JP2009235985A - Multiple cylinder rotary type compressor and refrigeration cycle device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide: a multiple cylinder rotary type compressor which has same dimension and shape of a cylinder chamber provided on each of a plurality of compression mechanism parts, which enables change over between normal operation and (deactivated cylinder operation)+(release operation), of which capacity ratio can be optionally set, and which can improve reliability with high efficiency; and a refrigeration cycle which is provided with the multiple cylinder rotary type compressor and which can improves refrigeration cycle efficiency. <P>SOLUTION: Operation is changed over among full capacity operation performing compression operation by all compression mechanism parts, deactivated cylinder operation by a second compression mechanism part provided with a cylinder deactivation mechanism, and release operation by a first compression mechanism provided with a release mechanism by the release mechanism Y provided on the first compression mechanism part 2A and releasing gas in a middle of compression in the first cylinder chamber 14a to a low pressure side, the cylinder deactivation mechanism Z provided on the second compression mechanism part 2B and deactivating compression operation in a second compression chamber 14b by separating a blade 15b from a circumference wall of a roller 13b, and a four-way change over valve 30. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a multi-cylinder rotary compressor that is a rotary compressor including a plurality of cylinders, and a refrigeration cycle apparatus that constitutes a refrigeration cycle using the multi-cylinder rotary compressor.

  For example, in a rotary compressor mounted on an air conditioner, in recent years, a two-cylinder type two-cylinder rotary compressor provided with two sets of upper and lower cylinders is being standardized. In such a compressor, the inverter connected to the electric motor unit is controlled, and the compression capacity is adjusted by changing the rotation speed of the rotating shaft.

  In this case, the rotors are driven to rotate at the same rotational speed in the two cylinder chambers, and the same compression action is performed. In addition, the cylinder that always performs the compression action and switching between compression and stop as required is possible. If it is possible to provide the cylinder, it is advantageous that the specifications are further expanded.

[Patent Document 1] discloses the above-described two-cylinder rotary compressor. This is characterized in that it is provided with high pressure introducing means for forcibly holding the blade of the cylinder chamber away from the roller during cylinder resting operation and for increasing the pressure of the cylinder chamber to interrupt the compression action.
JP-A-1-247786

  The technology of [Patent Document 1] is 100% of the full capacity operation in which the compression action is performed in two cylinder chambers and the cylinder rest operation in which the compression action is performed in one cylinder but not in the other cylinder chambers. And 50% compression capacity can be switched. In other words, it is not possible to switch the capacity ratio other than this.

  For example, the displacement volume of the cylinder chamber in the two compression mechanism portions is changed, and the displacement volume of the cylinder chamber of the compression mechanism portion that is always operated is smaller than the displacement volume of the cylinder chamber of the compression mechanism portion that enables the cylinder resting operation. Set. That is, the compression capacity is switched between 100% and 40%, and a compressor different from the compressor of [Patent Document 1] is obtained.

  If this technique is adopted, the compression capacity ratio can be arbitrarily switched, but the compression reaction forces and the compression reaction forces of the two compression mechanisms are different during full capacity operation. For this reason, the vibration generated by the compression operation becomes large and the operation noise may increase, which is not suitable for practical use.

  The present invention has been made on the basis of the above circumstances. The purpose of the present invention is to make the dimensions and shapes of the cylinder chambers provided in each of the plurality of compression mechanisms the same, and to perform normal operation and cylinder-free operation + release operation. Multi-cylinder rotary compressor that can be switched, capacity ratio can be set arbitrarily, high efficiency and improved reliability, and refrigeration that improves refrigeration cycle efficiency with this multi-cylinder rotary compressor A cycle device is to be provided.

In order to satisfy the above object, the multi-cylinder rotary compressor of the present invention accommodates an electric motor unit and a plurality of compression mechanism units connected to each other through a rotating shaft in a sealed case. A cylinder having a cylinder chamber in which the roller is eccentrically rotatably accommodated, and a tip edge abutting against the peripheral wall of the roller in a state of being movably provided and pressed with respect to the cylinder chamber, and accompanying the eccentric rotation of the roller A blade that bisects the cylinder chamber and a discharge valve mechanism that discharges the gas compressed in the cylinder chamber into the sealed case are provided.
At least one compression mechanism section is provided with a release mechanism for releasing the gas being compressed in the cylinder chamber to the low pressure side, and the blade chamber is separated from the peripheral wall of the roller provided in at least one other compression mechanism section. There is a cylinder resting mechanism that stops the compression operation in the engine, and one switching means performs full capacity operation in which all the compression mechanism sections perform the compression operation and a cylinder resting operation in the compression mechanism section having the cylinder resting mechanism. At the same time, the release operation is performed by the compression mechanism portion provided with the release mechanism, and the operation is switched.
In order to satisfy the above object, the refrigeration cycle apparatus of the present invention forms a refrigeration cycle with the above-described multi-cylinder rotary compressor, a condenser, an expansion mechanism, and an evaporator.

  According to the present invention, a multi-cylinder rotary compressor that can switch between normal operation and idle cylinder operation + release operation, can arbitrarily set the capacity ratio, can obtain high efficiency and improved reliability, It is possible to provide a refrigeration cycle apparatus that includes this multi-cylinder rotary compressor and obtains an improvement in refrigeration cycle efficiency.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 shows a cross-sectional structure of a two-cylinder rotary compressor A which is a multi-cylinder rotary compressor in the first embodiment, and a schematic configuration of a refrigeration cycle apparatus R including the two-cylinder rotary compressor A. FIG. (Note that in order to avoid complications in the drawings, components that are not denoted by reference numerals are not illustrated even if they are described. Alternatively, they are illustrated but not denoted by reference numerals in the drawings. same as below)
First, from the configuration of the refrigeration cycle apparatus R, a two-cylinder rotary compressor A, a condenser B, an expansion mechanism C, an evaporator D, and a gas-liquid separator E are provided. The refrigerant pipe P is communicated.

  Between the gas-liquid separator E and the two-cylinder rotary compressor A on the suction side of the two-cylinder rotary compressor A, there are two refrigerant pipes, a first suction refrigerant pipe Pa and a second The suction refrigerant pipes Pb are arranged in parallel.

  As will be described later, the refrigerant gas compressed by the two-cylinder rotary compressor A is discharged into the refrigerant pipe P and circulates in the order of the above components to form a refrigeration cycle. The two-cylinder rotary compressor A is sucked through the suction refrigerant pipe Pa and the second suction refrigerant pipe Pb.

