JP2018025154A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress deterioration of vibration of a rotating shaft 25 by suppressing inhibition of rotational motion of a balancer 254 in a scroll compressor 1.SOLUTION: In a scroll compressor 1, volume of a working chamber 15 is changed by revolution of a movable scroll 11 to suck a refrigerant into the working chamber 15 for compression and then a high-pressure refrigerant is discharged from the working chamber 15. The scroll compressor includes: a back pressure chamber 50 for storing the high-pressure refrigerant discharged from the working chamber 15 to generate refrigerant pressure for pressing the movable scroll 11 against a fixation scroll 12; a balancer 254 disposed in the back pressure chamber 50 and driven by a rotating shaft 25 for rotation; and a liquid storage chamber 70 communicated with the back pressure chamber 50 and temporarily storing a liquid-phase refrigerant discharged from the working chamber 15 when the liquid-phase refrigerant is compressed and discharged from the working chamber 15 through the revolution of the movable scroll 11.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a scroll compressor.

  2. Description of the Related Art Conventionally, some scroll compressors include a fixed scroll, a movable scroll that forms a working chamber between the fixed scroll, and a balancer that relieves unbalance of a rotating shaft caused by the movable scroll (for example, a patent). Reference 1).

  In this structure, the movable scroll orbits with respect to the fixed scroll, whereby the refrigerant containing the lubricating oil can be sucked into the working chamber, compressed, and discharged from the working chamber.

  Further, the scroll compressor is provided with a bypass that guides a part of the discharge gas discharged from the working chamber to a back pressure chamber provided on the back side of the movable scroll.

  The discharge gas guided into the back pressure chamber is applied to the movable scroll as a back pressure, and the movable scroll is pressed against the fixed scroll. Thus, by bringing the movable scroll into close contact with the fixed scroll, the airtightness of the movable scroll with respect to the fixed scroll can be increased, and the efficiency of the compression function can be increased.

JP 2007-211702 A

  The present inventor employs a scroll compressor that supplies a part of the refrigerant discharged from the discharge hole to the back pressure chamber and applies the refrigerant pressure from the back pressure chamber as a back pressure to the movable scroll to perform heating operation. The construction of the heat pump system to be implemented was examined.

  First, when applying a scroll compressor to a heat pump system that secures heating capacity using a refrigeration cycle, it is established that the cooling operation and the heating operation are shared by the heat pump system in a low temperature environment that is a necessary temperature band. For this purpose, it is necessary to employ an accumulator cycle.

  Since the required amount of refrigerant differs between cooling operation and heating operation, an accumulator is required as a liquid storage function for storing unnecessary refrigerant. Because of its simplicity, cost, and mounting layout, It is common to install an accumulator in the suction pipe.

  However, in consideration of the operation state, in the heating operation, the time required for warming up the scroll compressor is longer than that in the cooling operation in the transitional region after the heat pump system is activated until the operation state is stabilized. This is because the ambient temperature, operating load, and refrigerant temperature / pressure are low, but with this, the refrigerant state is not stable in the transient region. The liquid-phase refrigerant to be stored in the accumulator temporarily stays in a portion other than the accumulator, for example, a heat exchanger, a scroll compressor, a pipe, or the like that is assumed to have a low temperature or a large heat capacity during the stop.

  Such a problem also occurs when a refrigeration cycle such as a receiver cycle in which a receiver for storing unnecessary refrigerant is disposed between a condenser and a pressure reducing valve is employed.

  In this way, when the heat pump system is started with the liquid phase refrigerant remaining in a part other than the accumulator or receiver, the liquid phase refrigerant is sucked into the scroll compressor while the refrigerant moves to the accumulator in the process of reaching the stable state. Therefore, there is a concern that an operation state that is not the intended operation state such as liquid compression occurs, and the vibration of the scroll compressor is thereby deteriorated.

