JP2024107631A - Double-rotating scroll compressor - Google Patents

Abstract

To provide a double rotary type scroll compressor excellent in durability.SOLUTION: A double rotary type scroll compressor includes a driving scroll 30 having a driving spiral body 33, and a driven scroll 40 having a driven spiral body 43. The driving spiral body 33 and the driven spiral body 43 form a compression chamber 12. The driving scroll 30 or the driven scroll 40 is provided with a suction port 9 and an outflow preventing wall 37. The suction port 9 is constructed by the outflow preventing wall 37. The outflow preventing wall 37 extends to a radial inside further than an end 330, 430 on a radial outside of the driving spiral body 33 or the driven spiral body 43.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 (hereinafter simply referred to as a compressor). This compressor includes a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism. The housing is provided with a main frame, which divides the housing into a scroll chamber and a low-pressure chamber. The scroll chamber contains the drive scroll, the driven scroll, and the driven mechanism. The low-pressure chamber contains the drive mechanism. The main frame is also formed with an intake port that connects the low-pressure chamber to the scroll chamber. Furthermore, the housing is provided with an intake pipe that connects the low-pressure chamber to the outside of the housing.

The driving scroll has a driving end plate, a driving scroll, and a driving shaft. The driving shaft is rotatably supported by the main frame, extends into the low pressure chamber, and is fixed to the driving mechanism. The driven scroll has a driven end plate and a driven scroll. The driving scroll and the driven scroll face each other. The driving scroll and the driven scroll come into contact with each other to form a compression chamber between them. The driven mechanism is disposed between the driving scroll and the driven scroll.

In this compressor, the drive scroll is driven to rotate about the drive axis by the drive mechanism, and the driven scroll is driven to rotate about the driven axis by the drive scroll and the driven mechanism. Refrigerant is drawn into the low pressure chamber from outside the housing through the suction pipe, and this refrigerant is then drawn into the scroll chamber through the suction port. In this compressor, the drive scroll, which is driven to rotate, and the driven scroll, which is driven to rotate, bring the drive scroll and the driven scroll into contact with each other, forming a compression chamber between them. As the drive scroll and the driven scroll rotate, the drive scroll and the driven scroll change the volume of the compression chamber, compressing the refrigerant in the compression chamber.

Japanese Patent Application Publication No. 4-76287

However, in the above conventional compressor, the refrigerant drawn into the scroll chamber from the suction port is affected by the rotating drive scroll and driven scroll, and the lubricating oil contained in the refrigerant may be separated from the refrigerant by centrifugal separation. As a result, the refrigerant compressed in the compression chamber does not contain enough lubricating oil, and the drive scroll and driven scroll cannot be adequately lubricated by the lubricating oil. As a result, in this compressor, the drive scroll and driven scroll, including the drive scroll and driven scroll, are prone to wear, raising concerns about durability.

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 with excellent durability.

The double-rotating scroll compressor of the present invention comprises a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism,
The housing has a scroll chamber in which the driving scroll and the driven scroll are accommodated,
The driving scroll is rotated about a drive axis by the driving mechanism,
The driven scroll is rotated around a driven axis by the driving scroll and the driven mechanism while being eccentric with respect to the driving scroll,
The drive scroll has a drive end plate and a drive scroll that is integral with the drive end plate and protrudes in a spiral shape toward the driven scroll,
The driven scroll has a driven end plate facing the driving scroll, and a driven scroll integral with the driven end plate and protruding in a spiral shape toward the driving end plate,
A double-rotating scroll compressor in which a compression chamber for compressing a refrigerant is formed by the driving scroll and the driven scroll,
The drive scroll and the driven scroll form a suction portion that draws the refrigerant into the compression chamber,
The housing is provided with a cylindrical protrusion protruding into the scroll chamber in the drive axial direction toward the drive scroll and the driven scroll,
The driving scroll or the driven scroll is provided with a supported portion that is supported by the housing while entering the protruding portion, a suction port that allows the refrigerant to be sucked into the suction portion, and an outflow prevention wall that extends from the outside of the protruding portion toward the protruding portion in the radial direction of the driving scroll and the driven scroll and prevents lubricating oil contained in the refrigerant sucked from the suction port from flowing out into the scroll chamber,
The intake port is constituted by the outflow prevention wall,
The outflow prevention wall is characterized in that it extends radially inward beyond a radially outer end of the driving scroll or the driven scroll.

In the double-rotating scroll compressor of the present invention, refrigerant is drawn into the suction section from the suction port. The refrigerant drawn into the suction section is then trapped and compressed in the compression chamber formed by the driving scroll and the driven scroll.

Here, in this compressor, the suction port is configured with an outflow prevention wall. Therefore, the outflow prevention wall exists around the suction port, and the suction port is located radially inward of the outflow prevention wall. Therefore, the refrigerant drawn into the suction port flows from the inside to the outside in the radial direction, and is drawn into the suction section and ultimately the compression chamber. As a result, in this compressor, even if the lubricating oil contained in the refrigerant is affected by the rotating driving scroll and the rotating driven driven scroll and tries to splash toward the outside in the radial direction of the driving scroll and the driven scroll, this lubricating oil can easily flow from the suction port to the suction section and ultimately the compression chamber together with the refrigerant.

In addition, in this compressor, the outflow prevention wall extends radially inward beyond the radially outer end of the driving scroll or the driven scroll. Therefore, the outflow prevention wall can effectively prevent the lubricating oil separated by centrifugal force from the refrigerant from flowing out from the suction section into the scroll chamber. Therefore, such lubricating oil can also be circulated into the compression chamber together with the refrigerant newly flowing from the suction port toward the suction section.

As a result, this compressor is less likely to suffer from insufficient lubrication within the compression chamber, and the lubricating oil can effectively lubricate the drive scroll and driven scroll, including the drive scroll and driven scroll.

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

In the compressor of the present invention, it is preferable that the protrusion extends into the inside of the suction port. In this case, the driving scroll or driven scroll and the protrusion can be arranged close to each other, so that the compressor can be made compact. Also, as described above, since the suction port is formed by the outflow prevention wall, the protrusion extends into the inside of the suction port, so that the outflow prevention wall and the protrusion face each other in the radial direction.

The inside of the protrusion can be a suction passage through which the refrigerant can flow toward the suction port. The suction port and the suction passage can be connected while facing each other in the drive shaft direction. The inner circumferential surface of the suction passage is preferably located radially inward from the inner circumferential surface of the suction port.

In this case, the refrigerant flows through the suction passage and from the suction port to the suction section. Here, since the protrusion is provided in the housing, it does not rotate, unlike the driving scroll and the driven scroll. Therefore, an unavoidable gap is created between the protrusion and the driving scroll or the driven scroll in which the suction port and the outflow prevention wall are formed, in order to ensure the rotation of the driving scroll and the driven scroll.

In this regard, in this compressor, the inner circumferential surface of the suction passage is located radially inward from the inner circumferential surface of the suction port, so the suction passage and the above-mentioned gap can be radially separated. This makes it possible to effectively prevent the refrigerant flowing through the suction passage and the lubricating oil contained in the refrigerant from flowing into the scroll chamber through the above-mentioned gap without being sucked into the suction port.

The housing may have a storage chamber that separates the refrigerant drawn in from the outside into gas and liquid and stores liquid refrigerant containing lubricating oil therein, and a partition wall that separates the storage chamber from the scroll chamber and has a protrusion. The partition wall is preferably provided with a communication passage that connects the suction passage and the storage chamber.

In this case, the lubricating oil contained in the liquid refrigerant can also be effectively sucked into the suction section and further into the compression chamber through the suction passage and suction port. This allows the driving scroll and driven scroll to be sufficiently lubricated. Here, the liquid refrigerant flowing toward the suction section can be vaporized by the heat of the driving scroll and driven scroll during operation. This compressor therefore effectively prevents the liquid refrigerant from being sucked into the compression chamber.

The double-rotating scroll compressor of the present invention has excellent durability.

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 cross-sectional view of the main parts of the double-rotating scroll compressor of the first embodiment, showing the protrusion, the suction port, the outflow prevention wall, and the like. FIG. 3 is an enlarged cross-sectional view of the main part of the double-rotating scroll compressor of the first embodiment, showing the protrusion, the suction port, the outflow prevention wall, and the like. FIG. 4 is a cross-sectional view taken along line AA of FIG. 1 showing the driving scroll and the driven scroll at the moment when the compression chamber is formed in the double rotary scroll compressor of the first embodiment. FIG. 5 is an enlarged cross-sectional view of a main portion of a double rotary scroll compressor according to a second embodiment, similar to FIG. 3, showing a protrusion, an intake port, an outflow prevention wall, etc. FIG. 6 is a cross-sectional view of a double-rotating scroll compressor according to a third embodiment.

