JP2020007910A - Electric scroll compressor - Google Patents

Abstract

To provide an electric scroll compressor capable of suppressing vibration and noise.SOLUTION: A motor housing 10 is formed in a bottomed cylindrical shape. A middle housing 30 is abutted on or fixed to the inner wall of the motor housing 10. A movable scroll 40 revolves around a rotation axis Ax of a shaft 23 with torque transmitted from the shaft 23 of a motor part 20. A fixed scroll 50 is fixed to the middle housing 30 not to be relatively displaced in a direction perpendicular to the rotation axis Ax of the shaft 23. A rear housing 60 is fixed to the axial end of the motor housing 10 for supporting the fixed scroll 50 on the middle housing 30. In this construction, stiffness at a position where the motor housing 10 and the middle housing 30 are abutted on or fixed to each other is greater than stiffness at a position where the rear housing 60 supports the fixed scroll 50.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an electric scroll compressor.

  BACKGROUND ART Conventionally, an electric scroll compressor that compresses a refrigerant has been known. The electric scroll compressor described in Patent Literature 1 has a motor unit, a movable crawl, and a motor inside a semi-hermetic container formed by a bottomed cylindrical motor housing and a rear housing fixed to an end of the motor housing. A fixed scroll or the like is accommodated. The motor section has a motor stator fixed to the inner wall of the motor housing, a motor rotor rotatably provided inside the motor stator, and a shaft that rotates with the motor rotor to transmit torque to the movable scroll. are doing. The movable crawl is configured to revolve around a rotation axis of a shaft of the motor unit, and forms a working chamber that compresses the refrigerant together with the fixed scroll. The fixed scroll is fixed to the rear housing with bolts.

JP 2017-155717 A

  In the electric scroll compressor, the motor generates torque against the reaction force of the refrigerant compressed in the working chamber. Therefore, torque fluctuations generated in the motor section and the working chamber cause vibration. In the configuration described in Patent Literature 1, vibration generated during compression of the refrigerant is transmitted from the motor unit and the movable scroll to the fixed scroll via the refrigerant in the working chamber, and passes through the rear housing fixed to the fixed scroll by bolts. And transmitted to the motor housing. Further, the vibration generated when the refrigerant is compressed is transmitted to the motor housing via the motor stator of the motor unit. As described above, in the configuration described in Patent Document 1, the path through which the vibration is transmitted has a loop shape including the motor unit, the movable scroll, the fixed scroll, the rear housing, and the motor housing. The loop path includes the rear housing and the motor housing, so that the distance is long. Therefore, the phase difference and the amplitude difference between the vibration transmitted from the rear housing side to the motor housing and the vibration transmitted from the motor stator side to the motor housing become large. Further, since the path through which the vibration is transmitted is long, the torsional rigidity of the rear housing and the motor housing (hereinafter, referred to as "both housings") serving as the transmission path of the vibration is reduced. If both housings are completely rigid, the vibrations cancel each other out, so that the vibrations are not transmitted to the outside. However, in practice, since both housings are not completely rigid, they transmit vibration with a small elastic deformation. Therefore, if the torsional rigidity of the two housings against vibration decreases, the vibration and noise of the compressor itself may increase. Further, when the compressor is mounted on an external member (for example, an engine block of a vehicle), the force of vibrating the external member from the mounting foot provided on the motor housing increases, and the compressor applies a force to the external member. There is a concern that transmitted vibration and noise will increase.

  In view of the above, an object of the present invention is to provide an electric scroll compressor capable of suppressing vibration and noise.

In order to achieve the above object, the invention according to claim 1 is:
In an electric scroll compressor that compresses a refrigerant,
A bottomed cylindrical motor housing (10);
A motor unit (21) having a motor stator (21) fixed to the inner wall of the motor housing, a motor rotor (22) rotatably provided inside the motor stator, and a shaft (23) rotating with the motor rotor ( 20)
A middle housing (30) abutted or fixed to an inner wall of the motor housing and rotatably supporting the shaft;
An eccentric part (26) provided eccentrically with respect to the rotation axis (Ax) of the shaft at an end of the shaft;
A movable scroll (40) that is arranged on the opposite side of the motor unit with respect to the middle housing and that receives torque from the eccentric part and revolves around the rotation axis of the shaft;
A fixed scroll (50) fixed to the middle housing so as not to be relatively displaced in a direction perpendicular to the rotation axis of the shaft, and forming a working chamber (47) for compressing the refrigerant together with the movable scroll;
A rear housing (60) fixed to an axial end of the motor housing and supporting the fixed scroll with respect to the middle housing;
The rigidity of the portion where the motor housing and the middle housing abut or are fixed is configured to be greater than the rigidity of the portion where the rear housing supports the fixed scroll.

  According to this, when the motor unit is driven, torque is transmitted from the shaft of the motor unit to the movable scroll via the eccentric unit, and the electric scroll compressor (hereinafter sometimes referred to as “compressor”) is driven. Revolves and the refrigerant in the working chamber is compressed. As described above, the motor section generates torque against the reaction force of the refrigerant compressed in the working chamber. Therefore, torque fluctuations generated in the motor section and the working chamber cause vibration. In the configuration according to the first aspect of the invention, the vibration generated when the refrigerant is compressed is transmitted from the motor unit and the movable scroll to the fixed scroll via the refrigerant in the working chamber, and from there, without passing through the rear housing. Through the motor housing. Further, the vibration generated when the refrigerant is compressed is transmitted to the motor housing via the motor stator of the motor unit. As described above, the configuration of the invention according to claim 1 is different from the configuration described in Patent Document 1 in that vibration is transmitted from the fixed scroll to the motor housing because the rear housing is not included in the path. The transmission path becomes shorter. Therefore, the phase difference and the amplitude difference between the vibration transmitted from the middle housing side to the motor housing and the vibration transmitted from the motor stator side to the motor housing become small, and the vibrations are easily offset. Further, the torsional torque acting on the motor housing and the like due to vibration is constant, but since the transmission path of the vibration in the motor housing is short, the amount of deformation of the motor housing and the like with respect to the torsional torque is small. . Therefore, vibration and noise of the compressor itself are reduced. Further, when the compressor is attached to an external member, a force for exciting the external member from the motor housing is reduced. Therefore, this compressor can reduce vibration and noise transmitted from the housing to the external member.

