JP2019056322A - Compressor - Google Patents

Abstract

To provide a compressor which can enhance an oil separation capacity from a discharge refrigerant over the whole operation area of the compressor, can improve an OCR in the compressor, can improve the durability of the compressor, can improve the performance of the compressor, and can improve the operation efficiency of a system using the compressor.SOLUTION: A compressor 1 comprises: a suction chamber 3 for sucking a refrigerant containing oil; a compression chamber 4 for compressing the refrigerant sucked into the suction chamber 3; a refrigerant flow passage 94 which is formed before the discharged refrigerant which is discharged from the compression chamber 4 is discharged to the outside; first and second oil separators 90, 91 which are arranged in the refrigerant flow passage 94 in series, and separate oil contained in the discharged refrigerant by a different oil separation capacity; a first oil flow passage 92 for making the oil separated by the first oil separator 90 circulate to a suction side of the refrigerant in the compression chamber 4; and a second oil flow passage 93 for making the oil separated by the second oil separator 91 circulate to the suction chamber 3 side.SELECTED DRAWING: Figure 2

Description

  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 in a vehicle air conditioner system or the like, oil is mixed in refrigerant gas to lubricate each part of the compressor. However, if oil flows out to the external refrigerant circuit for heat exchange, the operating efficiency of the vehicle air conditioner system and the like is lowered, 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 (OCR).

  For example, Patent Document 1 discloses a compressor including an oil separator that performs oil separation by a collision separation method and an oil separator that performs oil separation by a centrifugal separation method. The collision separator type oil separator separates oil in the discharged refrigerant gas by colliding the discharged refrigerant gas discharged from the compression mechanism into the discharge chamber against the partition wall of the discharge chamber. Centrifugal oil separators rotate discharged refrigerant gas around a cylindrical separator disposed in a separation chamber to centrifuge oil in the discharged refrigerant gas.

  The discharge chamber and the separation chamber are each communicated with the oil storage chamber via a communication path, and the oil separated by each oil separator is collectively collected in the oil storage chamber. Collected oil flows to the suction chamber while lubricating the object to be lubricated including the bearings and the like, and is returned to the suction side of the compression chamber together with the refrigerant. At this time, the oil contained in the suction refrigerant lubricates the compression mechanism. .

  That is, in patent document 1, each oil separator which is a different separation system and has different oil separation ability is arrange | positioned in a different separation chamber. The oil separated by each oil separator is collected in the oil storage chamber through each communication path, and then lubricates the object to be lubricated, passes through the suction chamber, and passes through a single oil flow path to the suction side of the compression chamber. Circulate.

JP 2008-88945 A

  If the pressure or flow rate of the discharged refrigerant changes depending on the operating conditions of the compressor, each separation chamber may be at a lower pressure than the oil storage chamber, or each separation chamber may be at a higher pressure. For this reason, if the throttle of each communication path between the oil storage chamber and each separation chamber is insufficient, the backflow of oil from the oil storage chamber to each separation chamber may occur. On the other hand, if each communication path between the oil storage chamber and each separation chamber is excessively throttled, there is a possibility that oil does not flow from each separation chamber to the oil storage chamber.

  When backflow or stagnation of oil occurs, the compressor performance (volumetric efficiency) decreases due to a decrease in OCR in the compressor, a decrease in the durability of the compressor due to poor lubrication, and a decrease in the sealing performance of the sliding portion of the compression mechanism. There is a fear. In addition, when 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 reduce the operating efficiency of the vehicle air conditioner system and the like.

  In order to prevent such backflow or stagnation of oil, it is necessary to optimize the throttle of each communication path in order to balance the pressure difference between the oil storage chamber and each separation chamber. However, since the oil separated in each oil separator is collected in the oil storage chamber through each communication passage, the oil storage chamber is easily affected by the pressure in each separation chamber, and the entire operation range from low to high flow rate of the compressor It has been difficult to optimize the throttle of each communication path in order to maintain the oil flow appropriately.

