JP2024058035A - Double-rotating scroll compressor - Google Patents

Abstract

To provide a double rotary scroll type compressor which can inhibit increase in the size of a bearing for supporting a scroll provided with a discharge valve in a manner that allows the scroll to rotate relative to a housing, inhibit deterioration of efficiency, and suppress noise and vibration.SOLUTION: A bearing cover body 40B having a cover part 47 and a boss part 48 is coupled to a front surface 411 of a driven end plate 41. A recessed part 50 forming a discharge valve chamber 44 is recessed on the front surface 411, and a discharge valve 57 is housed in the discharge valve chamber 44. A part of the discharge valve chamber 44 and a part of the discharge valve 57 are covered with the cover part 47. An internal space 48A of the boss part 48 leads to a discharge part 65C and the discharge valve chamber 44. An outer peripheral surface of the boss part 48 is provided with a bearing 72 which supports a driven scroll 40 in a manner that allows the driven scroll 40 to rotate relative to the housing 60.SELECTED DRAWING: Figure 1

Description

The present invention relates to a double-rotating scroll compressor.

Patent Document 1 discloses a conventional double-rotating scroll compressor. This double-rotating scroll compressor includes a drive mechanism, a drive scroll, a driven mechanism, a driven scroll, and a housing.

The housing has a suction chamber into which fluid is drawn in from the outside, and a discharge chamber from which the fluid is discharged to the outside.

The drive scroll is rotated around the drive axis by the drive mechanism. The driven scroll is rotated around the driven axis by the drive scroll and the driven mechanism while being eccentric with respect to the drive scroll.

The drive scroll has a drive end plate and a drive scroll. The drive end plate extends across the drive axis. The drive scroll protrudes from the drive end plate toward the driven scroll and forms a spiral shape.

The driven scroll has a driven end plate and a driven scroll. The driven end plate extends across the driven axis. The driven scroll protrudes from the driven end plate toward the driving scroll and forms a scroll shape.

The driving scroll and the driven scroll face each other to form a compression chamber, and the volume of the compression chamber is changed by the rotational drive and the rotational driven, and the fluid sucked in from the suction chamber is compressed in response to the change in volume and discharged into the discharge chamber.

JP 2002-310073 A

In a double-rotating scroll compressor, a pair of bearings are arranged between the drive scroll and the driven scroll, and the drive scroll is rotatably supported relative to the housing via the drive-side bearing, while the driven scroll is rotatably supported relative to the housing via the driven-side bearing.

However, in the above-mentioned conventional double-rotating scroll compressor, a cylindrical boss is integrally formed on the outer end face of the driven end plate opposite the compression chamber, and a driven-side bearing is attached to the outer circumferential surface of this boss. A discharge port through which fluid is discharged from the compression chamber is provided in the driven end plate, and a discharge valve that opens and closes the discharge port is disposed in the boss.

In this configuration, in the conventional double-rotating scroll compressor, the discharge valve is disposed inside the boss, but the inner diameter of the boss is longer than the length of the longest part of the discharge valve, so the boss and the bearing attached to the boss are inevitably enlarged. When the bearing is enlarged, the sliding distance per rotation increases, which increases the power required, raising concerns about efficiency, noise, and vibration.

The present invention was made in consideration of the above-mentioned conventional situation, and the problem to be solved is to provide a double-rotating scroll compressor that can suppress the decrease in efficiency, noise, and vibration by preventing the bearings for rotatably supporting the scroll on the side where the discharge valve is provided relative to the housing from becoming too large.

The double-rotating scroll compressor of the present invention comprises a housing having a suction chamber into which a fluid is drawn from the outside and a discharge chamber from which the fluid is discharged to the outside;
A first scroll disposed within the housing;
a second scroll provided in the housing, facing the first scroll, and defining a compression chamber for compressing a fluid between the first scroll and the second scroll,
the first scroll has a first end plate and a first scroll body that is integral with the first end plate and protrudes in a spiral shape toward the second scroll,
The second scroll has a second end plate and a second scroll body that is integral with the second end plate and protrudes in a spiral shape toward the first scroll,
the first scroll has a bearing cover body fixed to an end surface of the first end plate opposite to the compression chamber,
a discharge valve chamber that constitutes a part of the discharge chamber is formed between the first end plate and the bearing cover body,
a discharge port that communicates between the compression chamber and the discharge valve chamber is formed in the first end plate,
A discharge valve that opens and closes the discharge port is provided in the discharge valve chamber,
the bearing cover body includes a cover portion which covers a part of the discharge valve chamber and a part of the discharge valve, and a boss portion which extends cylindrically from an inner circumferential side of the cover portion toward an opposite side to the compression chamber, the boss portion having an internal space which communicates with the discharge valve chamber,
A bearing for rotatably supporting the first scroll is provided on the outer circumferential surface of the boss portion.

In the double-rotating scroll compressor of the present invention, a bearing cover body is fixed to the end face of the first end plate of the first scroll opposite the compression chamber. A discharge valve chamber that constitutes part of the discharge chamber is formed between the first end plate and the bearing cover body, and a discharge port that connects the compression chamber and the discharge valve chamber is formed in the first end plate, and a discharge valve that opens and closes the discharge port is provided in the discharge valve chamber.

The bearing cover body has a cover portion and a boss portion. The cover portion covers a part of the discharge valve chamber and a part of the discharge valve. The internal space of the boss portion is connected to the discharge valve chamber. Therefore, the fluid compressed in the compression chamber is discharged through the discharge port into the discharge chamber, which includes the discharge valve chamber and the internal space of the boss portion. A bearing is provided on the outer peripheral surface of the boss portion.

In the conventional compressor described above, in which the discharge valve is housed in the internal space of the boss, the internal space of the boss is necessarily larger than the discharge valve. In this regard, in the double-rotating scroll compressor of the present invention, in which a discharge valve chamber that houses the discharge valve is provided between the bearing cover body having the boss and the first end plate, the internal space of the boss can be set regardless of the size of the discharge valve.

For this reason, in this double-rotary scroll compressor, the boss portion can be made smaller than in the conventional compressor described above, in which the internal space of the boss portion is necessarily larger than the discharge valve. As a result, the bearings provided on the outer circumferential surface of the boss portion can also be made smaller.

The double-rotating scroll compressor of the present invention therefore prevents the bearings used to rotatably support the scroll on the side where the discharge valve is provided relative to the housing from becoming too large, thereby minimizing efficiency decline, noise, and vibration.

The discharge valve is preferably a discharge reed valve having a tip valve portion that opens and closes the discharge port and a base end fixing portion that fixes the discharge valve to the first end plate. The base end fixing portion is preferably covered by a cover portion.

In this case, even if the bolt for fixing the base end fixing part becomes loose, the cover part can prevent the bolt from falling out.

It is preferable that the tip valve portion is located closer to the center of the boss portion than the base end fixing portion.