  In addition, the reference numerals in parentheses attached to the respective components and the like indicate an example of a correspondence relationship between the components and the like and specific components and the like described in the embodiments described later.

It is a sectional view of an electric scroll compressor concerning a 1st embodiment. FIG. 2 is an enlarged view of a portion II in FIG. 1. It is a sectional view showing a part of electric scroll compressor concerning a 2nd embodiment. It is a sectional view showing a part of electric scroll compressor concerning a 3rd embodiment. It is a sectional view showing a part of electric scroll compressor concerning a 4th embodiment. It is a sectional view showing a part of the electric scroll compressor concerning a 5th embodiment. It is a sectional view showing a part of electric scroll compressor concerning a 6th embodiment. FIG. 8 is a sectional view taken along line VIII-VIII in FIG. 7. It is a sectional view showing a part of electric scroll compressor concerning a 7th embodiment. It is sectional drawing of the XX line of FIG. It is a sectional view showing a part of electric scroll compressor concerning an 8th embodiment. It is a sectional view showing a part of electric scroll compressor concerning a 9th embodiment. It is sectional drawing of the XIII-XIII line of FIG. It is a sectional view showing a part of electric scroll compressor concerning a 10th embodiment. FIG. 15 is a sectional view taken along line XV-XV in FIG. 14. It is sectional drawing which shows a part of electric scroll compressor concerning 11th Embodiment. It is sectional drawing of the XVII-XVII line of FIG. It is a sectional view showing a part of electric scroll compressor concerning a 12th embodiment. It is sectional drawing of the electric scroll compressor of a comparative example.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals and description thereof will be omitted.

(1st Embodiment)
The first embodiment will be described with reference to the drawings. The electric scroll compressor 1 (hereinafter, referred to as “compressor 1”) of the present embodiment constitutes a part of a refrigeration cycle (not shown) mounted on a vehicle. The compressor 1 sucks refrigerant from the piping of the refrigeration cycle, compresses the refrigerant, and then discharges the refrigerant to the piping of the refrigeration cycle.

  As shown in FIGS. 1 and 2, the compressor 1 of the present embodiment includes a motor housing 10, a motor unit 20, a middle housing 30, a movable scroll 40, a fixed scroll 50, a rear housing 60, and the like.

  The motor housing 10 is formed in a bottomed tubular shape, and has a bottom portion 11 and a tubular portion 12 that extends in a tubular shape from the outer edge of the bottom portion 11. A rear housing 60 is fixed to an axial end of the bottom 11 of the motor housing 10. Specifically, an end of the cylindrical portion 12 of the motor housing 10 opposite to the bottom 11 and the rear housing 60 are fixed by bolts 61. Thus, the motor housing 10 and the rear housing 60 form a closed container structure. Note that the structure in which the motor housing 10 and the rear housing 60 are fixed by the bolts 61 is sometimes called a semi-hermetic container structure to distinguish it from the structure fixed by welding.

  The motor housing 10 is provided with a suction port 13 for sucking refrigerant from the piping of the refrigeration cycle to the inside of the closed container structure. On the other hand, the rear housing 60 is provided with a discharge port 62 for discharging the refrigerant compressed inside the closed container structure to the piping of the refrigeration cycle.

  Inside the closed container structure formed by the motor housing 10 and the rear housing 60, a motor unit 20 that generates a driving force for compressing the refrigerant, and a movable scroll 40 that constitutes a compression mechanism unit for compressing the refrigerant. And a fixed scroll 50 and the like.

  The motor section 20 includes a motor stator 21 fixed to the motor housing 10, a motor rotor 22 rotatably provided inside the motor stator 21, and rotates together with the motor rotor 22 to apply torque to the movable scroll 40. It has a shaft 23 for transmitting.

  The motor stator 21 is fixed to the inner wall of the motor housing 10 by, for example, shrink fitting or press fitting. A coil 24 is wound around each tooth of the motor stator 21 formed of a magnetic material. When the coil 24 is energized, the motor stator 21 generates a rotating magnetic field for rotating the motor rotor 22.

  The motor rotor 22 is rotatably provided inside the motor stator 21 in the radial direction. The motor rotor 22 is formed of a magnetic material, and has different magnetic poles arranged alternately in the circumferential direction. A shaft 23 is fixed to the center of the motor rotor 22. One end of the shaft 23 is rotatably supported by a front bearing 14 provided on the bottom 11 of the motor housing 10, and the other end is rotatably supported by a main bearing 32 provided on the middle housing 30.

  The middle housing 30 is formed in a substantially disk shape. In the present embodiment, the outer wall 31 on the radially outer side of the middle housing 30 is fixed to the inner wall of the motor housing 10 by press fitting. Thus, the middle housing 30 and the motor housing 10 are fixed in a direction perpendicular to the rotation axis Ax of the shaft 23. Therefore, in the present embodiment, it is possible to increase the rigidity of the shaft 23 at a position where the motor housing 10 and the middle housing 30 are fixed against a load perpendicular to the rotation axis Ax of the shaft 23. The rigidity is the reciprocal of the amount of deformation with respect to the load between two parts.

  A step surface 15 perpendicular to the axis of the shaft 23 is formed on the inner wall of the motor housing 10 by changing its inner diameter. The outer peripheral portion of the surface of the middle housing 30 on the motor side in the axial direction is in contact with the step surface 15 of the motor housing 10. This prevents the axial displacement of the middle housing 30 in the axial direction.

