member 110 includes leaf springs 115 </ b> A and 115 </ b> B. The leaf springs 115A and 115B are attached to a pair of outer wall surfaces on the short side of the first transmission member 110, respectively.

  The root portion of the leaf spring 115 </ b> A is fixed by a locking pin to a portion of the one outer wall surface on the short side of the first transmission member 110 that is farthest from the first end portion 47 </ b> A on the front side of the first vane 51. Yes. The leaf spring 115A extends flat when not pressed in the first direction W1. One outer wall surface on the short side of the first transmission member 110 is curved so as to be separated from the first vane 51 as it is separated from the locking pin. The front end of the leaf spring 115 </ b> A is in contact with the first end 47 </ b> A on the front side of the first vane 51. When the leaf spring 115 </ b> A is pushed by the first vane 51, the distal end portion of the leaf spring 115 </ b> A is bent so as to approach one outer wall surface on the short side of the first transmission member 110, and a restoring force is accumulated.

  The root portion of the leaf spring 115B is fixed to the portion of the other outer wall surface on the short side of the first transmission member 110 that is farthest from the second end portion 48A on the front side of the second vane 52 by a locking pin. Yes. The leaf spring 115B extends flat when not pressed in the first direction W1. The other outer wall surface on the short side of the first transmission member 110 is curved so as to be separated from the second vane 52 as it is separated from the locking pin. The tip of the leaf spring 115B is in contact with the second end 48A on the front side of the second vane 52. When the leaf spring 115B is pushed by the second vane 52, the distal end portion of the leaf spring 115B is bent so as to approach the other outer wall surface on the short side of the first transmission member 110, and the restoring force is accumulated.

  The tip of the leaf spring 115A is the first pressing portion 110A. The tip of the leaf spring 115B is a second pressing portion 110B. That is, the leaf springs 115A and 115B are an example of the “biasing means” in the present invention, and bias the first pressing portion 110A and the second pressing portion 110B so as to be separated from each other in the first direction W1. .

  As shown in FIG. 6, the distance D20 in the first direction W1 between the pair of outer wall surfaces on the short side of the first transmission member 110 is constant, and is set smaller than the first distance D1 shown in FIG. The distance in the first direction W1 between the tip of the first pressing part 110A and the tip of the second pressing part 110B is D21. The distance D21 is larger than the distance D20 in a state where the first pressing part 110A and the second pressing part 110B are not elastically deformed, but increases or decreases by the elastic deformation of the first pressing part 110A and the second pressing part 110B. , Can be smaller than the distance D20. Thus, even when the first distance D1 slightly varies, the relationship of the first distance D1 = the distance D21 is maintained by the elastic deformation of the leaf springs 115A and 115B.

  As shown in FIG. 6, the second transmission member 120 has leaf springs 125A and 125B. The leaf springs 125A and 125B are attached to a pair of outer wall surfaces on the short side of the second transmission member 120, respectively.

  The root portion of the leaf spring 125A is fixed to the portion of the outer wall on the short side of the second transmission member 120 that is farthest from the first end 47A on the rear side of the first vane 51 by a locking pin. ing. The plate spring 125A has the same configuration as the plate spring 115A of the first transmission member 110. The front end of the leaf spring 125 </ b> A is in contact with the first end 47 </ b> A on the rear side of the first vane 51. When the leaf spring 125 </ b> A is pushed by the first vane 51, the distal end portion of the leaf spring 125 </ b> A is bent so as to approach one outer wall surface on the short side of the first transmission member 110, and a restoring force is accumulated.

  The root portion of the leaf spring 125B is fixed by a locking pin to a portion of the other outer wall surface on the short side of the second transmission member 120 that is farthest from the second end portion 48A on the rear side of the second vane 52. ing. The leaf spring 125B has the same configuration as the leaf spring 115B of the first transmission member 110. The tip of the leaf spring 125B is in contact with the second end 48A on the rear side of the second vane 52. When the leaf spring 125B is pushed by the second vane 52, the distal end portion of the leaf spring 125B is bent so as to approach the other outer wall surface on the short side of the first transmission member 110, and a restoring force is accumulated.

  The tip of the leaf spring 125A is the first pressing portion 120A. The tip of the leaf spring 125B is a second pressing portion 120B. That is, the leaf springs 125A and 125B are an example of the “biasing means” of the present invention, and bias the first pressing portion 120A and the second pressing portion 120B so as to be separated from each other in the first direction W1. .

