JP7647643B2 - Scroll Compressor - Google Patents

Description

The present invention relates to a scroll compressor.

Patent Document 1 discloses a conventional scroll compressor. This scroll compressor includes a housing, a drive shaft, a fixed scroll, and a movable scroll. The housing defines a suction chamber into which refrigerant is drawn. The drive shaft is provided within the housing and is rotatable about the drive shaft center. The fixed scroll is fixed within the housing. The movable scroll is provided within the housing. The movable scroll rotates together with the drive shaft and defines a compression chamber between the movable scroll and the fixed scroll.

In addition, in this scroll compressor, the housing has a fixed block. The fixed block is located between the suction chamber and the movable scroll, and the drive shaft is inserted rotatably through it. The movable scroll and the fixed block are connected by an anti-rotation mechanism that prevents the movable scroll from rotating on its axis.

The fixed block is provided with an intake passage, a first accommodation groove, a second accommodation groove, a first sealing member, and a second sealing member. The intake passage is disposed outside the drive shaft and the rotation prevention mechanism in the radial direction of the drive shaft. The first accommodation groove is located inside the rotation prevention mechanism in the radial direction of the drive shaft. The second accommodation groove is located between the first accommodation groove and the rotation prevention mechanism in the radial direction of the drive shaft. The first accommodation groove and the second accommodation groove are each formed in an annular shape surrounding the drive shaft. The first sealing member and the second sealing member are formed in an annular shape corresponding to the first accommodation groove and the second accommodation groove. The first sealing member is accommodated in the first accommodation groove. The second sealing member is accommodated in the second accommodation groove. As a result, the second sealing member forms a back pressure chamber together with the first sealing member.

In this scroll compressor, the refrigerant in the suction chamber flows into the compression chamber through the suction passage. As the drive shaft rotates around the drive shaft, the movable scroll revolves and the volume of the compression chamber decreases. In this way, the refrigerant is compressed in the compression chamber. Also, a portion of the refrigerant compressed in the compression chamber is supplied to the back pressure chamber. As a result, the movable scroll is biased toward the compression chamber by the pressure in the back pressure chamber, and is prevented from rotating in an inclined state with respect to the drive shaft center. In this way, this compressor prevents refrigerant leakage from the compression chamber, preventing a decrease in compression efficiency, and preventing the generation of noise due to discharge pulsation.

JP 2015-4296 A

In this type of scroll compressor, in order to further improve compression efficiency and achieve high quietness, it is necessary to further prevent refrigerant leakage from the compression chamber. Therefore, in the above-mentioned conventional scroll compressor, it is possible to secure a large back pressure chamber and urge the movable scroll toward the compression chamber by using a larger pressure-receiving area. On the other hand, there is also a demand to make the scroll compressor smaller. However, with this scroll compressor, it is difficult to secure a large back pressure chamber while reducing the size.

The present invention was made in consideration of the above-mentioned conventional situation, and the problem to be solved is to provide a scroll-type compressor that has excellent compression efficiency and quietness, and can be made compact.

The scroll compressor of the present invention comprises: a housing having a suction chamber into which a fluid is drawn;
a drive shaft provided within the housing and rotatable about a drive shaft center;
a fixed scroll fixed within the housing;
a movable scroll provided in the housing, rotating together with the drive shaft and defining a compression chamber for compressing a fluid between the movable scroll and the fixed scroll,
the housing is located between the suction chamber and the movable scroll and has a fixed block through which the drive shaft is rotatably inserted,
The movable scroll and the fixed block are connected by a rotation prevention mechanism that prevents the movable scroll from rotating.
the fixed block has an intake passage disposed radially outward of the drive shaft and the rotation prevention mechanism, the intake passage allowing the fluid in the intake chamber to flow to the compression chamber;
a first accommodating groove that is located outside the rotation prevention mechanism in the radial direction and that is formed in an annular shape surrounding the drive shaft;
a second accommodating groove formed in an annular shape surrounding the drive shaft and located between the first accommodating groove and the suction passage in the radial direction;
a first sealing member formed in an annular shape and accommodated in the first accommodating groove;
a second sealing member that is formed in an annular shape and accommodated in the second accommodating groove, and that, together with the first sealing member, forms a back pressure chamber that urges the movable scroll toward the compression chamber,
the first accommodating groove has a first protruding portion that protrudes in the radial direction toward the second accommodating groove so as to avoid the rotation prevention mechanism,
the second accommodating groove has a second protruding portion protruding in the radial direction toward the first accommodating groove so as to avoid the suction passage,
The first protrusion and the second protrusion are arranged to be shifted from each other in the circumferential direction of the drive shaft.

In the scroll compressor of the present invention, the first protrusion of the first accommodating groove protrudes radially toward the second accommodating groove so as to avoid the rotation prevention mechanism, and the second protrusion of the second accommodating groove protrudes radially toward the first accommodating groove so as to avoid the suction passage. This allows the portion of the first accommodating groove excluding the first protrusion and the portion of the second accommodating groove excluding the second protrusion to be appropriately separated radially.

In addition, in this scroll compressor, the first protruding portion and the second protruding portion are arranged offset in the circumferential direction of the drive shaft. Therefore, in this scroll compressor, the back pressure chamber is unlikely to become narrower in the radial direction between the first protruding portion and the second protruding portion, and a large back pressure chamber can be ensured. As a result, in this scroll compressor, the large pressure receiving area can urge the movable scroll toward the compression chamber.

In addition, because the back pressure chamber is unlikely to become narrower in the radial direction between the first and second protruding portions, this scroll compressor can also prevent variations in the pressure-receiving area due to the phase between the movable scroll and the back pressure chamber during operation. Therefore, in this scroll compressor, the movable scroll can be preferably biased toward the compression chamber by the large pressure-receiving area, regardless of the phase between the movable scroll and the back pressure chamber. As a result, the movable scroll can be preferably prevented from rotating in an inclined state with respect to the drive shaft center, which can preferably prevent refrigerant leakage from the compression chamber and suppress discharge pulsation.

And with this scroll compressor, there is no need to make the fixed block, and therefore the housing, excessively large in the radial direction in order to ensure a large back pressure chamber.

The scroll compressor of the present invention therefore has excellent compression efficiency and quietness, and can be made compact.

The first sealing member may have a third protruding portion that protrudes radially along the first protruding portion. And, it is preferable that the second sealing member has a fourth protruding portion that protrudes radially along the second protruding portion.

In this case, the first sealing member housed in the first housing groove can be prevented from being excessively bent by the first protruding portion, and the second sealing member housed in the second housing groove can be prevented from being excessively bent by the second protruding portion. This allows the first sealing member and the second sealing member to effectively seal the back pressure chamber.

It is preferable that a thrust plate is provided between the movable scroll and the fixed block, which forms a back pressure chamber together with the first sealing member and the second sealing member. In this case, the back pressure chamber can be formed suitably, and the movable scroll can be more suitably biased toward the compression chamber through the thrust plate. This makes it possible to more suitably prevent refrigerant leakage from the compression chamber.

The scroll compressor of the present invention has excellent compression efficiency and quietness, and can be made compact.

