WO2014156743A1

WO2014156743A1 - Scroll compressor and refrigeration cycle device comprising same

Info

Publication number: WO2014156743A1
Application number: PCT/JP2014/057035
Authority: WO
Inventors: 角田　昌之; 昌晃須川; 石園　文彦; 政則伊藤; 修平小山; 浩平達脇; 哲仁 ▲高▼井; 増本　浩二
Original assignee: 三菱電機株式会社
Priority date: 2013-03-28
Filing date: 2014-03-17
Publication date: 2014-10-02
Also published as: JP6038287B2; CN105121855B; CN105121855A; JPWO2014156743A1

Abstract

A scroll compressor has an injection pipe (27) that is provided across the interior and exterior of a sealed container (21) and is used to supply a refrigerant to a compression chamber (A), and a power mechanism (139) that is accommodated in the sealed container and oscillates an orbiting scroll (12). The portion of the injection pipe inside the sealed container is provided on the side opposite, with the orbiting scroll and a fixed scroll (11) as the boundary, to the side where the power mechanism is provided, and one end of the fixed scroll communicates with the injection pipe, and the other end has an injection port (11e) that communicates with the compression chamber.

Description

Scroll compressor and refrigeration cycle apparatus including the same

The present invention relates to a scroll compressor and a refrigeration cycle apparatus including the scroll compressor.

When R32 having a low global warming potential GWP as the refrigerant is enclosed in the refrigerant circuit of the refrigeration cycle apparatus, the discharge gas temperature of the compressor is, for example, about 20 deg higher than that when the conventional R22, R410A or the like is used. Become. As a result, there may be a problem that the insulating material of the electric motor used in the hermetic compressor, the refrigeration oil, and the like are deteriorated. Here, the refrigerant having a low global warming potential GWP other than R32 includes a mixed refrigerant of HFO-1123 and R32 or a mixed refrigerant of HFO-1123 and HFO-1234yf. However, HFO-1123 has properties such as a low environmental load, but may cause a rapid decomposition reaction under high temperature and high pressure (disproportionation reaction). For this reason, when using the mixed refrigerant mentioned above, it is necessary to suppress the discharge gas temperature of a compressor.

In addition, since the R32 refrigerant is flammable, it is necessary to suppress the amount of refrigerant charged in the circuit constituting the refrigeration cycle in order to prevent leakage and ignition, and the pressure in the sealed container during operation of the compressor is reduced. It is desirable to use a low-pressure shell type compressor that has a low pressure.

Here, a refrigeration apparatus having a refrigeration cycle having a compressor, a condenser, a main decompression unit, and an evaporator, which are connected by refrigerant piping, provided between the condenser and the main decompression unit The subcooling heat exchanger, the supercooling pressure reducing means provided on the upstream side of the supercooling heat exchanger, and the refrigerant cooled by the supercooling heat exchanger is supplied to the compressor bypassing the evaporator The thing which has bypass piping to do is proposed (for example, refer to patent documents 1).
In the technique described in Patent Document 1, in order to suppress the temperature of the gas refrigerant discharged from the compressor while using the refrigerant containing the R32 refrigerant, the gas that has been condensed by the condenser and then decompressed by the main decompression means and passed through the evaporator The refrigerant and the refrigerant cooled by the supercooling heat exchanger are combined via a bypass pipe and then supplied to the suction side of the compressor.

JP 2001-227823 A (see, for example, FIG. 1)

When the technique described in Patent Document 1 uses a low-pressure shell type compressor from the viewpoint of the flammability of the R32 refrigerant, the bypass refrigerant supplied from the bypass pipe merges with the refrigerant flowing out of the evaporator. Thus, the specific enthalpy of the refrigerant is reduced to the two-phase state. And the refrigerant | coolant with which specific enthalpy fell is suck | inhaled in the airtight container of a compressor, Then, it is taken in into the compression mechanism part which compresses a refrigerant | coolant, and compression of a refrigerant | coolant is performed.