  Although illustration is omitted, the first and second vanes 51 and 52, the first transmission member 110, and the leaf springs 115A and 115B are also used for the first and second vanes 51 and 52, the second transmission member 120, and the leaf springs 125A and 125B. The same relationship as the first distance D1 = distance D21 is established.

  As shown in FIG. 2, a space between the bottom surface of the first vane 51 and the first vane groove 41A is a first back pressure chamber 49A. A space between the bottom surface of the second vane 52 and the second vane groove 41B is a second back pressure chamber 49B.

  As shown in FIG. 1, a communication path 5 </ b> G is formed in the rotating shaft 19 and the rotor 41. The communication path 5G extends from the rear end surface of the rotation shaft 19 to the front side along the rotation axis X1, and then bends in the radially outward direction of the rotation axis X1 to form the first back pressure chamber 49A and the second back pressure chamber. It communicates with 49B. In FIG. 1, only a portion communicating with the second back pressure chamber 49B in the communication passage 5G is illustrated, and a portion communicating with the first back pressure chamber 49A in the communication passage 5G is omitted. The first and second passages 5E and 5F, the oil supply chamber 310, and the communication passage 5G are examples of the “back pressure passage” of the present invention.

  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.

  Meanwhile, in this compressor, when the rotor 41 rotates in the rotation direction R1 from the state shown in FIG. 3 with the rotation of the rotary shaft 19, the second vane 52 is pushed by the inner peripheral surface 31S of the cylinder chamber 31 and the second It is buried in the vane groove 41B. When the rotor 41 rotates 90 degrees from the state shown in FIG. 3, the state shown in FIG. 4 is obtained. When further rotated 90 degrees from this state, the positions of the first vane 51 and the second vane 52 are interchanged, and the state shown in FIG. 3 is obtained.

  At this time, the second end portions 48A and 48A of the second vane 52 press the second pressing portions 110B and 120B of the first and second transmission members 110 and 120, and the first and second transmission members 110 and 120 are moved in the first direction. Displace to W1. Further, the leaf springs 115A, 115B, 125A, 125B bias the first pressing portions 110A, 120A and the second pressing portions 110B, 120B so as to be separated from each other in the first direction W1. Therefore, the first pressing portions 110A and 120A of the first and second transmission members 110 and 120 reliably press the first end portions 47A and 47A of the first vane 51, and the first vane 51 is removed from the first vane groove 41A. Make it protrude. When the positions of the first vane 51 and the second vane 52 are switched to be in the state shown in FIG. 3, if the rotor 41 rotates, the first vane 51 acts similarly to the second vane 52.

  Thus, in this compressor, the displacement when the second vane 52 is buried is reliably transmitted to the first vane 51 via the first and second transmission members 110 and 120, and the first vane 51 is transmitted to the first vane groove 41A. The displacement when the first vane 51 is buried is reliably transmitted to the second vane 52 via the first and second transmission members 110 and 120, and the second vane 52 projects from the second vane groove 41B.

  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 lubricating oil is supplied to the first and second back pressure chambers 49A and 49B through the first and second passages 5E and 5F, the oil supply chamber 310 and the communication passage 5G, A back pressure is applied to the first and second vanes 51 and 52. As a result, the first and second vanes 51 and 52 are pushed by the back pressure and are suitably urged to the inner peripheral surface 31S of the cylinder chamber 31, and work is performed with high compression efficiency.

  At this time, in this compressor, even if the first distance D1 related to the first and second vanes 51 and 52 slightly varies, the first end portions 47A and 47A and the first end portions 47A and 47A are The backlash hardly occurs between the pressing portions 110A and 120A or between the second end portions 48A and 48A and the second pressing portions 110B and 120B. For this reason, in this compressor, the 1st press part 110A, 120A of the 1st, 2nd transmission members 110, 120 contact | abuts reliably to 1st end part 47A, 47A, and 2nd press part 110B, 120B is a 2nd end. The first and second vanes 51 and 52 are pressed against the first and second vane grooves 41A and 41B even if the back pressure is weakened. Can be infested. For this reason, in this compressor, while suppressing chattering of each vane 51 and 52, pressure loss can be suppressed and by extension, compression performance can be improved.

  Therefore, with this compressor, it is possible to improve the compression performance.

