CO-ROTATING SCROLL COMPRESSOR

A co-rotating scroll compressor includes: a housing; a driving scroll; and a driven scroll. The housing has a suction chamber into which a refrigerant containing lubricating oil is drawn from outside of the housing. The driving scroll and the driven scroll form a compression chamber. An accumulator is accommodated in the suction chamber. The accumulator is in communication with the suction chamber. The accumulator receives the refrigerant drawn from the suction chamber and allows the refrigerant to be separated into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil. The accumulator is fixed to the driving scroll or the driven scroll and rotatable in the suction chamber. At least one of the driving scroll and the driven scroll has a suction passage which is in communication with the accumulator and through which the gaseous refrigerant in the accumulator is drawn into the compression chamber.

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Description
CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a National Stage of International Application No. PCT/JP2024/007329 filed Feb. 28, 2024, claiming priority based on Japanese Patent Application No. 2023-085205 filed May 24, 2023, the contents of all of which are incorporated herein by reference in their entirety.

TECHNICAL FIELD

The present disclosure relates to a co-rotating scroll compressor.

BACKGROUND ART

Patent Literature 1 discloses a known co-rotating scroll compressor (hereinafter simply referred to as a compressor). The compressor includes a housing, a driving mechanism, a driving scroll, a driven scroll, and a driven mechanism. The housing includes a main frame, which defines a scroll chamber and a low-pressure chamber in the housing. In the scroll chamber, the driving scroll, the driven scroll, and the driven mechanism are accommodated. In the low-pressure chamber, the driving mechanism is accommodated. The main frame has a suction passage through which the low-pressure chamber is in communication with the scroll chamber. The housing has a suction pipe through which the low-pressure chamber is in communication with the outside of the housing.

The driving scroll faces the driven scroll in the scroll chamber. The driving scroll and the driven scroll cooperate to form a compression chamber therebetween. The driving scroll includes a drive shaft. The drive shaft is rotatably supported by the main frame, extends into the low-pressure chamber, and is fixed to the driving mechanism. The driven mechanism is disposed between the driving scroll and the driven scroll.

In this compressor, the driving scroll is driven to rotate about the driving axis by the driving mechanism, and the driven scroll is driven to rotate about the driven axis by the driving scroll and the driven mechanism. A refrigerant is drawn from the outside of the housing into the low-pressure chamber through the suction pipe, and then drawn into the scroll chamber through the suction passage. In this compressor, the volume of the compression chamber changes with the rotation of the driving scroll and the rotation of the driven scroll, so that the refrigerant in the scroll chamber is drawn into and compressed in the compression chamber.

Citation List Patent Literature

    • Patent Literature 1: Japanese Patent Application Publication No. H04-076287

SUMMARY OF INVENTION Technical Problem

This type of compressor may be used for an air conditioning device that includes a heat exchanger and the like. Such an air conditioning device may have a concern that a liquid refrigerant in the heat exchanger and the like may be drawn into the housing together with a gaseous refrigerant, which is in the vapor phase, when the air conditioning device switches from cooling operation to heating operation, for example. If such a liquid refrigerant is drawn into and compressed in the compression chamber, the driving scroll and the driven scroll may be damaged, leading to a decrease in the reliability of the compressor.

Accordingly, it is considered to provide an accumulator in this compressor to separate the refrigerant into a gaseous refrigerant and a liquid refrigerant, allowing the gaseous refrigerant to be drawn from the low-pressure chamber into the compression chamber while preventing the liquid refrigerant from being drawn into the compression chamber.

However, if a large amount of the liquid refrigerant is stored in the accumulator due to the gas-liquid separation, the liquid refrigerant may be carried upward inside the accumulator by the gaseous refrigerant that is drawn into the accumulator. Accordingly, the gas-liquid separation in the accumulator may be insufficient, and the liquid refrigerant in the accumulator may be partially drawn into the low-pressure chamber, and consequently into the compression chamber, together with the gaseous refrigerant.

The present disclosure, which has been made in light of the above-mentioned problem, is directed to providing a co-rotating scroll compressor that has excellent reliability.

Solution to Problem

A co-rotating scroll compressor according to the present disclosure comprises: a housing; a driving mechanism; a driving scroll; a driven scroll; and a driven mechanism, wherein

    • the housing has a suction chamber in which the driving scroll and the driven scroll are accommodated and into which a refrigerant containing lubricating oil is drawn from outside of the housing,
    • the driving scroll is configured to be driven to rotate by the driving mechanism about a driving axis,
    • the driven scroll is eccentric to the driving scroll and configured to be rotated by the driving scroll and the driven mechanism about a driven axis, and
    • the driving scroll and the driven scroll form a compression chamber for compressing the refrigerant, wherein
    • an accumulator is accommodated in the suction chamber, the accumulator being in communication with the suction chamber, the accumulator receiving the refrigerant drawn from the suction chamber and allowing the refrigerant to be separated into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil,
    • the accumulator is fixed to the driving scroll or the driven scroll and rotatable in the suction chamber, and
    • at least one of the driving scroll and the driven scroll has a suction passage which is in communication with the accumulator and through which the gaseous refrigerant in the accumulator is drawn into the compression chamber.

In the co-rotating scroll compressor according to the present disclosure, in addition to the driving scroll and the driven scroll, the accumulator is accommodated in the suction chamber of the housing. The refrigerant is drawn from the outside of the housing into the suction chamber. The refrigerant contains lubricating oil. The refrigerant in the suction chamber is drawn into the accumulator. Accordingly, in the compressor, the refrigerant is not directly drawn into the accumulator from the outside of the housing.

That is, in the compressor, the refrigerant is drawn into the suction chamber from the outside of the housing, and the refrigerant is initially separated into the gaseous refrigerant and the liquid refrigerant in the suction chamber. Then, the refrigerant is drawn from the suction chamber into the accumulator, and the refrigerant is subsequently separated into the gaseous refrigerant and the liquid refrigerant in the accumulator. In the compressor, the initial gas-liquid separation of the refrigerant in the suction chamber causes the refrigerant drawn into the accumulator to be less likely to include the liquid refrigerant, compared to a configuration in which the refrigerant is directly drawn into the accumulator from the outside of the housing and the refrigerant is separated into the gaseous refrigerant and the liquid refrigerant only in the accumulator.

In the compressor, the accumulator is fixed to the driving scroll or the driven scroll, and rotatable in the suction chamber. This causes the refrigerant drawn into the accumulator to be suitably separated into the gaseous refrigerant and the liquid refrigerant under the influence of the centrifugal force of the rotating accumulator. The gaseous refrigerant in the accumulator is drawn into the compression chamber through the suction passage, and compressed in the compression chamber. The liquid refrigerant separated from the gaseous refrigerant tends to remain in the accumulator on the radially outer side of the accumulator, i.e., on the radially outer side of the driving scroll and the driven scroll due to the centrifugal force.

This configuration of the compressor prevents the liquid refrigerant in the accumulator from being drawn into the compression chamber, even when a large amount of the liquid refrigerant is present in the accumulator. Accordingly, the compressor is less likely to compress the liquid refrigerant in the compression chamber.

The gaseous refrigerant drawn into the compression chamber may contain some lubricating oil, so that the compression chamber is lubricated by the lubricating oil. Accordingly, in the compressor, the driving scroll and the driven scroll are less likely to wear.