Below, embodiments 1 to 3 of the present invention will be described with reference to the drawings. The compressors of embodiments 1 to 3 are mounted on a vehicle (not shown) and form an air conditioning system for the vehicle.

Although detailed illustrations are omitted, when an air conditioner using the compressors of Examples 1 to 3 performs heating operation, the refrigerant discharged from the compressor flows into the condenser, where it exchanges heat with the air surrounding the condenser. This heats the air, and the heated air is supplied to the vehicle cabin. The refrigerant that flows out of the condenser then passes through an expansion valve and flows into the exterior heat exchanger, where it exchanges heat with the air outside the vehicle. The refrigerant that has thus exchanged heat in the exterior heat exchanger flows out of the exterior heat exchanger and into the compressor.

On the other hand, when this air conditioner is in cooling operation, the refrigerant discharged from the compressor passes through the condenser and flows into the exterior heat exchanger, exchanging heat with the air outside the vehicle. The refrigerant that has exchanged heat in the exterior heat exchanger flows out of the exterior heat exchanger and flows into the evaporator through an expansion valve. In the evaporator, the refrigerant exchanges heat with the air around the evaporator. This cools the air, and the cooled air is supplied to the vehicle interior. The refrigerant that has exchanged heat in the evaporator flows out of the evaporator and flows into the compressor.

Example 1
1, the compressor of the first embodiment includes a housing 6, an electric motor 10, a driving scroll 30, a driven scroll 40, and a driven mechanism 20. The electric motor 10 is an example of the "driving mechanism" in the present invention.

In this embodiment, the front-to-rear direction of the compressor is defined by the arrow shown in Figure 1. In Figures 2 and onwards, the front-to-rear direction of the compressor is defined in accordance with Figure 1. The compressor of this embodiment is mounted on the vehicle in such a position that the bottom of the pages of Figures 1 and 6 is the bottom of the compressor. Note that the front-to-rear direction is an example for ease of explanation, and the compressor can change its position as appropriate depending on the vehicle in which it is mounted.

As shown in FIG. 1, the housing 6 is composed of a housing body 60, a first housing cover 61, a second housing cover 62, and an attachment 63. The housing body 60 and the first and second housing covers 61, 62 are made of an aluminum alloy. On the other hand, the attachment 63 is made of resin.

The housing body 60 is a bottomed tubular member having a first outer peripheral wall 60a and a partition wall 60b. The first outer peripheral wall 60a is cylindrical with the drive shaft center O1 as its center. The drive shaft center O1 is parallel to the front-rear direction. The first outer peripheral wall 60a also has an inner peripheral surface 601.

As shown in FIG. 2, the partition wall 60b is located at the rear end of the housing body 60. The partition wall 60b extends in a generally circular flat plate shape perpendicular to the drive shaft center O1. The outer peripheral edge of the partition wall 60b is connected to the rear end of the first outer peripheral wall 60a. A first support portion 64 is formed at the center of the inner surface of the partition wall 60b. The first support portion 64 is generally cylindrical with the drive shaft center O1 as its center, and protrudes forward from the center of the inner surface of the partition wall 60b, that is, toward the inside of the scroll chamber 65 described later. The first support portion 64 is provided with a first plain bearing 51.

A pin hole 4 is formed in the first support portion 64. The pin hole 4 is formed in the first support portion 64 at a position eccentric to the drive axis O1. The pin hole 4 opens to the front end face of the first support portion 64 and extends linearly rearward within the first support portion 64. Here, the pin hole 4 does not penetrate the first support portion 64 in the front-rear direction. Therefore, the rear end of the pin hole 4 is located within the first support portion 64.

A protruding member 70 is fixed to the partition wall 60b. The protruding member 70 is an example of a "protruding portion" in the present invention. The protruding member 70 is made of resin. By being fixed to the partition wall 60b, the protruding member 70 is integrated with the housing main body 60 and, ultimately, the housing 6. The protruding member 70 may also be made of metal.

The protruding member 70 is composed of a main body portion 70a and an extension portion 70b. The main body portion 70a is formed in a cylindrical shape centered on the drive axis O1. More specifically, the main body portion 70a is formed in a cylindrical shape with a larger diameter than the first support portion 64. The inside of the main body portion 70a is formed as a suction passage 71. The suction passage 71 has an inner circumferential surface 710.

As shown in FIG. 3, the main body 70a has a large diameter portion 701, a small diameter portion 702, and a step 703. The large diameter portion 701 constitutes the rear of the main body 70a. The small diameter portion 702 has a smaller diameter than the large diameter portion 701. The small diameter portion 702 is continuous with the large diameter portion 701 in front of the large diameter portion 701. As a result, the small diameter portion 702 constitutes the front of the main body 70a. The step 703 is located between the large diameter portion 701 and the small diameter portion 702.

As shown in FIG. 2, the main body 70a has the first support 64 disposed within the suction passage 71 by fixing the protruding member 70 to the partition wall 60b. In other words, the main body 70a surrounds the first support 64 and the first plain bearing 51 from the outer periphery. The main body 70a protrudes from the partition wall 60b in the direction of the drive axis O1 toward the inside of the scroll chamber 65, and further toward the drive scroll 30 and the driven scroll 40, in the same manner as the first support 64. Here, the length by which the main body 70a protrudes in the direction of the drive axis O1 is shorter than the length by which the first support 64 protrudes in the direction of the drive axis O1.

The extension portion 70b is integral with the large diameter portion 701 of the main body portion 70a, and extends from the large diameter portion 701 toward the outside in the radial direction of the partition wall 60b. A connection passage 72 is formed inside the extension portion 70b. The connection passage 72 extends in the radial direction of the partition wall 60b along the extension portion 70b, and one end opens to the end face of the extension portion 70b. The other end of the connection passage 72 is connected to the suction passage 71. This allows the suction passage 71 to communicate with the connection passage 72. As a result, the suction passage 71 communicates with the scroll chamber 65 via the connection passage 72.

The partition wall 60b is also formed with a first communication port 66 and a communication passage 73. The first communication port 66 and the communication passage 73 each penetrate the partition wall 60b in the direction of the drive shaft center O1. Here, the first communication port 66 is disposed at a location outside the first support portion 64 and the main body portion 70a. Meanwhile, the communication passage 73 is disposed at a location between the first support portion 64 and the main body portion 70a. As a result, the communication passage 73 is in communication with the suction passage 71.

As shown in FIG. 1, the first housing cover 61 is disposed in front of the housing body 60. The first housing cover 61 extends in a generally circular flat plate shape perpendicular to the drive axis O1. The outer peripheral edge of the first housing cover 61 abuts against the front end of the first outer peripheral wall 60a of the housing body 60. As a result, the first housing cover 61 blocks the housing body 60 from the front. In this way, a scroll chamber 65 is formed within the housing body 60.

A second support portion 67 is formed in the center of the inner surface of the first housing cover 61. The second support portion 67 is cylindrical and centered on the drive shaft center O1, and protrudes rearward from the center of the inner surface of the first housing cover 61. The outer ring of the needle bearing 14 is fitted into the second support portion 67.

The first housing cover 61 is also formed with a discharge communication port 68. The discharge communication port 68 is located at the center of the first housing cover 61 and penetrates the first housing cover 61 in the direction of the drive shaft center O1. The discharge communication port 68 communicates with the discharge chamber 13, which will be described later. A pipe H1 is connected to the discharge communication port 68. The pipe H1 allows the refrigerant gas discharged into the discharge chamber 13 to flow toward the condenser.

The second housing cover 62 is disposed at the rear of the housing body 60. The second housing cover 62 is a bottomed tubular member having a second outer peripheral wall 62a and a rear wall 62b. The second outer peripheral wall 62a is cylindrical with its center at the drive axis O1 and extends in the direction of the drive axis O1. Here, the length of the second outer peripheral wall 62a in the direction of the drive axis O1 is shorter than the length of the first outer peripheral wall 60a of the housing body 60 in the direction of the drive axis O1.

The rear wall 62b is located at the rear end of the second housing cover 62. The rear wall 62b extends in a generally circular flat plate shape perpendicular to the drive shaft center O1. The outer peripheral edge of the rear wall 62b is connected to the rear end of the second outer peripheral wall 62a.