Next, the two-cylinder rotary compressor A will be described in detail.
In the figure, reference numeral 1 denotes a sealed case. A compression mechanism 2 is provided at the lower part of the sealed case 1, and an electric motor part 3 is provided at the upper part. The compression mechanism unit 2 and the electric motor unit 3 are connected via a rotating shaft 4.

  For example, a brushless DC synchronous motor (which may be an AC motor or a commercial motor) is used for the electric motor unit 3, and a stator 5 that is press-fitted and fixed to the inner surface of the sealed case 1 and a predetermined gap inside the stator 5 exist. And a rotor 6 fitted to the rotating shaft 4.

  The compression mechanism unit 2 includes an intermediate partition plate 7, and a first compression mechanism unit 2 </ b> A and a second compression mechanism unit 2 </ b> B provided on both end surfaces of the intermediate partition plate 7. The first compression mechanism 2A is formed on the upper surface side of the intermediate partition plate 7 and includes a first cylinder 8A. The second compression mechanism portion 2B is formed on the lower surface side of the intermediate partition plate 7 and includes a second cylinder 8B.

  The first cylinder 8A is press-fitted and fixed to the inner peripheral wall of the sealed case 1, and the main bearing 11 is overlapped on the upper surface portion and fixed via a mounting bolt. The auxiliary bearing 12 and the valve cover are overlapped on the lower surface portion of the second cylinder 8B, and are attached and fixed to the intermediate partition plate 7 via attachment bolts.

  The part pivotally supported by the main bearing 11 of the rotating shaft 4 is referred to as a main shaft part, and the part pivotally supported by the sub bearing 12 which is the lowermost end of the rotating shaft 4 is referred to as a sub shaft part. Crankshaft portions c and d are integrally provided at positions passing through the insides of the first cylinder 8A and the second cylinder 8B of the rotating shaft 4, respectively. The connecting portion between the crankshaft portions c and d faces the intermediate partition plate 7.

  The crankshaft portions c and d are formed with the same amount of eccentricity from each other by the same amount from the central axis of the main shaft portion and the subshaft portion of the rotating shaft 4 with a phase difference of about 180 °. A first roller 13a is fitted to the crankshaft portion c, and a second roller 13b is fitted to the crankshaft portion d. The first and second rollers 13a and 13b are formed to have the same outer diameter.

  Upper and lower surfaces of the inner diameter portions of the first cylinder 8A and the second cylinder 8B are partitioned by the main bearing 11 and the intermediate partition plate 7, and the intermediate partition plate 7 and the auxiliary bearing 12, respectively. A first cylinder chamber 14a is formed in the inner diameter portion of the first cylinder 8A, and a second cylinder chamber 14b is formed in the inner diameter portion of the second cylinder 8B.

  The first suction refrigerant pipe Pa is connected to a suction passage provided in the first cylinder 8A, and the suction passage communicates with a suction port provided in a predetermined portion of the first cylinder chamber 14a. Therefore, the gas-liquid separator E and the first cylinder chamber 14a communicate with each other through the first suction refrigerant pipe Pa.

  The second suction refrigerant pipe Pb is connected to a suction passage provided in the second cylinder 8B, and this suction passage communicates with a suction port provided in a predetermined portion of the second cylinder chamber 14b. Therefore, the gas-liquid separator E and the second cylinder chamber 14b are communicated with each other via the second suction refrigerant pipe Pb.

  The first roller 13a is accommodated in the first cylinder chamber 14a so as to be eccentrically rotatable, and the second roller 13b is accommodated in the second cylinder chamber 14b so as to be eccentrically rotatable. The first and second rollers 13a and 13b have a phase difference of 180 ° from each other, and part of the peripheral walls along the respective axial directions can be eccentrically rotated while making line contact with the peripheral walls of the cylinder chambers 14a and 14b.

FIG. 2 is an exploded perspective view showing the first cylinder 8A and the second cylinder 8B.
The first cylinder 8A is provided with a first blade chamber 22a, and the second cylinder 8B is provided with a second blade chamber 22b.

  The first blade chamber 22a has a blade housing groove 23a in which both side surfaces of the blade 15a can be slidably moved, and is integrally connected to an end portion of the blade housing groove 23a so as to house a rear end portion of the blade 15a. It consists of a vertical hole 24a.

  Further, the first cylinder 8A is provided with a lateral hole 25a for communicating the outer peripheral wall and the longitudinal hole portion 24a of the first blade chamber 22a, and the spring member 26 is accommodated therein. The spring member 26 is a compression spring that is interposed between the end face of the rear end of the blade 15a and the inner peripheral wall of the sealing case 1, and applies an elastic force (back pressure) to the blade 15a so that the tip edge contacts the roller 13a. is there.

  The second blade chamber 22b has a blade housing groove 23b in which both side surfaces of the blade 15b can be slidably moved, and is integrally connected to an end portion of the blade housing groove 23b so as to house a rear end portion of the blade 15b. It consists of a vertical hole 24b.

  The second cylinder 8B is provided with a horizontal hole 25b that communicates the outer peripheral wall and the vertical hole portion 24b of the second blade chamber 22b, and a magnet 27 is fitted into the second cylinder 8B. The magnet 27 can magnetically attract the blade 15b only when the blade 15b is in a close position. If the blade 15b is in a separated state due to a strong back pressure, it cannot be magnetically attracted.

  At least the vertical hole 24a of the first blade chamber 22a provided in the first cylinder 8A and the vertical hole 24b of the second blade chamber 22b provided in the second cylinder 8B are both in the main bearing 11, It is located outside the outer peripheral wall of the partition plate 7 and the auxiliary bearing 12. In other words, the vertical hole portions 24a and 24b of the blade chambers 22a and 22b are exposed to the inside of the sealed case 1.

  Therefore, the rear end portions of the blades 15a and 15b accommodated in the vertical hole portions 24a and 24b of the blade chambers 22a and 22b and the blade accommodation grooves 23a and 23b respectively receive the internal pressure of the sealed case 1.

  Since each of the blade chambers 22a and 22b is a structure, there is no influence even if the internal pressure of the sealed case 1 is applied. The blades 15a and 15b are movably accommodated in the blade chambers 22a and 22b. In particular, the rear end portions are located in the vertical hole portions 24a and 24b and the blade accommodation grooves 23a and 23b, so that back pressure is received.

  The tips of the blades 15a and 15b are formed in a semicircular shape in plan view. The tip edge of the blade 15a with respect to the first cylinder chamber 14a is set so as to always come into line contact with the peripheral wall of the cylindrical roller 13a by the action of the spring member 26 regardless of the rotation angle of the roller.