FIG. 1 is a cross-sectional view of a scroll compressor according to an embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line AA of FIG. 1, showing the scroll compressor of the embodiment. FIG. 3 is an enlarged cross-sectional view of a portion of the scroll compressor of the embodiment, showing the portion α of FIG. FIG. 4 is a rear view of the first sealing member of the scroll compressor of the embodiment. FIG. 5 is a rear view of the second sealing member of the scroll compressor of the embodiment. FIG. 6 is a cross-sectional view similar to FIG. 2, showing a scroll compressor of a comparative example.

The following describes an embodiment of the present invention with reference to the drawings. The scroll compressor (hereinafter simply referred to as a compressor) of the embodiment is specifically a scroll-type electric compressor. This compressor is mounted on a vehicle (not shown) and forms a refrigeration circuit of the vehicle.

As shown in FIG. 1, the compressor of the embodiment includes a housing 1, a drive shaft 5, an electric motor 7, a fixed scroll 9, and a movable scroll 11.

In this embodiment, the front-to-rear direction of the compressor is defined by the solid arrow shown in FIG. 1. Also, in FIG. 3, the front-to-rear direction of the compressor is defined corresponding to FIG. 1. Note that this front-to-rear direction is an example for convenience of explanation, and the position of the compressor is appropriately changed according to the vehicle in which it is installed, etc.

As shown in FIG. 1, the housing 1 is composed of a motor housing 13, a compressor housing 14, and a fixed block 15. The motor housing 13 constitutes the front portion of the housing 1, and the compressor housing 14 constitutes the rear portion of the housing 1.

The motor housing 13 has a front wall 13a and a first peripheral wall 13b. The front wall 13a is located at the front end of the motor housing 13 and extends in the radial direction of the motor housing 13. The first peripheral wall 13b is connected to the front wall 13a and extends rearward from the front wall 13a. The front wall 13a and the first peripheral wall 13b give the motor housing 13 a cylindrical shape with a bottom that is open at the rear. A suction chamber 17 is formed within the motor housing 13.

The motor housing 13 is also formed with a suction opening 13c and a support portion 13d. The suction opening 13c is formed in the first peripheral wall 13b and communicates with the suction chamber 17. The suction opening 13c is connected to an evaporator (not shown) by piping (not shown), and allows the refrigerant gas that has passed through the evaporator to be sucked into the suction chamber 17. The refrigerant gas is an example of the "fluid" in this invention.

The support portion 13d protrudes from the front wall 13a into the suction chamber 17. The support portion 13d is cylindrical and has a first radial bearing 19 provided therein. The suction opening 13c may be formed in the front wall 13a.

The compressor housing 14 has a rear wall 14a and a second peripheral wall 14b. The rear wall 14a is located at the rear end of the compressor housing 14 and extends in the radial direction of the compressor housing 14. The second peripheral wall 14b is connected to the rear wall 14a and extends forward from the rear wall 14a. The rear wall 14a and the second peripheral wall 14b form the compressor housing 14 into a cylindrical shape with a bottom that is open at the front.

The compressor housing 14 is formed with an oil separation chamber 14c, a first discharge recess 14d, a discharge passage 14e, and a discharge opening 14f. The oil separation chamber 14c is located on the rear side within the compressor housing 14 and extends in the radial direction of the compressor housing 14. The first discharge recess 14d is located forward of the oil separation chamber 14c within the compressor housing 14 and is recessed toward the oil separation chamber 14c. The discharge passage 14e extends in the front-rear direction and connects the oil separation chamber 14c to the first discharge recess 14d. The discharge opening 14f is connected to the upper end of the oil separation chamber 14c and opens toward the outside of the compressor housing 14. The discharge opening 14f is connected to a condenser (not shown) by piping.

A separation cylinder 21 is fixed inside the oil separation chamber 14c. The separation cylinder 21 has a cylindrical outer peripheral surface 21a. The outer peripheral surface 21a is coaxial with the inner peripheral surface 140 of the oil separation chamber 14c. The outer peripheral surface 21a and the inner peripheral surface 140 form a separator. In addition, a filter 23 is provided below the separation cylinder 21 inside the oil separation chamber 14c.

The fixed block 15 is provided between the motor housing 13 and the compressor housing 14. The motor housing 13, the compressor housing 14, and the fixed block 15 are fastened by four bolts 25 from the compressor housing 14 side (see FIG. 2). Thus, the fixed block 15 is fixed to the motor housing 13 and the compressor housing 14 while being sandwiched between them. Thus, the fixed block 15 is located between the suction chamber 17 and the movable scroll 11 shown in FIG. 1 in the front-rear direction. Note that FIG. 1 shows only one of the four bolts 25. Also, the method of fixing the motor housing 13, the compressor housing 14, and the fixed block 15 can be designed as appropriate.

The fixed block 15 has a boss 15a that protrudes forward. An insertion hole 15b is formed at the tip of the boss 15a. A second radial bearing 27 and a seal member 29 are provided inside the boss 15a.

The drive shaft 5 is provided in the housing 1. The drive shaft 5 is cylindrical and extends in the front-rear direction. The drive shaft 5 is composed of a small diameter section 5a, a large diameter section 5b, and a tapered section 5c. The small diameter section 5a is located at the front end of the drive shaft 5. The large diameter section 5b is located rearward of the small diameter section 5a. The large diameter section 5b is formed with a larger diameter than the small diameter section 5a. The rear end of the large diameter section 5b is formed with a flat rear end surface 5d. The tapered section 5c is located between the small diameter section 5a and the large diameter section 5b. The tapered section 5c is connected to the small diameter section 5a at the front end. The tapered section 5c expands in diameter toward the rear and is connected to the large diameter section 5b at the rear end.

The small diameter portion 5a of the drive shaft 5 is rotatably supported by the support portion 13d of the motor housing 13 via the first radial bearing 19. The rear end side of the large diameter portion 5b is inserted into the insertion hole 15b of the fixed block 15 and enters the boss 15a. Inside the boss 15a, the rear end of the large diameter portion 5b is rotatably supported by the second radial bearing 27. In this way, the drive shaft 5 is rotatable around the drive axis O within the housing 1. The drive axis O extends parallel to the front-rear direction of the compressor. The space between the fixed block 15 and the drive shaft 5 is sealed by a seal member 29.

In addition, an eccentric pin 50 is fixed to the large diameter portion 5b of the drive shaft 5. The eccentric pin 50 is disposed at a position eccentric from the drive shaft center O on the rear end face 5d. The eccentric pin 50 is formed in a cylindrical shape with a smaller diameter than the drive shaft 5, and extends rearward from the rear end face 5d. The eccentric pin 50 enters the boss 15a by inserting the rear end side of the large diameter portion 5b into the insertion hole 15b. The eccentric pin 50 fits into a bushing 50a inside the boss 15a.

Furthermore, in the drive shaft 5, a balance weight 33 is integrally formed on the large diameter portion 5b. The balance weight 33 is disposed in a position eccentric from the drive shaft center O in the large diameter portion 5b. More specifically, the balance weight 33 is disposed on the opposite side of the eccentric pin 50 across the drive shaft center O.

