WO2019058849A1

WO2019058849A1 - Compressor

Info

Publication number: WO2019058849A1
Application number: PCT/JP2018/030890
Authority: WO
Inventors: 芳夫小和田
Original assignee: サンデンホールディングス株式会社
Priority date: 2017-09-21
Filing date: 2018-08-22
Publication date: 2019-03-28
Also published as: JP2019056322A

Abstract

[Problem] To provide a compressor with which it is possible to increase the capacity to separate oil from ejected refrigerant in the entire operation range of the compressor, to increase the OCR in the compressor, durability and performance of the compressor, and to achieve an increase in the operation efficiency of a system in which the compressor is used. [Solution] The compressor 1 is provided with: a suction chamber 3 for suctioning a refrigerant which contains oil; a compression chamber 4 for compressing the refrigerant suctioned into the suction chamber 3; a refrigerant flow path 94 formed to externally discharge ejected refrigerant ejected from the compression chamber 4; first and second oil separators 90, 91 which are arranged in series in the refrigerant flow path 94, and which separate the oil contained in the ejected refrigerant using different oil separating capacities; a first oil flow path 92 for distributing the oil separated in the first oil separator 90 to a refrigerant suction side of the compression chamber 4; and a second oil flow path 93 for distributing the oil separated in the second oil separator 91 to the suction chamber 3 side.

Description

Compressor

The present invention relates to a compressor, for example, a compressor suitable for use in a vehicle air conditioner system.

For example, in a compressor used for a vehicle air-conditioner system etc., oil is mixed in refrigerant gas, and each part of the compressor is lubricated. However, when oil flows out to the external refrigerant circuit for heat exchange, the operating efficiency of the vehicle air conditioner system etc. decreases, so the amount of oil flowing out from the compressor to the external refrigerant circuit is reduced, and the oil circulation ratio (Oil Circulation Ratio: There is a need to optimize the OCR).

For example, Patent Document 1 discloses a compressor provided with an oil separator that performs collision separation type oil separation and an oil separator that performs centrifugal separation oil separation. The collision separation type oil separator causes the discharge refrigerant gas discharged from the compression mechanism to the discharge chamber to collide with the partition of the discharge chamber to separate the oil in the discharge refrigerant gas. The centrifugal type oil separator swirls the discharged refrigerant gas around a cylindrical separator disposed in the separation chamber to centrifuge oil in the discharged refrigerant gas.

The discharge chamber and the separation chamber are respectively communicated with the oil storage chamber via the communication passage, and the oil separated by each oil separator is collectively collected in the oil storage chamber. The oil collected at one time flows to the suction chamber while lubricating the lubrication target including bearings etc., and is returned together with the refrigerant to the suction side of the compression chamber. At this time, the oil contained in the suction refrigerant lubricates the compression mechanism. .

That is, in Patent Document 1, oil separators having different separation systems and having different oil separation capacities are disposed in different separation chambers. The oil separated by each oil separator is collectively collected in the oil storage chamber through each communication passage, then lubricates the lubrication target, passes through the suction chamber, and forms a single oil flow path leading to the suction side of the compression chamber. It distributes.

JP 2008-88945 A

Depending on the operating conditions of the compressor, when the pressure or flow rate of the discharged refrigerant changes, the pressure in each separation chamber may be lower than that in the oil storage chamber, or the pressure in each separation chamber may be higher. For this reason, if the restriction of each communication passage between the oil storage chamber and each separation chamber is insufficient, a back flow of oil from the oil storage chamber to each separation chamber may occur. On the other hand, if each communication passage between the oil storage chamber and each separation chamber is narrowed too much, oil may not flow from each separation chamber to the oil storage chamber.

If backflow or stagnation of oil occurs, the performance (volume efficiency) of the compressor decreases due to a decrease in OCR in the compressor, a decrease in durability of the compressor due to a lubrication failure, and a decrease in sealability of sliding parts of the compression mechanism. There is a fear. In addition, as the amount of oil contained in the discharged refrigerant increases, the amount of oil discharged from the compressor to the external refrigerant circuit also increases, which may lower the operating efficiency of the vehicle air conditioner system or the like.

In order to prevent such backflow and retention of oil, it is necessary to optimize the throttling of each communication passage in order to balance the pressure difference between the oil storage chamber and each separation chamber. However, since the oil separated by each oil separator is collectively collected in the oil storage chamber via each communication passage, the oil storage chamber is easily affected by the pressure of each separation chamber, and the entire range of operation from low flow to high flow of the compressor It was difficult to optimize the throttling of each communication passage in order to maintain the flow of oil properly.

