JP2007154680A - Refrigerating cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enhance reliability by simplifying a structure for pressing and biasing one cylinder against vane and reducing the number of parts and labor in multi-cylinder rotary type closed hermetic compressors in which the vane chambers of the cylinders on the cylinder cut-off operation side are closed and the operation mode is changed by controlling the pressure in the closed chamber among the multi-cylinder rotary type hermetic compressors in which the capacity is changed in two stages, i.e., full load operation and controlled load operation by operating one cylinder under cylinder cut-off operation. <P>SOLUTION: As shown in Fig. 9, the refrigerating cycle device uses a pilot valve 40 as the operation mode changing means for one cylinder. Also, the device has a control mode which requires a controlled load operation for starting it. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention has two cylinder chambers, performs compression action simultaneously in the two chambers, interrupts the compression action in one of the cylinder chambers to reduce the compression work, and can perform so-called variable capacity refrigerating air conditioning. The present invention relates to a refrigeration cycle apparatus that uses a hermetic type compressor.

  A general rotary type hermetic compressor has a motor case and a compression mechanism connected to the motor unit in a hermetic case, and gas compressed by the compressor mechanism is temporarily discharged into the hermetic case. It is a high pressure type inside the case. The compression mechanism unit has a piston housed in a cylinder chamber provided in the cylinder. The cylinder is provided with a vane chamber in which the vane is slidably accommodated. The tip edge of the vane is pressed and urged by a compression spring so as to protrude toward the cylinder chamber and elastically contact the peripheral surface of the piston.

  Accordingly, the cylinder chamber is divided into two chambers along the rotational direction of the piston by the vanes, and the suction portion is communicated with the one chamber side and the discharge portion is communicated with the other chamber side. A suction pipe is connected to the suction part, and the discharge part is opened in the sealed case.

  By the way, in recent years, a two-cylinder type rotary hermetic compressor including two sets of the above and below cylinders is being standardized. If such a compressor can be provided with a cylinder that always performs a compression action and a cylinder that can be switched between compression and stop as necessary, the usable capacity range is expanded, which is advantageous.

For example, in Patent Document 1, two cylinder chambers are provided, and if necessary, the vanes of one of the cylinder chambers are forcibly separated from the rollers, and the pressure is increased to interrupt the compression action by increasing the pressure of the cylinder chamber. A technique characterized by having an introduction means is disclosed.
JP-A-1-247786

  This type of compressor is extremely functionally superior, but in order to constitute a high-pressure introduction means, a high-pressure introduction hole that communicates one cylinder chamber and the inside of the sealed case is provided, and a two-stage throttle mechanism is provided in the refrigeration cycle. A bypass refrigerant pipe that branches off from the middle part of the throttle mechanism and communicates with the vane chamber on one side and that has an electromagnetic on-off valve in the middle part is provided.

  That is, it is necessary to make a hole for making a high-pressure introduction means for the compressor, and the throttle device on the refrigeration cycle must be a two-stage throttle mechanism. Further, the two-stage throttle mechanism, the cylinder chamber, The structure is complicated, such as connecting a bypass refrigerant pipe between the two, which has an adverse effect on cost.

  The present invention has been made on the basis of the above circumstances, and the purpose thereof is to omit the pressing and urging structure for the vane of one cylinder on the premise that the first cylinder and the second cylinder are provided. Therefore, it is intended to provide a refrigeration cycle apparatus equipped with a hermetic compressor that can reduce processing time and improve reliability.

