Double-rotating scroll compressor

Abstract

To provide a co-rotating scroll compressor having excellent durability.SOLUTION: In a co-rotating scroll compressor of the present invention, a driving scroll 31 has a driving end plate 31, a driving spiral body 33, a driving peripheral wall 35, and a cover body 37, and a driven scroll 41 has a driven end plate 41 and a driven spiral body 43. The driven end plate 41 is disposed between the driving peripheral wall 35 and the cover body 37 in a state where the driven end plate can be rotationally driven. The driven end plate 41 and the driving peripheral wall 35 can abut against each other. In this co-rotating scroll compressor, in the state where the driven end plate 41 and the driving peripheral wall 35 are in abutment against each other, a gap S2 between the driven scroll body 43 and the driving end plate 31 and a gap S3 between the driving scroll body 33 and the driven end plate 41 are set such that the driven scroll body 43 and the driving end plate 31 are not in contact with each other and the driving scroll body 33 and the driven end plate 41 are not in contact with each other.SELECTED DRAWING: Figure 6

Description

[Technical Field]

[0001] The present invention relates to a double-rotating scroll compressor. [Background technology]

[0002] Patent Document 1 discloses a conventional double-rotating scroll compressor. This double-rotating scroll compressor includes a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism. The housing accommodates the drive mechanism, the drive scroll, the driven scroll, and the driven mechanism.

[0003] The drive mechanism has a rotor. The rotor has a generally disk-shaped bottom wall portion and a cylindrical portion extending from the bottom wall portion toward the drive axis. The drive scroll has a drive end plate, a drive spiral, and a drive peripheral wall. The drive spiral is integral with the drive end plate and projects spirally toward the driven scroll. The drive peripheral wall projects cylindrically toward the driven scroll. The drive peripheral wall is integral with the drive end plate and surrounds the drive spiral. The drive scroll is integrated with the rotor by fixing the drive peripheral wall to the cylindrical portion of the rotor. As a result, the drive scroll is driven to rotate around the drive axis by the drive mechanism.

[0004] The driven scroll is disposed inside the rotor, more specifically, between the bottom wall portion of the rotor and the driving scroll in the drive axial direction. The driven scroll faces the driving scroll inside the rotor. The driven scroll has a driven end plate and a driven scroll. The driven end plate faces the driving scroll and the drive peripheral wall. The driven scroll is integral with the driven end plate and protrudes spirally toward the drive end plate. The driving scroll and the driven scroll face each other to form a compression chamber for compressing a fluid.

[0005] The driven mechanism is disposed between the bottom wall portion of the rotor and the driven end plate of the driven scroll, so that the driven scroll is rotated by the driving scroll and the driven mechanism about a driven axis that is eccentric to the drive axis and can revolve relative to the driving scroll.

[0006] In this scroll compressor, the drive scroll rotates about the drive axis and the driven scroll rotates about the driven axis, thereby changing the volume of the compression chamber. As a result, fluid is drawn into the compression chamber from outside the drive scroll and the driven scroll and compressed in the compression chamber. The compressed fluid is then discharged from the compression chamber to outside the drive scroll and the driven scroll. [Prior art documents] [Patent documents]

[0007] [Patent Document 1] Japanese Patent Application Publication No. 7-229480 Summary of the Invention [Problem to be solved by the invention]

[0008] In the conventional double-rotating scroll compressor described above, a tilting moment inevitably acts on the driven scroll during operation due to a reaction force from the fluid compressed in the compression chamber, tilting the driven scroll relative to the drive axis and the driven axis. This tilting moment causes the driven scroll to tilt, bringing the driven scroll into contact with the drive end plate. When the drive scroll and the driven end plate come into contact, the driven scroll tilted by the tilting moment is supported by the drive scroll and the driven scroll. This increases the load on the drive scroll and the driven scroll, making them more susceptible to damage. This raises concerns about reduced durability in this double-rotating scroll compressor.

[0009] The present invention has been made in view of the above-mentioned conventional circumstances, and an object to be achieved is to provide a double-rotation scroll compressor having excellent durability. [Means for solving the problem]

[0010] The double-rotating scroll compressor of the present invention comprises a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism, the drive scroll is driven to rotate about a drive axis by the drive mechanism; The driven scroll is rotated around a driven axis by the driving scroll and the driven mechanism while being eccentric with respect to the driving scroll, The drive scroll has a drive end plate extending in a direction intersecting the drive axis, a drive circumferential wall protruding in a cylindrical shape from the drive end plate toward the driven scroll, and a drive scroll body protruding in a spiral shape from the drive end plate toward the driven scroll within the drive circumferential wall, The driven scroll has a driven end plate extending in a direction intersecting the driven axis, and a driven scroll protruding in a spiral shape from the driven end plate toward the drive scroll, The drive scroll and the driven scroll form a compression chamber by opposing each other, and the volume of the compression chamber is changed by the rotation driving and the rotation driven, The driving scroll has a cover body fixed to the driving peripheral wall, the driven end plate is disposed between the driving peripheral wall and the cover body in a rotationally driven state; a sum of a gap between the driving peripheral wall and the driven end plate in the drive axial direction and a gap between the driven end plate and the cover body in the drive axial direction is a first gap, a gap between the drive end plate and the driven scroll in the drive shaft direction is a second gap; a gap between the driven end plate and the driving scroll in the drive shaft direction is a third gap; The driven end plate and the driving peripheral wall in the direction of the drive shaft The driven end plate and the driving peripheral wall are capable of abutting against each other. In the direction of the drive shaft In the abutting state, the driven scroll and the driving end plate, and the driving scroll and the driven end plate, are not in contact with each other, The second gap and the third gap are larger than the first gap.It is characterized by:

[0011] In the double rotary scroll compressor of the present invention, the driven end plate is disposed between the drive peripheral wall and the cover body in a state in which it can be rotated. The driven end plate and the drive peripheral wall can abut against each other. Here, in this double rotary scroll compressor, the driven end plate and the drive peripheral wall are In the direction of the drive shaft A gap between the driven scroll and the drive end plate is set so that the driven scroll and the drive end plate, and the drive scroll and the driven end plate, are not in contact with each other when they are in contact with each other. The second gap is , and the gap between the driving scroll and the driven end plate The third gap is larger than the first gap. is doing.

[0012] As a result, in this double rotary scroll compressor, even if the driven scroll tilts due to the tilting moment during operation and the driven end plate comes into contact with the driving peripheral wall, the driven scroll and the driving end plate will not come into contact, and the driving scroll and the driven end plate will not come into contact.

