Double-rotating scroll compressor

Abstract

We provide highly reliable double-rotation scroll compressors. [Solution] In the compressor of the present invention, the drive mechanism 10 has a stator 17 and a rotor 11, and the rotor 11 covers the stator 17 from the outside. The drive scroll 30 also has a cover body 37. A cylindrical portion 37c that transmits the rotational drive of the rotor 11 to the cover body 37 is connected to the wall portion 37a of the cover body 37. An intake port 374 is also formed in the wall portion 37a. Between the housing 6 and the rotor 11, a first intake passage 71 is formed that allows the fluid in the scroll chamber 65 to flow from the cover body 37 side to the rotor 11 side in the direction of the drive axis O1. A second intake passage 72 is formed between the rotor 11 and the stator 17 in the radial direction of the drive scroll 30 that guides the fluid that has flowed through the first intake passage 71 to the intake port 374 while allowing it to flow from the rotor 11 side to the cover body 37 side in the direction of the drive axis O1.

Description

Technical Field

[0001] The present invention relates to a double-rotary scroll compressor.

Background Art

[0002] Patent Document 1 discloses a conventional double-rotary scroll compressor (hereinafter simply referred to as a compressor). This compressor includes a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism. The housing has a scroll chamber that houses the drive scroll, the driven scroll, the drive mechanism, and the driven mechanism. Fluid is inhaled into the scroll chamber from the outside of the housing. In this document, the fluid is specifically a refrigerant.

[0003] The drive scroll is rotatably driven around the drive axis by a drive mechanism. The driven scroll is eccentric with respect to the drive scroll and is rotatably driven around the driven axis by the drive scroll and the driven mechanism. These drive scroll and driven scroll form a compression chamber that compresses fluid by rotational driving and rotational following. The drive mechanism has a stator and a rotor. The stator is formed in a cylindrical shape extending in the drive axis direction and is fixed in the scroll chamber. The rotor is formed in a cylindrical shape with a smaller diameter than the stator and extending in the drive axis direction, and is disposed inside the stator.

[0004] Also, in this compressor, a protrusion is provided on the housing. The protrusion protrudes into the scroll chamber in the drive axis direction toward the drive scroll and the driven scroll. A discharge passage extending in the drive axis direction is formed inside the protrusion. The discharge passage communicates with a discharge chamber on one side in the drive axis direction and communicates with the outside of the housing on the other side in the drive axis direction.

[0005] Furthermore, in this compressor, the drive scroll has a cover body. The cover body has a cylindrical extension. A rotor is fixed to the outer surface of the extension. A projection also enters the interior of the extension. In this way, the drive scroll is rotatably supported by the projection via the cover body. An intake port is also formed in the drive scroll. The intake port communicates with the scroll chamber and the compression chamber.

[0006] In this compressor, the rotor rotates in the drive mechanism, causing the drive scroll to rotate together with the rotor around the drive axis. As a result, the driven scroll rotates around the drive axis due to the drive scroll and the driven mechanism. Thus, the volume of the compression chamber changes due to the rotation of the drive scroll and the rotation of the driven scroll. The fluid in the scroll chamber flows from one side to the other in the direction of the drive axis and is drawn into the compression chamber through the intake port. After being compressed in the compression chamber, the fluid flows through the discharge passage and is discharged to the outside of the housing. [Prior art documents] [Patent Documents]

[0007] [Patent Document 1] Japanese Patent Application Publication No. 2-227575 [Overview of the Initiative] [Problems that the invention aims to solve]

[0008] In this type of compressor, it is necessary to suppress the performance degradation of the drive mechanism due to heat generated during operation. In this regard, in the conventional compressor described above, when the fluid in the scroll chamber is drawn into the intake port, it flows between the stator and rotor from one side to the other in the direction of the drive axis. In this compressor, the stator and rotor, i.e., the drive mechanism, can be cooled by the fluid, but it is difficult to cool the drive mechanism sufficiently. For this reason, this compressor cannot be made highly reliable.

[0009] This invention has been made in view of the above-mentioned conventional circumstances, and aims to solve the problem of providing a highly reliable double-rotation scroll compressor. [Means for solving the problem]

[0010] The dual-rotation scroll compressor of the present invention comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism. The housing has a scroll chamber in which the drive scroll, the driven scroll, the drive mechanism, and the driven mechanism are housed, and into which fluid is drawn from the outside. The drive scroll is rotationally driven around the drive axis by the drive mechanism, The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. The drive scroll and the driven scroll form a compression chamber that compresses the fluid through the rotational drive and the rotational drive, The drive mechanism comprises a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator. The stator is a double-rotation scroll compressor having a cylindrical stator core extending in the direction of the drive axis, a first coil end protruding cylindrically from the stator core to one side in the direction of the drive axis, and a second coil end located on the opposite side of the stator core from the first coil end and protruding cylindrically to the other side in the direction of the drive axis. The scroll chamber is provided with a projection that extends toward the drive scroll and the driven scroll in the direction of the drive axis, and to which the stator core is fixed. The drive scroll has a cover body that is rotationally driven by the rotor, The cover body has a wall portion that extends radially and faces the first coil end in the direction of the drive axis, A cylindrical portion is connected to the wall portion, extending cylindrically in the direction of the drive axis and covering the first coil end from the radially outside, while transmitting the rotational drive of the rotor to the cover body. An intake port is formed, located radially inward from the cylindrical portion, to draw the fluid in the scroll chamber into the compression chamber. A first intake passage is formed between the housing and the rotor in the radial direction, allowing the fluid in the scroll chamber to flow from the cover side to the rotor side in the direction of the drive axis. A second intake passage is formed between the rotor and the stator in the radial direction, which guides the fluid that has flowed through the first intake passage towards the intake port while allowing it to flow from the rotor side towards the cover body side in the direction of the drive axis.

[0011] In the double-rotation scroll compressor of the present invention, the drive mechanism comprises a stator and a rotor, with the rotor rotating while covering the stator from the outside. Furthermore, in this compressor, a first intake passage is formed between the housing and the rotor, and a second intake passage is formed between the rotor and the stator.

[0012] In this compressor, the fluid in the scroll chamber flows through the first intake passage from the cover side to the rotor side in the direction of the drive axis, that is, from one side to the other in the direction of the drive axis. At this time, the rotor can be cooled by the fluid flowing through the first intake passage. The fluid that has flowed through the first intake passage is then guided to the intake port by flowing through the second intake passage from the rotor side to the cover side in the direction of the drive axis, that is, from the other side to the one side in the direction of the drive axis. At this time, the rotor and stator can be cooled by the fluid flowing through the second intake passage. The fluid that has been guided to the intake port by the second intake passage is then drawn into the compression chamber from the intake port and compressed in the compression chamber.

[0013] Thus, in this compressor, the rotor can be cooled by the fluid flowing through the first intake passage, and the rotor and stator can also be cooled by the fluid flowing through the second intake passage. As a result, the operating mechanism can be sufficiently cooled by the fluids flowing through the first and second intake passages in this compressor, thereby suppressing the performance degradation of the drive mechanism due to heat generation.

[0014] Therefore, the dual-rotation scroll compressor of the present invention is highly reliable.

[0015] In particular, in this compressor, the operating mechanism can be sufficiently cooled by the fluid flowing through the first and second intake passages. Therefore, there is no need to enlarge the rotor to suppress iron loss due to heat, nor to use magnets with excessively high demagnetization resistance to suppress demagnetization due to heat. As a result, this compressor can be made smaller and have lower manufacturing costs.

[0016] In the compressor of the present invention, the housing may have an intake port for drawing fluid into the scroll chamber from the outside. The drive scroll may have a case in which a discharge chamber is formed inside through which the fluid compressed in the compression chamber is discharged. Furthermore, the case may be located on one side of the drive axis direction relative to the cover body. Preferably, the intake port is located closer to the cover body than the case in the drive axis direction.

[0017] Since the fluid compressed in the compression chamber is at a high temperature, the discharge chamber, and consequently the case in which the discharge chamber is formed, tends to become hot. In this compressor, the intake port formed in the housing is located closer to the cover body than to the case in the direction of the drive axis. Therefore, the fluid drawn into the scroll chamber through the intake port is less affected by the heat of the case. As a result, in this compressor, the drive mechanism can be more effectively cooled by the fluid flowing through the first intake passage and the fluid flowing through the second intake passage.