  In addition, each oil separator of Patent Document 1 has different oil separation capabilities, and the oil separated by each oil separator is collected in the oil storage chamber in a collective manner, although the amount of oil that can be separated from the discharged refrigerant is different. It flows through a single oil passage and is used for lubrication. This makes it impossible to properly distribute the oil according to the oil separation ability of the oil separator and the lubrication requirements of each part of the compressor, so the oil separation ability from the discharged refrigerant is increased throughout the compressor operation, and the compressor There was still a problem with improving the lubrication performance.

  The present invention has been made in view of such a problem, and can improve the oil separation ability from the discharged refrigerant over the entire operation range of the compressor, improve the OCR in the compressor, 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 improving the operation efficiency of a system using the compressor.

  In order to achieve the above object, a compressor according to the present invention includes a suction chamber for sucking refrigerant containing oil, a compression chamber for compressing refrigerant sucked into 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 arranged in series in the refrigerant flow path and separating oil contained in the discharged refrigerant with different oil separation capacities A first oil flow path for circulating the oil separated by the first oil separator to the refrigerant suction side in the compression chamber, and a second oil flow path for flowing the oil separated by the second oil separator to the suction chamber side. .

  According to the compressor of the present invention, it is possible to increase the oil separation ability from the discharged refrigerant over the entire operation of the compressor, improve the OCR in the compressor, improve the durability of the compressor, improve the performance of the compressor, and Thus, it is possible to improve the operation efficiency of the system using the compressor.

It is a longitudinal section of the 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 schematic diagram 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 schematic diagram which showed the refrigerant | coolant flow path and each oil flow path of FIG. 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 schematic diagram which showed the refrigerant | coolant flow path and each oil flow path which concern on another modification of this invention.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the accompanying drawings.
<First Embodiment>
FIG. 1 is a longitudinal sectional view of a compressor according to a first embodiment of the present invention. The compressor 1 is incorporated in a refrigerant circuit (not shown) that circulates a refrigerant by connecting a condenser, an expansion valve, an evaporator, and the like in a vehicle air conditioner system, for example.

  In the refrigerant circuit, the compressor 1 is configured such that the liquid phase refrigerant radiated and condensed by the condenser is a downstream expansion valve, the refrigerant gas partially evaporated after being decompressed and expanded, and the remaining liquid phase refrigerant is downstream of the expansion valve. The refrigerant gas that has been vaporized by removing heat from ambient air in the evaporator is compressed and heated, and then pumped toward 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 suction port 2 that is a suction port for sucking refrigerant gas from the outside, the suction chamber 3 for sucking the refrigerant gas through the suction port 2, and the refrigerant gas sucked into the suction chamber 3. A compression chamber 4 and a discharge port 5 which is a discharge port for discharging the refrigerant gas discharged from the compression chamber 4 to the outside. In the compression chamber 4, a pair of spiral bodies having the same shape are meshed with each other, Is a hermetic scroll electric compressor that compresses refrigerant gas by rotating the other using the rotational force of the electric motor 20. One fixed spiral body is called a fixed scroll 10, and the other spiral body to be rotated is called a rotary scroll 11, and the fixed scroll 10 and the rotary scroll 11 form a compression mechanism of the compressor 1. Further, the compressor 1 includes an inverter 30 for driving the electric motor 20.

  The fixed scroll 10 has a spiral scroll wrap 10b protruding from the end plate 10a in a substantially vertical direction, and the orbiting scroll 11 has a scroll wrap 11b protruding from the end plate 11a in a substantially vertical direction. . When the scroll wrap 10b of the fixed scroll 10 and the scroll wrap 11b of the orbiting scroll 11 are engaged with each other, the end plate 10a and the end plate 11a become parallel, and the protruding end of the scroll wrap 10b in 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 projecting end of the scroll wrap 10b, an airtight chip seal (not shown) that obstructs the circulation of the refrigerant gas in the gap between the end plate 11a and the end is provided, and the projecting end of the scroll wrap 10b has a chip seal. Via the end plate 11a. A similar tip seal (not shown) is also embedded in the protruding end of the scroll wrap 11b, and the protruding end of the scroll wrap 11b contacts the end plate 10a via the tip seal.