  In particular, the scroll compressor 1A (FIG. 3, FIG. 3) has a configuration in which a back pressure chamber that bears a back pressure adjustment function that is employed to increase the efficiency of the compression function is provided with a function of accommodating a balancer that reduces rotational vibration of the rotation shaft. In FIG. 4), the following operations and malfunctions can be considered.

  The liquid phase refrigerant sucked into the scroll compressor 1A is sucked into the working chamber 1a at the initial stage of the start-up under the low temperature described above, and then the refrigerant remains in a liquid phase state liquid after being compressed or in a gas-liquid two-layer state. Is discharged.

  A part of the refrigerant discharged from the working chamber 1a is guided to the back pressure chamber 2 through the paths 3a and 3b installed to secure the pressure, and serves as a refrigerant pressure for pressing the movable scroll 1b against the fixed scroll 1c. Back pressure is secured.

  In order not to raise the back pressure more than necessary, there is a discharge path 4 for discharging from the back pressure chamber 2 to the suction chamber 3, and a balance is provided by the differential pressure between the back pressure and the suction pressure and the flow path resistance of the discharge path 4. Designed to keep state.

  However, when the above-described liquid-phase refrigerant flows into the back pressure chamber 2, the balancer 5 is always rotating during the operation of the scroll compressor 1A in the back pressure chamber 2, and the liquid-phase refrigerant is thereby rotated. At the same time, the outer periphery of the back pressure chamber 2 continues to be rotated by centrifugal force.

  On the other hand, the discharge path 4 for extracting the back pressure into the suction chamber 3 is set as a long hole extending in the axial direction of the rotary shaft 1d provided on the rotary shaft 1d for driving the movable scroll 1b. For this reason, while the balancer 5 rotates in the back pressure chamber 2, the liquid-phase refrigerant in the back pressure chamber 2 is not guided to the discharge path 4 provided in the rotating shaft 1d. For this reason, the liquid phase refrigerant in the back pressure chamber 2 can be discharged by evaporating as the temperature of the compressor body and the refrigerant pressure rise.

  For this reason, the liquid refrigerant continues to rotate together with the balancer 5 in the back pressure chamber 2 until the vaporization of the liquid refrigerant is completed. At this time, the liquid refrigerant rotates due to the weight of the liquid refrigerant and the viscous resistance due to the movement. The shaft 1d is unbalanced, and a problem that rotational vibration deteriorates occurs.

  Such a problem may occur not only when the heating operation is performed in a low temperature environment but also when the cooling operation is performed in a low temperature environment.

  In view of the above points, an object of the present invention is to suppress deterioration of vibration of a rotating shaft in a scroll compressor.

In order to achieve the above object, according to the first aspect of the present invention, a working chamber is formed between the fixed scroll (12) and the fixed scroll, and the fixed scroll is driven by being driven by the rotating shaft (25). A scroll compressor including a movable scroll (11) revolving relative to the movable scroll, wherein the revolving motion of the movable scroll changes the capacity of the working chamber, sucks and compresses the refrigerant into the working chamber, and discharges the high-pressure refrigerant from the working chamber. Because
A back pressure chamber (50) for storing high-pressure refrigerant discharged from the working chamber and generating refrigerant pressure for pressing the movable scroll against the fixed scroll;
A balancer (254) disposed in the back pressure chamber and driven by the rotation shaft to rotate and relieve the unbalance of the rotation shaft caused by the movable scroll;
A liquid storage chamber (70) that communicates with the back pressure chamber and temporarily stores the liquid phase refrigerant discharged from the working chamber when the working chamber compresses and discharges the liquid phase refrigerant by the revolving motion of the movable scroll; Is provided.

  Accordingly, the liquid refrigerant can be avoided from the back pressure chamber to the liquid storage chamber until the vaporization of the liquid refrigerant is completed. For this reason, when the balancer rotates in the back pressure chamber together with the rotation shaft, it is possible to prevent the liquid phase refrigerant from rotating with the balancer. Accordingly, it is possible to suppress the counterweight effect of the balancer from being obstructed and to prevent the vibration of the rotating shaft from deteriorating. The counterweight effect is an effect that alleviates the unbalance of the rotating shaft.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a figure which shows the cross-sectional structure of the scroll compressor in one Embodiment of this invention. It is II-II sectional drawing in FIG. It is a figure which shows the cross-sectional structure of the scroll compressor which is proportional. FIG. 4 is a sectional view taken along line IV-IV in FIG. 3.