Although detailed illustration is omitted, the balance weight 33 is formed in a plate shape that is approximately fan-shaped. The balance weight 33 extends in the radial direction of the drive shaft 5 in a direction away from the large diameter portion 5b. The radial direction of the drive shaft 5 is a direction perpendicular to the front-rear direction. In other words, the balance weight 33 extends from the large diameter portion 5b toward the first peripheral wall 13b of the motor housing 13. The balance weight 33 is located in the suction chamber 17 by providing the drive shaft 5 in the housing 1. More specifically, the balance weight 33 is located between the fixed block 15 and the electric motor 7 in the suction chamber 17. The shape of the balance weight 33 can be designed as appropriate.

As shown in Figs. 2 and 3, a recess 53 is formed at the rear end of the fixed block 15. The recess 53 is recessed from the rear end of the fixed block 15 toward the front. As shown in Fig. 2, the recess 53 is located outside the drive shaft 5 in the radial direction of the drive shaft 5, and is in a substantially annular shape surrounding the drive shaft 5. In the fixed block 15, the portion outside the recess 53 is defined as an outer periphery 150a, and the portion inside the recess 53 is defined as an inner periphery 150b. In Fig. 2, the drive shaft 5 is shown by a virtual line, and the eccentric pin 50 and the like are omitted from the illustration, for ease of explanation. The same applies to Fig. 6.

The first to fourth fixing holes 151a to 151d are formed in the inner periphery 150b. That is, the first to fourth fixing holes 151a to 151d are formed on the outside of the drive shaft 5 and on the inside of the recess 53 in the radial direction of the drive shaft 5. The first to fourth fixing holes 151a to 151d are arranged at 90° intervals in the circumferential direction of the drive shaft 5. The first to fourth fixing holes 151a to 151d are all of the same configuration, and as shown in FIG. 3, they open at the rear end of the inner periphery 150b and extend forward inside the inner periphery 150b. These first to fourth fixing holes 151a to 151d do not penetrate the inner periphery 150b, and thus the fixed block 15, in the front-rear direction. The intervals between the first to fourth fixing holes 151a to 151d in the circumferential direction of the drive shaft 5 can be designed as appropriate. Also, in Figures 1 and 3, only the first fixing hole 151a is shown.

As shown in FIG. 2, the first to fourth fixing holes 151a to 151d are arranged at equal intervals in the circumferential direction of the drive shaft 5. In addition, in the inner peripheral portion 150b, the periphery of the first fixing hole 151a is defined as a first protruding portion 152a, the periphery of the second fixing hole 151b is defined as a second protruding portion 152b, the periphery of the third fixing hole 151c is defined as a third protruding portion 152c, and the periphery of the fourth fixing hole 151d is defined as a fourth protruding portion 152d. The first to fourth protruding portions 152a to 152d protrude further toward the outside of the drive shaft 5 in the radial direction of the drive shaft 5 than other points in the inner peripheral portion 150b.

As shown in FIG. 1, the electric motor 7 is housed in the suction chamber 17. In other words, the suction chamber 17 also serves as a motor chamber that houses the electric motor 7. The electric motor 7 is located in front of the balance weight 33 in the suction chamber 17.

The electric motor 7 has a stator 7a and a rotor 7b. The stator 7a is fixed to the inner circumferential surface of the first peripheral wall 13b. The stator 7a is connected to an inverter (not shown) provided outside the motor housing 13.

The stator 7a has a stator core 71 and coil ends 73. The stator core 71 is formed in a cylindrical shape. A coil 75 is wound around the stator core 71. The coil ends 73 are annular and protrude forward and backward in the axial direction from the stator core 71. The coil ends 73 are formed by a part of the coils 75. The rear end of the coil ends 73 is inclined on the inner circumferential side to avoid interference with the balance weight 33.

The rotor 7b is disposed within the stator 7a. The large diameter portion 5b of the drive shaft 5 is press-fitted into the rotor 7b. This fixes the drive shaft 5 to the rotor 7b. The rotor 7b rotates within the stator 7a, causing the drive shaft 5 to rotate around the drive shaft center O.

The fixed scroll 9 is fixed to the compressor housing 14 and is disposed within the compressor housing 14. The fixed scroll 9 has a fixed base plate 9a, a fixed peripheral wall 9b, and a fixed spiral wall 9c. The fixed base plate 9a is located at the rear end of the fixed scroll 9 and is formed in a disk shape. The fixed base plate 9a is formed with a second discharge recess 9d and a discharge port 9e. The second discharge recess 9d is shaped to be recessed forward from the rear end surface of the fixed base plate 9a. The second discharge recess 9d faces the first discharge recess 14d as the fixed scroll 9 is fixed to the compressor housing 14. Thus, the first discharge recess 14d and the second discharge recess 9d form a discharge chamber 35. The discharge chamber 35 is connected to the oil separation chamber 14c through the discharge passage 14e. The discharge port 9e penetrates the fixed base plate 9a in the front-rear direction and is connected to the discharge chamber 35.

The discharge reed valve 39 and the retainer 41 are attached to the fixed substrate 9a by a pin 37. The pin 37, the discharge reed valve 39, and the retainer 41 are disposed in the discharge chamber 35. The discharge reed valve 39 opens and closes the discharge port 9e by elastically deforming. The retainer 41 adjusts the amount of elastic deformation of the discharge reed valve 39.

The fixed peripheral wall 9b is connected to the fixed base plate 9a at its outer periphery and extends forward in a cylindrical shape. An intake port 9f is formed in the fixed peripheral wall 9b. The intake port 9f penetrates the fixed peripheral wall 9b in the radial direction. As a result, the intake port 9f opens into the compressor housing 14. The fixed volute wall 9c is raised on the front surface of the fixed base plate 9a and is integral with the fixed peripheral wall 9b on the inside of the fixed peripheral wall 9b.

The fixed scroll 9 is also formed with an oil supply passage 43. The oil supply passage 43 penetrates the fixed base plate 9a and the fixed peripheral wall 9b. As a result, the rear end of the oil supply passage 43 opens into the rear end surface of the fixed base plate 9a, and the front end of the oil supply passage 43 opens into the front end surface of the fixed peripheral wall 9b. The oil supply passage 43 communicates with the oil separation chamber 14c through the filter 23. The shape of the oil supply passage 43 can be designed as appropriate.

The movable scroll 11 is provided in the compressor housing 14 and is located between the fixed scroll 9 and the fixed block 15. The movable scroll 11 has a movable base plate 11a and a movable spiral wall 11b. The movable base plate 11a is located at the front end of the movable scroll 11 and is formed in a disk shape. A bush 50a is rotatably supported on the movable base plate 11a via a third radial bearing 45. As a result, the movable scroll 11 is connected to the drive shaft 5 at a position eccentric from the drive shaft center O through the bush 50a and the eccentric pin 50. The movable spiral wall 11b is raised on the front surface of the movable base plate 11a and extends toward the fixed base plate 9a.

The fixed scroll 9 and the movable scroll 11 are meshed with each other. As a result, a compression chamber 49 is formed between the fixed scroll 9 and the movable scroll 11 by the fixed base plate 9a, the fixed spiral wall 9c, the movable base plate 11a, and the movable spiral wall 11b. The volume of the compression chamber 49 changes as the movable scroll 11 rotates. As a result, the compression chamber 49 is connected to the suction port 9f and the discharge port 9e, respectively.