[0018] Also, in this case, it is preferable that the suction communication port faces at least a part of the rotor in the radial direction. Thereby, since the suction communication port is disposed closer to the rotor, the fluid that is sucked into the scroll chamber through the suction communication port and flows through the first suction passage can more suitably cool the rotor.

[0019] Further, in the compressor of the present invention, a suction communication port for sucking fluid from the outside into the scroll chamber may be formed in the housing. Further, the driving scroll may have a case in which a discharge chamber for discharging the fluid compressed in the compression chamber is formed inside. Also, the case may be located on one side in the driving axis direction rather than the cover body. Further, the suction communication port may face the case in the driving axis direction. And, in the scroll chamber, it is preferable that a third suction passage is formed which is located on one side in the driving axis direction rather than the first suction passage and allows fluid to flow in the driving axis direction toward the first suction passage.

[0020] In this case, since the suction communication port faces the case in the driving axis direction, the suction communication port and the rotor, and thus the suction communication port and the first suction passage are arranged remotely in the driving axis direction. Here, in this compressor, a third suction passage is formed in the scroll chamber, and this third suction passage is located on one side in the driving axis direction rather than the first suction passage and allows fluid to flow in the driving axis direction toward the first suction passage. For this reason, in this compressor, even if the suction communication port and the first suction passage are remotely arranged in the driving axis direction, it is possible to suitably prevent the fluid sucked into the scroll chamber from the suction communication port from stagnating in the scroll chamber without flowing through the first suction passage.

[0021] Also, in this compressor, since the suction communication port faces the case in the driving axis direction, the fluid sucked into the scroll chamber through the suction communication port can be made to collide with the case in the driving axis direction. Thereby, in this compressor, the lubricating oil contained in the fluid can be suitably separated from the fluid, and the scroll chamber can be suitably lubricated with this lubricating oil.

[0022] In the compressor of the present invention, the fluid can be a refrigerant. And in the radial direction, it is preferable that the housing and the rotor are separated by an interval that generates a shearing force on the refrigerant flowing through the first suction passage by the rotating rotor.

[0023] In this case, even if liquid refrigerant, which is a liquid-phase refrigerant, is inhaled into the scroll chamber, this liquid refrigerant can be evaporated in the process of flowing through the first suction passage. Therefore, in this compressor, it is possible to suitably prevent the liquid refrigerant from being inhaled from the suction port into the compression chamber.

[0024] The housing may have a main body portion extending in the direction of the drive axis. Further, the main body portion may have a first inner diameter portion located on one side in the drive axis direction with respect to the rotor, and a second inner diameter portion located on the other side in the drive axis direction with respect to the first inner diameter portion, connected to the first diameter portion in the drive axis direction and facing the rotor in the radial direction. And it is preferable that the second inner diameter portion is formed to have a larger diameter than the first inner diameter portion.

[0025] By forming the second inner diameter portion to have a larger diameter than the first inner diameter portion, in this compressor, an appropriate interval between the second inner diameter portion and the rotor in the radial direction can be ensured, and accordingly, the first suction passage can be formed wider. As a result, in this compressor, it becomes difficult for the lubricating oil to stay in the first suction passage, and thus the fluid can flow through the first suction passage more suitably.

[0026] Also, in this case, it is preferable that the main body portion gradually increases in diameter from the first inner diameter portion toward the second inner diameter portion in the drive axis direction. Thereby, even if the lubricating oil stays in the first suction passage, the inner peripheral surface of the main body portion can suitably flow the lubricating oil from the first inner diameter portion side to the second inner diameter portion side. As a result, in this compressor, it becomes more difficult for the lubricating oil to stay in the first suction passage, and thus the fluid can flow through the first suction passage more suitably.

[0027] The rotor may have a cylindrical rotor body formed from a plurality of electromagnetic steel sheets stacked in the direction of the drive axis. Furthermore, a first intake passage may be formed between the inner circumferential surface of the housing and the outer circumferential surface of the rotor body in the radial direction. Preferably, a second intake passage is formed between the inner circumferential surface of the rotor and the outer circumferential surface of the stator in the radial direction.

[0028] In this case, the fluid flowing through the first intake passage and the fluid flowing through the second intake passage can be brought into suitable contact with the outer and inner surfaces of the rotor body, that is, the outer and inner surfaces of each electrical steel sheet, respectively, thereby allowing the rotor body to be cooled effectively. [Effects of the Invention]

[0029] The dual-rotation scroll compressor of the present invention offers excellent reliability. [Brief explanation of the drawing]

[0030] [Figure 1] Figure 1 is a cross-sectional view of the compressor of Example 1. [Figure 2] Figure 2 is an enlarged cross-sectional view of the main parts of the compressor of Example 1, showing the stator, rotor, etc. [Figure 3] Figure 3 is a cross-sectional view of the compressor in Example 2. [Figure 4] Figure 4 is a cross-sectional view of the compressor in Example 3. [Modes for carrying out the invention]

[0031] Examples 1 to 3 embodying the present invention will be described below with reference to the drawings. These compressors are mounted on a vehicle (not shown) and constitute the vehicle's air conditioning system.

[0032] (Example 1) As shown in Figure 1, the compressor of Embodiment 1 comprises a housing 6, an electric motor 10, a drive scroll 30, a driven scroll 40, and a driven mechanism 20. The electric motor 10 is an example of a "drive mechanism" in the present invention.

[0033] In this embodiment, the front-to-rear direction of the compressor is defined by the solid arrow shown in Figure 1. Then, in Figures 2 and onward, the front-to-rear direction of the compressor is defined in accordance with Figure 1. Note that the front-to-rear direction of the compressor is merely an example for illustrative purposes, and the compressor can appropriately change its orientation depending on the vehicle it is mounted on.

[0034] As shown in Figure 1, the housing 6 is composed of a housing body 60, a first housing cover 61, and a second housing cover 62. The housing body 60 is an example of the "main body" in the present invention.

[0035] The housing body 60 is made of aluminum alloy. The housing body 60 is cylindrical with the drive shaft O1 as its center, and has openings at its front and rear ends. The drive shaft O1 is parallel to the front-rear direction. Thus, in the front-rear direction of the compressor, the front direction corresponds to "one of the drive shaft directions" in this invention, and the rear direction corresponds to "the other of the drive shaft directions" in this invention.

[0036] Furthermore, the housing body 60 has an outer circumferential surface 601 and an inner circumferential surface 602. In addition, the housing body 60 has a first inner diameter portion 60a with an inner diameter length of first length L1 and a second inner diameter portion 60b with an inner diameter length of second length L2. The second length L2 is longer than the first length L1.

[0037] The first inner diameter portion 60a is located at the front end of the housing body 60, and the second inner diameter portion 60b is located at the rear end of the housing body 60. Furthermore, the housing body 60 gradually expands in diameter from the first inner diameter portion 60a to the second inner diameter portion 60b in the direction of the drive axis O1. In other words, the housing body 60 has a shape in which the inner diameter expands from the front end to the rear end, from a first length L1 to a second length L2. Even though the inner diameter expands in this way, the outer diameter of the housing body 60 is maintained at a constant size.

[0038] Furthermore, an intake port 81 is formed in the housing body 60. The intake port 81 is located on the other side in the direction of the drive axis O1 of the housing body 60, that is, on the rear side of the center in the front-rear direction of the housing body 60. The intake port 81 extends radially through the housing body 60 and communicates the inside and outside of the housing body 60. The intake port 81 is connected to an evaporator (not shown) through piping (not shown).

[0039] The first housing cover 61 is made of steel. The first housing cover 61 is located at the rear end of the housing body 60. The first housing cover 61 is substantially disc-shaped with the drive shaft center O1 at its center. The first housing cover 61 has a front surface 61a facing forward and a rear surface 61b located on the opposite side of the front surface 61a and facing rear.

[0040] Furthermore, a protruding body 64 is provided inside the housing 6. More specifically, the protruding body 64 is integrally provided with the first housing cover 61. As a result, the protruding body 64 is also made of steel. The protruding body 64 protrudes cylindrically forward from the center of the front surface 61a in the direction of the drive axis O1. The protruding body 64 has a first diameter portion 64a and a second diameter portion 64b.

[0041] The first diameter portion 64a constitutes the front part of the protruding body 64. As shown in Figure 2, the first diameter portion 64a is formed to be smaller in diameter than the insertion hole 375, which will be described later. A pin hole 4 is also formed in the first diameter portion 64a. The pin hole 4 extends through the interior of the first diameter portion 64a in the direction of the drive axis O1 and opens to the front end surface of the first diameter portion 64a.

