JP2008291650A - Rotary type two stage compressor and air conditioning machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary type two stage compressor with improved compressor efficiency. <P>SOLUTION: A rotary type two stage compressor compressing refrigerant by a first compression element which is a low stage compression element and compressing the refrigerant by a second compression element which is a high stage compression element includes a low stage retainer regulating quantity of refrigerant discharged from the low stage compression element via a low stage delivery port, and a high stage retainer regulating quantity of refrigerant discharged from the high stage compression element via a high stage delivery port. A shape of the low stage delivery port and a shape of the high stage delivery port are same. When lift of the low stage retainer and lift of the high stage retainer are defined as H1, H2 respectively, the purpose of this invention is achieved by making their relation to be H1>H2. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rotary two-stage compressor having a low-stage compression element and a high-stage compression element in a compression mechanism section.

  As rotary type two-stage compressors, those disclosed in Patent Documents 1 and 2 are known. Further, Patent Document 2 is known as disclosing the optimization of the discharge shape of a compression element in a rotary multistage compressor. Patent Document 2 discloses a technique for improving compressor efficiency by optimizing the discharge shape of a compression element in a rotary multistage compressor. When the low-stage discharge diameter is φD1 and the high-stage discharge diameter is φD2, if φD2 <φD1, the pressure loss of the low-stage compression element is reduced and the dead volume of the high-stage compression element is reduced, improving the volume efficiency. Is disclosed.

JP 60-128990 A JP 2002-98081 A

  However, regarding this Patent Document 2, when the rotary multistage compressor is used in an injection cycle that is a high efficiency cycle, the flow rate of the low-stage compression element discharge gas is higher than that of the high-stage compression element discharge gas. There is a problem of increasing the pressure loss of the high-stage compression element. Moreover, in order to prevent this, it is necessary to change the machining shapes of the low and high cylinders respectively, which causes changes in the machining process, resulting in increased setup time and machining defects. There is a problem.

  An object of the present invention is to provide a rotary two-stage compressor having improved compressor efficiency.

  Another object of the present invention is to provide an air conditioner having improved cycle efficiency in an air conditioner including a rotary two-stage compressor.

The object of the present invention is as follows.
A rotary two-stage compressor that compresses refrigerant with a low-stage compression element that is a first compression element and compresses the refrigerant with a high-stage compression element that is a second compression element,
A low stage retainer that regulates the amount of refrigerant discharged from the low stage compression element via a low stage discharge port;
A high stage retainer that regulates the amount of refrigerant discharged from the high stage compression element via a high stage discharge port,
The shape of the low stage outlet and the shape of the high stage outlet are the same,
When the lift amount of the low stage retainer is H1, the lift amount of the high stage retainer is H2,
H1> H2
This is achieved.

The object of the present invention is as follows.
A rotary two-stage compressor used in an air conditioner having an injection flow path for returning a refrigerant between a low-stage compression element and a high-stage compression element of a rotary two-stage compressor,
A low stage retainer that regulates the amount of refrigerant discharged from the low stage compression element via a low stage discharge port;
A high stage retainer that regulates the amount of refrigerant discharged from the high stage compression element via a high stage discharge port,
The shape of the low stage outlet and the shape of the high stage outlet are the same,
When the lift amount of the low stage retainer is H1, the lift amount of the high stage retainer is H2,
H1 <H2
This is achieved.

The object of the present invention is as follows.
A compressor, a first heat exchanger, a first expansion mechanism, a gas-liquid separator, a second expansion mechanism, and a second heat exchanger, which are sequentially connected, and In an air conditioner having a refrigeration cycle configured to be connected to the compressor from a second heat exchanger,
The compressor is
A rotary two-stage compressor that compresses refrigerant with a low-stage compression element that is a first compression element and compresses the refrigerant with a high-stage compression element that is a second compression element,
A low stage retainer that regulates the amount of refrigerant discharged from the low stage compression element via a low stage discharge port;
A high stage retainer that regulates the amount of refrigerant discharged from the high stage compression element via a high stage discharge port,
A flow path that connects the gas-liquid separator and the low-stage compression element and the high-stage compression element, and sends a gaseous refrigerant from the gas-liquid separator to the high-stage compression element An injection flow path capable of
The shape of the low stage outlet and the shape of the high stage outlet are the same,
When the lift amount of the low stage retainer is H1, the lift amount of the high stage retainer is H2,
H1 <H2
This is achieved.