The movable scroll 11 is also formed with a first air supply passage 11d, a second air supply passage 11e, and a third air supply passage 11f. The first air supply passage 11d opens at the rear end of the movable spiral wall 11b near the center of the movable spiral wall 11b. The first air supply passage 11d extends linearly forward within the movable spiral wall 11b and reaches the movable base plate 11a.

The second air supply passage 11e opens to the outer peripheral surface 111 of the movable substrate 11a and extends linearly within the movable substrate 11a in the radial direction of the movable substrate 11a. The second air supply passage 11e is connected to the front end of the first air supply passage 11d. As shown in FIG. 3, the second air supply passage 11e is provided with a plug member 112 that closes the opening on the outer peripheral surface 111 side.

The third air supply passage 11f opens at the front end of the movable base plate 11a near the outer circumferential surface 111. The third air supply passage 11f extends linearly rearward within the movable base plate 11a toward the second air supply passage 11e and is connected to the second air supply passage 11e.

A thrust plate 51 is provided between the movable scroll 11 and the fixed block 15. The thrust plate 51 is made of a thin metal plate and is in contact with the movable scroll 11 and the fixed block 15. The thrust plate 51 is capable of biasing the movable scroll 11 backward, i.e., toward the fixed scroll 9, by the restoring force generated when the thrust plate 51 is elastically deformed.

The thrust plate 51 is also formed with a communication hole 51a and four pin holes 51b. The communication hole 51a penetrates the thrust plate 51 in the front-rear direction and communicates with the third air supply passage 11f. Each pin hole 51b also penetrates the thrust plate 51 in the front-rear direction. Each pin hole 51b is positioned so as to align with the first to fourth fixing holes 151a to 151d of the fixed block 15 in the front-rear direction, respectively. Note that Figs. 1 and 3 show one of the four pin holes 51b.

The movable scroll 11, thrust plate 51, and fixed block 15 are connected by an anti-rotation mechanism 16. The anti-rotation mechanism 16 is composed of four rings 47 and the first to fourth anti-rotation pins 31a to 31d shown in FIG. 2. Each ring 47 is fixed to the movable base plate 11a. Note that only one of the four rings 47 is shown in FIG. 1 and FIG. 3.

The first to fourth rotation prevention pins 31a to 31d are inserted through the pin holes 51b of the thrust plate 51 and the first to fourth fixing holes 151a to 151d of the fixed block 15, respectively, and are fixed to the first to fourth fixing holes 151a to 151d. Thus, the first to fourth rotation prevention pins 31a to 31d protrude rearward from the fixed block 15 and the thrust plate 51 toward the movable base plate 11a of the movable scroll 11 while being fixed to the inner peripheral portion 150b of the fixed block 15. Here, since the first to fourth fixing holes 151a to 151d are arranged at 90° intervals in the circumferential direction of the drive shaft 5 in the inner peripheral portion 150b, the first to fourth rotation prevention pins 31a to 31d are also arranged at 90° intervals in the circumferential direction of the drive shaft 5.

The first to fourth rotation prevention pins 31a to 31d are inserted into the rings 47, connecting the rings 47 to the first to fourth rotation prevention pins 31a to 31d. In this way, in the rotation prevention mechanism 16, the first to fourth rotation prevention pins 31a to 31d slide and roll on the inner circumferential surfaces of the rings 47, restricting the rotation of the movable scroll 11 and allowing only revolution.

As shown in FIG. 2, the compressor has first to fourth suction passages 55a to 55d in the fixed block 15, as well as a first accommodation groove 57, a second accommodation groove 59, a first seal ring 61, and a second seal ring 63. The first to fourth suction passages 55a to 55d are an example of an "suction passage" in the present invention. The first seal ring 61 is an example of a "first sealing member" in the present invention. And the second seal ring 63 is an example of a "second sealing member" in the present invention.

The first to fourth suction passages 55a to 55d are formed in the outer periphery 150a of the fixed block 15. In other words, the first to fourth suction passages 55a to 55d are arranged outside the drive shaft 5 and the first to fourth rotation prevention pins 31a to 31d in the radial direction of the drive shaft 5. The first to fourth suction passages 55a to 55d are arranged at predetermined intervals in the circumferential direction of the drive shaft 5 and penetrate the fixed block 15 in the front-rear direction. As a result, the first to fourth suction passages 55a to 55d communicate the suction chamber 17 and the suction port 9f. Note that only the first suction passage 55a is shown in Figures 1 and 3. The number of suction passages can be designed as appropriate.

In addition, on the outer circumferential portion 150a, the periphery of the first suction passage 55a is the fifth protruding portion 153a, the periphery of the second suction passage 55b is the sixth protruding portion 153b, the periphery of the third suction passage 55c is the seventh protruding portion 153c, and the periphery of the fourth suction passage 55d is the eighth protruding portion 153d. The fifth to eighth protruding portions 153a to 153d protrude further toward the inner circumferential portion 150b in the radial direction of the drive shaft 5 than other points on the outer circumferential portion 150a.

As shown in FIG. 2, when the first to fourth rotation prevention pins 31a to 31d, the fixed block 15, and the drive shaft 5 are viewed from the rear, imaginary first to fourth reference lines L1 to L4 are defined that linearly connect the drive shaft center O and the centers X1 to X4 of the first to fourth suction passages 55a to 55d in the radial direction of the drive shaft 5. In other words, the first reference line L1 linearly connects the drive shaft center O and the center X1 of the first suction passage 55a in the radial direction of the drive shaft 5, the second reference line L2 linearly connects the drive shaft center O and the center X2 of the second suction passage 55b in the radial direction of the drive shaft 5, the third reference line L3 linearly connects the drive shaft center O and the center X3 of the third suction passage 55c in the radial direction of the drive shaft 5, and the fourth reference line L4 linearly connects the drive shaft center O and the center X4 of the fourth suction passage 55d in the radial direction of the drive shaft 5.

When the first to fourth reference lines L1 to L4 are defined in this manner, the first to fourth rotation prevention pins 31a to 31d are arranged in the fixed block 15 at a distance from the first to fourth reference lines L1 to L4 in the circumferential direction of the drive shaft 5. In other words, the first to fourth fixing holes 151a to 151d are not formed in the inner peripheral portion 150b of the fixed block 15 at positions overlapping the first to fourth reference lines L1 to L4, and the first to fourth rotation prevention pins 31a to 31d are not fixed to the inner peripheral portion 150b at positions overlapping the first to fourth reference lines L1 to L4. More specifically, in the inner peripheral portion 150b, the first rotation prevention pin 31a is located between the first reference line L1 and the second reference line L2. The second rotation prevention pin 31b is located between the second reference line L2 and the third reference line L3. The third rotation prevention pin 31c is located between the third reference line L3 and the fourth reference line L4. The fourth rotation prevention pin 31d is located between the fourth reference line L4 and the first reference line L1.

In this way, in the fixed block 15, the first to fourth suction passages 55a to 55d and the first to fourth rotation prevention pins 31a to 31d are arranged to be offset in the circumferential direction of the drive shaft 5. Similarly, the fifth to eighth protruding portions 153a to 153d and the first to fourth protruding portions 152a to 152d are also arranged to be offset in the circumferential direction of the drive shaft 5.