  The middle housing 30 has an insertion hole 33 through which the shaft 23 is inserted. The middle housing 30 rotatably supports the shaft 23 via the main bearing 32. The middle housing 30 is provided with a supply hole 34 for supplying a refrigerant from the space 25 on the motor section 20 side in the motor housing 10 to the space 41 on the compression mechanism section side, and a positioning for positioning the fixed scroll 50. It has an insertion hole 35 into which the pin 70 is inserted.

  An eccentric part 26 is provided at an end of the shaft 23 that extends further toward the compression mechanism than the main bearing 32 provided in the middle housing 30. The eccentric part 26 is formed in a columnar shape, and its center of gravity is provided eccentrically with respect to the rotation axis Ax of the shaft 23. The eccentric part 26 is slidably fitted inside a boss part 42 of the movable scroll 40. A balance weight 27 is provided on the opposite side of the eccentric portion 26 with respect to the rotation axis Ax of the shaft 23.

  The movable scroll 40 and the fixed scroll 50 constituting the compression mechanism are arranged in a space on the opposite side of the middle housing 30 from the motor 20.

  The movable scroll 40 has a disk-shaped movable plate 43 and a spiral movable wrap 44 provided on the movable plate 43. The movable wrap 44 is provided so as to protrude from the movable plate 43 toward the fixed plate 51 of the fixed scroll 50. The orbiting scroll 40 is restricted from rotating by a rotation preventing mechanism (not shown). Therefore, the orbiting scroll 40 is configured to revolve around the rotation axis Ax of the shaft 23 by the torque transmitted from the eccentric portion 26 of the shaft 23 via the boss portion 42.

  A back pressure chamber 45 is provided between the movable plate 43 of the movable scroll 40 and the middle housing 30. The high-pressure refrigerant compressed by the compression mechanism is supplied to the back pressure chamber 45 through a flow path (not shown). Therefore, the movable scroll 40 is pressed toward the fixed scroll 50 by the refrigerant pressure in the back pressure chamber 45.

  The fixed scroll 50 includes a disk-shaped fixed plate 51, a spiral fixed wrap 52 provided on the fixed plate 51, and the middle housing 30 from the outer edge of the fixed plate 51 radially outside the fixed wrap 52. And a fixing portion 53 extending in a cylindrical shape. The fixed portion 53 of the fixed scroll 50 has an insertion hole 54 into which the positioning pin 70 is inserted. One end of the positioning pin 70 is inserted into the insertion hole 35 of the middle housing 30, and the other end is inserted into the insertion hole 54 of the fixed scroll 50. Thus, the fixed scroll 50 is fixed to the middle housing 30 so as not to be relatively displaced in a direction perpendicular to the rotation axis Ax of the shaft 23. Note that a common sliding plate 46 is arranged between the middle housing 30 and the fixed portion 53 of the fixed scroll 50 and the movable plate 43 of the movable scroll 40.

  The fixed wrap 52 of the fixed scroll 50 and the movable wrap 44 of the movable scroll 40 are installed so as to fit each other. Therefore, between the fixed scroll 50 and the movable scroll 40, an operation chamber 47 for compressing the refrigerant is formed. Although not shown, the working chamber 47 is formed in a crescent shape when viewed from the axial direction. When the orbiting scroll 40 revolves, the working chamber 47 orbits from the outside in the radial direction to the inside in the radial direction, and gradually reduces its volume. Thereby, the refrigerant is compressed.

  The fixed scroll 50 is provided with a discharge hole 55 for discharging the refrigerant compressed in the working chamber 47. The discharge hole 55 is provided in a portion of the fixed platen 51 of the fixed scroll 50 where the working chamber 47 has a minimum volume. A thin discharge valve (not shown) for preventing the backflow of the refrigerant and a stopper 56 for regulating the operation range of the discharge valve are provided in the discharge hole 55 and the vicinity thereof.

  As described above, the rear housing 60 is fixed to the axial end of the motor housing 10. The rear housing 60 of the present embodiment supports the fixed scroll 50 while sandwiching the fixed scroll 50 with respect to the middle housing 30. Specifically, a gap is formed between the rear housing 60 and the fixed scroll 50. In FIG. 2, the thickness of the gap is indicated by reference symbol S. An O-ring 63 is provided between the rear housing 60 and the fixed scroll 50 as a seal member. That is, the rear housing 60 supports the fixed scroll 50 via the O-ring 63 which is an elastic body. In the present embodiment, with this configuration, it is possible to reduce the rigidity of the portion where the rear housing 60 supports the fixed scroll 50.

  The O-ring 63 urges the fixed scroll 50 toward the middle housing 30. Thus, when the compressor 1 is not operating, the rattling of the fixed scroll 50 is suppressed by the elastic force of the O-ring 63.

  A high-pressure muffler chamber 64 is provided between the rear housing 60 and the fixed scroll 50. The high-pressure muffler chamber 64 is a space for reducing the discharge pulsation of the refrigerant discharged from the discharge holes 55. The O-ring 63 prevents the refrigerant from flowing between the high-pressure muffler chamber 64 and the space outside the fixed scroll 50. When the compressor 1 operates, the refrigerant compressed in the working chamber 47 is discharged from the discharge hole 55 into the high-pressure muffler chamber 64, and the fixed scroll 50 is urged toward the middle housing 30 by the refrigerant pressure in the high-pressure muffler chamber 64. . Therefore, the middle housing 30 receiving the urging force from the fixed scroll 50 is pressed against the step surface 15 in the axial direction of the motor housing 10.