  According to the present invention, the compressor efficiency of a rotary two-stage compressor can be improved.

  Moreover, the cycle efficiency of the air conditioner can be improved.

  A rotary type two-stage compressor according to a first embodiment of the present invention will be described with reference to FIGS. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent. FIG. 1 is a longitudinal sectional view of a rotary two-stage compressor showing an embodiment of the present invention, FIG. 2 is a block diagram of a rotary two-stage compressor showing an embodiment of the present invention, and FIG. 4 is a cross-sectional view taken along the line A-A in FIG. 3, FIG. 5 is a cross-sectional view taken along the line Y-Y in FIG. 1, and FIG. 6 is a cross-sectional view taken along the line BB in FIG. .

  The compressor 1 includes a sealed container 13 including a bottom portion 21, a lid portion 12, and a body portion 22. An electric motor 14 having a stator 7 and a rotor 8 is provided at the upper part in the sealed container 13. The outer periphery of the stator 7 is fixed to the hermetic container 13, and the rotor 8 is fixed to the outer periphery of the upper portion of the crankshaft 2 and is rotatably disposed in the stator 7. When the stator 7 is energized, the rotor 8 is rotated, and the crankshaft 2 is driven and rotated accordingly. A compression mechanism unit including a low-stage compression element 20a and a high-stage compression element 20b is provided in the lower part of the hermetic container 13. The low-stage compression element 20a and the high-stage compression element 20b are driven by the crankshaft 2 and compress the gas refrigerant that is the working fluid.

  The crankshaft 2 connected to the electric motor 14 includes a low-stage eccentric portion 5a and a high-stage eccentric portion 5b, and is supported by the main bearing 9 and the auxiliary bearing 19a. The main bearing 9 is installed on the upper side of the high stage eccentric part 5b, and the auxiliary bearing 19a is installed on the lower side of the low stage eccentric part 5a.

  Each compression element 20a and 20b is configured as shown in FIGS. The low-stage compression element 20a includes a low-stage cylinder 10a, a low-stage roller 11a disposed in the low-stage cylinder 10a and driven to rotate by the low-stage eccentric portion 5a, and the low-stage cylinder 10a and the high-stage cylinder 10b. And a partition plate 15 sandwiched between the low-stage cylinder 10a, a low-stage end plate 19b disposed on the side opposite to the partition plate, and a radially extending from the outer periphery of the low-stage roller 11a into the vane groove of the low-stage cylinder 10a. It has a low-stage compression chamber 23a composed of a low-stage vane 18a that is slidably fitted.

  A circular cylinder chamber is formed in the center of the low-stage cylinder 10a, and a low-stage suction passage 25a and a low-stage discharge port 42a are formed in a portion adjacent to the low-stage vane 18a on the inner peripheral surface forming the cylinder chamber. ing. The low stage suction passage 25a and the low stage discharge port 42a are disposed on both sides of the low stage vane 18a. The outer periphery of both side portions of the low-stage cylinder 10a is formed so as to coincide with the inner periphery of the sealed container. The center of the cylinder chamber of the low stage cylinder 10 a coincides with the rotation center 2 a of the crankshaft 2.

  The partition plate 15 is shared by the low-stage compression element 20a and the high-stage compression element 20b.

  The low-stage vane 18a is formed separately from the low-stage roller 11a in a flat plate shape, and moves forward and backward while always in contact with the outer peripheral surface of the low-stage roller 11a that rotates eccentrically with the rotation of the low-stage eccentric part 5a. Further, an applying force is applied from the back by an urging force applying means such as a coil spring, and the low-stage compression chamber 23a is divided into a compression space and a suction space.

  The auxiliary bearing 19a, the low stage end plate 19b, and the outer wall portion 19c constituting the intermediate container 19 are formed of the same member. An intermediate discharge space 33 is configured by closing the lower surface opening of the concave space formed by the intermediate container 19 with a cover 35. In the present embodiment, the low-stage end plate 19b is fixed by the bolt 36 as a fastening element, but may be fixed to the trunk portion 22 by welding.

