SPIRAL COMPRESSOR

Abstract

A scroll compressor (10) has a housing (11); a rotating shaft (15) rotatably mounted on the housing (11); a stationary scroll (25) with a stationary scroll base plate (25a), a stationary scroll wall (25b), and a stationary scroll circumferential wall (25c); a rotating scroll (26) with a rotating scroll base plate (26a) and a rotating scroll wall (26b); and an elastic plate (30). The stationary scroll circumferential wall (25c) has a plurality of thick-walled sections (50) spaced apart from one another in the circumferential direction of the stationary scroll circumferential wall (25c).A groove (55) is formed in at least one of the end faces of the plurality of thick-walled sections (50) facing the elastic plate (30) and accommodates elastic deformation of the elastic plate (30), so that a counter-pressure chamber (45) and an inlet channel (35) communicate with each other when a pressure difference between the counter-pressure chamber (45) and the inlet channel (35) exceeds a predetermined value.

Description

Background of the invention: Technical field

[0001] The present invention relates to a spiral compressor. State of the art

[0002] Japanese patent application JP 2022-149824 discloses a spiral compressor comprising a housing, a rotating shaft, a stationary spiral, a rotating spiral, and an elastic plate. The rotating shaft is rotatably mounted in the housing. The stationary spiral has a stationary spiral base plate, a stationary spiral wall, and a stationary spiral circumferential wall. The stationary spiral wall extends from the stationary spiral base plate and surrounds the stationary spiral wall. The rotating spiral has a rotating spiral base plate and a rotating spiral wall. The rotating spiral base plate faces the stationary spiral base plate.The rotating spiral wall extends from the rotating spiral base plate towards the stationary spiral base plate and engages with the stationary spiral wall. A compression chamber for compressing coolant is defined by the stationary spiral base plate, the stationary spiral wall, the rotating spiral base plate, and the rotating spiral wall. The rotating spiral executes a circular motion within the stationary spiral circumferential wall when the rotating shaft rotates. The elastic plate presses the rotating spiral towards the stationary spiral.

[0003] The housing comprises a shaft bearing housing, an outlet housing, and an intake housing. The shaft bearing housing is located on one side of the rotating spiral base plate, opposite the stationary spiral base plate. The shaft bearing housing supports the rotating shaft. The outlet housing has an end wall and a circumferential wall. The circumferential wall extends from the end wall into a tube shape and surrounds the stationary spiral circumferential wall. The outlet housing defines an outlet chamber between the end wall and the stationary spiral base plate. Coolant compressed in the compression chamber is discharged into the outlet chamber. The intake housing and the shaft bearing housing work together to define an intake chamber into which coolant is drawn from the outside.

[0004] An inlet channel is defined between the stationary spiral's circumferential wall and the outlet housing's circumferential wall. Coolant in the intake chamber is drawn into the compression chamber through the inlet channel. A backpressure chamber is defined between the rotating spiral's base plate and the shaft bearing housing. Coolant is introduced into the backpressure chamber to press the rotating spiral towards the stationary spiral. An outer circumferential section of the elastic plate is held between the stationary spiral's circumferential wall and the shaft bearing housing.

[0005] The circumferential wall of the exhaust housing has a plurality of bead sections. These bead sections are spaced apart along the circumference of the wall and project towards the fixed spiral's circumferential wall with a convex inner surface. The exhaust housing is attached to the intake housing by fasteners that extend axially along sections of the circumferential wall corresponding to the bead sections. The fixed spiral is attached to the housing, with its circumferential wall held axially between the end wall of the exhaust housing and the shaft bearing housing by a clamping force exerted by the fasteners.

[0006] The stationary spiral perimeter wall has numerous thick-walled sections and numerous thin-walled sections. The thick-walled sections are spaced apart along the circumference of the stationary spiral perimeter wall. The thin-walled sections have an outer circumferential surface that is recessed in a concave shape between the thick-walled sections, which are adjacent to each other along the circumference of the stationary spiral perimeter wall. This recess allows the bead sections to be positioned, and each thin-walled section has a thickness less than that of each of the thick-walled sections. This configuration allows the spiral compressor to be smaller.

[0007] In this scroll compressor, if the compressor is stopped, the refrigerant can cool and liquefy. For example, if the scroll compressor is started in a state where liquefied refrigerant, produced by liquefaction, is present in the back-pressure chamber, heat can be transferred from the refrigerant compressed in the compression chamber to the liquefied refrigerant in the back-pressure chamber via the rotating scroll base plate. This can cause the liquefied refrigerant in the back-pressure chamber to evaporate, potentially increasing the pressure in the back-pressure chamber excessively. If the pressure in the back-pressure chamber becomes excessive, the pushing force generated by this pressure, which forces the rotating scroll towards the stationary scroll, becomes too great.As a result, it becomes difficult for the rotating spiral to perform a circular motion, and the compression efficiency of the spiral compressor decreases.

[0008] Furthermore, in the aforementioned spiral compressor described in the publication, the thin-walled sections are closer to the beaded sections than the thick-walled sections. The fastening elements extend through sections of the circumferential wall of the outlet housing corresponding to the beaded sections in an axial direction of the circumferential wall. Therefore, a reaction / counterforce from / to the shaft bearing housing, caused by a fastening force of the fastening elements, is more likely to act locally on end faces of the thin-walled sections facing the elastic plate than on end faces of the thick-walled section facing the elastic plate.In this case, if a groove is formed in the end faces of the thin-walled sections facing the elastic plate, these end faces are less likely to receive the reaction / counterforce from the shaft bearing housing caused by the fastening force of the fasteners. Therefore, there is a risk that the fixed spiral's circumferential wall will struggle to withstand the fastening force between the outlet housing's end wall and the shaft bearing housing. If the fixed spiral's strength is reduced in this way, failure, such as deformation of the fixed spiral, can occur. Therefore, it is desirable to suppress excessive pressure buildup in the backpressure chamber while maintaining the fixed spiral's strength. Summary of the invention