In this case, since the tip valve portion is located near the center of the boss portion, the discharge port that is opened and closed by the tip valve portion is also set near the center of the boss portion. The center of the boss portion where the bearing of the first scroll is provided is also the center of rotation of the first scroll. This allows the fluid that is more compressed in the compression chamber to be discharged from the discharge port, which is advantageous in improving compression efficiency.

Of the first and second end plates, at least the first end plate has a bulging portion that bulges toward the opposing first or second end plate, a non-bulging portion located on the outer periphery of the bulging portion, and an end plate side step portion that connects to the bulging portion and the non-bulging portion, and the first or second spiral body that protrudes from the opposing first or second end plate preferably has a spiral main body portion, a short spiral portion that protrudes shorter than the spiral main body portion to avoid interference with the bulging portion, and a spiral body side step portion that connects to the spiral main body portion and the short spiral portion. And, the discharge valve chamber is preferably formed by a recess that recesses from the end face of the first end plate toward the compression chamber in the region where the bulging portion is provided.

In this case, a discharge valve chamber is formed in the region of the first end plate where the bulge is provided. This first end plate has a non-bulge portion on the outer periphery of the bulge portion, and only a portion of the first end plate is made thick. This makes it possible to prevent the first end plate from becoming heavier than when the entire first end plate is made thick to provide a discharge valve chamber. In addition, the volume of the compression chamber partitioned between the first end plate and the second end plate is reduced by the amount that the distance between the first end plate and the second end plate is shortened by the formation of the bulge portion compared to the distance between the first end plate and the second end plate where no bulge is formed, and the compression efficiency can be improved.

It is preferable that an oil return passage is provided that opens to the inner peripheral surface of the discharge valve chamber, extends from the inner peripheral surface of the discharge valve chamber toward the outer peripheral side, and connects the discharge valve chamber to the suction chamber or the compression chamber.

In this case, the discharge valve chamber rotates while the compressor is in operation, and centrifugal force acts on the fluid discharged from the discharge port into the discharge valve chamber. This separates the oil from the fluid by centrifugal force. The oil separated from the fluid is then directed toward the outer periphery by the action of centrifugal force in the discharge valve chamber. In addition, because part of the discharge valve chamber is covered by a cover, the cover blocks most of the oil flowing out from the discharge valve chamber toward the internal space of the boss.

As a result, the oil in the discharge valve chamber is easily introduced into the oil return passage that opens to the inner peripheral surface of the discharge valve chamber. The oil introduced into the oil return passage is subjected to centrifugal force and flows to the outer peripheral side and out into the suction chamber. The oil that flows out into the suction chamber can provide oil lubrication and oil sealing effects in areas where lubrication and sealing properties are required.

The double-rotating scroll compressor of the present invention prevents the bearings for rotatably supporting the scroll on the side where the discharge valve is provided relative to the housing from becoming too large, thereby reducing efficiency losses, noise, and vibration.

FIG. 1 is a cross-sectional view of a double-rotating scroll compressor according to a first embodiment of the present invention. FIG. 2 is an enlarged partial cross-sectional view of a main portion of the double-rotating scroll compressor of the first embodiment. FIG. 3 is a partial cross-sectional view showing a second boss of a bearing cover body in the double rotary scroll compressor of the first embodiment. FIG. 4 is an exploded perspective view showing a driven scroll body, a gasket, and a bearing cover body of the double-rotating scroll compressor of the first embodiment, as viewed from the front side. FIG. 5 is a perspective view of the driven scroll body seen from the front in the double-rotating scroll compressor of the first embodiment. FIG. 6 is a partial front view of the discharge valve chamber in the driven scroll body of the double-rotating scroll compressor of the first embodiment, as viewed from the front. FIG. 7 is an explanatory diagram showing the shapes of a driving end plate and a driving scroll of the double rotary scroll compressor according to the first embodiment, as viewed from the front of the driving scroll. FIG. 8 is an explanatory diagram showing the shapes of the driven end plate and the driven scroll body of the double-rotating scroll compressor of the first embodiment, as viewed from the front of the driven scroll. FIG. 9 is an enlarged partial cross-sectional view of a main portion of a double-rotating scroll compressor according to a second embodiment of the present invention. FIG. 10 is a partial front view of a discharge valve chamber in a driven scroll body of a double rotary scroll compressor according to a second embodiment.

Below, examples 1 and 2 of the present invention will be described with reference to the drawings.

Example 1
As shown in Fig. 1, the double-rotating scroll compressor (hereinafter simply referred to as the compressor) of the first embodiment includes a housing 60, an electric motor 10, an inverter circuit 70, a driving scroll 30, a driven scroll 40, and a driven mechanism 20. This compressor is mounted on a vehicle (not shown) and constitutes an air conditioner for the vehicle.

In this embodiment, the front-to-rear direction of the compressor is defined by the solid arrow shown in FIG. 1. Note that the front-to-rear direction is an example for ease of explanation, and the compressor can change its own position as appropriate depending on the vehicle in which it is installed.

In this embodiment, the driven scroll 40, the driven end plate 41 described later, and the driven spiral body 43 described later correspond to the "first scroll," "first end plate," and "first spiral body" in the present invention, respectively. Also, the driving scroll 30, the driving end plate 31 described later, and the driving spiral body 33 described later correspond to the "second scroll," "second end plate," and "second spiral body" in the present invention, respectively.

The housing 60 is composed of a housing body 61, a cover 65, and an inverter case 67. The housing body 61 is a bottomed tubular member having a first outer peripheral wall 62 and a first bottom wall 63. The first outer peripheral wall 62 is cylindrical with the drive axis R1 as its center. The drive axis R1 is parallel to the front-rear direction. The first outer peripheral wall 62 also has an inner peripheral surface 62B. The first bottom wall 63 is located at the rear end of the housing body 61. The first bottom wall 63 extends in a substantially circular flat plate shape perpendicular to the drive axis R1.

The outer peripheral edge of the first bottom wall 63 is connected to the rear end of the first outer peripheral wall 62. A cylindrical support portion 64 that protrudes forward is provided at the center of the inner surface of the first bottom wall 63. The inner ring of the bearing 71 is fitted onto the support portion 64.

The cover 65 is disposed in front of the housing body 61. The cover 65 extends in a generally circular flat plate shape perpendicular to the drive axis R1. The cover 65 is fastened to the first outer peripheral wall 62 of the housing body 61 by bolts (not shown) with its outer peripheral edge abutting the front end of the first outer peripheral wall 62 of the housing body 61. As a result, the cover 65 blocks the housing body 61 from the front. In this way, a suction chamber 61A is formed within the housing body 61.

A cylindrical support 66 is provided in a protruding manner on the center of the inner surface of the cover 65, with the driven axis R2 as its center. The driven axis R2 extends parallel to the drive axis R1 while being eccentric with respect to the drive axis R1. In other words, the driven axis R2 is also parallel to the front-rear direction. The outer ring of a needle bearing 72 is fitted into the support 66. The needle bearing 72 is an example of a "bearing" in this invention.