Therefore, the co-rotating scroll compressor according to the present disclosure has excellent reliability.

The housing may have a support portion that extends into the suction chamber and supports the accumulator such that the accumulator is rotatable. The support portion preferably has a reflux passage through which the lubricating oil in the suction chamber flows into the accumulator.

This allows the lubricating oil in the suction chamber to suitably flow into the accumulator through the reflux passage. This therefore allows the lubricating oil in the suction chamber to be suitably returned to the compression chamber through the accumulator, allowing the compression chamber to be suitably lubricated.

At least one of the driving scroll and the driven scroll may have a supply passage through which the lubricating oil in the accumulator is supplied to the compression chamber. The supply passage is preferably located outward of the suction passage in the radial direction of the driving scroll and a radial direction of the driven scroll, and is in communication with the accumulator.

The lubricating oil in the accumulator is also likely to accumulate on the radially outer side of the driving scroll and the driven scroll under the influence of the centrifugal force of the rotating accumulator. In this regard, at least one of the driving scroll and the driven scroll of the compressor has the supply passage, and the supply passage is located outward of the suction passage in the radial direction of the driving scroll and the driven scroll and is in communication with the accumulator. This configuration allows the lubricating oil in the accumulator to be suitably supplied to the compression chamber through the supply passage. Accordingly, the compression chamber is suitably lubricated by the lubricating oil.

In the compressor, a part of the liquid refrigerant in the accumulator may inevitably flow through the supply passage together with the lubricating oil. However, the liquid refrigerant is vaporized by the heat of the driving scroll and the driven scroll generated while the liquid refrigerant flows toward the compression chamber. This prevents the liquid refrigerant in the accumulator from being drawn into the compression chamber through the supply passage.

In the compressor, the suction passage is located inward of the supply passage in the radial direction of the driving scroll and the driven scroll, and this configuration suitably prevents the liquid refrigerant in the accumulator from being drawn into the compression chamber through the suction passage.

The driving mechanism may include: a stator fixed to the housing and accommodated in the suction chamber; and a rotor having a cylindrical shape and rotatably disposed inside the stator. The accumulator is preferably fixed to the driving scroll and disposed inside the rotor.

Fixing the accumulator of the compressor to the driving scroll and disposing the accumulator inside the rotor reduces the need for elongation of the housing in the direction of the driving axis, compared to a configuration in which the accumulator is fixed to the driving scroll and disposed outside the rotor, for example.

The driving mechanism may include: a stator accommodated in the suction chamber and fixed to the housing; and a rotor having a cylindrical shape and rotatably disposed inside the stator. The driving scroll may be disposed inside the rotor. The accumulator is preferably fixed to the driving scroll.

This configuration eliminates the need to place the accumulator inside the rotor, thereby increasing the design flexibility of the shape of the accumulator. This easily allows an increase in the diameter of the accumulator, thereby facilitating centrifugal separation of the liquid refrigerant and the lubricating oil in the compressor.

Advantageous Effects of Invention

The co-rotating scroll compressor according to the present disclosure has excellent reliability.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a cross-sectional view of a co-rotating scroll compressor according to a first embodiment.

FIG. 2 is a schematic diagram of an air conditioning device including the co-rotating scroll compressor according to the first embodiment, illustrating the air conditioning device in cooling operation.

FIG. 3 is a schematic diagram of the air conditioning device including the co-rotating scroll compressor according to the first embodiment, illustrating the air conditioning device in heating operation.

FIG. 4 is a cross-sectional view of a co-rotating scroll compressor according to a second embodiment.

 DESCRIPTION OF EMBODIMENTS

The following will describe a first embodiment and a second embodiment of the present disclosure in detail with reference to the accompanying drawings. A compressor 1 according to the first embodiment and a compressor 2 according to the second embodiment are mounted on a vehicle (not illustrated).

First Embodiment

FIG. 1 illustrates the compressor 1 according to the first embodiment including a housing 6, an electric motor 10, a driving scroll 30, a driven scroll 40, a driven mechanism 20, and an accumulator 15. The electric motor 10 serves as the driving mechanism of the present disclosure, for example.

In the present embodiments, the front-rear direction and the up-down direction of the compressors 1, 2 are defined by solid arrows in FIGS. 1 and 4. The front-rear direction and the up-down direction are perpendicular to each other. In the embodiments, the compressors 1, 2 are mounted on the vehicle so that the lower sides of the compressors 1, 2 correspond to the lower side of the vehicle. It is noted that the directions are merely one example for convenience of explanation, and the posture of each of the compressors 1, 2 may be changed, as appropriate, depending on the vehicle on which the each of the compressors 1, 2 is mounted.

As illustrated in FIG. 1, the housing 6 includes a housing body 60, a housing cover 61, and an attachment 62. The housing body 60 and the housing cover 61 are made of aluminum alloy. The attachment 62 is made of resin. The attachment 62 may be made of aluminum alloy.

The housing body 60 is a bottomed tubular member, and includes an outer peripheral wall 60a and a rear wall 60b. The outer peripheral wall 60a has a cylindrical shape centered about a driving axis O1. The driving axis O1 is parallel to the front-rear direction. The outer peripheral wall 60a has a suction communication port 69. The suction communication port 69 is formed through the outer peripheral wall 60a in the radial direction of the housing body 60. The suction communication port 69 is connected to a pipe H7. The suction communication port 69 is connected to the outside of the housing 6, i.e., the outside of the compressor 1, through the pipe H7.

The rear wall 60b is located at the rear end of the housing body 60. The rear wall 60b has a substantially circular plate shape and is perpendicular to the driving axis O1. The outer peripheral edge of the rear wall 60b is connected to the rear end of the outer peripheral wall 60a. The rear wall 60b has a first support portion 64 at the center of the inner surface of the rear wall 60b. The first support portion 64 serves as the support portion of the present disclosure, for example. The first support portion 64 has a substantially circular solid cylindrical shape centered about the driving axis O1, and extends forward from the center of the inner surface of the rear wall 60b into a suction chamber 65, which will be described later.

The first support portion 64 has a pin hole 4. The pin hole 4 is formed on the front end surface of the first support portion 64, and extends in the first support portion 64 linearly and rearward. The pin hole 4 is not formed through the first support portion 64 in the front-rear direction.

The first support portion 64 has a reflux passage 8. The reflux passage 8 includes a reflux main passage 8a, a first radial passage 8b, and a second radial passage 8c. The reflux main passage 8a opens at the rear wall 60b, and extends forward from the rear wall 60b in the direction of the driving axis O1 inside the first support portion 64. The reflux main passage 8a is spaced apart from the pin hole 4 in the front-rear direction, and is not in communication with the pin hole 4. The opening of the reflux main passage 8a at the rear wall 60b is closed by a sealing member 81, and the reflux main passage 8a is not in communication with the outside of the housing 6.

The first radial passage 8b is located at the rear end of the first support portion 64, and in communication with the reflux main passage 8a. The first radial passage 8b extends through the first support portion 64 from the reflux main passage 8a in the radial direction of the first support portion 64, and opens at the outer peripheral surface of the first support portion 64. In the first support portion 64, the second radial passage 8c is located in front of the first radial passage 8b, and substantially at the center of the first support portion 64 in the front-rear direction. The second radial passage 8c is in communication with the reflux main passage 8a. Similar to the first radial passage 8b, the second radial passage 8c extends through the first support portion 64 from the reflux main passage 8a in the radial direction of the first support portion 64, and opens at the outer peripheral surface of the first support portion 64.