The second housing cover 62 has a front end of the second outer peripheral wall 62a in contact with the rear end of the partition wall 60b of the housing body 60. In the housing 6, the first housing cover 61, the housing body 60, and the second housing cover 62 are fixed in the drive shaft center O1 direction by a plurality of bolts (not shown) with the first housing cover 61 in contact with the front end of the first outer peripheral wall 60a of the housing body 60 and the second outer peripheral wall 62a of the second housing cover 62 in contact with the rear end of the partition wall 60b of the housing body 60 as described above. Thus, the front of the second housing cover 62 is blocked by the partition wall 60b. As a result, the storage chamber 8 is formed in the second housing cover 62. In the housing 6, the partition wall 60b is located between the scroll chamber 65 and the storage chamber 8 in the drive shaft center O1 direction, and separates the scroll chamber 65 from the storage chamber 8.

In addition, in the second housing cover 62, a suction communication port 69 is formed in the second outer peripheral wall 62a. The suction communication port 69 penetrates the second outer peripheral wall 62a in the radial direction of the second housing cover 62. As a result, the suction communication port 69 communicates between the storage chamber 8 and the outside of the compressor. The suction communication port 69 is connected to the piping H2. Here, when the air conditioner performs heating operation as described above, low-temperature, low-pressure refrigerant that has passed through the exterior heat exchanger flows through the piping H2. On the other hand, when the air conditioner performs cooling operation, low-temperature, low-pressure refrigerant that has passed through the evaporator flows through the piping H2. In addition, in the second outer peripheral wall 62a, the part opposite the suction communication port 69 across the drive shaft center O1, including the part farthest from the suction communication port 69 in the radial direction of the second housing cover 62 across the drive shaft center O1, constitutes the bottom of the storage chamber 8.

The attachment 63 extends perpendicular to the drive axis O1 and has a generally circular flat plate shape. The attachment 63 is attached to the partition wall 60b while being disposed within the storage chamber 8. The attachment 63 is formed with a guide path 63a and a second communication port 63b.

The guide passage 63a is recessed in the front surface of the attachment 63, i.e., the surface of the attachment 63 facing the partition wall 60b. The guide passage 63a opens at the outer periphery of the attachment 63 on the rear surface of the attachment 63, i.e., the surface of the attachment 63 facing the storage chamber 8. The guide passage 63a communicates with the communication passage 73 by attaching the attachment 63 to the partition wall 60b. As a result, the communication passage 73 and the guide passage 63a communicate with the suction passage 71 and the inside of the storage chamber 8. Here, since the guide passage 63a opens at the outer periphery of the attachment 63 on the rear surface of the attachment 63, the suction passage 71 communicates with the bottom of the storage chamber 8.

The second communication port 63b is formed in the attachment 63 at a position different from the guide passage 63a, and penetrates the attachment 63 in the direction of the drive axis O1. The second communication port 63b is aligned with the first communication port 66 and communicates with the first communication port 66 by attaching the attachment 63 to the partition wall 60b. This allows the scroll chamber 65 to communicate with the storage chamber 8 via the first communication port 66 and the second communication port 63b.

The electric motor 10 is housed in the scroll chamber 65. As a result, the scroll chamber 65 also serves as a motor chamber that houses the electric motor 10. As described below, refrigerant gas is drawn into the scroll chamber 65 from the storage chamber 8. As a result, the scroll chamber 65 also serves as a suction chamber.

The electric motor 10 is composed of a stator 17 and a rotor 11. The stator 17 is cylindrical and has a drive shaft center O1 and a winding 17a. The stator 17 is fixed to the housing body 60 by fitting into the inner circumferential surface 601 of the first outer circumferential wall 60a.

The rotor 11 is cylindrical around the drive shaft center O1 and is disposed within the stator 17. As shown in Figures 2 and 3, the rotor 11 has an inner peripheral surface 111. Although not shown in detail, the rotor 11 is composed of a number of permanent magnets corresponding to the stator 17 and laminated steel plates that secure each permanent magnet.

The driving scroll 30 shown in FIG. 1 is made of an aluminum alloy. The driving scroll 30 is housed in a scroll chamber 65. The driving scroll 30 has a driving end plate 31, a driving scroll body 33, and a cover body 35.

The driving end plate 31 extends in a generally circular plate shape perpendicular to the driving axis O1 and the driven axis O2. Here, the driven axis O2 extends parallel to the driving axis O1 while being eccentric with respect to the driving axis O1. In other words, the driven axis O2 is also parallel to the front-rear direction.

The drive end plate 31 has a front surface 311 that faces the first housing cover 61 inside the scroll chamber 65, and a rear surface 312 located on the opposite side of the front surface 311. A first boss 34 that protrudes toward the first housing cover 61 is formed in the center of the front surface 311. The first boss 34 is cylindrical and centered on the drive shaft center O1.

The drive end plate 31 also has a discharge port 38. The discharge port 38 is located in the drive end plate 31 at a location within the first boss 34, and penetrates the drive end plate 31 in the front-rear direction.

In addition, within the first boss 34, a discharge reed valve 57 and a retainer 58 are fixed to the drive end plate 31 by a fixing bolt 59. This allows the discharge reed valve 57 to open and close the discharge port 38. In addition, the retainer 58 allows the opening degree of the discharge reed valve 57 to be adjusted.

The drive scroll 33 is integral with the drive end plate 31 and extends from the rear surface 312 of the drive end plate 31 backward, i.e., toward the driven scroll 40, parallel to the drive axis O1 and the driven axis O2. As shown in FIG. 4, the drive scroll 33 extends in a spiral shape from the center of the spiral toward the outer periphery, with the center side of the drive end plate 31 being the center of the spiral. The radially outer end of the drive scroll 33 is the first end 330. The drive scroll 33 also has a first inward surface 33a facing the inside of the spiral and a first outward surface 33b facing the outside of the spiral.

As shown in FIG. 2, the cover body 35 has a main body portion 35a and a peripheral wall portion 35b. The main body portion 35a extends in a generally circular plate shape perpendicular to the drive axis O1 and the driven axis O2. A second boss 35c is formed in the center of the main body portion 35a and protrudes toward the partition wall 60b. The second boss 35c is an example of the "supported portion" in the present invention.

The second boss 35c is formed with a smaller diameter than the main body 70a of the protruding member 70, and is capable of entering the main body 70a. An insertion hole 350 is formed in the second boss 35c. The insertion hole 350 penetrates the main body 35a, including the inside of the second boss 35c, in the direction of the drive axis O1. This gives the second boss 35c a cylindrical shape centered on the drive axis O1.

A first plain bearing 51 is provided in the insertion hole 350. The first plain bearing 51 is cylindrical and centered on the drive shaft center O1, with an outer diameter approximately equal to the inner diameter of the insertion hole 350 and an inner diameter approximately equal to the outer diameter of the first support portion 64. Note that a ball bearing or the like may be used instead of the first plain bearing 51.

In addition, multiple through holes 35d are formed in the main body 35a at locations that are more outer than the second boss 35c. The through holes 35d penetrate the main body 35a in the direction of the drive axis O1. The through holes 35d are arranged at predetermined intervals in the circumferential direction of the main body 35a. The number of through holes 35d can be designed as appropriate.

Furthermore, in the main body 35a, a number of rotation prevention pins 21 are fixed in positions between the through holes 35d in a state where they protrude forward. In this embodiment, four rotation prevention pins 21 are provided. Also, in Figure 1 and other figures, two of the four rotation prevention pins 21 are illustrated.

The peripheral wall portion 35b is connected to the outer peripheral edge of the main body portion 35a. The peripheral wall portion 35b is cylindrical and centered on the drive shaft center O1, and extends forward from the main body portion 35a. The peripheral wall portion 35b has an inner peripheral surface 351.

The cover body 35 is also provided with an outflow prevention wall 37. The outflow prevention wall 37 is formed with an inlet 9. In other words, the inlet 9 is constituted by the outflow prevention wall 37. The inlet 9 penetrates the outflow prevention wall 37 in the direction of the drive shaft center O1. The inlet 9 is formed with a larger diameter than the second boss 35c and the main body portion 70a of the protruding member 70. As shown in FIG. 3, the inlet 9 has an inner peripheral surface 9a.