[0042] Furthermore, a first radial ball bearing 51 is provided on the outer circumferential surface of the first diameter portion 64a. Alternatively, a sliding bearing may be provided on the outer circumferential surface of the first diameter portion 64a instead of the first radial ball bearing 51.

[0043] The second diameter portion 64b is integral with the first diameter portion 64a and is located behind the first diameter portion 64a. As a result, the second diameter portion 64b constitutes the rear part of the projection 64. The second diameter portion 64b is connected to the front surface 61a of the first housing cover 61 at its rear end. Furthermore, the second diameter portion 64b is formed to have a larger diameter than the first diameter portion 64a.

[0044] As shown in Figure 1, the second housing cover 62 is positioned in front of the housing body 60. The second housing cover 62 is made of aluminum alloy. The second housing cover 62 is substantially disc-shaped with the drive shaft center O1 as its center. The second housing cover 62 has a front surface 62a that faces forward and a rear surface 62b that is located on the opposite side of the front surface 62a and faces rear.

[0045] Furthermore, a support portion 66 and a discharge port 83 are formed in the second housing cover 62. The support portion 66 is integrally formed approximately in the center of the rear surface 62b and protrudes rearward from the rear surface 62b. The support portion 66 is formed in a cylindrical shape centered on the drive shaft center O1, and a second radial ball bearing 52 and a shaft seal member 63 are provided inside. The shaft seal member 63 is positioned in front of the second radial ball bearing 52 inside the support portion 66. The shaft seal member 63 is formed in an annular shape. Note that a sliding bearing may be provided inside the support portion 66 instead of the second radial ball bearing 52.

[0046] The discharge port 83 penetrates the second housing cover 62 in the direction of the drive axis O1, and connects the inside of the support portion 66 with the outside of the second housing cover 62. The discharge port 83 is also connected to a condenser (not shown) through piping (not shown).

[0047] In the housing 6, the front surface 61a of the first housing cover 61 is in contact with the rear end of the housing body 60, and the rear surface 62b of the second housing cover 62 is in contact with the front end of the housing body 60. The housing body 60, the first housing cover 61, and the second housing cover 62 are fixed together in the direction of the drive axis O1 by a plurality of bolts (not shown).

[0048] Thus, in the housing 6, the housing body 60 is sandwiched in the front-rear direction by the first housing cover 61 and the second housing cover 62, and the front and rear ends of the housing body 60 are closed by the first housing cover 61 and the second housing cover 62, respectively. As a result, a scroll chamber 65 is formed inside the housing body 60 in the housing 6. The scroll chamber 65 is in communication with the intake port 81. Therefore, refrigerant is drawn into the scroll chamber 65 from outside the housing 6 through the intake port 81. The refrigerant is an example of a "fluid" in this invention.

[0049] Furthermore, the aforementioned protruding body 64 protrudes from the first housing cover 61 into the scroll chamber 65 in the direction of the drive axis O1. More specifically, the protruding body 64 protrudes forward from the first housing cover 61 toward the drive scroll 30 and the driven scroll 40.

[0050] The electric motor 10 is housed within the scroll chamber 65. Thus, the scroll chamber 65 also serves as the motor chamber housing the electric motor 10.

[0051] As shown in Figure 2, the electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 has a stator core 17a and windings 17b. The stator core 17a is formed in a cylindrical shape with the drive axis O1 as the center. The windings 17b are wound around the stator core 17a. As a result, the windings 17b form a first coil end 171 and a second coil end 172.

[0052] The first coil end 171 protrudes cylindrically forward from the stator core 17a in the direction of the drive axis O1. The second coil end 172 is located on the opposite side of the stator core 17a from the first coil end 171. The second coil end 172 protrudes cylindrically backward from the stator core 17a in the direction of the drive axis O1.

[0053] In the stator 17, the stator core 17a is fitted onto the outer circumferential surface of the second diameter portion 64b. In this way, the stator core 17a is fixed to the second diameter portion 64b, and consequently to the protruding body 64. Although not shown in the figures, multiple slits extending in the direction of the drive axis O1 are formed on the inner circumferential surface of the stator core 17a. As a result, the slits form a gap between the stator core 17a and the outer circumferential surface of the second diameter portion 64b while the stator core 17a is fixed to the second diameter portion 64b.

[0054] As shown in Figure 2, the rotor 11 comprises a rotor body 11a, a plurality of magnet cores 11b, a first retaining plate 11c, and a second retaining plate 11d. Note that Figure 2 shows one of the plurality of magnet cores 11b. Also, in Figures 1, 3, and 4, the shape of the rotor 11 is shown in a simplified form.

[0055] As shown in Figure 2, the rotor body 11a is formed by stacking multiple electromagnetic steel sheets 111, each formed in a substantially disc shape, in the direction of the drive axis O. As a result, the rotor body 11a is a substantially cylindrical body extending in the direction of the drive axis O1. In addition, each electromagnetic steel sheet 111, i.e., the rotor body 11a, has multiple magnet chambers 112 and multiple first bolt holes 113 formed therein.

[0056] Each magnet core 11b is formed in a columnar shape extending in the direction of the drive axis O1 and is housed in each magnet chamber 112. The first retaining plate 11c and the second retaining plate 11d are made of metal plate material and have a disc shape. The first retaining plate 11c is positioned in front of the rotor body 11a. The second retaining plate 11d is positioned behind the rotor body 11a. The first retaining plate 11c has a plurality of through holes 114 corresponding to each bolt hole 113, and the second retaining plate 11d has a plurality of through holes 115 corresponding to each first bolt hole 113.

[0057] The first retaining plate 11c and the second retaining plate 11d clamp the rotor body 11a in the front-rear direction, aligning their respective through holes 114 and 115 with respect to the respective first bolt holes 113 in the front-rear direction. In this state, the rotor body 11a, the first retaining plate 11c, and the second retaining plate 11d are fastened together in the front-rear direction by multiple rivets (not shown). Furthermore, the front and rear ends of each magnet chamber 112 are closed by the first retaining plate 11c and the second retaining plate 11d. As a result, each magnet core 11b cannot fall out of each magnet chamber 112. In this way, the rotor 11 is formed.

[0058] Here, each electrical steel sheet 111, the first retaining plate 11c, and the second retaining plate 11d are formed to have a larger diameter than the stator core 17a. As a result, the rotor 11 is formed in a cylindrical shape with a larger diameter than the stator core 17a and has an outer circumferential surface 110a and an inner circumferential surface 110b. The rotor 11 covers the stator core 17a from the radially outside of the drive scroll 30 within the scroll chamber 65. In other words, in the electric motor 10, the rotor 11 is positioned outside the stator 17.

[0059] As shown in Figure 1, the drive scroll 30 is housed in the scroll chamber 65. The drive scroll 30 is made of a metal such as an aluminum alloy. The drive scroll 30 includes a drive end plate 31, a drive spiral body 33, a drive peripheral wall 35, a cover body 37, and a case 39.

[0060] The drive end plate 31 extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The driven axis O2 extends parallel to the drive axis O1 while being eccentric with respect to the drive axis O1. In other words, the driven axis O2 is also parallel in the front-rear direction. The drive end plate 31 has a first front surface 311 facing forward and a first rear surface 312 located on the opposite side of the first front surface 311 and facing rear.

[0061] Furthermore, a discharge port 32 is formed in the drive end plate 31. The discharge port 32 penetrates the drive end plate 31 in the direction of the drive axis O1. In addition, a discharge reed valve 57 and a retainer 58 are fixed to the first front surface 311 of the drive end plate 31 by fixing bolts 59. As a result, the discharge reed valve 57 can open and close the discharge port 32. The retainer 58 can adjust the opening degree of the discharge reed valve 57.

[0062] The drive spiral body 33 is integral with the drive end plate 31 and protrudes from the first rear surface 312 toward the rear, i.e., toward the driven scroll 40, parallel to the drive axis O1 and the driven axis O2. Although detailed illustration is omitted, the drive spiral body 33 has the center of the drive end plate 31 as its spiral center and protrudes outward from the spiral center.

[0063] The drive circumferential wall 35 is formed in a cylindrical shape, extending parallel to the drive axis O1 and the driven axis O2, with the drive axis O1 as its center. The front end of the drive circumferential wall 35 is integral with the outer peripheral edge of the drive end plate 31. As a result, the drive circumferential wall 35 surrounds the drive vortex body 33 from the outside and protrudes cylindrically toward the rear from the first rear surface 312. Although not shown in the figures, the outer peripheral end of the vortex in the drive vortex body 33 is connected to the inner peripheral surface of the drive circumferential wall 35.