That is, in the technique described in Patent Document 1, the temperature of the gas refrigerant discharged from the compressor can be suppressed. However, since the bypass refrigerant that has flowed through the bypass pipe and joined flows into the compression mechanism part, the compression mechanism part There is a problem that the refrigerant is diluted at a stage before the refrigerant is supplied. In addition, if a refrigerant | coolant is diluted in the step before a refrigerant | coolant is supplied to a compression mechanism part, the refrigeration oil in a refrigerant | coolant will also be diluted. As a result, for example, it becomes difficult to reduce the friction of the sliding portion between the orbiting scroll and the frame that slidably supports it, which may lead to damage to the compressor.

In view of this, a method of joining (injecting) the bypass refrigerant after the refrigerant has been taken into the compression mechanism section is conceivable so that the refrigerant is not diluted before being supplied to the compression mechanism section. That is, a bypass pipe (injection pipe) for supplying a bypass refrigerant is connected to the compression mechanism section, and the bypass refrigerant is merged with the refrigerant after passing the sliding section.
However, even with this method, heat is transferred to the injection pipe from the heat generating element such as the electric motor and the sliding portion described above in the sealed container between the outside of the sealed container and the compression chamber. There is a problem that the cooling effect of the bypass refrigerant is reduced and it is difficult to lower the temperature of the gas refrigerant discharged from the compressor.
Further, when a mixed refrigerant of HFO-1123 and R32 or a mixed refrigerant of HFO-1123 and HFO-1234yf is adopted as the refrigerant, if the temperature of the gas refrigerant discharged from the compressor is difficult to lower, The possibility that a disproportionation reaction will occur becomes high.

The present invention has been made to solve the above-described problems, and provides a scroll compressor and a refrigeration cycle apparatus including the scroll compressor that suppress the refrigerant temperature discharged from the compressor from becoming difficult to decrease. It is an object.

A scroll compressor according to the present invention includes a hermetic container, a swinging scroll accommodated in the hermetic container, in which a first spiral body is formed, and fixed to the inner peripheral surface of the hermetic container. A second scroll body to be compressed is formed, a fixed scroll that forms a compression chamber with the swing scroll, and an injection pipe that is provided across the inside and outside of the sealed container and is used to supply a refrigerant to the compression chamber And a rotating shaft for swinging the swing scroll, one end of which is connected to the side of the swing scroll opposite to the side on which the fixed scroll is provided, and the sealed container. The other end of the rotating shaft is connected, and a power mechanism for rotating the rotating shaft, and the injection pipe has a power mechanism with a portion in the hermetic container at the boundary of the swing scroll and the fixed scroll. Provided to the provided side located opposite the fixed scroll is one in which one is through injection pipe and communicating, with the injection port and the other communicates with the compression chamber.

Since the scroll compressor according to the present invention has the above-described configuration, it is possible to suppress the temperature of the refrigerant discharged from the compressor from being easily lowered.

It is a schematic longitudinal cross-sectional view of the scroll compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing of a fixed spiral body and a rocking | swirling spiral body shown in FIG. 1, a discharge port, and an injection port. It is the example of a structure of the refrigerating-cycle apparatus provided with the scroll compressor shown in FIG. 1, and the Mollier diagram of this refrigerating-cycle apparatus. It is a schematic longitudinal cross-sectional view of the scroll compressor which concerns on Embodiment 2 of this invention. It is explanatory drawing of a fixed spiral body and a rocking | swirling spiral body shown in FIG. 1, a discharge port, an injection port, and a sub discharge port. It is a schematic diagram explaining the operation | movement at the time of the intermediate | middle cooling operation of the scroll compressor which concerns on Embodiment 2 of this invention. It is the example of a structure of the refrigerating-cycle apparatus provided with the scroll compressor shown in FIG. 4, and the Mollier diagram of this refrigerating-cycle apparatus. The Mollier diagram of FIG.7 (c) is simplified for description of a compression process.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a schematic longitudinal sectional view of a scroll compressor 1 according to the first embodiment. FIG. 2 is an explanatory diagram of the fixed spiral body 11b and the swinging spiral body 12b, the discharge port 11c, and the injection port 11e shown in FIG. The configuration of the scroll compressor 1 will be described with reference to FIGS. 1 and 2.
The scroll compressor 1 according to Embodiment 1 is provided with an improvement for suppressing the temperature of the refrigerant discharged from the scroll compressor 1 from becoming difficult to decrease.