The first accommodating groove 57 and the second accommodating groove 59 are disposed within the recess 53. As a result, the first accommodating groove 57 and the second accommodating groove 59 are both disposed outside the drive shaft 5 and inside the first to fourth suction passages 55a to 55d. More specifically, the first accommodating groove 57 is disposed outside the first to fourth rotation prevention pins 31a to 31d, and therefore outside the inner periphery 150b. And the second accommodating groove 59 is disposed outside the first accommodating groove 57.

As shown in FIG. 3, the first accommodating groove 57 and the second accommodating groove 59 are each recessed forward from the recess 53. Also, as shown in FIG. 2, the first accommodating groove 57 is formed in a substantially annular shape centered on the drive shaft center O, and surrounds the inner periphery 150b and the drive shaft 5 from the outside. The second accommodating groove 59 has a larger diameter than the first accommodating groove 57, and is formed in a substantially annular shape centered on the drive shaft center O. The second accommodating groove 59 surrounds the first accommodating groove 57, the inner periphery 150b, and the drive shaft 5 from the outside.

The first housing groove 57 is composed of four first protrusions 57a-57d and four first connection parts 57e-57h. Each of the first protrusions 57a-57d is located outside the first to fourth protrusions 152a-152d on the inner periphery 150b, that is, outside the first to fourth rotation prevention pins 31a-31d.

The first connection portion 57e is located between the first protrusion 57a and the first protrusion 57b. The first connection portion 57e extends in an arc shape and connects to the first protrusion 57a and the first protrusion 57b. The first connection portion 57f is located between the first protrusion 57b and the first protrusion 57c. The first connection portion 57f extends in an arc shape and connects to the first protrusion 57b and the first protrusion 57c. The first connection portion 57g is located between the first protrusion 57c and the first protrusion 57d. The first connection portion 57g extends in an arc shape and connects to the first protrusion 57c and the first protrusion 57d. The first connection portion 57h is located between the first protrusion 57d and the first protrusion 57a. The first connection portion 57h extends in an arc shape and connects to the first protrusion portion 57d and the first protrusion portion 57a.

In the first housing groove 57, the first protrusions 57a to 57d protrude radially of the drive shaft 5 toward the second housing groove 59 so as to avoid the first to fourth rotation prevention pins 31a to 31d and the first to fourth protruding portions 152a to 152d. In other words, the first protrusions 57a to 57d protrude outward further than the first connection portions 57e to 57h.

The second housing groove 59 is composed of four second protrusions 59a-59d and four second connection parts 59e-59h. Each of the second protrusions 59a-59d is disposed inside the first to fourth suction passages 55a-55d, and therefore inside the fifth to eighth protrusions 153a-153d on the outer periphery 150a.

The second connection portion 59e is located between the second protrusion 59a and the second protrusion 59b. The second connection portion 59e extends in an arc shape and connects to the second protrusion 59a and the second protrusion 59b. The second connection portion 59f is located between the second protrusion 59b and the second protrusion 59c. The second connection portion 59f extends in an arc shape and connects to the second protrusion 59b and the second protrusion 59c. The second connection portion 59g is located between the second protrusion 59c and the second protrusion 59d. The second connection portion 59g extends in an arc shape and connects to the second protrusion 59c and the second protrusion 59d. The second connection portion 59h is located between the second protrusion 59d and the second protrusion 59a. The second connection portion 59h extends in an arc shape and connects to the second protrusion portion 59d and the second protrusion portion 59a.

In the second housing groove 59, the second protrusions 59a-59d protrude in an arc shape in the radial direction of the drive shaft 5 toward the first housing groove 57 so as to avoid the first to fourth suction passages 55a-55d and the fifth to eighth protrusions 153a-153d. In other words, the second protrusions 59a-59d protrude inward more than the second connection portions 59e-59h.

As shown in FIG. 3, the first seal ring 61 and the second seal ring 63 are both made of resin and are elastically deformable. As shown in FIG. 4, the first seal ring 61 is formed in a shape corresponding to the first housing groove 57, and is substantially annular with the drive shaft center O as its center. The first seal ring 61 is composed of four third protrusions 61a-61d and four third connection portions 61e-61h. Each of the third protrusions 61a-61d is disposed at a position corresponding to each of the first protrusions 57a-57d of the first housing groove 57.

The third connection parts 61e to 61h are disposed at positions corresponding to the first connection parts 57e to 57e of the first housing groove 57. Specifically, the third connection part 61e is located between the third protrusion 61a and the third protrusion 61b, and is connected to the third protrusion 61a and the third protrusion 61b. The third connection part 61f is located between the third protrusion 61b and the third protrusion 61c, and is connected to the third protrusion 61b and the third protrusion 61c. The third connection part 61g is located between the third protrusion 61c and the third protrusion 61d, and is connected to the third protrusion 61c and the third protrusion 61d. The third connection part 61h is located between the third protrusion 61d and the third protrusion 61a, and is connected to the third protrusion 61d and the third protrusion 61a.

In the first seal ring 61, the third protrusions 61a to 61d protrude radially of the drive shaft 5 toward the second accommodating groove 59 along the first protrusions 57a to 57d of the first accommodating groove 57. In other words, the third protrusions 61a to 61d protrude outward more than the third connecting portions 61e to 61h. Meanwhile, the third connecting portions 61e to 61h form an arc shape that follows the first connecting portions 57e to 57h of the first accommodating groove 57.

As shown in FIG. 5, the second seal ring 63 is formed in a shape corresponding to the second housing groove 59, and is generally annular with the drive shaft center O as its center. The second seal ring 63 is formed with a larger diameter than the first seal ring 61. The second seal ring 63 is composed of four fourth protrusions 63a-63d and four fourth connection portions 63e-63h. Each of the fourth protrusions 63a-63d is disposed at a position corresponding to each of the second protrusions 59a-59d of the second housing groove 59.

The fourth connection parts 63e to 63h are disposed at positions corresponding to the second connection parts 59e to 59h of the second housing groove 59, respectively. Specifically, the fourth connection part 63e is located between the fourth protrusions 63a and 63b, and is connected to the fourth protrusions 63a and 63b. The fourth connection part 63f is located between the fourth protrusions 63b and 63c, and is connected to the fourth protrusions 63b and 63c. The fourth connection part 63g is located between the fourth protrusions 63c and 63d, and is connected to the fourth protrusions 63c and 63d. The fourth connection part 63h is located between the fourth protrusions 63d and 63a, and is connected to the fourth protrusions 63d and 63a.

In the second seal ring 63, the fourth protrusions 63a to 63d protrude in an arc shape in the radial direction of the drive shaft 5 toward the first accommodating groove 57 along the second protrusions 59a to 59d of the second accommodating groove 59. In other words, the fourth protrusions 63a to 63d protrude further inward than the fourth connecting portions 63e to 63h. On the other hand, the fourth connecting portions 63e to 63h form an arc shape that follows the second connecting portions 59e to 59h of the second accommodating groove 59.

As shown in FIG. 2, the first seal ring 61 is accommodated in the first accommodating groove 57. At this time, in the first seal ring 61, the third protrusions 61a to 61d are accommodated in the first protrusions 57a to 57d of the first accommodating groove 57, respectively, and the third connection portions 61e to 61h are accommodated in the first connection portions 57e to 57h of the first accommodating groove 57, respectively.