Next, the operation of the compressor 1 of the present embodiment will be described.
When the coil 24 of the motor unit 20 is energized, the motor stator 21 generates a rotating magnetic field for rotating the motor rotor 22. Thereby, the motor rotor 22 and the shaft 23 rotate around the axis of the shaft 23. When torque is transmitted from the eccentric portion 26 of the shaft 23 to the movable scroll 40 via the boss portion 42, the movable scroll 40 revolves around the rotation axis Ax of the shaft 23. As a result, the working chamber 47 formed between the fixed scroll 50 and the movable scroll 40 gradually reduces its volume while turning from the outside in the radial direction to the inside in the radial direction. Therefore, the refrigerant in the working chamber 47 is compressed. The refrigerant compressed in the working chamber 47 is discharged from the discharge hole 55 to the high-pressure muffler chamber 64, and is discharged from the high-pressure muffler chamber 64 to the piping of the refrigeration cycle via the discharge port 62.

  By the way, in the electric compressor 1, the motor section 20 generates torque against the reaction force of the refrigerant compressed in the working chamber 47. Therefore, the torque fluctuation generated in the motor unit 20 and the working chamber 47 causes vibration. As described above, in the present embodiment, the motor housing 10 and the middle housing 30 are firmly fixed by press-fitting, and the fixed scroll 50 and the middle housing 30 are relatively positioned by the positioning pins 70 in a direction perpendicular to the rotation axis Ax. It is fixed so as not to be displaced. On the other hand, the rear housing 60 supports the fixed scroll 50 via an O-ring 63 which is an elastic body. Therefore, as shown by the broken line V1 in FIG. 1, the vibration generated during the compression of the refrigerant is transmitted from the motor unit 20 and the movable scroll 40 to the fixed scroll 50 via the refrigerant in the working chamber 47, and from there, the middle housing 30 Through the motor housing 10. Further, the vibration generated when the refrigerant is compressed is transmitted to the motor housing 10 via the motor stator 21 of the motor unit 20. That is, as shown by the broken line V1 in FIG. 1, in the configuration of the present embodiment, the path through which the vibration generated during the compression of the refrigerant is transmitted is formed in a loop. In the configuration of the present embodiment, the vibration transmission path is short because the rear housing 60 is not included in the path where the vibration is transmitted from the fixed scroll 50 to the motor housing 10.

  Here, the configuration of the compressor 100 of the comparative example will be described for comparison with the configuration of the compressor 1 of the above-described actual embodiment.

  As shown in FIG. 19, in the comparative example, the rear housing 60 and the fixed scroll 50 are fixed by a first positioning pin 71 so as not to be relatively displaced in a direction perpendicular to the rotation axis Ax of the shaft 23. The rear housing 60 and the fixed scroll 50 are in contact with each other. Therefore, in the configuration of the comparative example, the rigidity of the portion where the rear housing 60 supports the fixed scroll 50 is large.

  The fixed scroll 50 and the middle housing 30 are also fixed by the second positioning pins 70 so as not to be relatively displaced in a direction perpendicular to the rotation axis Ax of the shaft 23. In order to enable both the first positioning pin 71 and the second positioning pin 70 to be installed, a predetermined gap is provided between the radially outer outer wall 31 of the middle housing 30 and the inner wall of the motor housing 10. Is provided.

  Also in FIG. 19, the path through which the vibration generated during the compression of the refrigerant is transmitted is indicated by a broken line V2. In the configuration of the comparative example, the rigidity of the portion where the rear housing 60 supports the fixed scroll 50 is large. Therefore, the vibration generated during the compression of the refrigerant is transmitted from the motor unit 20 and the movable scroll 40 to the fixed scroll 50 via the refrigerant in the working chamber 47, and from there to the motor housing 10 via the rear housing 60. Further, the vibration generated when the refrigerant is compressed is transmitted to the motor housing 10 via the motor stator 21 of the motor unit 20. Thus, in the configuration of the comparative example, the path through which the vibration is transmitted from the fixed scroll 50 to the motor housing 10 is longer than the path of the above-described first embodiment.

  By the way, if all of the components serving as the vibration transmission path are completely rigid, the vibrations cancel each other out, so that the vibrations are not transmitted to the outside. However, actually, since each component is not strictly a perfect rigid body, the vibration is transmitted with a small elastic deformation, so that the vibration is transmitted to the outside.

  In the configuration of the comparative example, the path through which the vibration is transmitted includes the rear housing 60, so that the path is long. Therefore, the phase difference and the amplitude difference between the vibration transmitted from the rear housing 60 to the motor housing 10 and the vibration transmitted from the motor stator 21 to the motor housing 10 increase. Further, since the path through which the vibration is transmitted is long, the torsional rigidity against vibration of the rear housing 60, the motor housing 10, and the like is reduced. As described above, when the torsional rigidity of the rear housing 60 and the motor housing 10 and the like constituting the path through which the vibration is transmitted is reduced, the vibration and noise of the compressor 100 itself may increase. Further, when the compressor 100 is attached to an external member such as an engine block of a vehicle, a force for vibrating the external member from a mounting foot (not shown) provided on the motor housing 10 or the like increases, and the compressor 1 There is a concern that vibration and noise transmitted to external members may increase.

Compared to the compressor 100 of the comparative example described above, the compressor 1 of the present embodiment has the following effects.
(1) In this embodiment, the rigidity of the portion where the motor housing 10 and the middle housing 30 are in contact with or fixed to each other is greater than the rigidity of the portion where the rear housing 60 supports the fixed scroll 50. Have been. According to this configuration, since the rear housing 60 is not included in the path in which the vibration is transmitted from the fixed scroll 50 to the motor housing 10, the vibration transmission path is shorter than in the configuration of the above-described comparative example. Therefore, the phase difference and the amplitude difference between the vibration transmitted from the middle housing 30 side to the motor housing 10 and the vibration transmitted from the motor stator 21 side to the motor housing 10 become small, and the vibration is easily canceled. The torsional torque acting on the motor housing 10 and the like due to vibration is constant, but the vibration transmission path in the motor housing 10 is short, so that the amount of deformation of the motor housing 10 with respect to the torsional torque is small. Become smaller. Therefore, vibration and noise of the compressor 1 itself are reduced. Further, when the compressor 1 is attached to an external member, the force for exciting the external member from the motor housing 10 is reduced. Therefore, the compressor 1 can reduce vibration and noise transmitted from the motor housing 10 to external members.