  Further, in this compressor, the first accommodating portion 42 is provided on the front end surface of the rotor 41, the second accommodating portion 43 is provided on the rear end surface of the rotor 41, and the first, second accommodating portions 42, 43 have first, The two transmission members 110 and 120 are accommodated while bypassing the rotary shaft 19, and the first and second transmission members 110 and 120 reciprocate while slidingly contacting the first and second accommodation portions 42 and 43 in the first direction W1. Is adopted. That is, in this compressor, unlike the pump disclosed in Patent Document 1, there is no need to drill the rotary shaft 19 for the first and second transmission members 110 and 120. Further, in this compressor, unlike the vane type compressor disclosed in Patent Document 2, it is not necessary to manufacture the first and second vanes 51 and 52 and the first and second transmission members 110 and 120 as one member. It is not necessary to form support portions for supporting the first and second transmission members 110 and 120 on the rear surface of the first side plate 4 and the front surface of the second side plate 5, and only the first and second transmission members 110 and 120 are provided on the rotor 41. It is only necessary to form the first and second accommodating portions 42 and 43 to be accommodated. For this reason, in this compressor, compared with the compressor of the said patent document 1 and 2, the simplification of a manufacturing process and reduction of a number of parts are realizable.

  In this compressor, 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. Accordingly, in this compressor, as shown in FIGS. 5A and 5B, a configuration in which the first distance D1 related to the first and second vanes 51 and 52 has a substantially constant length can be easily realized. As a result, the first and second transmission members 110 and 120 are surely maintained in contact with the first vane 51 by the first pressing portions 110A and 120A and are in contact with the second vane 52 by the second pressing portions 110B and 120B. it can.

  Further, in this compressor, as shown in FIGS. 5A and 5B, the first vane groove 41A and the second vane groove 41B are separated from the reference plane S1 by an equal distance D41. That is, in this compressor, compared with the case where the first vane groove 41A and the second vane groove 41B extend overlapping the reference surface S1, the first and second end portions 47A of the first and second vanes 51, 52 are compared. 47A, 48A, and 48A are separated from the rotation axis X1, a space for arranging the first and second transmission members 110 and 120 on the front end face side and the rear end face side of the rotor 41 is secured widely, and the first and second transmissions are provided. The degree of freedom in designing the members 110 and 120 can be increased. Therefore, in this compressor, the first and second transmission members 110 and 120 have a bypass hole 110C for bypassing the rotary shaft 19, the first and second pressing portions 110A, 120A, 110B, and 120B, and the leaf springs 115A and 115B. , 125A, 125B can be easily provided.

  Further, in this compressor, as shown in FIG. 3 and the like, the first and second transmission members 110 and 120 have a substantially rectangular shape that is long in the first direction W1 when viewed from the direction of the rotation axis X1 of the rotation shaft 19. ing. The first pressing portions 110 </ b> A and 120 </ b> A are in contact with the first vane 51 on the corner portion side of the outer surfaces on the short side facing the first vane 51 in the first and second transmission members 110 and 120. The second pressing portions 110 </ b> B and 120 </ b> B are in contact with the second vane 52 on the corner portion side of the outer surface on the short side facing the second vane 52 in the first and second transmission members 110 and 120. Thus, in this compressor, the first and second transmission members 110 and 120 are moved by the first pressing portions 110A and 120A while realizing simplification and miniaturization of the shapes of the first and second transmission members 110 and 120. The state of contacting the first vane 51 and the contact of the second vane 52 by the second pressing portions 110B and 120B can be reliably maintained.

  Further, in this compressor, the sliding contact portions 110D and 110D which are a pair of outer surfaces on the long side of the first and second transmission members 110 and 120 slide on the guide surfaces 42A and 42A of the first and second storage portions 42 and 43, respectively. By contacting, the first and second transmission members 110 and 120 are guided so as to be able to reciprocate in the first direction W1. Thereby, in this compressor, since the inclination with respect to the 1st direction W1 of the 1st, 2nd transmission members 110 and 120 is suppressed, the 1st and 2nd transmission members 110 and 120 are 1st by 110 A of 1st press parts, and 120A. The state of contacting the vane 51 and the contact of the second vane 52 by the second pressing portions 110B and 120B can be reliably maintained.

  Further, in this compressor, a bypass hole 110C through which the rotary shaft 19 is inserted penetrates the first and second transmission members 110 and 120, and the bypass hole 110C has an oval shape that is long in the first direction W1. . Thus, in this compressor, the first and second transmission members 110 and 120 can smoothly reciprocate within the first and second accommodating portions 42 and 43 without interfering with the rotary shaft 19.