The housing cover 61 is disposed in front of the housing body 60. The housing cover 61 has a substantially circular plate shape, and is perpendicular to the driving axis O1. The housing cover 61 is fixed to the housing body 60 by bolts (not illustrated) with the outer peripheral edge of the housing cover 61 in contact with the front end of the outer peripheral wall 60a of the housing body 60. Accordingly, the housing body 60 is closed by the housing cover 61 on the front side. The housing body 60 therefore has the suction chamber 65 inside the housing body 60.

The housing cover 61 has a second support portion 67 at the center of the inner surface of the housing cover 61. The second support portion 67 has a cylindrical shape centered about the driving axis O1, and extends rearward from the center of the inner surface of the housing cover 61. An outer ring of a needle bearing 14 is fitted into the second support portion 67.

The housing cover 61 has a discharge communication port 68. The discharge communication port 68 is located at the center of the housing cover 61, and is formed through the housing cover 61 in the direction of the driving axis O1. The discharge communication port 68 is in communication with a discharge chamber 13, which will be described later. The discharge communication port 68 is connected to a pipe H1. The discharge communication port 68 is connected to the outside of the compressor 1 through the pipe H1.

The suction chamber 65 is in communication with the suction communication port 69. This configuration allows a refrigerant to be drawn into the suction chamber 65 from the outside of the compressor 1 through the pipe H7 connected to the suction communication port 69.

The attachment 62 is disposed in the suction chamber 65 and attached to the rear wall 60b of the housing body 60. The attachment 62 has a plate shape and extends perpendicular to the driving axis O1. The attachment 62 has a first guide passage 62a and a second guide passage 62b.

The first guide passage 62a is recessed in the rear surface of the attachment 62, i.e., the surface of the attachment 62 facing the rear wall 60b. Since the attachment 62 is attached to the rear wall 60b, the first guide passage 62a extends in the radial direction of the housing body 60. The first guide passage 62a is in communication with the first radial passage 8b at the upper end of the first guide passage 62a.

The second guide passage 62b is formed in the lower portion of the attachment 62. The second guide passage 62b opens, at the front end thereof, at the surface of the attachment 62 facing the suction chamber 65, and is connected, at the rear end thereof, to the first guide passage 62a. The first radial passage 8b, i.e., the reflux passage 8, is in communication with the bottom of the suction chamber 65 through the first guide passage 62a and the second guide passage 62b. The attachment 62 does not necessarily need to be attached to the housing body 60, and the first radial passage 8b may be in direct communication with the suction chamber 65.

The electric motor 10 is accommodated in the suction chamber 65. The suction chamber 65 serves as a motor chamber in which the electric motor 10 is accommodated. The electric motor 10 includes a stator 17 and a rotor 11. The stator 17 has a cylindrical shape centered about the driving axis O1, and has a winding wire 17a. The stator 17 is fitted onto the inner peripheral surface of the outer peripheral wall 60a, so that the stator 17 is fixed to the housing body 60.

The rotor 11 has a cylindrical shape centered about the driving axis O1, and is disposed inside the stator 17. Although not illustrated in detail, the rotor 11 is formed of a plurality of permanent magnets corresponding to the stator 17, electromagnetic steel sheets for fixing the permanent magnets, and the like.

The driving scroll 30 is made of aluminum alloy. The driving scroll 30 is accommodated in the suction chamber 65. The driving scroll 30 includes a driving scroll end plate 31, a driving scroll peripheral wall 32, a driving scroll body 33, and a cover body 35.

The driving scroll end plate 31 has a substantially disc shape and is perpendicular to the driving axis O1 and a driven axis O2. The driven axis O2 is eccentric and parallel to the driving axis O1. That is, the driven axis O2 is parallel to the front-rear direction.

The driving scroll end plate 31 has opposite surfaces: a front surface 311 facing the housing cover 61; and a rear surface 312, in the suction chamber 65. A first boss 34 extends from the center of the front surface 311 toward the housing cover 61. The first boss 34 has a cylindrical shape centered about the driving axis O1.

The driving scroll end plate 31 has a discharge port 38. The discharge port 38 is formed in the first boss 34 of the driving scroll end plate 31, and formed through the driving scroll end plate 31 in the front-rear direction.

In the first boss 34, a discharge reed valve 57 and a retainer 58 are fixed to the driving scroll end plate 31 by a fixing bolt 59. The discharge reed valve 57 opens and closes the discharge port 38, and the retainer 58 adjusts the opening degree of the discharge reed valve 57.

The driving scroll peripheral wall 32 has a cylindrical shape centered about the driving axis 01, and extends parallel to the driving axis O1 and the driven axis O2. The driving scroll peripheral wall 32 is integrated with the outer peripheral edge of the driving scroll end plate 31 at the front end of the driving scroll peripheral wall 32, has a cylindrical shape, and extends rearward from the driving scroll end plate 31.

The driving scroll body 33 is disposed inside the driving scroll peripheral wall 32. The driving scroll body 33 is integrated with the driving scroll end plate 31, and extends rearward from the rear surface 312 of the driving scroll end plate 31 toward the driven scroll 40 and parallel to the driving axis O1 and the driven axis O2. Although not illustrated in detail, the driving scroll body 33 has a spirally extending shape centered about the center of the driving scroll end plate 31, and radially outwardly extending from the center of the spiral shape. The driving scroll body 33 is connected, at the outer peripheral edge thereof, to the inner peripheral surface of the driving scroll peripheral wall 32.

The cover body 35 has a substantially disc shape, and is perpendicular to the driving axis O1 and the driven axis O2. The cover body 35 has substantially the same diameter as the diameter of the driving scroll end plate 31 and the diameter of the driving scroll peripheral wall 32. The cover body 35 has a front surface 351 and a rear surface 352. The front surface 351 faces the rear surface 312 of the driving scroll end plate 31 in the front-rear direction. The rear surface 352 is opposite to the front surface 351.

The cover body 35 has a second boss 36, a suction passage 35a, and a supply passage 35b. The second boss 36 is integrated with the cover body 35 at the center of the cover body 35, and extends rearward from the rear surface 352. The second boss 36 has an insertion hole 350. The insertion hole 350 is formed through the second boss 36 and the cover body 35 in the direction of the driving axis O1. The second boss 36 has a cylindrical shape centered about the driving axis 01. A plain bearing 51 is disposed in the insertion hole 350. Instead of the plain bearing 51, a ball bearing or the like may be disposed in the insertion hole 350.

The suction passage 35a is formed through the cover body 35 in the front-rear direction. The supply passage 35b is located outward of the suction passage 35a in the radial direction of the cover body 35. The supply passage 35b is formed through the cover body 35 in the front-rear direction. The suction passage 35a is not in communication with the supply passage 35b. The opening of the suction passage 35a and the opening of the supply passage 35b on the front surface 351 are located outward of the opening of the suction passage 35a and the opening of the supply passage 35b on the rear surface 352 in the radial direction of the cover body 35. That is, the suction passage 35a and the supply passage 35b extend outwardly from the rear surface 352 to the front surface 351 in the radial direction of the cover body 35.