  The fixed scroll 10 and the orbiting scroll 11 have a plurality of locations where the side surfaces of the scroll wraps 10b and 11b except for the projecting ends are different in the circumferential direction with the circumferential angles of the scroll wraps 10b and 14b shifted from each other. So that both end plates 10a, 11a and both scroll wraps 10b, 11b are fluid pockets that are crescent-shaped sealed spaces when viewed from the vertical direction with respect to the end plate 10a (or the end plate 11a). 12 is partially formed.

  The orbiting scroll 11 meshed with the fixed scroll 10 as described above is configured to be capable of revolving orbiting around the central axis of the fixed scroll 10 via a crank mechanism 40 described later in a state in which the rotation is prevented. . As the orbiting scroll 11 revolves and revolves as described above, the fluid pockets 12 partially formed by the both end plates 10a and 11a and the both scroll wraps 10b and 11b are removed from the outer ends of the both scroll wraps 10b and 11b. The volume of the fluid pocket 12 is gradually reduced while moving toward the inner end of the center. Accordingly, 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 includes a cylindrical or columnar rotor (rotor) 22 in which a permanent magnet is disposed in a central space of a cylindrical stator (stator) 21 in which a coil is disposed in a slot of an armature core. 21 is configured to be rotatable while maintaining an air gap with the inner peripheral surface of 21. The rotor 22 is provided with a drive shaft 23 for driving the orbiting scroll 11 on its axis.

  The drive shaft 23 is connected to the end plate 11a of the orbiting scroll 11 via a crank mechanism 40, and the electric motor 20 is rotated when the rotor 22 rotates around the axis due to the interaction of electromagnetic force between the rotor 22 and the stator 21. 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. Is possible.

  The crank mechanism 40 is eccentric to a cylindrical boss portion 41 projecting from the end plate 11a toward the side opposite to the scroll wrap 11b and a crank 23b provided at one shaft end portion 23a of the drive shaft 23. And an eccentric bush 42 attached in a state. The eccentric bush 42 is rotatably supported in the boss portion 41. Although not shown in the drawings, the compressor 1 is provided with a rotation prevention mechanism for preventing the rotation of the orbiting scroll 11, and the rotation of the orbiting scroll 11 is prevented from rotating through the crank mechanism 40. It is configured to be capable of revolving around the central axis of the fixed scroll 10. A balancer weight 43 is attached to one shaft end 23 a of the drive shaft 23 to cancel the centrifugal force generated when the orbiting scroll 11 is revolving.

  The housing of the compressor 1 includes a front housing 50 that houses the electric motor 20 and the inverter 30, an inverter cover 60, a center housing 70 that houses 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 with the center housing 70 interposed therebetween.

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

  The front housing 50 includes a substantially cylindrical peripheral wall portion 51 and a partition wall portion 52 that partitions 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 housed and fixed in the peripheral wall portion 51 on the one end opening side from the partition wall portion 52 with the drive shaft 23 facing the center housing 70 from the front housing 50, and the peripheral wall on the other end opening side from the partition wall portion 52. The inverter 30 is accommodated and fixed in the part 51.

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

  The center housing 70 includes a substantially cylindrical peripheral wall portion 71, an annular inner flange portion 72 that protrudes inward from the inner surface of the peripheral wall portion 71 and opens toward the front housing 50, and an opening peripheral edge portion of the inner flange portion 72. And a bowl-shaped bulging portion 73 that bulges 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 a peripheral wall portion 71 on one end opening side with respect to the inner flange portion 72. The surface of the inner flange portion 72 on the one end opening side is in contact with the end plate 11 a of the orbiting scroll 11 via the annular thrust plate 74 to support the orbiting scroll 11 in the thrust direction of the drive shaft 23.

  The back pressure chamber 6 formed by being surrounded by the bulging portion 73 and the end plate 11a accommodates the crank mechanism 40 and a bearing portion 75 that pivotally supports the drive shaft 23. . 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 meshed with the orbiting scroll 11 closes one end opening of the peripheral wall portion 71.