  On the other hand, the tip edge of the blade 15b with respect to the second cylinder chamber 14b may be in line contact with the peripheral wall of the cylindrical roller 13b under the influence of the internal pressure of the sealed case 1 depending on conditions, regardless of the rotation angle of the roller. Is set to Further, depending on the conditions, the rear end portion is magnetically attracted to the magnet 27 and the front end edge is held away from the peripheral wall of the roller 13b.

  When the rollers 13a and 13b rotate eccentrically along the inner peripheral walls of the cylinder chambers 14a and 14b, the blades 15a and 15b reciprocate along the blade housing grooves 23a and 23b, and the rear end of the blade has a vertical hole 24a, It becomes possible to advance and retreat from 24b.

  Only the first cylinder 8A is provided with the release mechanism Y, and only the second cylinder 8B is provided with the idle cylinder mechanism X. The release mechanism Y and the cylinder resting mechanism X will be described later.

  As shown in FIG. 1 again, the main bearing 11 and the sub-bearing 12 are provided with discharge valve mechanisms 28a and 28b, respectively. Each discharge valve mechanism 28a, 28b communicates with each cylinder chamber 14a, 14b and is covered with a valve cover.

  As will be described later, the discharge valve mechanisms 28a and 28b are opened while the refrigerant gas compressed in the cylinder chambers 14a and 14b has risen to a predetermined pressure. The compressed refrigerant gas is discharged from the cylinder chambers 14 a and 14 b into the valve cover, and further guided into the sealed case 1.

Next, the release mechanism Y provided in the first cylinder 8A and the cylinder resting mechanism Z provided in the second cylinder 8B will be described.
The release mechanism Y and the cylinder resting mechanism Z are configured to be switched by a four-way switching valve 30 which is one switching means. Specifically, the release mechanism Y and the cylinder resting mechanism Z are set to operate simultaneously or not simultaneously by switching the four-way switching valve 30.

First, the four-way switching valve 30 will be described.
The four-way switching valve 30 has a first port a1 and a second port a2 that communicate with each other, and a third port a3 and a fourth port a4 that communicate with each other depending on the position of the valve element housed therein. Can be set to the switching position.

  Further, the four-way switching valve 30 has a second switching position in which the first port a1 and the fourth port a4 communicate with each other and the second port a2 and the third port a3 communicate with each other depending on the position of the valve. Can be set to

  A second suction refrigerant pipe Pb is connected to the first port a 1 of the four-way switching valve 30, and this refrigerant pipe communicates with the gas-liquid separator E. A second suction refrigerant pipe Pb is connected to the second port a2, and this refrigerant pipe communicates with the second cylinder chamber 14b.

  A high-pressure introduction pipe Pc is connected to the third port a3, and this high-pressure introduction pipe Pc communicates with the inside of the sealed case 1 just above the first cylinder 8A. A release pipe Pd is connected to the fourth port a4, and this release pipe Pd communicates from the sealed case 1 to a release valve chamber 40 provided in the first cylinder 8A.

The release mechanism Y includes a combination of four pipes connected to the four-way switching valve 30 and the following components provided in the release valve chamber 40.
The release valve chamber 40 has a closed wall surface with respect to the first cylinder chamber 14a formed in the first cylinder 8A. A release port 35 composed of a small hole is provided on the closed wall surface, and the first cylinder chamber 14a and the release valve chamber 40 communicate with each other via the release port 35.

  Further, the release valve chamber 40 accommodates a release valve 36 made of a plate. The release valve 36 is elastically pressed and urged by a presser spring 37 so as to close the release port 35.

  As described above, the release pipe Pd communicates with the release valve chamber 40, and the refrigerant gas led to the release pipe Pd fills the release valve chamber 40. Further, the switching operation of the four-way switching valve 30 may lead to a low-pressure refrigerant gas or a high-pressure refrigerant gas to the release pipe Pd.

  In addition, a release port 35 that opens to the first cylinder chamber 14 a is provided on the closed wall surface constituting the release valve chamber 40. The release valve 36 receives a back pressure by the gas pressure of the refrigerant gas filling the release valve chamber 40 and the elastic force of the presser spring 37, and is biased in a direction to close the release port 35.

  On the other hand, the release valve 36 receives the internal pressure of the first cylinder chamber 14 a via the release port 35 and is biased in a direction to open the release port 35. If the back pressure with respect to the release valve 36 is larger than the internal pressure of the first cylinder chamber 14a, the release valve 36 closes the release port 35. If the internal pressure in the first cylinder chamber 14 a is greater than the back pressure for the release valve 36, the release valve 36 opens the release port 35.

  The position at which the release port 35 opens in the first cylinder chamber 14a is the refrigerant sucked into the rotation direction side of the roller 13a from the suction port communicating with the first suction refrigerant pipe Pa, that is, the first cylinder chamber 14a. It is the direction side which compresses gas.

  Therefore, when the release port 35 is opened, the refrigerant gas being compressed in the first cylinder chamber 14 a is led out from the first cylinder chamber 14 a via the release port 35. Until the peripheral wall of the roller 13a in sliding contact with the cylinder chamber 14a passes through the release port 35, the refrigerant gas in the middle of compression is led out, and the compression capacity is reduced accordingly.

The cylinder resting mechanism Z includes four pipes connected to the four-way switching valve 30 and a second blade chamber 22b provided in the second cylinder 8B and accommodating the blade 15b.
As described above, the rear end portion of the blade 15 a accommodated in the first blade chamber 22 a is affected by the internal pressure of the sealed case 1, but the spring member is interposed between the rear end portion of the blade 15 a and the sealed case 1. 26 is interposed and is always elastically pressed and biased by the spring member 26.

  On the other hand, a magnet 27 is provided in the second blade chamber 22b and faces the rear end of the blade 15b. The magnetic attraction force of the magnet 27 to the blade 15b is weak, and even if magnetically attracted, if the blade 15b receives a high pressure in the direction opposite to the magnetic attraction direction, it is easily separated. The rear end portion of the blade 15b is influenced by the internal pressure of the sealed case 1 as a back pressure, and the front end portion of the blade 15b is affected by the internal pressure of the second cylinder chamber 14b.

  Depending on the switching operation of the four-way switching valve 30, the high pressure gas may be guided to the second cylinder chamber 14b or the low pressure gas may be guided. For this reason, a pressure difference is generated or not generated at the front end portion and the rear end portion of the blade 15b, the position (state) of the blade 15b is set, and the cylinder resting operation and the normal operation are switched. ing.