In addition, although each oil separator of Patent Document 1 has different oil separation ability and the amount of oil that can be separated from the discharged refrigerant is different, the oil separated by each oil separator is collectively collected in the oil storage chamber, It flows through a single oil flow path and is used for lubrication to be lubricated. In this case, the oil can not be properly distributed according to the oil separation capacity of the oil separator and the lubrication requirement of each part of the compressor. Therefore, the oil separation capacity from the discharged refrigerant is enhanced over the entire operation range of the compressor. There was still a challenge in improving the lubrication performance of

The present invention has been made in view of such problems, and can increase the oil separation capability from the discharged refrigerant over the entire operation range of the compressor, improve the OCR in the compressor, and improve the durability of the compressor, It is an object of the present invention to provide a compressor capable of improving the performance of the compressor and the operation efficiency of a system using the compressor.

In order to achieve the above object, the compressor according to the present invention comprises a suction chamber for sucking in a refrigerant containing oil, a compression chamber for compressing the refrigerant sucked in the suction chamber, and a discharge from the compression chamber. A refrigerant flow path formed until the discharged refrigerant is discharged to the outside, and first and second oil separators disposed in series in the refrigerant flow path and separating oil contained in the discharged refrigerant with different oil separation capabilities And a first oil flow path for circulating oil separated by the first oil separator to the suction side of the refrigerant in the compression chamber, and a second oil flow path for circulating oil separated by the second oil separator to the suction chamber side .

According to the compressor of the present invention, the oil separation ability from the discharged refrigerant can be enhanced over the entire operation range of the compressor, the OCR in the compressor is improved, the durability of the compressor is improved, the performance of the compressor is improved, The improvement of the operating efficiency of the system using the compressor can be realized.

It is a longitudinal section of a compressor concerning a 1st embodiment of the present invention. It is sectional drawing to which the inside of the rear housing of FIG. 1 was expanded. It is the model which showed the refrigerant | coolant flow path and each oil flow path of FIG. It is sectional drawing to which the inside of the rear housing which concerns on 2nd Embodiment of this invention was expanded. It is the model which showed the refrigerant | coolant flow path of FIG. 4, and each oil flow path. It is the schematic diagram which showed the refrigerant | coolant flow path and each oil flow path which concern on the modification of this invention. It is the schematic diagram which showed the refrigerant | coolant flow path and each oil flow path which concern on another modification of this invention. It is the model which showed the refrigerant | coolant flow path and each oil flow path which concern on another modification of this invention.

Hereinafter, each embodiment for carrying out the present invention will be described with reference to the attached drawings.
First Embodiment
FIG. 1 shows a longitudinal sectional view of a compressor according to a first embodiment of the present invention. The compressor 1 is used, for example, in a vehicle air conditioner system or the like, by connecting a condenser, an expansion valve, an evaporator and the like in communication and circulating a refrigerant in a refrigerant circuit (not shown).

In the refrigerant circuit, the compressor 1 is an expansion valve downstream of a liquid phase refrigerant that has dissipated heat and condensed in the condenser, and refrigerant gas that has partially evaporated and decompressed and expanded, and the remaining liquid phase refrigerant downstream of the expansion valve. In the evaporator, heat is taken from the ambient air to compress and heat the vaporized refrigerant gas, and then it is pressure-fed to the condenser, whereby the refrigerant circulates in the refrigerant circuit. In the compressor 1, oil is mixed in the refrigerant gas in order to lubricate each part of the compressor 1.

The compressor 1 compresses the refrigerant gas sucked into the suction chamber 3 and the suction chamber 3 for suctioning the refrigerant gas through the suction port 2 and the suction port 2, which are suction ports for sucking the refrigerant gas from the outside. And a discharge port 5 for discharging the refrigerant gas discharged from the compression chamber 4 to the outside, and a pair of spiral members of the same shape are engaged in the compression chamber 4 to , And the other is a closed type scroll electric compressor which compresses the refrigerant gas by turning it using the rotational force of the electric motor 20. One scroll fixed is referred to as a fixed scroll 10, and the other scroll to be turned is referred to as a turning scroll 11. The fixed scroll 10 and the turning scroll 11 form a compression mechanism of the compressor 1. The compressor 1 also incorporates an inverter 30 for driving the electric motor 20.

The fixed scroll 10 has a scroll wrap 10b projecting in a substantially vertical direction from the end plate 10a, and the orbiting scroll 11 has a scroll wrap 11b projecting in a substantially vertical direction from the end plate 11a. . When the scroll wrap 10b of the fixed scroll 10 and the scroll wrap 11b of the orbiting scroll 11 mesh with each other, the end plate 10a and the end plate 11a become parallel, and the protruding end of the scroll wrap 10b of the fixed scroll 10 faces the end plate 11a. The protruding end of the scroll wrap 11b in the orbiting scroll 11 faces the end plate 10a.