  Furthermore, in this compressor, as shown in FIG. 6, the first pressing portion 110 </ b> A of the first transmission member 110 presses the first end portion 47 </ b> A on the front side of the first vane 51, and the first transmission member 120 first Since the pressing portion 120A presses the first end 47A on the rear side of the first vane 51, the first vane 51 is not easily twisted in the first vane groove 41A. Further, the second pressing portion 110B of the first transmission member 110 presses the second end portion 48A on the front side of the second vane 52, and the second pressing portion 120B of the second transmission member 120 is on the rear side of the second vane 52. Since the second end 48A is pressed, the second vane 52 is less likely to be twisted in the second vane groove 42A. For this reason, in this compressor, the 1st, 2nd vanes 51 and 52 can be made to appear smoothly with respect to the 1st and 2nd vane grooves 41A and 41B.

(Example 2)
As shown in FIG. 7, in the compressor of the second embodiment, the oil supply chamber 310 and the communication path 5G in the compressor of the first embodiment are 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. 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 of the second embodiment, the lubricating oil stored in the discharge chamber 9A passes through the first and second passages 5E and 305F, the annular grooves 4C and 5C, and the first and second storage portions 42 and 43, and then passes through the first back. The pressure chamber 49A and the second back pressure chamber 49B are supplied.

  The compressor of Example 2 which is the said structure can also show | play the effect similar to the compressor of Example 1. FIG. Moreover, in this compressor, since lubricating oil is supplied also to the 1st, 2nd accommodating parts 42 and 43, lubricating oil is temporarily stored in the 1st and 2nd accommodating parts 42 and 43. And the sudden movement of the 1st and 2nd transmission members 110 and 120 is buffered by the stored lubricating oil, and the 1st and 2nd transmission members 110 and 120 are made into the 1st and 2nd receiving parts 42 by the lubrication effect. , 43 can slide smoothly.

  Hereinafter, specific examples of transmission members that can be replaced with the first and second transmission members 110 and 120 according to the first embodiment will be described with reference to FIGS.

Example 3
As shown in FIG. 8, the transmission member 410 is provided with a bypass hole 410 </ b> C similar to the bypass hole 110 </ b> C according to the first embodiment. A pair of outer wall surfaces on the short side of the transmission member 410 have bottomed holes recessed in the first direction W1, and guide pins 415P and 415P and compression coil springs 415A and 415B are accommodated in the bottomed holes. Yes. The compression coil springs 415A and 415B are inserted through the guide pins 415P and 415P. The distal end portion of the compression coil spring 415A serves as the first pressing portion 410A, and presses the first end portion 47A of the first vane 51. The distal end portion of the compression coil spring 415B serves as the second pressing portion 410B and presses the second end portion 48A of the second vane 52. The compression coil springs 415A and 415B are also examples of the “biasing means” of the present invention.

Example 4
The transmission member 510 shown in FIG. 9 is divided into a first member 511 and a second member 512. The first member 511 and the second member 512 are substantially U-shaped when viewed from the direction of the rotation axis X <b> 1 and bypass the rotation shaft 19.

  The end faces of the first member 511 and the second member 512 facing each other in the first direction W1 have bottomed holes recessed in the first direction W1, and the bottomed holes have guide pins 515P and 515P and compression coil springs 515A, 515B is accommodated. The compression coil springs 515A and 515B are inserted through the guide pins 515P and 515P. The compression coil springs 515A and 515B bias the first member 511 and the second member 512 so as to be separated from each other in the first direction W1.

  The outer wall surface of the first member 511 on the first vane 51 side is used as the first pressing portion 510 </ b> A and presses the first end 47 </ b> A of the first vane 51. The outer wall surface of the second member 512 on the second vane 52 side is used as the second pressing portion 510B, and presses the second end portion 48A of the second vane 52. The compression coil springs 515A and 515B are also examples of the “biasing means” of the present invention.

(Example 5)
As shown in FIG. 10, the transmission member 610 is provided with a bypass hole 610C similar to the bypass hole 110C according to the first embodiment. A pair of outer wall surfaces on the short side of the transmission member 610 are formed with fitting grooves, and rubber blocks 615A and 615B are fitted into these fitting grooves. The front end portion of the rubber block 615 </ b> A serves as a first pressing portion 610 </ b> A and presses the first end portion 47 </ b> A of the first vane 51. The front end portion of the rubber block 615B serves as the second pressing portion 610B and presses the second end portion 48A of the second vane 52. The rubber blocks 615A and 615B are also examples of the “biasing means” of the present invention. The outer shape and the like of the rubber blocks 615A and 615B are set so that the thickness in the direction of the rotation axis X1 is less than the plate thickness of the transmission member 610 even when elastically deformed.