  Hereinafter, an embodiment of a scroll compressor 1 of the present invention will be described with reference to FIGS. 1 and 2.

  The scroll compressor 1 is applied to a refrigeration cycle device of an in-vehicle air conditioner. The refrigeration cycle apparatus constitutes an accumulator cycle in which an accumulator that stores liquid phase refrigerant is disposed between the refrigerant inlet of the scroll compressor 1 and the refrigerant outlet of the evaporator.

  The scroll compressor 1 is an electric compressor, and is a horizontal type in which a compression mechanism unit 10 that compresses a refrigerant (fluid) and an electric motor unit 20 that drives the compression mechanism unit 10 are arranged in a horizontal direction (lateral direction). ing.

  The compression mechanism unit 10 and the electric motor unit 20 are accommodated in a housing 30.

  The housing 30 includes a cylindrical member 31 whose axial direction is parallel to the horizontal direction, an oil separation container 32 that closes one side of the cylindrical member 31 in the axial direction, and a lid that closes the other axial side of the cylindrical member 31. This is a sealed container formed by joining the member 34.

  Specifically, the cylindrical member 31 is formed in a cylindrical shape with iron. The cylindrical member 31 forms a suction chamber 40 that houses the compression mechanism unit 10 and the electric motor unit 20, and a suction hole (not shown) that introduces the refrigerant flowing from the accumulator into the suction chamber 40. Further, the cylindrical member 31 forms an inverter housing portion 42 that houses an inverter 60 that supplies three-phase AC power to the motor portion 20.

  The lid member 34 is formed of resin or the like, and closes an opening formed on the other side in the axial direction of the inverter accommodating portion 42.

  The oil separation container 32 is made of iron. The oil separation container 32 forms a refrigerant discharge port 32a and a lubricating oil separation chamber 32b communicating with the refrigerant discharge port 32a. The lubricating oil separation chamber 32b houses a lubricating oil separation mechanism 32c that separates lubricating oil from high-pressure refrigerant discharged from a discharge chamber, which will be described later, and guides the high-pressure refrigerant from which the lubricating oil has been separated to the refrigerant discharge port 32a. An oil storage chamber 33 for storing the lubricating oil separated by the lubricating oil separation mechanism 32c is provided below the lubricating oil separation chamber 32b. The cylindrical member 31 and the oil separation container 32 are airtightly joined by bolts or the like.

  The electric motor unit 20 constitutes a three-phase AC synchronous motor, and includes a stator 21 that forms a stator and a rotor 22 that forms a rotor. The stator 21 has a substantially cylindrical shape that extends in the horizontal direction as a whole, and is fixed to a cylindrical member 31 of the housing 30. Specifically, the stator 21 includes a stator core 211 and a stator coil 212 wound around the stator core 211.

  Supply of three-phase AC power to the stator coil 212 is performed from the inverter 60 via the power supply terminal 23. The power supply terminal 23 is disposed above the stator 21 in the housing 30. Specifically, a power supply terminal fixing plate 24 that penetrates the power supply terminal 23 is disposed on the other side in the axial direction with respect to the electric motor unit 20 in the housing 30.

  The rotor 22 includes a permanent magnet, and is disposed on the radially inner side of the stator 21. The rotor 22 has a cylindrical shape whose axis coincides with the horizontal direction, and a rotation shaft 25 extending in the horizontal direction is fixed to the center hole of the rotor 22.

  The rotating shaft 25 is formed in an elongated cylindrical shape having an oil supply passage 251 extending in the axial direction. The oil supply passage 251 opens into the back pressure chamber 50 on one side in the axial direction of the rotation shaft 25. The oil supply passage 251 is an oil supply passage for supplying lubricating oil to the bearing 27.