  The low-stage end plate 19b is formed with a low-stage discharge port 26a communicating with the low-stage discharge port 42a of the low-stage compression chamber 23a. The low-stage discharge port 26a has a low-stage opening that opens at a predetermined intermediate pressure Pm. A discharge valve 28a is installed. The gas refrigerant compressed in the low-stage compression chamber 23a is discharged from the low-stage discharge port 42a through the low-stage discharge port 26a, through the low-stage discharge valve 28a, and into the intermediate discharge space 33. As shown in FIG. 4, the low-stage discharge valve 28a is sandwiched between low-stage end plates 19b and a low-stage retainer 43a and fastened by a low-stage rivet 44a or a bolt (not shown). The movable range of the valve 28a is suppressed by the low stage lift amount H1 of the low stage retainer 43a.

  The low stage lift amount H1 is a distance from the low stage discharge valve 28a to the center line of the low stage discharge port 26a hitting the low stage retainer 43a (the same applies to the high stage lift amount H2 described later).

  The high-stage compression element 20b includes a high-stage cylinder 10b, a high-stage roller 11b disposed in the high-stage cylinder 10b and driven to rotate by the high-stage eccentric portion 5b, a partition plate 15, and an anti-partition of the high-stage cylinder 10b. A high-stage end plate 9a disposed on the plate side and a high-stage vane 18b extending in a radial direction from the outer periphery of the high-stage roller 11b and slidably fitted in a vane groove of the high-stage cylinder 10b are configured. A high-stage compression chamber 23b.

  A circular cylinder chamber is formed in the center of the high-stage cylinder 10b, and a high-stage discharge port 42b is formed in a portion close to the high-stage vane 18b on the inner peripheral surface forming the cylinder chamber, and a remote part A high-stage suction passage 25b is formed at the top. The high stage suction passage 25b and the high stage discharge port 42b are arranged on both sides of the high stage vane 18b. The outer periphery of both side portions of the high-stage cylinder 10b is formed so as to coincide with the inner peripheral surface of the sealed container. The center of the cylinder chamber of the high stage cylinder 10b coincides with the rotation center 2a of the crankshaft 2. The cylinder chamber of the low-stage cylinder 10a and the cylinder chamber of the high-stage cylinder 10b have the same radial dimension and different dimensions in the height direction (axial direction). The height dimension of the cylinder chamber of the low stage cylinder 10a is larger than the height dimension of the cylinder chamber of the high stage cylinder 10b.

  The high-stage end plate 9 a is formed integrally with the main bearing 9. The high stage end plate 9a and the main bearing 9 are composed of the same member. The high-stage end plate 9 a is fixed to the inner wall of the body portion 22 by welding and supports the main bearing 9. The low stage end plate 19b is supported by the auxiliary bearing 19a.

  The high-stage vane 18b is formed separately from the high-stage roller 11b in a flat plate shape, and moves forward and backward while always abutting on the outer peripheral surface of the high-stage roller 11b that rotates eccentrically with the rotation of the high-stage eccentric part 5b. An application force is applied from the back by an urging force application means such as a coil spring, and the high-stage compression chamber 23b is divided into a compression space and a suction space.

  The high stage end plate 9a is formed with a high stage discharge port 26b communicating with the high stage discharge port 42b of the high stage compression chamber 23b. The shape of the high stage discharge port 26b is the same as that of the low stage discharge port 26a. That is, the cross-sectional area and length are the same. A high-stage discharge valve 28b that opens at a predetermined discharge pressure Pd is installed on the discharge side of the high-stage discharge port 26b. As shown in FIG. 6, the high-stage discharge valve 28b is sandwiched between the high-stage end plate 9a and the high-stage retainer 43b and fastened by a high-stage rivet 44b or a bolt (not shown). The movable range of the valve 28b is suppressed by the high stage lift amount H2 of the high stage retainer 43b.

  The gas refrigerant compressed in the high stage compression chamber 23b is discharged from the high stage retainer 43b through the high stage discharge port 26b, through the high stage discharge valve 28b, and into the sealed container 13. The outer peripheries of both side portions of the high stage end plate 9a are formed and fixed so as to coincide with the inner perimeter of the sealed container.

  The cover 35, the low-stage end plate 19b, the low-stage cylinder 10a, the partition plate 15, the high-stage cylinder 10b, and the high-stage end plate 9a are stacked in this order from the bottom, and the vane groove of the low-stage cylinder 10a The planar angular position (angular position in the rotational direction of the crankshaft 2) with the vane groove of the high-stage cylinder 10b is the same, and is fastened integrally through a bolt 36 from below the cover 35.