[0064] The cover body 37 has a wall portion 37a, an inner cylindrical portion 37b, and an outer cylindrical portion 37c. The outer cylindrical portion 37c is an example of a "cylindrical portion" in the present invention.

[0065] The wall portion 37a extends in a substantially plate-like shape in the radial direction of the drive scroll 30. The wall portion 37a has a second front surface 371 facing forward and a second rear surface 372 located on the opposite side of the second front surface 371 and facing rear.

[0066] Furthermore, a recess 373 and an intake port 374 are formed in the wall portion 37a. The recess 373 is located approximately in the center of the second front surface 371 and is recessed toward the rear from the second front surface 371.

[0067] The intake port 374 is located radially outward from the recess 373 of the drive scroll 30. The intake port 374 penetrates the wall portion 37a in the front-rear direction, with its front end opening to the second front surface 371 and its rear end opening to the second rear surface 372. In this compressor, the intake port 374 is formed only in the wall portion 37a. Furthermore, there is only one intake port 374 formed in the wall portion 37a. However, multiple intake ports 374 may be formed in the wall portion 37a.

[0068] Furthermore, in the wall portion 37a, multiple rings 22 are attached to the area between the recess 373 and the intake port 374. Although detailed illustrations are omitted, each ring 22 is arranged at equal intervals in the circumferential direction of the recess 373 when facing forward, surrounding the recess 373 from the outside. In this embodiment, there are six rings 22. Figures 1, 3, and 4 illustrate one of the six rings 22.

[0069] The inner cylindrical portion 37b is located in the radial direction of the cover body 37, inside the stator 17, and extends cylindrically backward from the second rear surface 372 of the wall portion 37a in the direction of the drive axis O1. The inner cylindrical portion 37b is larger in diameter than the first diameter portion 64a of the protruding body 64, and smaller in diameter than the second diameter portion 64b. The inner diameter of the inner cylindrical portion 37b is formed to be approximately the same as the outer diameter of the first radial ball bearing 51. The outer diameter of the inner cylindrical portion 37b may be approximately the same as the outer diameter of the second diameter portion 64b, or it may be larger than the outer diameter of the second diameter portion 64b.

[0070] Furthermore, the cover body 37 has an insertion hole 375. The insertion hole 375 extends in the direction of the drive shaft center O1 and connects the inner cylindrical portion 37b and the recess 373.

[0071] The outer cylindrical portion 37c is integral with the wall portion 37a at its outer peripheral edge. As a result, the outer cylindrical portion 37c is connected to the wall portion 37a and extends cylindrically backward from the wall portion 37a in the direction of the drive axis O1. The outer diameter of the outer cylindrical portion 37c is formed to be approximately the same as the outer diameter of the drive peripheral wall 35 and the outer diameter of the rotor 11.

[0072] Furthermore, the inner diameter of the outer cylindrical portion 37c is formed to be larger than that of the inner cylindrical portion 37b. As a result, in the cover body 37, the inner cylindrical portion 37b is positioned on the inner circumference side of the outer cylindrical portion 37c, separated from the outer cylindrical portion 37c in the radial direction of the drive scroll 30. In this way, the cover body 37 has a housing portion 38 formed by the wall portion 37a, the inner cylindrical portion 37b, and the outer cylindrical portion 37c. The housing portion 38 has a bottomed annular shape that opens at the rear.

[0073] The intake port 374 formed in the wall portion 37a is located in the radial direction of the drive scroll 30, outside the inner cylindrical portion 37b and inside the outer cylindrical portion 37c. Thus, the intake port 374 communicates with the housing portion 38 at a point between the inner cylindrical portion 37b and the outer cylindrical portion 37c.

[0074] Furthermore, multiple second bolt holes 376 are formed in the outer cylindrical portion 37c. Each second bolt hole 376 penetrates the outer cylindrical portion 37c in the direction of the drive axis O1. Although not shown in the figures, the number of second bolt holes 376 is equal to the number of first bolt holes 113 formed in the rotor 11. Figures 1 to 4 show one of each of the multiple first bolt holes 113 and second bolt holes 376.

[0075] As shown in Figure 1, the cover body 37 has its front end of the outer cylindrical portion 37c in contact with the rear end of the drive peripheral wall 35. The cover body 37 also has the rotor 11, more specifically the first retaining plate 11c, in contact with the rear end of the outer cylindrical portion 37c. In this state, the first bolts 34a are inserted from the second retaining plate 11d side through the through holes 115, the first bolt holes 113, the through holes 114, and the second bolt holes 376 in that order, and the first bolts 34a are screwed into the drive peripheral wall 35. In this way, the cover body 37 is fixed to the drive peripheral wall 35 and the rotor 11 while being sandwiched in the front-rear direction by the drive peripheral wall 35 and the rotor 11. As a result, the drive scroll 30 is integrated with the rotor 11.

[0076] Case 39 is a bottomed cylindrical member having an outer peripheral wall 39a and a front wall 39b. The outer peripheral wall 39a is cylindrical with the drive axis O1 as its center. Here, the outer diameter of the outer peripheral wall 39a is formed to be approximately the same as the outer diameter of the drive peripheral wall 35.

[0077] The front wall 39b is located at the front end of the case 39. The front wall 39b extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The outer edge of the front wall 39b is connected to the front end of the outer wall 39a. A boss 39c is formed on the front wall 39b. The boss 39c is integrally formed in the center of the front wall 39b and protrudes forward from the front wall 39b in the direction of the drive axis O1. The outer diameter of the boss 39c is formed to be substantially the same as the inner diameter of the second radial ball bearing 52 and the inner diameter of the shaft sealing member 63. A discharge passage 390 is also formed on the boss 39c. The discharge passage 390 penetrates the boss 39c in the direction of the drive axis O1.

[0078] Furthermore, third bolt holes 39d are formed in the outer periphery wall 39a and the front wall 39b. The third bolt holes 39d penetrate the outer periphery wall 39a and the front wall 39b in the direction of the drive axis O1. Although not shown in the figures, multiple third bolt holes 39d are formed in the outer periphery wall 39a and the front wall 39b. Figures 1, 3, and 4 illustrate one of these multiple third bolt holes 39d.

[0079] As shown in Figure 1, the case 39 has its rear surface of the outer peripheral wall 39a in contact with the front end of the drive peripheral wall 35. In this state, the second bolts 34b are inserted through each of the third bolt holes 39d and screwed into the drive peripheral wall 35. In this way, the case 39 is fixed to the drive peripheral wall 35 in the drive scroll 30.

[0080] As the case 39 is fixed to the drive peripheral wall 35, a discharge chamber 14 is formed inside the case 39, that is, inside the outer peripheral wall 39a, between the front wall 39b of the case 39 and the drive end plate 31. The discharge chamber 14 is in communication with the discharge port 32 and also with the discharge passage 390.

[0081] Thus, with the case 39 fixed to the drive peripheral wall 35, in the drive scroll 30, the drive peripheral wall 35, the drive spiral body 33, and the case 39 and cover body 37 are arranged to be separated in the front-rear direction with the drive peripheral wall 35 in between. Furthermore, since the rotor 11 is fixed to the outer cylindrical portion 37c of the cover body 37, the case 39 and the rotor 11, including the discharge chamber 14, are also arranged to be separated in the front-rear direction.

[0082] The driven scroll 40 is also made of aluminum alloy. The driven scroll 40 has a driven end plate 41 and a driven spiral body 43.

[0083] The driven end plate 41 extends in a substantially disc shape perpendicular to the drive axis O1 and the driven axis O2. The driven end plate 41 has a third front surface 411 facing forward and a third rear surface 412 located on the opposite side of the third front surface 411 and facing rear.

[0084] A receiving recess 15 is formed in the driven end plate 41. The receiving recess 15 is located in the center of the driven end plate 41. The receiving recess 15 is recessed in a cylindrical shape from the third rear surface 412 of the driven end plate 41 toward the front, with the driven axis O2 as the center. As a result, the receiving recess 15 faces the rear of the driven end plate 41, and consequently the first diameter portion 64a of the protruding body 64.