At the protruding end of the scroll wrap 10b, an airtight tip seal (not shown) is embedded which blocks the flow of the refrigerant gas in the gap between the scroll wrap 10b and the end plate 11a, and the protruding end of the scroll wrap 10b It contacts with the end plate 11a via A similar tip seal (not shown) is embedded in the projecting end of the scroll wrap 11b, and the projecting end of the scroll wrap 11b contacts the end plate 10a via the tip seal.

Further, in the fixed scroll 10 and the orbiting scroll 11, in the state in which the circumferential direction angles of both scroll wraps 10b and 14b are shifted from each other, the side faces excluding the protruding ends of both

scroll wraps

10b and 11b differ in plural in circumferential direction And the

scroll plates

10a and 11b and the

scroll wraps

10b and 11b are sealed in a crescent-like sealed space as viewed from the direction perpendicular to the end plate 10a (or the end plate 11a). Form 12 in part.

The orbiting scroll 11 meshed with the fixed scroll 10 as described above is configured to be able to revolve around the central axis of the fixed scroll 10 via a crank mechanism 40 described later, in a state where its rotation is blocked. . As described above, the orbiting scroll 11 performs the orbiting motion so that the fluid pocket 12 partially formed by the both

end plates

10a and 11a and the

scroll wraps

10b and 11b is from the outer end of the

scroll wraps

10b and 11b. The volume of the fluid pocket 12 gradually shrinks as one moves towards the central inner end. Therefore, the refrigerant gas taken into the fluid pocket 12 from the outer end side of the

scroll wraps

10b and 11b is compressed.

The electric motor 20 comprises a cylindrical or cylindrical rotor (rotor) 22 in which permanent magnets are disposed in a central space of a cylindrical stator (stator) 21 in which a coil is disposed in a slot of an armature core. The apparatus is rotatably provided while maintaining the inner circumferential surface of 21 and the air gap. The rotor 22 is provided on its axis with a drive shaft 23 for driving the orbiting scroll 11.

The drive shaft 23 is connected to the end plate 11 a of the orbiting scroll 11 via the crank mechanism 40, and when the rotor 22 is rotated about its axis by the interaction of the electromagnetic force between the rotor 22 and the stator 21, the electric motor 20. Torque is transmitted from the drive shaft 23 to the orbiting scroll 11. The inverter 30 is electrically connected to the coil of the stator 21 in the electric motor 20, controls the amount of current supplied to the coil in accordance with an instruction signal from an external control device (not shown), and arbitrarily changes the rotational speed of the rotor 22. It is possible.

The crank mechanism 40 is eccentric to a cylindrical boss portion 41 formed to project from the end plate 11a to the opposite side to the scroll wrap 11b and a crank 23b provided at one shaft end 23a of the drive shaft 23 And an eccentric bushing 42 mounted in a state. The eccentric bush 42 is rotatably supported in the boss 41. Further, although not shown, the compressor 1 is provided with a rotation preventing mechanism for preventing rotation of the orbiting scroll 11, whereby the orbiting scroll 11 is prevented from rotating by means of the crank mechanism 40. It is configured to be able to revolve around the central axis of the fixed scroll 10. At one shaft end 23 a of the drive shaft 23, a balancer weight 43 is attached that cancels out the centrifugal force generated when the orbiting scroll 11 pivots.

The housing of the compressor 1 has a front housing 50 for housing the electric motor 20 and the inverter 30, an inverter cover 60, a center housing 70 for housing the fixed scroll 10 and the orbiting scroll 11, and a rear housing 80. Become. The front housing 50 and the rear housing 80 are disposed sandwiching the center housing 70.

Further, the inverter cover 60 is disposed on the opposite side of the front housing 50 to the center housing 70. And between the front housing 50 and the center housing 70, between the center housing 70 and the rear housing 80, and between the front housing 50 and the inverter cover 60 are fastened by fastening means (not shown) such as bolts. Constitute an integral housing.

The front housing 50 has a substantially cylindrical peripheral wall portion 51, and a partition wall portion 52 that divides the internal space of the peripheral wall portion 51 into one end opening side and the other end opening side. The electric motor 20 is accommodated and fixed in the peripheral wall portion 51 from the partition wall portion 52 to the one end opening side from the front housing 50 toward the center housing 70, and the peripheral wall from the partition wall portion 52 to the other end opening side The inverter 30 is accommodated and fixed in the portion 51.

One end opening of the circumferential wall 51 is closed by the center housing 70, and the other opening of the circumferential wall 51 is closed by the inverter cover 60. Further, the front housing 50 is open toward the center housing 70 on the one end opening side of the partition wall 52, and the other shaft end 23c of the drive shaft 23 of the electric motor 20 is rotatably fitted. The shaft end 23 c is supported by the support 53.