  The compression elements 20a and 20b drive the rollers 11a and 11b as the eccentric portions 5 rotate eccentrically. As shown in FIGS. 1 and 2, the low-stage eccentric portion 5a and the high-stage eccentric portion 5b have a phase difference of 180 °, and the phase difference in the compression process of the compression elements 20a and 20b is 180 °. That is, the compression process of the two compression elements is in opposite phase.

  Next, the compression operation of the compressor will be described with reference to FIGS. The arrows in FIGS. 1 and 2 indicate the flow of the gas refrigerant.

  The low-pressure Ps gas refrigerant supplied through the pipe 31 is sucked into the low-stage compression chamber 23a from the low-stage suction passage 25a connected to the pipe 31, and the low-stage roller 11a rotates eccentrically to the intermediate pressure Pm. Compressed. When the pressure in the low-stage compression chamber 23a reaches the intermediate pressure Pm, the low-stage discharge valve 28a opens, and the gas refrigerant that has reached the intermediate pressure Pm is discharged into the intermediate discharge space 33 that communicates with the low-stage discharge port 26a.

  The intermediate discharge space 33 is a space isolated from the sealed space 29 in the sealed container 13 by the intermediate container 19 and the cover 35, and the internal pressure thereof is basically the intermediate pressure Pm. The gas refrigerant having the intermediate pressure Pm discharged from the low-stage discharge port 26a is discharged to the intermediate discharge space 33, and then communicates with the high-stage compression chamber 23b of the high-stage compression element 20b through the intermediate flow path 30. It reaches the suction passage 25b. The intermediate flow path 30 is a flow path that connects the discharge port 26c from the intermediate discharge space 33 and the high-stage suction passage 25b.

  Next, the gas refrigerant having the intermediate pressure Pm passing through the intermediate flow path 30 and sucked into the high-stage compression element 20b from the high-stage suction passage 25b is compressed to the high pressure Pd by the revolution of the high-stage roller 11b. .

  The intermediate-pressure Pm gas refrigerant sucked into the high-stage compression chamber 23b is compressed to a predetermined high pressure Pd when the high-stage roller 11b revolves. When the pressure in the high-stage compression chamber 23b becomes high pressure Pd, the high-stage discharge valve 28b is opened, and the gas refrigerant is discharged from the high-stage discharge port 26b to the sealed space 29 that is the internal space of the sealed container 13. The gas refrigerant discharged into the sealed space 29 passes through the gap of the electric motor 14 and is discharged from the discharge pipe 27.

  As described above, according to the two-stage compressor 1 that sequentially compresses in stages with the two compression elements 20, the pressure ratio (Pm / Ps) or (Pd / Pm) of each compression element 20 is compressed in one stage. It becomes smaller than the pressure ratio (Pd / Ps) of the single stage compressor. Therefore, the re-expansion loss of the refrigerant depending on the pressure ratio and the leakage loss of the refrigerant can be reduced, and the compressor efficiency can be improved.

  The structure of the discharge valve and the retainer will be described with reference to FIGS.

  The low-stage discharge valve 28a is sandwiched between the low-stage end plate 19b and the low-stage retainer 43a and fastened by a low-stage rivet 44a or a bolt. The movable range of the low-stage discharge valve is the low-stage lift of the low-stage retainer 43a. Determined by the quantity H1.

  Generally, when the low stage lift amount H1 is small with respect to the gas flow rate, the flow path resistance at the time of gas discharge increases, causing pressure loss, and when the low stage lift amount H1 is large, the valve closing delay after gas discharge is large. As a result, leakage loss occurs. Thus, the optimum value of the discharge valve lift amount varies depending on the gas flow rate.

  Whether the low stage lift amount H1 is large or small is determined as follows. A figure V as if a cylinder was cut in the middle is shown in FIG. In this case, the low-stage discharge port 26a is virtually extended and cut at the intersection of the center line of the low-stage discharge port 26a and the low-stage retainer 43a. The upper part is defined as such, while the lower part is defined by the low stage discharge valve 28a. When the side area of this figure V is S1, and the cross-sectional area of the low stage discharge port 26a (perpendicular to the flow) is S2, it is considered that the flow resistance does not change if S1 = S2, and if S1> S2, the flow is If the path resistance decreases and S1 <S2, it is considered that the channel resistance has increased. Therefore, the low stage retainer 43a plays a role of regulating the amount of refrigerant discharged from the low stage compression element via the low stage discharge port.