[0009] According to one aspect of the present invention, a spiral compressor is provided comprising a housing; a rotating shaft rotatably mounted through the housing; a stationary spiral attached to the housing and comprising a stationary spiral base plate, a stationary spiral wall extending from the stationary spiral base plate, and a stationary spiral perimeter wall extending from the stationary spiral base plate and surrounding the stationary spiral wall;a circumferential spiral with a circumferential spiral base plate facing the stationary spiral base plate, and a circumferential spiral wall extending from the circumferential spiral base plate towards the stationary spiral base plate and engaging with the stationary spiral wall, wherein the circumferential spiral is configured to perform a circumferential motion within the stationary spiral circumferential wall when the rotating shaft is rotated; an elastic plate having a ring shape and configured to push the circumferential spiral towards the stationary spiral;and a compression chamber in which a coolant is compressed and which is defined by the stationary spiral base plate, the stationary spiral spiral wall, the rotating spiral base plate, and the rotating spiral spiral wall. The housing comprises: a shaft bearing housing located on one side of the rotating spiral base plate opposite the stationary spiral base plate, which supports the rotating shaft; an outlet housing comprising an end wall and a circumferential wall extending from the end wall in a tubular form to surround the stationary spiral circumferential wall, and defining an outlet chamber into which the coolant compressed in the compression chamber is discharged between the end wall and the stationary spiral base plate;and an intake housing that interacts with the shaft bearing housing to define an intake chamber into which the coolant is drawn from the outside. The scroll compressor comprises: an inlet channel defined between the stationary scroll circumferential wall and the circumferential wall, through which the coolant in the intake chamber is drawn into the compression chamber; a back pressure chamber defined between the rotating scroll base plate and the shaft bearing housing, into which the coolant is introduced to force the rotating scroll towards the stationary scroll; an outer circumferential section of the elastic plate held between the stationary scroll circumferential wall and the shaft bearing housing;A plurality of bead sections spaced apart in a circumferential direction of the circumferential wall and projecting towards the fixed spiral circumferential wall with an inner circumferential surface of the circumferential wall formed in a convex shape; a fastening element extending through a section of the circumferential wall where the plurality of bead sections are formed in an axial direction of the circumferential wall to fasten the outlet housing to the intake housing; and the fixed spiral, which is attached to the housing, wherein the fixed spiral circumferential wall is held between the end wall and the shaft bearing housing by a fastening force of the fastening element. The fixed spiral circumferential wall comprises: a plurality of thick-walled sections spaced apart in the circumferential direction of the fixed spiral circumferential wall;and a plurality of thin-walled sections, which are formed with an outer circumferential surface of the fixed spiral perimeter wall that is recessed in a concave shape between the plurality of thick-walled sections that are arranged adjacent to each other in the circumferential direction of the fixed spiral perimeter wall, in order to allow the bead sections to be arranged, and which have a thickness that is less than the thickness of each of the plurality of thick-walled sections. A groove is formed in at least one of the end faces of the plurality of thick-walled sections that face the elastic plate, the groove accommodating elastic deformation of the elastic plate so that the counter-pressure chamber and the inlet channel are in (fluid) communication with each other when a pressure difference between a pressure in the counter-pressure chamber and a pressure in the inlet channel exceeds a predetermined value.

[0010] Further aspects and advantages of the invention will become apparent from the following description in conjunction with the accompanying drawings, which illustrate the principles of the invention by way of example. Brief description of the characters

[0011] The invention, together with its tasks and advantages, can best be understood with reference to the following description of the embodiments together with the accompanying drawings, in which: Fig. 1 a cross-sectional view of a spiral compressor according to one embodiment; Fig. 2 is a front view of an outlet housing and a stationary spiral; Fig. 3 is a perspective view of the stationary spiral; Fig. 4 is a partially enlarged cross-sectional view of the spiral compressor; Fig. 5 is an enlarged perspective view of a groove; Fig. 6 is a partially enlarged cross-sectional view of the spiral compressor; Fig. 7 is a cross-sectional view illustrating a condition in which an elastic plate is elastically deformed; and Fig. Figure 8 is a cross-sectional view illustrating a condition in which the elastic plate is elastically deformed. Detailed description of the embodiments

[0012] The following describes an embodiment of a spiral compressor with reference to Fig. 1, Fig. 2, Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7 to Fig. 8 described. The spiral compressor of the present embodiment is used, for example, in a vehicle air conditioning system. Basic configuration of spiral compressor

[0013] As in Fig. As illustrated in Figure 1, a scroll compressor 10 has a housing 11 with a tubular shape. The housing 11 contains an intake housing 12, a shaft bearing housing 13, and an outlet housing 14. The intake housing 12, the shaft bearing housing 13, and the outlet housing 14 are made of metallic materials. For example, the intake housing 12, the shaft bearing housing 13, and the outlet housing 14 are made of aluminum. The scroll compressor 10 has a rotating shaft 15. The rotating shaft 15 is housed in the housing 11.

[0014] The intake housing 12 has an end wall 12a in the shape of a plate and a circumferential wall 12b in the shape of a tube. The circumferential wall 12b extends in a tube shape from an outer circumferential section of the end wall 12a. An axial direction of the circumferential wall 12b coincides with an axial direction of the rotating shaft 15. The intake housing 12 has a plurality of internally threaded bores 12c. Six internally threaded bores 12c are formed in the intake housing 12. The internally threaded bores 12c are formed in an opening end of the circumferential wall 12b. The six internally threaded bores 12c are arranged at regular intervals in one circumferential direction of the circumferential wall 12b. For the purposes of this description, in Fig. Figure 1 illustrates only one of the internal threaded bores 12c. The intake housing 12 has an inlet port 12h through which coolant is drawn in from the outside. The inlet port 12h is formed in the circumferential wall 12b on the side of the end wall 12a. The inlet port 12h provides fluid communication between an inside and an outside of the intake housing 12.

[0015] The intake housing 12 has a hub 12d with a cylindrical shape. The hub 12d projects from a central section of an inner surface of the end wall 12a. A first end of the rotating shaft 15, corresponding to an end of the rotating shaft 15 in the axial direction, is inserted into the hub 12d. The spiral compressor 10 has a bearing 16. The bearing 16 is, for example, a rolling bearing. The bearing 16 is arranged between an inner circumferential surface of the hub 12d and an outer circumferential surface of the first end of the rotating shaft 15. The first end of the rotating shaft 15 is rotatably mounted through the intake housing 12 via the bearing 16.

[0016] The shaft bearing housing 13 has an end wall 17 in a plate shape and a circumferential wall 18 in a tube shape. The circumferential wall 18 projects from an outer circumferential section of the end wall 17 in a tube shape. An axial direction of the circumferential wall 18 coincides with the axial direction of the rotating shaft 15. The shaft bearing housing 13 has a flange wall 19 in an annular shape. The flange wall 19 extends radially along the rotating shaft 15 from one end of an outer circumferential surface of the circumferential wall 18 opposite the end wall 17 outwards.

[0017] The shaft bearing housing 13 has a round-shaped insertion hole 17a. The insertion hole 17a is formed in a central section of the end wall 17. The insertion hole 17a extends through the end wall 17 in the thickness direction of the end wall 17. The rotating shaft 15 is inserted through the insertion hole 17a. An end face 15e of the rotating shaft 15, located at a second end of the rotating shaft 15 corresponding to its other end in the axial direction, is positioned within the circumferential wall 18.

[0018] The spiral compressor 10 has a bearing 21. The bearing 21 is, for example, a rolling bearing. The bearing 21 is arranged between an inner circumferential surface of the circumferential wall 18 and an outer circumferential surface of the rotating shaft 15. The rotating shaft 15 is rotatably mounted via the bearing 21 by the shaft bearing housing 13. Thus, the shaft bearing housing 13 rotatably mounts the rotating shaft 15. Accordingly, the rotating shaft 15 is rotatably mounted by the housing 11.

[0019] The shaft bearing housing 13 has a plurality of screw insertion holes 19a. Six screw insertion holes 19a are formed in the shaft bearing housing 13. The screw insertion holes 19a are formed in an outer circumferential section of the flange wall 19. The six screw insertion holes 19a are arranged at regular intervals in a circumferential direction of the flange wall 19. The screw insertion holes 19a each extend through the flange wall 19 in one thickness direction. The screw insertion holes 19a of the flange wall 19 are in (fluid) communication with their associated internal threaded bores 12c of the intake housing 12. For the purposes of this description, in Fig. 1 only one of the screw insertion holes 19a is illustrated.