The center housing 70 has a substantially cylindrical peripheral wall portion 71, an annular inner flange portion 72 which is opened toward the front housing 50 while projecting inward from the inner surface of the peripheral wall portion 71, and an opening peripheral portion of the inner flange portion 72. And a bowl-like bulging portion 73 bulging toward the front housing 50. One end opening of the peripheral wall portion 71 is closed by the rear housing 80, and the other end opening of the peripheral wall portion 71 is closed by the front housing 50.

In the center housing 70, the fixed scroll 10 and the orbiting scroll 11 are accommodated in the peripheral wall 71 at the one end opening side with respect to the inner flange 72. The surface on the one end opening side of the inner flange portion 72 contacts the end plate 11 a of the orbiting scroll 11 via the annular thrust plate 74, and supports the orbiting scroll 11 in the thrust direction of the drive shaft 23.

A crank mechanism 40 is accommodated in the back pressure chamber 6 formed by being surrounded by the bulging portion 73 and the end plate 11a, and a bearing portion 75 for pivotally supporting the drive shaft 23 is disposed. . The bearing portion 75 extends from the electric motor 20 of the front housing 50 and penetrates the bulging portion 73. The end plate 10 a of the fixed scroll 10 engaged with the orbiting scroll 11 closes one end opening of the peripheral wall portion 71.

The suction port 2 is formed on one end side of the peripheral wall 51 of the front housing 50 from the partition wall 52, and the suction chamber 3 for sucking the refrigerant through the suction port 2 is the peripheral wall 51 and partition of the front housing 50. The wall 52 and the peripheral wall 71 of the center housing 70, the inner flange 72, and the bulging portion 73 are rigidly formed. Further, the compression chamber 4 is formed by being fixed to the end plate 10a, the peripheral wall portion 71 on the one end opening side from the inner flange portion 72, the inner flange portion 72, and the end plate 11a closing the opening of the inner flange portion 72.

In at least one of the peripheral wall portion 71 and the inner flange portion 72 of the center housing 70, a refrigerant introduction passage L1 for introducing the refrigerant gas sucked into the suction chamber 3 to the compression chamber 4 is formed. In the end plate 10a of the fixed scroll 10, a discharge hole 7 for discharging the refrigerant gas compressed in the fluid pocket 12 to the outside of the compression chamber 4 is formed at the inner end of the scroll wrap 10b.

A one-way valve V is provided on the outlet side of the discharge hole 7 to prevent the discharged refrigerant gas (discharged refrigerant gas) from flowing back to the compression chamber 4. The one-way valve V is used to compress the discharged refrigerant gas. The elastically deformable valve body that closes the discharge hole 7 when flowing back to 4 is fastened to the end plate 10 a of the fixed scroll 10 by fastening means such as a bolt.

The rear housing 80 is formed in a substantially bottomed cylindrical shape having a bottom portion 81 and a peripheral wall portion 82, and the opening end surface of the peripheral wall portion 82 contacts one end opening in the peripheral wall portion 71 of the center housing 70 and the end plate 10a of the fixed scroll 10. An exhaust port 5 is formed in contact with the inner space to connect the inner space with the outside, and is provided on the side of the circumferential wall 82 of the rear housing 80 near the bottom 81. The compressor 1 is installed with the discharge port 5 upward.

Here, as shown in FIG. 2, the compressor 1 includes a first oil separator 90 and a second oil separator 91 that separate and lower the oil from the discharged refrigerant gas in the internal space of the rear housing 80. In the inner space of the rear housing 80, a partition wall 86 is provided to face the bottom 81 and the end plate 10a. The partition wall 86 communicates with the first separation chamber 83, which is a space on the discharge hole 7 side communicating the internal space of the rear housing 80 with the compression chamber 4 via the discharge hole 7, and discharge from the discharge port 5. It is divided into a second separation chamber 84 which is a space on the port 5 side. The first oil separator 90 is disposed in the first separation chamber 83, and the second oil separator 91 is disposed in the second separation chamber 84.

The first separation chamber 83 and the second separation chamber 84 communicate with each other by the flow passage L2 penetrating the partition wall 86 in the

upper portions

83a and 84a while making the vertical direction the same. Therefore, the refrigerant flow path formed until the discharged refrigerant gas discharged from the compression chamber 4 through the discharge hole 7 is discharged from the discharge port 5 to the outside is the first separation chamber 83, the flow passage L2, the second The first oil separator 90 and the second oil separator 91 are arranged in series in this order as viewed in the flow direction of the refrigerant.

The first oil separator 90 of the present embodiment is a collision separation type oil separator. The first separation chamber 83 has a collided body 83 b for causing the discharged refrigerant gas discharged from the compression chamber 4 through the discharge hole 7 to collide. In the first separation chamber 83, the first oil separator 90 promotes the separation of the oil from the discharged refrigerant gas by the collision with the collided body 83b, and selectively lowers the separated oil by the relative specific gravity difference. Perform oil separation process.