  The same applies to the high stage.

  The compressor 1 is used for a general air conditioner or the like. The gas discharged from the high-stage compression element 20b and the gas discharged from the low-stage compression element 20a have different flow rates due to the difference in density. That is, the discharge gas of the low-stage compression element 20a has a higher flow rate than the discharge gas of the high-stage compression element 20b. This is the case when there is no refrigerant inflow or outflow in the middle of the compressor as shown in FIG.

  Thus, in the rotary type two-stage compressor, since the gas flow rates discharged from the high-stage compression element 20b and the low-stage compression element 20a are different, the lift amount of the low-stage retainer 43a is H1, and the high-stage retainer is When the lift amount H2 is 43b, H1> H2.

  With the above configuration, the compressor of the present embodiment can reduce pressure loss and leakage loss during gas discharge.

  Next, the case where this compressor is applied to an air conditioner will be described with reference to FIG. FIG. 7 is a configuration diagram of a refrigeration cycle showing an embodiment of the present invention. Injection is performed between the low and high stages.

  The high-pressure Pd refrigerant gas discharged from the rotary two-stage compressor 1 of the present embodiment is condensed by the condenser 3 and then expanded by the first expansion mechanism 4 to reduce the pressure to the intermediate pressure Pm. The decompressed refrigerant gas is separated into a gas refrigerant and a liquid refrigerant by the gas-liquid separator 6. The separated liquid refrigerant is further depressurized to a low pressure Ps by the second expansion mechanism 4 downstream of the gas-liquid separator 6 and then evaporated by the evaporator 16 to become a gas refrigerant. The low-pressure Ps gas refrigerant is sucked into the low-stage compression element 20a from the pipe 31 and the low-stage suction passage 25a, and the low-stage roller 11a fitted in the low-stage eccentric portion 5a revolves and is compressed to the intermediate pressure Pm. It is discharged to the intermediate flow path 30.

  The gas refrigerant in the intermediate flow path 30 is mixed with the gas refrigerant having an intermediate pressure Pm guided from the injection flow path 17 in which the gas-liquid separator 6 and the intermediate flow path 30 communicate with each other. Thereafter, the intermediate pressure Pm gas refrigerant sucked into the high-stage compression element 20b from the high-stage suction passage 25b is compressed to the high pressure Pd by the revolution of the high-stage roller 11b fitted in the high-stage eccentric portion 5b. , Discharged from the discharge pipe 27.

  In such an injection cycle, the gas refrigerant having low heat transfer performance is bypassed to the intermediate flow path 30 in the evaporator 16, so that the extra circulation flow to the low-stage compression element 20 a is reduced to reduce the compression work, and the refrigeration Improve cycle coefficient of performance COP. Further, a two-way valve 34 for opening and closing the injection flow path 17 is provided in the middle of the injection flow path 17. When the two-way valve 34 is opened, an injection cycle is established, and when the two-way valve 34 is closed, the normal refrigeration cycle shown in FIG. It is good also as a structure which can be switched. Further, instead of the two-way valve 34, an expansion valve capable of adjusting the flow rate may be used.

  In a refrigeration cycle of a general air conditioner to which this embodiment is not applied, the discharge gas of the low-stage compression element 20a is more than the discharge gas of the high-stage compression element 20b as described in the first embodiment. The flow rate is high. However, in the gas injection cycle shown in FIG. 7, the refrigerant flows into the intermediate flow path 30 from the injection flow path 17, whereby the refrigerant is increased in the high-stage compression element 20 b. Therefore, the gas flow rate discharged from the high stage compression element 20b increases. That is, in the gas injection cycle, although the cycle efficiency is ideally improved, pressure loss at the time of gas discharge in the high stage compression element 20b and leakage loss due to valve closing delay are likely to occur. Therefore, the rotary type two-stage compressor of the present embodiment adjusts the flow rate such that H1 <H2 when the lift amount of the low stage retainer 43a is H1 and the lift amount H2 of the high stage retainer 43b.

  In such a gas injection cycle, when the rotary type two-stage compressor 1 of the present embodiment is used, H1 <H2, and therefore pressure loss and leakage loss associated with an increase in gas flow rate of the high-stage compression element 20b can be reduced. The effect is more remarkable in the gas injection cycle than in the normal refrigeration cycle. Therefore, the refrigeration cycle of the present embodiment can realize a gas injection cycle that is closer to the ideal, and can improve the cycle efficiency of the refrigeration cycle.