  The other side portion in the axial direction of the rotating shaft 25 is rotatably supported by a bearing 27. The bearing 27 is fixed to the cylindrical member 31 of the housing 30 via the interposed member 28.

  A portion of the rotary shaft 25 on one side in the axial direction with respect to the rotor 22 is rotatably supported by a bearing 291 formed in the front housing 29. The front housing 29 has a cylindrical shape in which an outer diameter and an inner diameter increase stepwise from the other axial side toward the other axial side, and the outermost peripheral surface abuts on the cylindrical member 31 of the housing 30. It is fixed in the state.

  A portion of the rotating shaft 25 on one side in the axial direction with respect to the rotor 22 is located inside the front housing 29, and the other side portion in the axial direction having the smallest inner diameter of the front housing 29 constitutes a bearing 291. Yes.

  A back pressure chamber 50 is formed between the bearing 120 and the bearing 291 in the front housing 29. The back pressure chamber 50 is formed in an annular shape centering on the axis of the rotary shaft 25. As will be described later, the refrigerant discharged from the discharge chamber 124 is stored in the back pressure chamber 50 and the refrigerant pressure of the discharged refrigerant is applied to the movable scroll 11 as a back pressure.

  In the back pressure chamber 50, one side in the axial direction of the rotary shaft 25, an eccentric shaft 253, and a bush balancer 254 are accommodated. The eccentric shaft 253 is a shaft member that protrudes from one axial direction side of the rotary shaft 25 to one axial direction side. The eccentric shaft 253 is offset in the radial direction with respect to the axis of the rotary shaft 25.

  The front housing 29 is provided with a recess 70 a that is recessed from the back pressure chamber 50 to the other side in the axial direction to form a liquid storage chamber 70. The liquid storage chamber 70 communicates with the back pressure chamber 50. Accordingly, the liquid storage chamber 70 is formed so as to protrude radially outward from the back pressure chamber 50. The outer side in the radial direction is the outer side in the radial direction with the axis of the rotation shaft 25 as the center.

  The eccentric shaft 253 is fitted into the boss portion 254 a of the bush balancer 254. The bush balancer 254 includes a weight portion 254b that is disposed radially outside the boss portion 254a and connected to the boss portion 254a. The bush balancer 254 alleviates the unbalance of the rotating shaft 25 caused by the movable scroll 11.

  The movable scroll 11 is disposed on one side in the axial direction with respect to the front housing 29 and constitutes a movable member of the compression mechanism unit 10. On one side in the axial direction with respect to the movable scroll 11, a fixed scroll 12 that is a fixed member of the compression mechanism unit 10 is disposed.

  The movable scroll 11 and the fixed scroll 12 have disk-shaped substrate portions 111 and 121. The movable scroll 11 and the fixed scroll 12 are arranged so as to face each other in the horizontal direction.

  A support portion 113 that supports the bearing 120 is formed at the center of the movable scroll substrate portion 111. The boss portion 254a of the bush balancer 254 is rotatably supported by the bearing 120.

  The movable scroll 11 and the front housing 29 are provided with a rotation prevention mechanism (not shown) that prevents the movable scroll 11 from rotating about the eccentric shaft 253. Therefore, when the rotary shaft 25 rotates, the movable scroll 11 revolves (turns) around the rotation center of the rotary shaft 25 without rotating about the eccentric shaft 253.

  The movable scroll 11 is formed with a spiral tooth portion 112 protruding from the substrate portion 111 toward the fixed scroll 12 side. On the other hand, the substrate portion 121 of the fixed scroll 12 is fixed to the cylindrical member 31 of the housing 30, and the tooth portion 112 of the movable scroll 11 and the upper surface of the fixed scroll substrate portion 121 (surface on the movable scroll 11 side) Engaging spiral teeth 122 are formed. Specifically, a spiral groove portion is formed on the upper surface of the fixed scroll substrate portion 121, and a side wall of the spiral groove portion constitutes a spiral tooth portion 122.