The cover 65 is formed with an intake port 65A, a discharge port 65B, and a discharge section 65C. The intake port 65A is located between the outer periphery of the cover 65 and the shaft support section 66, and penetrates the cover 65 in a direction parallel to the drive shaft center R1. The intake port 65A communicates between the intake chamber 61A and the outside of the compressor. A pipe is connected to the intake port 65A. As a result, low-temperature, low-pressure refrigerant gas that has passed through the evaporator through the pipe is sucked into the intake chamber 61A. The refrigerant gas is an example of a "fluid" in this invention.

The discharge portion 65C is recessed in the rear surface 651 of the cover 65 at the center of the cover 65. The discharge communication port 65B penetrates the cover 65 in a direction parallel to the drive axis R1 so as to communicate with the discharge portion 65C. A pipe (not shown) is connected to the discharge communication port 65B, and the discharge communication port 65B allows the refrigerant gas discharged to the discharge portion 65C to flow toward the condenser. The pipes, evaporator, and condenser are not shown in the illustration.

The inverter case 67 is disposed at the rear of the housing body 61. The inverter case 67 is a bottomed tubular member having a second outer peripheral wall 68 and a second bottom wall 69. The second outer peripheral wall 68 is cylindrical with its center at the drive axis R1. The second bottom wall 69 is located at the rear end of the inverter case 67. The second bottom wall 69 extends in a substantially circular plate shape perpendicular to the drive axis R1. The outer peripheral edge of the second bottom wall 69 is connected to the rear end of the second outer peripheral wall 68.

The inverter case 67 is fastened to the first bottom wall 63 by bolts (not shown) with the front end of the second outer peripheral wall 68 abutting against the rear surface of the first bottom wall 63. This forms an inverter chamber 67A between the inverter case 67 and the first bottom wall 63. The inverter chamber 67A is adjacent to the suction chamber 61A behind the suction chamber 61A. The inverter chamber 67A is also partitioned from the suction chamber 61A by the first bottom wall 63. Although not shown, the inverter case 67 is provided with a connector portion.

The electric motor 10 is housed in the suction chamber 61A. As a result, the suction chamber 61A also serves as a motor chamber that houses the electric motor 10. The electric motor 10 is composed of a stator 17 and a rotor 11.

The stator 17 is cylindrical and centered on the drive shaft R1, and has windings 18. The stator 17 is fixed to the housing body 61, and thus to the housing 60, by fitting into the inner peripheral surface 62B of the first outer peripheral wall 62 of the housing body 61.

The rotor 11 is cylindrical around the drive shaft center R1 and is disposed within the stator 17. Although detailed illustration is omitted, the rotor 11 is composed of multiple permanent magnets corresponding to the stator 17 and laminated steel plates that secure each permanent magnet.

The inverter circuit 70 is housed in the inverter chamber 67A. The inverter circuit 70 is composed of a circuit board 70A and a switching element 70B provided on the circuit board 70A. The inverter circuit 70 is fixed to the rear surface of the first bottom wall 63 by bolts (not shown). The inverter circuit 70 is electrically connected to the vehicle battery (not shown) through a connector provided on the inverter case. The inverter circuit 70 is also electrically connected to the stator 17 through an airtight passage (not shown) provided in the first bottom wall 63. As a result, the inverter circuit 70 supplies power to the stator 17 while converting the direct current supplied from the battery into alternating current.

The drive scroll 30 has a drive end plate 31, a drive peripheral wall 32, and a drive scroll 33.

The driving end plate 31 extends in a generally circular plate shape perpendicular to the driving axis R1. The driving end plate 31 has a front surface 311 and a rear surface 312 located on the opposite side of the front surface 311. A first boss 34 is formed in the center of the rear surface 312, protruding toward the first bottom wall 63. The first boss 34 is cylindrical and centered on the driving axis R1.

The drive end plate 31 is formed with an intake port 35. The intake port 35 is located at a location that is more outer than the first boss 34. The intake port 35 is farther away from the drive axis R1 than the first boss 34 in the radial direction of the drive end plate 31. The intake port 35 is formed in a substantially elliptical shape that extends in the circumferential direction of the drive end plate 31. As shown in FIG. 1, the intake port 35 penetrates the drive end plate 31 in the direction of the drive axis R1, i.e., in the front-rear direction. The shape and number of the intake ports 35 can be designed as appropriate.

The driving peripheral wall 32 is formed integrally with the driving end plate 31 and extends forward from the outer periphery of the driving end plate 31, i.e., toward the driven scroll 40, parallel to the driving axis R1. As shown in FIG. 7, the driving peripheral wall 32 is substantially cylindrical with the driving axis R1 at its center. Four fixing holes 32A are formed at the front end of the driving peripheral wall 32. Note that FIG. 1 illustrates two of the four fixing holes 32A.

The drive spiral 33 is formed integrally with the drive end plate 31 and is located inside the drive peripheral wall 32. As shown in FIG. 1, the drive spiral 33 extends forward from the front surface 311 of the drive end plate 31 in parallel with the drive axis R1. As shown in FIG. 7, the drive spiral 33 is spiral-shaped around the drive axis R1. More specifically, when viewed from the front, the drive spiral 33 is formed in a right-handed spiral around the drive axis R1 from the center of the spiral.

As shown in FIG. 4, the driven scroll 40 is composed of a driven scroll body 40A, a bearing cover body 40B, and a gasket 40C. The driven scroll body 40A has a driven end plate 41 and a driven scroll body 43.

The driven end plate 41 extends in a generally circular plate shape perpendicular to the driven axis R2. The driven end plate 41 has a front surface 411 and a rear surface 412 located opposite the front surface 411. The front surface 411 corresponds to the "end surface of the first end plate opposite the compression chamber" in this invention.

The discharge valve chamber 44 is formed on the front surface 411 of the driven end plate 41. The discharge valve chamber 44 is made of a recess 50 formed by partially recessing the front surface 411 toward the compression chamber 55 described later, and is defined by a recess bottom surface 50A and a recess inner peripheral surface 50B. As shown in Figures 2 and 5, the recess 50 is made of a first recess 51, a second recess 52, and a third recess 53. The first recess 51, the second recess 52, and the third recess 53 are deeper in this order. That is, the first recess 51 is the shallowest, and the third recess 53 is the deepest.

2 and 6, the recess bottom surface 50A of the recess 50 has a first recess bottom surface 51A, a second recess bottom surface 52A, and a third recess bottom surface 53A. The recess inner peripheral surface 50B of the recess 50 has a first recess inner peripheral surface 51B, a second recess inner peripheral surface 52B, and a third recess inner peripheral surface 53B. The first recess 51 is defined by the first recess bottom surface 51A and the first recess inner peripheral surface 51B. The second recess 52 is defined by the second recess bottom surface 52A and the second recess inner peripheral surface 52B. The third recess 53 is defined by the third recess bottom surface 53A and the third recess inner peripheral surface 53B.