[Configuration of scroll compressor 1]
The scroll compressor 1 supplies an airtight container 21 constituting an outer shell, a suction pipe 23 that guides the refrigerant to the airtight container 21, a discharge pipe 24 that discharges the compressed refrigerant, and a cooled refrigerant in the airtight container 21. The injection pipe 27 used for the above, the subframe 110 that partitions the space in the sealed container 21, the bottom oil reservoir 22 that stores the refrigerating machine oil, and the fixed spiral body 11b that compresses the refrigerant are formed. The scroll 11 has a discharge pipe connecting portion 50 provided on the upper end surface of the fixed scroll 11 and connected to the discharge pipe 24.
In addition, the scroll compressor 1 rotates the orbiting scroll 12 formed with the orbiting spiral body 12b used to compress the refrigerant, the frame 14 that accommodates the orbiting scroll 12, and the orbiting scroll 12. The shaft 15 includes an oil pump 91 that pulls up the refrigerating machine oil, an electric motor 139 that rotates the shaft 15, and an Oldham ring 13 that swings the swing scroll 12.
Further, the scroll compressor 1 includes a compression chamber A formed by the fixed spiral body 11 b of the fixed scroll 11 and the swing spiral body 12 b of the swing scroll 12, the inner surface of the frame 14, the fixed scroll 11 and the swing scroll 12. And a suction chamber B that communicates with the compression chamber A.

(Sealed container 21)
The hermetic container 21 constitutes an outline of the scroll compressor 1. In the sealed container 21, a fixed scroll 11, a swing scroll 12, a frame 14, a shaft 15, an electric motor 139, an Oldham ring 13, and the like are provided.
A suction pipe 23 communicating with the inside of the sealed container 21 is connected to the side surface of the sealed container 21. Further, a discharge pipe 24 communicating with the innermost compression chamber A and an injection pipe 27 used for supplying the refrigerant to the compression chamber A are connected to the upper portion of the sealed container 21.

(Suction pipe 23 and discharge pipe 24)
The suction pipe 23 is a pipe for guiding the refrigerant flowing into the scroll compressor 1 into the sealed container 21. The suction pipe 23 is provided on the side surface of the sealed container 21 so as to communicate with the inside of the sealed container 21.
The discharge pipe 24 is a pipe for discharging the refrigerant compressed by the scroll compressor 1. The discharge pipe 24 penetrates the sealed container 21 and is connected to the discharge pipe connecting portion 50 at one end side. That is, the discharge pipe 24 is provided over the inside and outside of the sealed container 21, and one end side is connected to the discharge pipe connecting portion 50 and communicates with the compression chamber A.
As shown in FIG. 1, the portion of the discharge pipe 24 provided in the sealed container 21 is provided so as to extend in the vertical direction in the same manner as the injection pipe 27.

(Injection piping 27)
The injection pipe 27 is a pipe used to supply a refrigerant to the compression chamber A in the middle of the compression process formed between the fixed scroll 11 and the swing scroll 12 provided in the sealed container 21. The injection pipe 27 penetrates the sealed container 21 and is connected to the discharge pipe connection part 50 at one end side. That is, the injection pipe 27 is provided across the inside and outside of the sealed container 21, and one end side is connected to the discharge pipe connecting part 50 and communicates with the compression chamber A.

