WO2018008368A1

WO2018008368A1 - Compressor

Info

Publication number: WO2018008368A1
Application number: PCT/JP2017/022432
Authority: WO
Inventors: 好信前村; 美早子冠城; 芳夫小和田; 宏本田; 淳夫手島; 和博生方
Original assignee: サンデン・オートモーティブコンポーネント株式会社
Priority date: 2016-07-05
Filing date: 2017-06-13
Publication date: 2018-01-11
Also published as: JP2018003736A

Abstract

In order to reduce variation in oil separation efficiency due to changes in the flow volume of a discharged coolant, a first separation chamber 83, which uses a collision separation method wherein the discharged coolant gas collides with a collision body 83b and lubricating oil is separated and dropped down, and a second separation chamber 84, which uses a centrifugal separation method wherein the discharged coolant gas is made to swirl and the lubricating oil is separated and dropped down, are arranged in series in a flow path through which a discharged coolant gas discharged from a compression chamber 400 via a discharge hole 700 is exhausted to the outside via an exhaust port 500. When the flow volume of the discharged coolant gas increases, the oil separation efficiency in the first separation chamber 83 using the collision separation method decreases, but the oil separation efficiency in the second separation chamber 84 using the centrifugal separation method increases. Conversely, when the flow volume of the discharged coolant gas decreases, the oil separation efficiency in the second separation chamber 84 using the centrifugal separation method decreases, but the oil separation efficiency in the first separation chamber 83 using the collision separation method increases.

Description

Compressor

The present invention relates to a compressor having a function of separating lubricating oil contained in refrigerant gas.

In a compressor used in a conventional vehicle air conditioner system or the like, lubricating oil is mixed in refrigerant gas to lubricate each part of the compressor. However, when the lubricating oil flows out to an external refrigerant circuit for heat exchange, the system Since the efficiency is lowered, it is required to reduce the amount of lubricating oil flowing out from the compressor to the external refrigerant circuit.
For this reason, the compressor is provided with a collision separation type separation chamber for intentionally colliding the discharged refrigerant gas discharged from the compression mechanism with the internal structural member of the compressor and separating the lubricating oil in the discharged refrigerant gas. Have been proposed (for example, see Patent Document 1) and those equipped with a centrifugal separation chamber for rotating the discharged refrigerant gas to centrifuge the lubricating oil in the discharged refrigerant gas (for example, see Patent Document 2). ing.

JP 2010-031655 A JP 2009-13827 A

However, in the separation chamber of the collision separation type, the oil separation efficiency tends to decrease as the flow rate of the discharged refrigerant gas increases, whereas in the separation chamber of the centrifugal separation type, the oil separation occurs as the flow rate of the discharged refrigerant gas decreases. Since the efficiency tends to decrease, the oil may not be efficiently separated depending on the change in the flow rate of the discharged refrigerant gas.
In view of the above-described conventional problems, an object of the present invention is to provide a compressor that suppresses fluctuations in oil separation efficiency due to changes in the flow rate of discharged refrigerant.

In order to achieve the above object, the compressor of the present invention discharges the discharged refrigerant to the outside after the separation process of the contained oil is performed. A first separation chamber that separates and lowers and a second separation chamber that swirls the discharged refrigerant and separates and lowers the contained oil until the discharged refrigerant is discharged to the outside. Are arranged in series in the flow path. Here, the “discharge refrigerant” is a concept that can include a liquid phase refrigerant in a gas phase refrigerant.

According to the compressor of the present invention, in the flow path until the discharged refrigerant is discharged to the outside, the discharged refrigerant is caused to collide with the colliding body to separate and lower the contained oil, and the discharged refrigerant is swirled and contained. Since the second separation chamber that separates and lowers the oil is arranged in series, fluctuations in the oil separation efficiency due to changes in the flow rate of the discharged refrigerant can be suppressed.

It is sectional drawing which shows typically the whole structure of the compressor which concerns on embodiment of this invention. It is sectional drawing to which the inside of the center housing in the compressor was expanded. It is sectional drawing to which the inside of the rear housing in the same compressor was expanded. It is explanatory drawing which shows typically the to-be-collided body in the compressor.