A plurality of rings 22 is attached to the cover body 35 at positions radially outward of the second boss 36. The rings 22 are arranged at equal intervals in the circumferential direction of the cover body 35, face forward, and surround the second boss 36 and the insertion hole 350. In the present embodiment, the number of the rings 22 is six. FIG. 1 illustrates two of the six rings 22. The same is true for FIG. 4.

The driven scroll 40 illustrated in FIG. 1 is made of aluminum alloy. The driven scroll 40 is accommodated in the suction chamber 65, more specifically, inside the driving scroll 30. The driven scroll 40 includes a driven scroll end plate 41 and a driven scroll body 43.

The driven scroll end plate 41 has a substantially disc shape and is perpendicular to the driving axis O1 and the driven axis O2. The driven scroll end plate 41 has a front surface 411 and a rear surface 412. The front surface 411 faces the rear surface 312 of the driving scroll end plate 31 in the driving scroll 30. The rear surface 412 is opposite to the front surface 411 and faces the front surface 351 of the cover body 35.

The driven scroll end plate 41 has an accommodation portion 41a. The accommodation portion 41a has a shape centered about the driven axis O2, and is recessed cylindrically forwardly from the rear surface 412 of the driven scroll end plate 41. A bushing 53 is disposed in the accommodation portion 41a. The bushing 53 may be disposed in the accommodation portion 41a via a bearing, such as a plain bearing or a ball bearing.

A driven pin 55 is inserted into the bushing 53. The driven pin 55 is inserted into the bushing 53 at the center of the bushing 53, i.e., at a position eccentric to the driven axis 02. The driven pin 55 is made of steel, and has a solid cylindrical shape. The driven pin 55 protrudes rearward from the bushing 53, i.e., the driven scroll end plate 41.

A plurality of anti-rotation pins 21 is fixed in the driven scroll end plate 41 at positions radially outward of the accommodation portion 41a, and the anti-rotation pins 21 protrude rearward from the rear surface 412. More specifically, each of the anti-rotation pins 21 is fixed at a position outward of the accommodation portion 41a and facing the ring 22. In the driven scroll end plate 41, the anti-rotation pins 21 are arranged at equal intervals in the circumferential direction of the driven scroll end plate 41, and surround the accommodation portion 41a and the bushing 53. In the present embodiment, the number of the anti-rotation pins 21 is six, corresponding to the number of the rings 22. FIGS. 1 and 4 illustrate two of the six anti-rotation pins 21.

As illustrated in FIG. 1, the driven scroll body 43 is integrated with the driven scroll end plate 41, and extends forward from the front surface 411 of the driven scroll end plate 41 toward the driving scroll end plate 31 and parallel to the driving axis O1 and the driven axis O2. Although not illustrated in detail, the driven scroll body 43 has a spirally extending shape centered about the center of the driven scroll end plate 41, and outwardly extending from the center of the spiral shape.

The driven mechanism 20 includes the anti-rotation pins 21 and the rings 22. The number of the anti-rotation pins 21 and the number of the rings 22 of the driven mechanism 20 may be changed as appropriate as long as each of them is three or more.

The accumulator 15 is a bottomed tubular member, and includes an outer peripheral wall 15a and a rear wall 15b. The outer peripheral wall 15a has a cylindrical shape centered about the driving axis O1. The outer diameter of the outer peripheral wall 15a is substantially the same diameter as the inner diameter of the rotor 11. The rear wall 15b is located at the rear end of the accumulator 15. The rear wall 15b has a substantially circular plate shape and is perpendicular to the driving axis O1. The outer peripheral edge of the rear wall 15b is connected to the rear end of the outer peripheral wall 15a.

A through hole 150 is formed through the rear wall 15b in the direction of the driving axis O1 at the center of the rear wall 15b. The inner diameter of the through hole 150 is slightly greater than the outer diameter of the first support portion 64 of the housing body 60. The rear wall 15b has a suction flow path 151 at a position radially outward of the through hole 150. The suction flow path 151 has a diameter smaller than the diameter of the through hole 150, and is formed through the rear wall 15b in the direction of the driving axis O1.

In the compressor 1, the front surface 351 of the cover body 35 faces the rear surface 312 of the driving scroll end plate 31, and the cover body 35 is in contact with the rear end of the driving scroll peripheral wall 32. The driving scroll end plate 31, the driving scroll peripheral wall 32, and the cover body 35 are connected to each other by a plurality of bolts 50a. Accordingly, the driving scroll end plate 31, the driving scroll peripheral wall 32, and the cover body 35 are integrated with each other.

In the compressor 1, the driven scroll 40 is accommodated in the driving scroll 30, and the driving scroll body 33 is meshed with the driven scroll body 43. Each of the anti-rotation pins 21 is inserted into the ring 22. In such a manner, the driving scroll 30 is assembled with the driven scroll 40 in the front-rear direction, so that the driving scroll 30 and the driven scroll 40 cooperate to form a scroll compression part 100. Specifically, the driving scroll body 33 is meshed with the driven scroll body 43, the anti-rotation pin 21 is inserted into the ring 22, and the driving scroll end plate 31 and the driving scroll peripheral wall 32 of the driving scroll 30 are connected to the cover body 35 by the bolts 50a.

Assembling the driving scroll 30 with the driven scroll 40 allows a suction space 30a to be formed by the driving scroll 30 and the driven scroll 40. That is, the driving scroll body 33 and the driven scroll body 43 are located within the suction space 30a. The suction space 30a is separated from the suction chamber 65 by the driving scroll end plate 31, the driving scroll peripheral wall 32, and the cover body 35.

In the driving scroll 30, the cover body 35 is located behind the driving scroll body 33, the driven scroll body 43, and the driven scroll end plate 41 in the direction of the driving axis O1. Accordingly, in the driving scroll 30, i.e., the scroll compression part 100, the cover body 35 is located furthest to the rear in the direction of the driving axis O1.

In the compressor 1, the accumulator 15 is fixed to the driving scroll 30. Specifically, the outer peripheral wall 15a of the accumulator 15 is oriented toward the cover body 35, and the front end of the outer peripheral wall 15a is in contact with the rear surface 352 of the cover body 35. The accumulator 15 is fixed to the cover body 35 by bolts 50b. Accordingly, the accumulator 15 is integrated with the driving scroll 30.

Since the accumulator 15 is fixed to the driving scroll 30 in this way, a gas-liquid separation chamber 16 is defined in the accumulator 15 by the outer peripheral wall 15a and the rear wall 15b of the accumulator 15 and the cover body 35. The gas-liquid separation chamber 16 is in communication with the suction space 30a through the suction passage 35a and the supply passage 35b.

In the accumulator 15, the outer peripheral wall 15a is inserted into the rotor 11, and fixed to the inner peripheral surface of the rotor 11. That is, the accumulator 15 is disposed inside the rotor 11, and fixed to both the driving scroll 30 and the rotor 11. Accordingly, the accumulator 15 is rotatable together with the rotor 11, and the driving scroll 30 is also rotatable with the rotation of the accumulator 15.

The first support portion 64 of the housing body 60 is inserted through the through hole 150 of the rear wall 15b of the accumulator 15. The accumulator 15 is accommodated in the suction chamber 65 and is rotatably supported by the first support portion 64 in the gas-liquid separation chamber 16. The gas-liquid separation chamber 16 is in communication with the suction chamber 65 through the suction flow path 151. The gas-liquid separation chamber 16 is in communication with the reflux passage 8.