[0020] The spiral compressor 10 has an intake chamber 20. The intake chamber 20 is defined by the intake housing 12 and the shaft bearing housing 13. Thus, the intake housing 12 and the shaft bearing housing 13 work together to define the intake chamber 20. In this way, the intake chamber 20 is formed within the housing 11. The intake chamber 20 is in fluid communication with the inlet port 12h. Coolant is drawn into the intake chamber 20 through the inlet port 12h. Therefore, coolant is drawn into the intake chamber 20 from the outside. Thus, the intake chamber 20 is a suction pressure chamber.

[0021] The spiral compressor 10 has a motor 22. The motor 22 is housed in the intake chamber 20. The motor 22 has a tubular stator 23 and a tubular rotor 24. The rotor 24 is located inside the stator 23. The rotor 24 rotates integrally with the rotating shaft 15. The stator 23 surrounds the rotor 24. The rotor 24 has a rotor core 24a attached to the rotating shaft 15, and a plurality of permanent magnets (not illustrated) are arranged in the rotor core 24a.

[0022] The stator 23 has a tubular stator core 23a and a motor coil 23b. The stator core 23a is attached to an inner circumferential surface of the circumferential wall 12b of the intake housing 12. The motor coil 23b is wound onto the stator core 23a. Electrical power controlled by an inverter (not shown) is then supplied to the motor coil 23b, causing the rotor 24 to rotate. Thus, the rotor 24 rotates in unison with the rotating shaft 15. Accordingly, the motor 22 rotates the rotating shaft 15.

[0023] The spiral compressor 10 has a compression mechanism C1. The compression mechanism C1 has a stationary spiral 25 and a rotating spiral 26. Thus, the spiral compressor 10 has the stationary spiral 25 and the rotating spiral 26. The compression mechanism C1 is of the screw type. The rotating spiral 26 performs a rotary motion relative to the stationary spiral 25 when the rotating shaft 15 is turned.

[0024] As in Fig. 1 and Fig. As illustrated in Figure 2, the stationary spiral 25 has a stationary spiral base plate 25a, a stationary spiral wall 25b, and a stationary spiral perimeter wall 25c. The stationary spiral base plate 25a is disc-shaped. An outlet port 25h is formed in the center of the stationary spiral base plate 25a. The outlet port 25h has a round hole shape. The outlet port 25h extends through the stationary spiral base plate 25a in one direction of its thickness. The stationary spiral wall 25b extends from the stationary spiral base plate 25a. The stationary spiral perimeter wall 25c extends from an outer circumferential section of the stationary spiral base plate 25a. The fixed spiral perimeter wall 25c surrounds the fixed spiral spiral wall 25b.

[0025] As in Fig. As illustrated in Figure 1, the scroll compressor 10 has a valve mechanism 25v. The valve mechanism 25v is mounted on an end face of the stationary spiral base plate 25a opposite the stationary spiral spiral wall 25b. The valve mechanism 25v is configured to open or close the outlet port 25h.

[0026] The circumferential spiral 26 has a circumferential spiral base plate 26a and a circumferential spiral wall 26b. The circumferential spiral base plate 26a is disc-shaped. The circumferential spiral base plate 26a faces the stationary spiral base plate 25a. The circumferential spiral wall 26b extends from the circumferential spiral base plate 26a towards the stationary spiral base plate 25a. The circumferential spiral wall 26b engages with the stationary spiral wall 25b. The circumferential spiral 26 is arranged within the stationary spiral perimeter wall 25c. The circumferential spiral 26 performs a circumferential movement within the stationary spiral perimeter wall 25c. A distal end face of the stationary spiral wall 25b is in contact with the circumferential spiral base plate 26a. A distal end face of the circumferential spiral wall 26b is in contact with the stationary spiral base plate 25a.

[0027] The spiral compressor 10 has a compression chamber 27. The compression chamber 27 is defined by the stationary spiral base plate 25a, the stationary spiral wall 25b, the rotating spiral base plate 26a, and the rotating spiral wall 26b. Thus, the compression chamber 27 is defined between the stationary spiral 25 and the rotating spiral 26. Coolant from the outside is drawn into the compression chamber 27 and compressed therein.

[0028] The rotating spiral base plate 26a has a cylindrical hub 26c. The hub 26c projects from an end face 26e of the rotating spiral base plate 26a towards an inner side of the circumferential wall 18 of the shaft bearing housing 13, opposite the stationary spiral base plate 25a. The shaft bearing housing 13 is located on one side of the rotating spiral base plate 26a opposite the stationary spiral base plate 25a. An axial direction of the hub 26c coincides with the axial direction of the rotating shaft 15. The rotating spiral base plate 26a has a plurality of grooves 26d. The grooves 26d are formed in the end face 26e of the rotating spiral base plate 26a around the hub 26c. The grooves 26d are arranged at predetermined intervals in a circumferential direction of the rotating shaft 15. For the purposes of the description, in Fig. Figure 1 illustrates only one of the grooves 26d. Ring elements 28, each with a ring shape, are fitted into the grooves 26d. Pins 29 are each inserted into their corresponding ring element 28. The pins 29 protrude from an end face 13e of the shaft bearing housing 13 on the side of the circumferential spiral 26.

[0029] The spiral compressor 10 has an elastic plate 30. The elastic plate 30 is ring-shaped. An outer circumferential section of the elastic plate 30 is held between an open end face of the stationary spiral circumferential wall 25c and the end faces 13e of the shaft bearing housing 13. The elastic plate 30 constantly presses the rotating spiral 26 in the direction of the stationary spiral 25.

[0030] The spiral compressor 10 has an eccentric shaft 31. The eccentric shaft 31 extends from the end face 15e of the rotating shaft 15 at a position that is eccentric to an axial line L1 of the rotating shaft 15 in the direction of the rotating spiral 26. The eccentric shaft 31 is formed integrally with the rotating shaft 15. An axial direction of the eccentric shaft 31 coincides with the axial direction of the rotating shaft 15. The eccentric shaft 31 is inserted into the hub 26c.

[0031] The spiral compressor 10 has a counterweight 32 and a bushing 33. The bushing 33 is fitted onto an outer circumferential surface of the eccentric shaft 31. The counterweight 32 is integrated with the bushing 33. The counterweight 32 and the bushing 33 are formed integrally. The counterweight 32 is received in the circumferential wall 18 of the shaft bearing housing 13. The rotating spiral 26 is supported by the eccentric shaft 31 via the bushing 33 and a rolling bearing 34 and is rotatable relative to the eccentric shaft 31.

[0032] The rotation of the rotating shaft 15 is transmitted to the rotating spiral 26 via the eccentric shaft 31, the bushing 33, and the rolling bearing 34. This sets the rotating spiral 26 into rotation. The pins 29, in contact with the inner circumferential surfaces of their associated ring elements 28, prevent the rotating spiral 26 from rotating and allow it only to perform a circular motion. Thus, the rotating spiral 26 performs the circular motion while the rotating spiral wall 26b is in contact with the stationary spiral wall 25b. The volume of the compression chamber 27 decreases during the circular motion of the rotating spiral 26, thereby compressing the coolant in the compression chamber 27. The circumferential spiral 26 performs the circumferential movement within the stationary spiral circumferential wall 25c when the rotating shaft 15 is rotated.The counterweight 32 compensates for a centrifugal force acting on the rotating spiral 26 when the rotating spiral 26 performs its rotational movement. This reduces the imbalance of the rotating spiral 26.