The portion of the injection pipe 27 provided in the sealed container 21 is provided so as to extend in parallel in the vertical direction, as shown in FIG. That is, the injection pipe 27 is provided so that the portion in the sealed container 21 is located on the opposite side to the side where the electric motor 139 as a power mechanism is provided, with the swing scroll 12 and the fixed scroll 11 as a boundary. It has been. For this reason, the frictional heat generated on the sliding surface between the orbiting scroll 12 and the frame 14 and the heat generated by the current supplied to the electric motor 139 are not easily transmitted to the injection pipe 27, and flow through the injection pipe 27. It is possible to suppress the refrigerant from being heated.

(Subframe 110)
The sub frame 110 is provided so as to partition the space in the sealed container 21, and is provided with a sub bearing 20 that rotatably supports the lower end side of the shaft 15. A bottom oil reservoir 22 is provided below the subframe 110, and an electric motor 139 is provided above the subframe 110.

(Bottom oil reservoir 22)
The bottom oil reservoir 22 stores refrigerating machine oil. The bottom oil reservoir 22 is provided below the subframe 110.
The refrigerating machine oil stored in the bottom oil reservoir 22 is swung through a refrigerating machine oil passage (not shown) formed in the shaft 15 by an oil pump 91 provided at the lower end of the shaft 15. It can be pulled up to 12 side.

(Fixed scroll 11)
The fixed scroll 11 compresses the refrigerant together with the swing scroll 12. The fixed scroll 11 is disposed opposite to the swing scroll 12. The fixed scroll 11 includes a base plate 11a that is substantially parallel to the horizontal plane, and a fixed spiral body 11b that protrudes downward from the lower surface of the base plate 11a.

The base plate 11 a constitutes the compression chamber A and the suction chamber B together with the fixed spiral body 11 b, the swing scroll 12 and the frame 14. The base plate 11 a is substantially parallel to the horizontal plane, and the outer peripheral surface thereof faces the inner peripheral surface of the sealed container 21, and the outer side of the lower end surface of the base plate 11 a faces the upper portion of the frame 14. Further, it is fixed in the sealed container 21.

The base plate 11a is a flat plate-like member, and at the center thereof, a discharge port 11c from which the refrigerant compressed in the compression chamber A is discharged, a concave portion 11d communicating with the discharge port 11c, and the compression chamber A An injection port 11e for supplying a refrigerant is formed. The central portion of the base plate 11a corresponds to the central portion in the radial direction when the base plate 11a is viewed in a horizontal cross section.

The discharge port 11c is formed to extend in the vertical direction of the base plate 11a so that one communicates with the compression chamber A and the other communicates with the concave portion 11d. The diameter of the discharge port 11c is smaller than the diameter of the concave portion 11d, and the other of the discharge ports 11c is closed by a discharge valve 11f that opens the discharge port 11c when the pressure is higher than a preset pressure.
The concave portion 11d is formed to be concave from the upper side to the lower side, and a discharge valve 11f is provided at a connection position with the discharge port 11c. The concave portion 11d is formed on the base plate 11a so that one communicates with the discharge port 11c and the other communicates with a concave portion 50a of the discharge pipe connecting portion 50 described later.
The discharge valve 11f closes the discharge port 11c when the pressure is lower than a preset pressure, and restricts the flow of refrigerant from the compression chamber A side to the discharge pipe 24 side. However, when the pressure becomes equal to or higher than the preset pressure, the discharge port 11c. Is to release.

The injection port 11e is used to supply a refrigerant having a low specific enthalpy into the compression chamber A via the injection pipe 27 so that the temperature of the refrigerant in the compression chamber A can be lowered. is there.
The injection port 11e is formed outside the discharge port 11c and the recessed portion 11d in the radial direction when the base plate 11a is viewed in a horizontal section.
The injection port 11e is formed on the base plate 11a so that one communicates with the compression chamber A and the other communicates with a concave portion 50b of a discharge pipe connecting portion 50 described later.
As shown in FIG. 2, two injection ports 11e are formed with the discharge port 11c as a boundary. The formation position of one injection port 11e is a first compression chamber Aa described later, and the formation position of the other injection port 11e is a second compression chamber Ab described later.