On the other hand, the second seal ring 63 is housed in the second housing groove 59. At this time, in the second seal ring 63, the fourth protrusions 63a to 63d are housed in the second protrusions 59a to 59d of the second housing groove 59, respectively, and the fourth connection parts 63e to 63h are housed in the second connection parts 59e to 59h of the second housing groove 59, respectively.

As described above, in this compressor, the first to fourth rotation prevention pins 31a to 31d are arranged at a distance from the first to fourth reference lines L1 to L4 in the circumferential direction of the drive shaft 5. Therefore, each of the first protrusions 57a to 57d is arranged at a distance from the first to fourth reference lines L1 to L4 in the circumferential direction of the drive shaft 5.

Specifically, the first protrusion 57a is located between the first reference line L1 and the second reference line L2, the first protrusion 57b is located between the second reference line L2 and the third reference line L3, the first protrusion 57c is located between the third reference line L3 and the fourth reference line L4, and the first protrusion 57d is located between the fourth reference line L4 and the first reference line L1.

In contrast, the second protrusion 59a is arranged so as to overlap the first reference line L1, the second protrusion 59b is arranged so as to overlap the second reference line L2, the second protrusion 59c is arranged so as to overlap the third reference line L3, and the second protrusion 59d is arranged so as to overlap the fourth reference line L4.

As a result, in this compressor, when the first to fourth rotation prevention pins 31a to 31d, the fixed block 15, and the drive shaft 5 are viewed from the rear, i.e., from the direction of the drive shaft center O, the first protrusions 57a to 57d of the first accommodating groove 57 and the second protrusions 59a to 59d of the second accommodating groove 59 are arranged offset in the circumferential direction of the drive shaft 5. The first protrusions 57a to 57d face the second connection parts 59e to 59h of the second accommodating groove 59, respectively, in the radial direction of the drive shaft 5. Similarly, the second protrusions 59a to 59d face the first connection parts 57e to 57h of the first accommodating groove 57, respectively, in the radial direction of the drive shaft 5.

In addition, since the first protrusions 57a-57d and the second protrusions 59a-59d of the second housing groove 59 are arranged with a circumferential offset, the third protrusions 61a-61d housed in the first protrusions 57a-57d and the fourth protrusions 63a-63d housed in the second protrusions 59a-59d are also arranged with a circumferential offset.

As shown in FIG. 3, the first seal ring 61 housed in the first housing groove 57 comes into contact with the thrust plate 51 while elastically deforming. Similarly, the second seal ring 63 housed in the second housing groove 59 comes into contact with the thrust plate 51 while elastically deforming. Thus, in the recess 53, the first seal ring 61, the second seal ring 63, and the thrust plate 51 form a back pressure chamber 65. In other words, the back pressure chamber 65 is formed in a substantially annular shape on the outside of the drive shaft 5 and is located in front of the movable base plate 11a of the movable scroll 11 across the thrust plate 51. The back pressure chamber 65 also communicates with the third air supply passage 11f through the communication hole 51a of the thrust plate 51.

In this compressor, the electric motor 7 is operated under the control of an inverter, causing the drive shaft 5 to rotate around the drive axis O. This causes the movable scroll 11 to rotate, causing the movable base plate 11a to slide over the tip of the fixed spiral wall 9c, and causing the fixed spiral wall 9c and the movable spiral wall 11b to slide against each other. At this time, the rotation prevention mechanism 16 restricts the rotation of the movable scroll 11, and the movable scroll 11 only revolves. In this way, as the movable scroll 11 rotates, the refrigerant gas in the suction chamber 17 flows through the first to fourth suction passages 55a to 55d to the suction port 9f, and is sucked into the compression chamber 49 from the suction port 9f. The compression chamber 49 then compresses the refrigerant gas inside while reducing its volume as the movable scroll 11 rotates.

The high-pressure refrigerant gas compressed in the compression chamber 49 is discharged from the discharge port 9e into the discharge chamber 35, and then passes from the discharge chamber 35 through the discharge passage 14e to the oil separation chamber 14c. This high-pressure refrigerant gas then flows through the inside of the separation tube 21, separating the lubricating oil as it circulates between the outer circumferential surface 21a of the separation tube 21 and the inner circumferential surface 140 of the oil separation chamber 14c, and is discharged from the discharge opening 14f.

Meanwhile, the lubricating oil separated from the refrigerant gas is stored in the oil separation chamber 14c. This lubricating oil then passes through the filter 23 and flows through the oil supply passage 43, where it is supplied to the sliding points between the fixed scroll 9 and the movable scroll 11, lubricating the sliding points between the fixed scroll 9 and the movable scroll 11. The lubricating oil flowing through the oil supply passage 43 is also supplied between the second radial bearing 27 and the drive shaft 5, as well as into the suction chamber 17, etc.

In addition, a portion of the high-pressure refrigerant gas compressed in the compression chamber 49 flows through the first supply passage 11d, the second supply passage 11e, the third supply passage 11f, and the communication hole 51a and is supplied to the back pressure chamber 65. This increases the pressure in the back pressure chamber 65. As a result, the movable scroll 11 is urged toward the compression chamber 49 by the pressure in the back pressure chamber 65 through the thrust plate 51. The movable scroll 11 is also urged toward the compression chamber 49 by the elastic force of the thrust plate 51. In this way, in this compressor, the movable scroll 11 is prevented from rotating in an inclined state with respect to the drive axis O.

In this compressor, the back pressure chamber 65 is made large, which allows the movable scroll 11 to be biased toward the compression chamber 49 by the large pressure-receiving area. In addition, in this compressor, variations in the pressure-receiving area due to the phase of the movable scroll 11 and the back pressure chamber 65 during operation are less likely to occur. These actions will be explained in detail in comparison with a compressor of a comparative example.

As shown in FIG. 6, in the compressor of the comparative example, first to fourth suction passages 54a to 54d are formed in the fixed block 15, and the first to fourth suction passages 54a to 54d are arranged at 90° intervals in the circumferential direction of the drive shaft 5 on the outer periphery 150a of the fixed block 15. In addition, fifth to eighth protruding portions 153a to 153d are also arranged at 90° intervals in the circumferential direction of the drive shaft 5 corresponding to the first to fourth suction passages 54a to 54d.

In the compressor of the comparative example, a first accommodation groove 56 and a second accommodation groove 58 are recessed in the recess 53 of the fixed block 15. The first accommodation groove 56 is composed of four first protrusions 56a to 56d and four first connection portions 56e to 56h. The second accommodation groove 58 is composed of four second protrusions 58a to 58d and four second connection portions 58e to 58h. The first protrusions 56a to 56d protrude in the radial direction of the drive shaft 5 toward the second accommodation groove 58, and the second protrusions 58a to 58d protrude in the radial direction of the drive shaft 5 toward the first accommodation groove 56.

In the compressor of the comparative example, a first seal ring 60 is accommodated in the first accommodation groove 56, and a second seal ring 62 is accommodated in the second accommodation groove 58. The first seal ring 60 is composed of four third protrusions 60a to 60d accommodated in the first protrusions 56a to 56d, and four third connection parts 60e to 60h accommodated in the first connection parts 56e to 56h. The second seal ring 62 is composed of four fourth protrusions 62a to 62d accommodated in the second protrusions 58a to 58d, and four fourth connection parts 62e to 62h accommodated in the second connection parts 58e to 58h.