[0085] As shown in Figure 2, a driven shaft portion 16 is provided within the housing recess 15. The driven shaft portion 16 has a bush 53 and a driven pin 55. The bush 53 is housed within the housing recess 15 via a sliding bearing 13. The driven pin 55 is inserted through the bush 53. More specifically, the driven pin 55 is inserted through the bush 53 at a position eccentric to the center of the bush 53, i.e., the driven axis O2. The driven pin 55 protrudes rearward from the bush 53 and, consequently, from the driven end plate 41.

[0086] Furthermore, as shown in Figure 1, a pivot pin 21 is fixed to the driven end plate 41 at the location facing the ring 22. The pivot pin 21 protrudes rearward from the third rear surface 412. Six pivot pins 21 are fixed to the driven end plate 41, the same number as the rings 22. Figures 1, 3, and 4 illustrate one of the six pivot pins 21.

[0087] As shown in Figure 1, the driven mechanism 20 is composed of these pivot pins 21 and rings 22. Here, the number of pivot pins 21 and rings 22 can be designed as appropriate, as long as there are three or more of each.

[0088] The driven spiral body 43 is integral with the driven end plate 41 and extends forward from the third front surface 411 of the driven end plate 41 parallel to the drive axis O1 and the driven axis O2. The driven spiral body 43 has the center of the driven end plate 41 as its spiral center and extends outward from the spiral center.

[0089] In this compressor, the driven scroll 40 is housed within the drive scroll 30, more specifically, in the drive scroll 30, at a location between the drive spiral body 33 and the drive peripheral wall 35 and the cover body 37. The drive spiral body 33 and the driven spiral body 43 are then meshed together. As a result, the drive spiral body 33 and the driven spiral body 43 face each other to form a compression chamber 12.

[0090] Furthermore, a suction section 30a is formed between the drive peripheral wall 35 and the driven scroll 40. In other words, the drive spiral body 33 and the driven spiral body 43 are located within the suction section 30a. The suction section 30a is separated from the scroll chamber 65 by the drive peripheral wall 35 and the cover body 37, and is also separated from the discharge chamber 14 by the drive end plate 31. The suction section 30a is also in communication with the suction port 374.

[0091] Furthermore, by housing the driven scroll 40 within the driven scroll 30, each orbital pin 21 enters each ring 22. In this way, the driven scroll 30 and the driven scroll 40 are assembled in the front-rear direction, and the driven scroll 30 and the driven scroll 40 constitute the scroll compression section 100. More precisely, after the driven spiral body 33 and the driven spiral body 43 are meshed and each orbital pin 21 enters each ring 22, the cover body 37 of the driven scroll 30 is fixed to the drive peripheral wall 35 and the rotor 11.

[0092] Furthermore, when the drive scroll 30 and the driven scroll 40 are assembled, the housing recess 15 of the driven end plate 41 and the driven shaft portion 16 face the recess 373 of the cover body 37.

[0093] The drive scroll 30 is positioned in front of the stator 17 within the scroll chamber 65. As shown in Figure 2, in the drive scroll 30, the inner cylindrical portion 37b of the cover body 37 is inserted into the inner circumference of the first coil end 171. In this state, the first radial ball bearing 51 is inserted into the inner cylindrical portion 37b. As a result, the cover body 37 is rotatably supported by the first diameter portion 64a via the first radial ball bearing 51. The housing portion 38 is in communication with the scroll chamber 65. The front portion of the first diameter portion 64a is inserted into the insertion hole 375.

[0094] Furthermore, since the cover body 37 is supported by the first diameter portion 64a, the first coil end 171 is housed within the housing portion 38. As a result, within the housing portion 38, the first coil end 171 is covered from the front by the wall portion 37a and covered from the radially inner side of the drive scroll 30 by the inner cylindrical portion 37b. The first coil end 171 is also covered from the radially outer side of the drive scroll 30 by the outer cylindrical portion 37c within the housing portion 38.

[0095] Furthermore, in this compressor, with the cover body 37 supported by the first diameter portion 64a, the first diameter portion 64a, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37c are arranged in this order from the drive axis O1 side outward in the radial direction of the drive scroll 30. These first diameter portion 64a, the first radial ball bearing 51, the inner cylindrical portion 37b, the first coil end 171, and the outer cylindrical portion 37c are arranged overlapping in the radial direction of the drive scroll 30.

[0096] Furthermore, as shown in Figure 1, in the drive scroll 30, the boss 39c of the case 39 is inserted through the second radial ball bearing 52 and the shaft sealing member 63. As a result, the case 39 is rotatably supported by the support portion 66 via the second radial ball bearing 52. Thus, the drive scroll 30 is positioned within the scroll chamber 65 and is rotatably supported by the housing 6 by both the protrusion 64 and the support portion 66, so as to be around the drive axis O1.

[0097] On the other hand, in the driven scroll 40, the driven pin 55 of the driven shaft portion 16 is inserted into the pin hole 4. As a result, the driven scroll 40 is positioned within the scroll chamber 65 and is rotatably supported around the driven axis O2 by the first diameter portion 64a of the projection 64. In other words, unlike the drive scroll 30, the driven scroll 40 is rotatably supported around the driven axis O2 in the housing 6 solely by the projection 64.

[0098] Furthermore, in this compressor, in order to ensure rotation of the rotor 11 and drive scroll 30 around the drive axis O1, the outer circumferential surface 110a of the rotor 11 and the inner circumferential surface 602 of the housing body 60 are separated in the radial direction of the drive scroll 30 when the rotor 11 and drive scroll 30 are arranged within the scroll chamber 65. Similarly, the outer cylindrical portion 37c of the cover body 37, the drive peripheral wall 35, and the outer circumferential wall 39a of the case 39 are also separated from the inner circumferential surface 602 in the radial direction of the drive scroll 30.

[0099] Furthermore, when the rotor 11 covers the stator 17 from the radially outer side of the drive scroll 30, the inner circumferential surface 110b of the rotor 11 and the outer circumferential surface of the stator core 17a are separated in the radial direction of the drive scroll 30.

[0100] In this compressor, a first intake passage 71 is formed between the outer circumferential surface 110a of the rotor 11 in the radial direction of the drive scroll 30 and the inner circumferential surface 602 of the housing body 60. A second intake passage 72 is formed between the inner circumferential surface 110b of the rotor 11 in the radial direction of the drive scroll 30 and the stator core 17a.

[0101] As described above, the housing body 60 has a shape in which the inner diameter expands from the front end to the rear end, from a first length L1 to a second length L2. For this reason, the distance between the outer circumferential surface 110a of the rotor 11 and the inner circumferential surface 602 of the housing body 60 in the radial direction of the drive scroll 30 (hereinafter referred to as the passage width of the first intake passage 71) is wider than the distance between the outer cylindrical portion 37c and the inner circumferential surface 602, the distance between the drive circumferential wall 35 and the inner circumferential surface 602, and the distance between the outer circumferential wall 39a and the inner circumferential surface 602. In addition, the passage width of the first intake passage 71 gradually widens from front to rear in the direction of the drive axis O1.

[0102] Furthermore, the passage width of the first intake passage 71 is wider than the distance between the outer circumferential surface 110a of the rotor 11 and the inner circumferential surface 602 of the housing body 60 in the radial direction of the drive scroll 30 (hereinafter referred to as the passage width of the second intake passage 72). Unlike the passage width of the first intake passage 71, the passage width of the second intake passage 72 remains constant and does not expand or contract.

[0103] Furthermore, in this compressor, the width of the first intake passage 71 is set to a size that generates a shear force in the refrigerant flowing through the first intake passage 71 due to the rotating rotor 11. Specifically, in this compressor, the maximum width of the first intake passage 71 is approximately 1 mm. On the other hand, the maximum width of the second intake passage 72 is approximately 0.5 mm. Note that the width of the first intake passage 71 can be designed as appropriate, as long as it is large enough to generate a shear force in the refrigerant flowing through the first intake passage 71 due to the rotating rotor 11. Also, in Figures 1 to 4, the widths of the first intake passage 71 and the second intake passage 72 are exaggerated in the illustrations for the sake of clarity.

[0104] Furthermore, in this compressor, the drive scroll 30 and rotor 11 are arranged within the scroll chamber 65, so that the intake port 81 faces the front portion of the rotor 11 in the radial direction of the drive scroll 30. In other words, in this compressor, the intake port 81 is located closer to the rotor 11 than the case 39 in the direction of the drive axis O1. The intake port 81 is in direct communication with the first intake passage 71.