(1) When full capacity operation (normal operation) is selected:
At high loads such as at start-up, normal operation that is full capacity operation is performed.
As shown by a solid arrow in FIG. 1, the control unit communicates the four-way switching valve 30 with the first port a1 and the second port a2 and with the third port a3 and the fourth port a4. , Control to the first switching position. And a control part sends an operation signal to the electric motor part 2 via an inverter, and drives the rotating shaft 4 by high rotation.

  The rollers 13a and 13b rotate eccentrically in the cylinder chambers 14a and 14b. In the first cylinder 8A, since the blade 15a is always elastically pressed and urged by the spring member 26, the tip edge of the blade 15a is slidably contacted with the peripheral wall of the roller 13a regardless of the internal pressure of the sealed case 1. The cylinder chamber 14a is divided into a suction chamber and a compression chamber.

When the inner wall rolling contact position of the first cylinder chamber 14a of the roller 13a coincides with the blade housing groove 23a, and the blade 15a is most retracted, the space capacity of the first cylinder chamber 14a is maximized.
As shown by the solid line arrow in the figure, the low-pressure refrigerant gas passes through the first suction refrigerant pipe Pa from the gas-liquid separator E and the second suction refrigerant pipe Pb provided with the four-way switching valve 30 in the middle. The two-cylinder rotary compressor A is sucked into the first cylinder chamber 14a and the second cylinder chamber 14b.

  In the first cylinder chamber 14a, as the roller 13a rotates eccentrically, the rolling contact position of the roller 13a with respect to the inner peripheral wall of the first cylinder chamber 14a moves, and the volume of the compression chamber partitioned by the cylinder chamber 14a decreases. To do. Therefore, the gas previously introduced into the first cylinder chamber 14a is gradually compressed.

  The rotary shaft 4 is continuously rotated, the compression chamber capacity of the first cylinder chamber 14a is further reduced, the gas is compressed, and when the pressure rises to a predetermined pressure, the discharge valve mechanism 28a is opened. The high-pressure refrigerant gas is discharged into the sealed case 1 through the valve cover and is filled.

  Due to the compression action in the first cylinder chamber 14a, the inside of the sealed case 1 is in a high pressure atmosphere. Since the rear end of the blade 15b on the second cylinder 8B side is exposed in the sealed case 1, it is in a high-pressure atmosphere. On the other hand, low pressure refrigerant is sucked into the second cylinder chamber 14b via the second suction refrigerant pipe Pb, and the tip of the blade 15b is in a low pressure atmosphere.

  The tip of the blade 15b is in a low pressure atmosphere, the rear end is in a high pressure atmosphere, and a differential pressure is generated between the tip and the rear end. The rear end portion of the blade 15b is pushed to a high pressure, and the leading edge comes into contact with the peripheral wall of the roller 13b. The eccentric rotation of the roller 13a in the first cylinder chamber 14a and the eccentric rotation of the roller 13b in the second cylinder chamber 14b have a phase difference of 180 °.

The blade 15a on the first cylinder chamber 14a side is pressed and urged by the spring member 26, and the same compression action as the compression action is performed also in the second cylinder chamber 14b.
At this time, the rear end of the blade 15b repeatedly approaches and separates from the magnet 27 provided in the blade chamber 22b. However, since the back pressure is applied to the blade 15b, the magnet 27 magnetically attracts the rear end of the blade 15b. Never do. Therefore, the cylinder resting mechanism Z does not work.

By setting the four-way switching valve 30 to the first switching position, the third port a3 and the fourth port a4 communicate with each other as described above. As shown by the solid line arrow in the figure, the high-pressure refrigerant gas that fills the sealed case 1 is guided from the high-pressure introduction pipe Pc to the release pipe Pd through the four-way switching valve 30.
The high-pressure refrigerant gas fills the release valve chamber 40 provided in the first cylinder 8A and presses the release valve 36. The release valve 36 is pressed by the high-pressure refrigerant gas at the position pressed by the presser spring 37, and reliably closes the release port 35.

In the first cylinder chamber 14a, the roller 13a rotates eccentrically to compress the low-pressure refrigerant gas sucked from the first suction refrigerant pipe Pa. The compression is in progress until the roller 13a passes through the release port 35, and the internal pressure of the first cylinder chamber 4a facing the release port 35 is lower than the pressure of the compressed refrigerant gas filling the release valve chamber 40. .
Accordingly, the release valve 36 continues to close the release port 35 due to a strong back pressure, and the release mechanism Y does not act.

  Eventually, the compression action is performed in the first cylinder chamber 14a, the compression action is also performed in the second cylinder chamber 14b, and the normal operation (full capacity operation) in which the compression action is performed in the cylinder chambers 14a and 14b is performed. Is called.

  The high-pressure gas discharged from the sealed case 1 through the refrigerant pipe P is led to the condenser B to be condensed and liquefied, adiabatically expanded by the expansion mechanism C, and the evaporator D takes the latent heat of evaporation from the heat exchange air and cools it. It works. The evaporated refrigerant is led to the gas-liquid separator E to be gas-liquid separated, and is again sucked into the two-cylinder rotary compressor A from the first and second suction refrigerant pipes Pa and Pb and performs the above-described compression action. .

(2) When reduced capacity operation (cylinder operation + release operation) is selected:
Although the air conditioning load is large at the time of starting, if the air conditioning operation is continued to some extent, the air conditioning load becomes small. At this time, the ability-reducing operation that automatically proceeds with the cylinder resting operation + the release operation is automatically selected.

That is, the control unit controls the four-way switching valve 30 to the second switching position where the first port a1 and the fourth port a4 communicate with each other and the second port a2 and the third port a3 communicate with each other. Make.
As indicated by broken line arrows in FIG. 1, the low-pressure refrigerant gas guided from the gas-liquid separator E to the second suction refrigerant pipe Pb flows through the release pipe Pd via the four-way switching valve 30. Since the release pipe Pd communicates with the release valve chamber 40, a low-pressure refrigerant gas is led into the release valve chamber 40 to be filled.

  The release valve 36 receives the pressure during the compression in the first cylinder chamber 14a while receiving the presser spring 37 and the back pressure of the low-pressure refrigerant gas. The pressure in the middle of compression in the first cylinder chamber 14a is higher than the back pressure plus the low pressure of the refrigerant gas and the elastic force of the presser spring 37.