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

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

  On the outlet side of the discharge hole 7, a one-way valve V for preventing the discharged refrigerant gas (discharged refrigerant gas) from flowing back into the compression chamber 4 is provided. 4 is configured to be fastened to the end plate 10a of the fixed scroll 10 by fastening means such as a bolt, which closes the discharge hole 7 when it flows backward to 4.

  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 is in contact with one end opening in the peripheral wall portion 71 of the center housing 70 and the end plate 10 a of the fixed scroll 10. The discharge port 5 that is in contact with each other to form an internal space and communicates the internal space with the outside is provided on the side of the peripheral wall portion 82 of the rear housing 80 that is close to the bottom portion 81. The compressor 1 is installed with the discharge port 5 facing 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. A partition wall 86 is provided in the internal space of the rear housing 80 so as to face the bottom 81 and the end plate 10a. The partition wall 86 discharges the internal space of the rear housing 80 from the first separation chamber 83, which is a space on the discharge hole 7 side communicating with the compression chamber 4 via the discharge hole 7, and to the outside via the discharge port 5. It is partitioned 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 through the flow passage L2 that penetrates the partition wall 86 in the upper portions 83a and 84a while maintaining the same vertical direction. Therefore, the refrigerant flow path formed until the discharged refrigerant gas discharged from the compression chamber 4 through the discharge hole 7 is discharged to the outside from the discharge port 5 is the first separation chamber 83, the flow passage L2, the second passage. The separation chamber 84 and the discharge port 5 are configured in this order, and the first oil separator 90 and the second oil separator 91 are arranged in series in this refrigerant flow path as viewed in the refrigerant flow direction.

  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. The first oil separator 90 promotes the separation of oil from the discharged refrigerant gas by the collision with the collision target 83b in the first separation chamber 83, and selectively lowers the separated oil by the relative specific gravity difference. Perform oil separation.

  The collision object 83 b is provided so that the discharged 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 83b is configured as, for example, a substantially U-shaped collision wall that stands from the end plate 10a and surrounds the lower side of the periphery of the discharge hole 7. Note that the discharged refrigerant gas may directly collide from the discharge hole 7 to the partition wall 86, the peripheral wall portion 82, and the like.

  In the first separation chamber 83, the discharged refrigerant gas is allowed to fall from the discharged refrigerant gas at a position that is not above the collision target 83 b (for example, the lowermost position of the collision target 83 b or below it). Is provided (particularly, the discharged refrigerant gas that has collided with the collision object 83b enters the lower part 83c of the first separation chamber 83). The shield 83d is 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 lowest position of the collided body 83b, for example. Is 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 from the first separation chamber 83 into the second separation chamber 84 via the flow path L2, and the oil contained in the discharged refrigerant gas due to a relative specific gravity difference. Centrifuging is promoted, and the separated oil is lowered to perform oil separation. The oil separation capability of the second oil separator 91 that is the centrifugal separation method is about 4 than the oil separation capability of the first oil separator 90 that is the collision separation method over the entire operation range from the low flow rate to the high flow rate of the compressor 1. It has been proved by experiments and the like that it is about 5 times higher. 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 an inner tube 84c substantially coaxial with the second separation chamber 84 opens one end into the second separation chamber 84, and at the other end. The discharged refrigerant gas is oriented 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 cannula 84c from a substantially tangential direction of the second separation chamber 84.

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

  The second oil passage 93 includes a shaft through hole 93a formed through the back pressure chamber 6 from the one shaft end 23a to the other shaft end 23c in the drive shaft 23, and the shaft through hole 93a is interposed therebetween. The suction chamber 3 is formed. The second oil passage 93 includes a throttle hole (passage resistance portion) 93b that opens into the back pressure chamber 6 and has a passage cross-sectional area that is smaller than that of the shaft through hole 93a. The throttle hole 93b functions as an orifice that depressurizes and accelerates 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 refrigerant gas discharged from the compression chamber 4 through the discharge hole 7 to the first separation chamber 83 (indicated by broken arrows in FIG. 2) is first promoted to separate oil in the first oil separator 90. . Specifically, the discharged refrigerant gas discharged into the first separation chamber 83 collides with the collision target 83b in the first separation chamber 83, and the oil separated from the discharged refrigerant gas (the white arrow in FIG. 2) Is lowered to the lower part 83c of the first separation chamber 83 due to the relative specific gravity difference.