As with the compressor of the embodiment, the compressor of the comparative example also defines imaginary first to fourth reference lines L1 to L4 that linearly connect the drive shaft center O and the centers X1 to X4 of the first to fourth suction passages 54a to 54d in the radial direction of the drive shaft 5 when looking at the first to fourth rotation prevention pins 31a to 31d, the fixed block 15, and the drive shaft 5 from the rear.

As a result, in the compressor of the comparative example, the first rotation prevention pin 31a overlaps with the first reference line L1, the second rotation prevention pin 31b overlaps with the second reference line L2, the third rotation prevention pin 31c overlaps with the third reference line L3, and the fourth rotation prevention pin 31d overlaps with the fourth reference line L4.

For this reason, in the compressor of the comparative example, the first protrusion 56a and the second protrusion 58a both overlap with the first reference line L1. Similarly, the first protrusion 56b and the second protrusion 58b both overlap with the second reference line L2, the first protrusion 56c and the second protrusion 58c both overlap with the third reference line L3, and the first protrusion 56d and the second protrusion 58d both overlap with the fourth reference line L4.

In other words, in the radial direction of the drive shaft 5, the first protrusion 56a faces the second protrusion 58a, the first protrusion 56b faces the second protrusion 58b, the first protrusion 56c faces the second protrusion 58c, and the first protrusion 56d faces the second protrusion 58d.

In addition, by accommodating the first seal ring 60 and the second seal ring 62 in the first accommodating groove 56 and the second accommodating groove 58, the third protrusions 60a-60d of the first seal ring 60 and the fourth protrusions 62a-62d of the second seal ring 62 also face each other in the radial direction of the drive shaft 5. The other configurations of the compressor of the comparative example are the same as those of the compressor of the embodiment, and the same components are denoted by the same reference numerals and detailed description of the configurations is omitted.

In this way, in the compressor of the comparative example, the first protrusions 56a to 56d and the second protrusions 58a to 58d face each other in the radial direction of the drive shaft 5, so that the first protrusions 56a to 56d and the second protrusions 58a to 58d approach each other in the radial direction of the drive shaft 5. In addition, the first seal ring 60 and the second seal ring 62 are housed in the first housing groove 56 and the second housing groove 58, so that the third protrusions 60a to 60d and the fourth protrusions 62a to 62d also approach each other in the radial direction of the drive shaft 5.

For these reasons, in the compressor of the comparative example, as shown by the dashed line, in the back pressure chamber 65, the first portion S1 located between the first protrusion 56a and the third protrusion 60a and the second protrusion 58a and the fourth protrusion 62a is narrowed. Similarly, in the back pressure chamber 65, the second portion S2 located between the first protrusion 56b and the third protrusion 60b and the second protrusion 58b and the fourth protrusion 62b is narrowed. Furthermore, in the back pressure chamber 65, the third portion S3 located between the first protrusion 56c and the third protrusion 60c and the second protrusion 58c and the fourth protrusion 62c is narrowed. And, in the back pressure chamber 65, the fourth portion S4 located between the first protrusion 56d and the third protrusion 60d and the second protrusion 58d and the fourth protrusion 62d is narrowed. Thus, in the compressor of the comparative example, the back pressure chamber 65 cannot be made sufficiently large due to the presence of the first to fourth sections S1 to S4.

In addition, because the first to fourth portions S1 to S4 are narrowed, in the compressor of the comparative example, the first to fourth portions S1 to S4 have a smaller pressure-receiving area for biasing the movable scroll 11 than other portions in the back pressure chamber 65. As a result, in the compressor of the comparative example, the pressure-receiving area is likely to vary depending on the phase of the movable scroll 11 and the back pressure chamber 65 during operation. For this reason, in the compressor of the comparative example, it is difficult to favorably bias the movable scroll 11 toward the compression chamber 49 by the pressure in the back pressure chamber 65. As a result, in the compressor of the comparative example, the movable scroll 11 cannot be sufficiently prevented from rotating in a state inclined with respect to the drive axis O, and leakage of refrigerant gas from within the compression chamber 49 cannot be sufficiently prevented. In addition, in the compressor of the comparative example, the discharge pulsation increases due to leakage of refrigerant gas from within the compression chamber 49, and noise also increases.

In addition, in the compressor of the comparative example, if it is desired to separate the first protrusions 56a-56d and the second protrusions 58a-58d in the radial direction of the drive shaft 5 so that the first to fourth sections S1-S4 do not become narrow, it is necessary to increase the size of the fixed block 15 and, by extension, the housing 1 in the radial direction of the drive shaft 5 accordingly.

In contrast, in the compressor of the embodiment, as shown in FIG. 2, the first to fourth rotation prevention pins 31a to 31d are positioned away from the first to fourth reference lines L1 to L4 in the circumferential direction of the drive shaft 5. In other words, the first to fourth suction passages 55a to 55d and the first to fourth rotation prevention pins 31a to 31d are offset in the circumferential direction of the drive shaft 5.

For this reason, in the compressor of the embodiment, the first protrusions 57a-57d and the second protrusions 59a-59d are arranged in a circumferentially offset manner in the first and second accommodating grooves 57 and 59, respectively. In addition, in the compressor of the embodiment, when the first seal ring 61 and the second seal ring 63 are accommodated in the first and second accommodating grooves 57 and 59, respectively, the third protrusions 61a-61d of the first seal ring 61 and the fourth protrusions 63a-63d of the second seal ring 63 are also arranged in a circumferentially offset manner in the drive shaft 5.

For these reasons, in the compressor of the embodiment, in the back pressure chamber 65, the first protrusion 57a and the third protrusion 61a can be suitably separated from the second protrusion 59a and the fourth protrusion 63a in the radial direction of the drive shaft 5. Similarly, the first protrusion 57b and the third protrusion 61b can be suitably separated from the second protrusion 59b and the fourth protrusion 63b in the radial direction of the drive shaft 5. In addition, the first protrusion 57c and the third protrusion 61c can be suitably separated from the second protrusion 59c and the fourth protrusion 63c in the radial direction of the drive shaft 5. In addition, the first protrusion 57d and the third protrusion 61d can be suitably separated from the second protrusion 59d and the fourth protrusion 63d in the radial direction of the drive shaft 5. In other words, in the compressor of the embodiment, unlike the first to fourth portions S1 to S4 in the compressor of the comparative example, the back pressure chamber 65 is less likely to have a narrow portion in the radial direction of the drive shaft 5. In this way, in the compressor of the embodiment, it is possible to ensure that the back pressure chamber 65 is large overall.

As a result, in the compressor of the embodiment, the movable scroll 11 can be biased toward the compression chamber 49 side by the large pressure-receiving area. In addition, in the compressor of the embodiment, the variation in the pressure-receiving area due to the phase of the movable scroll 11 and the back pressure chamber 65 during operation is less likely to occur. Therefore, in the compressor of the embodiment, the movable scroll 11 can be suitably biased toward the compression chamber 49 side by the pressure in the back pressure chamber 65. As a result, in the compressor of the embodiment, the movable scroll 11 can be suitably prevented from rotating in a state inclined with respect to the drive axis O, and the leakage of refrigerant gas from the compression chamber 49 can be suitably prevented. In addition, in the compressor of the embodiment, discharge pulsation can also be suitably suppressed.