  (2) In the present embodiment, a gap is formed between the rear housing 60 and the fixed scroll 50, and the rear housing 60 supports the fixed scroll 50 via the O-ring 63. According to this, since the rear housing 60 and the fixed scroll 50 are connected via the O-ring 63, the rigidity of the portion where the rear housing 60 supports the fixed scroll 50 is reduced. Therefore, it is possible to shorten the vibration transmission path without including the rear housing 60 in the path where the vibration is transmitted from the fixed scroll 50 to the motor housing 10. Accordingly, vibration and noise of the compressor 1 itself can be reduced, and vibration and noise transmitted from the compressor 1 to an external member can be reduced.

  (3) In the present embodiment, the O-ring 63 provided between the rear housing 60 and the fixed scroll 50 urges the fixed scroll 50 toward the middle housing 30 and the O-ring 63 between the fixed scroll 50 and the rear housing 60. A high-pressure muffler chamber 64 is formed at the bottom. According to this, when the compressor 1 is not operating, the fixed scroll 50 is urged toward the middle housing 30 by the elastic force of the O-ring 63, so that the fixed scroll 50 can be prevented from rattling.

  When the compressor 1 operates, the refrigerant compressed in the working chamber 47 is discharged into the high-pressure muffler chamber 64, so that the fixed scroll 50 is urged toward the middle housing 30 by the refrigerant pressure in the high-pressure muffler chamber 64. Therefore, the middle housing 30 receiving the urging force from the fixed scroll 50 is pressed against the step surface 15 in the axial direction of the motor housing 10, and the transmission path of the vibration by the middle housing 30 and the motor housing 10 is also provided on the step surface 15. It is formed.

  (4) In the present embodiment, the middle housing 30 and the motor housing 10 are fixed in a direction perpendicular to the rotation axis Ax of the shaft 23 by press fitting. Thereby, the rigidity of the portion where the motor housing 10 and the middle housing 30 are fixed with respect to the load in the direction perpendicular to the rotation axis Ax of the shaft 23 increases. Here, since the vibration generated during the compression of the refrigerant is caused by the torque fluctuation generated in the motor section 20 and the working chamber 47, the component in the direction perpendicular to the rotation axis Ax of the shaft 23 is large. Therefore, by fixing the middle housing 30 and the motor housing 10 in a direction perpendicular to the rotation axis Ax of the shaft 23, it is possible to reliably transmit the vibration in the transmission path of the vibration formed by the middle housing 30 and the motor housing 10. Can be.

(Second to fifth embodiments)
The second to fifth embodiments are different from the first embodiment in the method of fixing the motor housing 10 and the middle housing 30. The other configurations are the same as those of the first embodiment. Only parts different from the embodiment will be described.

  In the second embodiment, as shown in FIG. 3, the motor housing 10 and the middle housing 30 are fixed by bolts 80. Specifically, the bolt 80 is screwed into the female screw 16 provided on the motor housing 10 from the radial outside of the motor housing 10, and presses the radially outer wall 31 of the middle housing 30. Thereby, the motor housing 10 and the middle housing 30 are firmly fixed. A groove in which the bolt 80 fits may be provided on the outer wall 31 on the radially outer side of the middle housing 30.

  In the third embodiment, as shown in FIG. 4, the motor housing 10 and the middle housing 30 are fixed by welding 81. Specifically, welding 81 is performed from the radial outside of the motor housing 10, and the outer wall 31 on the radial outside of the middle housing 30 and the motor housing 10 are firmly fixed by the welding 81.

  In the fourth embodiment, as shown in FIG. 5, the motor housing 10 and the middle housing 30 are fixed by wedges 82. Specifically, a wedge 82 is driven into the gap between the inner wall of the motor housing 10 and the outer wall 31 on the radially outer side of the middle housing 30 from the fixed scroll 50 side. Thereby, the motor housing 10 and the middle housing 30 are firmly fixed. Although not shown, it is preferable to provide a plurality of wedges 82 in the circumferential direction.

  In the fifth embodiment, as shown in FIG. 6, the motor housing 10 and the middle housing 30 are fixed by an adhesive 83. Specifically, an adhesive 83 is applied between the inner wall of the motor housing 10 and the outer wall 31 on the radially outer side of the middle housing 30. Thereby, the motor housing 10 and the middle housing 30 are firmly fixed.

  In the second to fifth embodiments described above, the motor housing 10 and the middle housing 30 are fixed by various fixing methods so as not to be relatively displaced in the direction perpendicular to the rotation axis Ax of the shaft 23. Thereby, the rigidity of the portion where the motor housing 10 and the middle housing 30 are fixed with respect to the load in the direction perpendicular to the rotation axis Ax of the shaft 23 increases. Here, since the vibration generated during the compression of the refrigerant is caused by the torque fluctuation generated in the motor section 20 and the working chamber 47, the component in the direction perpendicular to the rotation axis Ax of the shaft 23 is large. Therefore, by fixing the middle housing 30 and the motor housing 10 in a direction perpendicular to the rotation axis Ax of the shaft 23, it is possible to reliably transmit the vibration in the transmission path of the vibration formed by the middle housing 30 and the motor housing 10. Can be.

(Sixth and seventh embodiments)
The sixth and seventh embodiments also differ from the first embodiment and the like in the method of fixing the motor housing 10 and the middle housing 30. Others are the same as the first embodiment and the like. Only parts different from the first embodiment will be described.