By forming the suction port 9 in this manner, the outflow prevention wall 37 has a ring shape with a predetermined thickness in the direction of the drive axis O1. In addition, since the outflow prevention wall 37 exists around the suction port 9, the suction port 9 is located inside the outflow prevention wall 37 in the radial direction of the driving scroll 30 and the driven scroll 40. In other words, the outflow prevention wall 37 is located outside the suction port 9 and extends linearly from the outer periphery of the outflow prevention wall 37 toward the suction port 9 in the radial direction of the driving scroll 30 and the driven scroll 40.

The outflow prevention wall 37 has a fixed surface 37a, an outer peripheral surface 37b, a rear end surface 37c, and a connection surface 37d. The fixed surface 37a is located at the front end of the outflow prevention wall 37 and extends linearly in the radial direction of the driving scroll 30 and the driven scroll 40. The outer peripheral surface 37b is located at the outer edge of the outflow prevention wall 37. The outer peripheral surface 37b is connected to the fixed surface 37a and extends linearly rearward from the fixed surface 37a in the direction of the drive axis O1. The rear end surface 37c is located at the rear end of the outflow prevention wall 37. The rear end surface 37c is connected to the outer peripheral surface 37b on the opposite side to the fixed surface 37a, and extends linearly from the outer peripheral surface 37b toward the suction port 9 in the radial direction of the driving scroll 30 and the driven scroll 40. As a result, the tip of the rear end surface 37c is connected to the inner peripheral surface 9a of the suction port 9. The connection surface 37d is located between the fixed surface 37a and the suction port 9. The connection surface 37d is connected to the fixed surface 37a on the side opposite the outer circumferential surface 37b, and extends linearly from the fixed surface 37a toward the suction port 9 in the radial direction of the driving scroll 30 and the driven scroll 40. The tip of the connection surface 37d is connected to the inner circumferential surface 9a on the side opposite the tip of the rear end surface 37c.

Here, the outflow prevention wall 37 is shaped so that its thickness in the direction of the drive axis O1 becomes thinner as it moves from the outer periphery toward the suction port 9 in the radial direction of the drive scroll 30 and the driven scroll 40. Therefore, the connection surface 37d is inclined so as to approach the rear end surface 37c in the direction of the drive axis O1 as it moves from the fixed surface 37a toward the suction port 9 in the radial direction of the drive scroll 30 and the driven scroll 40. Note that the outflow prevention wall 37 may be shaped so that its thickness in the direction of the drive axis O1 becomes constant as it moves from the outer periphery toward the suction port 9 in the radial direction of the drive scroll 30 and the driven scroll 40.

The outflow prevention wall 37 is fixed to the main body 35a with the fixing surface 37a abutting against the main body 35a on the side opposite the peripheral wall 35b of the cover body 35. As a result, the outflow prevention wall 37 is located at the rear of the cover body 35 and is integrated with the cover body 35. The outflow prevention wall 37 covers the main body 35a from the rear with the second boss 35c protruding from the suction port 9. The outflow prevention wall 37 also faces each of the through holes 35d in the direction of the drive shaft center O1.

The driven scroll 40 shown in FIG. 1 is also made of an aluminum alloy. The driven scroll 40 is housed in the scroll chamber 65, more specifically, in the driving scroll 30. The driven scroll 40 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 drive axis O1 and the driven axis O2. The driven end plate 41 has a front surface 411 and a rear surface 412. The front surface 411 faces the rear surface 312 of the drive end plate 31 inside the drive scroll 30. The rear surface 412 is located on the opposite side of the front surface 411 and faces the main body portion 35a of the cover body 35.

As shown in Figs. 2 and 3, the driven end plate 41 is formed with an accommodating recess 41a. The accommodating recess 41a is cylindrically recessed from the rear surface 412 of the driven end plate 41 toward the front. A bush 53 is provided in the accommodating recess 41a. The bush 53 may be provided in the accommodating recess 41a via a sliding bearing, a ball bearing, or the like.

Furthermore, a driven pin 55 is inserted into the bush 53. In this case, the driven pin 55 is inserted into the bush 53 at a position eccentric to the center of the bush 53, i.e., the driven axis O2. The driven pin 55 is made of steel and has a cylindrical shape. The driven pin 55 protrudes rearward from the bush 53 and, therefore, from the driven end plate 41.

Furthermore, rings 22 are fixed to the driven end plate 41 at locations on the outer periphery of the receiving recess 41a and facing each of the rotation prevention pins 21. The number of rings 22 corresponds to the number of rotation prevention pins 21. In other words, in this embodiment, the number of rings 22 is four. Also, in Figure 1 etc., two of the four rings 22 are illustrated.

As shown in FIG. 1, the driven spiral body 43 is integral with the driven end plate 41 and extends forward from the front surface 411 of the driven end plate 41, i.e., toward the driving end plate 31, parallel to the drive axis O1 and the driven axis O2. As shown in FIG. 4, the driven spiral body 43 extends in a spiral shape from the spiral center toward the outer periphery, with the center side of the driven end plate 41 being the spiral center. The radially outer end of the driven spiral body 43 is the second end 430. The driven spiral body 43 also has a second inward surface 43a facing the inside of the spiral and a second outward surface 43b facing the outside 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.

In this compressor, the rotor 11 is sandwiched between the drive end plate 31 and the peripheral wall portion 35b of the cover body 35, with the peripheral wall portion 35b facing the rear surface 312 of the drive end plate 31. With the rotor 11 sandwiched between them, the drive end plate 31, the rotor 11, and the cover body 35 are connected by a number of bolts 50. In this way, the drive scroll 30 is fixed to the rotor 11 and is integrated with the rotor 11.

In this compressor, the driven scroll 40 is housed within the driving scroll 30, while the driving scroll 33 and the driven scroll 43 are meshed. Also, each rotation prevention pin 21 is inserted into each ring 22. In this way, the driving scroll 30 and the driven scroll 40 are assembled in the front-rear direction, and the driving scroll 30 and the driven scroll 40 form the scroll compression section 100. In more detail, after the driving scroll 33 and the driven scroll 43 are meshed and each rotation prevention pin 21 is inserted into each ring 22, the driving scroll 30 connects the driving end plate 31, the rotor 11, and the cover body 35 with each bolt 50.

The drive scroll 30 and the driven scroll 40 are assembled together to form the suction section 30a. In other words, the drive scroll 33 and the driven scroll 43 are located within the suction section 30a. The suction section 30a is separated from the scroll chamber 65 by the drive end plate 31, the rotor 11, and the cover body 35. The suction section 30a is also connected to the suction port 9 through each through hole 35d of the cover body 35.

In addition, in the driving scroll 30, the cover body 35 is located rearward of the driving scroll 33 and the driven scroll 43 in the direction of the driving axis O1. Furthermore, the outflow prevention wall 37 is located on the opposite side of the driving scroll 33 and the driven scroll 43 in the direction of the driving axis O1, sandwiching the cover body 35 therebetween. Furthermore, the outflow prevention wall 37 extends from the outside of the driving scroll 33 toward the suction port 9 in the radial direction of the driving scroll 30 and the driven scroll 40. More specifically, the outflow prevention wall 37 extends radially inward of the driving scroll 30 and the driven scroll 40 from the first end 330 of the driving scroll 33 shown in FIG. 4.

As shown in FIG. 1, in the drive scroll 30, the first boss 34 of the drive end plate 31 is fitted into the inner ring of the needle bearing 14. As a result, the first boss 34 is rotatably supported by the second support portion 67 of the first housing cover 61 via the needle bearing 14. In this way, the first boss 34 is supported by the second support portion 67, and a discharge chamber 13 is formed in the housing 6 by a space surrounded by the inner circumferential surface of the first boss 34 and sandwiched between the first housing cover 61 and the drive end plate 31.

In addition, in the driving scroll 30, the first plain bearing 51 is inserted into the insertion hole 350 of the cover body 35. As a result, with the first support portion 64 inserted into the second boss 35c of the cover body 35, the second boss 35c, and therefore the cover body 35, are rotatably supported by the first support portion 64 via the first plain bearing 51. In this way, the driving scroll 30 is rotatably supported by the housing 6 around the drive axis O1 by both the first support portion 64 and the second support portion 67.

By rotatably supporting the driving scroll 30 in this manner in the housing 6, the outflow prevention wall 37 is positioned radially outward of the driving scroll 30 and the driven scroll 40 relative to the main body portion 70a of the protruding member 70. The outflow prevention wall 37 then extends radially of the driving scroll 30 and the driven scroll 40 toward the main body portion 70a.