In addition, as described above, since the back pressure chamber 65 can be made large, in the compressor of the embodiment, there is no need to make the fixed block 15 excessively large to ensure the back pressure chamber 65.

The compressor of the embodiment therefore has excellent compression efficiency and quietness, and can be made compact.

In particular, in this compressor, the first seal ring 61 has four third protrusions 61a to 61d, each of which protrudes in the radial direction of the drive shaft 5 along the first protrusions 57a to 57d of the first accommodating groove 57. In addition, the second seal ring 63 has four fourth protrusions 63a to 63d, each of which protrudes in the radial direction of the drive shaft 5 along the second protrusions 59a to 59d of the second accommodating groove 59.

As a result, in this compressor, when the first seal ring 61 is accommodated in the first accommodation groove 57, the first seal ring 61 is prevented from bending excessively by the first protrusions 57a to 57d. Similarly, when the second seal ring 63 is accommodated in the second accommodation groove 59, the second seal ring 63 is prevented from bending excessively by the second protrusions 59a to 59d. As a result, in this compressor, the back pressure chamber 65 can be sealed appropriately by the first seal ring 61 and the second seal ring 63, making it difficult for refrigerant gas to leak from the back pressure chamber 65.

In addition, in this compressor, a thrust plate 51 is provided between the fixed block 15 and the movable scroll 11, so that the first seal ring 61, the second seal ring 63, and the thrust plate 51 can favorably form a back pressure chamber 65. In addition, by using the thrust plate 51, the pressure of the back pressure chamber 65 can favorably urge the movable scroll 11 toward the compression chamber 49. Furthermore, the elastic force of the thrust plate 51 can also favorably urge the movable scroll 11 toward the compression chamber 49. In this respect, too, in this compressor, the movable scroll 11 can be favorably prevented from rotating in a state inclined with respect to the drive axis O.

In addition, in this compressor, the first accommodation groove 57 has the first protrusions 57a to 57d, and the second accommodation groove 59 has the second protrusions 59a to 59d. Therefore, for the first accommodation groove 57, it is possible to bring the first accommodation groove 57 as close as possible to the first to fourth rotation prevention pins 31a to 31d in the radial direction of the drive shaft 5 while avoiding the first to fourth rotation prevention pins 31a to 31d. Similarly, for the second accommodation groove 59, it is possible to bring the second accommodation groove 59 as close as possible to the first to fourth suction passages 55a to 55d in the radial direction of the drive shaft 5 while avoiding the first to fourth suction passages 55a to 55d. As a result, the first accommodation groove 57 and the second accommodation groove 59 can be suitably separated in the radial direction of the drive shaft 5. In this respect, too, in this compressor, it is possible to ensure a large back pressure chamber 65.

In addition, in this compressor, the first protrusions 57a-57d and the second protrusions 59a-59d of the second accommodating groove 59 are offset in the circumferential direction of the drive shaft 5, so that when the first accommodating groove 57 and the second accommodating groove 59 are formed in the fixed block 15, the first protrusions 57a-57d and the second protrusions 59a-59d are preferably prevented from being inadvertently connected in the radial direction of the drive shaft 5. Therefore, in this compressor, there is no need to require excessively high precision when forming the first accommodating groove 57 and the second accommodating groove 59, and the first accommodating groove 57 and the second accommodating groove 59 can be easily formed.

Although the present invention has been described above with reference to examples, it goes without saying that the present invention is not limited to the above examples and can be modified as appropriate without departing from the spirit of the invention.

For example, in the compressor of the embodiment, a dedicated exhaust port for discharging the refrigerant gas in the back pressure chamber 65 may be formed in the fixed plate 15 or the thrust plate 51.

In addition, instead of the first to third supply passages 1e to 11f and the communication hole 51a, a supply passage that supplies refrigerant gas in the compression chamber 49 to the back pressure chamber 65 may be formed in the fixed plate 15.

In addition, in the compressor of the embodiment, the thrust plate 51 may be omitted.

In addition, in the compressor of the embodiment, the rotation prevention mechanism 16 is made up of four rings 47 and the first to fourth rotation prevention pins 31a to 31d, but this is not limited thereto, and the rotation prevention mechanism 16 may have a different configuration.

Furthermore, the third protrusions 61a to 61d may be omitted from the first seal ring 61. Similarly, the fourth protrusions 63a to 63d may be omitted from the second seal ring 63.

In addition, in the compressor of the embodiment, the refrigerant gas as a fluid is compressed in the compression chamber 49, but this is not limited thereto, and a fluid such as air to be supplied to the fuel cell may also be compressed in the compression chamber 49.

The present invention can be used in air conditioning systems for vehicles, etc.

1...Housing 5...Drive shaft 9...Fixed scroll 11...Moving scroll 15...Fixed block 16...Rotation prevention mechanism 17...Suction chamber 49...Compression chamber 51...Thrust plate 55a to 55d...First to fourth suction passages (suction passages)
57: First accommodating groove 57a to 57d: First protrusion 59: Second accommodating groove 59a to 59d: Second protrusion 61: First seal ring (first sealing member)
61a to 61d...Third protrusion 63...Second seal ring (second sealing member)
63a to 63d...Fourth protrusion 65...Back pressure chamber O...Drive shaft center

Claims (3)

a housing having a suction chamber into which a fluid is drawn;
a drive shaft provided within the housing and rotatable about a drive shaft center;
a fixed scroll fixed within the housing;
a movable scroll provided in the housing, rotating together with the drive shaft and defining a compression chamber for compressing a fluid between the movable scroll and the fixed scroll,
the housing is located between the suction chamber and the movable scroll and has a fixed block through which the drive shaft is rotatably inserted,
The movable scroll and the fixed block are connected by a rotation prevention mechanism that prevents the movable scroll from rotating.
the fixed block has an intake passage disposed radially outward of the drive shaft and the rotation prevention mechanism, the intake passage allowing the fluid in the intake chamber to flow to the compression chamber;
a first accommodating groove that is located outside the rotation prevention mechanism in the radial direction and that is formed in an annular shape surrounding the drive shaft;
a second accommodating groove formed in an annular shape surrounding the drive shaft and located between the first accommodating groove and the suction passage in the radial direction;
a first sealing member formed in an annular shape and accommodated in the first accommodating groove;
a second sealing member that is formed in an annular shape and accommodated in the second accommodating groove, and that, together with the first sealing member, forms a back pressure chamber that urges the movable scroll toward the compression chamber,
the first accommodating groove has a first protruding portion that protrudes in the radial direction toward the second accommodating groove so as to avoid the rotation prevention mechanism,
the second accommodating groove has a second protruding portion protruding in the radial direction toward the first accommodating groove so as to avoid the suction passage,
The scroll compressor, wherein the first protrusion and the second protrusion are arranged to be shifted from each other in a circumferential direction of the drive shaft. the first sealing member has a third protruding portion protruding in the radial direction along the first protruding portion,
The scroll compressor according to claim 1 , wherein the second sealing member has a fourth protruding portion that protrudes in the radial direction along the second protruding portion. The scroll compressor according to claim 1 or 2, wherein a thrust plate is provided between the movable scroll and the fixed block, and the thrust plate forms the back pressure chamber together with the first sealing member and the second sealing member.

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