  When the tooth portions 112 and 122 of the movable scroll 11 and the fixed scroll 12 are engaged with each other and contacted at a plurality of locations, a plurality of crescent-shaped working chambers 15 are formed. In FIG. 1, for convenience of illustration, only one working chamber among the plurality of working chambers 15 is denoted by reference numerals, and the other working chambers are not denoted by reference numerals.

  The working chamber 15 moves while changing the volume from the outer peripheral side to the center side by the revolving motion of the movable scroll 11. By enlarging the volume of the working chamber 15, the working chamber 15 is supplied with the refrigerant flowing from the accumulator through the suction chamber 40 and the suction hole. When the volume of the working chamber 15 is reduced, the working chamber 15 is reduced. The refrigerant in 15 is compressed.

  A discharge port 123 through which the refrigerant compressed in the working chamber 15 is discharged is formed at the center of the fixed scroll substrate 121.

  A discharge chamber 124 communicating with the discharge port 123 is formed on one side in the axial direction with respect to the fixed scroll substrate portion 121. The discharge chamber 124 is disposed on the other side in the axial direction with respect to the lubricating oil separation chamber 32b with the partition wall 33f interposed therebetween. A passage 121 a that guides the lubricating oil from the oil storage chamber 33 to the back pressure chamber 50 is formed in the fixed scroll substrate portion 121.

  Further, a back pressure intake port 121 b that guides the refrigerant discharged from the discharge chamber 124 to the back pressure chamber 50 is formed in the fixed scroll substrate portion 121. On the other hand, the movable scroll 11 is formed with a back pressure intake port 121b and a communication passage 11a communicating between the back pressure chamber 50.

  In the discharge chamber 124, the refrigerant is prevented from flowing back to the working chamber 15 via the discharge port 123, and a reed valve (not shown) that opens and closes the discharge port 123 and the maximum opening of the reed valve are regulated. A stopper 19 is arranged. The reed valve plays a role of opening and closing the back pressure intake port 121b.

  Next, the operation of the scroll compressor 1 of this embodiment will be described.

  First, when three-phase AC power is supplied from the inverter 60 to the stator coil 212, a rotating magnetic field is applied from the stator coil 212 to the rotor 22, and a rotational force is generated in the rotor 22. For this reason, the rotating shaft 25 rotates integrally with the rotor 22. At this time, the bush balancer 254 rotates in the back pressure chamber 50 as the rotating shaft 25 rotates.

  At this time, the rotational force of the rotary shaft 25 is transmitted to the movable scroll 11 through the eccentric shaft 253. For this reason, the movable scroll 11 performs a turning motion with respect to the fixed scroll. As a result, the capacity of the plurality of working chambers 15 changes. For this reason, when the pressure of the sucked refrigerant rises when it is sucked from the accumulator through the suction hole 41 and the suction chamber 40 into one of the plurality of working chambers 15, the refrigerant pressure opens the reed valve. Then, the discharge port 123 is opened.

  At this time, the high-pressure refrigerant from the working chamber 15 is discharged into the discharge chamber 124 through the discharge port 123 and the communication path 11a.

  Most of the refrigerant in the discharge chamber 124 flows to the lubricating oil separation chamber 32b through the refrigerant discharge port 32a. In the lubricating oil separation chamber 32b, the oil separation container 32 separates the lubricating oil from the refrigerant supplied from the discharge chamber 124, and the separated refrigerant flows from the refrigerant discharge port 32a to the refrigerant inlet of the condenser.

  The lubricating oil separated in the oil separation container 32 flows from the oil storage chamber 33 to the back pressure chamber 50 through the passageway 121a. Lubricating oil from the back pressure chamber 50 is supplied to the bearings 120 and 291. In addition to this, the lubricating oil in the back pressure chamber 50 is supplied to the bearing 27 through the oil supply passage 251 of the rotating shaft 25.