The injection port 11 e is provided so as to extend in parallel with the top and bottom of the fixed scroll 11. If the injection port 11e is formed on the frame 14, the injection port 11e and the sliding surface are formed on the same member in addition to being closer to the sliding surface between the orbiting scroll 12 and the frame 14. The Rukoto.
However, since the injection port 11e is formed on the fixed scroll 11 in the first embodiment, the injection port 11e is far from the sliding surface and is a separate member from the frame 14 on which the sliding surface is formed. Thus, the frictional heat generated on the sliding surface is difficult to be transmitted to the refrigerant flowing through the injection port 11e.
The injection port 11e is provided so as to be located on the side opposite to the side on which the electric motor 139 as a power mechanism is provided with the swing scroll 12 as a boundary. For this reason, the heat etc. which arise with the electric current supplied to the electric motor 139 become difficult to be transmitted to the injection port 11e, and it can suppress that the refrigerant | coolant which flows through the injection port 11e is heated. Yes.

In the first embodiment, the discharge port 11c, the concave portion 11d, and the injection port 11e are described as being formed in parallel in the vertical direction. However, the discharge port 11c, the concave portion 11d, and the injection port 11e are not necessarily formed in parallel. It may be formed slightly deviated from the direction.
In the first embodiment, the horizontal cross-sectional shapes of the discharge port 11c, the concave portion 11d, and the injection port 11e are described as being circular, but are not limited thereto, and may be elliptical. However, it may be a polygon.
Furthermore, in the first embodiment, it has been described that two injection ports 11e are formed. However, the number is not limited to two, and may be one or three or more. If the number formed in the first compression chamber Aa described later and the number formed in the second compression chamber Ab are equal, the temperatures of both the refrigerant in the first compression chamber Aa and the refrigerant in the second compression chamber Ab are set. The temperature of the refrigerant discharged from the scroll compressor 1 can be efficiently reduced.

The fixed spiral body 11 b and the swing scroll body 12 b of the swing scroll 12 form a compression chamber A whose volume changes as the swing scroll 12 swings. The fixed spiral body 11 b constitutes the suction chamber B together with the frame 14 and the swing scroll 12. The fixed spiral body 11b has a horizontal cross section having a spiral shape, that is, an involute curve shape (see FIG. 2).

(Discharge pipe connection 50)
The discharge pipe connecting portion 50 is provided in contact with the upper end surface of the fixed scroll 11, and the discharge pipe 24 and the injection pipe 27 are connected to the discharge pipe connecting portion 50. The discharge pipe connecting part 50 is formed with a concave part 50a on the center side in the radial direction when viewed in a horizontal section, and a concave part 50b is formed outside the position where the concave part 50a is formed.
The concave portion 50a and the concave portion 50b are formed so as to be concave from the lower side toward the upper side. The upper end side of the concave portion 50 a is open, and the discharge pipe 24 is connected to communicate with the discharge pipe 24.
The concave portion 50b is a concave portion having a horizontal cross-sectional shape, for example, a donut shape. And the upper end side of the recessed part 50b is opened, and the injection piping 27 is connected and is connected with the injection piping 27. FIG. That is, the refrigerant supplied from the injection pipe 27 flows into the injection port 11e on the left side of FIG. 1 and flows into the injection port 11e on the right side of FIG.
Thus, the compression chamber A and the discharge pipe 24 communicate with each other through the discharge port 11c, the concave portion 11d, and the concave portion 50a.
Further, the injection pipe 27 and the compression chamber A communicate with each other via the concave portion 50b and the injection port 11e.

(Oscillating scroll 12)
The orbiting scroll 12 compresses the refrigerant together with the fixed scroll 11. The orbiting scroll 12 is disposed to face the fixed scroll 11. The swing scroll 12 includes a base plate 12a parallel to the horizontal plane, a swing spiral body 12b formed to protrude upward from the upper surface of the base plate 12a, and a boss portion 12c formed below the base plate 12a. And have.