  The release valve 36 moves leftward from the position in FIG. 1 and opens the release port 35. Therefore, the refrigerant gas being compressed in the first cylinder chamber 14a flows out into the release pipe Pd, and the compression capacity is reduced. In the first cylinder chamber 14a, a so-called high pressure release operation is performed.

  At the same time, a part of the high-pressure refrigerant gas filling the sealed case 1 is led from the high-pressure introduction pipe Pc to the second suction refrigerant pipe Pb through the four-way switching valve 30 as indicated by the broken line arrow in the figure. Further, the high-pressure refrigerant gas is led to the second cylinder chamber 14b and is filled, and the tip of the blade 15b is changed to a high-pressure atmosphere.

The rear end portion of the blade 15b provided in the second cylinder 8B is exposed in the sealed case 1 and exposed to the high-pressure atmosphere in the sealed case 1. The blade 15b has a high-pressure atmosphere at the front end and the rear end, and no differential pressure is generated at the front-rear end.
As the roller 13b rotates, the blade 15b is pushed away and retracts along the blade housing groove 23b. When the rear end portion of the blade 15b comes close to the magnet 27, it is magnetically attracted and maintains its position. The tip of the blade 15b is kept at a position separated from the peripheral wall of the roller 13b, and the roller 13b is idle.

  That is, in the second cylinder chamber 14b, a so-called cylinder deactivation operation state is achieved in which no compression action is performed. As described above, the operation becomes simultaneous with the release operation in the first cylinder chamber 14a, and the compression capacity is reduced according to the load.

  Thus, in accordance with the switching operation of the four-way switching valve 30, the full capacity operation (normal operation) in which the compression operation is simultaneously performed in the first cylinder chamber 14a and the second cylinder chamber 14b, and the first cylinder chamber 14a At the same time as the release operation is performed, the cylinder can be switched between the cylinder closed operation and the release operation in which the cylinder rest operation is performed in the second cylinder chamber 14b.

In particular, by changing the position of the release port 35 that constitutes the release mechanism Y, the amount of refrigerant gas that is being compressed from the second cylinder chamber 14b to the low pressure side can be arbitrarily set, and the selection range can be further expanded. .
Therefore, it is possible to provide the two-cylinder rotary compressor A that is highly efficient and has an increased capability variable range and can improve reliability. The component parts and the piping configuration are simplified, and accordingly, a reduction in space can be promoted, and control can be facilitated and costs can be reduced. In the refrigeration cycle apparatus provided with the two-cylinder rotary compressor A, the refrigeration cycle efficiency can be improved.

Next, a two-cylinder rotary compressor Aa in the second embodiment will be described with reference to FIG. The same components as those in FIGS. 1 and 2 are denoted by the same reference numerals or not shown, and a new description is omitted. (same as below)
Here, the thickness of the intermediate partition plate 7A interposed between the first cylinder 8A and the second cylinder 8B is formed thicker than the intermediate partition plate 7 described in the first embodiment. Yes. A suction passage 39 is provided through the sealed case 1 in the radial direction from the outer peripheral wall of the intermediate partition plate 7A.

  A suction refrigerant pipe P extending from the gas-liquid separator E is connected to the suction passage 39. That is, only one suction refrigerant pipe P is provided, and the gas-liquid separator E and the two-cylinder rotary compressor Aa are communicated with one suction refrigerant pipe P.

The front end of the suction passage 39 is branched in the vertical direction of the intermediate partition plate 7A, and the suction passage branched upward is communicated with the suction port of the first cylinder chamber 14a provided in the first cylinder 8A. . The suction passage branched downward communicates with the suction port of the second cylinder chamber 14b provided in the second cylinder 8B.
Therefore, in this embodiment, the gas-liquid separator E communicates with the first cylinder chamber 14a and the second cylinder chamber 14b through one suction refrigerant pipe P.

  Further, a release valve chamber 40a constituting a release mechanism Ya is provided in a portion opposite to the suction passage 39 of the intermediate partition plate 7A and the central axis of the intermediate partition plate 7A. A release valve 36a is accommodated in the release valve chamber 40a so as to be movable in the radial direction of the intermediate partition plate 7A.

The release valve 36a is pressed and urged to the outer peripheral side by a presser spring 37a. As shown in FIG. 3, in a state where the release valve 36a is pressed against the elastic biasing force of the presser spring 37a,
As will be described later, even if the roller 13a of the first cylinder chamber 14a rotates eccentrically and the roller 13b rotates eccentrically in the second cylinder chamber 14b, each cylinder chamber 14a, 14b has no change and does not have a sealed structure. ing.

  However, unlike the case shown in FIG. 3, the release valve 36a is affected by the elastic force of the presser spring 37a. The cylinder chambers 14a and 14b communicate with each other through a part of the release valve chamber 40a according to the position of the roller 13b that rotates eccentrically.

  On the other hand, the second blade chamber 22b provided in the second cylinder 8B has an intermediate partition plate 7A on the upper surface of the second cylinder 8B and a portion of the auxiliary bearing 12 on the lower surface enlarged in the outer diameter direction. The upper and lower surfaces are sealed. In other words, in this embodiment, the second blade chamber 22b is not exposed in the sealed case 1 and is not affected by the internal pressure of the sealed case 1.

  A magnet 27a is attached to the second blade chamber 22b, and the magnet 27a is provided with a groove along the radial direction of the second cylinder 8B. Therefore, the outer peripheral side and the inner peripheral side of the blade chamber 22b are in communication with each other through the groove portion of the magnet 27a.

  Here, a three-way switching valve 30a is used as the switching means. The three-way switching valve 30a has a first switching position in which the second port b2 and the third port b3 communicate with each other and the first port b1 is closed, The switching can be set to the second switching position where the port b1 and the third port b3 communicate with each other and the second port b2 is closed.

  Connected to the first port b1 of the three-way switching valve 30a is a low-pressure inlet pipe Pf that branches from a midway portion of the suction refrigerant pipe P that communicates the gas-liquid separator E and the suction passage 39 of the intermediate partition plate 7A. . The second port b2 is connected to a high-pressure introduction pipe Pg with an open end facing the sealed case 1.

  A guide pipe Ph is connected to the third port b3. The distal end of the guide pipe Ph includes a release pipe Pj connected to the release valve chamber 40a, and a back pressure pipe Pi that penetrates the sealing case 1 and communicates from the outer peripheral wall of the second cylinder 8B to the second blade chamber 22b. A branch is provided.