The inner peripheral surface 51B of the first recess is circular, and the first recess 51 has a circular outer shape centered on the driven axis R2. The outer shape of the third recess 53 roughly corresponds to the outer shape of the discharge valve mechanism 56, and the depth of the third recess 53 is slightly greater than the thickness of the discharge valve mechanism 56. In other words, the size of the third recess 53 is large enough to accommodate the discharge valve mechanism 56. Within the circular first recess 51, the third recess 53 is positioned offset to one side with respect to the driven axis R2, and the second recess 52 extends from the outer edge of the third recess 53 to the other side.

The driven end plate 41 is formed with a discharge port 45 that penetrates the driven end plate 41 in the front-rear direction. One end of the discharge port 45 opens into the compression chamber 55 (described later), and the other end of the discharge port 45 opens into the bottom surface 53A of the third recess, and the discharge port 45 communicates between the compression chamber 55 and the discharge valve chamber 44.

As shown in Figures 2 and 6, a discharge valve mechanism 56 is disposed in the discharge valve chamber 44. More specifically, the discharge valve mechanism 56 is disposed in the third recess 53 of the recesses 50 that form the discharge valve chamber 44. In Figure 6, the discharge valve mechanism 56 is indicated by a two-dot chain line.

The discharge valve mechanism 56 has a discharge reed valve 57, a retainer 58, and a fixing bolt 59. The discharge reed valve 57 is an example of the "discharge valve" in the present invention. The discharge reed valve 57 and the retainer 58 are fixed to the bottom surface 53A of the third recess by the fixing bolt 59. The discharge reed valve 57 can open and close the discharge port 45. In addition, the retainer 58 can adjust the opening degree of the discharge reed valve 57.

6, the discharge reed valve 57 has a tip valve portion 57A and a base end fixing portion 57B. The tip valve portion 57A opens and closes the discharge port 45 and is disposed near the driven axis R2. More specifically, in the front-rear direction, the driven axis R2 is located inside the outer edge of the tip valve portion 57A. The base end fixing portion 57B is fixed to the bottom surface 53A of the third recess by a fixing bolt 59. As shown in FIG. 2 and FIG. 6, the discharge port 45 is disposed near the driven axis R2, and the base end fixing portion 57B is disposed a predetermined distance away from the driven axis R2. That is, the tip valve portion 57A that opens and closes the discharge port 45 is disposed closer to the driven axis R2 than the base end fixing portion 57B. In other words, the tip valve portion 57A is disposed closer to the center of the second boss 48 described later than the base end fixing portion 57B.

As shown in Figures 2 and 6, the driven end plate 41 is provided with an oil return passage 54. The oil return passage 54 consists of a groove 541 recessed in the front surface 411 of the driven end plate 41 and a hole 542 penetrating the driven end plate 41 in the front-rear direction.

One end of the groove 541 on the inner circumferential side opens to the first recess inner circumferential surface 51B. The groove 541 extends linearly from one end on the inner circumferential side toward the outer circumferential side. The other end on the outer circumferential side of the groove 541 connects to the front end of the hole 542. The hole 542 extends linearly in the front-rear direction. The rear end of the hole 542, whose front end connects to the other end of the groove 541, opens to the rear surface 412 of the driven end plate 41. The opening position of this hole 542 is in the suction chamber 61A. More specifically, the hole 542 opens on the outer circumferential side of the driven scroll 43, just outside the confinement start portion of the compression chamber 55 described later. In this way, the oil return passage 54 communicates between the discharge valve chamber 44 and the suction chamber 61A. The first recess inner circumferential surface 51B is an example of the "inner circumferential surface of the discharge valve chamber" in the present invention, where the oil return passage 54 described later opens.

The driven scroll 43 is formed integrally with the driven end plate 41 and extends from the rear surface 412 of the driven end plate 41 rearward, i.e., toward the driving scroll 30, parallel to the driven axis R2. As shown in FIG. 8, the driven scroll 43 is spiral-shaped around the driven axis R2. More specifically, when viewed from the front, the driven scroll 43 is formed in a right-handed spiral around the driven axis R2 from the center of the spiral.

As shown in FIG. 1, the driven mechanism 20 is composed of four rotation prevention pins 21 and four rings 22. The number of rotation prevention pins 21 and rings 22 can be appropriately designed as long as there are three or more of each. Also, in FIG. 1, two of each rotation prevention pins 21 and two of each ring 22 are illustrated.

Each rotation prevention pin 21 is fixed by being inserted into each fixing hole 32A of the driving peripheral wall 32. As a result, each rotation prevention pin 21 is fixed to the driving peripheral wall 32 in a state where it protrudes forward from the driving peripheral wall 32.

Each ring 22 is provided on the driven end plate 41 side so as to face each rotation prevention pin 21. Each ring 22 is fitted into a circular bottomed hole recessed in the rear surface 412 of the driven end plate 41.

The gasket 40C is disk-shaped, and a communication hole 46 is provided in the center of the gasket 40C. The diameter of the communication hole 46 is the same as the inner diameter d of the second boss 48 described below. The gasket 40C is sandwiched between the front surface 411 of the driven end plate 41 and the rear surface 472 of the cover part 47 described below, sealing the gap between the two.

The bearing cover body 40B has a cover portion 47 and a second boss 48 formed integrally with the cover portion 47. The second boss 48 corresponds to the "boss portion" in the present invention.

The cover portion 47 extends in a substantially circular plate shape perpendicular to the driven axis R2. The cover portion 47 has a front surface 471 and a rear surface 472 located on the opposite side of the front surface 471. A through hole 47A is formed in the center of the cover portion 47. The second boss 48 protrudes forward from the inner peripheral edge of the cover portion 47, i.e., the center of the front surface 471 of the cover portion 47. The second boss 48 extends cylindrically in the driven axis R2 direction with the driven axis R2 as the center. The inner diameter d of the cylindrical internal space 48A of the second boss 48 and the outer diameter D of the second boss 48 are shorter than the length L of the longest part of the discharge reed valve 57 (see Figures 3 and 6). In addition, in a plan view seen from the front-rear direction, the outer edge of the internal space 48A of the second boss 48 is located inside the outer edge of the third recess 53, i.e., the inner peripheral surface 53B of the third recess. In this compressor, the discharge chamber is formed by the discharge valve chamber 44, the internal space 48A, and the discharge section 65C.

As shown in FIG. 4, the driven end plate 41 of the driven scroll body 40A, the gasket 40C, and the cover portion 47 of the bearing cover body 40B each have four bolt insertion holes 49 formed in the outer periphery. The driven scroll body 40A and the bearing cover body 40B are integrally joined together with bolts (not shown) inserted through each bolt insertion hole 49, with the gasket 40C sandwiched between them. The joining of the driven scroll body 40A and the bearing cover body 40B is performed after the discharge valve mechanism 56 is placed in the discharge valve chamber 44 and the discharge reed valve 57 and the retainer 58 are fixed to the bottom surface 53A of the third recess by the fixing bolts 59.