[0013] In this double-rotary scroll compressor, the tilting moment acting on the driven scroll can be appropriately supported by the drive peripheral wall and the driven end plate. Furthermore, in this double-rotary scroll compressor, the driven scroll, which tilts due to the tilting moment, does not need to be supported by the drive scroll or the driven scroll, so large loads can be prevented from acting on the drive scroll and the driven scroll. As a result, in this double-rotary scroll compressor, damage to the drive scroll and the driven scroll, and ultimately to the drive scroll and the driven scroll, can be prevented.

[0014] Therefore, the double-rotating scroll compressor of the present invention has excellent durability.

[0015] Furthermore, in this double-rotating scroll compressor, the driven scroll is disposed between the drive circumferential wall and the cover, which facilitates positioning of the driven scroll relative to the drive scroll, thereby simplifying manufacturing of the double-rotating scroll compressor.

[0016] A plurality of through holes may be formed in the outer periphery of the driven end plate, and each through hole preferably contains a spacer for rotatably positioning the driven end plate between the driving peripheral wall and the cover body.

[0017] In this case, the spacer allows the driven end plate to be easily disposed between the driving peripheral wall and the cover body in a state in which it can be rotated and driven, thereby facilitating manufacturing.

[0018] The drive mechanism may have a cylindrical rotor that surrounds the peripheral wall and is fixed to the peripheral wall, and the driven end plate is preferably formed to have a larger diameter than the rotor.

[0019] In this case, the diameter of the driven end plate is increased, so that the tilting moment load acting on the driven end plate when it comes into contact with the driving peripheral wall can be reduced, thereby improving the durability of this double rotary scroll compressor.

[0020] In both rotary scroll compressors, when the driven end plate is disposed between the driving peripheral wall and the cover body, the driven end plate protrudes radially beyond the driving peripheral wall, which facilitates the placement of the driven end plate between the driving peripheral wall and the cover body during manufacturing, and also facilitates the positioning of the driven scroll relative to the driving scroll. [Effects of the Invention]

[0021] The double-rotating scroll compressor of the present invention is excellent in durability. [Brief explanation of the drawings]

[0022] [Figure 1] FIG. 1 is a cross-sectional view of a scroll compressor according to an embodiment of the present invention. [Figure 2] FIG. 2 is a cross-sectional view taken along line AA in FIG. 1, showing the housing, the cover body, etc., of the scroll compressor of the embodiment. [Figure 3]FIG. 3 is an enlarged cross-sectional view of the scroll compressor of the embodiment, showing the driving peripheral wall, the cover body, the space, and the like. [Figure 4] FIG. 4 is a cross-sectional view of the scroll compressor of the embodiment, taken in the same direction as FIG. 2, showing a driven end plate and the like. [Figure 5] FIG. 5 is a cross-sectional view taken in the same direction as FIG. 2, showing the housing, the cover body, the driven end plate, etc., of the scroll compressor of the embodiment. [Figure 6] FIG. 6 is an enlarged cross-sectional view similar to FIG. 3 showing the scroll compressor of the embodiment, in which a driven end plate is disposed between the drive peripheral wall and the cover body, and the cover body is fixed to the drive peripheral wall. [Figure 7] 7 is an enlarged cross-sectional view taken along the line BB in FIG. 5 showing the drive scroll, the driven scroll, etc. when the driven scroll is tilted by a tilting moment in the scroll compressor of the embodiment. [Figure 8] FIG. 8 is an enlarged cross-sectional view similar to FIG. 6 of a main part of a scroll compressor of a comparative example, showing a state in which a driven end plate is disposed between the drive peripheral wall and the cover body, and a cover body is fixed to the drive peripheral wall. [Figure 9] FIG. 9 is an enlarged cross-sectional view of a main part of a scroll compressor of a comparative example, similar to FIG. 7, showing a driving scroll, a driven scroll, etc. when the driven scroll is tilted by a tilting moment. DETAILED DESCRIPTION OF THE INVENTION

[0023] Hereinafter, embodiments of the present invention will be described with reference to the drawings. A double-rotating scroll compressor (hereinafter simply referred to as a compressor) of the embodiment is mounted in a vehicle (not shown) and constitutes an air conditioning system for the vehicle.

[0024] The compressor of the embodiment includes a housing 6 shown in Fig. 1, an electric motor 10, a driving scroll 30, a driven scroll 40, a driven shaft 16, and a driven mechanism 20 shown in Fig. 5. The electric motor 10 is an example of the "drive mechanism" of the present invention.

[0025] In this embodiment, the front-to-rear direction of the compressor is defined by the solid arrows shown in Fig. 1. Also, in this embodiment, the solid arrows shown in Fig. 2 define the radial direction of the driven end plate 41, and therefore the radial direction of the driven scroll 40. In Fig. 3 and subsequent figures, the radial direction of the compressor and the radial direction of the driven end plate 41 are defined in accordance with Figs. 1 and 2. Note that these front-to-rear directions and the like are merely examples for the sake of convenience, and the compressor's position can be changed as appropriate depending on the vehicle in which it is installed.

[0026] 1, the housing 6 is made up of a housing main body 60, a bearing housing 61, and a housing cover 62. The housing main body 60, the bearing housing 61, and the housing cover 62 are made of an aluminum alloy.

[0027] The housing body 60 is a cylindrical member with a bottom and includes a first outer peripheral wall 60a and a rear wall 60b. The first outer peripheral wall 60a is cylindrical and has a drive axis O1 as its center. The drive axis O1 is parallel to the front-rear direction.

[0028] The first outer peripheral wall 60a has an inner peripheral surface 601. The first outer peripheral wall 60a is also formed with an intake communication port 68. The intake communication port 68 extends in the radial direction of the housing body 60. The intake communication port 68 is connected to an evaporator (not shown) through piping (not shown).

[0029] The rear wall 60b is located at the rear end of the housing main body 60. The rear wall 60b extends in a generally circular, flat plate shape perpendicular to the drive axis O1. The outer peripheral edge of the rear wall 60b is connected to the rear end of the first outer peripheral wall 60a. The above-mentioned suction communication port 68 may be formed in the rear wall 60b.

[0030] A first support portion 64 is formed at the center of the inner surface of the rear wall 60b. The first support portion 64 is generally cylindrical and centered on the drive axis O1, and protrudes forward from the center of the inner surface of the rear wall 60b, i.e., into the suction chamber 65. A first plain bearing 51 is provided on the first support portion 64.