2 and 3, in this compressor, when the cover body 35 is rotatably supported by the first support portion 64, the second boss 35c has a part of itself inserted into the main body portion 70a of the protruding member 70, that is, into the suction passage 71. At the same time, the main body portion 70a enters the suction port 9. More specifically, the small diameter portion 702 of the main body portion 70a enters the suction port 9. Therefore, the inner circumferential surface 710 of the main body portion 70a is located radially inward of the driving scroll 30 and the driven scroll 40 relative to the inner circumferential surface 9a of the suction port 9. Then, as the main body portion 70a enters the suction port 9, the outflow prevention wall 37 and the small diameter portion 702 face each other in the radial direction of the driving scroll 30 and the driven scroll 40. Furthermore, the suction passage 71 communicates with the suction port 9 and each through hole 35d. Here, the driving scroll 30 including the cover body 35 rotates around the driving axis O1, while the housing 6 including the protruding member 70 does not rotate. Therefore, between the suction port 9 and the small diameter portion 702, i.e., between the suction port 9 and the main body portion 70a, there is a gap to prevent interference between the rotating driving scroll 30 and the protruding member 70.

On the other hand, as shown in FIG. 1, in the driven scroll 40, the driven pin 55 is inserted into the pin hole 4 of the first support portion 64. As a result, the driven scroll 40 is supported by the first support portion 64 by the driven pin 55 so as to be rotatable about the driven axis O2. In other words, unlike the driving scroll 30, the driven scroll 40 is supported by the housing 6 only by the first support portion 64 so as to be rotatable about the driven axis O2.

As shown in Fig. 4, in the suction section 30a, the first inward surface 33a and the second outward surface 43b of the driving scroll 33 and the driven scroll 43 come into contact with each other, and the first outward surface 33b and the second inward surface 43a come into contact with each other, forming two compression chambers 12 between them, as shown by dotted hatching in Fig. 4. Details of each compression chamber 12 will be described later.

In the compressor configured as described above, when the air conditioner is in heating operation, the low-temperature, low-pressure refrigerant that has passed through the outdoor heat exchanger is drawn into the storage chamber 8 through the suction communication port 69 from the pipe H2, and is separated into gas and liquid in the storage chamber 8. In other words, the storage chamber 8 functions as an accumulator. As a result, the refrigerant gas, which is the refrigerant in the gas phase, flows from the storage chamber 8 through the second communication port 63b and the first communication port 66 into the scroll chamber 65, as shown by the solid arrows in Figures 1 to 3. On the other hand, the liquid refrigerant 18, which is the refrigerant in the liquid phase, is stored in the storage chamber 8. Here, the refrigerant drawn into the storage chamber 8 from the pipe H2 contains the lubricating oil 19. Therefore, the refrigerant gas flowing into the scroll chamber 65 through the first communication port 66 and the liquid refrigerant 18 in the storage chamber 8 each contain the lubricating oil 19.

In addition, in this compressor, when the electric motor 10 is operated and the rotor 11 rotates, the drive scroll 30 is rotated around the drive axis O1 in the scroll chamber 65. In other words, the drive scroll 30 and the rotor 11 rotate together. At this time, in the driven mechanism 20, each rotation prevention pin 21 slides against the inner peripheral 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 drive scroll 30 to the driven scroll 40.

As a result, the driven scroll 40 is rotated around the driven axis O2 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 own axis. This causes the driven scroll 40 to revolve around the driven axis O2 relative to the driving scroll 30.

As shown by the solid arrows in Figs. 1 to 3, the refrigerant gas in the scroll chamber 65 flows from the connecting passage 72 formed in the extension portion 70b of the protruding member 70 into the suction passage 71. The refrigerant gas in the suction passage 71 flows toward the suction port 9 and is sucked into the suction section 30a through the suction port 9 and each through hole 35d. Meanwhile, the liquid refrigerant 18 in the storage chamber 8 also flows into the suction passage 71 through the guide path 63a and the communication path 73. As a result, the liquid refrigerant 18 in the suction passage 71 is also sucked into the suction section 30a through the suction port 9 and each through hole 35d together with the refrigerant gas. In the process of being sucked into the suction section 30a, the liquid refrigerant 18 is heated and vaporized by the heat of the driving scroll 30 that rotates and the driven scroll 40 that rotates. As a result, the liquid refrigerant 18 also becomes a refrigerant gas in the process of being sucked into the suction section 30a.

In addition, as the driving scroll 30 rotates and the driven scroll 40 rotates, the driving scroll 33 and the driven scroll 43 rotate in the suction section 30a. As a result, the driving scroll 33 and the driven scroll 43 come into contact with each other as described above to form each compression chamber 12 (see FIG. 4). Here, in this compressor, the radially outermost contact points of the driving scroll 30 and the driven scroll 40 between the driving scroll 33 and the driven scroll 43 at the moment when each compression chamber 12 is formed are the first contact point P1 and the second contact point P2. More specifically, the radially outermost contact points of the driving scroll 30 and the driven scroll 40 between the first outward surface 33b of the driving scroll 33 and the second inward surface 43a of the driven scroll 43 at the moment when each compression chamber 12 is formed are the first contact point P1. In addition, the outermost contact point in the radial direction of the driving scroll 30 and the driven scroll 40 between the first inward surface 33a of the driving scroll 33 and the second outward surface 43b of the driven scroll 43 at this time is the second contact point P2.

Each compression chamber 12 thus formed is partitioned from the suction section 30a by the driving end plate 31, the driving scroll 33, the driven end plate 41, and the driven scroll 43. Therefore, the refrigerant gas present in each compression chamber 12 among the refrigerant gas sucked into the suction section 30a is confined in each compression chamber 12. Then, as the driving scroll 30 rotates and the driven scroll 40 rotates, the driving scroll 33 and the driven scroll 43 displace each compression chamber 12 toward the center of the scroll from the state shown in FIG. 4, reducing the volume. As a result, the refrigerant gas in each compression chamber 12 is compressed. Then, the refrigerant gas compressed to the discharge pressure is discharged from the discharge port 38 to the discharge chamber 13, and further discharged from the discharge communication port 68 to the pipe H1 and ultimately to the condenser. In this way, air conditioning is performed by the vehicle air conditioning device. When the refrigerant gas is discharged from the discharge port 38 into the discharge chamber 13, the compression chambers 12 merge into one.

Here, as described above, the suction port 9 is located radially inward of the driving scroll 30 and the driven scroll 40 than the outflow prevention wall 37. As a result, in this compressor, the suction port 9 is located radially inward of the driving scroll 30 and the driven scroll 40 than the first contact point P1 and the second contact point P2, which are the radially outermost contact points of the driving scroll 30 and the driven scroll 40 between the driving scroll 33 and the driven scroll 43 at the moment when each compression chamber 12 is formed. In addition, since the outflow prevention wall 37 extends radially inward of the driving scroll 30 and the driven scroll 40 than the first end 330 of the driving scroll 33, in this compressor, the outflow prevention wall 37 extends radially inward of the driving scroll 30 and the driven scroll 40 than the first contact point P1 and the second contact point P2. In other words, as shown in FIG. 2, when a virtual first reference line L1 extending in the direction of the drive axis O1 through the first contact point P1 and a virtual second reference line L2 extending in the direction of the drive axis O1 through the second contact point P2 are defined, the suction port 9 is located between the first reference line L1 and the second reference line L2 in the radial direction of the drive scroll 30 and the driven scroll 40. In addition, the outflow prevention wall 37 extends inward in the radial direction of the drive scroll 30 and the driven scroll 40 from the first reference line L1 and the second reference line L2.

In addition, in this compressor, because the main body 70a of the protruding member 70 enters the suction port 9, the inner circumferential surface 710 of the suction passage 71 is located radially inward of the driving scroll 30 and the driven scroll 40 relative to the inner circumferential surface 9a of the suction port 9. In other words, the suction passage 71, including the inner circumferential surface 710, is located closer to the center of the driving scroll 30 and the driven scroll 40 than the suction port 9.