Hereinafter, embodiments for carrying out the present invention will be described in detail with reference to the accompanying drawings.
FIG. 1 shows an example of a compressor according to an embodiment of the present invention.
The compressor 100 is used by being 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 or the like. In the refrigerant circuit, the compressor 100 includes a refrigerant gas in which the liquid phase refrigerant radiated and condensed by the condenser is decompressed and expanded by the downstream expansion valve and partially evaporated, and the remaining liquid phase refrigerant is evaporated downstream of the expansion valve. The refrigerant gas that has been vaporized by removing heat from ambient air in the condenser is compressed and heated, and then pumped toward the condenser, whereby the refrigerant circulates in the refrigerant circuit. In the compressor 100, lubricating oil (containing oil) is mixed into the refrigerant gas in order to lubricate each part of the compressor 100.
The compressor 100 compresses the refrigerant gas sucked into the suction chamber 300, the suction port 200 which is a suction port for sucking the refrigerant gas from the outside, the suction chamber 300 for sucking the refrigerant gas through the suction port 200, and the suction chamber 300. A compression chamber 400 and a discharge port 500 that is a discharge port for discharging refrigerant gas discharged from the compression chamber 400 to the outside. Is a scroll type electric compressor that compresses the refrigerant gas by rotating the other using the rotational force of the electric motor 20. One fixed spiral body is referred to as a fixed scroll 10, and the other spiral body to be rotated is referred to as a rotary scroll 11. The compressor 100 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 14b 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. Thus, both end plates 10a, 14a and both scroll wraps 10b, 14b are fluid pockets which 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 described later in a state in which the rotation is prevented. As the orbiting scroll 11 revolves as described above, the fluid pockets 12 partially formed by the both end plates 10a and 14a and the both scroll wraps 10b and 14b are formed from the outer ends of the both scroll wraps 10b and 14b. 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 both scroll wraps 10b, 14b 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, which will be described later. When the rotor 22 rotates around the axis due to the interaction of electromagnetic force between the rotor 22 and the stator 21, the electric motor Twenty rotational forces are 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 the external control device, and can arbitrarily change the rotation speed of the rotor 22.
As shown in FIG. 2, the crank mechanism 40 has a cylindrical boss 41 projecting from the end plate 11 a toward the opposite side of the scroll wrap 11 b and one shaft end 23 a of the drive shaft 23. And an eccentric bush 42 attached to the provided crank 23b in an eccentric state. The eccentric bush 42 is rotatably supported in the boss portion 41. Although not shown in the drawings, the compressor 100 is provided with a rotation prevention mechanism for preventing the rotation of the orbiting scroll 11, so that the rotation of the orbiting scroll 11 is inhibited via 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 that cancels the centrifugal force generated when the orbiting scroll 11 is turned is attached to one shaft end 23 a of the drive shaft 23.
The housing of the compressor 100 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, and 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. It has a cylindrical support portion 53 that supports the shaft end portion 23c.
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 600 formed by being surrounded by the bulging portion 73 and the end plate 11a accommodates the crank mechanism 40 and extends from the electric motor 20 of the front housing 50 and passes through the bulging portion 73. A bearing portion 75 that pivotally supports the shaft 23 is disposed. 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 200 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 300 for sucking the refrigerant through the suction port 200 is connected to the peripheral wall portion 51 of the front housing 50 and the partition wall. The wall portion 52 and the peripheral wall portion 71, the inner flange portion 72, and the bulging portion 73 of the center housing 70 are surrounded. Further, the compression chamber 400 is formed by being surrounded by the end plate 10 a, the peripheral wall 71 on the opening side from the inner flange 72, the inner flange 72, and the end plate 11 a that closes the opening of the inner flange 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 300 to the compression chamber 400. The end plate 10 a of the fixed scroll 10 is formed with a discharge hole 700 for discharging the refrigerant gas compressed in the fluid pocket 12 to the outside of the compression chamber 400 at the inner end of the scroll wrap 10 b. On the outlet side of the discharge hole 700, a one-way valve V for preventing the discharged refrigerant gas (discharged refrigerant gas) from flowing back into the compression chamber 400 is provided. An elastically deformable valve element that closes the discharge hole 700 when backflowing to 400 is fastened to the end plate 10a 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 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. A discharge port 500 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 82 of the rear housing 80 that is close to the bottom 81. The compressor 100 is installed with the discharge port 500 facing upward.
Here, as shown in FIG. 3, the compressor 100 includes a first separation chamber 83 and a second separation chamber 84 that separate and lower the lubricating oil from the discharged refrigerant gas in the inner space of the rear housing 80. An oil storage chamber 85 is provided which is arranged in series in a flow path from the discharge port 500 to the outside and stores lubricating oil (separated oil) separated and lowered in the first separation chamber 83 and the second separation chamber 84. Prepare.
The rear housing 80 includes a partition wall 86 that divides an internal space into a discharge hole 700 side space communicating with the compression chamber 400 via the discharge hole 700 and a discharge port 500 side space communicating with the outside via the discharge port 500. It is provided facing the bottom 81 and the end plate 10a. The first separation chamber 83 is formed by the space on the discharge hole 700 side, the second separation chamber 84 is formed by the space on the discharge port 500 side, and the first separation chamber 83 and the second separation chamber 84 have the same vertical direction. However, the