The collided body 83 b is provided so that the discharge refrigerant gas discharged from the discharge hole 7 does not scatter to the lower portion 83 c of the first separation chamber 83. The collision target body 83b is configured, for example, as a substantially U-shaped collision wall which stands upright from the end plate 10a and surrounds the lower side of the periphery of the discharge hole 7. The discharged refrigerant gas may directly collide with the partition wall 86, the peripheral wall portion 82, and the like from the discharge hole 7.

The discharge refrigerant gas is allowed to fall in the first separation chamber 83 at a position not above the collided body 83b (for example, the lowermost position of the collided body 83b or below), while the oil separated from the discharged refrigerant gas is allowed to fall. A shield 83d is provided for suppressing the descent of the first separation chamber 83 (in particular, the approach of the first separation chamber 83 to the lower portion 83c of the discharged refrigerant gas which has collided with the collision target 83b). The shield 83d is, for example, configured as a shield wall having a gap with the end plate 10a (including the collided body 83b) while extending from the partition wall 86 toward the end plate 10a at the lowermost position of the collided body 83b. Be done.

The second oil separator 91 of the present embodiment is a centrifugal oil separator. The second oil separator 91 swirls the discharged refrigerant gas introduced into the second separation chamber 84 from the first separation chamber 83 via the flow passage L2, and the oil contained in the discharged refrigerant gas due to the relative specific gravity difference. Promote the centrifugation of the oil, let down the separated oil and perform the oil separation process. The oil separation capacity of the second oil separator 91, which is a centrifugal separation system, is about 4 over the oil separation capacity of the first oil separator 90, which is a collision separation system, over the entire operation range from low flow to high flow of the compressor 1. It has been proved by experiments etc that it is higher by 5 times. That is, the amount of oil separated by the second oil separator 91 is several times the amount of oil separated by the first oil separator 90.

The second separation chamber 84 has, for example, a circumferential surface 84b having a substantially circular cross section, and the introductory tube 84c substantially coaxial with the second separation chamber 84 has one end opened in the second separation chamber 84 and the other end The refrigerant gas is directed so as to be introduced between the inner peripheral surface 84b of the second separation chamber 84 and the outer peripheral surface of the inner tube 84c from a direction substantially tangential to the second separation chamber 84.

Here, the first separation chamber 83 communicates with the suction side of the refrigerant in the compression chamber 4 by the first oil flow path 92 formed in the peripheral wall portion 82 of the rear housing 80 and the peripheral wall portion 71 of the center housing 70. Further, the second separation chamber 84 is formed by the second oil flow passage 93 formed in the peripheral wall 82 of the rear housing 80 and the peripheral wall 71 and the inner flange 72 (which may include the bulging part 73) of the center housing 70. It communicates with the back pressure chamber 6.

The second oil flow passage 93 includes an axial through hole 93a penetrating from one back end 23a to the other axial end 23c inside the drive shaft 23 from the back pressure chamber 6, and through the axial through hole 93a Are formed up to the suction chamber 3. Further, the second oil flow passage 93 includes a throttle hole (a passage resistance portion) 93b which is open to the back pressure chamber 6 and has a passage cross-sectional area smaller than that of the shaft through hole 93a. The throttling hole 93 b functions as an orifice for reducing and accelerating the oil flowing through the second oil passage 93.

Hereinafter, an oil separation process for separating oil from the discharged refrigerant gas in the compressor 1 will be described with reference to FIG. The discharged refrigerant gas (indicated by the broken arrow in FIG. 2) discharged from the compression chamber 4 to the first separation chamber 83 through the discharge hole 7 first promotes oil separation in the first oil separator 90. . Specifically, the discharged refrigerant gas discharged to the first separation chamber 83 collides with the collided body 83b in the first separation chamber 83, and oil separated from the discharged refrigerant gas (white arrows in FIG. 2). Is lowered to the lower portion 83c of the first separation chamber 83 by the relative specific gravity difference.

At this time, the oil separated from the discharged refrigerant gas drops to the lower portion 83c of the first separation chamber 83 through the gap between the shield 83d and the end plate 10a (including the collided body 83b). On the other hand, most of the discharged refrigerant gas rises toward the upper portion 83a and partially drops after colliding with the collision target 83b, but a part of the discharged refrigerant gas is separated by the shield 83d into the first separation chamber 83. Since the entry of the oil into the lower portion 83c is suppressed, re-mixing of the separated oil into the discharged refrigerant gas can be suppressed.

The oil separated by the first oil separator 90 and dropped to the lower portion 83c of the first separation chamber 83 flows to the suction side of the refrigerant in the compression chamber 4 via the first oil passage 92, and the fixed scroll 10 and the orbiting scroll And 11 mainly lubricate the compression mechanism formed from That is, the first oil passage 92 is formed from the first separation chamber 83 to the compression chamber 4.