As a result, in this compressor, the refrigerant gas sucked into the suction port 9 from the suction passage 71 flows from the center side of the driving scroll 30 and the driven scroll 40 toward the outside, while flowing through the cover body 35 and being sucked into the suction section 30a and each compression chamber 12. Here, in this compressor, the refrigerant gas flowing from the suction passage 71 through the cover body 35 toward the suction section 30a is affected by the rotating driving scroll 30 and the rotating driven driven scroll 40. For this reason, the lubricating oil 19 contained in the refrigerant gas tends to scatter toward the outside in the radial direction of the driving scroll 30 and the driven scroll 40 due to centrifugal force. However, as described above, since the refrigerant gas flowing through the cover body 35 toward the suction section 30a flows from the center side of the driving scroll 30 and the driven scroll 40 toward the outside, even if the lubricating oil 19 tries to scatter toward the outside, the lubricating oil 19 is also easily circulated to each compression chamber 12 together with the refrigerant gas.

In addition, in this compressor, the outflow prevention wall 37 extends radially inward of the driving scroll 30 and the driven scroll 40 beyond the first end 330 of the driving scroll 33. As a result, the outflow prevention wall 37 extends radially inward of the driving scroll 30 and the driven scroll 40 beyond each compression chamber 12 where the compression of the refrigerant gas begins. Therefore, in this compressor, the lubricating oil 19 that has been centrifuged from the refrigerant gas and has not been able to flow to each compression chamber 12 together with the refrigerant gas may adhere to the inner circumferential surface 111 of the rotor 11 and the inner circumferential surface 351 of the peripheral wall portion 35b, but the outflow prevention wall 37 can suitably prevent this lubricating oil 19 from flowing out from the suction portion 30a into the scroll chamber 65. As a result, the lubricating oil 19 that has adhered to the inner circumferential surfaces 111 and 351 can flow to each compression chamber 12 together with the refrigerant gas that is newly flowing to each compression chamber 12.

As a result, in this compressor, insufficient lubrication is unlikely to occur within each compression chamber 12, and the lubricating oil 19 can suitably lubricate the driving scroll 30 and the driven scroll 40, including the driving scroll 33 and the driven scroll 43. As a result, in this compressor, the driving scroll 30 and the driven scroll 40 are unlikely to wear out.

Therefore, the compressor of Example 1 has excellent durability.

In particular, in this compressor, when the main body 70a of the protruding member 70 is inserted into the suction port 9, a gap exists between the suction port 9 and the small diameter portion 702, but the inner circumferential surface 710 of the suction passage 71 is located radially inward of the driving scroll 30 and the driven scroll 40 relative to the inner circumferential surface 9a of the suction port 9. Therefore, in this compressor, it is possible to move the suction passage 71 away from the gap between the suction port 9 and the small diameter portion 702 in the radial direction of the driving scroll 30 and the driven scroll 40. Therefore, in this compressor, it is possible to suitably suck the refrigerant gas and liquid refrigerant 18 flowing through the suction passage 71 into the suction section 30a while preventing the refrigerant gas and liquid refrigerant 18 from leaking into the scroll chamber 65 through the above-mentioned gap.

In addition, in this compressor, by inserting the main body 70a into the suction port 9, the second boss 35c is supported by the first support portion 64, and the driving scroll 30 and the protruding member 70 can be arranged close to each other in the direction of the drive axis O1. Furthermore, in this compressor, by inserting the main body 70a into the suction port 9, the outflow prevention wall 37 and the main body 70a face each other in the radial direction of the driving scroll 30 and the driven scroll 40. In this respect, too, in this compressor, the driving scroll 30 and the protruding member 70 can be arranged close to each other in the direction of the drive axis O1. As a result, this compressor is also compact in the direction of the drive axis O1.

The outflow prevention wall 37 is shaped so that its thickness in the direction of the drive axis O1 becomes thinner as it moves from the outer periphery toward the suction port 9 in the radial direction of the drive scroll 30 and the driven scroll 40. This makes it easier to form the outflow prevention wall 37 in this compressor.

Furthermore, in this compressor, the suction passage 71 and the storage chamber 8 are connected by the communication passage 73 and the guide passage 63a, so that the lubricating oil 19 contained in the liquid refrigerant 18 in the storage chamber 8 can also be sucked into the suction section 30a and, ultimately, into each compression chamber 12. In this respect, too, this compressor is able to suitably lubricate the driving scroll 30 and the driven scroll 40. In addition, since the liquid refrigerant 18 is heated and vaporized in the process of flowing toward the suction section 30a, this compressor can suitably prevent the liquid refrigerant 18 from being sucked into each compression chamber 12.

Example 2
As shown in FIG. 5 , in the compressor of the second embodiment, the driving scroll 30 has a cover body 81 instead of the cover body 35 .

The cover body 81 has a main body portion 81a and a peripheral wall portion 81b. The main body portion 81a extends in a generally circular plate shape perpendicular to the drive axis O1 and the driven axis O2. Similar to the cover body 35 in the compressor of the first embodiment, a second boss 35c is formed in the center of the main body portion 81a. Also, similar to the cover body 35, a rotation prevention pin 21 is fixed to the main body portion 81a.

The main body 81a is provided with an outflow prevention wall 81e. The outflow prevention wall 81e is located at the rear end of the main body 81a and extends in the radial direction of the driving scroll 30 and the driven scroll 40 from the outer periphery of the main body 81a toward the second boss 35c. The outflow prevention wall 81e also serves as the rear wall of the main body 81a.

The outflow prevention wall 81e is also formed with an intake port 81d. In other words, the intake port 81d is formed by the outflow prevention wall 81e. The intake port 81d is composed of a recess 801 and a through portion 802. The recess 801 is recessed in a cylindrical shape centered on the drive axis O1 from the rear end surface of the outflow prevention wall 81e and thus the main body portion 81a toward the front. The recess 801c is formed with a larger diameter than the second boss 35c so as to surround the second boss 35c. The recess 801 is also formed with a larger diameter than the small diameter portion 702 of the protruding member 70 and a smaller diameter than the large diameter portion 701.

The through-hole 802 is located inside the recess 801 and outside the second boss 35c. The through-hole 802 has a smaller diameter than the recess 801 and penetrates the outflow prevention wall 81e in the direction of the drive axis O1. In other words, unlike the recess 801, the through-hole 802 does not have a shape that surrounds the second boss 35c. The through-hole 802 also connects the recess 801 to the inside of the main body 81a. The through-hole 802 has an inner circumferential surface 810.

By forming the suction port 81d in this manner, the outflow prevention wall 81e is located outside the suction port 81d and extends linearly from the outer periphery of the outflow prevention wall 81e toward the suction port 81d in the radial direction of the driving scroll 30 and the driven scroll 40. In other words, the suction port 81d is located inside the outflow prevention wall 81e in the radial direction of the driving scroll 30 and the driven scroll 40.

The peripheral wall portion 81b is connected to the outer peripheral edge of the main body portion 81a. The peripheral wall portion 81b is cylindrical and centered on the drive shaft center O1, and extends forward from the main body portion 81a. The peripheral wall portion 81b has an inner peripheral surface 811.

As with the compressor of the first embodiment, in this compressor, the driving end plate 31, the rotor 11, and the cover body 81 are connected by a plurality of bolts 50. Also, in this compressor, the second boss 35c is rotatably supported by the first support portion 64. As a result, the outflow prevention wall 81e is located radially outward of the driving scroll 30 and the driven scroll 40 from the main body portion 70a of the protruding member 70. The outflow prevention wall 81e extends radially of the driving scroll 30 and the driven scroll 40 toward the main body portion 70a.

In addition, in this compressor, the small diameter portion 702 of the main body portion 70a enters the recessed portion 801 of the suction port 81d. As a result, the suction passage 71 and the through portion 802 of the suction port 81d face each other in the direction of the drive axis O1. In addition, the inner circumferential surface 710 of the suction passage 71 is located radially inside the driving scroll 30 and the driven scroll 40, relative to the inner circumferential surface 810 of the through portion 802. Here, in this compressor, between the suction port 81d and the main body portion 70a, i.e., between the recessed portion 801 and the small diameter portion 702, and between the through portion 802 and the small diameter portion 702, there are gaps to prevent interference between the driving scroll 30 and the protruding member 70.

In this compressor, the outflow prevention wall 81e also extends radially inward of the driving scroll 30 and the driven scroll 40 beyond the first end 330 (see FIG. 4) of the driving scroll 33. Therefore, the outflow prevention wall 81e extends radially inward of the driving scroll 30 and the driven scroll 40 beyond the first contact point P1 and the second contact point P2. The suction port 81d is located radially inward of the driving scroll 30 and the driven scroll 40 beyond the outflow prevention wall 81e. Since the protruding portion 70 enters the suction port 81d, the suction port 81d and the suction passage 71 are located radially inward of the driving scroll 30 and the driven scroll 40 beyond the first contact point P1 and the second contact point P2. The other configurations of this compressor are the same as those of the compressor of the first embodiment, and the same configurations are designated by the same reference numerals, and detailed description of the configurations is omitted.