upper portions

83a and 84a communicate with each other through the flow passage L2 that penetrates the partition wall 86. Therefore, the flow path from when the discharge refrigerant gas discharged from the compression chamber 400 through the discharge hole 700 is discharged to the outside through the discharge port 500 is the first separation chamber 83, the flow passage L2, the second separation chamber 84, The discharge port 500 is configured in this order.
The first separation chamber 83 has a collided body 83b for colliding the discharged refrigerant gas discharged from the compression chamber 400 through the discharge hole 700, and lubricating oil from the discharged refrigerant gas due to the collision with the collided body 83b. This is a collision separation type separation chamber in which the separation of the lubricating oil is promoted, and the separated lubricating oil is selectively lowered by the relative specific gravity difference to perform the separation processing of the lubricating oil. The collision object 83 b is provided so that the discharged refrigerant gas discharged from the discharge hole 700 does not scatter to the lower part 83 c of the first separation chamber 83. As shown in FIG. 4, for example, the collision object 83b in the present embodiment has the discharge hole 700 (or one-way valve V) so that the discharged refrigerant gas is discharged from the discharge hole 700 in the radial direction (see the broken line arrow). After forming with a configuration not shown in the figure, the discharge refrigerant gas discharged in the radial direction from the discharge hole 700 collides and scatters from the end plate 10a so as to be scattered outside the lower part 83c of the first separation chamber 83. It is configured as a substantially U-shaped collision wall surrounding the lower side of the periphery of the hole 700. Note that the discharged refrigerant gas may directly collide from the discharge hole 700 to the partition wall 86, the peripheral wall portion 82, and the like.
In the first separation chamber 83, the discharged refrigerant is allowed to fall in the lubricating oil separated 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). A shielding body 83d is provided for suppressing gas lowering (particularly, the discharge refrigerant gas that has collided with the collision target 83b enters the lower portion 83c of the first separation chamber 83). The shield 83d in the present embodiment extends from the partition wall 86 toward the end plate 10a at the lowermost position of the collided body 83b, and has a gap between the end plate 10a (including the collided body 83b). Configured as
The second separation chamber 84 swirls the discharged refrigerant gas introduced from the first separation chamber 83 via the flow path L2, and promotes centrifugal separation of the lubricating oil contained in the discharged refrigerant gas by a relative specific gravity difference. In addition, the separation chamber is a centrifugal separation system in which the separated lubricating oil is lowered to separate the lubricating oil. In the present embodiment, the second separation chamber 84 has an inner peripheral surface 84b having a substantially circular cross section, and an intubation tube 84c substantially coaxial with the second separation chamber 84 opens one end into the second separation chamber 84, and the like. The end is connected to the discharge port 500. The flow path L2 is formed in the upper portion 84a of the second separation chamber 84 between the inner peripheral surface 84b of the second separation chamber 84 and the outer peripheral surface of the inner tube 84c from the substantially tangential direction of the second separation chamber 84. Oriented to be introduced.
In the internal space of the rear housing 80, the oil storage chamber 85 is located at substantially the same height or lower than the lowest position of the first separation chamber 83 and the second separation chamber 84. It is formed independently of the second separation chamber 84, communicates with the lower portion 83c of the first separation chamber 83 through the first communication passage E1, and communicates with the lower portion 84d of the second separation chamber 84 through the second communication passage E2. The relationship between the passage resistance of the first communication passage E1 and the passage resistance of the second communication passage E2 is, for example, by making the passage cross-sectional area of the first communication passage E1 smaller than the passage cross-sectional area of the second communication passage E2. The passage resistance of the first communication passage E1 is set to be higher than the passage resistance of the second communication passage E2.
Further, the oil storage chamber 85 is a back pressure chamber 600 by a first oil return passage R1 formed in the peripheral wall portion 82 of the rear housing 80 and the peripheral wall portion 71 and flange portion (including the bulging portion 73) of the center housing 70. Communicate with. The back pressure chamber 600 communicates with the suction chamber 300 by a second oil return passage R2 formed through the drive shaft 23 from one shaft end 23a to the other shaft end 23c.
Next, an oil separation process for separating the lubricating oil from the discharged refrigerant gas in the compressor 100 will be described with reference to FIG.
Discharged refrigerant gas (indicated by broken line arrows in the figure) discharged from the compression chamber 400 to the first separation chamber 83 through the discharge hole 700 collides with the collision target 83b in the first separation chamber 83, Separation of the contained lubricating oil is promoted. Then, the lubricating oil separated from the discharged refrigerant gas (indicated by the white arrow in the figure) falls to the lower portion 83c of the first separation chamber 83 due to the relative specific gravity difference. At this time, the lubricating 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 discharged refrigerant gas that has undergone the collision separation type oil separation process in the first separation chamber 83 is introduced into the second separation chamber 84 via the flow passage L2 of the upper portion 83a. Since the discharged refrigerant gas introduced into the second separation chamber 84 may contain lubricating oil that could not be separated in the first separation chamber 83, further oil separation processing is performed in the second separation chamber 84. Thus, oil separation efficiency can be increased.
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 in a spiral manner, the lubricating oil contained in the discharged refrigerant gas is Centrifugal separation is performed by the relative difference in specific gravity, and the separated lubricating oil descends along the inner peripheral surface 84b to the lower portion 84d of the second separation chamber 84. On the other hand, the discharged refrigerant gas starts to rise toward the one end opening of the outflow pipe as the turning motion becomes smaller, and is discharged from the discharge port 500 through the outflow pipe.
