JP2016079809A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce mechanical loss at a vehicular electric compressor 1 caused by sliding motion between a low stage side stator 21 an a rotor 22.SOLUTION: A low stage side stator 21 is provided with an operation chamber 30 and a rotor 22 is provided with low stage side teeth 51. A high stage side stator 23 is provided with an operation chamber 40 and the rotor 22 is provided with high stage side teeth 52. The low stage side stator 21 is formed with a groove 35 enclosing the operation chamber 30. Lubricant oil showing a higher pressure than that of middle pressure refrigerant is guided to the groove 35 to generate a load pressing the rotor 22 toward the high stage side stator 23. With this arrangement as above, it is possible to reduce the load pressing the rotor 22 toward the low stage side stator 21 by a differential pressure SA between a pressure of high pressure refrigerant in the compression chamber 40b and a pressure of the middle pressure refrigerant in the compression chamber 30b.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor.

  2. Description of the Related Art Conventionally, in a two-stage compression type scroll compressor, two oscillating scrolls are back-to-back, and a fixed scroll is opposed to each of the oscillating scrolls to form two compression chambers. There is one that leads to the other compression chamber and compresses it in two stages (for example, see Patent Document 1).

  In this structure, a partition plate whose position is fixed with respect to the fixed scroll is provided between the two swing scrolls, and an inner seal ring and an outer seal ring are provided between the partition plate and each swing scroll. Back pressure chambers partitioned by each are provided. The two compression chambers are communicated with the respective back pressure chambers, and a gas load slightly exceeding the thrust gas load generated in the compression chambers is generated in the respective back pressure chambers.

  Thereby, a floating force is generated in each of the swing scrolls, and the swing scrolls are pressed against the fixed scrolls with a minute load. Therefore, the sliding loss occurring at the spiral tip in each compression chamber can be greatly reduced, and the possibility of abnormal wear and seizure at the spiral tooth tip can be eliminated.

JP 2007-23827 A

  In the compressor of the above-mentioned patent document 1, as described above, the gas pressure slightly exceeding the thrust gas load generated in the compression chamber by communicating the two compression chambers with the respective back pressure chambers is applied to each back pressure chamber. generate. This can reduce the sliding loss generated at the tip of the spiral in each compression chamber, but it is necessary to provide a back pressure chamber between the partition plate and each swing scroll. The structure becomes complicated.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a compressor that achieves both simplification of the structure and suppression of sliding loss.

  In order to achieve the above object, according to the first aspect of the present invention, the low stage side stator (21), the high stage side stator (23), and the low stage side stator and the high stage side stator are disposed and revolved. A rotor (22) supported so as to be capable of movement, and either one of the low-stage stator and the rotor has a low-stage working chamber (30) formed to extend in a spiral shape. The other side is provided with a lower stage tooth portion (51) projecting into the lower stage working chamber and spirally formed along the direction in which the lower stage working chamber extends. Along with the movement, one of the low-stage side tooth portion and the low-stage working chamber is displaced with respect to the other, and a refrigerant containing lubricating oil is sucked into the low-stage working chamber and compressed to compress the refrigerant. Is discharged as an intermediate pressure refrigerant, and the upper stage stator and rotor Either one is provided with a high-stage working chamber (40) formed so as to extend in a spiral shape, and the other is a direction projecting into the high-stage working chamber and extending the high-stage working chamber. A high-stage tooth part (52) formed in a spiral shape is provided along the rotor, and one of the high-stage tooth part and the high-stage working chamber is displaced with respect to the other in accordance with the revolution movement of the rotor. A compressor that sucks intermediate pressure refrigerant into the high-stage working chamber, compresses it, and discharges it as high-pressure refrigerant, provided in at least one of the rotor and the low-stage stator, A groove (35) formed so as to surround the oil passage, and an oil passage (66, for guiding lubricating oil having a pressure higher than that of the intermediate pressure refrigerant to the groove in order to generate a load for pushing the rotor toward the high-stage side stator. 45, 36).

  According to the first aspect of the present invention, a load that pushes the rotor toward the high-stage side stator is generated by introducing lubricating oil having a pressure higher than that of the intermediate pressure refrigerant into the groove.