(Example 6)
A transmission member 710 shown in FIG. 11 is divided into two parts, a first member 711 and a second member 712. The first member 711 and the second member 712 are substantially U-shaped when viewed from the direction of the rotation axis X <b> 1 and bypass the rotation shaft 19.

  Fitting grooves are formed on the end surfaces of the first member 711 and the second member 712 facing in the first direction W1, and the rubber blocks 715A and 715B are fitted into these fitting grooves. The rubber blocks 715A and 715B bias the first member 711 and the second member 712 so as to be separated from each other in the first direction W1.

  The outer wall surface of the first member 711 on the first vane 51 side is the first pressing portion 710 </ b> A, and presses the first end 47 </ b> A of the first vane 51. The outer wall surface of the second member 712 on the second vane 52 side is used as the second pressing portion 710 </ b> B, and presses the second end portion 48 </ b> A of the second vane 52. The rubber blocks 715A and 715B are also examples of the “biasing means” of the present invention. The outer shape and the like of the rubber blocks 715A and 715B are set so that the thickness in the direction of the rotation axis X1 is less than the plate thickness of the first and second members 711 and 712 even when elastically deformed.

(Example 7)
The transmission member 910 shown in FIG. 12 is divided into two parts, a first member 911 and a second member 912. The first member 911 and the second member 912 are substantially U-shaped as viewed from the direction of the rotation axis X1 and bypass the rotation shaft 19.

  Between the end surfaces of the first member 911 and the second member 912 facing in the first direction W1, substantially U-shaped springs 915A and 915B are disposed. The springs 915A and 915B may be disc springs or the like. The springs 915A and 915B bias the first member 911 and the second member 912 so as to be separated from each other in the first direction W1.

  An outer wall surface on the first vane 51 side of the first member 911 is used as a first pressing portion 910 </ b> A to press the first end 47 </ b> A of the first vane 51. The outer wall surface of the second member 912 on the second vane 52 side is used as the second pressing portion 910 </ b> B, and presses the second end portion 48 </ b> A of the second vane 52. The springs 915A and 915B are also examples of the “biasing means” of the present invention.

(Example 8)
The transmission member 1010 shown in FIG. 13 is divided into two parts, a first member 1011 and a second member 1012. The first member 1011 and the second member 1012 are substantially U-shaped when viewed from the direction of the rotation axis X <b> 1 and bypass the rotation shaft 19.

  The outer wall surface of the transmission member 1010 on the first vane 51 side is a first pressing portion 1010A, and is in contact with the first end 47A of the first vane 51. The outer wall surface of the transmission member 1010 on the second vane 52 side is a second pressing portion 1010B, and is in contact with the second end 48A of the second vane 52.

  The first member 1011 and the second member 1012 are made of a magnetic material, and an N-pole and an S-pole are located at a pair of substantially U-shaped tip portions like a horseshoe magnet. The end faces of the first member 1011 and the second member 1012 facing in the first direction W1 are set so that the N pole and the N pole face each other and the S pole and the S pole face each other. Accordingly, the first member 1011 and the second member 1012 repel each other and urge the first pressing portion 1010A and the second pressing portion 1010B so as to be separated from each other in the first direction W1, so that the first pressing The portion 1010A presses the first end portion 47A, and the second pressing portion 1010B presses the second end portion 48A. The first member 1011 and the second member 1012 made of a magnetic material are also examples of the “biasing means” of the present invention.

  Even if the transmission members 410, 510, 610, 710, 910, 1010 of the third to eighth embodiments are employed instead of the first and second transmission members 110, 120 for the compressors of the first and second embodiments, the present invention. The effect of this can be achieved.

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

  In the embodiment, the cross-sectional shape of the cylinder chamber 31 perpendicular to the direction of the rotation axis X1 is a perfect circle, but the configuration is not limited to this. For example, the cross-sectional shape of the inner peripheral surface of the cylinder chamber may be a distorted circle so that the first distance is constant.