The front portion of the first support portion 64 is inserted into the plain bearing 51, i.e., the second boss 36 of the driving scroll 30. Accordingly, the cover body 35 is rotatably supported by the first support portion 64 via the plain bearing 51.

In the driving scroll 30, the first boss 34 of the driving scroll end plate 31 is fitted into the inner ring of the needle bearing 14, whereby the first boss 34 is rotatably supported by the second support portion 67 of the housing cover 61 via the needle bearing 14. In this way, the first boss 34 is supported by the second support portion 67, so that the discharge chamber 13 is formed of a space defined by the inner peripheral surface of the first boss 34, the housing cover 61, and the driving scroll end plate 31 in the housing 6.

Accordingly, the driving scroll 30 is supported by both the first support portion 64 and the second support portion 67 of the housing 6 such that the driving scroll 30 is rotatable about the driving axis O1.

In the driven scroll 40, the driven pin 55 is inserted into the pin hole 4 of the first support portion 64. Accordingly, the driven scroll 40 is rotatably supported by the first support portion 64 such that the driven scroll 40 is rotated by the driven pin 55 about the driven axis O2. That is, unlike the driving scroll 30, the driven scroll 40 is supported only by the first support portion 64 of the housing 6 such that the driven scroll 40 is rotatable about the driven axis O2.

The driven axis 02 is eccentric to the driving axis O1. The driven scroll 40 is supported by the housing 6 such that the driven scroll 40 is rotatable about the driven axis O2, and is eccentric to and accommodated in the driving scroll 30.

The compressor 1 is used for an air conditioning device 200 illustrated in FIGS. 2 and 3. The air conditioning device 200 includes the compressor 1, and further includes: a condenser 101, an external heat exchanger 102, an evaporator 103, a receiver 104, a first flow switching valve 105, a second flow switching valve 106, a first expansion valve 107, a second expansion valve 108, an on-off valve 109, and pipes H1 to H10. The first flow switching valve 105 and the second flow switching valve 106 are specifically three-way valves.

The discharge communication port 68 of the compressor 1 is connected to an inlet 101a of the condenser 101 by the pipe H1. An outlet 101b of the condenser 101 is connected to the first flow switching valve 105 by the pipe H2. The first flow switching valve 105 is connected to an inlet 102a of the external heat exchanger 102 by the pipe H3. An outlet 102b of the external heat exchanger 102 is connected to the second flow switching valve 106 by the pipe H4.

The second flow switching valve 106 is connected to the receiver 104 by the pipe H5. The receiver 104 is connected to an inlet 103a of the evaporator 103 by the pipe H6. An outlet 103b of the evaporator 103 is connected to the suction communication port 69 of the compressor 1 by the pipe H7.

The first flow switching valve 105 is connected to one end of the pipe H8, and the other end of the pipe H8 is connected to the pipe H6. The pipe H3 is connected to one end of the pipe H9, and the other end of the pipe H9 is connected to the pipe H5. The second flow switching valve 106 is connected to one end of the pipe H10, and the other end of the pipe H10 is connected to the pipe H7.

The first expansion valve 107 is provided in the pipe H3. The second expansion valve 108 is provided in the pipe H6. The on-off valve 109 is provided in the pipe H9. Although not illustrated, the compressor 1, the first flow switching valve 105 and the second flow switching valve 106, the first expansion valve 107 and the second expansion valve 108, and the on-off valve 109 are connected to a control device (not illustrated) mounted on the vehicle.

When the air conditioning device 200 is in cooling operation, as illustrated in FIG. 2, the first flow switching valve 105 connects the pipe H2 and the pipe H3, and disconnects the pipes H2, H3 from the pipe H8. The second flow switching valve 106 connects the pipe H4 and the pipe H5, and disconnects the pipes H4, H5 from the pipe H10. The opening degree of the first expansion valve 107 and the opening degree of the second expansion valve 108 are adjusted, and the on-off valve 109 is closed. During the cooling operation, the opening degree of the first expansion valve 107 is almost at maximum.

Accordingly, in the air conditioning device 200, the refrigerant discharged from the compressor 1 flows into the external heat exchanger 102 through the pipe H1, the condenser 101, the pipe H2, and the pipe H3 in this order. The heat of the refrigerant is transferred to the air surrounding the external heat exchanger 102, i.e., the air outside the vehicle. That is, in the external heat exchanger 102, the refrigerant is cooled by transferring the heat of the refrigerant to the air outside the vehicle. The refrigerant from which the heat is transferred in the external heat exchanger 102 flows out from the external heat exchanger 102 into the evaporator 103 through the pipe H4, the pipe H5, the receiver 104, and the pipe H6 in this order. At this time, the opening degree of the second expansion valve 108 is appropriately adjusted to adjust the pressure of the refrigerant flowing from the pipe H6 into the evaporator 103.

The air surrounding the evaporator 103 is cooled by the refrigerant in the evaporator 103 through transfer of heat from the air surrounding the evaporator 103. The cooled air is supplied to the compartment of the vehicle, so that the compartment is cooled. The refrigerant from which the heat is transferred in the evaporator 103 flows out from the evaporator 103 into the compressor 1 through the pipe H7. During the cooling operation, the air surrounding the condenser 101 is heated by transfer of the heat from the refrigerant flowing through the condenser 101. However, the heated air is not supplied to the compartment of the vehicle.

When the air conditioning device 200 is in heating operation, as illustrated in FIG. 3, the first flow switching valve 105 connects the pipe H2 and the pipe H8, and disconnects the pipes H2, H8 from the pipe H3. The second flow switching valve 106 connects the pipe H4 and the pipe H10, and disconnects the pipes H4, H10 from the pipe H5. The opening degree of the first expansion valve 107 is adjusted, and the on-off valve 109 is opened.

Accordingly, in the air conditioning device 200, the refrigerant is discharged from the compressor 1 and flows into the condenser 101 through the pipe H1. The air surrounding the condenser 101 is heated by the refrigerant in the condenser 101 through the transfer of the heat to the air surrounding the condenser 101. The heated air is supplied to the compartment of the vehicle, so that the compartment is heated.

The refrigerant from which the heat is transferred in the condenser 101 flows out from the condenser 101 into the external heat exchanger 102 through the pipe H2, the pipe H8, the pipe H6, the receiver 104, the pipe H5, the pipe H9, and the pipe H3 in this order. At this time, the opening degree of the first expansion valve 107 is appropriately adjusted to adjust the pressure of the refrigerant flowing from the pipe H3 into the external heat exchanger 102. The refrigerant in the external heat exchanger 102 is heated through the transfer of heat from the air outside the vehicle. The refrigerant to which the heat is transferred in the external heat exchanger 102 flows out from the external heat exchanger 102 into the compressor 1 through the pipe H4, the pipe H10, and the pipe H7 in this order.

Specifically, in the operation of the compressor 1, as illustrated in FIG. 1, the electric motor 10 operates so that the rotor 11 rotates, causing the accumulator 15 to rotate about the driving axis O1 in the suction chamber 65. The driving scroll 30 is also rotated about the driving axis O1 in the suction chamber 65 by the rotation of the accumulator 15. That is, in this compressor, although the rotor 11 is not in contact with the driving scroll 30, the rotation of the rotor 11 is transmitted to the driving scroll 30 via the accumulator 15.