[0031] Furthermore, a pin hole 4 is formed in the first support portion 64. As shown in FIG. 2, the pin hole 4 is formed in the first support portion 64 at a position eccentric with respect to the drive axis O1. As shown in FIG. 1, the pin hole 4 opens to the front end surface of the first support portion 64 and extends linearly rearward within the first support portion 64. Here, the pin hole 4 does not penetrate the first support portion 64 in the front-rear direction. Therefore, the rear end of the pin hole 4 is located within the first support portion 64.

[0032] The bearing housing 61 is disposed in front of the housing body 60. The bearing housing 61 extends in a generally circular flat plate shape perpendicular to the drive axis O1. The outer peripheral edge of the bearing housing 61 abuts against the front end of the first outer peripheral wall 60a of the housing body 60.

[0033] A cylindrical second support portion 66 is provided in the center of the bearing housing 61, with its center on the drive axis O1. A second plain bearing 52 is provided inside the second support portion 66. Note that instead of the first and second plain bearings 51 and 52, ball bearings or the like may be provided in the first and second support portions 64 and 66, respectively.

[0034] The housing cover 62 is disposed in front of the bearing housing 61. The housing cover 62 is a bottomed, cylindrical member having a second outer peripheral wall 62a and a front wall 62b. The second outer peripheral wall 62a is cylindrical and centered on the drive axis O1, extending in the direction of the drive axis O1. The length of the second outer peripheral wall 62a in the direction of the drive axis O1 is shorter than the length of the first outer peripheral wall 60a of the housing main body 60 in the direction of the drive axis O1.

[0035] The front wall 62b is located at the front end of the housing cover 62. The front wall 62b extends in a generally circular flat plate shape, perpendicular to the drive axis O1. The outer peripheral edge of the front wall 62b is connected to the front end of the second outer peripheral wall 62a. A discharge communication port 69 is formed in the front wall 62b. The discharge communication port 69 extends in the direction of the drive axis O1. The discharge communication port 69 may also be formed in the second outer peripheral wall 62a.

[0036] The rear end of the second outer peripheral wall 62a of the housing cover 62 abuts against the front end of the bearing housing 61, i.e., the side of the bearing housing 61 opposite to the first outer peripheral wall 60a of the housing main body 60. In the housing 6, the bearing housing 61 abuts against the first outer peripheral wall 60a as described above, and the second outer peripheral wall 62a abuts against the bearing housing 61, and in this state, the housing cover 62, bearing housing 61, and housing main body 60 are fixed in the direction of the drive axis O1 by a plurality of bolts (not shown).

[0037] In this manner, in the housing 6, the front of the housing main body 60 is blocked by the bearing housing 61, thereby forming a suction chamber 65 within the housing main body 60. In addition, in the housing 6, the rear of the housing cover 62 is blocked by the bearing housing 61, thereby forming a discharge communication chamber 13 within the housing cover 62. That is, in the housing 6, the bearing housing 61 separates the suction chamber 65 from the discharge communication chamber 13. The suction chamber 65 communicates with the suction communication port 68. As a result, refrigerant gas is drawn into the suction chamber 65 from outside the housing 6 through the suction communication port 68. The refrigerant gas is an example of the "fluid" in the present invention. Meanwhile, the discharge communication chamber 13 communicates with the discharge communication port 69.

[0038] The electric motor 10 is accommodated in the suction chamber 65. As a result, the suction chamber 65 also serves as a motor chamber that accommodates the electric motor 10.

[0039] The electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 is formed in a cylindrical shape centered on the drive axis O1 and extending in the direction of the drive axis O1. The stator 17 also has windings 17a. The stator 17 is fixed to the housing main body 60 and, by extension, the housing 6, by fitting into the inner circumferential surface 601 of the first outer circumferential wall 60a.

[0040] The rotor 11 has a cylindrical shape centered on the drive axis O1 and extends in the direction of the drive axis O1. The rotor 11 has a smaller diameter than the stator 17 and is disposed within the stator 17. Although not shown in detail, the rotor 11 is composed of a plurality of permanent magnets corresponding to the stator 17 and laminated steel plates that secure the permanent magnets.

[0041] The driving scroll 30 is made of a metal such as an aluminum alloy and is housed in the suction chamber 65. The driving scroll 30 has a driving end plate 31, a driving scroll 33, a driving peripheral wall 35, and a cover body 37.

[0042] The drive end plate 31 comprises an end plate main body 31a and a boss 31b. The end plate main body 31a extends in a generally circular plate 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 to the front-to-rear direction.

[0043] The end plate main body portion 31 a has a first front surface 311 that faces the bearing housing 61 inside the suction chamber 65 , and a first rear surface 312 that is located on the opposite side of the first front surface 311 .

[0044] The boss portion 31b is integral with the end plate main body portion 31a. The boss portion 31b is located at the center of the drive end plate 31 and protrudes cylindrically forward from the first front surface 311 in the direction of the drive axis O1. This forms a discharge chamber 38 inside the boss portion 31b. The discharge chamber 38 extends from the front end of the boss portion 31b to the inside of the end plate main body portion 31a. The shape of the discharge chamber 38 can be designed as appropriate.

[0045] The discharge chamber 38 communicates with a discharge port 32 formed in the end plate main body 31. The discharge port 32 penetrates the end plate main body 31 in the direction of the drive axis O1. A discharge reed valve 57 and a retainer 58 are fixed in the discharge chamber 38 with a fixing bolt 59. This allows the discharge reed valve 57 to open and close the discharge port 32, and the retainer 58 to adjust the opening degree of the discharge reed valve 57.

[0046] The drive scroll 33 is integral with the end plate main body 31a of the drive end plate 31 and protrudes rearward from the first rear surface 312 of the end plate main body 31a, i.e., toward the driven scroll 40, parallel to the drive axis O1 and the driven axis O2. The drive scroll 33 has a spiral shape extending from the center of the end plate main body 31a, i.e., the center of the drive end plate 31, toward the outer periphery. As shown in Figures 3, 6, and 7, the drive scroll 33 has a rear end surface 330.

[0047] As shown in FIG. 1, the driving peripheral wall 35 is formed in a cylindrical shape centered on the driving axis O1 and extending parallel to the driving axis O1 and the driven axis O2.

[0048] The drive peripheral wall 35 has a first opposing surface 351. The first opposing surface 351 is located at the rear end of the drive peripheral wall 35. Three bolt holes 35c are formed in the drive peripheral wall 35. Each bolt hole 35c opens to the first opposing surface 351 and extends forward within the drive peripheral wall 35. Note that Figures 1 and 3 show only one of the three bolt holes 35c. The number of bolt holes 35c can be designed as appropriate.