When the bearing cover body 40B is coupled to the driven scroll body 40A, most of the discharge valve chamber 44 and most of the discharge valve mechanism 56 are covered by the cover portion 47 of the bearing cover body 40B. More specifically, in the recess 50 that forms the discharge valve chamber 44, the entire first recess 51, the entire second recess 52, and a part of the third recess 53 are covered by the cover portion 47.

In this compressor, both the driving scroll 30 and the driven scroll 40 are disposed in the suction chamber 61A. The driving scroll 30 is integrated with the rotor 11 by fixing the driving peripheral wall 32 to the inner peripheral surface of the rotor 11. In the driving scroll 30, the outer ring of the bearing 71 is fitted inside the first boss 34. As a result, the driving scroll 30 is supported by the housing main body 61 so as to be rotatable around the drive axis R1. Here, in this compressor, the driving scroll 30 is supported by the housing main body 61, and thus the housing 60, in a so-called cantilevered state.

Meanwhile, the driven scroll 40 is disposed in front of the driving scroll 30 with the driven scroll 43 facing the driving scroll 30. As a result, the front surface 311 of the driving end plate 31 and the rear surface 412 of the driven end plate 41 face each other in the direction of the driving axis R1 and the direction of the driven axis R2. The driving scroll 30 and the driven scroll 40 mesh with the driving scroll 33 and the driven scroll 43 inside the driving peripheral wall 32, and each rotation prevention pin 21 enters each ring 22. In this way, the driving scroll 30 and the driven scroll 40 are assembled in the front-rear direction. The driving scroll 33 and the driven scroll 43 form a compression chamber 55 between them.

In the driven scroll 40, the inner ring of the needle bearing 72 is fitted onto the outer peripheral surface of the second boss 48. This allows the driven scroll 40 to be supported by the cover 65 so as to be rotatable around the driven axis R2. Here, in this compressor, the driven scroll 40 is also supported by the cover 65, and thus the housing 60, in a so-called cantilevered state.

By supporting the driven scroll 40 on the cover 65, the internal space 48A of the second boss 48 faces the discharge portion 65C in the front-rear direction. In addition, the discharge port 45 and the tip valve portion 57A of the discharge reed valve 57 are located near the driven axis R2.

As shown in FIG. 7, in this compressor, the driving end plate 31 of the driving scroll 30 has a driving side bulge 31A, a driving side non-bulge 31B, and a driving end plate side step 31C. The driving side bulge 31A, the driving side non-bulge 31B, and the driving end plate side step 31C correspond to the "bulge", "non-bulge", and "end plate side step" in the present invention, respectively. The driving scroll 33 of the driving scroll 30 has a driving scroll short portion 33A, a driving scroll main body portion 33B, and a driving scroll side step 33C. The driving scroll short portion 33A, the driving scroll main body portion 33B, and the driving scroll side step 33C correspond to the "volume short portion", "volume main body", and "volume side step" in the present invention, respectively.

Similarly, as shown in FIG. 8, the driven end plate 41 of the driven scroll 40 has a driven side bulge 41A, a driven side non-bulge 41B, and a driven end plate side step 41C. The driven side bulge 41A, the driven side non-bulge 41B, and the driven end plate side step 41C correspond to the "bulge", "non-bulge", and "end plate side step" in the present invention, respectively. The driven scroll 43 of the driven scroll 40 has a driven scroll short portion 43A, a driven scroll main body portion 43B, and a driven scroll side step 43C. The driven scroll short portion 43A, the driven scroll main body portion 43B, and the driven scroll side step 43C correspond to the "volute short portion", "volute main body portion", and "volute side step" in the present invention, respectively.

As shown in FIG. 7, the driving side bulge 31A is formed on the front surface 311 of the driving end plate 31. The driving side bulge 31A extends clockwise from the center of the front surface 311, i.e., near the driving axis R1 and near the center of the spiral of the driving spiral 33, toward the outer periphery of the front surface 311 along the driving spiral 33. As shown in FIG. 1, the driving side bulge 31A bulges toward the driven spiral 43 more than the driving side non-bulge 31B, which is the portion of the driving end plate 31 excluding the driving side bulge 31A. In other words, the driving side bulge 31A is formed thicker than the driving side non-bulge 31B. The driving side non-bulge 31B is located on the outer periphery of the driving side bulge 31A on the driving end plate 31.

As shown in FIG. 7, the driving end plate side step 31C is formed at the boundary between the driving side bulge 31A and the driving side non-bulge 31B, and is connected to the driving side bulge 31A and the driving side non-bulge 31B. The length by which the driving side bulge 31A extends toward the outer periphery of the front surface 311, i.e., the position at which the driving end plate side step 31C is formed, can be designed as appropriate.

On the other hand, as shown in FIG. 1, the driven side bulge 41A is formed on the rear surface 412 of the driven end plate 41. As shown in FIG. 8, the driven side bulge 41A extends clockwise along the driven spiral 43 from the center of the rear surface 412, i.e., near the driven axis R2 and near the spiral center of the driven spiral 43, toward the outer periphery of the rear surface 412. As shown in FIG. 1, the driven side bulge 41A bulges toward the driving spiral 33 more than the driven side non-bulge 41B, which is the portion of the driven end plate 41 excluding the driven side bulge 41A. In other words, the driven side bulge 41A is formed thicker than the driven side non-bulge 41B. The driven side non-bulge 41B is located on the outer periphery of the driven side bulge 41A on the driven end plate 41.

As shown in FIG. 8, the driven end plate side step portion 41C is formed at the boundary between the driven side bulge portion 41A and the driven side non-bulge portion 41B, and is connected to the driven side bulge portion 41A and the driven side non-bulge portion 41B. The length by which the driven side bulge portion 41A extends toward the outer periphery of the rear surface 412, i.e., the position at which the driven end plate side step portion 41C is formed, can be designed as appropriate.

The discharge port 45 opens into the driven side expansion portion 41A. As shown in FIG. 2, the driven side expansion portion 41A and the discharge valve mechanism 56 overlap in the front-rear direction, i.e., in the direction of the driven axis R2. That is, the second recess 52 and the third recess 53 of the recesses 50 forming the discharge valve chamber 44 are disposed in an area corresponding to the driven side expansion portion 41A. More specifically, in a plan view seen from the front-rear direction, the outer edge of the second recess 52 and the outer edge of the third recess 53 are both located inside the outer edge of the driven side expansion portion 41A.

As shown in FIG. 7, the drive scroll short portion 33A extends from the center of the drive scroll 33 toward the outer periphery of the scroll. As shown in FIG. 1, the drive scroll short portion 33A faces the driven side bulge portion 41A when the drive scroll 30 and the driven scroll 40 are assembled in the front-to-rear direction. Here, the length of the drive scroll short portion 33A extending toward the driven end plate 41, i.e., the length in the direction of the drive axis R1, is shorter than the length of the drive scroll main body portion 33B, which is the portion of the drive scroll 33 excluding the drive scroll short portion 33A, in the direction of the drive axis R1.