  Here, the pressure of the high-pressure refrigerant in the high-stage working chamber is higher than the pressure of the intermediate-pressure refrigerant in the low-stage working chamber. For this reason, the load which pushes a rotor to the low stage side stator side is generated by the differential pressure between the pressure of the high pressure refrigerant and the pressure of the intermediate pressure refrigerant.

  In contrast, according to the first aspect of the present invention, as described above, the lubricating oil having a pressure higher than that of the intermediate pressure refrigerant is guided to the groove, thereby pushing the rotor toward the high stage side stator (ie, the force). ). For this reason, the load which pushes a rotor to the low stage side stator side by differential pressure | voltage can be reduced. Thereby, the sliding loss (mechanical loss) which arises by the sliding of the rotor with respect to a low stage side stator can be reduced. In this specification, sliding means moving while sliding.

  In addition, in the first aspect of the invention, a common rotor is used in the low-stage working chamber and the high-stage working chamber to suck, compress, and discharge the refrigerant. For this reason, the structure of the compressor can be simplified.

  As described above, both simplification of the compressor structure and suppression of sliding loss can be achieved.

  Specifically, in the invention described in claim 3, the intermediate pressure passages (37a, 37b) for supplying the intermediate pressure refrigerant discharged from the low stage working chamber to the high stage working chamber are provided. The passage side and the low stage side working chamber side communicate with each other through the low stage side stator and the rotor, and the groove is arranged between the low stage side working chamber and the intermediate pressure passage. And

  According to the invention described in claim 3, the oil film is formed so as to surround the low-stage working chamber by sliding the rotor with respect to the low-stage side stator along with the revolution movement of the rotor. For this reason, the oil film can prevent the refrigerant from entering the low-stage working chamber from the intermediate pressure passage through the rotor and the low-stage stator. Therefore, the efficiency of refrigerant compression can be improved.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a figure which shows the cross-sectional structure of the vehicle-mounted electric compressor in one Embodiment of this invention. It is II-II sectional drawing in FIG. It is sectional drawing in the comparative example of the said embodiment, Comprising: It is drawing corresponding to FIG.

  Hereinafter, an embodiment of an in-vehicle electric compressor 1 according to the present invention will be described with reference to FIGS. 1 and 2.

  The on-vehicle electric compressor 1 of the present embodiment constitutes a refrigeration cycle device for an on-vehicle air conditioner that circulates refrigerant together with a cooler, a pressure reducing valve, and an evaporator. The refrigerant of the present embodiment contains lubricating oil. The lubricating oil serves to lubricate the bearings of the in-vehicle electric compressor 1 and the sliding portion of the compression mechanism.

  Specifically, the on-vehicle electric compressor 1 includes an electric motor 10 and a compression mechanism 20 as shown in FIGS. 1 and 2. The electric motor 10 is a synchronous AC motor including a front housing 11, a rotating shaft 12, a rotor 13, an armature 14, and a bearing 15.

  The front housing 11 is formed in a cylindrical shape having a bottom portion 11a that closes one side in the axial direction and an opening portion 11d that opens on the other side in the axial direction. The bottom 11a is provided with an annular protrusion 11b that protrudes on the other side in the axial direction and is formed in an annular shape with the axis S as the center. The rotating shaft 12 is accommodated in the front housing 11. The axis S of the rotary shaft 12 coincides with the axis of the front housing 11. The other side in the axial direction of the rotary shaft 12 passes through a through hole 21a of a low-stage stator 21 described later. The other end portion in the axial direction of the rotary shaft 12 constitutes a crank portion 12a. The crank portion 12 a is connected to the rotor 22 with the rotation center of the rotor 22 being offset from the rotation center of the rotation shaft 12. Thus, the rotor 22 is supported by the front housing 11 and the low stage side stator 21 via the rotary shaft 12 so as to be capable of revolving.

  The rotor 13 is formed in a cylindrical shape centered on the axis of the rotating shaft 12. The rotating shaft 12 passes through the hollow portion of the rotor 13. The rotor 13 is supported by the rotating shaft 12. The armature 14 has a plurality of armature coils 14b wound around a stator core 14a. The plurality of armature coils 14b are arranged at the same interval in the circumferential direction around the axis S. The armature 14 is supported on the inner wall 11 c of the front housing 11. The bearing 15 is disposed in the annular protrusion 11b, and rotatably supports one side in the axial direction of the rotating shaft 12.