[0049] The drive circumferential wall 35 is integral with the outer peripheral edge of the end plate main body 31a at its front end, i.e., the side opposite the first opposing surface 351. As a result, the drive circumferential wall 35 protrudes cylindrically rearward from the first rear surface 312. The drive circumferential wall 35 is located radially outward of the drive spiral 33 and surrounds it. The length by which the drive circumferential wall 35 protrudes rearward from the first rear surface 312 of the drive end plate 31 is longer than the length by which the drive spiral 33 protrudes rearward from the first rear surface 312 of the drive end plate 31. As a result, the first opposing surface 351 is spaced further rearward from the drive end plate 31 than the rear end surface 330 of the drive spiral 33 (see FIG. 3). Although not shown, the outer peripheral end of the drive spiral 33 is connected to the inner peripheral surface of the drive circumferential wall 35.

[0050] 1 and 2, the cover body 37 is composed of a cover main body portion 37a and a boss portion 37b. The cover main body portion 37a extends in a generally circular plate shape, perpendicular to the drive axis O1 and the driven axis O2. As shown in FIG. 1, the cover main body portion 37a is formed to have generally the same diameter as the end plate main body portion 31a and the drive peripheral wall 35.

[0051] 3, 6, and 7, the cover main body 37a has a second opposing surface 371 and a rear end surface 372. The second opposing surface 371 is located at the front end of the cover main body 37a and constitutes the front end surface of the cover main body 37a. The rear end surface 372 is located on the opposite side from the second opposing surface 371.

[0052] 2, the cover main body 37a is formed with a first suction port 37c and three bolt holes 37d. The first suction port 37c and each of the bolt holes 37d each penetrate the cover main body 37a from the second opposing surface 371 to the rear end surface 372. The first suction port 37c has a larger diameter than each of the bolt holes 37d. The shapes and numbers of the first suction port 37c and each of the bolt holes 37d can be designed as appropriate.

[0053] The cover main body 37a is provided with six rotation prevention pins 21. Each rotation prevention pin 21 is fixed by being inserted into a fixing hole (not shown) formed in the second opposing surface 371, and extends forward from the second opposing surface 371.

[0054] As shown in FIG. 1, the boss portion 37b is integral with the cover main body 37a at the center thereof and protrudes rearward from the cover main body 37a in the direction of the drive axis O1. An insertion hole 37e is formed in the boss portion 37b. The insertion hole 37e penetrates through the boss portion 37b and the cover main body 37a in the direction of the drive axis O1. This gives the boss portion 37b a cylindrical shape centered on the drive axis O1.

[0055] The driving scroll 30 is integrated with the rotor 11 by press-fitting the driving circumferential wall 35 into the rotor 11. As shown in Fig. 3, in the driving scroll 30, the cover body 37 is disposed rearward of the driving scroll 33 and the driving circumferential wall 35. In other words, the cover body 37 is disposed on the opposite side of the driving end plate 31 across the driving scroll 33 and the driving circumferential wall 35. The cover body 37 is disposed with the second opposing surface 371 facing the driving scroll 33 and the driving circumferential wall 35.

[0056] In the driving scroll 30, the cover body 37 is disposed farther away from the driving scroll 33 and the driving peripheral wall 35 in the direction of the driving axis O1. As a result, a space 14 is formed between the driving peripheral wall 35 and the cover body 37, more specifically, between the flange portion 35b of the driving peripheral wall 35 and the cover main body portion 37a of the cover body 37. The width of this space 14 in the direction of the driving axis O1 is a first length L1.

[0057] Thus, in the driving scroll 30, the first opposing surface 351 of the flange portion 35b and the second opposing surface 371 of the cover main body portion 37a face each other in the direction of the drive axis O1 with the space 14 in between. In other words, the first opposing surface 351 and the second opposing surface 371 face each other at an interval of a first length L1, which is the width of the space 14. As shown in FIGS. 1 and 5 to 7, the cover body 37 is fixed to the driving peripheral wall 35 by three bolts 71. The fixing of the cover body 37 to the driving peripheral wall 35 will be described in detail later.

[0058] 1 is also made of an aluminum alloy. The driven scroll 40 has a driven end plate 41 and a driven scroll 43.

[0059] 1 and 4, the driven end plate 41 extends in a generally circular plate shape perpendicular to the drive axis O1 and the driven axis O2. Here, as shown in Fig. 6, the plate thickness of the driven end plate 41 is defined as a second length L2. The second length L2 is shorter than the first length L1, which is the width of the space 14 in the direction of the drive axis O1.

[0060] 1 and 7, the driven end plate 41 has a larger diameter than the driving peripheral wall 35, the cover body 37, and the rotor 11. The driven end plate 41 has a second front surface 411 and a second rear surface 412 located on the opposite side of the second front surface 411.

[0061] As shown in Fig. 4, three through holes 41a and six mounting recesses 41b are formed in the driven end plate 41. As shown in Figs. 1, 6, and 7, each through hole 41a is located on the outer periphery of the driven end plate 41, that is, at a location on the driven end plate 41 that is closer to the outer periphery than the driven spiral body 43, and each through hole 41a extends cylindrically through the driven end plate 41 from the second front surface 411 to the second rear surface 412. As shown in Fig. 4, the through holes 41a are arranged at equal intervals in the circumferential direction of the driven end plate 41.

[0062] Each mounting recess 41b is disposed between adjacent through holes 41a in the circumferential direction of the driven end plate 41. Each mounting recess 41b is recessed in a cylindrical shape extending forward from the second rear surface 412. In other words, each mounting recess 41b does not penetrate the driven end plate 41. A ring 22 is fitted into each mounting recess 41b.

[0063] Furthermore, the driven end plate 41 is formed with a second suction port 41c and a housing portion 41d. The second suction port 41c is located between the two mounting recesses 41b. Like each through-hole 41a, the second suction port 41c is located on the outer periphery of the driven scroll 43 in the driven end plate 41, and extends cylindrically from the second front surface 411 to the second rear surface 412 through the driven end plate 41 (see FIG. 7). The second suction port 41c has a larger diameter than the first suction port 37c shown in FIG. 2 and is formed with approximately the same diameter as each through-hole 41a (see FIG. 4). The shape of the second suction port 41c can be designed as appropriate.

[0064] The accommodation portion 41d is located in the center of the driven end plate 41. The accommodation portion 41d is recessed in a cylindrical shape extending forward from the second rear surface 412 of the driven end plate 41 and centered on the driven axis O2.