  During full capacity operation, the three-way switching valve 30a is set to the first switching position that connects the second port b2 and the third port b3 and closes the first port b1. The high-pressure refrigerant gas that fills the sealed case 1 is guided from the high-pressure introduction pipe Pg to the guide pipe Ph through the three-way switching valve 30a as indicated by solid arrows in the figure.

  Then, the flow is divided from the guide pipe Ph into the release pipe Pj and the back pressure pipe Pi. The high-pressure refrigerant gas guided to the release pipe Pj fills the release valve chamber 40a and presses and biases the release valve 36a against the elastic force of the presser spring 37a.

  The release valve 36a communicates the first cylinder chamber 14a and the second cylinder chamber 14b regardless of the position of the roller 13a in the first cylinder chamber 14a and the position of the roller 13b in the second cylinder chamber 14b. Stop. That is, the cylinder chambers 14a and 14b have a sealed structure.

  The high-pressure refrigerant gas guided to the back pressure pipe Pi fills the second blade chamber 22b and flows into the rear end portion of the blade 15b through the groove portion of the magnet 27a provided here. As described above, since the second blade chamber 22b has a sealed structure, a high back pressure is applied to the rear end portion of the blade 15b.

  In the first cylinder chamber 14a, the blade 15a, whose rear end is pressed by the presser spring 26, is in sliding contact with the peripheral wall of the roller 13a. In the second cylinder chamber 14b, the blade 15b whose rear end is pressed by the high-pressure gas slides in contact with the peripheral wall of the roller 13b.

  The low-pressure refrigerant gas guided from the gas-liquid separator E to the suction refrigerant pipe P is guided to the suction passage 39, and is branched and compressed to the suction port of the first cylinder chamber 14a at the tip. At the same time, the flow is diverted to the suction port of the second cylinder chamber 14b and compressed. The first cylinder chamber 14a and the second cylinder chamber 14b perform full capacity operation in which a compression action is simultaneously performed.

When the three-way switching valve 30a is switched to the second switching position where the first port b2 and the third port b3 are communicated and the second port b2 is closed, the release operation and the idle cylinder operation are performed simultaneously.
That is, a part of the low-pressure refrigerant gas guided from the gas-liquid separator E to the suction refrigerant pipe P is transferred from the low-pressure introduction pipe Pf through the three-way switching valve 30a and the guide pipe Ph as shown by broken line arrows in the figure. The flow is divided into the release pipe Pj and the back pressure pipe Pi.

The low-pressure refrigerant gas guided to the release pipe Pj fills the release valve chamber 40a and applies a back pressure to the release valve 36a. However, since the pressure is low, the elastic force of the presser spring 37a is won and the release valve 36a moves to the left in FIG.
In this state, a part of the release valve chamber 40a has a first cylinder chamber corresponding to the positions of the roller 13a eccentrically rotated to the first cylinder chamber 14a and the roller 13b eccentrically rotated to the second cylinder chamber 14b. 14a communicates with the second cylinder chamber 14b.

  Since each roller rotates eccentrically with a phase difference of 180 °, when one cylinder chamber is in the suction process, the other cylinder chamber is in the discharge process. Moreover, since the other cylinder chambers 14a and 14b communicate with each other via the release valve chamber 40a, a release operation is performed in which refrigerant gas in the middle of compression flows into the cylinder chamber during the suction process.

  The low-pressure refrigerant gas guided to the back pressure pipe Pi fills the second blade chamber 22b and applies back pressure to the rear end portion of the blade 15b through a groove provided in the magnet 27a. On the other hand, low-pressure refrigerant gas is guided to the first cylinder chamber 14a and the second cylinder chamber 14b via the suction refrigerant pipe P and the suction passage 39 provided in the intermediate partition plate 7A.

  In the first cylinder chamber 14a, since the blade 15a is pressed by the spring member 26, the leading edge thereof is in sliding contact with the peripheral wall of the roller 13a. That is, the compression operation (release operation) is performed with the eccentric rotation of the roller 13a.

  However, in the second cylinder chamber 14b, the front end portion and the rear end portion of the blade 15b are both in a low pressure atmosphere, and no differential pressure is generated at the front rear end portion. The blade 15b is pushed away by the roller 13b, and the magnet 27b magnetically attracts the blade 15b at that position. Therefore, the cylinder resting operation in which the compression action is not performed in the second cylinder chamber is performed.

FIG. 4 shows a two-cylinder rotary compressor Ab in the third embodiment.
Here, the structure of the first cylinder 8A and the second cylinder 8B, the first cylinder chamber 14a and the gas-liquid separator E communicate with each other via the first suction refrigerant pipe Pa, and the second cylinder chamber 14b. The point that the gas-liquid separator E communicates with the second suction refrigerant pipe Pb is exactly the same as that described in the first embodiment.

  However, the first three-way switching valve 40a and the second three-way switching valve 40b are provided as means for switching between full capacity operation and idle cylinder operation + release operation, and the piping configuration associated therewith is different from that of the release mechanism Yb. The cylinder mechanism Zb is provided.

  That is, the first release pipe Pd branched from the middle portion of the first suction refrigerant pipe Pa is connected to the first port of the first three-way switching valve 40a. A second release pipe Pk that communicates with a release valve chamber 40 provided in the first cylinder 8A is connected to the second port.

A guide pipe Pl is connected to the third port, and this guide pipe Pl is connected to a third port in the second three-way switching valve 40b. Further, the high-pressure introduction pipe Pm is branched from the middle part of the guide pipe Pl, and this faces the open end in the sealed case 1.
A second suction refrigerant pipe Pb extending from the gas-liquid separator E is connected to a first port of the second three-way switching valve 40b, and a second port provided in the second cylinder 8B is connected to the second port. The second suction refrigerant pipe Pb communicating with the cylinder chamber 14b is connected as it is.

  During full capacity operation, as indicated by solid arrows in the figure, low-pressure refrigerant gas is led from the gas-liquid separator E to the first cylinder chamber 14a via the first suction refrigerant pipe Pa, and the second suction refrigerant. It is led to the second cylinder chamber 14b through the pipe Pb and the second three-way switching valve 40b.

  In the first cylinder chamber 14a, the blade 15a is pressed and biased by the spring member 26, so that a compression action is performed. The compressed high-pressure gas fills the sealed case 1. A part of the high-pressure gas is led from the high-pressure introduction pipe Pm to the second release pipe Pk via the second three-way switching valve 40b and fills the release valve chamber 40.