The separated oil that has dropped to the lower portion 83c of the first separation chamber 83 flows into the oil storage chamber 85 via the first communication passage E1, and the separation oil that has fallen to the lower portion 84d of the second separation chamber 84 passes through the second communication passage E2. Then, the oil flows into the oil storage chamber 85 and the separated oil is stored in the oil storage chamber 85. At this time, since the passage resistance of the first communication passage E1 is higher than the passage resistance of the second communication passage E2, the separation oil flowing into the oil storage chamber 85 is affected by the internal pressure of the first separation chamber 83, and the second resistance The possibility of backflow to the second separation chamber 84 via the communication path E2 is reduced. The separated oil stored in the oil storage chamber 85 due to the internal pressure difference between the suction chamber 300 and the oil storage chamber 85 is further supplied to the back pressure chamber 600 via the first oil return passage R1 with reference to FIG. The lubricating oil is used for lubrication of the sliding mechanism such as the portion 75, and is further returned from the back pressure chamber 600 to the suction chamber 300 through the second oil return passage R2 and sucked through the suction port 200. It is mixed.
Here, when the rotational speed of the electric motor 20 is increased and the flow rate of the discharged refrigerant gas discharged from the compression chamber 400 through the discharge hole 700 is increased, the oil in the first separation chamber 83 of the collision separation method is oiled. Although the separation efficiency is lowered, the oil separation efficiency is increased in the second separation chamber 84 of the centrifugal separation method, so that the oil separation efficiency is higher than that in the case where the compressor 100 includes only the first separation chamber 83. The decrease can be suppressed. On the other hand, when the rotational speed of the electric motor 20 decreases and the flow rate of the discharged refrigerant gas discharged from the compression chamber 400 through the discharge hole 700 decreases, the oil separation is performed in the centrifugal separation type second separation chamber 84. Although the efficiency is decreased, the oil separation efficiency is increased in the first separation chamber 83 of the collision separation method, and therefore, the oil separation efficiency is decreased as compared with the case where the compressor 100 includes only the second separation chamber 84. Can be suppressed.
According to such a compressor 100, the discharged refrigerant gas is collided in the flow path until the discharged refrigerant gas discharged from the compression chamber 400 through the discharge hole 700 is discharged to the outside through the discharge port 500. A first separation chamber 83 that collides with the body 83b to separate and lower the lubricating oil, and a second separation chamber 84 that separates and lowers the lubricating oil by swirling the discharged refrigerant gas are connected in series. Since it arrange | positions, the fluctuation | variation of the oil separation efficiency by the flow volume change of discharge refrigerant gas can be suppressed. Therefore, regardless of the flow rate of the discharged refrigerant gas, the amount of lubricating oil flowing out from the compressor 100 to the external refrigerant circuit is suppressed to a certain level, thereby suppressing a decrease in system efficiency of a vehicle air conditioner system to which the compressor 100 is applied. It becomes possible to do.
In the above-described embodiment, the compressor 100 includes the first separation chamber 83 and the second separation chamber 83 for separating and lowering the lubricating oil from the discharged refrigerant gas in the flow path until the discharged refrigerant gas is discharged from the discharge port 500 to the outside. The separation chambers 84 are arranged in series in this order. However, the present invention is not limited to this, and the second separation chamber 84 and the first separation chamber 83 are replaced by replacing the first separation chamber 83 and the second separation chamber 84. Even if they are arranged in series in this order, the same effects as in the above embodiment can be obtained.
When the second separation chamber 84 and the first separation chamber 83 are arranged in series in this order, the discharge hole 700 is formed so that the discharged refrigerant gas is discharged from the substantially tangential direction of the second separation chamber 84 in the upper portion 84a of the second separation chamber 84. 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 intubation tube 84c. The other end of the inner tube 84c having one end opened into the second separation chamber 84 is connected to the flow path L2. Further, the collision object 83b of the first separation chamber 83 is provided so that the discharged refrigerant gas introduced into the first separation chamber 83 from the flow passage L2 collides, for example, the outlet of the flow passage L2 is in the radial direction. It may be configured as a substantially U-shaped collision object 83b which is formed so as to have a structure to be discharged and which stands up from the partition wall 86 and surrounds the lower side of the periphery of the outlet of the flow path L2. A discharge port 500 is provided in the upper part 83 a of the first separation chamber 83.
As mentioned above, although the invention made | formed by this inventor was concretely demonstrated based on said embodiment, this invention is not limited to said embodiment, A various change is possible in the range which does not deviate from the summary. Needless to say. For example, although the discharge refrigerant discharged from the discharge hole 700 of the compressor 100 has been described as the discharge refrigerant gas, the discharge refrigerant may include not only a gas phase refrigerant but also a liquid phase refrigerant.
Further, in the above embodiment, the compressor 100 meshes the pair of fixed scrolls 10 and the orbiting scroll 11 having the same shape in the compression chamber 400 and turns the orbiting scroll 11 using the rotational force of the built-in electric motor 20. It demonstrated as what compresses refrigerant | coolant gas by damaging. 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 100 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. Alternatively, 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 motion of the piston, or a plurality of vanes in the housing. The present invention can be applied to any compression type compressor such as a rotary vane type compressor that compresses the refrigerant gas by rotating the rotor on the side surface while bringing the vane into contact with the inner wall of the housing.