  The compression mechanism 20 includes a low stage side stator 21, a rotor 22, a high stage side stator 23, and a rear housing 24.

  The low stage side stator 21 is arranged on the other side in the axial direction with respect to the electric motor 10 and closes the opening 11 d of the front housing 11. As shown in FIGS. 1 and 2, the low-stage stator 21 is formed in a disc shape centered on the axis S (see FIG. 1). The low stage side stator 21 is fixed to the front housing 11 with its thickness direction aligned with the axial direction. The low stage side stator 21 is formed with a working chamber 30 as a low stage side working chamber. The working chamber 30 is a groove formed so as to be recessed from the other axial side of the low-stage side stator 21 to the one axial side. The working chamber 30 is formed so as to extend in a spiral shape about the axis S.

  A low-stage discharge port 31 is formed in the low-stage stator 21. The low-stage discharge port 31 communicates between the suction chamber 30 a of the working chamber 30 and the inside of the front housing 11. A low-stage discharge valve 32 and a stopper 33 are disposed on the front housing 11 side of the low-stage discharge port 31. The low-stage discharge valve 32 is a check valve that restricts the flow of refrigerant from the front housing 11 side into the low-stage discharge port 31. The stopper 33 prevents the low-stage discharge valve 32 from opening the low-stage discharge port 31 too much. A suction passage 34 is formed in the lower stage side stator 21. The suction passage 34 communicates between the suction chamber 30a of the working chamber 30 and the refrigerant outlet of the evaporator.

  The suction passage forming portion 34 a that forms the suction passage 34 in the low stage side stator 21 is formed so as to protrude radially outward with respect to the front housing 11 and the high stage side stator 23. The low-stage stator 21 is provided with a through hole 21 a that passes through the rotary shaft 12. The through hole 21 a is formed so as to penetrate the low stage side stator 21 in the axial direction.

  As shown in FIG. 1, a groove 35 is formed on the other side in the axial direction of the low stage side stator 21. The groove 35 is formed so as to be recessed on one side in the axial direction of the low stage side stator 21. The groove 35 is formed in an annular shape surrounding the working chamber 30 around the axis S (see FIG. 2). Specifically, the outer periphery and inner periphery of the groove 35 are formed concentrically around the axis S. The groove 35 is disposed between the intermediate pressure passages 37 a and 37 b and the working chamber 30.

  The low stage side stator 21 is provided with an oil passage 36 for guiding lubricating oil to the groove 35. The oil passage 36 is provided on the opposite side of the suction passage 34 with respect to the rotating shaft 12. The formation part 36a which forms the oil passage 36 among the low stage side stators 21 is located in the intermediate pressure passage 37a as shown in FIG.

  In this embodiment, the inside of the front housing 11 and the inside of the suction chamber 40a of the working chamber 40 are communicated through intermediate pressure passages 37a and 37b (see FIG. 2). The intermediate pressure passages 37a and 37b are disposed with an offset of 45 degrees in the circumferential direction around the axis (see FIG. 2). The intermediate pressure passage 37 a is provided on the opposite side of the suction passage 34 with respect to the rotating shaft 12.

  Here, the intermediate pressure passage 37 a and the suction chamber 30 a communicate with each other through the rotor end plate 50 and the low-stage stator 21. The intermediate pressure passage 37 a and the suction chamber 40 a communicate with each other through the rotor end plate 50 and the high stage side stator 23.

  Specifically, the intermediate pressure passage 37a includes intermediate pressure chambers 38a and 39a (see FIG. 1). The intermediate pressure chamber 38a is formed so as to penetrate the low stage side stator 21 in the axial direction. The intermediate pressure chamber 39a is disposed on the other side in the axial direction with respect to the intermediate pressure chamber 38a. The intermediate pressure chamber 39 a is formed between the rotor end plate 50 and the high stage side stator 23 on the radially outer side centered on the axis with respect to the rotor end plate 50.

  The intermediate pressure passage 37b and the suction chamber 30a communicate with each other through the rotor end plate 50 and the low-stage stator 21. The intermediate pressure passage 37 b and the suction chamber 40 a communicate with each other through the rotor end plate 50 and the high stage side stator 23.