Furthermore, the discharged refrigerant gas subjected to the oil separation processing by the first oil separator 90 is introduced into the second separation chamber 84 through the flow passage L2 of the upper portion 83a, and the oil separation is promoted in the second oil separator 91. Ru. Specifically, when the discharged refrigerant gas introduced into the second separation chamber 84 swirls between the inner peripheral surface 84 b and the outer peripheral surface of the inner tube 84 c and descends in a spiral shape, the discharged refrigerant gas is introduced into the discharged refrigerant gas. The contained oil is centrifuged by the relative specific gravity difference, and the separated oil falls along the inner circumferential surface 84b to the lower portion 84d of the second separation chamber 84.

The oil separated by the second oil separator 91 and dropped to the lower portion 84d of the second separation chamber 84 flows to the back pressure chamber 6 through the second oil passage 93, and the crank mechanism 40, thrust plate 74, bearing portion After lubricating the object to be lubricated including the sliding portion 75 such as the drive shaft 23, etc. and reducing the pressure and accelerating the pressure in the throttle hole 93b, it is circulated to the suction chamber 3 through the shaft through hole 93a. That is, the second oil passage 93 is formed from the second separation chamber 84 to the suction chamber 3 and has a passage length several times or more than that of the first oil passage 92. There are many lubrication targets.

The oil flowing into the suction chamber 3 mixes with the refrigerant gas drawn into the suction chamber 3 from the suction port 2. After flowing through the electric motor 20, the suction refrigerant gas containing oil is introduced to the compression chamber 4 through the refrigerant introduction passage L1. On the other hand, the discharged refrigerant gas starts rising toward the one end opening of the outflow pipe as the turning motion becomes smaller, and is discharged from the exhaust port 5 to the system such as the vehicle air conditioning system through the outflow pipe.

As described above, the compressor 1 of the present embodiment, as shown in FIG. 3, discharges the refrigerant gas discharged from the compression chamber 4 through the discharge hole 7 after being compressed by the compression mechanism, as the discharge port 5. The refrigerant flow path 94 (shown by a solid line in FIG. 3) passes through to an external system such as a vehicle air conditioning system. The refrigerant flow path 94 includes a first oil separator 90 (indicated as collision separation OS in FIG. 3) and a second oil separator 91 (indicated as centrifugation OS in FIG. 3) having different oil separation capacities. It arranges in series in this order.

Then, the oil separated by the first oil separator 90 is made to flow to the suction side of the suction refrigerant gas in the compression chamber 4 via the first oil flow path 92 (shown by a broken line in FIG. 3). Furthermore, the oil separated by the second oil separator 91 having an oil separation ability higher than that of the first oil separator 90 is circulated to the back pressure chamber 6 via the second oil flow path 93 (shown by the alternate long and short dash line in FIG. 3). The pressure is reduced and accelerated by the throttle hole 93b to lubricate the object to be lubricated, and then the fluid is circulated to the suction chamber 3 side.

As a result, the oil separated by the first and

second oil separators

90 and 91 is less likely to be affected by the pressure of the first and

second separation chambers

83 and 84, and hence the operation from low flow to high flow of the compressor The flow of oil can be properly maintained over the entire area. Therefore, it is possible to prevent the backflow and retention of oil over the entire operation range of the compressor 1 and maintain the flow of oil appropriately.

Also, as described above, the second oil separator 91 has a higher oil separation ability than the first oil separator 90, and the amount of oil separated by the second oil separator 91 is the amount of oil separated by the first oil separator 90. It tends to be more than that. As a result, a relatively large amount of oil separated by the second oil separator 91 has a longer flow path length than the first oil flow path 92 and has more lubrication targets, ie, preferentially to the second oil flow path 93 having a high lubrication requirement. It can be distributed. Therefore, in the second oil flow path 93 having a relatively long flow path length, it is possible to prevent an oil film to be lubricated, etc. from running out.

On the other hand, the oil separated by the first oil separator 90 is required to be lubricated during operation of the compressor 1 via the first oil flow path 92 shorter than the second oil flow path 93 even though the amount is relatively small. In particular, it can be supplied directly and quickly to high compression mechanisms. As described above, the entire operation range of the compressor 1 can be achieved by appropriately distributing the oil according to the oil separation capability of the first and

second oil separators

90 and 91, the lubrication request of each part of the compressor 1, and the request type. Since the oil separation capability can be enhanced and the lubricating performance of the compressor 1 can be enhanced, the OCR improvement in the compressor 1, the durability improvement of the compressor 1, the performance improvement of the compressor 1, and the compressor can be improved. The operation efficiency of the system using 1 can be improved.