[0033] As in Fig. 1 and Fig. As illustrated in Figure 2, the outlet housing 14 has an end wall 14a with a plate shape and a circumferential wall 14b with a tube shape. The circumferential wall 14b extends in a tube shape from / of an outer circumferential section of the end wall 14a. An axial direction of the circumferential wall 14b coincides with the axial direction of the rotating shaft 15. The circumferential wall 14b surrounds the stationary spiral circumferential wall 25c. Thus, the circumferential wall 14b surrounds the stationary spiral 25. Accordingly, the stationary spiral 25 is accommodated in the housing 11.

[0034] As in Fig. As illustrated in Figure 2, the circumferential wall 14b has a plurality of bead sections 14d. The circumferential wall 14b has six bead sections 14d. The six bead sections 14d are arranged at regular intervals along one circumferential direction of the circumferential wall 14b. In this way, the six bead sections 14d are spaced apart from each other along the circumferential direction of the circumferential wall 14b. Each bead section 14d projects towards the direction of the fixed spiral circumferential wall 25c with an inner circumferential surface of the circumferential wall 14b that is formed in a convex shape. An outer surface of each bead section 14d is a curved surface that is curved in an arc shape that is convex in the direction of the fixed spiral circumferential wall 25c.

[0035] As in Fig. 1 and Fig. As illustrated in Figure 2, the outlet housing 14 has a plurality of screw insertion holes 14c. Six screw insertion holes 14c are formed in the outlet housing 14. The screw insertion holes 14c extend through sections of the circumferential wall 14b, corresponding to the bead sections 14d, in an axial direction of the circumferential wall 14b. For the purposes of this description, in Fig. Figure 1 illustrates only one of the screw insertion holes 14c. The screw insertion holes 14c are in (fluid) communication with the corresponding screw insertion holes 19a of the flange wall 19.

[0036] As in Fig. As illustrated in Figure 1, screws B1, extending through the screw holes 14c, are inserted through the screw holes 19a of the flange wall 19 and screwed into the internal threaded bores 12c of the intake housing 12. Consequently, the shaft bearing housing 13 is connected to the circumferential wall 12b of the intake housing 12; and the exhaust housing 14 is connected to the circumferential wall 12b of the intake housing 12 via the flange wall 19 of the shaft bearing housing 13. In this way, the exhaust housing 14 is fastened to the intake housing 12 by the screws B1, which extend through the sections of the circumferential wall 14b corresponding to the bead sections 14d in the axial direction of the circumferential wall 14b. The intake housing 12, the shaft bearing housing 13 and the exhaust housing 14 are arranged in this order in the axial direction of the rotating shaft 15.The flange wall 19 of the shaft bearing housing 13 is held between the circumferential wall 14b of the outlet housing 14 and the circumferential wall 12b of the intake housing 12.

[0037] The fixed spiral circumferential wall 25c of the fixed spiral 25 is held between the end wall 14a of the outlet housing 14 and the shaft bearing housing 13 in the axial direction of the circumferential wall 14b by an axial force, which is a fastening force of the screws B1. In this way, the fixed spiral 25 is attached to the housing 11, with the fixed spiral circumferential wall 25c being held between the end wall 14a of the outlet housing 14 and the shaft bearing housing 13 in the axial direction of the circumferential wall 14b by the fastening force of the screws B1.

[0038] The spiral compressor 10 has an outlet chamber 40. The outlet chamber 40 is defined between the end wall 14a of the outlet housing 14 and the stationary spiral base plate 25a. Thus, the outlet housing 14 defines the outlet chamber 40 between the end wall 14a and the stationary spiral base plate 25a. Coolant compressed in the compression chamber 27 is discharged into the outlet chamber 40 through the outlet port 25h. A seal 41 seals a section between the end wall 14a of the outlet housing 14 and the stationary spiral base plate 25a, and around the outlet chamber 40.

[0039] The outlet housing 14 has an outlet port 14h. The outlet port 14h is formed in the end wall 14a of the outlet housing 14. The outlet port 14h is in (fluid) communication with the outlet chamber 40. The outlet port 14h allows coolant in the outlet chamber 40 to be discharged to the outside. Counterpressure chamber

[0040] A backpressure chamber 45 is defined between the rotating spiral base plate 26a of the rotating spiral 26 and the shaft bearing housing 13. The backpressure chamber 45 is formed on one side of the rotating spiral base plate 26a opposite the stationary spiral base plate 25a in the housing 11. The shaft bearing housing 13 separates the backpressure chamber 45 from the intake chamber 20. An inner surface of the circumferential wall 18 of the shaft bearing housing 13 is a section of the backpressure chamber 45. Furthermore, a gap between the elastic plate 30 and the shaft bearing housing 13 is a section of the backpressure chamber 45.

[0041] The spiral compressor 10 has a feed channel 46. The feed channel 46 is formed within the rotating spiral 26. A first end of the feed channel 46 is open at a distal end of the rotating spiral wall 26b. This first end of the feed channel 46 is (fluid-)communicating with the compression chamber 27. A second end of the feed channel 46 is / is in (fluid) communication with the counter-pressure chamber 45. The feed channel 46 extends through an inner end of the rotating spiral wall 26b, which converges in a spiral shape towards the center of the rotating spiral 26, and the rotating spiral base plate 26a.

[0042] The supply channel 46 allows a portion of the coolant compressed in the compression chamber 27 to be supplied to the backpressure chamber 45. Consequently, the pressure in the backpressure chamber 45 is higher than that in the intake chamber 20. An increase in pressure in the backpressure chamber 45 pushes the rotating spiral 26 towards the stationary spiral 25, so that the distal end of the rotating spiral wall 26b is pressed against the stationary spiral base plate 25a. In this way, coolant is introduced into the backpressure chamber 45 to push the rotating spiral 26 towards the stationary spiral 25. Inlet channel

[0043] The spiral compressor 10 has an inlet channel 35. The inlet channel 35 has a plurality of first grooves 36, a plurality of first holes 37, and a plurality of second grooves 38. The first grooves 36 are formed in the inner circumferential surface of the circumferential wall 12b of the intake housing 12. Six first grooves 36 are formed in the inner circumferential surface of the circumferential wall 12b of the intake housing 12. The first grooves 36 are open at the opening end of the circumferential wall 12b. The first holes 37 are formed in an outer circumferential section of the flange wall 19 of the shaft bearing housing 13. Six first holes 37 are formed in the outer circumferential section of the flange wall 19. The first holes 37 each extend through the flange wall 19 in the thickness direction thereof. The first holes 37 are in (fluid) communication with their associated first grooves 36.

[0044] As in Fig. 1 and Fig. As illustrated in Figure 2, the second grooves 38 are formed in the inner circumferential surface of the circumferential wall 14b of the outlet housing 14. Six second grooves 38 are formed in the inner circumferential surface of the circumferential wall 14b. As shown in Fig. As illustrated in Figure 2, the second grooves 38 are formed in the inner circumferential surface of the circumferential wall 14b, such that a (single) second groove 38 is arranged between adjacent two of the bead sections 14d in the circumferential direction of the circumferential wall 14b. The second grooves 38 are in (fluid) communication with each other via a gap between the bead sections 14d and an outer circumferential surface of the fixed spiral circumferential wall 25c. As shown in Fig. As illustrated in Figure 1, the second grooves 38 are in (fluid) communication with their associated first holes 37. The second grooves 38 each form a section of the inlet channel 35. Therefore, the inlet channel 35 is defined between the fixed spiral circumferential wall 25c and the circumferential wall 14b of the outlet housing 14. Thick-walled section and thin-walled section

[0045] As in Fig. 2 and Fig. As illustrated in Figure 3, the fixed spiral perimeter wall 25c has a plurality of thick-walled sections 50 and a plurality of thin-walled sections 51. The fixed spiral perimeter wall 25c has six thick-walled sections 50. The six thick-walled sections 50 are arranged at regular intervals in one circumferential direction of the fixed spiral perimeter wall 25c. In this way, the six thick-walled sections 50 are spaced apart from each other in the circumferential direction of the fixed spiral perimeter wall 25c. As shown in Fig. As illustrated in Figure 2, the thick-walled sections 50 are each positioned within the second grooves 38. Therefore, the inlet channel 35 is located outside the thick-walled sections 50.