  On the other hand, in a state where the reed valve opens the discharge port 123 due to the refrigerant pressure in the working chamber 15, the reed valve also opens the back pressure intake port 121b. At this time, high-pressure refrigerant other than the high-pressure refrigerant supplied to the lubricating oil separation chamber 32b out of the high-pressure refrigerant discharged from the working chamber 15 through the discharge port 123 to the discharge chamber 124 passes through the back pressure intake port 121b. To be supplied. Accordingly, the pressure of the refrigerant in the back pressure chamber 50 is applied to the movable scroll 11. For this reason, the movable scroll 11 is pressed against the fixed scroll 12.

  On the other hand, when the inverter 60 supplies three-phase AC power to the stator coil 212 and the movable scroll 11 starts to turn at low temperatures, the inverter 60 is sucked into one of the plurality of working chambers 15. The sucked liquid phase refrigerant is compressed in the working chamber 15 and is discharged from the working chamber 15 to the discharge chamber 124 through the discharge port 123 as a liquid phase refrigerant (or a gas-liquid two-phase refrigerant).

  Here, when the liquid phase refrigerant is discharged from the working chamber 15 to the discharge chamber 124 through the discharge port 123, the liquid phase refrigerant flows from the discharge chamber 124 to the liquid storage chamber 70 through the communication path 11 a and the back pressure chamber 50.

  For this reason, when the balancer 254 rotates in the back pressure chamber 50 as the rotating shaft 25 rotates, the liquid phase refrigerant is avoided from the back pressure chamber 50 to the liquid storage chamber 70. Therefore, it is possible to prevent the liquid-phase refrigerant from continuing around the outer periphery of the balancer 254 as the balancer 254 rotates. Thereafter, the refrigerant in the liquid storage chamber 70 is vaporized by the warm-up of the scroll compressor 1 and flows into the suction chamber 40.

  When the refrigerant pressure in the working chamber 15 is lowered and the reed valve closes the discharge port 123, the reed valve also closes the back pressure intake port 121b.

  According to the present embodiment described above, the scroll compressor 1 forms the working chamber 15 between the fixed scroll 12 and the fixed scroll 12 and is driven by the rotary shaft 25 so that the fixed compressor 12 is driven. A movable scroll 11 that revolves, and the movable scroll 11 revolves to change the capacity of the working chamber 15 to suck and compress the refrigerant into the working chamber and discharge the high-pressure refrigerant from the working chamber 15.

  The scroll compressor 1 is disposed in the back pressure chamber 50 that stores the high-pressure refrigerant discharged from the working chamber 15 and generates refrigerant pressure that presses the movable scroll 11 against the fixed scroll 12. The balancer 254 that is driven and rotated to relieve the imbalance of the rotary shaft 25 caused by the movable scroll 11 and the back pressure chamber 50 communicate with the back-pressure chamber 50, and the liquid-phase state refrigerant is operated by the revolving motion of the movable scroll 11. And a liquid storage chamber 70 for temporarily storing the refrigerant discharged from the working chamber 15 when 15 is compressed and discharged.

  Accordingly, the liquid refrigerant can be avoided from the back pressure chamber 50 to the liquid storage chamber 70 until the vaporization of the liquid refrigerant is completed by warming up the scroll compressor 1. For this reason, when the balancer 254 rotates in the back pressure chamber 50 together with the rotary shaft 25, it is possible to prevent the liquid-phase refrigerant from rotating together with the balancer 254. Therefore, in the scroll compressor 1 with a low degree of design freedom, it is possible to suppress the counterweight effect of the balancer 254 from being obstructed and to suppress the vibration of the rotating shaft 25 from deteriorating. The counterweight effect of the balancer 254 is a function that relaxes the unbalance of the rotating shaft 25.

(Other embodiments)
(1) In the above embodiment, the example in which the scroll compressor 1 is applied to the in-vehicle air conditioner has been described. However, the present invention is not limited to this, and the scroll compressor 1 is applied to various air conditioners such as a building air conditioner and a residential air conditioner. May be.