Second Embodiment
FIG. 4 is an enlarged cross-sectional view of the inside of a rear housing 80 according to a second embodiment of the present invention. In addition, about the structure similar to 1st Embodiment, a same sign may be attached | subjected in a figure and description may be abbreviate | omitted. In the internal space of the rear housing 80, the compressor 1 of the present embodiment includes an oil storage chamber 95 for storing the oil separated and dropped in the first separation chamber 83, and an oil storage chamber for storing the oil separated and dropped in the second separation chamber 84. And 96.

The oil storage chamber 95 is provided in the middle of the first oil flow passage 92 formed in the peripheral wall portion 82 of the rear housing 80, and temporarily stores oil separated by the first oil separator 90 and flowing through the first oil flow passage 92. . The oil storage chamber 96 is provided in the middle of the second oil flow passage 93 formed in the peripheral wall portion 82 of the rear housing 80, separates by the second oil separator 91, and temporarily stores the oil flowing through the second oil flow passage 93.

Further, in the first oil flow passage 92, a throttle hole (passage resistance portion) 92a in which the passage cross-sectional area is reduced is formed. The throttling hole 92a is formed in the first oil flow passage 92 so as to, for example, straddle the peripheral wall 82 of the rear housing 80 and the peripheral wall 71 of the center housing 70, and reduces or accelerates the oil flowing through the first oil flow passage 92. Function as an orifice.
As shown in FIG. 5, the compressor 1 according to the present embodiment is similar to the first embodiment in that the first oil separator 90 (shown as the collision separation OS in FIG. And a second oil separator 91 (shown as centrifugal OS in FIG. 5) are arranged in series in this order.

The oil separated by the first oil separator 90 is disposed in the first oil flow path 92 (shown by a broken line in FIG. 5), the oil storage chamber 95 and the throttle hole 92a. Distribute to the suction side. Furthermore, the oil separated by the second oil separator 91 having an oil separation ability higher than that of the first oil separator 90 is disposed via the oil storage chamber 96 disposed in the second oil flow passage 93 (shown by the alternate long and short dash line in FIG. 5). After flowing into the back pressure chamber 6 and reducing pressure and acceleration through the throttle hole 93 b to lubricate the object to be lubricated, it is circulated to the suction chamber 3 side.

As described above, the compressor 1 according to the present embodiment includes the

oil storage chambers

95 and 96 and the throttle holes 92 a and 93 b which are independent of each other in both the first oil flow channel 92 and the second oil flow channel 93. . Thereby, in the first and second

oil flow passages

92 and 93, the oil can be supplied to the lubrication target more quickly than the throttle holes 92a and 93b while appropriately holding the oil in the

oil storage chambers

95 and 96. Therefore, it is possible to more efficiently allocate the oil according to the oil separation capability of the first and

second oil separators

90 and 91 and the lubrication requirement of each part of the compressor 1.

This completes the description of the embodiments of the present invention, but the present invention is not limited to this, and various modifications can be made without departing from the spirit of the present invention.
For example, in each of the above-described embodiments, the compressor 1 includes the first oil separator 90 and the second oil separator 91 arranged in series in this order in the refrigerant flow path 94. However, the present invention is not limited to this, and as shown in FIG. 6 as a modified example of the second embodiment, the first oil separator 90 and the second oil separator 91 may be interchanged.

Even when the second oil separator 91 and the first oil separator 90 are arranged in series in this order in the refrigerant flow path 94, the oil separated by the first oil separator 90 is compressed via the first oil flow path 92. The same effect as in each of the above embodiments, because the oil in the chamber 4 flows to the suction side of the refrigerant and the oil separated by the second oil separator 91 flows separately to the suction chamber 3 via the second oil flow path 93 Can be played.

Further, as shown in FIG. 7, both of the first oil separator 90 and the second oil separator 91 may be centrifugal type oil separators as long as they have different oil separation capacities. Specifically, the first centrifugal separation OS shown in FIG. 7 has a specification in which the oil separation capacity is enhanced compared to the second centrifugal separation OS, and the oil separated by the second centrifugal separation OS is passed through the first oil flow passage 92. Flow to the suction side of the refrigerant in the compression chamber 4 and to the oil separated by the second centrifugal separation OS through the second oil flow passage 93 to the suction chamber 3 side, similar to the above embodiments. It can produce an effect.

Further, as shown in FIG. 8, both of the first oil separator 90 and the second oil separator 91 may be collision separation type oil separators as long as they have different oil separation capabilities. Specifically, the first collision separation OS shown in FIG. 8 has a specification in which the oil separation capacity is enhanced compared to the second collision separation OS, and the oil separated by the second collision separation OS is passed through the first oil flow path 92. Flow to the suction side of the refrigerant in the compression chamber 4 and the oil separated by the second collision separation OS to flow to the suction chamber 3 side via the second oil flow path 93, as in the above embodiments. It can produce an effect.