[0046] The fixed spiral circumferential wall 25c has six thin-walled sections 51. An outer circumferential surface of the fixed spiral circumferential wall 25c is recessed in a concave shape between adjacent pairs of the thick-walled sections 50 in the circumferential direction of the fixed spiral circumferential wall 25c that forms each of the thin-walled sections 51. The outer surfaces of the thin-walled sections 51 are each a curved surface, curved in an arc shape and recessed relative to the circumferential wall 14b of the outlet housing 14. The outer surfaces of the thin-walled sections 51 extend along their associated outer surfaces of the beaded sections 14d.Each of the thin-walled sections 51 is formed with the outer circumferential surface of the fixed spiral perimeter wall 25c, which is recessed in a concave shape between adjacent two of the thick-walled sections 50 in the circumferential direction of the fixed spiral perimeter wall 25c, in order to allow each of the beaded sections 14d to be / be arranged, and has a thickness that is less than the thickness of each of the thick-walled sections 50.

[0047] When the fixed spiral 25 is viewed in the axial direction of the fixed spiral perimeter wall 25c, a straight line passing through an axial line L2 of the fixed spiral perimeter wall 25c and through two of the plurality of thin-walled sections 51 is defined as an imaginary straight line L10. When the fixed spiral perimeter wall 25c is viewed in the axial direction of the fixed spiral perimeter wall 25c, three thick-walled sections 50 are arranged on one side of the imaginary straight line L10. When the fixed spiral perimeter wall 25c is viewed in the axial direction of the fixed spiral perimeter wall 25c, three thick-walled sections 50 are arranged on the other side of the imaginary straight line L10.In this way, when the fixed spiral perimeter wall 25c is seen in the axial direction of the fixed spiral perimeter wall 25c, the thick-walled sections 50 are arranged such that some of the plurality of thick-walled sections 50 are arranged on one side and the others of the plurality of thick-walled sections 50 are arranged on the other side of the imaginary straight line L10.

[0048] Two inlet ports 39 are formed in the fixed spiral circumferential wall 25c. When the fixed spiral circumferential wall 25c is viewed in the axial direction, the inlet ports 39 are formed in the fixed spiral circumferential wall 25c such that the inlet ports 39 each extend through the two thin-walled sections 51, through which the imaginary straight line L10 runs, in the thickness directions of the two thin-walled sections 51. The inlet ports 39 are in (fluid) communication with the second grooves 38 via a gap between the bead sections 14d and the outer circumferential surface of the fixed spiral circumferential wall 25c. Thus, the inlet ports 39 are in communication with the inlet channel 35. The inlet ports 39 are in communication with an outermost circumferential section of the compression chamber 27.Thus, the inlet channel 35 communicates with the compression chamber 27 via the inlet connection 39.

[0049] Coolant in the intake chamber 20 flows through the first grooves 36, the first holes 37, the second grooves 38, and the inlet port 39; and is drawn into the compression chamber 27. Thus, coolant in the intake chamber 20 is drawn into the compression chamber 27 through the inlet channel 35. The inlet channel 35 is a suction pressure region through which the coolant drawn into the compression chamber 27 flows. The coolant drawn into the compression chamber 27 is compressed in the compression chamber 27 by the rotational movement of the circulating spiral 26. In this way, the compression mechanism C1 compresses the coolant introduced into the housing 11. Pinhole

[0050] Pin holes 52 are formed in the end faces of the thick-walled sections 50 facing the elastic plate 30. Two of the six thick-walled sections 50 each have a pin hole 52 in their end face facing the elastic plate 30. Thus, the pin hole 52 is formed in the end face of any one of the plurality of thick-walled sections 50 facing the elastic plate 30. When the fixed spiral perimeter wall 25c is viewed in the axial direction of the fixed spiral perimeter wall 25c, the two pin holes 52 are formed in the end faces facing the elastic plate 30 of two of the three thick-walled sections 50 arranged on one side of the imaginary straight line L10.When the fixed spiral perimeter wall 25c is viewed in the axial direction of the fixed spiral perimeter wall 25c, the thick-walled sections 50, each having the pin insertion hole 52, are arranged next to the two thin-walled sections 51 through which the imaginary straight line L10 runs.

[0051] As in Fig. As illustrated in Figure 4, the shaft bearing housing 13 has two positioning pins 53 projecting from / out of the end face 13e of the shaft bearing housing 13. For better illustration, in Fig. Figure 4 illustrates only one of the positioning pins 53. The elastic plate 30 has holes 30a into which the positioning pins 53 are inserted. The positioning pins 53 are inserted into the pin insertion holes 52 through the holes 30a of the elastic plate 30. In this way, the positioning pins 53 are inserted into the pin insertion holes 52. The positioning pins 53 are inserted through the holes 30a of the elastic plate 30 into the pin insertion holes 52, thereby positioning the elastic plate 30. Nut

[0052] As in Fig. 2 and Fig. As illustrated in Figure 3, grooves 55 are formed in the end faces of the thick-walled sections 50 facing the elastic plate 30. The grooves 55 are formed in the end faces of some thick-walled sections 50 facing the elastic plate 30, in which the pin insert holes 52 are not formed, of the plurality of thick-walled sections 50. The grooves 55 are formed in the end faces of two thick-walled sections 50 facing the elastic plate 30 of the plurality of thick-walled sections 50. Thus, the fixed spiral circumferential wall 25c has two grooves 55.

[0053] When the fixed spiral perimeter wall 25c is viewed in the axial direction, one of the two grooves 55 in the end face facing the elastic plate 30 is formed by one of the plurality of thick-walled sections 50 arranged on one side of the imaginary straight line L10. Furthermore, when the fixed spiral perimeter wall 25c is viewed in the axial direction, the other of the two grooves 55 in the end face facing the elastic plate 30 is formed by one of the plurality of thick-walled sections 50 arranged on the other side of the imaginary straight line L10.When the fixed spiral perimeter wall 25c is viewed in the axial direction, the two grooves 55 are formed in the end faces of the two thick-walled sections 50 facing the elastic plate 30, which are oriented in a direction perpendicular to the imaginary straight line L10. In this way, the grooves 55 are formed in the end face facing the elastic plate 30 of one of the multiple thick-walled sections 50 arranged on one side of the imaginary straight line L10, and in the end face facing the elastic plate 30 of one of the multiple thick-walled sections 50 arranged on the other side of the imaginary straight line L10.