[0065] A bushing 53 is accommodated within the accommodation portion 41d. A driven pin 55 is inserted into the bushing 53. In this case, the driven pin 55 is inserted into the bushing 53 at a position eccentric to the center of the bushing 53, i.e., the driven axis O2. The driven pin 55 is made of steel and has a cylindrical shape. The driven pin 55 protrudes rearward from the bushing 53 and, by extension, from the driven end plate 41. The bushing and the driven pin 55 form the driven shaft portion 16. The bushing 53 may be accommodated within the accommodation portion 41d via a bearing such as a plain bearing.

[0066] The driven end plate 41 also has three metal spacers 18. Each spacer 18 has a smaller diameter than each through-hole 41a and is disposed within each through-hole 41a. Each spacer 18 has the same shape and is a cylindrical body through which the bolt 71 can be inserted. Each spacer 18 extends in the direction of the drive axis O1. As shown in FIG. 6, the length of each spacer 18 in the direction of the drive axis O1 is a first length L1. Each spacer 18 may also be made of resin.

[0067] As described above, the thickness of the driven end plate 41 is the second length L2. Therefore, when each spacer 18 is disposed in each through hole 41a, it protrudes from the through hole 41a toward the drive axis O1 by the difference between the first length L1 and the second length L2.

[0068] 1, the driven spiral 43 is integral with the driven end plate 41 and protrudes forward from the second front surface 411 of the driven end plate 41, i.e., toward the driving end plate 31, parallel to the drive axis O2 and the driven axis O2. The driven spiral 43 has a spiral center located on the central side of the driven end plate 41 and protrudes from the spiral center toward the outer periphery. As shown in FIGS. 6 and 7, the driven spiral 43 has a front end surface 430.

[0069] Here, the length by which the driven spiral 43 protrudes forward from the second front surface 411 of the driven end plate 41 is equal to the length by which the drive spiral 33 protrudes rearward from the first rear surface 312 of the drive end plate 31. As a result, the length by which the drive peripheral wall 35 protrudes rearward from the first rear surface 312 of the drive end plate 31 is longer than the length by which the driven spiral 43 protrudes forward from the second front surface 411 of the driven end plate 41.

[0070] 5, the driven mechanism 20 is made up of six rotation-preventing pins 21 and six rings 22. Here, the number of rotation-preventing pins 21 and rings 22 can be appropriately designed as long as there are three or more of each.

[0071] In this compressor, when the drive scroll 30 and the driven scroll 40 are assembled, as described above, the cover body 37 is disposed in the drive scroll 30 so as to be spaced apart from the drive scroll 33 and the drive peripheral wall 35 in the direction of the drive axis O1. This forms a space 14 between the flange portion 35b of the drive peripheral wall 35 and the cover main body portion 37a of the cover body 37 (see FIG. 3).

[0072] In the driven scroll 40, a spacer 18 is placed in each through-hole 41a of the driven end plate 41. Then, as shown in Fig. 6, with the second front surface 411 of the driven end plate 41 and the driven scroll 43 facing the drive end plate 31, the portion of the driven end plate 41 that is on the outer periphery of the driven scroll 43, including the spacers 18 and the through-holes 41a, is inserted into the space 14. In this way, the driven end plate 41 is placed between the drive peripheral wall 35 and the cover body 37.

[0073] Here, the driven end plate 41 has a larger diameter than the drive circumferential wall 35, the cover body 37, and the rotor 11. Therefore, as shown in FIG. 7, when the driven end plate 41 is disposed between the drive circumferential wall 35 and the cover body 37, a portion of the driven end plate 41, i.e., the outer periphery of the driven end plate 41, protrudes radially beyond the drive circumferential wall 35 and the cover body 37. Furthermore, by disposing the driven end plate 41 between the drive circumferential wall 35 and the cover body 37 in this manner, the drive spiral 33 and the driven spiral 43 mesh with each other. As a result, the drive spiral 33 and the driven spiral 43 face each other to form the compression chamber 12. Furthermore, as shown in FIG. 5, each rotation-preventing pin 21 is inserted into each ring 22.

[0074] With the driven end plate 41 disposed between the drive peripheral wall 35 and the cover body 37, the bolt holes 35c of the drive peripheral wall 35, the bolt holes 37d of the cover body 37, and the spacers 18 are aligned along the drive axis O1. Then, as shown in FIGS. 5 and 6 , bolts 71 are inserted through the bolt holes 37d, the spacers 18, and the bolt holes 35c from the rear end surface 372 of the cover body 37, and the cover body 37 is fixed to the drive peripheral wall 35 along the drive axis O1 by the bolts 71. By fixing the cover body 37 to the drive peripheral wall 35 with the bolts 71 in this manner, the first suction port 37c of the cover body 37 and the second suction port 41c of the driven end plate 41 are communicated along the drive axis O1. The first suction port 37c and the second suction port 41c are communicated with the compression chamber 12.

[0075] In this way, the drive scroll 30 and the driven scroll 40 are assembled together with the driven end plate 41 disposed between the drive peripheral wall 35 and the cover body 37, whereby the drive scroll 30 and the driven scroll 40 form a scroll compression section 100. Furthermore, within each through-hole 41a, the driven end plate 41 moves relative to each spacer 18 through which the bolt 71 is inserted, thereby allowing the driven scroll 40 to rotate around the driven axis O2 with respect to the drive scroll 30.

[0076] 6, the length of each spacer 18 in the direction of the drive axis O1 is a first length L1, and therefore, by disposing the driven end plate 41 between the drive peripheral wall 35 and the cover body 37, the front end of each spacer 18 abuts against the first opposing surface 351 of the drive peripheral wall 35 and the rear end abuts against the second opposing surface 371 of the cover body 37. As a result, the distance between the first opposing surface 351 and the second opposing surface 371 in the direction of the drive axis O1, i.e., the width of the space portion 14 in the direction of the drive axis O1, is uniformly defined as the first length L1.

[0077] On the other hand, the thickness of the driven end plate 41 is a second length L2 that is shorter than the first length L1. Therefore, by assembling the drive scroll 30 and the driven scroll 40, a first gap S1 based on the difference between the first length L1 and the second length L2 is formed between the first opposing surface 351 and the second opposing surface 371 and the driven end plate 41 in the space portion 14.