The base plate 12 a constitutes the compression chamber A and the suction chamber B together with the swinging spiral body 12 b, the fixed scroll 11, and the frame 14. The base plate 12 a is a disk-shaped member, and swings within the frame 14 by the rotation of the shaft 15.
The base plate 12 a is provided to be supported by the frame 14 so as to swing on the frame 14. The base plate 12a swings on the frame 14 as the shaft 15 rotates.

The oscillating spiral body 12 b compresses the refrigerant together with the fixed spiral body 11 b of the fixed scroll 11. Further, the swinging spiral body 12 b constitutes the compression chamber A together with the base plate 12 a and the fixed scroll 11, and constitutes the suction chamber B together with the frame 14 and the fixed scroll 11. The oscillating spiral body 12b has a horizontal cross section having a spiral shape, that is, an involute curve shape so as to correspond to the fixed spiral body 11b (see FIG. 2).
The boss portion 12c is a hollow cylindrical member formed on the lower side of the base plate 12a. The upper end side of the shaft 15 is connected to the boss portion 12c. That is, the rocking scroll 12 is rotated by the rotation of the shaft 15 connected to the boss portion 12c.

(Frame 14)
The frame 14 accommodates the orbiting scroll 12 so that the orbiting scroll 12 can slide. That is, a sliding surface is formed by the upper surface of the frame 14 and the lower surface of the base plate 12 a of the swing scroll 12.
The frame 14 has a shape in which an upper part and a lower part are opened. The frame 14 is closed by providing a base plate 11 a of the fixed scroll 11 at the upper part of the frame 14, and a shaft 15 is inserted at the lower part of the frame 14.
The frame 14 has an outer peripheral surface facing the inner peripheral surface of the sealed container 21, and an inside of the sealed container 21 so that an outer upper portion thereof faces an outer side of the lower end surface of the base plate 11 a of the fixed scroll 11. It is fixed with.

(Axis 15)
The shaft 15 is provided with an eccentric portion 15 a connected to the boss portion 12 c of the swing scroll 12 and a first balancer 15 b that balances the swing motion of the swing scroll 12 at the upper end portion of the shaft 15. A refrigerating machine oil passage (not shown) for guiding refrigerating machine oil from the bottom oil reservoir 22 to the swing scroll 12 side is formed inside the shaft 15.
The eccentric portion 15 a is a portion formed by shifting a dimension set in advance in the horizontal direction with respect to the central axis of the shaft 15.
The first balancer 15 b is provided above the electric motor 139 of the shaft 15 and below the frame 14. The first balancer 15 b is used to suppress unbalance associated with the movement of the orbiting scroll 12 and the Oldham ring 13.

(Oil pump 91)
The oil pump 91 pulls the refrigerating machine oil from the bottom oil reservoir 22. The oil pump 91 is provided at the lower end of the shaft 15. The oil pump 91 may be a pump that generates a pump action (use of differential pressure) by the rotation of the shaft 15 such as a centrifugal pump or a positive displacement pump.

(Electric motor 139)
The electric motor 139 rotates the shaft 15. The electric motor 139 includes a stator 19 that is fixedly supported by the sealed container 21 and a rotor 18 that generates torque by being combined with the stator 19.
The electric motor 139 is provided so as to partition an upper space in which the swing scroll 12 and the fixed scroll 11 are provided and a lower space in which the bottom oil reservoir 22 is provided.
The stator 19 is configured, for example, by mounting a multiphase winding on a laminated iron core.
The rotor 18 has, for example, a permanent magnet (not shown) inside and is supported by the shaft 15 so that a preset gap is formed between the rotor 18 and the inner peripheral surface of the stator 19. The rotor 18 is rotationally driven when the stator 19 is energized to rotate the shaft 15. The rotor 18 is provided with a second balancer 18a that is used to suppress an imbalance associated with the movement of the orbiting scroll 12 and the Oldham ring 13.