  Specifically, the intermediate pressure passage 37b is composed of first and second intermediate pressure chambers (not shown), similarly to the intermediate pressure passage 37a. The first intermediate pressure chamber corresponds to the intermediate pressure chamber 38a, and the second intermediate pressure chamber corresponds to the intermediate pressure chamber 39a.

  The high stage side stator 23 is disposed on one side in the axial direction with respect to the low stage side stator 21. The high stage side stator 23 is formed in a disc shape centered on the axis S. The high stage side stator 23 is fixed to the low stage side stator 21 in a state where the thickness direction thereof coincides with the axial direction. Thereby, the high stage side stator 23 and the low stage side stator 21 respectively support the rotor 22 so that revolving motion is possible. A working chamber 40 as a high-stage working chamber is formed in the high-stage stator 23. The working chamber 40 is a groove portion formed so as to be recessed from one axial direction side to the other axial direction side of the high stage side stator 23. The working chamber 40 is formed to extend in a spiral shape about the axis S.

  A high stage discharge port 41 is formed in the high stage side stator 23. The high-stage discharge port 41 communicates between the compression chamber 40 b and the discharge chamber 42 in the working chamber 40.

  A high-stage discharge valve 43 and a stopper 44 are arranged on the discharge chamber 42 side of the high-stage discharge port 41. The high-stage discharge valve 43 is a check valve that restricts the flow of refrigerant from the discharge chamber 42 side into the high-stage discharge port 41. The stopper 44 prevents the high-stage discharge valve 43 from opening the high-stage discharge port 41 too much. The high stage side stator 23 is provided with an oil passage 45 for guiding lubricating oil to the oil passage 36.

  The rotor 22 is disposed between the low stage side stator 21 and the high stage side stator 23. The rotor 22 includes a rotor end plate 50, a low stage side tooth part 51, and a high stage side tooth part 52.

  The rotor end plate 50 is disposed between the low-stage side stator 21 and the high-stage side stator 23 and is formed in a disc shape centered on the axis S. The rotor end plate 50 is disposed so that the plate pressure direction thereof coincides with the axial direction. A recess 60 into which the crank portion 12a of the rotary shaft 12 is fitted is formed. The rotor end plate 50 is formed to be covered from the outer side in the radial direction around the axis S by the high stage side stator 23. The low-stage side tooth portion 51 is a low-stage side tooth portion that protrudes into the working chamber 30 from the rotor end plate 50 and is formed in a spiral shape over the direction in which the working chamber 30 extends. The low stage side tooth portion 51 together with the working chamber 30 constitutes a known low stage side compression mechanism that compresses the refrigerant sucked from the evaporator side through the suction passage 34.

  Here, a suction chamber 30 a for sucking refrigerant from the evaporator side is formed outside the working chamber 30 of the lower stage side stator 21 in the radial direction centering on the axis with respect to the lower stage tooth portion 51. A compression chamber 30b for compressing the sucked refrigerant is formed in the working chamber 30 on the radially inner side centering on the axis with respect to the lower-stage tooth portion 51.

  The high-stage side tooth portion 52 is a high-stage side tooth portion that protrudes from the rotor end plate 50 into the working chamber 40 and is formed in a spiral shape in the direction in which the working chamber 40 extends. The high stage side tooth part 52 constitutes a known high stage side compression mechanism that compresses the intermediate pressure refrigerant discharged from the working chamber 30 together with the working chamber 40.

  Here, a suction chamber 40a for sucking in the intermediate pressure refrigerant is formed outside the working chamber 40 of the high-stage side stator 23 in the radial direction centering on the axis with respect to the high-stage side tooth portion 52. A compression chamber 40b for compressing the sucked intermediate pressure refrigerant is formed on the inside of the working chamber 40 in the radial direction centering on the axis with respect to the higher stage tooth portion 52.

  The rear housing 24 has a recess 60 that opens to one side in the axial direction. In the rear housing 24, the opening of the recess 60 is covered with the high-stage stator 23. The recess 60 is covered with the high stage side stator 23 to form the discharge chamber 42.