In this compressor, the refrigerant gas and liquid refrigerant 18 are sucked into the through-hole 802 of the suction port 81d through the suction passage 71. The refrigerant gas and liquid refrigerant 18 then flow from the center side of the driving scroll 30 and the driven scroll 40 toward the outside, while flowing through the cover body 81, and are sucked into the suction section 30a and each compression chamber 12. As a result, in this compressor, as in the compressor of Example 1, it is easy to favorably circulate the lubricating oil 19 to each compression chamber 12 together with the refrigerant gas.

In addition, in this compressor, lubricating oil 19 that does not flow into each compression chamber 12 together with the refrigerant gas may adhere to the inner circumferential surface 111 of the rotor 11 as well as to the inner circumferential surface 811 of the peripheral wall portion 81b of the cover body 81, but the outflow prevention wall 81e can effectively prevent this lubricating oil 19 from flowing into the scroll chamber 65. In this way, this compressor can achieve the same effect as the compressor of the first embodiment.

Furthermore, in this compressor, the inner circumferential surface 710 of the suction passage 71 is located radially inward of the driving scroll 30 and the driven scroll 40 relative to the inner circumferential surface 810 of the through-hole 802. Therefore, in this compressor, the suction passage 71 can be suitably located away from the gap between the small diameter portion 702 of the main body 70a and the recess 801 in the radial direction of the driving scroll 30 and the driven scroll 40. Therefore, in this compressor, the refrigerant gas and liquid refrigerant 18 flowing through the suction passage 71 can be suitably sucked into the suction section 30a from the through-hole 802, i.e., the suction port 81d, while preventing leakage into the scroll chamber 65.

In addition, by inserting the small diameter portion 702 into the recess 801, the drive scroll 30 and the protruding member 70 can be positioned close to each other in the direction of the drive axis O1 in this compressor as well. As a result, this compressor is also compact in the direction of the drive axis O1.

In addition, by inserting the small diameter portion 702 into the recess 801, the outflow prevention wall 81e and the protruding member 70 face each other in the radial direction of the driving scroll 30 and the driven scroll 40. The other functions of this compressor are the same as those of the compressor of the first embodiment.

Example 3
6 , the compressor of the third embodiment includes a driving scroll 130, a driven scroll 140, and a driven mechanism 20a, instead of the driving scroll 30, the driven scroll 40, and the driven mechanism 20. In this compressor, a protruding portion 91 is formed on the partition wall 60b of the housing body 60, instead of the first support portion 64.

The protrusion 91 is integrally formed at the center of the inner surface of the partition wall 60b. The protrusion 91 is cylindrical and centered on the drive axis O1, and protrudes from the partition wall 60b in the direction of the drive axis O1 toward the drive scroll 130 and the driven scroll 140. The outer ring of the bearing 92 is fitted inside the protrusion 91.

The drive scroll 130 has a drive end plate 131 and a drive peripheral wall 132, and also has a drive scroll 33 like the drive scroll 30. The drive end plate 131 extends in a generally circular plate shape perpendicular to the drive axis O1 and the driven axis O2. The drive end plate 131 has a front surface 131a and a rear surface 131b located opposite the front surface 131a. The drive scroll 33 is integrally formed with the front surface 131a.

The driving end plate 131 is provided with a first boss 83, a communication portion 84, and a fixed portion 85. The first boss 83 is also an example of a "supported portion" in the present invention. The first boss 83 is integrally formed in the center of the rear surface 131b. The first boss 83 is cylindrical with the driving axis O1 at its center, and protrudes from the rear surface 131b toward the partition wall 60b in the direction of the driving axis O1.

The communication part 84 is located on the drive end plate 131 at a position radially outward of the drive scroll 130 and the driven scroll 140 from the suction port 88 described below. The communication part 84 penetrates the drive end plate 131 in the direction of the drive axis O1. The fixing part 85 is located on the outer periphery of the drive end plate 131. The fixing part 85 protrudes rearward from the rear surface 131b in the form of an annular ring having the same diameter as the drive end plate 131.

The drive end plate 131 is also provided with an outflow prevention wall 87. An inlet 88 is formed in the outflow prevention wall 87. In other words, the inlet 88 is formed by the outflow prevention wall 87. The inlet 88 penetrates the outflow prevention wall 87 in the direction of the drive axis O1. The inlet 88 is formed with a larger diameter than the first boss 83 and the protruding portion 91.

By forming the suction port 88 in this manner, the outflow prevention wall 87 has a circular ring shape similar to the outflow prevention wall 37. In addition, since the outflow prevention wall 87 exists around the suction port 88, the suction port 88 is located radially inward of the outflow prevention wall 87 in the driving scroll 130 and the driven scroll 140. In other words, the outflow prevention wall 87 extends linearly from the outer periphery of the outflow prevention wall 87 toward the suction port 88 in the radial direction of the driving scroll 130 and the driven scroll 140.

The outflow prevention wall 87 is fixed to the fixing portion 85. As a result, the outflow prevention wall 87 is located at the rear of the driving end plate 131 and is integral with the driving end plate 131. The outflow prevention wall 87 covers the driving end plate 131 from the rear while causing the first boss 83 to protrude from the suction port 88. In addition, as the outflow prevention wall 87 is fixed to the fixing portion 85, the suction port 88 is connected to the communication portion 84.

The driving peripheral wall 132 is formed integrally with the driving end plate 131 and extends forward from the outer periphery of the driving end plate 131, i.e., parallel to the driving axis O1, toward the driven scroll 140. The driving peripheral wall 132 is cylindrical with the driving axis O1 at its center, and surrounds the driving scroll 33.

Four rotation prevention pins 21a are fixed to the front end of the driving peripheral wall 132 in a state where they protrude forward. Note that Figure 6 illustrates two of the four rotation prevention pins 21a.

The driven scroll 140 has a driven end plate 141 and a driven scroll 43, similar to the driven scroll 40. The driven end plate 141 extends in a generally circular plate shape perpendicular to the drive axis O1 and the driven axis O2. The driven end plate 141 has a front surface 141a and a rear surface 141b located on the opposite side of the front surface 141a.

A second boss 89 is formed in the center of the front surface 141a, protruding toward the first housing cover 61. The second boss 89 is cylindrical and centered on the driven axis O2. The driven spiral body 43 is integrally formed on the rear surface 141b. Four rings 22a are fixed to the rear surface 141b at locations on the outer periphery side of the driven spiral body 43 so as to correspond to the rotation prevention pins 21a. Two of the four rings 22a are shown in Figure 6.

The driven end plate 141 is also formed with a discharge port 38a. The discharge port 38a is located in the driven end plate 141 at a location within the second boss 89, and penetrates the driven end plate 141 in the front-rear direction. Similar to the driving end plate 31 in the compressor of the first embodiment, the discharge reed valve 57 and the retainer 58 are fixed to the driven end plate 141 by fixing bolts 59.

The driven mechanism 20a is composed of four rotation prevention pins 21a and four rings 22a.

In this compressor, the driving scroll 130 and the driven scroll 140 are housed in the scroll chamber 65, with the front surface 131a of the driving end plate 131 facing the rear surface 141b of the driven end plate 141. In this state, the driving scroll 33 and the driven scroll 43 are meshed within the driving peripheral wall 132, i.e., within the suction section 30b.

The rotation prevention pins 21a are inserted into the rings 22a. In this way, the driving scroll 130 and the driven scroll 140 are assembled in the front-rear direction. As a result, the driving scroll 130 and the driven scroll 140 form the scroll compression section 101. The driving scroll 130 and the driven scroll 140 form the suction section 30b. The driving scroll 33 and the driven scroll 43 are located in the suction section 30b. The suction section 30b is separated from the scroll chamber 65 by the driving end plate 131, the driving peripheral wall 132, and the driven end plate 141.

The driving scroll 130 is integrated with the rotor 11 by fixing the driving peripheral wall 132 to the rotor 11. In the driving scroll 130, the first boss 83 enters the protruding portion 91. The inner ring of the bearing 92 is fitted into the first boss 83. As a result, the first boss 83 is rotatably supported by the protruding portion 91 via the bearing 92. As a result, the driving scroll 130 is rotatably supported by the housing 6 around the driving axis O1.