  In order to satisfy the above object, the refrigeration cycle apparatus of the present invention accommodates an electric motor unit and a rotary compression mechanism unit connected to the electric motor unit in a sealed case, and once seals the gas compressed by the compression mechanism unit. In a rotary hermetic compressor that discharges into a case to generate a high pressure in the case, the compression mechanism section includes an intermediate partition plate and eccentric rollers provided on both sides of the intermediate partition plate, which are accommodated so as to be eccentrically rotatable. A first cylinder and a second cylinder provided with a cylinder chamber, and are provided in the first cylinder and the second cylinder, the tip edge of which is pressed and urged so as to contact the peripheral surface of the eccentric roller, Accommodates a vane that bisects the cylinder chamber along the rotational direction of the eccentric roller, a first vane chamber that houses the back side end of the first vane and the spring member, and a back side end of the second vane. The intermediate partition plate and the second vane chamber sealed by the sub-bearing, and the vane provided in the second cylinder includes an internal pressure of the case guided to the vane chamber, and a second cylinder chamber. It has a hermetic compressor that is pressed and urged according to a differential pressure with respect to a suction pressure or a discharge pressure that is guided.

  In order to satisfy the above object, the refrigeration cycle apparatus of the present invention forms a refrigeration cycle with the above-described hermetic compressor, a condenser, an expansion mechanism, and an evaporator.

  In order to satisfy the above object, a refrigeration cycle apparatus of the present invention comprises a heat pump refrigeration cycle comprising the above-described hermetic compressor, a four-way switching valve, an indoor heat exchanger, an expansion mechanism, and an outdoor heat exchanger, The cylinder chamber in the first cylinder always receives the suction pressure regardless of the switching operation of the four-way switching valve, and the cylinder chamber in the second cylinder receives the suction pressure or the discharge pressure according to the switching operation of the four-way switching valve. It is piped so that is guided.

  According to the present invention, on the premise that the first cylinder and the second cylinder are provided, the pressure biasing structure with respect to the vane of one of the cylinders can be omitted, the number of parts and the processing labor can be reduced, and the reliability can be improved. A refrigeration cycle apparatus including a hermetic compressor can be provided.

(Embodiment 1)
Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  FIG. 1 shows a cross-sectional structure of a rotary hermetic compressor. First, the rotary hermetic compressor R will be described. A compression mechanism 2 described later is provided in the lower part of the hermetic case 1, and an electric motor part 3 is provided in the upper part. The electric motor unit 3 and the compression mechanism unit 2 are connected via a rotating shaft 4.

  The electric motor unit 3 includes a stator 5 that is fixed to the inner surface of the sealed case 1 and a rotor 6 that is disposed on the inner side of the stator 5 with a predetermined gap and in which the rotating shaft 4 is inserted.

  The compression mechanism section 2 includes a first cylinder 8 a and a second cylinder 8 b that are disposed below the rotary shaft 4 via an intermediate partition plate 7. A main bearing 9 is superimposed on the upper surface of the first cylinder 8a, and is fixed to the cylinder 8a together with the first valve cover 10a. The auxiliary bearing 11 is superimposed on the lower surface portion of the second cylinder 8b, and is fixed to the second cylinder 8b together with the second valve cover 10b.

  On the other hand, the rotating shaft 4 is pivotally supported by the main bearing 9 and the sub-bearing 10 at its midway portion and lower end portion. Further, the rotary shaft 4 penetrates through the cylinders 8a and 8b, and integrally includes two eccentric portions 4a and 4b formed with a phase difference of about 180 °.

  A detailed structure of the cylinder portion will be described with reference to FIG. The eccentric portions 4a and 4b have the same diameter as each other, and are assembled so as to be positioned at the inner diameter portions of the cylinders 8a and 8b. Eccentric rollers 12a and 12b having the same diameter are fitted to the peripheral surfaces of the eccentric parts 4a and 4b. Each cylinder 8a, 8b is provided with vane grooves 14a, 14b and vane chambers 15a, 15b communicating with the cylinder chambers 13a, 13b. The vanes 16a and 16b are accommodated in the vane grooves 14a and 14b so as to protrude and retract with respect to the cylinder chambers 13a and 13b. A spring member 17 is accommodated in the vane chamber 15a. The spring member 17 is interposed between the rear side end surface of the vane 16a and the inner peripheral surface of the sealing case 1, and applies an elastic force (back pressure) to the vane 16a so that the tip edge contacts the eccentric roller 12a. It is. The tip edges of the vanes 16a and 16b are formed in a semicircular shape, and can make line contact with the circumferential walls of the circular eccentric rollers 12a and 12b regardless of the rotation angle of the eccentric roller 12a.