  A hole 62 is formed in the rear housing 24 on the other side in the axial direction with respect to the recess 60. The hole 62 constitutes a high-stage discharge port 61 that opens to the outside. The hole 62 and the discharge chamber 42 communicate with each other through the refrigerant passage 63. A lubricating oil separator 64 is provided in the hole 62. The lubricating oil separator 64 separates the lubricating oil from the high-pressure refrigerant that has flowed from the discharge chamber 42 through the refrigerant passage 63. As the lubricating oil separator 64 of the present embodiment, a centrifugal lubricating oil separator is used.

  Here, an oil storage chamber 65 for storing the lubricating oil separated by the lubricating oil separator 64 is provided on the bottom side of the hole 62. The rear housing 24 is provided with an oil passage 66 for guiding the lubricating oil in the oil storage chamber 65 to the oil passage 45.

  In addition, the front housing 11, the low stage side stator 21, the rotor 22, the high stage side stator 23, and the rear housing 24 of this embodiment are formed with metals, such as aluminum.

  Next, the operation of the on-vehicle electric compressor 1 of the present embodiment will be described.

  First, when a three-phase alternating current is output from an inverter circuit (not shown) to the plurality of armature coils 14b of the armature 14 of the electric motor 10, a rotating magnetic field is generated from the plurality of armature coils 14b. The rotor 13 rotates in synchronization with the rotating magnetic field. Along with this, the rotating shaft 12 rotates.

  At this time, the rotor 22 is driven by the rotating shaft 12 and revolves (that is, turns). Along with this, the lower stage tooth portion 51 is displaced in the working chamber 30. For this reason, each shape and volume of the suction chamber 30a and the compression chamber 30b change. As a result, a compression step is performed in which the refrigerant is sucked, compressed, and discharged by the low-stage side tooth portion 51.

  First, the air is sucked from the refrigerant outlet side of the evaporator through the suction passage 34 to the suction chamber 30a side of the working chamber 30. The sucked refrigerant is moved and compressed in the working chamber 30 from the suction chamber 30a to the compression chamber 30b by the displacement of the low-stage side tooth portion 51. When the compressed refrigerant (hereinafter referred to as intermediate pressure refrigerant) opens the low-stage discharge valve 32 by the pressure, the intermediate pressure refrigerant is discharged from the working chamber 30 into the front housing 11. Then, the intermediate pressure refrigerant flows as indicated by an arrow Ra and flows into the intermediate pressure passages 37a and 37b.

  On the other hand, the high-stage side tooth portion 52 is displaced in the working chamber 40 as the rotor 22 revolves. For this reason, each shape and volume of the suction chamber 40a and the compression chamber 40b change. As a result, a compression process is performed in which the refrigerant is sucked, compressed, and discharged by the high-stage side tooth portion 52.

  First, the intermediate refrigerant in the intermediate pressure passages 37 a and 37 b is sucked into the suction chamber 40 a of the working chamber 40 through the space between the rotor end plate 50 and the high stage side stator 23. The sucked refrigerant is transferred from the suction chamber 40a to the compression chamber 40b in the working chamber 40 by the displacement of the high-stage side tooth portion 52 and compressed. When the compressed refrigerant (hereinafter referred to as high-pressure refrigerant) opens the high-stage discharge valve 43 by its pressure, the high-pressure refrigerant is discharged from the compression chamber 40 b into the discharge chamber 42 through the high-stage discharge port 41.

  Thereafter, the high-pressure refrigerant flows into the hole 62 through the refrigerant passage 63, and the high-pressure refrigerant is separated into refrigerant and lubricating oil by the lubricating oil separator 64. The separated refrigerant flows to the refrigerant inlet side of the cooler through the high stage discharge port 61.

  On the other hand, the lubricating oil separated by the lubricating oil separator 64 is stored in the oil storage chamber 65. The lubricating oil in the oil storage chamber 65 flows into the groove 35 through the oil passage 66, the oil passage 45, and the oil passage 36.

  Here, the pressure of the high-pressure refrigerant in the compression chamber 40 b of the working chamber 40 is higher than the pressure of the intermediate-pressure refrigerant in the compression chamber 30 b of the working chamber 30. For this reason, a thrust load F1 that pushes the rotor 22 toward the low-stage stator 21 side (that is, one side in the axial direction) by a differential pressure between the pressure of the high-pressure refrigerant and the pressure of the intermediate-pressure refrigerant (hereinafter referred to as differential pressure SA). Will occur.