Each of the modifications shown in FIGS. 6 to 8 is also applicable to the compressor 1 not provided with the

oil storage chambers

95 and 96 as described in the first embodiment. Further, depending on the specification of the compressor 1, there may be a form in which only one of the

oil storage chambers

95 and 96 is formed, and a form in which only one of the throttle holes 92a and 93b is formed. Also, instead of means for reducing the passage cross sectional area such as the throttle holes 92a and 93b, other means for passage resistance may be provided in the first and second

oil flow passages

92 and 93.

In addition, such a passage resistance portion is preferably provided between the first separation chamber 83 and the compression chamber 4 in the first oil passage 92 where the pressure difference of the flowing oil becomes relatively large, while the second oil passage 92 Preferably, the oil passage 93 is provided between the second separation chamber 84 and the back pressure chamber 6.
In each of the above embodiments, the discharge refrigerant discharged from the discharge hole 7 of the compressor 1 is described as the discharge refrigerant gas, but the discharge refrigerant may include not only a gas phase refrigerant but also a liquid phase refrigerant.
The first and

second oil separators

90 and 91 may be separation methods other than the collision separation method or the centrifugal separation method as long as the oil separation ability is different.

Further, on the premise that at least the first and

second oil separators

90 and 91 are provided, one or more oil separators may be additionally provided, provided that the pressure loss of the discharged refrigerant does not become excessive. In this case, in consideration of the oil separation ability of the oil separator to be added, it is determined whether the oil separated by the oil separator is to be circulated to the first oil passage 92 or to the second oil passage 93. Ru.

Further, in the above embodiments, the first oil flow passage 92 is formed in the peripheral wall 82 of the rear housing 80 and the peripheral wall 71 of the center housing 70. However, the present invention is not limited to this. The first oil passage 92 may be formed in the end plate 11 a of the fixed scroll 10 and may be in communication with the suction side of the refrigerant in the first separation chamber 83 and the compression chamber 4. However, in this case, it is necessary to form the first oil flow path 92 so that the scroll wrap 11 b of the orbiting scroll 11 does not interfere with the orbit of the orbiting scroll 11.

In each of the above-described embodiments, the compressor 1 meshes the pair of fixed scrolls 10 and the orbiting scroll 11 having the same shape in the compression chamber 4 and uses the rotational force of the electric motor 20 with the orbiting scroll 11. It has been described that the refrigerant gas is compressed by turning. However, instead of the built-in electric motor 20, the orbiting scroll 11 may be pivoted by an external drive source.

For example, when the compressor 1 is applied to a vehicle air conditioner system, an engine may be used as an external drive source, and the rotational force of the crank 23b shaft may be transmitted to the drive shaft 23 via a pulley.
In each of the above embodiments, the compressor 1 is described as a sealed scroll compressor in which oil circulates in the housing and the back pressure chamber 6 is formed on the back side of the orbiting scroll 11. The present invention is also applicable to an open scroll compressor in which the back pressure chamber 6 is not formed.

Also, instead of the scroll compressor that compresses the refrigerant gas with the fixed scroll 10 and the orbiting scroll 11, a reciprocating compressor that compresses the refrigerant gas by the volume change of the cylinder due to the reciprocating motion of the piston The present invention can be applied to any compression type compressor, such as a rotary vane type compressor which compresses a refrigerant gas by rotating the rotor with the vane in contact with the inner wall of the housing.

DESCRIPTION OF SYMBOLS 1 compressor 3 suction chamber 4 compression chamber 83b collision object 90 1st oil separator 91 2nd oil separator 92 1st oil flow path 92a throttle hole (passage resistance part)
93 2nd oil flow passage 93b Throttle hole (passage resistance part)
94 Refrigerant channel 95 Oil storage chamber 96 Oil storage chamber

Claims

A suction chamber for suctioning a refrigerant containing oil;
A compression chamber for compressing the refrigerant drawn into the suction chamber;
A refrigerant flow path formed until the refrigerant discharged from the compression chamber is discharged to the outside;
First and second oil separators arranged in series in the refrigerant flow path and separating oil contained in the discharged refrigerant with different oil separation capabilities;
A first oil flow path for causing the oil separated by the first oil separator to flow to the suction side of the refrigerant in the compression chamber;
A compressor including: a second oil flow path for causing oil separated by the second oil separator to flow to the suction chamber side;
The compressor according to claim 1, wherein the second oil separator has a higher oil separation capacity than the first oil separator.
The compressor according to claim 2, wherein the first oil separator causes the discharged refrigerant to collide with a collision target to separate and lower the oil.
The compressor according to claim 2, wherein the second oil separator swirls the discharged refrigerant to separate and lower the oil.
The compressor according to any one of claims 1 to 4, wherein a passage resistance portion is provided in at least one of the first and second oil flow passages.
The compressor according to any one of claims 1 to 5, wherein an oil storage chamber is provided in at least one of the first and second oil flow paths.