  At this time, the oil separated from the discharged refrigerant gas descends to the lower part 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 after the collision with the collision target 83b, and part of the discharged refrigerant gas falls. However, due to the shield 83d, part of the discharged refrigerant gas is in the first separation chamber 83. Since the entry to the lower portion 83c of the fuel 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 lowered to the lower portion 83c of the first separation chamber 83 flows to the refrigerant suction side in the compression chamber 4 via the first oil flow path 92, and is fixed to the fixed scroll 10 and the orbiting scroll. 11 is mainly lubricated. That is, the first oil passage 92 is formed from the first separation chamber 83 to the compression chamber 4.

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

  The oil that has been separated by the second oil separator 91 and descended to the lower part 84d of the second separation chamber 84 flows into the back pressure chamber 6 through the second oil passage 93, and is connected to the crank mechanism 40, the thrust plate 74, the bearing portion. 75, the object to be lubricated having a sliding portion such as the drive shaft 23 is lubricated, depressurized / accelerated through the throttle hole 93b, and then circulated into the suction chamber 3 through the shaft through hole 93a. That is, the second oil flow path 93 is formed from the second separation chamber 84 to the suction chamber 3 and has a flow path length several times longer than the first oil flow path 92. There are many lubrication targets.

  The oil flowing into the suction chamber 3 is mixed into the refrigerant gas sucked into the suction chamber 3 from the suction port 2. The suction refrigerant gas containing oil is led to the compression chamber 4 through the refrigerant introduction passage L1 after flowing through the electric motor 20. On the other hand, the discharged refrigerant gas starts to rise toward one end opening of the outflow pipe as the turning motion becomes smaller, and is discharged from the discharge port 5 toward the system such as the vehicle air conditioner system through the outflow pipe.

  As described above, the compressor 1 of the present embodiment, as shown in FIG. 3, discharges the discharged refrigerant gas discharged from the compression chamber 4 through the discharge hole 7 after being compressed by the compression mechanism through the discharge port 5. Through the refrigerant flow path 94 (shown by a solid line in FIG. 3) until it is discharged to a system such as an external vehicle air conditioner system. The refrigerant channel 94 includes a first oil separator 90 (shown as a collision separation OS in FIG. 3) and a second oil separator 91 (shown as a centrifugal separation OS in FIG. 3) having different oil separation capabilities. They are arranged in series in this order.

  Then, the oil separated by the first oil separator 90 is circulated to the suction side of the suction refrigerant gas in the compression chamber 4 through the first oil flow path 92 (shown by a broken line in FIG. 3). Further, the oil separated by the second oil separator 91 having a higher oil separation capacity than the first oil separator 90 is circulated to the back pressure chamber 6 via the second oil passage 93 (shown by a one-dot chain line in FIG. 3). The pressure is reduced and accelerated through the throttle hole 93b to lubricate the object to be lubricated, and then circulates to the suction chamber 3 side.

  This makes it difficult for the oil separated by the first and second oil separators 90 and 91 to be affected by the pressures of the first and second separation chambers 83 and 84, so that the compressor can be operated from a low flow rate to a high flow rate. The oil flow can be appropriately maintained over the entire area. Therefore, it is possible to prevent oil backflow and stagnation throughout the entire operation of the compressor 1 and maintain the oil flow appropriately.

  Further, as described above, the second oil separator 91 has a higher oil separation capability 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. Tend to be more. As a result, a relatively large amount of oil separated by the second oil separator 91 has a longer channel length than the first oil channel 92 and has many objects to be lubricated, that is, preferentially to the second oil channel 93 having a high lubrication requirement. It can be distributed. Therefore, in the second oil passage 93 having a relatively long passage length, it is possible to prevent the oil film to be lubricated from being cut.