In the release valve chamber 40, the high-pressure refrigerant gas applies back pressure to the release valve 36 together with the presser spring 37 so as to close the release port 35. Therefore, refrigerant gas in the middle of compression does not escape from the first cylinder chamber 14a, and normal compression action is performed.
The low-pressure refrigerant gas introduced into the second cylinder chamber 14b makes the tip of the blade 15b a low-pressure atmosphere. On the other hand, the rear end portion of the blade 15b is exposed in the sealed case 1 to form a high-pressure atmosphere.

A differential pressure is generated at the front and rear end portions of the blade 15b, and a back pressure is applied so that the leading edge comes into sliding contact with the roller 13b. Therefore, the normal compression action is performed in the second cylinder chamber 14b together with the first cylinder chamber 14a.
In order to perform the idle cylinder operation + release operation, the first three-way switching valve 40a and the second three-way switching valve 40b are switched. As indicated by a broken line arrow in the figure, a part of the low-pressure refrigerant gas led from the gas-liquid separator E to the first suction refrigerant pipe Pa is divided into the first release pipe Pd.

  The refrigerant gas is guided to the second release pipe Pk through the first three-way switching valve 40a and fills the release valve chamber 40. The release valve 36 receives the pressure spring 37 and the back pressure of the low-pressure refrigerant gas, while receiving the pressure during compression in the first cylinder chamber 14 a, and the release valve 36 opens the release port 35.

  Therefore, the refrigerant gas being compressed in the first cylinder chamber 14a flows out to the second release pipe Pk, and the compression capacity is reduced. In the first cylinder chamber 14a, a so-called high pressure release operation is performed.

  At the same time, part of the high-pressure refrigerant gas filling the sealed case 1 is led from the high-pressure introduction pipe Pm and the guide pipe Pl to the second suction refrigerant pipe Pb through the second three-way switching valve 40b. Further, the high-pressure refrigerant gas is led to the second cylinder chamber 14b and is filled, and the tip of the blade 15b is changed to a high-pressure atmosphere.

  The blade 15b has a high-pressure atmosphere at the front end and the rear end, and no differential pressure is generated at the front-rear end. As the roller 13b rotates, the blade 15b is pushed away, and is magnetically attracted when the rear end portion is close to the magnet 27, and maintains its position. In the second cylinder chamber 14b, a compression operation is not performed, which is a so-called cylinder resting operation state.

  FIG. 5 shows a two-cylinder rotary compressor Ac in the fourth embodiment.

  Here, the structure of the first cylinder 8A and the second cylinder 8B, the structure of the intermediate partition plate 7A interposed between the first cylinder 8A and the second cylinder 8B, and the first cylinder chamber 14a And the second cylinder chamber 14b communicate with each other from the gas-liquid separator E via the suction refrigerant pipe P, and are exactly the same as those described in the second embodiment.

However, the first three-way switching valve 50a and the second three-way switching valve 50b are provided as means for switching between full capacity operation and idle cylinder operation + release operation, and the piping configuration associated therewith is different from that of the release mechanism Yc. The cylinder mechanism Zc is provided.
That is, the first port of the first three-way switching valve 50a is connected to the low pressure introduction pipe Pn branched from the midway portion of the suction refrigerant pipe P. A release pipe Po communicating with a release valve chamber 40a provided in the first cylinder 8A is connected to the second port.

  A guide pipe Pq is connected to the third port, and this guide pipe Pq is connected to a third port in the second three-way switching valve 50b. Further, the high-pressure introduction pipe Pp is branched from the middle part of the guide pipe Pq, and this faces the open end in the sealed case 1.

  A first branch pipe Ps branched from the low-pressure introduction pipe Pn is connected to the first port of the second three-way switching valve 50b. A second branch pipe Pr communicating with a blade chamber 22b provided in the second cylinder 8B is connected to the second port.

  During full capacity operation, the first three-way switching valve 50a causes the high-pressure refrigerant gas that fills the sealed case 1 to flow from the high-pressure inlet pipe Pp through the first three-way switching valve 50a, as indicated by solid arrows in the figure. Guide to the release tube Po. The high-pressure refrigerant gas fills the release valve chamber 40a and presses and biases the release valve 36a against the elastic force of the presser spring 37a.

  The release valve 36a communicates the first cylinder chamber 14a and the second cylinder chamber 14b regardless of the position of the roller 13a in the first cylinder chamber 14a and the position of the roller 13b in the second cylinder chamber 14b. Stop. Therefore, the cylinder chambers 14a and 14b have a sealed structure.

Further, the high-pressure refrigerant gas guided from the high-pressure introduction pipe Pp to the guide pipe Pq fills the second blade chamber 22b via the second three-way switching valve 50b and the second branch pipe Pr. Then, a high back pressure is applied to the rear end portion of the blade 15b through the groove portion of the magnet 27a.
In the first cylinder chamber 14a, the blade 15a whose rear end is pressed by the presser spring 26 has its front end slidably contacted with the peripheral wall of the roller 13a, and in the second cylinder chamber 14b, the rear end is pressed by high-pressure gas. The blade 15b slidably contacts the peripheral edge of the roller 13b.

  The low-pressure refrigerant gas guided from the gas-liquid separator E to the suction refrigerant pipe P is guided through the suction passage 39, and is branched and compressed at the tip portion to the suction port of the first cylinder chamber 14a. At the same time, the flow is diverted to the suction port of the second cylinder chamber 14b and compressed. The first cylinder chamber 14a and the second cylinder chamber 14b perform full capacity operation in which a compression action is simultaneously performed.

In order to perform the release operation and the idle cylinder operation at the same time, the first three-way switching valve 50a and the second three-way switching valve 50b are switched.
The low-pressure refrigerant gas led from the gas-liquid separator E to the suction refrigerant pipe P is led from the low-pressure introduction pipe Pn to the first three-way switching valve 50a and from the low-pressure introduction pipe Pn as shown by the broken line arrow in the figure. The flow is divided and guided to the first branch pipe Ps, and further fills the second blade chamber 22b (not shown by the broken arrow) via the second three-way switching valve 50b and the second branch pipe Pr.

  The low-pressure refrigerant gas guided to the first three-way switching valve 50a fills the release valve chamber 40a from the release pipe Po and applies a back pressure to the release valve 36a. Since the pressure is low, the elastic force of the presser spring 37a is won and the release valve 36a moves to the left in FIG.

  In this state, a part of the release valve chamber 40a has a first cylinder chamber corresponding to the positions of the roller 13a eccentrically rotated to the first cylinder chamber 14a and the roller 13b eccentrically rotated to the second cylinder chamber 14b. 14a communicates with the second cylinder chamber 14b. A release operation is performed in which the refrigerant gas being compressed in one cylinder chamber flows into the other cylinder chamber during the suction process.