  In the sixth embodiment, as shown in FIGS. 7 and 8, the motor housing 10 and the middle housing 30 can be relatively displaced by the pins 84 in the rotation direction of the shaft 23 and the direction perpendicular to the axis of the shaft 23. Being restrained. Specifically, one end of the pin 84 is inserted into the hole 17 provided on the step surface 15 of the motor housing 10, and the other end is inserted into the hole 36 provided on the middle housing 30.

  In the seventh embodiment, as shown in FIGS. 9 and 10, the motor housing 10 and the middle housing 30 are restrained from being relatively displaced in the rotation direction of the shaft 23 by the key 85. Specifically, the key 85 has a radially inner part partially fitted in the groove 18 provided in the motor housing 10 and a radially outer part partially fitted in the groove 37 provided in the middle housing 30. ing.

  In the sixth and seventh embodiments described above, the rigidity of the motor housing 10 and the middle housing 30 with respect to the load in the rotation direction of the shaft 23 increases. The vibration generated when the refrigerant is compressed has a large component in the rotation direction of the shaft 23. Therefore, the vibration can be transmitted reliably in the transmission path of the vibration formed by the middle housing 30 and the motor housing 10.

(Eighth embodiment)
The eighth embodiment is different from the first embodiment and the like in the method of fixing the motor stator 21 and the motor housing 10, and the rest is the same as the first embodiment and the like. Only parts different from the embodiment and the like will be described.

  As shown in FIG. 11, in the eighth embodiment, in the motor stator 21, the outer diameter of the portion 211 on the middle housing 30 side is formed larger than the outer diameter of the portion 212 on the opposite side to the middle housing 30. I have. Therefore, in the motor stator 21, the part 211 on the middle housing 30 side is fixed to the inner wall of the motor housing 10, and the part 212 on the opposite side to the middle housing 30 is not fixed to the inner wall of the motor housing 10. That is, a gap is formed between the portion 212 of the motor stator 21 opposite to the middle housing 30 and the inner wall of the motor housing 10.

  The portion 211 where the motor stator 21 and the motor housing 10 are fixed is disposed closer to the middle housing 30 than the axial center position 213 of the motor stator 21. Thereby, it is possible to shorten the transmission path of the vibration generated when the refrigerant is compressed in the motor housing 10. Therefore, it is possible to shorten the range of the motor housing 10 where the torsional torque acts. In FIG. 11, an arrow R indicates a range in the motor housing 10 where the torsional torque acts upon the compression of the refrigerant.

  In the eighth embodiment described above, the range of the motor housing 10 where the torsional torque acts upon the compression of the refrigerant is shortened. Therefore, the deformation of the motor housing 10 due to the vibration transmitted from the middle housing 30 to the motor housing 10 and the torsional torque acting on the motor housing 10 due to the vibration transmitted from the motor stator 21 to the motor housing 10. Is suppressed. Accordingly, vibration and noise of the compressor 1 itself can be reduced, and vibration and noise transmitted from the compressor 1 to an external member can be reduced.

(Ninth to eleventh embodiments)
In the ninth to eleventh embodiments, a part of the configuration of the motor housing 10 is changed from the first embodiment and the like, and the other configurations are the same as the first embodiment and the like. Only the parts different from the form will be described.

  In the ninth to eleventh embodiments, as shown in FIGS. 12 to 17, the motor housing 10 has a reinforcing portion 90 at a part of the cylindrical portion 12. The reinforcing portion 90 extends from a position corresponding to the position where the motor stator 21 is fixed in the cylindrical portion 12 of the motor housing 10 to a position corresponding to the position where the middle housing 30 is fixed. This is a portion configured to have large torsional rigidity.

In the ninth embodiment, as shown in FIGS. 12 and 13, the reinforcing portion 90 of the motor housing 10 is configured by a thick portion 91 having a larger thickness than a portion of the motor housing 10 other than the reinforcing portion 90. I have. Here, in the cylindrical portion 12 of the motor housing 10, the thickness of a portion closer to the rear housing 60 than the thick portion 91 is set to t1. The thickness of the thick portion 91 of the cylindrical portion 12 of the motor housing 10 is defined as t2. In the cylindrical portion 12 of the motor housing 10, the thickness of a portion on the bottom 11 side of the thick portion 91 is defined as t3.
At this time, the relationships of t2> t1 and t2> t3 hold.

  In the tenth embodiment, as shown in FIGS. 14 and 15, the reinforcing portion 90 of the motor housing 10 is configured by a rib 92 provided on an outer wall of the motor housing 10. The ribs 92 are formed to extend in the axial direction of the motor housing 10, and a plurality of ribs 92 are provided in the circumferential direction of the motor housing 10. The cylindrical portion 12 of the motor housing 10 and the rib 92 are formed integrally.

  In the eleventh embodiment, as shown in FIGS. 16 and 17, the reinforcing portion 90 of the motor housing 10 is configured by a reinforcing member 93 provided on the outer wall of the motor housing 10. The reinforcing member 93 is formed in a cylindrical shape, and is provided so as to surround a radial outside of the motor housing 10. The motor housing 10 and the reinforcing member 93 are formed as separate members, and are fixed by, for example, press fitting or shrink fitting.

  In the ninth to eleventh embodiments described above, it is possible to increase the torsional rigidity of the portion of the motor housing 10 serving as the vibration transmission path by the reinforcing portion 90. Therefore, the deformation of the motor housing 10 due to the vibration transmitted from the middle housing 30 to the motor housing 10 and the torsional torque acting on the motor housing 10 due to the vibration transmitted from the motor stator 21 to the motor housing 10. Is suppressed. Accordingly, vibration and noise of the compressor 1 itself can be reduced, and vibration and noise transmitted from the compressor 1 to an external member can be reduced.