[0054] As in Fig. 5 and Fig. As illustrated in Figure 6, the grooves 55 are open on the inner circumferential surface of the fixed spiral circumferential wall 25c. The grooves 55 are also open on the outer circumferential surface of the fixed spiral circumferential wall 25c. The inner surfaces of the grooves 55 are in (fluid) communication with the inlet channel 35. Therefore, the inner surfaces of the grooves 55 constitute the suction pressure area. As shown in Fig. As illustrated in Figure 2, a width W1 of each of the grooves 55 in the circumferential direction of the fixed spiral perimeter wall 25c is smaller than a width W2 of each of the thick-walled sections 50 in the circumferential direction of the fixed spiral perimeter wall 25c.

[0055] As in Fig. 7 and Fig. As illustrated in Figure 8, sections of the elastic plate 30 that overlap with the grooves 55 are elastically deformed in the direction of the grooves 55 when a pressure difference between the pressure in the back pressure chamber 45 and the pressure in the inlet channel 35 exceeds a predetermined value. At this point, the grooves 55 accommodate elastic deformation of the elastic plate 30, so that the back pressure chamber 45 and the inlet channel 35 communicate with each other when the pressure difference between the pressure in the back pressure chamber 45 and the pressure in the inlet channel 35 exceeds the predetermined value.

[0056] The sections of the elastic plate 30 that overlap with the grooves 55 correspond to elastically deformable sections 30b. When the elastically deformable sections 30b are elastically deformed in the direction of the grooves 55, 13 communication channels 56, which provide (fluid) communication between the back pressure chamber 45 and the inlet channel 35, are formed between the elastically deformable sections 30b and the shaft bearing housing. It can also be said that the elastically deformable sections 30b are elastically deformed by the pressure difference between the pressure in the back pressure chamber 45 and the pressure in the inlet channel 35 in order to open and close the communication channels 56. When the elastically deformable sections 30b are elastically deformed by the pressure difference, they are curved and project into the grooves 55.

[0057] The width W1 of each of the grooves 55 in the circumferential direction of the fixed spiral perimeter wall 25c is predetermined to be a width that allows elastic deformation of sections of the elastic plate 30 overlapping the grooves 55 in the direction of the grooves 55 when the pressure difference between the pressure in the counter-pressure chamber 45 and the pressure in the inlet channel 35 exceeds the predetermined value. The width W1 of each of the grooves 55 in the circumferential direction of the fixed spiral perimeter wall 25c is determined in advance by experiment or the like. Mode of operation of embodiment

[0058] The following describes the mode of operation of the present embodiment.

[0059] A portion of coolant compressed in the compression chamber 27 is supplied to the back-pressure chamber 45 via the supply channel 46. This increases the pressure in the back-pressure chamber 45. Furthermore, since the rotating spiral 26 is pressed towards the stationary spiral 25, coolant leakage from the compression chamber 27 is less likely. As a result, the compression efficiency of the scroll compressor 10 is improved.

[0060] In the scroll compressor 10 with the configuration described above, coolant can be cooled and liquefied when the scroll compressor 10 is stopped. For example, if the scroll compressor 10 is started in a state where liquefied coolant, produced by liquefaction, is present in the back-pressure chamber 45, heat from the coolant compressed in the compression chamber 27 can be transferred via the rotating spiral base plate 26a to the liquefied coolant in the back-pressure chamber 45. The liquefied coolant then evaporates in the back-pressure chamber 45, and the pressure in the back-pressure chamber 45 increases.

[0061] Here, if the pressure difference between the pressure in the backpressure chamber 45 and the pressure in the inlet channel 35 exceeds the predetermined value, the grooves 55 undergo elastic deformation of the elastic plate 30, so that the backpressure chamber 45 and the inlet channel 35 are in (fluid) communication with each other. Thus, as in Fig. Figure 7 illustrates the communication channels 56 formed between the elastically deformable sections 30b and the shaft bearing housing 13, and the coolant in the back pressure chamber 45 is discharged through the communication channels 56 into the inlet channel 35, as indicated by an arrow A1 in Fig.7. In this way, the coolant in the back-pressure chamber 45 is discharged through the grooves 55 into the inlet channel 35, thus suppressing an excessive increase in pressure in the back-pressure chamber 45. Consequently, the problem of the rotating spiral 26 becoming less likely to cause excessive pressure increase in the back-pressure chamber 45, which would reduce the compression efficiency of the spiral compressor 10, is avoided.

[0062] The thin-walled sections 51 are closer to the beaded sections 14d than the thick-walled sections 50. The screws B1 extend through sections corresponding to the beaded sections 14d of the circumferential wall 14b of the outlet housing 14 in the axial direction of the circumferential wall 14b. Therefore, a reaction / counterforce caused by a fastening force of the screws B1 from the shaft bearing housing 13 acts more locally on the end faces of the thin-walled sections 51 facing the elastic plate 30, compared to the end faces of the thick-walled sections 50 facing the elastic plate 30.

[0063] Here, the grooves 55 are formed in the end faces of the thick-walled sections 50 facing the elastic plate 30. Therefore, the end faces of the thin-walled sections 51, which face the elastic plate 30, can adequately absorb the reaction / counterforce caused by the fastening force of the screws B1 from the shaft bearing housing 13. Effects of embodiment

[0064] The embodiment described above offers the following effects. (1) The grooves 55 accommodate elastic deformation of the elastic plate 30, so that the backpressure chamber 45 and the inlet channel 35 are in (fluid) communication with each other when the pressure difference between the pressure in the backpressure chamber 45 and the pressure in the inlet channel 35 exceeds the predetermined value. As a result, coolant in the backpressure chamber 45 is released into the inlet channel 35 through the grooves 55, thus suppressing an excessive increase in pressure in the backpressure chamber 45. The grooves 55 are formed in the end faces of the thick-walled sections 50 facing the elastic plate 30. Therefore, the end faces of the thin-walled sections 51 facing the elastic plate 30 can adequately absorb the reaction / counterforce from the shaft bearing housing 13 caused by the fastening force of the screws B1.As a result, the pressure in the counter-pressure chamber 45 is prevented from rising excessively, while the rigidity of the stationary spiral 25 is maintained. (2) The end faces of the thick-walled sections 50 facing the elastic plate 30 are, in comparison to the end faces of the thin-walled sections 51 facing the elastic plate 30, suitable sections for forming the pin insertion holes 52 in an end face of the fixed spiral circumferential wall 25c facing the elastic plate 30. The grooves 55 are formed in the end faces of the thick-walled sections 50 facing the elastic plate 30, in which the pin insertion holes 52 are not formed, from the plurality of thick-walled sections 50. Thus, the grooves 55 can be formed more easily in the end faces of the thick-walled sections 50 facing the elastic plate 30 than in a case where the grooves 55 are formed in the end faces of the thick-walled sections 50 facing the elastic plate 30, in which the pin insert holes 52 are formed. (3) The grooves 55 are formed in the end faces of two thick-walled sections 50 of the plurality of thick-walled sections 50 facing the elastic plate 30. This allows coolant in the backpressure chamber 45 to be discharged more efficiently into the inlet channel 35 through the grooves 55 than in a case where the groove 55 is formed only in the end face of a single thick-walled section 50 of the plurality of thick-walled sections 50 facing the elastic plate 30. (4) The grooves 55 are formed in the end face facing the elastic plate 30 by one (single) of the plurality of thick-walled sections 50 arranged on one side of the imaginary straight line L10, and in the end face facing the elastic plate 30 by one (single) of the plurality of thick-walled sections 50 arranged on the other side of the imaginary straight line L10. As a result, depending on an orbital position of the circumferential spiral 26, the coolant in the back pressure chamber 45 can be efficiently discharged into the inlet channel 35 through one of the grooves 55 formed in the end face facing the elastic plate 30 by one of the plurality of thick-walled sections 50 arranged on one side of the imaginary straight line L10.Furthermore, depending on the orbital position of the circumferential spiral 26, the coolant in the counter-pressure chamber 45 can be efficiently discharged through the other of the grooves 55 formed in the end face facing the elastic plate 30 from one of the multitude of thick-walled sections 50 arranged on the other side of the imaginary straight line L10 to the inlet channel 35. (5) A configuration in which the width W1 of each of the grooves 55 in the circumferential direction of the fixed spiral perimeter wall 25c is smaller than the width W2 of each of the thick-walled sections 50 in the circumferential direction of the fixed spiral perimeter wall 25c is suitable for forming the grooves 55 in the end faces of the thick-walled sections 50 facing the elastic plate 30. modification

[0065] The embodiment described above can be modified in various ways, as illustrated below by way of example. The embodiment described above and the following modifications can be combined to the extent consistent with the present invention.