In the driven mechanism 20, each of the anti-rotation pins 21 slides on the inner peripheral surface of the ring 22 with the rotations of the accumulator 15 and the driving scroll 30, and allows the ring 22 to rotate relative to the anti-rotation pin 21 about the axis of the anti-rotation pin 21. Thus, the driven mechanism 20 transmits torque of the driving scroll 30 to the driven scroll 40.

Accordingly, the driven scroll 40 is driven to rotate about the driven axis O2 by the driving scroll 30 and the driven mechanism 20. The driven mechanism 20 prevents the driven scroll 40 from rotating on its own axis. Accordingly, the driven scroll 40 orbits relative to the driving scroll 30 about the driven axis O2. The driving scroll body 33 and the driven scroll body 43 rotate in the suction space 30a such that the driving scroll body 33 and the driven scroll body 43 come into contact with each other. The driving scroll body 33 and the driven scroll body 43 therefore form a compression chamber 12 therebetween.

The refrigerant is drawn into the suction chamber 65 from the outside of the compressor 1 through the pipe H7 and the suction communication port 69 with the rotations of the driving scroll 30 and the driven scroll 40, as indicated by the dashed arrow in FIG. 1. As previously described, the refrigerant is cooled in the external heat exchanger 102 when the air conditioning device 200 is in the cooling operation. Accordingly, during the cooling operation, the refrigerant is partly liquefied in the external heat exchanger 102 and stored as a liquid refrigerant in the external heat exchanger 102. In the air conditioning device 200, the external heat exchanger 102 is connected to the compressor 1 via the pipe H4, the pipe H5, the receiver 104, the pipe H6, the evaporator 103, and the pipe H7 during the cooling operation, whereas during the heating operation, the external heat exchanger 102 is connected to the compressor 1 via the pipe H4, the pipe H10, and the pipe H7.

Therefore, when the air conditioning device 200 is switched from the cooling operation to the heating operation, the refrigerant drawn into the suction chamber 65 through the pipe H7 and the suction communication port 69 may include not only the gaseous refrigerant, which is a vapor phase refrigerant, but also the liquid refrigerant stored in the external heat exchanger 102. The refrigerant drawn into the suction chamber 65 through the pipe H7 and the suction communication port 69 contains lubricating oil 18. For example, the cooling operation may be switched to the heating operation during the transition from summer to winter, and the cooling operation may be temporarily switched to the heating operation in the summer if the temperature in the vehicle is mistakenly set.

In the compressor 1, the refrigerant is drawn into the suction chamber 65 through the pipe H7 and the suction communication port 69, and the gas-liquid separation chamber 16 of the accumulator 15 receives the refrigerant from the suction chamber 65 through the suction flow path 151. The gas-liquid separation chamber 16 allows the refrigerant to be separated into a gaseous refrigerant and a liquid refrigerant. In the compressor 1, the refrigerant that has flowed through the pipe H7 and the suction communication port 69 is not directly drawn into the gas-liquid separation chamber 16, but is drawn into the gas-liquid separation chamber 16 through the suction chamber 65.

That is, in the compressor 1, the refrigerant is drawn into the suction chamber 65 from the outside of the compressor 1, and initially separated into the gaseous refrigerant and the liquid refrigerant in the suction chamber 65. Then, the refrigerant is drawn from the suction chamber 65 into the gas-liquid separation chamber 16 through the suction flow path 151, and subsequently separated into the gaseous refrigerant and the liquid refrigerant in the gas-liquid separation chamber 16. In the compressor 1, the refrigerant is initially separated into the gaseous refrigerant and the liquid refrigerant in the suction chamber 65, so that the refrigerant drawn into the gas-liquid separation chamber 16 is less likely to include the liquid refrigerant, compared to a configuration in which the refrigerant is directly drawn into the gas-liquid separation chamber 16 from the outside of the compressor 1 through the pipe H7 and the suction communication port 69 and the refrigerant is separated into the gaseous refrigerant and the liquid refrigerant only in the gas-liquid separation chamber 16.

In addition to the lubricating oil 18 that is already present in the suction chamber 65, a portion of the lubricating oil 18 contained in the refrigerant that has been drawn into the suction chamber 65, and a portion of the liquid refrigerant separated from the refrigerant in the suction chamber 65 are stored at the bottom of the suction chamber 65 due to gravity.

In the compressor 1, the accumulator 15 is rotated about the driving axis O1 in the suction chamber 65 by the rotor 11. This causes the refrigerant drawn into the gas-liquid separation chamber 16 to be suitably separated into the gaseous refrigerant and the liquid refrigerant under the influence of the centrifugal force of the rotating accumulator 15. The liquid refrigerant separated from the gaseous refrigerant tends to remain in the gas-liquid separation chamber 16 on the radially outer side of the accumulator 15, i.e., on the radially outer side of the driving scroll 30 and the driven scroll 40 due to the centrifugal force. The lubricating oil 18 tends to remain in the gas-liquid separation chamber 16 in the same manner as the liquid refrigerant.

In the compressor 1, the cover body 35 of the driving scroll 30 has the suction passage 35a and the supply passage 35b. This configuration allows the gaseous refrigerant in the gas-liquid separation chamber 16 to be suitably drawn into the compression chamber 12 from the suction space 30a through the suction passage 35a. The compression chamber 12 compresses the gaseous refrigerant while reducing its volume with the rotation of the driving scroll 30 and the rotation of the driven scroll 40. Thus, the gaseous refrigerant compressed to a discharge pressure is discharged from the discharge port 38 into the discharge chamber 13, and further discharged to the outside of the compressor 1, i.e., the condenser 101, through the pipe H1 connected to the discharge communication port 68.

In the cover body 35, the suction passage 35a is located inward of the supply passage 35b in the radial direction of the driving scroll 30. This configuration of the compressor 1 prevents the liquid refrigerant in the gas-liquid separation chamber 16 from being drawn into the compression chamber 12 through the suction space 30a, even when a large amount of the liquid refrigerant is present in the gas-liquid separation chamber 16. Furthermore, since the suction passage 35a is in communication with the gas-liquid separation chamber 16, the liquid refrigerant in the suction chamber 65 is not drawn into the suction passage 35a, and thus into the compression chamber 12, without flowing through the gas-liquid separation chamber 16. Accordingly, the compressor 1 is less likely to compress the liquid refrigerant in the compression chamber 12.

The gaseous refrigerant drawn into the compression chamber 12 through the suction passage 35a contains a portion of the lubricating oil 18. The supply passage 35b is located outward of the suction passage 35a in the radial direction of the driving scroll 30. The supply passage 35b opens to the gas-liquid separation chamber 16 at a position close to a region where the lubricating oil 18 is present in the gas-liquid separation chamber 16. This allows the lubricating oil 18 in the gas-liquid separation chamber 16 to be suitably drawn into the compression chamber 12 through the supply passage 35b. Accordingly, in the compressor 1, the compression chamber 12 is lubricated by the lubricating oil 18. Therefore, the driving scroll end plate 31, the driving scroll body 33, the driven scroll end plate 41, and the driven scroll body 43 of the compressor are less likely to wear.

The liquid refrigerant in the gas-liquid separation chamber 16 may partly flow through the supply passage 35b together with the lubricating oil 18. However, the liquid refrigerant is vaporized, while the liquid refrigerant flows through the supply passage 35b, by the heat of the driving scroll 30 and the driven scroll 40 generated when the compressor 1 is in operation. Accordingly, the compressor 1 suitably prevents the liquid refrigerant in the gas-liquid separation chamber 16 from being drawn into the compression chamber 12 through the supply passage 35b. It is the same in a case where the liquid refrigerant inevitably flows through the suction passage 35a.