  Here, the pressure of the lubricating oil in the groove 35 is higher than the pressure of the intermediate pressure refrigerant. For this reason, the load F2 which pushes the rotor 22 to the high stage side stator 23 side by the pressure of the lubricating oil in the groove 35 is generated. Thereby, the thrust load F1 generated by the differential pressure SA can be reduced by the load F2. Therefore, the load applied from the rotor 22 to the low stage side stator 21 can be reduced.

  On the other hand, the rotor 22 slides on the radially inner side and the radially outer side of the groove 35 in the lower stage stator 21 by the revolving motion of the rotor 22. For this reason, an oil film made of lubricating oil is formed between the rotor 22 and the lower stage side stator 21 on the radially inner side and the radially outer side of the groove 35. Therefore, an oil film is formed between the intermediate pressure passages 37a and 37b and the working chamber 30 so as to surround the working chamber 30 (that is, the suction chamber 30a and the compression chamber 30b).

  Here, the intermediate pressure passages 37 a and 37 b and the suction chamber 30 a among the working chambers 30 communicate with each other through the rotor 22 and the low-stage side stator 21. For this reason, the refrigerant may enter the suction chamber 30a from the intermediate pressure passages 37a and 37b due to a differential pressure between the pressure in the intermediate pressure passages 37a and 37b and the pressure in the suction chamber 30a.

  In contrast, in the present embodiment, as described above, an oil film is formed between the intermediate pressure passages 37a and 37b and the working chamber 30 by the lubricating oil having a pressure higher than that of the intermediate pressure refrigerant. For this reason, it is possible to prevent the oil film from entering the suction chamber 30a from the intermediate pressure passages 37a and 37b.

  According to the present embodiment described above, the in-vehicle electric compressor 1 is disposed between the low stage side stator 21, the high stage side stator 23, the low stage side stator 21, and the high stage side stator 23 to revolve. And a rotor 22 that is supported for movement. The low-stage stator 21 is provided with a working chamber 30 formed so as to extend in a spiral shape, and the rotor 22 is spirally formed so as to protrude into the working chamber 30 and extend in the direction in which the working chamber 30 extends. The low-stage side tooth part 51 currently formed in this is provided. Along with the revolution movement of the low-stage side tooth portion 51, a refrigerant containing lubricating oil is sucked into the working chamber 30 and compressed, and the compressed refrigerant is discharged as an intermediate pressure refrigerant. The high-stage stator 23 is provided with a working chamber 40 formed so as to extend in a spiral shape, and the rotor 22 is formed in a spiral shape so as to protrude into the working chamber 40 and extend in the working chamber 40. A high-stage side tooth portion 52 is provided. Along with the revolving motion of the high stage side tooth portion 52, the intermediate pressure refrigerant is sucked into the working chamber 40, compressed, and discharged as a high pressure refrigerant. A groove 35 is formed in the low-stage stator 21 so as to surround the working chamber 30, and by guiding lubricating oil having a pressure higher than that of the intermediate pressure refrigerant into the groove 35, the rotor 22 is made to be in the high-stage stator 23. It is characterized by generating a load to be pushed to the side.

  Here, the pressure of the high-pressure refrigerant in the compression chamber 40b is higher than the pressure of the intermediate-pressure refrigerant in the compression chamber 30b. For this reason, the thrust load which pushes the rotor 22 to the low stage side stator 21 side is generated by the differential pressure SA between the pressure of the high pressure refrigerant and the pressure of the intermediate pressure refrigerant.

  On the other hand, in this embodiment, the load which pushes the rotor 22 to the high stage side stator 23 side is generated by guiding the lubricating oil from the lubricating oil separator 64 to the groove 35. For this reason, the load which pushes the rotor 22 to the low stage side stator 21 side by the differential pressure SA between the pressure of a high pressure refrigerant | coolant and the pressure of an intermediate pressure refrigerant | coolant can be reduced. Thereby, the sliding loss (mechanical loss) which arises by the sliding of the rotor 22 with respect to the low stage side stator 21 can be reduced. The sliding of the rotor 22 is to move the rotor 22 while sliding with respect to the lower stage side stator 21.