  Since the first vane chamber 15a and the rear end of the vane 16a communicate with the inside of the sealed case 1, the pressure in the sealed case 1 is directly received. That is, since the vane 16a is slidably accommodated in the vane chamber 15a and the rear end portion is located in the vane chamber 15a, the internal pressure of the sealed case 1 is directly received.

  On the other hand, the second vane chamber 15b does not communicate with the inside of the sealed case 1, and forms a separate and independent sealed space. The structure of the second vane chamber 15b will be described below with reference to FIG. Sealing lid portions 7a and 11a are provided on the intermediate partition plate 7 and the auxiliary bearing 11 which are fixedly attached to the second cylinder 8b. By attaching and fixing these to the second cylinder 8b, the portion of the first cylinder 8a that has been opened in the sealed case 1, that is, the upper and lower sides of the vane groove 14b and the vane chamber 15b can be sealed.

  An oil supply path 19 is provided in the vane groove 14b provided in the second cylinder 8b, and communicates with the inside of the sealed case 1 via an oil communication hole 20 provided in the auxiliary bearing 11.

  FIG. 4 shows a cross-sectional view in a state where these are attached and fixed. The vane chamber 15b that forms the sealed space communicates with the outside of the sealed case 1 through the pressure introduction pipe 18 installed at the back thereof, and the rear end portions of the vane chamber 15b and the vane 16b are guided by the pressure introduction pipe 18. Will receive. The tip of the vane 16b (broken line portion) faces the second cylinder chamber 13b, and the vane tip receives the pressure in the cylinder chamber 13b. Eventually, the vane 16b is configured to move in the direction from the higher pressure to the lower pressure according to the magnitude of the mutual pressure received by the front end and the rear end.

  The operation of the compressor according to the present invention will be described with reference to FIG. 1 again. A discharge pipe 21 is connected to the upper end of the sealed case 1. The discharge pipe 21 is connected to an accumulator 25 via a condenser 22, an expansion mechanism 23 and an evaporator 24. Suction pipes 26 a and 26 b for the compressor R are connected to the bottom of the accumulator 25. One suction pipe 26a penetrates the sealed case 1 and the side of the first cylinder 8a, and communicates directly with the first cylinder chamber 13a. The other suction pipe 26b passes through the side of the second cylinder 8b through the sealed case 1 and communicates directly with the second cylinder chamber 13b.

  Further, a discharge pressure introducing pipe 27 connected to the second vane chamber 15b is provided from the side surface portion of the sealed container 1. The attachment position of the discharge pressure introducing pipe 27 to the sealed container 1 is a position below the oil level of the lubricating oil sealed in the sealed container 1. This takes into account the supply of lubricating oil to the second cylinder, and details will be described later.

  Further, a suction pressure introduction pipe 28 is provided branched from the middle part of the evaporator 24 and the suction pipe 26. The suction pressure introduction pipe 28 merges with the discharge pressure introduction pipe 27 and is led to the second vane chamber 15b. On the upstream side of the discharge pressure introduction pipe 27 and the junction with the suction pressure introduction pipe 28, an on-off valve 29 is provided.

  Similarly, the suction pressure introducing pipe 28 is provided with an on-off valve 30. The on-off valve 29 and the on-off valve 30 are electromagnetic valves, respectively, and are controlled to open and close according to an electrical signal from the control unit 31.

  In this way, the pressure switching mechanism K is configured by the opening / closing valves provided in the discharge pressure introduction pipe 27, the suction pressure introduction pipe 28, and the suction pipe connected to the second vane chamber 15b. In accordance with the switching operation of the pressure switching mechanism K, the suction pressure or the discharge pressure is guided to the vane chamber 15b of the second cylinder 8b.