Therefore, the compressor 1 according to the first embodiment has excellent reliability.

In particular, in the compressor 1, the first support portion 64 has the reflux passage 8, and the reflux passage 8 is in communication with the gas-liquid separation chamber 16 by the accumulator 15 being supported by the first support portion 64. The reflux passage 8 is in communication with the bottom of the suction chamber 65 through the first guide passage 62a and the second guide passage 62b of the attachment 62. This configuration of the compressor 1 allows the lubricating oil 18 stored at the bottom of the suction chamber 65 to flow into the gas-liquid separation chamber 16 through the first guide passage 62a, the second guide passage 62b, and the reflux passage 8. The lubricating oil 18 is suitably supplied to the compression chamber 12 through the supply passage 35b. Accordingly, in the compressor 1, the compression chamber 12 is suitably lubricated. Although a portion of the liquid refrigerant separated in the suction chamber 65 and stored at the bottom of the suction chamber 65 may flow into the gas-liquid separation chamber 16 together with the lubricating oil 18 flowing through the first guide passage 62a, the second guide passage 62b, and the reflux passage 8, as previously described, in the compressor 1, the liquid refrigerant in the gas-liquid separation chamber 16 is less likely to be drawn into the compression chamber 12 through the suction passage 35a and the supply passage 35b.

In the compressor 1, the accumulator 15 is fixed to the cover body 35 of the driving scroll 30 and disposed inside the rotor 11, and the accumulator 15 is fixed to the inner peripheral surface of the rotor 11. Accordingly, the accumulator 15 is not entirely placed outside the rotor 11 in the compressor 1. This configuration of the compressor 1 reduces the need for elongation of the housing 6 in the direction of the driving axis O1. In addition, the compressor 1 is capable of transmitting the power of the rotor 11 to the driving scroll 30 via the accumulator 15, so that it is unnecessary to directly connect the rotor 11 and the driving scroll 30 for power transmission. Accordingly, this configuration allows for greater design flexibility of the driving scroll 30 of the compressor 1. Therefore, this configuration of the compressor 1 allows an increase in the diameters of the driving scroll 30 and the driven scroll 40 so as to suitably secure the volume of the compression chamber 12, while reducing the need for an increase in the diameter of the housing 6 as much as possible.

Second Embodiment

FIG. 4 illustrates the compressor 2 according to the second embodiment including an accumulator 25, instead of the accumulator 15. In the compressor 2, the cover body 35 of the driving scroll 30 has a supply passage 35c, instead of the supply passage 35b. The supply passage 35c is located outward of the suction passage 35a in the radial direction of the cover body 35. The supply passage 35c is formed through the cover body 35 in the front-rear direction and parallel to the driving axis O1.

The accumulator 25 is a bottomed tubular member, and includes an outer peripheral wall 25a and a rear wall 25b. The outer peripheral wall 25a has a cylindrical shape centered about the driving axis O1. The outer diameter of the outer peripheral wall 25a is greater than that of the outer peripheral wall 15a of the accumulator 15 of the compressor 1 according to the first embodiment, and is substantially the same diameter as the outer diameter of the cover body 35. The rear wall 25b is located at the rear end of the accumulator 25, and the rear wall 25b has a substantially circular plate shape and is perpendicular to the driving axis O1. The outer peripheral edge of the rear wall 25b is connected to the rear end of the outer peripheral wall 25a.

The rear wall 25b has a through hole 250 and a suction flow path 251 at the center of the rear wall 25b. The through hole 250 and the suction flow path 251 have a structure similar to the structure of the through hole 150 and the suction flow path 151 of the accumulator 15.

Similar to the compressor according to the first embodiment, in the compressor 2, the accumulator 25 is fixed to the cover body 35 by the bolts 50b. Accordingly, a gas-liquid separation chamber 26 is defined in the accumulator 25 by the outer peripheral wall 25a and the rear wall 25b of the accumulator 25 and the cover body 35. The gas-liquid separation chamber 26 is in communication with the suction passage 35a and the supply passage 35c.

The accumulator 25 is accommodated in the suction chamber 65 and rotatably supported by the first support portion 64. The gas-liquid separation chamber 26 is in communication with the suction chamber 65 through the suction flow path 251, and also in communication with the reflux passage 8.

In the compressor 2, the electric motor 10 is located in front of the accumulator 25 within the suction chamber 65. The driving scroll peripheral wall 32 of the driving scroll 30 is inserted into the rotor 11, and fixed to the inner peripheral surface of the rotor 11. It is to be noted that, other components of the compressor 2 according to the second embodiment are the same as those of the compressor 1 according to the first embodiment, and the components of the second embodiment that correspond to those of the first embodiment are designated by the same reference numerals and will not be further elaborated here.

Similar to the compressor 1 according to the first embodiment, the compressor 2 is also used for the air conditioning device 200 (see FIGS. 2 and 3). In the compressor 2, the driving scroll 30 and the accumulator 25 are rotated about the driving axis O1 in the suction chamber 65 by the rotation of the rotor 11. The refrigerant is drawn into the suction chamber 65 from the outside of the compressor 1 through the pipe H7 and the suction communication port 69 as indicated by the dashed arrow in FIG. 4 and separated into the gaseous refrigerant and the liquid refrigerant. The refrigerant in the suction chamber 65 is drawn into the gas-liquid separation chamber 26 through the suction flow path 251, and the liquid refrigerant is separated from the refrigerant in the gas-liquid separation chamber 26. The gaseous refrigerant and the lubricating oil 18 in the gas-liquid separation chamber 26 are drawn into the compression chamber 12 through the suction passage 35a and the supply passage 35c. The compressor 2 is also capable of exhibiting the same effects as those of the compressor 1 according to the first embodiment.

In the compressor 2, the driving scroll peripheral wall 32 is disposed inside the rotor 11 and fixed to the inner peripheral surface of the rotor 11, and the accumulator 25 is fixed to the cover body 35 of the driving scroll 30. This configuration of the compressor 2 eliminates the need to place the accumulator 25 inside the rotor 11, thereby increasing the design flexibility of the accumulator 25. In the compressor 2, the diameter of the accumulator 25 is greater than that of the accumulator 15 of the compressor 1 according to the first embodiment, which suitably secures the volume of the gas-liquid separation chamber 26. This facilitates centrifugal separation of the liquid refrigerant and the lubricating oil 18 in the gas-liquid separation chamber 26.

In addition, the compressor 2 is capable of transmitting the power of the rotor 11 to the accumulator 25 via the driving scroll 30, so that it is unnecessary to directly connect the rotor 11 and the accumulator 25 for power transmission. In this regard, the configuration of the compressor 2 increases the design flexibility of the accumulator 25.

Although the present disclosure has been described by the first and second embodiments, the present disclosure is not limited to those embodiments, and may be modified within the scope of the present disclosure.

For example, in the compressor 1 according to the first embodiment, both the cover body 35 and the driven scroll end plate 41 may have the suction passage 35a, and both the cover body 35 and the driven scroll end plate 41 may have the supply passage 35b. The same applies to the compressor 2 according to the second embodiment.