  When trying to adjust the flow rate with the discharge port diameter as in the prior art, increasing the discharge port diameter will increase the dead volume and reduce the compressor efficiency. However, according to the above, when the lift amount of the low stage retainer is H1 and the lift amount H2 of the high stage retainer, a compressor of “H1> H2” is manufactured according to the presence or absence of injection, or “H1 By producing a compressor of <H2 ”, it is possible to provide a rotary two-stage compressor that reduces pressure loss during gas discharge and leakage loss due to improved valve closing delay, and improves compressor efficiency. it can.

  Conventionally, it has been necessary to change the machining shapes of the low and high cylinders. In other words, there is a possibility that a change in the machining process occurs, the setup time increases, and a machining defect may occur. However, according to this embodiment, only the parts are changed at the time of product assembly according to the application. This makes it possible to manage production easily and in a timely manner.

1 is a longitudinal sectional view of a rotary two-stage compressor showing an embodiment of the present invention. 1 is a configuration diagram of a rotary two-stage compressor showing an embodiment of the present invention. XX arrow sectional drawing of FIG. AA arrow sectional drawing of FIG. The YY arrow sectional drawing of FIG. BB arrow sectional drawing of FIG. The block diagram of the refrigerating cycle which shows one Embodiment of this invention. The figure for demonstrating flow-path resistance.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 2 Crankshaft 2a Center of rotation 3 Condenser 4 Expansion mechanism 5 Eccentric part 5a Low stage eccentric part 5b High stage eccentric part 6 Gas-liquid separator 9 Main bearing 9a High stage end plate 10a Low stage cylinder 10b High stage cylinder 11a Low stage roller 11b High stage roller 13 Sealed container 14 Motor 15 Partition plate 16 Evaporator 17 Injection flow path 18a Low stage vane 18b High stage vane 19 Intermediate container 19a Sub bearing 19b Low stage end plate 19c Outer wall part 20a Low stage compression element 20b High stage compression element 23a Low stage compression chamber 23b High stage compression chamber 25a Low stage suction passage 25b High stage suction passage 26a Low stage discharge port 26b High stage discharge port 26c Discharge port 27 Discharge pipe 28a Low stage discharge valve 28b High stage discharge Valve 30 Intermediate flow path 31 Pipe 33 Intermediate discharge space 34 Two-way valve 35 Cover 36 Bolt 42a Low stage discharge port 42b High stage discharge port 43a Low stage retainer 43b High stage retainer 44a Low stage rivet 44b High stage rivet

Claims (6)