  Next, the operation of the refrigeration cycle apparatus provided with the above-described rotary hermetic compressor R will be described.

  (1) When normal operation (full capacity operation) is selected.

  The control unit 31 opens the first on-off valve 29 and closes the second on-off valve 30.

  In the first cylinder 8a, since the vane 16a is always elastically pressed and biased by the spring member 17, the tip of the vane 16a is in contact with the eccentric roller 12a so that the inside of the first cylinder chamber 13a is in the suction chamber and the compression chamber. Divide into two.

  With the rotation of the eccentric roller 12a, the gas in the first cylinder chamber 13a is compressed. The rotating shaft 4 is continuously rotated, and the high-pressure gas is discharged and filled into the sealed case 1 through the valve cover 10a, and is discharged from the discharge pipe 21 at the upper part of the sealed case 1.

  Since the first on-off valve 29 is open, the high-pressure gas refrigerant is guided from the discharge pressure introduction pipe 27 to the vane chamber 15b of the second cylinder 8b. On the other hand, the second cylinder chamber 15b is in a suction pressure (low pressure) atmosphere. The vane 16b is pressed and urged so as to be in sliding contact with the eccentric roller 12b because the tip end portion is under a low pressure condition and the rear end portion is under a high pressure condition. That is, the compression action is performed in both the first cylinder chamber 13a and the second cylinder chamber 13b, and the full capacity operation is performed.

  (2) When special operation (capacity half operation) is selected.

  When the special operation (operation that halves the compression capacity) is selected, the control unit 31 closes the first on-off valve 29 and switches and sets the second on-off valve 30 to open. In the first cylinder chamber 13a, the normal compression action is performed as described above, and the high-pressure gas discharged into the sealed case 1 is filled to become the high pressure in the case. On the other hand, the suction pressure is introduced into the vane chamber 15b of the second cylinder 8b through the suction pressure introduction pipe 28 branched from the first suction pipe 26b. On the other hand, the suction pressure (low pressure) is guided to the second cylinder chamber 15b through the suction pipe 26b and the accumulator 25. Therefore, the vane 16b is placed in a low-pressure atmosphere at both the front and rear ends, and there is no differential pressure at the front and rear ends. However, since the eccentric roller 12b is rotating in the second cylinder chamber 13b, the vane 16b is forcibly accommodated in the vane chamber 15b and does not move at a position away from the outer peripheral surface of the eccentric roller 12b. The stop state is maintained. Therefore, no compression action is performed in the second cylinder chamber 13b. Eventually, only the compression action in the first cylinder chamber 13a is effective, and the operation is reduced by half.

  As described above, the compressor can be operated in two operation modes of normal operation (full capacity operation) and special operation (capability half operation). However, in this type of compressor, the vane groove 14b and the vane chamber 15b provided in the second cylinder 8b are sealed and disconnected from the sealed case 1. Therefore, the lubricating oil is not sufficiently supplied to the vane sliding portion, and problems such as wear and seizure of the vane sliding portion have occurred.

  However, in the compressor according to the present invention, the lubricating oil is guided to the oil supply path 19 of the vane groove 14b of the second cylinder 8b through the oil communication hole 32 provided from the central hole of the intermediate partition plate 7, and then the auxiliary oil is supplied. It returns to the inside of the sealed case via the oil communication hole 20 provided in the bearing 11. Since the lubricating oil path as described above is formed and sufficient lubricating oil is supplied to the sliding portion, the above problem does not occur.

  The oil supply path 19 is provided in the vane groove 14b and does not communicate with the vane chamber 15b. Since the vane 16b is accommodated in the vane groove 14b, the sealing property of the vane chamber 15b is not lost.