83 First separation chamber

83b Colliding body

83d Shielding body 84 Second separation chamber 84b Inner peripheral surface 84c Inner tube 85 Oil storage chamber 100 Compressor 400 Compression chamber 500 Discharge port 700 Discharge hole L2 Flow passage E1 First communication passage E2 Second Communication path

Claims

A compressor that discharges discharged refrigerant to the outside after separation of contained oil is performed,
A first separation chamber that separates and lowers the contained oil by causing the discharged refrigerant to collide with a collision target;
A second separation chamber that swirls the discharged refrigerant to separate and lower the contained oil,
The first separation chamber and the second separation chamber are compressors arranged in series in a flow path until the discharged refrigerant is discharged to the outside.
The compressor according to claim 1, wherein the first separation chamber and the second separation chamber are arranged in series in a flow path until the discharged refrigerant is discharged to the outside in this order.
An oil storage chamber for storing the separated oil separated and lowered in the first separation chamber and the second separation chamber;
The first communication path that communicates the first separation chamber and the oil storage chamber, and the second communication path that communicates the second separation chamber and the oil storage chamber are provided. Compressor.
The compressor according to claim 3, wherein a passage resistance of the first communication passage is larger than a passage resistance of the second communication passage.
The compressor according to any one of claims 1 to 4, wherein the first separation chamber is provided with a shield that prevents the discharge refrigerant from descending while allowing the oil contained to fall.
The compressor according to claim 5, wherein the shield is provided at a position not higher than the collision target in the first separation chamber.