  (2) In the above embodiment, an example in which an electric compressor is used as the scroll compressor 1 has been described. However, the present invention is not limited to this, and the scroll compressor 1 may be an engine-driven compressor that is driven by the driving force of the engine.

  (3) In the above embodiment, an example in which the scroll compressor 1 of the present invention is applied to an accumulator cycle has been described. Instead of this, the receiver of the present invention is applied to a receiver cycle in which a receiver is disposed between a capacitor and a pressure reducing valve. A scroll compressor 1 may be applied. Alternatively, the scroll compressor 1 of the present invention may be applied to various refrigeration cycles that can switch between the cooling operation and the heating operation even in refrigeration cycles other than the accumulator cycle and the receiver cycle.

  (4) It should be noted that the present invention is not limited to the above-described embodiment, and can be appropriately changed within the scope described in the claims. Moreover, the said embodiment and other embodiment are not irrelevant mutually, and a combination is possible suitably except the case where a combination is clearly impossible. Further, in the above-described embodiment and other embodiments, elements constituting the embodiment are not necessarily indispensable unless explicitly stated as essential and clearly considered essential in principle. It goes without saying that there is nothing. Further, in the above embodiment and other embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly specified in principle and clearly specified in principle. The number is not limited to the specific number except for the case where the number is limited. Further, in the above-described embodiment and other embodiments, when referring to the shape, positional relationship, etc. of the constituent elements, etc., unless otherwise specified or in principle limited to a specific shape, positional relationship, etc. It is not limited to the shape, positional relationship, and the like.

  According to the first aspect described in one or more embodiments of the above and other embodiments, an operation chamber is formed between the fixed scroll and the fixed scroll and is driven by the rotating shaft. And a movable scroll that revolves with respect to the fixed scroll. The revolving motion of the movable scroll changes the capacity of the working chamber, sucks and compresses the refrigerant into the working chamber, and discharges the high-pressure refrigerant from the working chamber. A scroll compressor that stores high-pressure refrigerant discharged from the working chamber and generates refrigerant pressure that presses the movable scroll against the fixed scroll, and is arranged in the back-pressure chamber and is driven by a rotating shaft to rotate. The revolving motion of the movable scroll communicates with the balancer that relieves the imbalance of the rotating shaft caused by the movable scroll and the back pressure chamber. And a liquid reservoir chamber which temporarily store the liquid phase refrigerant discharged from the working chamber when the dynamic chamber is discharged by compression.

  According to the 2nd viewpoint, the liquid storage chamber is formed in the radial direction outer side centering on a rotating shaft with respect to a back pressure chamber.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 10 Compression mechanism part 11 Movable scroll 12 Fixed scroll 20 Electric motor part 25 Rotating shaft 254 Bush balancer 30 Housing 40 Suction chamber 50 Back pressure chamber 60 Inverter

Claims (2)

Fixed scroll (12);
A movable scroll (11) that constitutes a working chamber with the fixed scroll and revolves relative to the fixed scroll by being driven by a rotary shaft (25);
A scroll compressor that changes the capacity of the working chamber by revolving motion of the movable scroll, sucks and compresses the refrigerant into the working chamber, and discharges high-pressure refrigerant from the working chamber;
A back pressure chamber (50) for storing a high-pressure refrigerant discharged from the working chamber and generating a refrigerant pressure for pressing the movable scroll against the fixed scroll;
A balancer (254) disposed in the back pressure chamber and driven to rotate by the rotating shaft to relieve imbalance of the rotating shaft caused by the movable scroll;
A liquid storage chamber that communicates with the back pressure chamber and temporarily stores the liquid-phase refrigerant discharged from the working chamber when the working chamber compresses and discharges the liquid-phase refrigerant by the revolving motion of the movable scroll. 70).   The scroll compressor according to claim 1, wherein the liquid storage chamber is formed on a radially outer side centering on the rotation shaft with respect to the back pressure chamber.

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