In the compressor 1 according to the first embodiment, the driven scroll 40 is accommodated in the driving scroll 30 and assembled with the driving scroll 30. However, the present disclosure is not limited thereto, and the driven scroll 40 may be disposed outside the driving scroll 30 and assembled with the driving scroll 30. In this configuration, the driven scroll end plate 41 may have the suction passage 35a and the supply passage 35b and may be fixed to the accumulator 15. The same applies to the compressor 2 according to the second embodiment.

In the compressor 1 according to the first embodiment, the driving scroll 30 may be connected to the rotor 11 via a drive shaft for power transmission, so that the driving scroll 30 and the accumulator 15 are spaced apart from the rotor 11 in the direction of the driving axis O1. The same applies to the compressor 2 according to the second embodiment.

In the compressor 1 according to the first embodiment, the driven mechanism 20 includes the anti-rotation pins 21 and the rings 22. However, the present disclosure is not limited thereto, and the driven mechanism 20 may be formed by a pin-ring-pin mechanism in which two pins slide on an inner peripheral surface of one free ring, a pin-and-pin mechanism in which outer peripheral surfaces of two pins slide on each other, a mechanism using Oldham's shaft coupling, or the like. The same applies to the compressor 2 according to the second embodiment.

This specification also includes the following disclosure.

Supplementary Note 1

A co-rotating scroll compressor comprising: a housing; a driving mechanism; a driving scroll; a driven scroll; and a driven mechanism, wherein

    • the housing has a suction chamber in which the driving scroll and the driven scroll are accommodated and into which a refrigerant containing lubricating oil is drawn from outside of the housing,
    • the driving scroll is configured to be driven to rotate by the driving mechanism about a driving axis,
    • the driven scroll is eccentric to the driving scroll and configured to be rotated by the driving scroll and the driven mechanism about a driven axis, and
    • the driving scroll and the driven scroll form a compression chamber for compressing the refrigerant, wherein
    • an accumulator is accommodated in the suction chamber, the accumulator being in communication with the suction chamber, the accumulator receiving the refrigerant drawn from the suction chamber and allowing the refrigerant to be separated into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil,
    • the accumulator is fixed to the driving scroll or the driven scroll and rotatable in the suction chamber, and
    • at least one of the driving scroll and the driven scroll has a suction passage which is in communication with the accumulator and through which the gaseous refrigerant in the accumulator is drawn into the compression chamber.

Supplementary Note 2

The co-rotating scroll compressor according to supplementary note 1, wherein the housing has a support portion that extends into the suction chamber and supports the accumulator such that the accumulator is rotatable, and

    • the support portion has a reflux passage through which the lubricating oil in the suction chamber flows into the accumulator.

Supplementary Note 3

The co-rotating scroll compressor according to supplementary note 1 or 2, wherein at least one of the driving scroll and the driven scroll has a supply passage through which the lubricating oil in the accumulator is supplied to the compression chamber, and

    • the supply passage is located outward of the suction passage in a radial direction of the driving scroll and a radial direction of the driven scroll, and is in communication with the accumulator.

Supplementary Note 4

The co-rotating scroll compressor according to any one of supplementary notes 1 to 3, wherein the driving mechanism includes: a stator accommodated in the suction chamber and fixed to the housing; and a rotor having a cylindrical shape and rotatably disposed inside the stator, and

    • the accumulator is fixed to the driving scroll, and disposed inside the rotor.

Supplementary Note 5

The co-rotating scroll compressor according to any one of supplementary notes 1 to 3, wherein the driving mechanism includes: a stator accommodated in the suction chamber and fixed to the housing; and a rotor having a cylindrical shape and rotatably disposed in the stator,

    • the driving scroll is disposed inside the rotor, and
    • the accumulator is fixed to the driving scroll.

Industrial Applicability

The present disclosure is applicable to an air conditioning device and the like for a vehicle.

REFERENCE SIGNS LIST

    • 1, 2 compressor (co-rotating scroll compressor)
    • 6 housing
    • 8 reflux passage
    • 10 electric motor (driving mechanism)
    • 11 rotor
    • 12 compression chamber
    • 15, 25 accumulator
    • 17 stator
    • 18 lubricating oil
    • 20 driven mechanism
    • 30 driving scroll
    • 35a suction passage
    • 35b, 35c supply passage
    • 40 driven scroll
    • 64 first support portion (support portion)
    • 65 suction chamber
    • O1 driving axis
    • O2 driven axis

Claims

1: A co-rotating scroll compressor comprising: a housing; a driving mechanism; a driving scroll; a driven scroll; and a driven mechanism, wherein

the housing has a suction chamber in which the driving scroll and the driven scroll are accommodated and into which a refrigerant containing lubricating oil is drawn from outside of the housing,
the driving scroll is configured to be driven to rotate by the driving mechanism about a driving axis,
the driven scroll is eccentric to the driving scroll and configured to be rotated by the driving scroll and the driven mechanism about a driven axis, and
the driving scroll and the driven scroll form a compression chamber for compressing the refrigerant, wherein
an accumulator is accommodated in the suction chamber, the accumulator being in communication with the suction chamber, the accumulator receiving the refrigerant drawn from the suction chamber and allowing the refrigerant to be separated into a gaseous refrigerant and a liquid refrigerant containing the lubricating oil,
the accumulator is fixed to the driving scroll or the driven scroll and rotatable in the suction chamber, and
at least one of the driving scroll and the driven scroll has a suction passage which is in communication with the accumulator and through which the gaseous refrigerant in the accumulator is drawn into the compression chamber.

2: The co-rotating scroll compressor according to claim 1, wherein the housing has a support portion that extends into the suction chamber and supports the accumulator such that the accumulator is rotatable, and

the support portion has a reflux passage through which the lubricating oil in the suction chamber flows into the accumulator.

3: The co-rotating scroll compressor according to claim 1, wherein at least one of the driving scroll and the driven scroll has a supply passage through which the lubricating oil in the accumulator is supplied to the compression chamber, and

the supply passage is located outward of the suction passage in a radial direction of the driving scroll and a radial direction of the driven scroll, and is in communication with the accumulator.

4: The co-rotating scroll compressor according to claim 1, wherein the driving mechanism includes: a stator accommodated in the suction chamber and fixed to the housing; and a rotor having a cylindrical shape and rotatably disposed inside the stator, and

the accumulator is fixed to the driving scroll, and disposed inside the rotor.

5: The co-rotating scroll compressor according to claim 1, wherein the driving mechanism includes: a stator accommodated in the suction chamber and fixed to the housing; and a rotor having a cylindrical shape and rotatably disposed in the stator,

the driving scroll is disposed inside the rotor, and
the accumulator is fixed to the driving scroll.
Patent History
Publication number: 20260348381
Type: Application
Filed: Feb 28, 2024
Publication Date: Nov 5, 2026
Applicant: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI (Kariya-shi, Aichi)
Inventors: Yosuke INAGAKI (Kariya-shi, Aichi), Kazunari HONDA | (Kariya-shi, Aichi), Hiroyuki KOBAYASHI (Kariya-shi, Aichi), Yuji HASHIMOTO (Kariya-shi, Aichi), Akito SUGAHARA (Kariya-shi, Aichi), Keishiro MUTO (Kariya-shi, Aichi)
Application Number: 19/485,882
Classifications
International Classification: F04C 18/02 (20060101); F04C 29/02 (20060101); F04C 29/12 (20060101);