In other words, the drive spiral main body 33B is the part of the drive spiral 33 that extends the longest toward the driven end plate 41. Therefore, the drive spiral short part 33A is shorter in the direction of the drive axis R1 than the part of the drive spiral 33 that extends the longest toward the driven end plate 41. This allows the drive spiral short part 33A to avoid interference with the driven side bulge part 41A.

As shown in FIG. 7, the drive spiral side step portion 33C is formed at the boundary between the drive spiral short portion 33A and the drive spiral main portion 33B, and is connected to the drive spiral short portion 33A and the drive spiral main portion 33B.

As shown in FIG. 8, the driven spiral short portion 43A extends from the center of the driven spiral body 43 toward the outer periphery of the spiral. As shown in FIG. 1, the driven spiral short portion 43A faces the driving side bulge portion 31A when the drive scroll 30 and the driven scroll 40 are assembled in the front-to-rear direction. Here, the length of the driven spiral short portion 43A extending toward the drive end plate 31, i.e., the length in the driven axis R2 direction, is shorter than the length of the driven spiral main body portion 43B, which is the portion of the driven spiral body 43 excluding the driven spiral short portion 43A, in the driven axis R2 direction.

In other words, the driven spiral main body 43B is the part of the driven spiral body 43 that extends the longest toward the driving end plate 31. Therefore, the driven spiral short part 43A is shorter in the driven axis R2 direction than the part of the driven spiral body 43 that extends the longest toward the driving end plate 31. This allows the driven spiral short part 43A to avoid interference with the driving side bulge part 31A.

As shown in FIG. 8, the driven spiral side step portion 43C is formed at the boundary between the driven spiral short portion 43A and the driven spiral main portion 43B and is connected to the driven spiral short portion 43A and the driven spiral main portion 43B.

In the compressor configured as described above, the inverter circuit 70 controls the operation of the electric motor 10 while supplying power to the stator 17, thereby operating the electric motor 10. This causes the rotor 11 to rotate, and the driving scroll 30 is driven to rotate around the driving axis R1 in the suction chamber 61A. In other words, the driving scroll 30 and the rotor 11 are driven to rotate together. At this time, in the driven mechanism 20, each rotation prevention pin 21 slides against the inner circumferential surface of each ring 22, causing each ring 22 to rotate relatively around the center of each rotation prevention pin 21. In this way, the driven mechanism 20 transmits the torque of the driving scroll 30 to the driven scroll 40.

As a result, the driven scroll 40 is rotated around the driven axis R2 by the driving scroll 30 and the driven mechanism 20. At this time, the driven mechanism 20 restricts the driven scroll 40 from rotating on its axis. As a result, the driving scroll 30 and the driven scroll 40 revolve around the driving axis R1 relative to the driving scroll 30 due to the rotational drive and the rotational follower, thereby changing the volume of the compression chamber 55.

As a result, the refrigerant gas in the suction chamber 61A is drawn into the compression chamber 55 through the suction port 35 and compressed in the compression chamber 55. The refrigerant gas compressed to the discharge pressure in the compression chamber 55 is discharged from the discharge port 45 into the discharge valve chamber 44, passes through the internal space 48A of the second boss 48, and is discharged into the discharge section 65C, and is discharged into the condenser from the discharge connection port 65B. In this way, air conditioning is performed by the vehicle air conditioning system.

Here, in this compressor, the driven scroll 40 has a driven scroll body 40A and a bearing cover body 40B. A discharge valve chamber 44 that houses a discharge valve mechanism 56 is formed in the driven end plate 41 of the driven scroll body 40A. The bearing cover body 40B has a cover part 47 that covers most of the discharge valve chamber 44 and the discharge valve mechanism 56, and a second boss 48 to which a needle bearing 72 is attached, and the internal space 48A of this second boss 48 communicates between the discharge valve chamber 44 and the discharge part 65C.

With this configuration, in this compressor, the discharge valve mechanism 56 is not accommodated in the internal space 48A of the second boss 48, so there is no need to make the internal space 48A of the second boss 48 larger than the discharge valve mechanism 56. Therefore, in this compressor, the internal space 48A of the second boss 48 can be made smaller than the conventional compressor described above, which has a boss integral with the driven end plate to which a driven side bearing that rotatably supports the driven scroll relative to the housing is attached, and which accommodates a discharge valve within this boss. As a result, the inner diameter d of the internal space 48A of the second boss 48 and the outer diameter D of the second boss 48 are made shorter than the length L of the longest part of the discharge reed valve 57. As a result, the needle bearing 72 attached to the outer circumferential surface of the second boss 48 can also be made smaller than the conventional compressor described above.

Therefore, the compressor of the embodiment can suppress the increase in size of the needle bearing 72, which is a bearing for rotatably supporting the driven scroll 40, in which the discharge valve mechanism 56 is provided, relative to the housing 60, thereby suppressing a decrease in efficiency, noise, and vibration.

In addition, in this compressor, the base end fixing portion 57B of the discharge reed valve 57 is covered by the cover portion 47. Therefore, even if the fixing bolt 59 loosens, the cover portion 47 can prevent the fixing bolt 59 from falling off. The tip valve portion 57A of the discharge reed valve 57 is disposed near the driven axis R2, and the discharge port 45 opened and closed by the tip valve portion 57A is also set near the driven axis R2. Therefore, the fluid compressed more in the compression chamber 55 can be discharged from the discharge port 45, which is advantageous in improving the compression efficiency.

Furthermore, in this compressor, a driving side bulge 31A is formed on the driving end plate 31 of the driving scroll 30, and a driven side bulge 41A and a driven side non-bulge 41B that is thinner than the driven side bulge 41A are formed on the driven end plate 41 of the driven scroll 40. Among the recesses 50 that form the discharge valve chamber 44, the second recess 52 and the third recess 53 are disposed in an area corresponding to the driven side bulge 41A in the driven end plate 41, and the outer edges of the second recess 52 and the third recess 53 are located inside the outer edge of the driven side bulge 41A.

As a result, in this compressor, since only a portion of the driven end plate 41 is made thick, the weight of the driven end plate 41 can be prevented from increasing compared to when the entire driven end plate 41 is made thick to provide the discharge valve chamber 44. In addition, the volume of the compression chamber 55 partitioned between the driven side bulge portion 41A and the driving side bulge portion 31A is reduced by the amount that the distance between the driven side bulge portion 41A and the driving side bulge portion 31A is shorter than the distance between the driven end plate on which the driven side bulge portion 41A is not formed and the driving end plate on which the driving side bulge portion 31A is not formed, and the compression efficiency can be improved.