A rotary two-stage compressor that compresses refrigerant with a low-stage compression element that is a first compression element and compresses the refrigerant with a high-stage compression element that is a second compression element,
A low-stage retainer that regulates the amount of refrigerant discharged from the low-stage compression element through a low-stage discharge port;
A high stage retainer that regulates the amount of refrigerant discharged from the high stage compression element through a high stage discharge port;
The shape of the low stage outlet and the shape of the high stage outlet are the same,
When the lift amount of the low stage retainer is H1, the lift amount of the high stage retainer is H2,
H1> H2
A rotary two-stage compressor characterized by the above. A rotary two-stage compressor used in an air conditioner having an injection flow path for returning a refrigerant between a low-stage compression element and a high-stage compression element of a rotary two-stage compressor,
A low-stage retainer that regulates the amount of refrigerant discharged from the low-stage compression element through a low-stage discharge port;
A high stage retainer that regulates the amount of refrigerant discharged from the high stage compression element through a high stage discharge port;
The shape of the low stage outlet and the shape of the high stage outlet are the same,
When the lift amount of the low stage retainer is H1, the lift amount of the high stage retainer is H2,
H1 <H2
A rotary two-stage compressor characterized by the above. In an airtight container, an electric motor, a crankshaft driven by the electric motor, and a compression mechanism portion driven by the crankshaft and including a low-stage compression element and a high-stage compression element are housed,
The crankshaft has a low stage eccentric part and a high stage eccentric part,
The low-stage compression element is sandwiched between a low-stage cylinder, a low-stage roller disposed in the low-stage cylinder and driven to rotate by the low-stage eccentric portion, and the low-stage cylinder and the high-stage cylinder. A partition plate, a low-stage end plate disposed on a side opposite to the partition plate of the low-stage cylinder, provided with a low-stage discharge valve and a low-stage retainer, and an outer periphery of the low-stage roller to contact the low-stage cylinder. Forming a low-stage compression chamber composed of a low-stage vane slidably fitted in the vane groove;
The high-stage compression element includes the high-stage cylinder, a high-stage roller disposed in the high-stage cylinder and driven to rotate by the high-stage eccentric portion, the partition plate, and an anti-partition plate of the high-stage cylinder. A high stage end plate provided with a high stage discharge valve and a high stage retainer, and a high stage slidably fitted in the vane groove of the high stage cylinder in contact with the outer periphery of the high stage roller A rotary type two-stage compressor formed with a high-stage compression chamber composed of a stage vane,
A rotary two-stage compressor, wherein H1 is not equal to H2, where the lift amount of the low stage retainer is H1, and the lift amount of the high stage retainer is H2.   4. The rotary two-stage compressor according to claim 3, wherein when the lift amount of the low stage retainer is H1, and the lift amount H2 of the high stage retainer is H1,> H2. Compressor. A compressor, a first heat exchanger, a first expansion mechanism, a gas-liquid separator, a second expansion mechanism, and a second heat exchanger, which are sequentially connected, and In an air conditioner having a refrigeration cycle configured to be connected to the compressor from a second heat exchanger,
The compressor is
A rotary two-stage compressor that compresses refrigerant with a low-stage compression element that is a first compression element and compresses the refrigerant with a high-stage compression element that is a second compression element,
A low-stage retainer that regulates the amount of refrigerant discharged from the low-stage compression element through a low-stage discharge port;
A high stage retainer that regulates the amount of refrigerant discharged from the high stage compression element through a high stage discharge port;
A flow path that connects the gas-liquid separator and the low-stage compression element and the high-stage compression element, and sends a gaseous refrigerant from the gas-liquid separator to the high-stage compression element An injection flow path capable of
The shape of the low stage outlet and the shape of the high stage outlet are the same,
When the lift amount of the low stage retainer is H1, the lift amount of the high stage retainer is H2,
H1 <H2
Air conditioner characterized by that. A rotary compressor, a condenser for condensing the high-pressure gas refrigerant discharged from the rotary compressor, a first expansion mechanism for expanding the condensed liquid refrigerant to an intermediate pressure, and an expanded intermediate pressure In an air conditioner that sequentially connects a second expansion mechanism that expands a refrigerant to a low pressure and an evaporator that evaporates the refrigerant, the rotary compressor is driven by the electric motor and the electric motor in a sealed container. A crankshaft and a compression mechanism that is driven by the crankshaft and includes a low-stage compression element and a high-stage compression element;
The crankshaft has a low stage eccentric part and a high stage eccentric part,
The low-stage compression element is sandwiched between a low-stage cylinder, a low-stage roller disposed in the low-stage cylinder and driven to rotate by the low-stage eccentric portion, and the low-stage cylinder and the high-stage cylinder. A partition plate, a low-stage end plate disposed on a side opposite to the partition plate of the low-stage cylinder, provided with a low-stage discharge valve and a low-stage retainer, and an outer periphery of the low-stage roller to contact the low-stage cylinder. Forming a low-stage compression chamber composed of a low-stage vane slidably fitted in the vane groove,
The high-stage compression element includes the high-stage cylinder, a high-stage roller disposed in the high-stage cylinder and driven to rotate by the high-stage eccentric portion, the partition plate, and an anti-partition plate of the high-stage cylinder. A high stage end plate provided with a high stage discharge valve and a high stage retainer, and a high stage slidably fitted in the vane groove of the high stage cylinder in contact with the outer periphery of the high stage roller Forming a high stage compression chamber composed of a stage vane,
A rotary type two-stage compressor comprising an intermediate flow path between the low-stage compression element and the high-stage compression element,
When the lift amount of the low stage retainer is H1, and the lift amount H2 of the high stage retainer is H1 <H2,
An air conditioner comprising a gas-liquid separator that separates a refrigerant into a gas refrigerant and a liquid refrigerant downstream of the first expansion mechanism, and an injection flow path that communicates the gas-liquid separator and the intermediate flow path. .

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