[0105] In this compressor configured as described above, as shown by the dashed arrows in Figures 1 and 2, low-temperature, low-pressure refrigerant that has passed through the evaporator is drawn into the scroll chamber 65 from the intake port 81. When the electric motor 10 operates and the rotor 11 rotates in the scroll chamber 65, the rotation of the rotor 11 is transmitted to the drive scroll 30, causing the drive scroll 30 to rotate around the drive axis O1. In other words, the drive scroll 30 and the rotor 11 rotate together around the drive axis O1. At this time, in the driven mechanism 20, each orbital pin 21 slides against the inner circumferential surface of each ring 22, causing each ring 22 to rotate relatively around the center of each orbital pin 21. In this way, the driven mechanism 20 transmits the torque of the drive scroll 30 to the driven scroll 40.

[0106] As a result, the driven scroll 40 is rotated by the drive scroll 30 and the driven mechanism 20 around the driven axis O2. At this time, the driven mechanism 20 restricts the driven scroll 40 from rotating relative to the drive scroll 30. This causes the driven scroll 40 to revolve relative to the drive scroll 30 around the driven axis O2. Then, as the drive volute body 33 and the driven volute body 43 rotate within the intake section 30a, the drive volute body 33 and the driven volute body 43 change the volume of the compression chamber 12.

[0107] In this compressor, the suction port 374 of the cover body 37 is located radially inward of the drive scroll 30 compared to the outer cylindrical portion 37c. Therefore, the refrigerant drawn into the scroll chamber 65 from the suction connection port 81 flows through the first suction passage 71 toward the rear of the scroll chamber 65 as it moves toward the suction port 374 (see the dashed arrows in Figures 1 and 2). Here, the refrigerant drawn into the scroll chamber 65 from the suction connection port 81 contains lubricating oil. Therefore, this lubricating oil also flows through the first suction passage 71 toward the rear of the scroll chamber 65 together with the lubricating oil.

[0108] Furthermore, in this compressor, not only gaseous refrigerant, which is a gaseous phase refrigerant, but also liquid refrigerant, which is a liquid phase refrigerant, can be drawn into the scroll chamber 65 from the intake port 81. Therefore, the liquid refrigerant also flows through the first intake passage 71. In this compressor, the rotating rotor 11 generates a shear force on the refrigerant flowing through the first intake passage 71, so that even if liquid refrigerant flows through the first intake passage 71, it is possible to evaporate this liquid refrigerant into gaseous refrigerant during the process of flowing through the first intake passage 71.

[0109] Then, the refrigerant and lubricating oil that have passed through the first intake passage 71 collide with the front surface 61a of the first housing cover 61 and change their flow direction so that they are directed towards the front of the scroll chamber 65. As a result, the refrigerant and lubricating oil that have passed through the first intake passage 71 flow through the second intake passage 72 toward the front of the scroll chamber 65.

[0110] In this way, the refrigerant and lubricating oil circulating in the second intake passage 72 are guided to the intake port 374 by the second intake passage 72. Here, the refrigerant and lubricating oil circulating in the second intake passage 72 reach the containment section 38 before the intake port 374, and are then drawn into the compression chamber 12 via the intake section 30a from the intake port 374. At this time, the intake port 374 draws the refrigerant and lubricating oil into the intake section 30a and, consequently, the compression chamber 12, from outside the driven end plate 41.

[0111] Furthermore, in this compressor, the rotating rotor 11 generates a shear force on the refrigerant flowing through the second intake passage 72. As a result, even if there is liquid refrigerant that was not completely evaporated during the process of flowing through the first intake passage 71, this liquid refrigerant can be evaporated during the process of flowing through the second intake passage 72. In addition, in this compressor, a portion of the refrigerant and lubricating oil that has passed through the first intake passage 71 also reaches the housing section 38 by flowing through slits formed in the stator core 17a and is drawn into the compression chamber 12 from the intake port 374.

[0112] The compression chamber 12 compresses the refrigerant by reducing its own volume while confining it within itself, through the rotational drive of the drive scroll 30 and the rotational movement of the driven scroll 40. The high-pressure refrigerant, thus compressed to the discharge pressure, is discharged from the discharge port 32 into the discharge chamber 14. At this time, the lubricating oil in the compression chamber is discharged from the discharge port 32 into the discharge chamber 14 along with the high-pressure refrigerant. The high-pressure refrigerant discharged into the discharge chamber 14 is then discharged to the outside of the compressor via the discharge passage 390 and the discharge connecting port 69. In this compressor, the space between the discharge passage 390 and the discharge connecting port 69 and the scroll chamber 65 is sealed by the shaft seal member 63, preventing the refrigerant flowing from the discharge passage 390 to the discharge connecting port 69 from flowing into the scroll chamber 65.

[0113] Thus, in this compressor, the rotor 11 can be suitably cooled by a low-temperature refrigerant that is drawn into the scroll chamber 65 from the intake port 81 and flows from front to back through the first intake passage 71. Furthermore, in this compressor, the rotor 11 and the stator 17 can be suitably cooled by a low-temperature refrigerant that flows from back to front through the second intake passage 72.

[0114] In other words, in this compressor, the rotor 11 is cooled not only from its outer surface 110a side by the refrigerant flowing through the first intake passage 71, but also from its inner surface 110b side by the refrigerant flowing through the second intake passage 72. Thus, in this compressor, it is possible to sufficiently cool the rotor 11 with a low-temperature refrigerant.

[0115] Furthermore, in this compressor, the second coil end 172 of the stator 17 can be suitably cooled by the refrigerant that flows through the first intake passage 71 to the second intake passage 72. The first coil end 171 of the stator 17 can be suitably cooled by the refrigerant that has reached the housing section 38 before being drawn into the intake port 374. As a result, the stator core 17a, the first coil end 171 and the second coil end 172, i.e., the stator 17, can also be sufficiently cooled by a low-temperature refrigerant.

[0116] In this way, the electric motor 10 can be sufficiently cooled by the refrigerant flowing through the first intake passage 71 and the second intake passage 72 in this compressor, thereby suppressing the deterioration of the electric motor 10's performance due to heat generation.

[0117] Therefore, the compressor of Example 1 is highly reliable.

[0118] In particular, in this compressor, the rotor body 11a is formed by multiple electromagnetic steel sheets 111 stacked in the direction of the drive axis O1. As the refrigerant flows through the first intake passage 71 and the second intake passage 72, the rotor body 11a, that is, each electromagnetic steel sheet 111, can come into direct contact with the refrigerant. In this respect as well, this compressor is capable of sufficiently cooling the rotor 11 and, consequently, the electric motor 10, with the refrigerant.

[0119] Furthermore, since the electric motor 10 can be sufficiently cooled by the refrigerant in this manner, this compressor does not require the rotor body 11a, or by extension the rotor 11, to be enlarged in order to suppress iron loss of the rotor body 11a due to heat. In addition, this compressor does not require the use of a magnet core 11b with excessively high demagnetization resistance in order to suppress demagnetization due to heat. For these reasons, this compressor achieves miniaturization and lower manufacturing costs.

[0120] Furthermore, in this compressor, the high-temperature refrigerant compressed in the compression chamber 12 is discharged into the discharge chamber 14, so the discharge chamber 14 and the case 39 inevitably become hot. In this respect, in this compressor, the intake port 81 is positioned closer to the rotor 11 than to the case 39 in the direction of the drive axis O1. As a result, the refrigerant drawn into the scroll chamber 65 from the intake port 81 is less affected by the heat of the discharge chamber 14 and the case 39.

[0121] In this compressor, the suction port 81 is directly connected to the first suction passage 71 because it faces the front portion of the rotor 11 in the radial direction of the drive scroll 30. Thus, in this compressor, the refrigerant drawn in from the suction port 81 can be circulated through the first suction passage 71 by changing the direction of flow while directly contacting a portion of the outer circumferential surface 110a of the rotor 11 in the radial direction of the drive scroll 30. In this respect as well, this compressor is capable of sufficiently cooling the rotor 11 with the refrigerant.

[0122] Furthermore, in this compressor, the inner diameter of the housing body 60 expands from the first length L1 to the second length L2. As a result, the passage width of the first intake passage 71, that is, the distance between the outer peripheral surface 110a of the rotor 11 and the inner peripheral surface 602 of the housing body 60 in the radial direction of the drive scroll 30, is wider than the distance between the outer cylindrical portion 37c and the inner peripheral surface 602, the distance between the drive peripheral wall 35 and the inner peripheral surface 602, and the distance between the outer peripheral wall 39a and the inner peripheral surface 602. Therefore, in this compressor, lubricating oil is less likely to accumulate in the first intake passage 71, and the flow of refrigerant in the first intake passage 71 is less likely to be obstructed.