  Further, in the ninth to eleventh embodiments, it is possible to effectively increase the rigidity in a range where the torsional torque acts upon the compression of the refrigerant without increasing the rigidity of the motor housing 10 as a whole. It is. This can minimize cost increases such as material costs.

(Twelfth embodiment)
The twelfth embodiment is different from the first embodiment and the like in the method of fixing the fixed scroll 50 and the middle housing 30. The other features are the same as those of the first embodiment and the like. Only the parts different from the form will be described.

  As shown in FIG. 18, in the twelfth embodiment, the fixed scroll 50 and the middle housing 30 are fixed by bolts 73. The bolt 73 passes through the bolt insertion hole 38 of the middle housing 30 and is screwed into a screw hole 57 provided in the fixed portion 53 of the fixed scroll 50. Accordingly, the displacement of the fixed scroll 50 in the axial direction with respect to the middle housing 30 is restricted.

  In the twelfth embodiment, the displacement of the fixed scroll 50 and the middle housing 30 in the direction perpendicular to the rotation axis Ax of the shaft 23 is restricted by the positioning pin 70. In the configuration of the twelfth embodiment, if the bolt 73 for fixing the fixed scroll 50 and the middle housing 30 has a function of restricting the displacement of the shaft 23 in the direction perpendicular to the rotation axis Ax, the positioning pin is used. It is also possible to abolish 70.

(Other embodiments)
The present invention is not limited to the embodiments described above, and can be appropriately modified within the scope described in the claims. In addition, the above embodiments are not irrelevant to each other, and can be appropriately combined unless a combination is clearly not possible. In each of the above embodiments, it is needless to say that the elements constituting the embodiment are not necessarily essential, unless otherwise clearly indicated as essential or in principle considered to be clearly essential. No. In each of the above embodiments, when a numerical value such as the number, numerical value, amount, range, or the like of the constituent elements of the exemplary embodiment is referred to, it is particularly limited to a specific number when it is clearly stated that it is essential and in principle. The number is not limited to the specific number unless otherwise specified. Further, in each of the above embodiments, when referring to the shape of components and the like, the positional relationship, and the like, the shape, It is not limited to a positional relationship or the like.

  (1) In the above embodiments, the O-ring 63 is illustrated as a seal member disposed between the rear housing 60 and the fixed scroll 50. However, the seal member is not limited thereto, and may be, for example, a gasket.

  (2) In each of the above embodiments, the outer wall 31 on the radially outer side of the middle housing 30 and the inner wall of the motor housing 10 are fixed by a fixing method including press-fitting, bolting, welding, wedge, or bonding. On the other hand, in another embodiment, the outer wall 31 on the radially outer side of the middle housing 30 and the inner wall of the motor housing 10 need not be fixed. Even in this case, the fixed scroll 50 is urged toward the middle housing 30 by the pressure of the high-pressure muffler chamber 64 formed between the rear housing 60 and the fixed scroll 50, so that the middle housing 30 is Is pressed against the step surface 15 in the direction. Thus, vibration is transmitted between the middle housing 30 and the motor housing 10 via the step surface 15. Therefore, it is possible to form a vibration transmission path by the motor section 20 → the movable scroll 40 → the fixed scroll 50 → the middle housing 30 → the motor housing 10 → the motor section 20.

(Summary)
According to a first aspect of the present invention, a motor housing, a motor unit, a middle housing, an eccentric unit, a movable scroll, a fixed scroll, and a rear scroll are provided. A housing is provided. The motor housing is formed in a bottomed cylindrical shape. The motor unit includes a motor stator fixed to an inner wall of the motor housing, a motor rotor rotatably provided inside the motor stator, and a shaft that rotates with the motor rotor. The middle housing abuts or is fixed to the inner wall of the motor housing and rotatably supports the shaft. The eccentric portion is provided at an end of the shaft eccentrically with respect to the rotation axis of the shaft. The orbiting scroll is arranged on the opposite side of the middle housing from the motor section, and receives torque from the eccentric section to revolve around the rotation axis of the shaft. The fixed scroll is fixed to the middle housing so as not to be relatively displaced in a direction perpendicular to the rotation axis of the shaft, and forms a working chamber that compresses the refrigerant together with the movable scroll. The rear housing is fixed to an axial end of the motor housing, and supports the fixed scroll with respect to the middle housing. The rigidity of the portion where the motor housing and the middle housing abut or are fixed is larger than the rigidity of the portion where the rear housing supports the fixed scroll.

  According to the second aspect, a gap is formed between the rear housing and the fixed scroll, and the rear housing supports the fixed scroll via the seal member.

  This allows the rear housing and the fixed scroll to be connected via the seal member, so that the rigidity of the portion where the rear housing supports the fixed scroll is reduced. Therefore, it is possible to shorten the vibration transmission path without including the rear housing in the path where the vibration is transmitted from the fixed scroll to the motor housing. Therefore, vibration and noise of the compressor itself can be reduced, and vibration and noise transmitted from the compressor to external members can be reduced.

  According to the third aspect, the seal member provided between the rear housing and the fixed scroll biases the fixed scroll toward the middle housing and forms a high-pressure muffler chamber between the fixed scroll and the rear housing. ing.

  According to this, when the compressor is not operating, the fixed scroll is urged toward the middle housing by the elastic force of the seal member, so that the fixed scroll can be prevented from rattling.

  Further, when the compressor operates, the refrigerant compressed in the working chamber is discharged into the high-pressure muffler chamber, so that the fixed scroll is urged toward the middle housing by the refrigerant pressure in the high-pressure muffler chamber. Therefore, the middle housing that has received the urging force from the fixed scroll is pressed against the step surface in the axial direction of the motor housing, so that a vibration transmission path is also formed by the middle housing and the motor housing there.

  According to the fourth aspect, the middle housing and the motor housing are fixed in a direction perpendicular to the rotation axis of the shaft by a fixing method including press-fitting, bolting, welding, wedge, or bonding.