  Further, the vane 16b of the second cylinder is in a free state because it is not provided with a spring member, and it is easy to dance in the vane chamber 15b such that the tip of the vane 16b comes into contact with the eccentric roller 12b at the time of activation, and abnormal noise is generated. There is a risk of reaching.

  In order to avoid this, the first compression mechanism section that is a one-cycle operation is operated (special operation) for a predetermined time after starting when starting the operation. As a result, at the time of start-up, the high pressure refrigerant is guided to the second cylinder chamber 13b and the vane chamber 15b is at a low pressure, so the vane 16b is held by the differential pressure at the most retracted position as shown in FIG. The Thereafter, the special operation is performed until the set time t1 until the set differential pressure is reached. When the set time t1 elapses, the operation shifts to the 2-cycle operation. At this time, the suction pressure is guided to the second cylinder chamber and the normal compression action is performed, the vane chamber 15b becomes high pressure, and the tip of the vane 16b is pressed and urged so as to be in sliding contact with the eccentric roller 12b by the differential pressure. .

  Therefore, the above-mentioned troubles can be completely removed, and the vane 16b does not dance in the vane chamber 15b, and the special operation (capacity half operation) is surely performed, thereby improving the reliability.

(Embodiment 2)
The second embodiment of the present invention will be described below with reference to the drawings.

  FIG. 9 is a diagram for explaining the configuration of the pilot valve in the second embodiment. The configurations of the hermetic compressor R and the refrigeration cycle are exactly the same as those described above, and the same reference numerals are given and a new description is omitted.

  The pilot valve 40 is branched from a middle portion of the discharge pipe 21 connected to the hermetic compressor R, and a branch thin tube 27 is provided. One end of the branch thin tube 27 is connected to the other port e of the pilot valve 40. Is done. A suction capillary 26b is connected to the remaining port f of the pilot valve 40. The suction capillary 26b penetrates the sealed case 1 and the side of the second cylinder 8b and communicates directly with the second cylinder chamber 13b. A mesh is provided in the middle of the suction thin tube 26b to prevent foreign matter from entering.

  The remaining port g of the pilot valve 40 is connected to one end of the suction pipe 28 that comes out from the bottom of the accumulator 25. Further, the remaining port h of the pilot valve 40 is connected to one end of a vane back pressure pipe 51 that penetrates the side of the second vane chamber 15b of the second cylinder 8b.

  The pilot valve 40 is controlled to be switched according to an electrical signal from the control unit 31. That is, during normal operation (full capacity operation), the suction gas passes through the suction pipe 28 from the bottom of the accumulator 25, passes through the port g of the pilot valve 40, passes through the port f of the pilot valve 40, and then passes through the suction thin pipe 26b. Connected to the cylinder chamber 13b.

  On the other hand, the gas discharged from the discharge pipe 21 passes through the discharge introduction thin tube 27, passes through the port e of the pilot valve 40, passes through the port h of the pilot valve 40, and passes through the pressure introduction thin tube 18. And through the side of the second cylinder 8b and connected to the second vane chamber 15b of the second cylinder 8b.

  As a result, full capacity operation is performed in which the compression action is performed in both the first cylinder chamber 13a and the second cylinder chamber 13b.

  Next, at the time of half capacity operation, the suction gas passes through the suction thin tube 28 from the bottom of the accumulator 25, passes through the port g of the pilot valve 40, passes through the port h of the pilot valve 40, passes through the pressure introducing thin tube 18, and the sealed case 1. It penetrates the second cylinder 8b side and is connected to the second vane chamber 15b of the second cylinder 8b.

  On the other hand, the gas discharged from the discharge pipe 21 passes through the discharge introduction thin tube 27, passes through the port e of the pilot valve 40, passes through the port f of the pilot valve 40, and passes through the suction thin tube 26b to the second cylinder chamber 13b. Connected to.