[0078] More specifically, the first gap S1 is the sum of a gap S11 between the first opposing surface 351 and the second front surface 411 of the driven end plate 41 in the direction of the drive axis O1, and a gap S12 between the second opposing surface 371 and the second rear surface 412 of the driven end plate 41 in the direction of the drive axis O1. Therefore, when the driven end plate 41 is positioned at the center of the space 14 in the direction of the drive axis O1, the gaps S11 and S12 are equal in size and are both half the size of the first gap S1. In contrast, for example, when the driven end plate 41 approaches the first opposing surface 351 in the space 14, the gap S11 becomes smaller and the gap S12 becomes larger accordingly. When the first opposing surface 351 and the second front surface 411 abut, the gap S11 becomes zero, while the gap S12 becomes maximum, and the first gap S1 is constituted solely by the gap S12. Conversely, when the second opposing surface 371 and the second rear surface 412 come into contact with each other, the gap S12 becomes zero while the gap S11 becomes maximum, so that the first gap S1 is formed only by the gap S11.

[0079] Furthermore, by assembling the drive scroll 30 and the driven scroll 40, a second gap S2 is formed in the direction of the drive axis O1 between the first rear surface 312 of the drive end plate 31 and the front end surface 430 of the driven scroll 43. Similarly, a third gap S3 is formed in the direction of the drive axis O1 between the second front surface 411 of the driven end plate 41 and the rear end surface 330 of the drive scroll 33.

[0080] Here, the length by which the drive scroll 33 extends rearward from the first rear surface 312 of the drive end plate 31 and the length by which the driven scroll 43 extends forward from the second front surface 411 of the driven end plate 41 are both equal. These lengths are shorter than the length by which the drive circumferential wall 35 extends rearward from the first rear surface 312 of the drive end plate 31. Therefore, in this compressor, the size of the second gap S2 and the size of the third gap S3 are equal, and the second gap S2 and the third gap S3 are larger than the first gap S1. Note that in Figure 6 and other figures, the first to third gaps S1 to S3 are exaggerated for ease of explanation.

[0081] After the drive scroll 30 and the driven scroll 40 are assembled in this manner, the first plain bearing 51 of the drive scroll 30 is inserted into the insertion hole 37e of the cover body 37, as shown in FIG. 1 . As a result, the boss portion 37b, and therefore the cover body 37, are rotatably supported by the first support portion 64 via the first plain bearing 51. Furthermore, in the drive scroll 30, the boss portion 31b of the drive end plate 31 is inserted into the second plain bearing 52. As a result, the drive end plate 31 is rotatably supported by the second support portion 66 via the second plain bearing 52. In this manner, the drive scroll 30 is disposed in the suction chamber 65 and is rotatably supported by the housing 6 by both the first support portion 64 and the second support portion 66 around the drive axis O1.

[0082] Furthermore, by inserting the boss portion 31b into the second plain bearing 52 in this way, the discharge chamber 38 and the discharge communication chamber 13 are communicated with each other. As a result, the discharge chamber 38 is communicated with the outside of the housing 6 through the discharge communication chamber 13 and the discharge communication port 69.

[0083] On the other hand, in the driven scroll 40, the driven pin 55 is inserted into the pin hole 4 of the first support portion 64. As a result, the driven scroll 40 is disposed in the suction chamber 65 and is supported by the driven shaft portion 16 to the first support portion 64 so as to be rotatable about the driven axis O2. In other words, unlike the driving scroll 30, the driven scroll 40 is supported by the housing 6 only by the first support portion 64 so as to be rotatable about the driven axis O2.

[0084] In the compressor configured as described above, low-temperature, low-pressure refrigerant gas that has passed through the evaporator is drawn into the suction chamber 65 through the suction communication port 68. When the electric motor 10 is operated and the rotor 11 rotates, the drive scroll 30 is driven to rotate about the drive axis O1 within the suction chamber 65. In other words, the drive scroll 30 and the rotor 11 are driven to rotate together. At this time, in the driven mechanism 20, each rotation-preventing pin 21 slides against the inner circumferential surface of each ring 22, causing the rings 22 to rotate relatively about the center of the rotation-preventing pin 21. In this way, the driven mechanism 20 transmits the torque of the drive scroll 30 to the driven scroll 40.

[0085] As a result, the driven scroll 40 is rotated around the driven axis O2 by the drive scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 restricts the rotation of the driven scroll 40. As a result, the driven scroll 40 revolves around the driven axis O2 relatively to the drive scroll 30.

[0086] Here, with the driven end plate 41 disposed between the drive peripheral wall 35 and the cover body 37, a first gap S1 is formed between the first opposing surface 351 and the second opposing surface 371 and the driven end plate 41. Therefore, in this compressor, when the driven scroll 40 revolves around the driven axis O2, interference between the drive peripheral wall 35 and the cover body 37 and the driven end plate 41 is prevented.

[0087] In this way, the driving scroll 30 and the driven scroll 40 change the volume of the compression chamber 12. As a result, refrigerant gas in the suction chamber 65 is drawn into the compression chamber 12 through the first and second suction ports 37c and 41c. The refrigerant gas drawn into the compression chamber 12 flows from the outer periphery of the driving scroll 33 and the driven scroll 43 toward the center of the scroll, and is compressed within the compression chamber 12. The refrigerant gas compressed to discharge pressure in the compression chamber 12 is discharged from the discharge port 32 into the discharge chamber 38, and further discharged through the discharge communication chamber 13 and the discharge communication port 69 to the condenser. In this way, air conditioning is performed by the vehicle air conditioner.

[0088] In this compressor, a tilting moment that tends to tilt the driven scroll 40 relative to the drive axis O1 and the driven axis O2 is inevitably applied to the driven scroll 40 during operation due to a reaction force from the refrigerant gas compressed in the compression chamber 12. In this compressor, even if the driven scroll 40 is tilted by the tilting moment, the front end portion of the driven scroll 43, including the front end surface 430 of the driven scroll 43, is prevented from contacting the first rear surface 312 of the drive end plate 31. Furthermore, in this compressor, the rear end portion of the drive scroll 33, including the rear end surface 330 of the drive scroll 33, is also prevented from contacting the second front surface 411 of the driven end plate 41. This effect will be described below in comparison with a compressor of a comparative example.

[0089] 8, in the compressor of the comparative example, similar to the compressor of the embodiment, the driving scroll 30 and the driven scroll 40 are assembled with the driven end plate 41 disposed between the driving peripheral wall 35 and the cover body 37. Here, in the compressor of the comparative example, the driving scroll 30 has the driving scroll 34, and the driven scroll 40 has the driven scroll 44.

[0090] As a result, in the compressor of the comparative example, by assembling the drive scroll 30 and the driven scroll 40, a fourth gap S4 is formed in the direction of the drive axis O1 between the first rear surface 312 of the drive end plate 31 and the front end surface 440 of the driven scroll 44. In addition, a fifth gap S5 is formed in the direction of the drive axis O1 between the second front surface 411 of the driven end plate 41 and the rear end surface 340 of the drive scroll 34.