[0123] In particular, the width of the first intake passage 71 gradually widens from front to rear. Thus, in this compressor, the shape of the inner surface of the first intake passage 71, that is, the inner circumferential surface 602 of the housing body 60 which gradually moves away from the rotor 11 in the radial direction of the drive scroll 30, makes it possible to suitably guide the lubricating oil flowing through the first intake passage 71 to the rear of the first intake passage 71. In this respect as well, in this compressor, lubricating oil is less likely to accumulate in the first intake passage 71.

[0124] Furthermore, in this compressor, the rotating rotor 11 generates shear force on the refrigerant flowing through the first intake passage 71 and the refrigerant flowing through the second intake passage 72, thereby enabling the evaporation of the liquid refrigerant. As a result, this compressor effectively prevents the liquid refrigerant from being drawn into the compression chamber 12.

[0125] (Example 2) As shown in Figure 3, in the compressor of Example 2, the housing body 60 does not have an intake port 81. On the other hand, in this compressor, an intake port 82 is formed in the second housing cover 62. The intake port 82 is also connected to the evaporator (not shown) through piping (not shown).

[0126] In the second housing cover 62, the intake port 82 is located on the outer circumference side of the discharge port 83. The intake port 82 communicates with the scroll chamber 65 in the direction of the drive axis O1. As a result, the intake port 82 faces the front wall 39b of the case 39 from the front.

[0127] Furthermore, in this compressor, a third intake passage 73 is formed between the outer peripheral wall 39a of the case 39 and the inner peripheral surface 602 of the housing body 60, between the drive peripheral wall 35 and the inner peripheral surface 602, and between the outer cylindrical portion 37c of the cover body 37 and the inner peripheral surface 602. The third intake passage 73 is located in front of the first intake passage 71. The third intake passage 73 also gradually widens as it moves from front to rear in the direction of the drive axis O1. The third intake passage 73 communicates with the front end of the first intake passage 71 at its rear end. Other components of this compressor are the same as those of the compressor in Embodiment 1, and the same reference numerals are used for the same components, and detailed descriptions of the components are omitted.

[0128] In this compressor, the refrigerant drawn into the scroll chamber 65 through the intake port 82 flows through the third intake passage 73, colliding with the outer peripheral wall 39a of the case 39 in the direction of the drive axis O1. This refrigerant is then guided to the first intake passage 71 by flowing from front to rear through the third intake passage 73. In this way, this compressor also makes it possible to suitably cool the electric motor 10 as the refrigerant is drawn into the compression chamber 12 while flowing through the first intake passage 71 and the second intake passage 72.

[0129] In this way, by having the refrigerant flow through the third intake passage 73, even if the intake port 82 is positioned in front of the first intake passage 71, the refrigerant drawn into the scroll chamber 65 from the intake port 82 can be suitably circulated through the first intake passage 71 in this compressor.

[0130] Furthermore, in this compressor, the lubricating oil contained in the refrigerant is suitably separated from the refrigerant during the process in which the refrigerant drawn into the scroll chamber 65 from the intake port 82 collides with the outer peripheral wall 39a. As a result, this compressor can suitably lubricate the inside of the scroll chamber 65, and consequently the drive scroll 30, the first radial ball bearing 51, and the second radial ball bearing 52, etc., with the lubricating oil. Other functions of this compressor are the same as those of the compressor in Example 1.

[0131] (Example 3) As shown in Figure 4, in the compressor of Embodiment 3, the housing 6 has a housing body 68 instead of a housing body 60. Thus, in this compressor, the housing 6 is composed of the housing body 68, a first housing cover 61, and a second housing cover 62.

[0132] The housing body 68 is also made of aluminum alloy and has a cylindrical shape centered on the drive shaft O1. The housing body 68 has an outer circumferential surface 681 and an inner circumferential surface 682. The housing body 68 also has a first inner diameter portion 68a with an inner diameter length of first length L1 and a second inner diameter portion 68b with an inner diameter length of second length L2. The first inner diameter portion 68a constitutes the front and central portions of the housing body 68, and the second inner diameter portion 68b constitutes the rear portion of the housing body 68.

[0133] Furthermore, the housing body 68 has a stepped portion 68c. The stepped portion 68c is located between the first inner diameter portion 68a and the second inner diameter portion 68b in the direction of the drive axis O1. Also, the stepped portion 68c is located rearward from the center of the housing body 68 in the direction of the drive axis O1.

[0134] Furthermore, an intake port 84 is formed in the housing body 68. The intake port 84 is located approximately in the center in the front-to-back direction of the housing body 68. As a result, the intake port 84 is located in front of the stepped portion 68c. The intake port 84 is also connected to the evaporator (not shown) through piping (not shown).

[0135] In this compressor, a first intake passage 75 is formed between the outer circumferential surface 110a of the rotor 11 in the radial direction of the drive scroll 30 and the inner circumferential surface 682 of the housing body 68. The stepped portion 68c is located within the first intake passage 75. As a result, the distance between the outer circumferential surface 110a of the rotor 11 in the radial direction of the drive scroll 30 and the inner circumferential surface 682 of the housing body 68 (hereinafter referred to as the passage width of the first intake passage 75) is wider on the rear side than on the front side. In other words, the passage width of the first intake passage 75 changes in steps at the stepped portion 68c. Other functions of this compressor are the same as those of the compressor in Embodiment 1.

[0136] In this compressor, the refrigerant drawn into the scroll chamber 65 from the intake port 84 flows through the first intake passage 75 and the second intake passage 72 before being drawn into the compression chamber 12. This makes it possible to suitably cool the electric motor 10 as the refrigerant flows through the first intake passage 75 and the second intake passage 72, even in this compressor.

[0137] Furthermore, in this compressor, the width of the first intake passage 75 is wider on the rear side than on the front side, making it less likely for lubricating oil to accumulate in the first intake passage 75. Other functions of this compressor are the same as those of the compressor in Example 1.

[0138] Although the present invention has been described above in reference to Examples 1 to 3, it goes without saying that the present invention is not limited to Examples 1 to 3, and can be applied with appropriate modifications without departing from its spirit.

[0139] For example, in the compressors of Examples 1 to 3, the protruding body 64 is integrally provided with respect to the first housing cover 61. However, the design is not limited to this, and the first housing cover 61 and the protruding body 64 may be formed separately, with the protruding body 64 fixed to the first housing cover 61. In this case, it is also easy to form the first housing cover 61 and the protruding body 64 from different materials.

[0140] Furthermore, in the compressors of Examples 1 to 3, an outer cylindrical portion 37c is formed on the cover body 37. However, the invention is not limited to this configuration; the rotor 11 may also be configured to serve as the "cylindrical portion" in the present invention by omitting the formation of the outer cylindrical portion 37c and extending the rotor 11 in the direction of the drive axis O1, thereby connecting the rotor 11 to the wall portion 37a.

[0141] Furthermore, in the compressors of Examples 1 to 3, the outer cylindrical portion 37c may be a separate component from the rotor 11 and the wall portion 37a of the cover body 37.

[0142] Furthermore, in the compressors of Examples 1 to 3, a recirculation passage may be formed to recirculate the lubricating oil contained in the refrigerant discharged into the discharge chamber 14 back to the first radial ball bearing 51 and the like for lubrication.