  As a result, the vane 16b of the second cylinder chamber 13b does not move at a position separated from the outer peripheral surface of the roller 12b and maintains a stopped state, and no compression action is performed in the second cylinder chamber 13b. Eventually, only the compression action in the first cylinder chamber 13a is effective, and an operation with half the capacity is performed.

  Since the inside of the second cylinder chamber 13b is at a high pressure, there is no leakage of compressed gas from the sealed case 1 into the second cylinder chamber 13b, and no loss is caused thereby. Therefore, it is possible to operate with half the capacity without lowering the compression efficiency. In the compressor, the capacity can be varied with a simple structure that simply eliminates the spring member that biases the vane, which is advantageous in terms of cost, excellent in manufacturability, and highly efficient. Can provide a machine.

  As described above, the compressor of the present invention can be operated in two operation modes of normal operation (full capacity operation) and special operation (capability half operation). However, in this type of compressor, the vane groove 14b and the vane chamber 15b provided in the second cylinder 8b are sealed and disconnected from the sealed case 1. Therefore, the lubricating oil is not sufficiently supplied to the vane sliding portion, and problems such as wear and seizure of the vane sliding portion have occurred.

  However, in the compressor of the present invention, the lubricating oil is guided to the oil supply path 19 of the vane groove 14b of the second cylinder 8b through the oil communication hole 32 provided from the central hole of the intermediate partition plate 7, and then the auxiliary bearing. 11 returns to the inside of the hermetically sealed case via the oil communication hole 20 provided in 11. Since the lubricating oil path as described above is formed and sufficient lubricating oil is supplied to the sliding portion, the above problem does not occur.

  The oil supply path 19 is provided in the vane groove 14b and does not communicate with the vane chamber 15b. Since the vane 16b is accommodated in the vane groove 14b, the sealing property of the vane chamber 15b is not lost.

  Further, the vane 16b of the second cylinder is not provided with a spring member, so that it is in a free state, and it is easy to dance in the vane chamber 15b such that the tip of the vane 16b comes into contact with the eccentric roller 12b when starting up. There is a risk of occurrence.

  In order to avoid this, the first compression mechanism section that is a one-cycle operation is operated (special operation) for a predetermined time after starting to start the operation. At the time of start-up, high-pressure refrigerant is introduced into the second cylinder chamber 13b, and the vane chamber 15b is at a low pressure, so that the vane 16b is held by the differential pressure at the most retracted position as shown in FIG. Thereafter, the special operation is performed until the set time t1 until the set differential pressure is reached. When the set time t1 elapses, the operation shifts to the 2-cycle operation. At this time, the suction pressure is guided to the second cylinder chamber, and a normal compression action is performed. The vane chamber 15b becomes high pressure, and the tip of the vane 16b is pressed and urged by the differential pressure so as to be in sliding contact with the eccentric roller 12b. .

  Therefore, the above-mentioned troubles can be completely removed, and the vane 16b does not dance in the vane chamber 15b, and the special operation (capacity half operation) is surely performed, thereby improving the reliability.

(Embodiment 3)
In recent years, a refrigeration cycle using an HFC refrigerant not containing chlorine has been developed from the viewpoint of protecting the ozone layer. It is also possible to use a refrigeration cycle having this mechanism for such an HFC refrigerant.

(Embodiment 4)
In recent years, a refrigeration cycle using a natural refrigerant such as carbon dioxide has been developed from the viewpoint of preventing global warming. The present invention can also be applied to a refrigeration cycle using such a natural refrigerant.

  As described above, since the refrigeration cycle apparatus according to the present invention can provide a variable capacity compression mechanism with a simpler configuration and higher reliability, in addition to refrigeration equipment such as an air conditioner and a refrigerator, a heat pump It can also be applied to applications such as applied hot water supply equipment and dryers.