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

9A ... Discharge chamber 31 ... Cylinder chamber 31S ... Inner circumferential surface of 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 19 ... Rotating shaft 41A, 241A ... First vane groove 41B, 241B ... Second vane groove 41 ... Rotor 41S ... Outer peripheral surface of rotor 51 ... First vane 52 ... Second vane 30A, 30B ... Compression chamber SL1 ... reference line S1 ... reference surface 47A ... first end 48A ... second end W1 ... protrusion direction (first direction)
D1 ... 1st distance 110, 120, 410, 510, 610, 710, 910, 1010 ... Transmission member (110 ... 1st transmission member, 120 ... 2nd transmission member)
110A, 120A, 410A, 510A, 610A, 710A, 910A, 1010A ... first pressing part 110B, 120B, 410B, 510B, 610B, 710B, 910B, 1010B ... second pressing part 115A, 115B, 125A, 125B, 415A, 415B, 515A, 515B, 615A, 615B, 715A, 715B, 915A, 915B ... biasing means (115A, 115B, 125A, 125B ... leaf spring)
42, 43 ... accommodating portion (42 ... first accommodating portion, 43 ... second accommodating portion)
110C ... hole (bypass hole)
49A ... 1st back pressure chamber 49B ... 2nd back pressure chamber 5E, 5F, 310, 5G ... Back pressure flow path (5E ... 1st passage, 5F ... 2nd passage, 310 ... Refueling chamber, 5G ... Communication passage)

Claims (6)

A housing in which a discharge chamber and a cylinder chamber are formed;
A rotating shaft rotatably provided in the housing;
A rotor provided in the cylinder chamber so as to be rotatable together with the rotating shaft, and formed with a first vane groove and a second vane groove;
A first vane provided in the first vane groove so as to be able to appear and disappear;
A second vane provided in the second vane groove so as to be able to appear and disappear,
A vane type compressor in which a compression chamber is formed by a front surface of the cylinder chamber, an inner peripheral surface of the cylinder chamber, a rear surface of the cylinder chamber, an outer peripheral surface of the rotor, the first vane and the second vane;
The first vane groove and the second vane groove extend in parallel to opposite directions in the radial direction of the rotor, the extending direction is shifted, and are symmetric in the rotation axis of the rotation shaft,
On at least one end surface of the rotor, a housing portion that is recessed while the rotating shaft is contained is formed,
The accommodating portion is in contact with the first vane at a first pressing portion provided on one end side, and is in contact with the second vane at a second pressing portion provided on the other end side. And a transmission member guided so as to reciprocate in the protruding and retracting directions of the first vane and the second vane. Has been
The transmission member causes the second vane to protrude from the second vane groove when the first vane is pressed against the inner peripheral surface of the cylinder chamber and accommodated in the first vane groove, and the second vane groove protrudes from the second vane groove. When the vane is pressed against the inner peripheral surface of the cylinder chamber and accommodated in the second vane groove, the first vane and the second vane are protruded from the first vane groove. A vane-type compressor configured to transmit movement. The transmission member has a substantially rectangular shape that is long in the direction of protrusion and depression when viewed from the direction of the rotation axis.
The first pressing portion is in contact with the first vane on the corner side of the outer surface on the short side facing the first vane in the transmission member;
2. The vane compressor according to claim 1, wherein the second pressing portion is in contact with the second vane on a corner portion side of an outer surface on a short side facing the second vane in the transmission member. The transmission member has a substantially rectangular shape that is long in the direction of protrusion and depression when viewed from the direction of the rotation axis.
The vane type compressor according to claim 1 or 2, wherein the pair of outer surfaces on the long side of the transmission member are slidably contacted with the housing portion, whereby the transmission member is guided so as to reciprocate in the retracting direction. The transmission member has a hole through which the rotating shaft is inserted,
The vane type compressor according to any one of claims 1 to 3, wherein the hole has an oval shape that is long in the protruding and protruding direction. The housing portion includes a first housing portion formed on one end surface of the rotor and a second housing portion formed on the other end surface of the rotor,
5. The vane type according to claim 1, wherein the transmission member includes a first transmission member housed in the first housing portion and a second transmission member housed in the second housing portion. Compressor. A space between the bottom surface of the first vane and the first vane groove is a first back pressure chamber,
A space between the bottom surface of the second vane and the second vane groove is a second back pressure chamber,
6. The back pressure flow path that connects the discharge chamber, the first back pressure chamber, and the second back pressure chamber is formed in the rotating shaft and the rotor, respectively. Vane type compressor.

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