  In addition to this, in this embodiment, the common rotor 22 is used in the working chambers 30 and 40 to suck, compress, and discharge the refrigerant. For this reason, the structure of the vehicle-mounted electric compressor 1 can be simplified.

  As described above, both simplification of the structure of the on-vehicle electric compressor 1 and suppression of sliding loss can be achieved.

  In the present embodiment, the groove 35 is formed in an annular shape surrounding the working chamber 30 around the axis S. For this reason, the rotor 22 slides on the radially inner side and the radially outer side of the groove 35 of the low-stage stator 21 as the rotor 22 revolves, thereby causing the radially inner side and the radially outer side of the groove 35 to slide. Thus, an oil film made of lubricating oil is formed. Therefore, the oil film is formed so as to surround the working chamber 30.

  Here, as shown in FIG. 3, when the groove 35 has a portion 35 a extending in the radial direction about the axis S, an oil film is not formed on the periphery 35 b of the portion 35 a due to the revolution movement of the rotor 22. . That is, the working chamber 30 cannot be surrounded by the oil film.

In contrast, in the present embodiment, as described above. An oil film is formed so as to surround the working chamber 30. For this reason, the oil film can form an oil seal that prevents refrigerant from the intermediate pressure passages 37a and 37b from entering between the rotor 22 and the low-stage stator 21 on the suction chamber 30a side of the working chamber 30. . For this reason,
The compression efficiency of the low-stage compression mechanism including the low-stage side tooth portion 51 and the working chamber 30 can be improved.

  In the present embodiment, the intermediate pressure passages 37 a and 37 b and the suction chamber 30 a communicate with each other through the rotor end plate 50 and the low-stage side stator 21. That is, the intermediate pressure passages 37 a and 37 b penetrate the low stage side stator 21 in the axial direction and are located on the radially outer side of the rotor end plate 50. Therefore, the vehicle-mounted electric compressor 1 can be reduced in size compared to the case where the intermediate pressure passages 37a and 37b are provided away from the low-stage stator 21.

  In the present embodiment, as described above, an oil film made of lubricating oil is formed between the rotor 22 and the lower stage stator 21. For this reason, the sliding part between the rotor 22 and the low stage side stator 21 can be lubricated further. Therefore, the reliability of the low-stage compression mechanism can also be achieved.

(Other embodiments)
In the above embodiment, the example in which the intermediate pressure passages 37 a and 37 b are formed so as to penetrate the low stage side stator 21 in the axial direction has been described, but instead, the intermediate pressure path is independent of the low stage side stator 21. 37a and 37b may be formed.

  In the above-described embodiment, an example in which one groove formed in an annular shape so as to surround the working chamber 30 is the groove 35 of the present invention has been described. Alternatively, a plurality of grooves may be the groove 35 of the present invention. Good. For example, the groove 35 of the present invention may be formed by arranging a plurality of grooves extending in an arc shape in the circumferential direction.

  In the above-described embodiment, the example in which the groove 35 is formed in the low-stage stator 21 has been described, but the groove 35 may be formed in the rotor 22 instead. Alternatively, the groove 35 may be formed in both the low stage side stator 21 and the rotor 22.

  In the above embodiment, the example in which the working chamber 30 is provided in the low stage side stator 21 and the low stage side tooth portion 51 is provided in the rotor 22 has been described. The stage side stator 21 may be provided with the low stage side teeth 51. In this case, the working chamber 30 is displaced with respect to the lower-stage tooth portion 51 with the revolution motion of the rotor 22.

In the above embodiment, the example in which the working chamber 40 is provided in the high stage side stator 23 and the high stage side tooth portion 52 is provided in the rotor 22 has been described. The step side stator 23 may be provided with a high step side tooth portion 52. in this case,
With the revolution movement of the rotor 22, the working chamber 40 is displaced with respect to the high-stage side tooth portion 52.

  In the above-described embodiment, the compressor of the present invention has been described as the on-vehicle compressor 1, but instead, the compressor of the present invention may be a stationary compressor.

  In the above embodiment, the compressor of the present invention is applied to a refrigeration cycle apparatus for an air conditioner. Instead, the compressor of the present invention is applied to a refrigeration cycle apparatus for a refrigerator or a refrigeration cycle apparatus for a freezer. May be.