In this way, the first boss 83 enters the protruding portion 91 while being supported by the protruding portion 91, so that the protruding portion 91 enters the suction port 88. Furthermore, the outflow prevention wall 87 is located radially outward of the driving scroll 130 and the driven scroll 140 relative to the protruding portion 91. The outflow prevention wall 87 then extends radially of the driving scroll 130 and the driven scroll 140 toward the protruding portion 91.

On the other hand, in the driven scroll 140, the second boss 89 is fitted into the inner ring of the needle bearing 14. As a result, the second boss 89 is rotatably supported by the second support portion 67 via the needle bearing 14. As a result, the driven scroll 140 is rotatably supported by the housing 6 around the driven axis O2.

In addition, because the second boss 89 is supported by the second support portion 67, in this compressor, the discharge chamber 13a is formed in the housing 6 by the space surrounded by the inner circumferential surface of the second boss 89 and sandwiched between the first housing cover 61 and the driven end plate 141. The discharge chamber 13a is in communication with the discharge communication port 68.

In this compressor, the drive scroll 130 is driven to rotate around the drive axis O1 by the rotation of the rotor 11. The driven scroll 140 is driven to rotate around the driven axis O2 by the drive scroll 130 and the driven mechanism 20a. As a result, in this compressor, as in the compressor of the first embodiment, the drive scroll 33 and the driven scroll 43 come into contact with each other to form each compression chamber 12. In this compressor, too, the radially outermost contact points of the drive scroll 130 and the driven scroll 140 with the drive scroll 33 and the driven scroll 43 at the moment when each compression chamber 12 is formed are the first contact point P1 and the second contact point P2 (see FIG. 4).

In this compressor, like the outflow prevention wall 37 in the compressor of the first embodiment, the outflow prevention wall 87 extends radially inward of the driving scroll 130 and the driven scroll 140 from the first end 330 of the driving scroll 33. Therefore, the outflow prevention wall 87 extends radially inward of the driving scroll 130 and the driven scroll 140 from the first contact point P1 and the second contact point P2. In addition, since the suction port 88 is located radially inward of the driving scroll 130 and the driven scroll 140 from the outflow prevention wall 87, the suction port 88 is located radially inward of the driving scroll 130 and the driven scroll 140 from the first contact point P1 and the second contact point P2. The other configurations of this compressor are the same as those of the compressor of the first embodiment.

In this compressor, the refrigerant gas in the scroll chamber 65 is sucked into the suction section 30b through the suction port 88. In addition, in this compressor, the liquid refrigerant 18 in the storage chamber 8 flows into the scroll chamber 65 through the guide passage 63a and the communication passage 73, and is sucked into the suction section 30b through the suction port 88. Here, the suction port 88 is located inside the outflow prevention wall 87 in the radial direction of the driving scroll 130 and the driven scroll 140. Therefore, the suction port 88 is located near the center of the driving scroll 130 and the driven scroll 140. As a result, the refrigerant gas and liquid refrigerant 18 sucked into the suction port 88 flow from the center side of the driving scroll 130 and the driven scroll 140 to the outside, and are sucked into the suction section 30b through the communication section 84 and into each compression chamber 12.

In this way, in this compressor, as in the compressor of the first embodiment, the lubricating oil 19 can be easily circulated to each compression chamber 12 together with the refrigerant gas. Furthermore, in this compressor, the lubricating oil 19 that has been separated from the refrigerant gas by centrifugal separation and is unable to circulate to each compression chamber 12 together with the refrigerant gas may adhere to the inner circumferential surface of the drive peripheral wall 132, but the outflow prevention wall 87 prevents this lubricating oil 19 from flowing into the scroll chamber 65. As a result, this compressor can achieve the same effect as the compressor of the first embodiment.

Although the present invention has been described above with reference to Examples 1 to 3, it goes without saying that the present invention is not limited to the above Examples 1 to 3, and can be modified as appropriate without departing from the spirit of the present invention.

For example, in the compressor of Example 1, the arrangement of the storage chamber 8, the driving scroll 30, and the driven scroll 40 may be changed to provide an outflow prevention wall 37 and an intake port 9 on the driven end plate 41 of the driven scroll 40. Here, when the outflow prevention wall 37 and the intake port 9 are provided on the driven end plate 41, it is sufficient that the outflow prevention wall 37 extends radially inward of the driving scroll 30 and the driven scroll 40 beyond the second end 430 of the driven scroll 43. The same applies to the compressors of Examples 2 and 3.

In the compressor of Example 1, the rotor 11 is sandwiched between the drive end plate 31 and the peripheral wall portion 35b of the cover body 35, and these are connected by the bolts 50. However, this is not limited to the above, and the drive end plate 31 and the peripheral wall portion 35b may be directly connected by the bolts 50, and the rotor 11 may be fixed to the outer circumferential surface of the peripheral wall portion 35b. The same applies to the compressor of Example 2.

In addition, in the compressor of Example 1, the drive scroll 30 and the rotor 11 may be connected to each other by a drive shaft so that the drive scroll 30 and the rotor 11 are spaced apart from each other in the direction of the drive axis O1. The same applies to the compressors of Examples 2 and 3.

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, this is not limited to this, and the driven mechanism 20 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. The same applies to the driven mechanism 20a in the compressor of Example 3.

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

6: Housing 8: Storage chamber 9, 81d, 88: Inlet port 10: Electric motor (drive mechanism)
12: Compression chamber 18: Liquid refrigerant 19: Lubricating oil 20, 20a: Driven mechanism 30, 130: Driving scroll 30a, 30b: Suction portion 31, 131: Driving end plate 33: Driving scroll body 35c: Second boss (supported portion)
37, 81e, 87... Outflow prevention wall 40, 140... Follower scroll 41, 141... Follower end plate 43... Follower scroll body 60b... Partition wall 65... Scroll chamber 70... Protruding member (protruding portion)
71... Suction passage 73... Communication passage 83... First boss (supported part)
91...Protrusion part 330...First end part (end part)
430...Second end (end)
O1... Drive shaft center O2... Driven shaft center

Claims (4)

The scroll includes a housing, a drive mechanism, a drive scroll, a driven scroll, and a driven mechanism,
The housing has a scroll chamber in which the driving scroll and the driven scroll are accommodated,
The driving scroll is rotated about a drive axis by the driving mechanism,
The driven scroll is rotated around a driven axis by the driving scroll and the driven mechanism while being eccentric with respect to the driving scroll,
The drive scroll has a drive end plate and a drive scroll that is integral with the drive end plate and protrudes in a spiral shape toward the driven scroll,
The driven scroll has a driven end plate facing the driving scroll, and a driven scroll integral with the driven end plate and protruding in a spiral shape toward the driving end plate,
A double-rotating scroll compressor in which a compression chamber for compressing a refrigerant is formed by the driving scroll and the driven scroll,
The drive scroll and the driven scroll form a suction portion that draws the refrigerant into the compression chamber,
The housing is provided with a cylindrical protrusion protruding into the scroll chamber in the drive axial direction toward the drive scroll and the driven scroll,
The driving scroll or the driven scroll is provided with a supported portion that is supported by the housing while entering the protruding portion, a suction port that allows the refrigerant to be sucked into the suction portion, and an outflow prevention wall that extends from the outside of the protruding portion toward the protruding portion in the radial direction of the driving scroll and the driven scroll and prevents lubricating oil contained in the refrigerant sucked from the suction port from flowing out into the scroll chamber,
The intake port is constituted by the outflow prevention wall,
2. A double-rotating scroll compressor, comprising: a drive scroll body and a driven scroll body, the drive scroll body being disposed radially inwardly of the drive scroll body and the driven scroll body being disposed radially outwardly of the drive scroll body and the driven scroll body; The double-rotating scroll compressor according to claim 1, wherein the protrusion extends into the inside of the suction port. The inside of the protruding portion is a suction passage through which a refrigerant can flow toward the suction port,
the suction port and the suction passage are opposed to each other in the drive shaft direction and communicate with each other,
3. The double-rotary scroll compressor according to claim 1, wherein an inner circumferential surface of the suction passage is located radially inward of an inner circumferential surface of the suction port. the housing has a storage chamber that separates a refrigerant drawn from the outside into gas and liquid and stores therein a liquid refrigerant containing the lubricating oil, and a partition wall that separates the storage chamber from the scroll chamber and is provided with the protrusion,
4. The double-rotating scroll compressor according to claim 3, wherein the partition wall is provided with a communication passage that connects the suction passage and the storage chamber.

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