[0066] In this embodiment, the grooves 55 can be formed in the end faces of three or more thick-walled sections 50 of the plurality of thick-walled sections 50 facing the elastic plate 30. Thus, three or more grooves 55 can be formed in the fixed spiral circumferential wall 25c. In short, the grooves 55 need only be formed in the end faces of at least two thick-walled sections 50 of the plurality of thick-walled sections 50 facing the elastic plate 30.

[0067] In this embodiment, the grooves 55 can be formed in the end faces of two or more thick-walled sections 50 of the plurality of thick-walled sections 50, which are arranged on one side of the imaginary straight line L10, facing the elastic plate 30. In this embodiment, the grooves 55 can be formed in the end faces of two or more thick-walled sections 50 of the plurality of thick-walled sections 50, which are arranged on the other side of the imaginary straight line L10.In short, the grooves 55 must be formed in the end face facing the elastic plate 30 of at least one of the plurality of thick-walled sections 50 arranged on one side of the imaginary straight line L10, and in the end face facing the elastic plate 30 of at least one of the plurality of thick-walled sections 50 arranged on the other side of the imaginary straight line L10.

[0068] In this embodiment, the groove 55 can only be formed in the end face of a single thick-walled section 50 of the plurality of thick-walled sections 50 facing the elastic plate 30. Thus, only a single groove 55 can be formed in the fixed spiral circumferential wall 25c.

[0069] In this embodiment, the grooves 55 can be formed in the end faces of the thick-walled sections 50, in which the pin insert holes 52 are formed, facing the elastic plate 30, of the plurality of thick-walled sections 50.

[0070] In this embodiment, the number of the respective thick-walled sections 50 and thin-walled sections 51 is not particularly limited, as long as there are two or more of them.

[0071] In this embodiment, for example, press-fit pins can be used as the fastening elements instead of screws B1.

[0072] In this embodiment, the screw insertion holes 19a do not need to be formed in the outer circumferential section of the flange wall 19 of the shaft bearing housing 13. Furthermore, the flange wall 19 does not need to be held between the circumferential wall 14b of the outlet housing 14 and the circumferential wall 12b of the intake housing 12, but can, for example, be press-fitted to the inner circumferential surface of the circumferential wall 12b of the intake housing 12. Therefore, the shaft bearing housing 13 does not need to be fastened to the intake housing 12 by the screws B1 as the fastening elements.

[0073] In this embodiment, the number of inlet ports 39 is not particularly limited.

[0074] In this embodiment, the spiral compressor 10 does not have to be driven by the motor 22, but can, for example, be driven by the engine of a vehicle.

[0075] Although the scroll compressor 10 is used for vehicle air conditioning in the above embodiment, its use is not limited to this. The scroll compressor 10 can be used in any desired way, as long as it is used to compress refrigerant. [Additional remarks]

[0076] The following describes technical ideas that can be derived from the embodiment and its variations. <Zusatzanmerkung 1>

[0077] Spiral compressor with: a case; a rotating shaft which is rotatably mounted through the housing; a fixed spiral which is attached to the housing and has a fixed spiral base plate, a fixed spiral spiral wall extending from the fixed spiral base plate, and a fixed spiral perimeter wall extending from the fixed spiral base plate and surrounding the fixed spiral spiral wall; a circumferential spiral with a circumferential spiral base plate facing the stationary spiral base plate and a circumferential spiral wall extending from the circumferential spiral base plate towards the stationary spiral base plate and engaging with the stationary spiral wall, wherein the circumferential spiral is arranged to perform a circumferential motion within the stationary spiral circumferential wall when the rotating shaft is rotated; an elastic plate which has a ring shape and is designed to push the circumferential spiral in the direction of the stationary spiral; and a compression chamber in which a coolant is compressed and which is defined by the fixed spiral base plate, the fixed spiral spiral wall, the rotating spiral base plate and the rotating spiral spiral wall; the case features: - a shaft bearing housing that is arranged on one side of the rotating spiral base plate opposite the stationary spiral base plate and supports the rotating shaft; - an outlet housing comprising an end wall and a circumferential wall extending from the end wall in a tubular form to surround the stationary spiral circumferential wall, and defining an outlet chamber into which the coolant compressed in the compression chamber is discharged between the end wall and the stationary spiral base plate; and - an intake housing that interacts with the shaft bearing housing to define an intake chamber into which the coolant is drawn from the outside; an inlet channel defined between the fixed spiral circumferential wall and the circumferential wall, wherein the coolant in the intake chamber is drawn into the compression chamber through the inlet channel; a back pressure chamber defined between the rotating spiral base plate and the shaft bearing housing, wherein the coolant is introduced into the back pressure chamber to push the rotating spiral in the direction of the stationary spiral; an outer circumferential section of the elastic plate, which is held between the fixed spiral circumferential wall and the shaft bearing housing; a multitude of bead sections that are spaced apart from each other in a circumferential direction of the circumferential wall and project in the direction of the fixed spiral circumferential wall with an inner circumferential surface of the circumferential wall formed in a convex shape; a fastening element extending through a section of the circumferential wall, corresponding to each of the plurality of bead sections, in an axial direction of the circumferential wall to fasten the outlet housing to the intake housing; wherein the stationary spiral is attached to the housing, wherein the stationary spiral circumferential wall is held between the end wall and the shaft bearing housing by a fastening force of the fastening element; and wherein the fixed spiral perimeter wall has: - a multitude of thick-walled sections spaced apart from each other in the circumferential direction of the stationary spiral perimeter wall; and - a plurality of thin-walled sections formed with an outer circumferential surface of the fixed spiral perimeter wall that is recessed in a concave shape between the plurality of thick-walled sections arranged adjacent to each other in the circumferential direction of the fixed spiral perimeter wall to allow the beaded sections to be arranged, and each having a thickness that is less than the thickness of each of the plurality of thick-walled sections; wherein a groove is formed in at least one of the end faces of the plurality of thick-walled sections facing the elastic plate, wherein the groove accommodates elastic deformation of the elastic plate, so that the back pressure chamber and the inlet channel are in communication with each other when a pressure difference between a pressure in the back pressure chamber and a pressure in the inlet channel exceeds a predetermined value. <Zusatzanmerkung 2>