[0091] Here, the drive scroll 34 and the driven scroll 44 extend further in the direction of the drive axis O1 than the drive scroll 33 and the driven scroll 43 in the compressor of the embodiment. In other words, the drive scroll 34 extends rearward from the first rear surface 312 further than the drive scroll 33 of the compressor of the embodiment, and the driven scroll 44 extends forward from the second front surface 411 further than the driven scroll 43 of the compressor of the embodiment. The drive scroll 34 and the driven scroll 44 extend further rearward from the first rear surface 312 of the drive end plate 31.

[0092] Therefore, the fourth gap S4 and the fifth gap S5 in the compressor of the comparative example are smaller than the second gap S2 and the third gap S3 in the compressor of the embodiment, respectively. The fourth gap S4 and the fifth gap S5 in the compressor of the comparative example are equal in size. The fourth gap S4 and the fifth gap S5 are also smaller than the first gap S1 (the sum of the gap S11 between the first opposing surface 351 and the second front surface 411 and the gap S12 between the second opposing surface 371 and the second rear surface 412). Other configurations of the compressor of the comparative example are similar to those of the compressor of the first embodiment, and the same components are denoted by the same reference numerals, and detailed description of the configurations will be omitted. For ease of explanation, the fourth gap 43, the fifth gap S5, etc. are exaggerated in FIG. 8 .

[0093] 9, when the driven scroll 40 tilts due to the tilting moment, for example, in the radial direction of the driven end plate 41, the first opposing surface 351 and the second front surface 411 approach each other on one side of the driven axis O2, and the second opposing surface 371 and the second rear surface 412 approach each other on the other side of the driven axis O2. Furthermore, as a result of the driven scroll 40 tilting, the front end portion of the driven scroll 44, including the front end surface 440, approaches the first rear surface 312, and the second front surface 411 approaches the rear end portion of the driven scroll 34, including the rear end surface 340 of the driven scroll 34.

[0094] As described above, the drive scroll 34 and the driven scroll 44 extend longer in the direction of the drive axis O1 than the drive scroll 33 and the driven scroll 43 in the compressor of the embodiment, and the fourth gap S4 and the fifth gap S5 are smaller than the second gap S2 and the third gap S3 in the compressor of the embodiment, respectively. Therefore, in the compressor of the comparative example, in the radial direction of the driven end plate 41, the first opposing surface 351 and the second front surface 411 abut on one side of the driven axis O2, and before the second opposing surface 371 and the second rear surface 412 abut on the other side of the driven axis O2, the rear end portion of the drive scroll 34 contacts the second front surface 411 and the front end portion of the driven scroll 44 contacts the first rear surface 312.

[0095] As a result, in the compressor of the comparative example, the driven scroll 40, which tilts due to the tilting moment, is supported by the drive scroll 34 in contact with the driven end plate 41 and the drive scroll 44 in contact with the drive end plate 31, and tilt of the driven scroll 40 due to the tilting moment is restricted. That is, in the compressor of the comparative example, the tilt of the driven scroll 40 is restricted by the drive scroll 34 and the driven scroll 44, so that the drive peripheral wall 35 and the driven end plate 41 do not come into contact with each other through the first opposing surface 351 and the second front surface 411, and the cover body 37 does not come into contact with the driven end plate 41 through the second opposing surface 371 and the second rear surface 412. As a result, in the compressor of the comparative example, the load on the drive scroll 34 and the driven scroll 44 increases, making the drive scroll 34 and the driven scroll 44 more susceptible to damage.

[0096] In contrast, in the compressor of the embodiment, a second gap S2 between the front end face 430 of the driven scroll 43 and the first rear face 312 of the drive end plate 31 and a third gap S3 between the rear end face 330 of the drive scroll 33 and the second front face of the driven end plate 41 are set so that the driven scroll 43 and the drive end plate 31, and the drive scroll 31 and the driven end plate 41 are not in contact with each other when the driven end plate 41 and the drive peripheral wall 35 are in contact with each other. Specifically, in the compressor of the embodiment, the length by which the drive peripheral wall 35 extends rearward from the drive end plate 31 is longer than the lengths of the drive scroll 33 and the driven scroll 43, and the second gap S2 and the third gap S3 are larger than the first gap S1.

[0097] 7, in the compressor of the embodiment, the tilting moment causes the driven scroll 40 to tilt relative to the drive axis O1 and the driven axis O2, and the first opposing surface 351 and the second front surface 411 abut on one side of the driven axis O2 in the radial direction of the driven end plate 41 within the space 14, and the second opposing surface 371 and the second rear surface 412 abut on the other side of the driven axis O2 in the radial direction of the driven end plate 41, thereby restricting the tilting of the driven scroll 40 due to the tilting moment. At this time, the tilt of the driven scroll 40 causes the front end portion of the driven scroll 43 to approach the first rear surface 312 of the drive end plate 31, but the driven scroll 43 and the first rear surface 312 do not come into contact with each other. Similarly, although the rear end portion of the driving scroll 33 approaches the second front surface 411 of the driven end plate 41 due to the tilt of the driven scroll 40, there is no contact between the driving end plate 33 and the second front surface 411. After the tilt of the driven scroll 40 due to the tilting moment is restricted, the tilt of the driven scroll 40 does not increase, so the front end portion of the driven scroll 43 does not approach any further to the first rear surface 312, and the rear end portion of the driving scroll 33 does not approach any further to the second front surface 411.

[0098] Thus, in the compressor of the embodiment, unlike the compressor of the comparative example, even if the tilting moment causes the driven scroll 40 to tilt toward the drive axis O1 and the driven axis O2, the driven scroll 43 and the first end plate 31 do not come into contact, and the drive scroll 33 and the second end plate 41 do not come into contact.

[0099] Thus, in the compressor of the embodiment, the drive peripheral wall 35 and the cover body 37 abut against the driven end plate 41 in the space 14, so that the tilting moment acting on the driven scroll 40 can be suitably supported by the drive peripheral wall 35, the cover body 37, and the driven end plate 41. On the other hand, in the compressor of the embodiment, the driven scroll 40, which tilts due to the tilting moment, does not need to be supported by the drive scroll 33 and the driven scroll 34, so no large load acts on the drive scroll 33 and the driven scroll 34. As a result, in the compressor of the embodiment, damage to the drive scroll 33 and the driven scroll 34 can be prevented.

[0100] Furthermore, the driven end plate 41 is disk-shaped and does not protrude toward the drive axis O1 like the drive scroll 33 and the driven scroll 43. Therefore, the driven end plate 41 has sufficient rigidity to support the driven scroll 40, which tilts due to the tilting moment. Therefore, in the compressor of the embodiment, damage to the driven end plate 41 can also be prevented.