  In the above embodiment, the compressor according to the present invention has been described as the electric compressor 1, but the compressor according to the present invention may be replaced with an engine-driven compressor. For example, an output shaft of a traveling engine of an automobile and a rotating shaft of the electric compressor 1 may be connected to a belt so that the traveling engine drives the electric compressor 1 via the belt.

  In the above embodiment, an example in which the oil passage 45 is formed in the high stage side stator 23 in order to guide the lubricating oil from the oil storage chamber 65 to the groove 35 has been described, but instead of this, it is independent of the high stage side stator 23. The oil passage 45 may be formed, and the lubricating oil may be guided from the oil storage chamber 65 to the groove 35 through the formed oil passage 45.

  In the above embodiment, the example in which the lubricating oil separator 64 and the oil storage chamber 65 are provided in the in-vehicle electric compressor 1 has been described, but instead, at least one of the lubricating oil separator 64 and the oil storage chamber 65 is mounted on the vehicle. The electric compressor 1 may be provided independently.

  In addition, this invention is not limited to above-described embodiment, In the range described in the claim, it can change suitably. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes.

DESCRIPTION OF SYMBOLS 1 In-vehicle electric compressor 10 Electric motor 12 Rotating shaft 13 Rotor 14 Armature 20 Compression mechanism 21 Low stage side stator 22 Rotor 23 High stage side stator 24 Rear housing 30 Working chamber (low stage side compression chamber)
35 groove 40 working chamber (high-stage compression chamber)
51 Lower gear teeth 52 High gear teeth

Claims (6)

A low stage side stator (21), a high stage side stator (23), a rotor (22) disposed between the low stage side stator and the high stage side stator and supported for revolving motion; With
One of the low-stage stator and the rotor is provided with a low-stage working chamber (30) formed so as to extend in a spiral shape, and the other protrudes into the low-stage working chamber. And a lower stage tooth portion (51) formed in a spiral shape along the direction in which the lower stage working chamber extends,
Along with the revolution movement of the rotor, one of the low-stage tooth portion and the low-stage working chamber is displaced with respect to the other, and a refrigerant containing lubricating oil is sucked into the low-stage working chamber. Compress and discharge the compressed refrigerant as an intermediate pressure refrigerant,
One of the high-stage stator and the rotor is provided with a high-stage working chamber (40) formed so as to extend in a spiral shape, and the other protrudes into the high-stage working chamber. And a high-stage tooth portion (52) formed in a spiral shape along the direction in which the high-stage working chamber extends,
Along with the revolving motion of the rotor, one of the high stage side tooth portion and the high stage side working chamber is displaced with respect to the other, and the intermediate pressure refrigerant is sucked into the high stage working chamber and compressed. And a compressor that discharges as a high-pressure refrigerant,
A groove (35) provided on at least one of the rotor and the lower stage side stator and formed to surround the lower stage working chamber;
An oil passage (66, 45, 36) for guiding lubricating oil having a pressure higher than that of the intermediate-pressure refrigerant to the groove in order to generate a load that pushes the rotor toward the high-stage stator side. Features compressor.   The compressor according to claim 1, wherein an outer periphery and an inner periphery of the groove are concentrically formed. An intermediate pressure passage (37a, 37b) for supplying the intermediate pressure refrigerant discharged from the low stage working chamber to the high stage working chamber; and the intermediate pressure passage side, the low stage working chamber side, Is communicated between the low-stage side stator and the rotor,
The compressor according to claim 2, wherein the groove is disposed between the low-stage working chamber and the intermediate pressure passage.   The lubricating oil separated by the oil separator (64) that separates the lubricating oil out of the high-pressure refrigerant discharged from the high-stage working chamber is the lubricating oil having a higher pressure than the intermediate-pressure refrigerant. The compressor according to any one of claims 1 to 3, wherein the compressor is supplied to the groove through the oil passage.   2. The compressor according to claim 1, wherein the groove is provided in the low-stage stator among the rotor and the low-stage stator. The low stage side stator is provided with the low stage side working chamber,
The high stage side stator is provided with the high stage side working chamber,
The compressor according to any one of claims 1 to 5, wherein the rotor is provided with the low-stage side tooth portion and the high-stage side tooth portion.

Images