[0078] Spiral compressor according to<Zusatzanmerkung 1> , where a pin insertion hole, into which a positioning pin for positioning the elastic plate is inserted, is formed in at least one of the end faces of the plurality of thick-walled sections facing the elastic plate; and the groove is formed in at least one of the end faces of the multitude of thick-walled sections facing the elastic plate, in which the pin insert hole is not formed. <Zusatzanmerkung 3>

[0079] Spiral compressor according to<Zusatzanmerkung 1> or<Zusatzanmerkung 2> , where The groove has a plurality of grooves formed in the end faces of at least two of the plurality of thick-walled sections facing the elastic plate. <Zusatzanmerkung 4>

[0080] Spiral compressor according to <Additional Note 3>, wherein a straight line passing through an axial line of the fixed spiral perimeter wall and two of the plurality of thin-walled sections is defined as an imaginary straight line when the fixed spiral is viewed in an axial direction of the fixed spiral perimeter wall; the multitude of thick-walled sections includes a multitude of thick-walled sections arranged on one side of the imaginary straight line and a multitude of thick-walled sections arranged on the other side of the imaginary straight line when the fixed spiral perimeter wall is viewed in the axial direction; the groove comprises a plurality of grooves formed in at least one of the end faces of the plurality of thick-walled sections arranged on one side of the imaginary straight line, and in at least one of the end faces of the plurality of thick-walled sections arranged on the other side of the imaginary straight line. <Zusatzanmerkung 5>

[0081] Spiral compressor according to a<Zusatzanmerkung 1> until<Zusatzanmerkung 4> , where a width of the groove in the circumferential direction is smaller than a width of each of the multitude of thick-walled sections in the circumferential direction. QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] JP 2022-149824

[0002]

Claims

[1] Spiral compressor (10) with: a housing (11); a rotating shaft (15) which is rotatably mounted through the housing (11); a fixed spiral (25) which is attached to the housing (11) and has a fixed spiral base plate (25a), a fixed spiral spiral wall (25b) extending from the fixed spiral base plate (25a), and a fixed spiral perimeter wall (25c) extending from the fixed spiral base plate (25a) and surrounding the fixed spiral spiral wall (25b); a circumferential spiral (26) with a circumferential spiral base plate (26a) facing the stationary spiral base plate (25a) and a circumferential spiral wall (26b) extending from the circumferential spiral base plate (26a) towards the stationary spiral base plate (25a) and engaging with the stationary spiral wall (25b), wherein the circumferential spiral (26) is arranged to perform a circumferential movement within the stationary spiral circumferential wall (25c) when the rotating shaft (15) is rotated; an elastic plate (30) which has a ring shape and is arranged to push the circumferential spiral (26) in the direction of the stationary spiral (25); and a compression chamber (27) in which a coolant is compressed and which is defined by the stationary spiral base plate (25a), the stationary spiral spiral wall (25b), the rotating spiral base plate (26a) and the rotating spiral spiral wall (26b); wherein the housing (11) has: - a shaft bearing housing (13) which is arranged on one side of the rotating spiral base plate (26a) opposite the stationary spiral base plate (25a) and supports the rotating shaft (15); - an outlet housing (14) comprising an end wall (14a) and a circumferential wall (14b) extending from the end wall (14a) in a tubular form to surround the stationary spiral circumferential wall (25c), and defining an outlet chamber (40) into which the coolant compressed in the compression chamber (27) is discharged between the end wall (14a) and the stationary spiral base plate (25a); and - an intake housing (12) that interacts with the shaft bearing housing (13) to define an intake chamber (20) into which the coolant is drawn from the outside; an inlet channel (35) defined between the fixed spiral circumferential wall (25c) and the circumferential wall (14b), wherein the coolant in the intake chamber (20) is drawn into the compression chamber (27) through the inlet channel (35); a back pressure chamber (45) defined between the rotating spiral base plate (26a) and the shaft bearing housing (13), wherein the coolant is introduced into the back pressure chamber (45) in order to push the rotating spiral (26) in the direction of the stationary spiral (25); an outer circumferential section of the elastic plate (30) which is held between the fixed spiral circumferential wall (25c) and the shaft bearing housing (13); a plurality of bead sections (14d) which are spaced apart from each other in a circumferential direction of the circumferential wall (14b) and project in the direction of the fixed spiral circumferential wall (25c) with an inner circumferential surface of the circumferential wall (14b) formed in a convex shape; a fastening element extending through a section of the circumferential wall (14b), corresponding to each of the plurality of bead sections (14d), in an axial direction of the circumferential wall (14b) to fasten the outlet housing (14) to the intake housing (12); wherein the stationary spiral (25) is attached to the housing, wherein the stationary spiral circumferential wall (25c) is held between the end wall (14a) and the shaft bearing housing (13) by a fastening force of the fastening element; and wherein the fixed spiral perimeter wall (25c) has: - a plurality of thick-walled sections (50) spaced apart from each other in the circumferential direction of the fixed spiral perimeter wall (25c); and - a plurality of thin-walled sections (51) formed with an outer circumferential surface of the fixed spiral perimeter wall (25c) that is recessed in a concave shape between the plurality of thick-walled sections (50) that are arranged adjacent to each other in the circumferential direction of the fixed spiral perimeter wall (25c) to allow the bead sections (14d) to be arranged, and each of which has a thickness that is less than the thickness of each of the plurality of thick-walled sections (50); characterized by , that a groove (55) is formed in at least one of the end faces of the plurality of thick-walled sections (50) facing the elastic plate (30), wherein the groove (55) accommodates elastic deformation of the elastic plate (30) so that the counter-pressure chamber (45) and the inlet channel (35) communicate with each other when a pressure difference between a pressure in the counter-pressure chamber (45) and a pressure in the inlet channel (35) exceeds a predetermined value. [2] Spiral compressor (10) according to claim 1, characterized by , that a pin insertion hole (52), into which a positioning pin (53) for positioning the elastic plate (30) is inserted, is formed in at least one of the end faces of the plurality of thick-walled sections (50) facing the elastic plate (30); and the groove (55) is formed in at least one of the end faces of the plurality of thick-walled sections (50) facing the elastic plate (30), in which the pin insert hole (52) is not formed. [3] Spiral compressor (10) according to claim 1 or 2, characterized by , that the groove (55) has a plurality of grooves (55) formed in the end faces of at least two of the plurality of thick-walled sections (50) facing the elastic plate (30). [4] Spiral compressor (10) according to claim 3, characterized by , that a straight line passing through an axial line of the fixed spiral perimeter wall (25c) and two of the plurality of thin-walled sections (51) is defined as an imaginary straight line (L10) when the fixed spiral (25) is seen in an axial direction of the fixed spiral perimeter wall (25c); the plurality of thick-walled sections (50) includes a plurality of thick-walled sections (50) arranged on one side of the imaginary straight line (L10) and a plurality of thick-walled sections (50) arranged on the other side of the imaginary straight line (L10) when the fixed spiral perimeter wall (25c) is viewed in the axial direction; the groove (55) comprises a plurality of grooves (55) formed in at least one of the end faces of the plurality of thick-walled sections (50) arranged on one side of the imaginary straight line (L10) and in at least one of the end faces of the plurality of thick-walled sections (50) arranged on the other side of the imaginary straight line (L10). [5] Spiral compressor (10) according to any one of claims 1 to 4, characterized by, that a width of the groove (55) in the circumferential direction is smaller than a width of each of the plurality of thick-walled sections (50) in the circumferential direction.

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