FIG. 1 is a longitudinal sectional view and a refrigeration cycle configuration diagram of a hermetic compressor according to Embodiment 1 of the present invention. 1 is an exploded perspective view of a first cylinder and a second cylinder according to Embodiment 1 of the present invention. 1 is an exploded perspective view of a second cylinder, an intermediate partition plate, and a secondary bearing according to Embodiment 1 of the present invention. Oil supply path sectional view of a compression mechanism portion according to Embodiment 1 of the present invention The perspective view of the auxiliary bearing which concerns on Embodiment 1 of this invention 1 is a perspective view of an intermediate partition plate according to Embodiment 1 of the present invention. Sectional drawing of the compression mechanism part which concerns on Embodiment 1 of this invention. Control mode diagram at startup according to Embodiment 1 of the present invention Configuration diagram of a refrigeration cycle using a pilot valve according to Embodiment 2 of the present invention

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Sealing case 2 Compression mechanism part 3 Electric motor part 4 Rotating shaft 5 Stator 6 Rotor,
7 Intermediate partition plate 8a, 8b Cylinder 9 Main bearing 10a, b Valve cover 11 Sub bearing 12a, 12b Eccentric roller 13a, 13b Cylinder chamber 14a, 14b Vane groove 15a, b Vane chamber 16a, b vane 17 Spring member 18 Pressure introduction pipe DESCRIPTION OF SYMBOLS 19 Oil supply groove 20 Oil communication hole 21 Discharge pipe 22 Condenser 23 Expansion valve 24 Evaporator 25 Accumulator 26a, b Suction thin tube 27 Discharge pressure introduction thin tube 28 Suction pressure introduction thin tube 29 1st on-off valve 30 2nd on-off valve 31 Control unit 40 Pilot valve 51b Vane back pressure pipe

Claims (3)

A compression mechanism portion that compresses and discharges gas taken from outside is accommodated in the sealed case, and the compression mechanism portion includes first and second cylinder chambers each including an eccentric roller for eccentric rotation. A cylinder is arranged in an axial direction with an intermediate partition plate interposed therebetween, and the intermediate partition plate has a central hole through which a drive shaft for driving the eccentric roller passes, and the first and second cylinders have a diameter from a cylinder chamber. First and second vane grooves extending outward in the direction are provided, and the tip of each vane groove is in contact with the circumferential surface of the eccentric roller so that the cylinder chamber is divided into two in the rotational direction of the eccentric roller. The vane is retractably stored, a main bearing is disposed in contact with the end surface on the anti-intermediate partition plate side of the first cylinder, and an auxiliary bearing is disposed on the end surface on the anti-intermediate partition plate side of the second cylinder. No ba The first vane chamber is formed by the groove, the rear end of the vane accommodated in the groove, the intermediate partition plate, and the main bearing, and the second vane groove, the rear end of the vane accommodated therein, and the intermediate partition plate. And a sub-bearing form a second vane chamber, and a spring member that presses and urges the vane rear side end toward the inner diameter side is housed in the first vane chamber. The pressure in the sealed case is introduced into the vane chamber, and the vane housed in the second vane groove is pressed and biased according to the differential pressure from the suction pressure or the discharge pressure guided to the cylinder chamber of the second cylinder. The high-pressure refrigerant discharged from the discharge pipe of the hermetic compressor is branched after passing through a well-known refrigeration cycle including a condenser, an expansion valve, an evaporator, and the like. Connected to the first and second cylinder chambers of the compressor A refrigeration cycle apparatus that is sucked in through a suction pipe, a branch tubule connected to the high-pressure side of the refrigeration cycle, a guide capillary that guides and guides the evaporated gas, and a suction capillary that communicates with the second cylinder chamber And a refrigeration cycle apparatus comprising a pilot valve housed in a four-way switching valve, each having a port to which a guide thin tube communicating with the second vane chamber is connected. The refrigeration cycle apparatus according to claim 1, wherein HCFC, HFC or the like not containing chlorine is used as a refrigerant. The refrigeration cycle apparatus according to claim 1, wherein a natural refrigerant such as carbon dioxide or ammonia is used as a refrigerant.

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