  On the other hand, even if the amount of oil separated by the first oil separator 90 is relatively small, a lubrication request is made during the operation of the compressor 1 through the first oil passage 92 that is shorter than the second oil passage 93. In particular, it can be supplied directly and quickly to a high compression mechanism. In this way, the oil separation capacity of the first and second oil separators 90 and 91, the lubrication requirements of each part of the compressor 1, and the appropriate distribution of oil according to the requirement type are performed, so that the entire operation range of the compressor 1 is achieved. Since the oil separation capability can be increased over time and the lubrication performance of the compressor 1 can be improved, the OCR in the compressor 1 is improved, the durability of the compressor 1 is improved, the performance of the compressor 1 is improved, and the compressor The improvement of the operation efficiency of the system using 1 can be realized.

Second Embodiment
FIG. 4 is an enlarged cross-sectional view of the interior of the rear housing 80 according to the 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. The compressor 1 of the present embodiment includes an oil storage chamber 95 that stores oil separated and lowered in the first separation chamber 83 and an oil storage chamber that stores oil separated and lowered in the second separation chamber 84 in the internal space of the rear housing 80. 96.

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

Further, the first oil passage 92 is formed with a throttle hole (passage resistance portion) 92a having a reduced passage sectional area. The throttle hole 92a is formed in the first oil passage 92 so as to straddle, for example, the peripheral wall portion 82 of the rear housing 80 and the peripheral wall portion 71 of the center housing 70, and the oil flowing through the first oil passage 92 is decompressed and accelerated. Function as an orifice.
As shown in FIG. 5, the compressor 1 of this embodiment has a first oil separator 90 (shown as a collision separation OS in FIG. 5) in the refrigerant flow path 94 shown by a solid line, as in the case of the first embodiment. And a second oil separator 91 (shown as a centrifugal separation OS in FIG. 5) is arranged in series in this order.

  The oil separated in the first oil separator 90 is disposed in the first oil flow path 92 (shown by a broken line in FIG. 5), and the suction refrigerant gas in the compression chamber 4 is sequentially passed through the throttle hole 92a. Distribute to the suction side. Further, the oil separated by the second oil separator 91 having a higher oil separation capacity than the first oil separator 90 is passed through an oil storage chamber 96 arranged in a second oil flow path 93 (shown by a one-dot chain line in FIG. 5). After flowing through the back pressure chamber 6 and depressurizing and accelerating through the throttle hole 93b 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 92a and 93b that are independent of each other in both the first oil passage 92 and the second oil passage 93. . Accordingly, in the first and second oil flow paths 92 and 93, the oil can be supplied to the lubrication target quickly from the throttle holes 92a and 93b while appropriately holding the oil in the oil storage chambers 95 and 96. Accordingly, it is possible to more efficiently distribute the oil according to the oil separation ability of the first and second oil separators 90 and 91 and the lubrication requirements of each part of the compressor 1.

Although the description of each embodiment of the present invention has been completed above, 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 embodiments described above, 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 the first oil separator 90 and the second oil separator 91 may be interchanged as shown in FIG. 6 as a modification of the second embodiment.

  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 through the first oil flow path 92. Since the oil that has flowed to the refrigerant suction side in the chamber 4 and separated by the second oil separator 91 flows individually to the suction chamber 3 side through the second oil flow path 93, the same effects as those of the above-described embodiments Can be played.

  As shown in FIG. 7, the first oil separator 90 and the second oil separator 91 may both be centrifugal oil separators as long as they have different oil separation capabilities. Specifically, the first centrifugal separation OS shown in FIG. 7 has a specification with higher oil separation capability than the second centrifugal separation OS, and the oil separated by the second centrifugal separation OS passes through the first oil flow path 92. Then, the oil is circulated to the refrigerant suction side in the compression chamber 4 and the oil separated by the second centrifugal separation OS is circulated to the suction chamber 3 side through the second oil flow path 93, so that the same as in the above embodiments. There is an effect.