[0101] Therefore, the compressor of the embodiment has excellent durability.

[0102] In particular, in this compressor, by fixing the cover body 37 to the drive peripheral wall 35 with the bolts 71 while the driven end plate 41 is disposed between the drive peripheral wall 35 and the cover body 37, it is possible to easily position the driven scroll 40 relative to the drive scroll 30 in the direction of the drive axis O1. Therefore, this compressor is also easy to manufacture.

[0103] Furthermore, in this compressor, the spacers 18 disposed in the through holes 41a make it possible to easily provide a gap S11 between the first opposing surface 351 of the driving peripheral wall 35 and the second front surface 411 of the driven end plate 41, and also to easily provide a gap S12 between the second opposing surface 371 of the cover body 37 and the second rear surface 412 of the driven end plate 41. This allows the driven end plate 41 to rotate suitably between the driving peripheral wall 35 and the cover body 37 without interfering with the driving peripheral wall 35 or the cover body 37.

[0104] Furthermore, in this compressor, the driven end plate 41 is formed with a diameter larger than the drive peripheral wall 35, the cover body 37, and the rotor 11. This makes it possible to minimize the load of the tilting moment acting on the driven end plate 41 when the driven end plate 41 abuts against the first opposing surface 351 of the drive peripheral wall 35 and the second opposing surface 371 of the cover body 37 in the space 14. In this respect, too, damage to the driven end plate 41 can be prevented in this compressor.

[0105] Furthermore, by increasing the diameter of the driven end plate 41, when the driven end plate 41 is disposed between the drive peripheral wall 35 and the cover body 37 in this compressor, the outer periphery of the driven end plate 41 protrudes radially beyond the drive peripheral wall 35 and the cover body 37. Therefore, in this compressor, the driven end plate 41 disposed between the drive peripheral wall 35 and the cover body 37 can be easily held from the outside of the drive peripheral wall 35 and the cover body 37. This makes it easier to position the driven scroll 40 relative to the drive scroll 30 in the direction of the drive axis O1, and also makes it possible to easily fix the cover body 37 to the drive peripheral wall 35 with each bolt 71.

[0106] Although the present invention has been described above with reference to the embodiments, it goes without saying that the present invention is not limited to the above embodiments and can be modified and applied as appropriate within the scope of the invention.

[0107] For example, instead of the bolts 71, the cover body 37 may be fixed to the driving peripheral wall 35 by means of press-fit pins or the like that are press-fitted into the driving peripheral wall 35 and the cover body 37, respectively.

[0108] Furthermore, in the compressor of the embodiment, a spacer 18 is provided in each insertion hole 41. However, this is not limiting, and a protrusion or the like that passes through each through-hole 41 a from the first opposing surface 351 of the drive peripheral wall 35 and abuts against the second opposing surface 371 may be provided to ensure the gap S11 between the first opposing surface 351 and the second front surface 411 and also ensure the gap S12 between the second opposing surface 371 and the second rear surface 412.

[0109] In the compressor of the embodiment, the driven shaft portion 16 is formed by the bush 53 and the driven pin 55. However, this is not limiting, and the driven shaft portion 16 may be formed by only the bush 53 by forming a shaft body that is journaled by the first support portion 64 integrally with the bush 53.

[0110] In the compressor of the embodiment, the drive scroll 30 and the rotor 11 may be connected to each other by a drive shaft so that power can be transmitted between them, so that the drive scroll 30 and the rotor 11 are spaced apart from each other in the direction of the drive axis O1.

[0111] In the compressor of the embodiment, the driven mechanism 20 is composed of the rotation-preventing pin 21 and the ring 22. However, the driven mechanism 20 is not limited to this, and may be composed of a pin-ring-pin system in which two pins are in sliding contact with the inner peripheral surface of one free ring, a pin-pin system in which the outer peripheral surfaces of two pins are in sliding contact with each other, a system using an Oldham coupling, or the like. [Industrial Applicability]

[0112] The present invention can be used in vehicle air conditioning systems and the like. [Explanation of symbols]

[0113] 6. Housing 10...Electric motor (drive mechanism) 11...Rotor 12...Compression chamber 18...Spacer 30...Drive scroll 31...Drive end plate 33...Driven spiral 35...Drive wall 37...Cover body 40...Driven scroll 41…Driven end plate 43...Driven spiral body O1...Drive shaft center O2…driven shaft center S2: Second gap (gap) S3...Third gap (gap)

Claims

1. a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism; the drive scroll is driven to rotate about a drive axis by the drive mechanism; The driven scroll is rotated around a driven axis by the driving scroll and the driven mechanism while being eccentric with respect to the driving scroll, The drive scroll has a drive end plate extending in a direction intersecting the drive axis, a drive circumferential wall protruding in a cylindrical shape from the drive end plate toward the driven scroll, and a drive scroll body protruding in a spiral shape from the drive end plate toward the driven scroll within the drive circumferential wall, The driven scroll has a driven end plate extending in a direction intersecting the driven axis, and a driven scroll protruding in a spiral shape from the driven end plate toward the drive scroll, The drive scroll and the driven scroll form a compression chamber by opposing each other, and the volume of the compression chamber is changed by the rotation driving and the rotation driven, The driving scroll has a cover body fixed to the driving peripheral wall, the driven end plate is disposed between the driving peripheral wall and the cover body in a rotationally driven state; a sum of a gap between the driving peripheral wall and the driven end plate in the drive axial direction and a gap between the driven end plate and the cover body in the drive axial direction is a first gap, a gap between the drive end plate and the driven scroll in the drive shaft direction is a second gap; a gap between the driven end plate and the drive scroll in the drive axial direction is a third gap; the driven end plate and the driving peripheral wall are capable of abutting against each other in the drive axial direction, and the second gap and the third gap are larger than the first gap so that the driven volute and the driving end plate, and the driving volute and the driven end plate are not in contact with each other in a state in which the driven end plate and the driving peripheral wall are in contact with each other in the drive axial direction.

2. A plurality of through holes are formed in the outer periphery of the driven end plate, 2. The double-rotary scroll compressor according to claim 1, wherein a spacer is provided in each of the through holes between the driving peripheral wall and the cover body to position the driven end plate in a state in which it can be rotated.

3. the drive mechanism has a cylindrical rotor that surrounds the drive circumferential wall from an outer periphery and is fixed to the drive circumferential wall, 3. A double-rotating scroll compressor according to claim 1, wherein the driven end plate has a diameter larger than that of the rotor.

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