[0143] Furthermore, this specification includes the following inventions. (Note 1) The system comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism. The housing has a scroll chamber into which the drive scroll, the driven scroll, the drive mechanism, and the driven mechanism are housed, and into which fluid is drawn from the outside. The drive scroll is rotationally driven around the drive axis by the drive mechanism, The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. The drive scroll and the driven scroll form a compression chamber that compresses the fluid through the rotational drive and the rotational drive, The drive mechanism comprises a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator. The stator is a double-rotation scroll compressor having a cylindrical stator core extending in the direction of the drive axis, a first coil end protruding cylindrically from the stator core to one side in the direction of the drive axis, and a second coil end located on the opposite side of the stator core from the first coil end and protruding cylindrically to the other side in the direction of the drive axis. The scroll chamber is provided with a projection that extends toward the drive scroll and the driven scroll in the direction of the drive axis, and to which the stator core is fixed. The drive scroll has a cover body that is rotationally driven by the rotor, The cover body extends radially in the direction of the drive scroll and has a wall portion facing the first coil end in the direction of the drive axis, A cylindrical portion is connected to the wall portion, extending cylindrically in the direction of the drive axis and covering the first coil end from the radially outside, while transmitting the rotational drive of the rotor to the cover body. An intake port is formed, located radially inward from the cylindrical portion, to draw the fluid in the scroll chamber into the compression chamber. A first intake passage is formed between the housing and the rotor in the radial direction, allowing the fluid in the scroll chamber to flow from the cover side to the rotor side in the direction of the drive axis. A double-rotating scroll compressor characterized in that a second intake passage is formed between the rotor and the stator in the radial direction, which guides the fluid that has flowed through the first intake passage to the intake port while flowing it from the rotor side toward the cover body side in the direction of the drive axis. (Note 2) The housing is provided with an intake port for drawing fluid into the scroll chamber from the outside. The drive scroll has a case in which a discharge chamber is formed inside from which the fluid compressed in the compression chamber is discharged. The case is located on one side of the cover body in the direction of the drive axis, The double-rotation scroll compressor described in Appendix 1, wherein the intake port is located closer to the cover body than the case in the direction of the drive axis. (Note 3) The suction port is located opposite at least a portion of the rotor in the radial direction, as described in Appendix 2 of the double-rotating scroll compressor. (Note 4) The housing is provided with an intake port for drawing fluid into the scroll chamber from the outside. The drive scroll has a case in which a discharge chamber is formed inside from which the fluid compressed in the compression chamber is discharged. The case is located on one side of the cover body in the direction of the drive axis, The aforementioned intake port faces the case in the direction of the drive axis, The double-rotation scroll compressor according to Appendix 1, wherein a third intake passage is formed in the scroll chamber, located on one side of the drive axis direction from the first intake passage, and allowing the fluid to flow toward the first intake passage in the drive axis direction. (Note 5) The aforementioned fluid is a refrigerant, A double-rotating scroll compressor according to any one of the appendices 1 to 4, wherein in the radial direction, the housing and the rotor are separated by an interval such that the rotating rotor generates a shear force on the refrigerant flowing through the first intake passage. (Note 6) The housing has a main body portion extending in the direction of the drive axis, The main body portion includes a first inner diameter portion located on one side of the rotor in the direction of the drive axis, It has a second inner diameter portion located on the other side of the drive axis direction from the first inner diameter portion, which is connected to the first inner diameter portion in the drive axis direction and faces the rotor in the radial direction, The double-rotating scroll compressor according to any one of the appendices 1 to 5, wherein the second inner diameter portion is formed to be larger in diameter than the first inner diameter portion. (Note 7) The main body is a double-rotating scroll compressor as described in Appendix 6, wherein the diameter gradually increases from the first inner diameter portion toward the second inner diameter portion in the direction of the drive axis. (Note 8) The rotor has a cylindrical rotor body formed from a plurality of electromagnetic steel plates stacked in the direction of the drive axis, The first intake passage is formed between the inner circumferential surface of the housing and the outer circumferential surface of the rotor body in the radial direction. A double-rotation scroll compressor according to any one of the appendices 1 to 7, wherein the second intake passage is formed between the inner circumferential surface of the rotor and the outer circumferential surface of the stator in the radial direction. [Industrial applicability]

[0144] This invention can be used in vehicle air conditioning systems and the like. [Explanation of Symbols]

[0145] 6… Housing 10…Electric motor (drive mechanism) 11…Rota 11a...Rotor body 12... Compression chamber 14...Discharge chamber 17…Status 17a... Stator core 20…Following mechanism 30…Drive Scroll 31…Drive end plate 33…Driving vortex 35… Driven peripheral wall 37... Cover body 37a...Wall part 37c...Cylinder part 39... Cases 40...Driven Scroll 41…Driven end plate 43... Driven vortex 60, 68... Housing body (main body) 60a, 68a...First inner diameter section 60b, 68b...2nd inner diameter part 64...Protruding body 65…Scroll Room 71, 75...1st suction passage 72…Second suction passage 73...Third suction passage 81, 82, 84... Inhalation port 111...Electromagnetic steel plate 171...First coil end 172... Second coil end 374... Inlet O1...Drive shaft center O2…driven shaft center

Claims

1. The system comprises a housing, a drive scroll, a driven scroll, a drive mechanism, and a driven mechanism. The housing has a scroll chamber into which the drive scroll, the driven scroll, the drive mechanism, and the driven mechanism are housed, and into which fluid is drawn from the outside. The drive scroll is rotationally driven around the drive axis by the drive mechanism, The driven scroll is rotated and driven by the driven scroll and the driven mechanism around its driven axis, while being eccentric with respect to the driven scroll. The drive scroll and the driven scroll form a compression chamber that compresses the fluid through the rotational drive and the rotational drive, The drive mechanism comprises a stator and a rotor that covers the stator from the outside and is rotationally driven by the stator. The stator is a double-rotating scroll compressor having a cylindrical stator core extending in the direction of the drive axis, a first coil end protruding cylindrically from the stator core to one side in the direction of the drive axis, and a second coil end located on the opposite side of the stator core from the first coil end and protruding cylindrically to the other side in the direction of the drive axis. The scroll chamber is provided with a projection that extends toward the drive scroll and the driven scroll in the direction of the drive axis, and to which the stator core is fixed. The drive scroll has a cover body that is rotationally driven by the rotor, The cover body extends radially in the direction of the drive scroll and has a wall portion facing the first coil end in the direction of the drive axis, A cylindrical portion is connected to the wall portion, extending cylindrically in the direction of the drive axis and covering the first coil end from the radially outside, while transmitting the rotational drive of the rotor to the cover body. An intake port is formed, located radially inward from the cylindrical portion, to draw the fluid in the scroll chamber into the compression chamber. A first intake passage is formed between the housing and the rotor in the radial direction, allowing the fluid in the scroll chamber to flow from the cover side to the rotor side in the direction of the drive axis. A double-rotating scroll compressor characterized in that a second intake passage is formed between the rotor and the stator in the radial direction, which guides the fluid that has flowed through the first intake passage to the intake port while flowing it from the rotor side toward the cover body side in the direction of the drive axis.

2. The housing is provided with an intake port for drawing fluid into the scroll chamber from the outside. The drive scroll has a case in which a discharge chamber is formed inside from which the fluid compressed in the compression chamber is discharged. The case is located on one side of the cover body in the direction of the drive axis, The double-rotating scroll compressor according to claim 1, wherein the intake port is located closer to the cover body than the case in the direction of the drive axis.

3. The double-rotating scroll compressor according to claim 2, wherein the intake port faces at least a portion of the rotor in the radial direction.

4. The housing is provided with an intake port for drawing fluid into the scroll chamber from the outside. The drive scroll has a case in which a discharge chamber is formed inside from which the fluid compressed in the compression chamber is discharged. The case is located on one side of the cover body in the direction of the drive axis, The aforementioned intake port faces the case in the direction of the drive axis, The double-rotating scroll compressor according to claim 1, wherein a third intake passage is formed in the scroll chamber, located on one side of the drive axis direction from the first intake passage, and allowing the fluid to flow toward the first intake passage in the drive axis direction.

5. The aforementioned fluid is a refrigerant, The double-rotating scroll compressor according to any one of claims 1 to 4, wherein in the radial direction, the housing and the rotor are separated by an interval such that the rotating rotor generates a shear force on the refrigerant flowing through the first intake passage.

6. The housing has a main body portion extending in the direction of the drive axis, The main body portion includes a first inner diameter portion located on one side of the rotor in the direction of the drive axis, It has a second inner diameter portion located on the other side of the drive axis direction from the first inner diameter portion, which is connected to the first inner diameter portion in the drive axis direction and faces the rotor in the radial direction, The double-rotating scroll compressor according to any one of claims 1 to 4, wherein the second inner diameter portion is formed to be larger in diameter than the first inner diameter portion.

7. The main body is a double-rotating scroll compressor according to claim 6, wherein the diameter of the main body gradually increases from the first inner diameter portion toward the second inner diameter portion in the direction of the drive axis.

8. The rotor has a cylindrical rotor body formed from a plurality of electromagnetic steel plates stacked in the direction of the drive axis, The first intake passage is formed between the inner circumferential surface of the housing and the outer circumferential surface of the rotor body in the radial direction. The double-rotation scroll compressor according to any one of claims 1 to 4, wherein the second intake passage is formed between the inner circumferential surface of the rotor and the outer circumferential surface of the stator in the radial direction.

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