  Further, as shown in FIG. 8, the first oil separator 90 and the second oil separator 91 may both 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 with higher oil separation capability than the second collision separation OS, and the oil separated by the second collision separation OS passes through the first oil flow path 92. Then, the oil is circulated to the refrigerant suction side in the compression chamber 4 and the oil separated by the second collision separation OS is circulated to the suction chamber 3 side via the second oil flow path 93, so that the same as in the above embodiments. There is an effect.

  6 to 8 can also be applied to the compressor 1 that does not include the oil storage chambers 95 and 96 as described in the first embodiment. Further, depending on the specifications of the compressor 1, there may be a form in which only one of the oil storage chambers 95, 96 is formed, or a form in which only one of the throttle holes 92a, 93b is formed. Further, instead of means for reducing the passage sectional area such as the throttle holes 92a and 93b, other means for passage resistance may be provided in the first and second oil 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 is relatively large, In the oil flow path 93, it is preferably 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 has been described as discharge refrigerant gas. However, the discharge refrigerant may include not only a gas phase refrigerant but also a liquid phase refrigerant.
Further, the first and second oil separators 90 and 91 may be of a separation method other than the collision separation method or the centrifugal separation method as long as the oil separation ability is different.

  Further, if it is a premise including at least the first and second oil separators 90 and 91, one or more oil separators may be additionally provided on condition that the pressure loss of the discharged refrigerant does not become excessive. In this case, considering the oil separation ability of the added oil separator, it is determined whether the oil separated by the oil separator is to be circulated through the first oil passage 92 or the second oil passage 93. The

  In each of the above embodiments, the first oil passage 92 is formed in the peripheral wall portion 82 of the rear housing 80 and the peripheral wall portion 71 of the center housing 70. However, the present invention is not limited to this, and the first oil passage 92 may be formed in the end plate 11 a of the fixed scroll 10 and communicated with the first separation chamber 83 and the refrigerant suction side in the compression chamber 4. However, in this case, it is necessary to form the swirl scroll 11 at a position where the scroll wrap 11b of the orbiting scroll 11 does not interfere with the first oil passage 92 due to the orbiting of the orbiting scroll 11.

  Further, in each of the above 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 built in. It demonstrated as what compresses refrigerant | coolant gas by making it turn. However, instead of the built-in electric motor 20, the orbiting scroll 11 may be turned 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.
Further, in each of the above embodiments, the compressor 1 has been described as a hermetic 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.

  Further, instead of the scroll compressor that compresses the refrigerant gas by the fixed scroll 10 and the orbiting scroll 11, a reciprocating compressor that compresses the refrigerant gas by changing the volume of the cylinder due to the reciprocating movement of the piston, and a plurality of vanes in the side surface in the housing. The present invention can be applied to any compression type compressor such as a rotary vane type compressor that compresses refrigerant gas by rotating the rotor having the vane in contact with the inner wall of the housing.

DESCRIPTION OF SYMBOLS 1 Compressor 3 Suction chamber 4 Compression chamber 83b Colliding body 90 1st oil separator 91 2nd oil separator 92 1st oil flow path 92a Restriction hole (passage resistance part)
93 Second oil passage 93b Restriction hole (passage resistance)
94 Refrigerant flow path 95 Oil storage chamber 96 Oil storage chamber

Claims (6)

An intake chamber for inhaling refrigerant containing oil;
A compression chamber for compressing the refrigerant sucked into the suction chamber;
A refrigerant flow path formed until the discharged 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 flowing oil separated by the first oil separator to a refrigerant suction side in the compression chamber;
A compressor comprising: a second oil flow path through which oil separated by the second oil separator flows to the suction chamber side.   The compressor according to claim 1, wherein the second oil separator has a higher oil separation capability 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 and separate and lower the oil.   The compressor according to claim 2 or 3, 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, further comprising a passage resistance portion in at least one of the first and second oil flow paths.   The compressor according to any one of claims 1 to 5, further comprising an oil storage chamber in at least one of the first and second oil flow paths.

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