In addition, in this compressor, the discharge port 45 opens to the third recess bottom surface 53B of the third recess 53, which is the deepest of the recesses 50 that form the discharge valve chamber 44. And one end of the inner periphery of the oil return passage 54 opens to the circular first recess inner periphery surface 51B of the first recess 51, which is the shallowest of the recesses 50. This oil return passage 54 extends to the outer periphery, and the other end of the oil return passage 54 on the outer periphery opens to the suction chamber 61A. That is, the discharge valve chamber 44 and the suction chamber 61A are connected by the oil return passage 54.

In this case, the fluid discharged from the discharge port 45 into the rotating discharge valve chamber 44 is subjected to centrifugal force, so that the oil is separated from the fluid by centrifugal force in the discharge valve chamber 44 and moves toward the outer periphery. In addition, most of the opening of the recess 50 forming the discharge valve chamber 44, that is, the entire first recess 51, the entire second recess 52, and most of the third recess 53, are covered by the cover portion 47. Therefore, the cover portion 47 blocks most of the oil flowing from the discharge valve chamber 44 toward the internal space 48A of the boss portion 48 in the driven axis R2 direction. In addition, in the discharge valve chamber 44, the oil can be stored in the second recess 52, which is provided separately from the third recess 53 that houses the discharge valve mechanism 56 and is deeper than the first recess 51. Furthermore, the oil in the first recess 51 is guided to the oil return passage 54 along the circular first recess inner circumferential surface 51B.

As a result, the oil in the discharge valve chamber 44 is easily introduced into the oil return passage 54 that opens into the inner circumferential surface 51B of the first recess. The oil introduced into the oil return passage 54 flows to the outer periphery due to centrifugal force and flows out into the suction chamber 61A. The oil that flows out into the suction chamber 61A can provide oil lubrication and oil sealing effects in areas where lubrication and sealing are required.

Example 2
9 and 10 , in the compressor of the second embodiment, the first recess 51 is eliminated from the recess 50 that forms the discharge valve chamber 44. Also, one end on the inner periphery side of the groove 541 of the oil return passage 54 opens into the second recess inner periphery surface 52B of the second recess 52. The second recess inner periphery surface 52B is an example of the "inner periphery of the discharge valve chamber" of the present invention where the oil return passage 54 opens.

In this compressor, oil separated by centrifugal force from the fluid discharged into the rotating discharge valve chamber 44 is directed toward the outer periphery. In addition, most of the opening of the recess 50 forming the discharge valve chamber 44, i.e., the entire second recess 52 and most of the third recess 53, are covered by the cover 47. Therefore, the cover 47 blocks most of the oil flowing from the discharge valve chamber 44 toward the internal space 48A of the boss 48 in the direction of the driven axis R2. In addition, in the discharge valve chamber 44, oil can be stored in the second recess 52 provided separately from the third recess 53 that houses the discharge valve mechanism 56.

As a result, the oil in the discharge valve chamber 44 is easily introduced into the oil return passage 54 that opens into the inner peripheral surface 52B of the second recess. The oil introduced into the oil return passage 54 flows to the outer periphery due to centrifugal force and flows out into the suction chamber 61A. The oil that flows out into the suction chamber 61A can provide oil lubrication and oil sealing effects in areas where lubrication and sealing are required.

The other configurations and functions of this compressor are the same as those of the compressor in Example 1, and the same components are designated by the same reference numerals and detailed descriptions of the configurations are omitted.

Although the present invention has been described above with reference to Examples 1 and 2, it goes without saying that the present invention is not limited to the above Examples 1 and 2, and can be modified as appropriate without departing from the spirit of the present invention.

For example, in the compressors of Examples 1 and 2, the driven scroll 40 is the first scroll, but this is not limited thereto, and the driving scroll 30 may be the first scroll.

In the compressors of Examples 1 and 2, the suction port 35 is formed on the driving scroll 30 side, which serves as the second scroll, but this is not limiting, and the suction port 35 may be provided on the driven scroll 40 side, which serves as the first scroll.

In the compressors of Examples 1 and 2, a driving side bulge 31A is formed on the driving end plate 31 of the driving scroll 30 as the second scroll, and a driven spiral short portion 43A is formed on the driven spiral body 43 of the driven scroll 40 as the first scroll, but the formation of the driving side bulge 31A on the driving end plate 31 and the formation of the driven spiral short portion 43A on the driven spiral body 43 may be omitted. Also, the formation of the driven side bulge 41A on the driven end plate 41 of the driven scroll 40 as the first scroll may be omitted, and the formation of the driving spiral short portion 33A on the driving spiral body 33 of the driving scroll 30 as the second scroll may be omitted.

In the first and second embodiments, the oil return passage 54 is formed by a groove 441 recessed in the rear surface 411 of the driven end plate 41 and a hole 542 penetrating the driven end plate 41 in the thickness direction, but this is not limited thereto, and the oil return passage may be formed by a groove or a through hole provided in the cover portion 47 of the gasket 40C or the bearing cover body 40B.

In the first and second embodiments, the oil return passage 54 is connected to the discharge valve chamber 44 and the suction chamber 61A, but this is not limiting, and the oil return passage 54 may be connected to the discharge valve chamber 44 and the compression chamber 55.

In the first and second embodiments, the recess 50 for forming the discharge valve chamber 44 is provided in the driven end plate 41 serving as the first end plate, but this is not limiting. Instead of the driven end plate 41, the recess 50 may be provided in the cover portion 47 of the bearing cover body 40B, or the recess 50 may be provided in both the first end plate and the cover portion 47.

In the first and second embodiments, the entire discharge valve mechanism 56 is disposed in a region corresponding to the driven-side bulging portion 41A of the driven end plate 41 as the first end plate, but the present invention is not limited to this. For example, the base end fixing portion 57B may be disposed in a region corresponding to the bulging portion of the first end plate, and the tip valve portion 57A may be disposed in a region corresponding to the non-bulging portion of the first end plate, or vice versa, the tip valve portion 57A may be disposed in a region corresponding to the bulging portion of the first end plate, and the base end fixing portion 57B may be disposed in a region corresponding to the non-bulging portion of the first end plate. In these cases, the recess 50 may be provided in both the first end plate and the cover portion 47.

In the compressors of Examples 1 and 2, the driven mechanism 20 is composed of a rotation prevention pin 21 and a 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 slide against the inner peripheral surface of one free ring, a pin-pin system in which the outer peripheral surfaces of two pins slide against each other, a system using an Oldham joint, etc.

In the compressors of Examples 1 and 2, the driving scroll 30 and the rotor 11 are integrated by fixing the driving peripheral wall 32 to the inner peripheral surface of the rotor 11. However, this is not limited to this, and the driving scroll 30 and the rotor 11 may be connected to each other so that power can be transmitted by a drive shaft, so that the driving scroll 30 and the rotor 11 are arranged apart in the direction of the drive axis R1.