  Further, the low-pressure refrigerant gas filled in the second blade chamber 22b from the second three-way switching valve 50b applies back pressure to the rear end portion of the blade 15b through a groove provided in the magnet 27a. On the other hand, low-pressure refrigerant gas is guided to the first cylinder chamber 14a and the second cylinder chamber 14b via the suction refrigerant pipe P and the suction passage 39 provided in the intermediate partition plate 7A.

  In the first cylinder chamber 14a, the blade 15a is pressed by the spring member 26, so that the leading edge is in sliding contact with the peripheral wall of the roller 13a. That is, the compression operation (release operation) is performed with the eccentric rotation of the roller 13a.

  However, in the second cylinder chamber 14b, the front end portion and the rear end portion of the blade 15b are both in a low pressure atmosphere, and no differential pressure is generated at the front rear end portion. The blade 15b is pushed away by the roller 13b, and the magnet 27b magnetically attracts the blade 15b at that position. Therefore, in the second cylinder chamber 14b, a cylinder resting operation is performed in which no compression action is performed.

  In addition, although it demonstrated as 2 cylinder rotary compressor A, Aa, Ab, Ac here, it is not limited to this, A rotary compressor provided with more cylinders may be sufficient, and the compression The refrigeration cycle apparatus provided with the machine may be used. Of course, the compressor itself is not limited to the configuration described above, and various modifications can be made without departing from the scope of the present invention.

The longitudinal cross-sectional view and refrigeration cycle block diagram of the 2-cylinder rotary compressor which concern on 1st Embodiment in this invention. The perspective view which decomposed | disassembled the 1st cylinder and 2nd cylinder based on the embodiment. The longitudinal cross-sectional view of the 2-cylinder rotary compressor which concerns on 2nd Embodiment in this invention. The longitudinal cross-sectional view of the 2-cylinder rotary compressor which concerns on 3rd Embodiment in this invention. The longitudinal cross-sectional view of the 2-cylinder rotary compressor which concerns on 4th Embodiment in this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Sealing case, 4 ... Rotating shaft, 3 ... Electric motor part, 2 ... Compression mechanism part, 2A ... 1st compression mechanism part, 2B ... 2nd compression mechanism part, 13a, 13b ... Roller, 14a ... 1st Cylinder chamber, 14b ... second cylinder chamber, 8A ... first cylinder, 8B ... second cylinder, 15a, 15b ... blade, 28a, 28b ... discharge valve mechanism, A ... two-cylinder rotary compressor, Y ... Release mechanism, Z ... cylinder resting mechanism, 30 ... four-way switching valve (switching means), 35 ... release port, 40 ... release valve chamber, 36 ... release valve, 30a ... three-way switching valve (switching means), 7A ... intermediate partition plate 40a ... Release valve chamber, 36a ... Release valve, B ... Condenser, C ... Expansion mechanism, D ... Evaporator.

Claims (4)

In the sealed case, an electric motor unit and a plurality of compression mechanism units connected through a rotating shaft are accommodated,
Each of the compression mechanisms is
A cylinder having a cylinder chamber in which a roller is rotatably accommodated eccentrically;
A blade that is movably provided with respect to the cylinder chamber, and a tip edge that abuts against the peripheral wall of the roller in a pressed state, and bisects the cylinder chamber with the eccentric rotation of the roller;
In the multi-cylinder rotary compressor including a discharge valve mechanism for discharging the gas compressed in the cylinder chamber into the sealed case,
A release mechanism that is provided in at least one compression mechanism, and releases the gas that is being compressed in the cylinder chamber to the low pressure side;
A cylinder resting mechanism that is provided in at least one other compression mechanism section and that separates the blade tip edge from the peripheral wall of the roller to stop the compression operation in the cylinder chamber;
Operation is switched between full-capacity operation in which compression operation is performed in all compression mechanism units, idle cylinder operation in a compression mechanism unit equipped with a deactivation mechanism, and release operation in a compression mechanism unit equipped with a release mechanism. A multi-cylinder rotary compressor characterized by comprising one switching means. The one switching means is one four-way switching valve,
The release mechanism is provided in the first cylinder and opens to the first cylinder chamber, a release valve chamber provided with the release port, and the release port provided in the release valve chamber can freely open and close the release port. With release valve,
The cylinder resting mechanism is provided in a second cylinder, and includes a blade whose tip receives the internal pressure of the second cylinder chamber and whose rear end receives the internal pressure of the sealed case,
The four-way switching valve
First switching that introduces high-pressure gas into the release valve chamber and closes the release port with the release valve, and introduces low-pressure gas into the second cylinder chamber to generate a differential pressure between the leading end and the trailing end of the blade location and,
A second switching in which a low pressure gas is introduced into the release valve chamber and the release port is opened by the release valve, and a high pressure gas is introduced into the second cylinder chamber so that no differential pressure is generated between the front end portion and the rear end portion of the blade. The multi-cylinder rotary compressor according to claim 1, wherein the multi-cylinder rotary compressor can be switched to a position. The first cylinder chamber provided in the first compression mechanism section and the second cylinder chamber provided in the second compression mechanism section are configured with a phase difference of 180 ° from each other.
The one switching means is one three-way switching valve,
The release mechanism includes a release valve chamber provided in an intermediate partition plate interposed between the first cylinder and the second cylinder, and a first cylinder chamber and a second cylinder chamber provided in the release valve chamber. Equipped with release valves that shut off each other or communicate with each other,
The cylinder resting mechanism is provided in the second cylinder, applies a back pressure to the blade of the second cylinder chamber,
The one three-way switching valve is
A high pressure gas is introduced into the release valve chamber, the first cylinder chamber and the second cylinder chamber are shut off from each other by the release valve, and a high pressure back pressure is applied to the blade rear end of the second cylinder chamber. A first switching position where the leading edge of the blade is in sliding contact with the roller;
A low pressure gas is introduced into the release valve chamber so that the first cylinder chamber and the second cylinder chamber communicate with each other by the release valve, and a low pressure back pressure is applied to the rear end of the blade of the second cylinder chamber. 2. The multi-cylinder rotary compressor according to claim 1, wherein the multi-cylinder rotary compressor can be switched to a second switching position where the leading edge of the blade is pushed away with the rotation of the roller.   A refrigeration cycle apparatus comprising the multi-cylinder rotary compressor according to any one of claims 1 to 3, a condenser, an expansion mechanism, and an evaporator to constitute a refrigeration cycle.

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