  Accordingly, the rigidity of the portion where the motor housing and the middle housing are fixed to a load in a direction perpendicular to the rotation axis of the shaft increases. Here, the vibration generated during the compression of the refrigerant is caused by the torque fluctuation generated in the motor section and the working chamber, and is a vibration in a direction perpendicular to the rotation axis of the shaft. Therefore, by fixing the middle housing and the motor housing in a direction perpendicular to the rotation axis of the shaft, the vibration can be transmitted reliably in the vibration transmission path formed by the middle housing and the motor housing.

  According to the fifth aspect, the motor housing and the middle housing are provided with pins or keys for restraining relative displacement in a direction perpendicular to the rotation axis of the shaft.

  Thereby, the rigidity of the motor housing and the middle housing against the load in the rotational direction of the shaft increases. The vibration generated when the refrigerant is compressed has a large component in the rotation direction of the shaft. Therefore, the vibration can be reliably transmitted in the transmission path of the vibration formed by the middle housing and the motor housing.

  According to the sixth aspect, the torsional rigidity of the motor housing is higher than that of other parts from the position corresponding to the position where the motor stator is fixed to the position corresponding to the position where the middle housing is fixed. It has a large configured reinforcement.

  According to this, it is possible to increase the torsional rigidity of the portion of the motor housing that becomes a vibration transmission path by the reinforcing portion. Therefore, the deformation of the motor housing is suppressed with respect to the vibration transmitted from the middle housing side to the motor housing and the torsional torque acting on the motor housing by the vibration transmitted from the motor stator side to the motor housing. Therefore, vibration and noise of the compressor itself can be reduced, and vibration and noise transmitted from the compressor to an external member can be reduced.

  Further, with this configuration, it is possible to effectively increase the rigidity in a range where the torsional torque acts upon the compression of the refrigerant without increasing the rigidity of the motor housing as a whole. This can minimize cost increases such as material costs.

  According to the seventh aspect, the reinforcing portion is constituted by a thick portion of the motor housing that is thicker than a portion other than the reinforcing portion, or a rib or a reinforcing member provided on an outer wall of the motor housing.

  According to this, a thick portion, a rib, or a reinforcing member is exemplified as the reinforcing portion.

  According to the eighth aspect, the portion where the motor stator and the motor housing are fixed is disposed closer to the middle housing than the axial center position of the motor stator.

  According to this, it is possible to shorten a portion of the motor housing that serves as a vibration transmission path. Therefore, the deformation of the motor housing is suppressed with respect to the vibration transmitted from the middle housing side to the motor housing and the torsional torque acting on the motor housing by the vibration transmitted from the motor stator side to the motor housing. Therefore, vibration and noise of the compressor itself can be reduced, and vibration and noise transmitted from the compressor to an external member can be reduced.

DESCRIPTION OF SYMBOLS 1 Electric scroll compressor 10 Motor housing 20 Motor part 23 Shaft 26 Eccentric part 30 Middle housing 40 Movable scroll 47 Working chamber 50 Fixed scroll 60 Rear housing

Claims (8)

In an electric scroll compressor that compresses a refrigerant,
A bottomed cylindrical motor housing (10);
It has a motor stator (21) fixed to the inner wall of the motor housing, a motor rotor (22) rotatably provided inside the motor stator, and a shaft (23) that rotates together with the motor rotor. A motor unit (20);
A middle housing (30) abutting or fixed to an inner wall of the motor housing and rotatably supporting the shaft;
An eccentric portion (26) provided at an end of the shaft eccentrically with respect to the rotation axis (Ax) of the shaft;
A movable scroll (40) that is arranged on the opposite side to the motor section with respect to the middle housing, and that receives torque from the eccentric section and revolves around a rotation axis of the shaft;
A fixed scroll (50) fixed to the middle housing so as not to be relatively displaced in a direction perpendicular to the rotation axis of the shaft, and forming a working chamber (47) for compressing refrigerant together with the movable scroll;
A rear housing (60) fixed to an axial end of the motor housing and supporting the fixed scroll with respect to the middle housing.
An electric scroll compressor, wherein the rigidity of a portion where the motor housing and the middle housing abut or are fixed is larger than the rigidity of a portion where the rear housing supports the fixed scroll. .   The electric motor according to claim 1, wherein a gap (S) is formed between the rear housing and the fixed scroll, and the rear housing supports the fixed scroll via a seal member (63). Scroll compressor.   The seal member provided between the rear housing and the fixed scroll urges the fixed scroll toward the middle housing, and forms a high-pressure muffler chamber (64) between the fixed scroll and the rear housing. The electric scroll compressor according to claim 2, which is formed.   The middle housing and the motor housing are fixed in a direction perpendicular to the rotation axis of the shaft by a fixing method including press fitting, bolts (80), welding (81), wedges (82), or bonding (83). The electric scroll compressor according to any one of claims 1 to 3, wherein:   5. The motor housing and the middle housing each include a pin (84) or a key (85) for restraining relative displacement in a direction perpendicular to a rotation axis of the shaft. 6. 4. The electric scroll compressor according to claim 1.   The motor housing has a torsion rigidity greater than other portions from a position corresponding to the position where the motor stator is fixed to a position corresponding to the position where the middle housing is fixed. The electric scroll compressor according to any one of claims 1 to 5, comprising a part (90).   The reinforcing portion is constituted by a thick portion (91) having a greater thickness than a portion of the motor housing other than the reinforcing portion, or a rib (92) or a reinforcing member (93) provided on an outer wall of the motor housing. The electric scroll compressor according to claim 6, wherein:   The part (211) to which the motor stator and the motor housing are fixed is disposed closer to the middle housing than an axial center position (213) of the motor stator. The electric scroll compressor according to any one of the above.

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