(Appendix 1)
a housing having a suction chamber into which fluid is drawn from the outside and a discharge chamber from which the fluid is discharged to the outside;
A first scroll disposed within the housing;
a second scroll provided in the housing, facing the first scroll, and defining a compression chamber for compressing a fluid between the first scroll and the second scroll,
the first scroll has a first end plate and a first scroll body that is integral with the first end plate and protrudes in a spiral shape toward the second scroll,
The second scroll has a second end plate and a second scroll body that is integral with the second end plate and protrudes in a spiral shape toward the first scroll,
the first scroll has a bearing cover body fixed to an end surface of the first end plate opposite to the compression chamber,
a discharge valve chamber that constitutes a part of the discharge chamber is formed between the first end plate and the bearing cover body,
a discharge port that communicates between the compression chamber and the discharge valve chamber is formed in the first end plate,
a discharge valve for opening and closing the discharge port is provided in the discharge valve chamber,
the bearing cover body includes a cover portion which covers a part of the discharge valve chamber and a part of the discharge valve, and a boss portion which extends cylindrically from an inner circumferential side of the cover portion toward an opposite side to the compression chamber, the boss portion having an internal space which communicates with the discharge valve chamber,
a bearing for rotatably supporting the first scroll on an outer circumferential surface of the boss portion,

(Appendix 2)
the discharge valve is a discharge reed valve having a tip valve portion that opens and closes the discharge port and a base end fixing portion that fixes the discharge valve to the first end plate,
2. The double-rotating scroll compressor according to claim 1, wherein the base end fixing portion is covered by the cover portion.

(Appendix 3)
3. The double-rotating scroll compressor according to claim 2, wherein the tip valve portion is disposed at a position closer to a center of the boss portion than the base end fixing portion.

(Appendix 4)
At least the first end plate of the first end plate and the second end plate has a bulging portion bulging toward the opposing first end plate or the second end plate, a non-bulging portion located on the outer circumferential side of the bulging portion, and an end plate side step portion connected to the bulging portion and the non-bulging portion, and the first spiral body or the second spiral body protruding from the opposing first end plate or the second end plate has a spiral main body portion, a spiral short portion protruding shorter than the spiral main body portion so as to avoid interference with the bulging portion, and a spiral body side step portion connected to the spiral main body portion and the spiral short portion,
4. The double rotary scroll compressor according to claim 1, wherein the discharge valve chamber is formed by a recess recessed from the end face of the first end plate toward the compression chamber in a region where the bulge portion is provided.

(Appendix 5)
5. The double rotary scroll compressor according to claim 1, further comprising an oil return passage that opens to an inner circumferential surface of the discharge valve chamber and extends from the inner circumferential surface of the discharge valve chamber toward an outer circumferential surface of the discharge valve chamber, the oil return passage communicating with the discharge valve chamber and the suction chamber or the compression chamber.

The present invention can be used in vehicle air conditioning systems, etc.

30... Driving scroll (second scroll)
31... Driving end plate (second end plate)
31A: Driving side bulge (bulge)
31B: Driving side non-bulging portion (non-bulging portion)
31C: Driving end plate side step portion (end plate side step portion)
33...Drive scroll (second scroll)
33A: Drive spiral short part (spiral short part)
33B: Drive scroll body (scroll body)
33C: Drive scroll side step portion (scroll side step portion)
40...follower scroll (first scroll)
40B: Bearing cover body 41: Driven end plate (first end plate)
411...Front (end face)
41A... Driven side bulge (bulge)
41B... driven side non-bulging portion (non-bulging portion)
41C...Follower end plate side step portion (end plate side step portion)
43...follower spiral body (first spiral body)
43A...follower spiral short part (spiral short part)
43B...follower scroll body (scroll body)
43C... Follower scroll side step portion (scroll side step portion)
44...Discharge valve chamber (discharge chamber)
45: Discharge port 47: Cover portion 48: Second boss (boss portion)
48A: Internal space (discharge chamber)
50: Recess 51B: First recess inner circumferential surface (inner circumferential surface)
52B: Second recess inner circumferential surface (inner circumferential surface)
54: Oil return passage 55: Compression chamber 57: Discharge reed valve (discharge valve)
57A: Tip valve portion 57B: Base end fixing portion 60: Housing 61A: Suction chamber 65C: Discharge portion (discharge chamber)
72...Needle bearing (bearing)

Claims (5)

a housing having a suction chamber into which fluid is drawn from the outside and a discharge chamber from which the fluid is discharged to the outside;
A first scroll disposed within the housing;
a second scroll provided in the housing, facing the first scroll, and defining a compression chamber for compressing a fluid between the first scroll and the second scroll,
the first scroll has a first end plate and a first scroll body that is integral with the first end plate and protrudes in a spiral shape toward the second scroll,
The second scroll has a second end plate and a second scroll body that is integral with the second end plate and protrudes in a spiral shape toward the first scroll,
the first scroll has a bearing cover body fixed to an end surface of the first end plate opposite to the compression chamber,
a discharge valve chamber that constitutes a part of the discharge chamber is formed between the first end plate and the bearing cover body,
a discharge port that communicates between the compression chamber and the discharge valve chamber is formed in the first end plate,
A discharge valve that opens and closes the discharge port is provided in the discharge valve chamber,
the bearing cover body includes a cover portion which covers a part of the discharge valve chamber and a part of the discharge valve, and a boss portion which extends cylindrically from an inner circumferential side of the cover portion toward an opposite side to the compression chamber, the boss portion having an internal space which communicates with the discharge valve chamber,
a bearing for rotatably supporting the first scroll on an outer circumferential surface of the boss portion, the discharge valve is a discharge reed valve having a tip valve portion that opens and closes the discharge port and a base end fixing portion that fixes the discharge valve to the first end plate,
2. The double-rotating scroll compressor according to claim 1, wherein the base end fixing portion is covered by the cover portion. The double-rotating scroll compressor according to claim 2, wherein the tip valve portion is disposed closer to the center of the boss portion than the base end fixing portion. At least the first end plate of the first end plate and the second end plate has a bulging portion bulging toward the opposing first end plate or the second end plate, a non-bulging portion located on the outer circumferential side of the bulging portion, and an end plate side step portion connected to the bulging portion and the non-bulging portion, and the first spiral body or the second spiral body protruding from the opposing first end plate or the second end plate has a spiral main body portion, a spiral short portion protruding shorter than the spiral main body portion so as to avoid interference with the bulging portion, and a spiral body side step portion connected to the spiral main body portion and the spiral short portion,
4. The double-rotary scroll compressor according to claim 1, wherein the discharge valve chamber is formed by a recess recessed from the end face of the first end plate toward the compression chamber in a region where the bulge portion is provided.
Type compressor. A double-rotating scroll compressor according to any one of claims 1 to 3, comprising an oil return passage that opens to the inner peripheral surface of the discharge valve chamber, extends from the inner peripheral surface of the discharge valve chamber toward the outer peripheral side, and connects the discharge valve chamber to the suction chamber or the compression chamber.

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