(Oldham Ring 13)
The Oldham ring 13 is disposed below the lower surface of the base plate 12a of the orbiting scroll 12, and is used to prevent the rotation movement of the orbiting scroll 12 during the orbiting movement. That is, the Oldham ring 13 functions to prevent the swinging scroll 12 from rotating and to swing the swinging scroll 12.

(Compression chamber A)
The compression chamber A is formed by the lower surface of the base plate 11a and the fixed spiral body 11b, and the upper surface of the base plate 12a and the swinging spiral body 12b. The compression chamber A communicates with the suction chamber B. The compression chamber A includes a first compression chamber Aa and a second compression chamber Ab.
More specifically, the first compression chamber Aa is formed by the fixed spiral body side surface 11A, the swinging spiral body outer surface 12A, the lower surface of the base plate 11a, and the upper surface of the base plate 12a.
In the first compression chamber Aa, one of the injection ports 11e is formed. Here, the discharge port 11c side of the first compression chamber Aa is defined as the innermost chamber, the suction chamber B side of the first compression chamber Aa is defined as the first outermost chamber, and the innermost chamber and the first chamber The space between the first outermost chamber is defined as the first intermediate chamber. That is, in the state shown in FIG. 2, the first compression chamber Aa has a first outermost chamber, a first intermediate chamber, and an innermost chamber from the outside.
At this time, in the state shown in FIG. 2, it turns out that one injection port 11e is located in a 1st outermost chamber. That is, one injection port 11e is provided at a position about one turn along the inward surface side from the end of winding of the involute of the fixed scroll 11.

The second compression chamber Ab is formed by the fixed spiral body outer surface 11B, the swing spiral body side surface 12B, the lower surface of the base plate 11a, and the upper surface of the base plate 12a. In the second compression chamber Ab, the other of the injection ports 11e is formed. Here, the discharge port 11c side of the second compression chamber Ab is defined as the innermost chamber common to the first compression chamber Aa, and the suction chamber B side of the second compression chamber Ab is defined as the second outermost chamber. And a space between the innermost chamber and the second outermost chamber is defined as a second intermediate chamber. That is, in the state shown in FIG. 2, the second compression chamber Ab has a second outermost chamber, a second intermediate chamber, and an innermost chamber from the outside.
At this time, in the state shown in FIG. 2, it can be seen that the other injection port 11e is located in the second outermost chamber. In other words, the other injection port 11e is provided at a position about one round along the inward surface side from the end of the involute winding of the rocking scroll 12.

The formation position of the injection port 11e is not limited to the first outermost chamber of the first compression chamber Aa and the second outermost chamber of the second compression chamber Ab. You may set according to the winding number etc. of the spiral body 12b.

(Suction chamber B)
The suction chamber B is formed by the inner surface of the frame 14, the outer periphery of the base plate 12a, the fixed spiral body outer surface 11B, and the swing spiral body outer surface 12A. The suction chamber B communicates with the compression chamber A. Therefore, the refrigerant supplied to the frame 14 flows into the suction chamber B from the space below the frame 14 in the sealed container 21, and further, the refrigerant that flows into the suction chamber B flows into the compression chamber A. Become.

[Description of Operation of Scroll Compressor 1]
Here, the operation of the scroll compressor 1 will be briefly described.
In FIG. 1, when electric power is supplied to the stator 19, the rotor 18 generates torque, and the shaft 15 supported by the main bearing portion of the frame 14 and the auxiliary bearing 20 rotates.
Since the orbiting scroll 12 is connected to the eccentric portion 15a of the shaft 15 via the boss portion 12c, when the shaft 15 rotates, the orbiting scroll 12 also rotates. Since the rotation operation of the swing scroll 12 is restricted by the Oldham ring 13, the swing scroll 12 swings.
Thus, the volume of the compression chamber A is changed by the swing operation of the swing scroll 12.
As the swing scroll 12 swings, the gas refrigerant is sucked into the sealed container 21 from the suction pipe 23. Then, the sucked gas refrigerant is supplied to the compression chamber A through the suction chamber B, compressed, and sent to the discharge port 11 c provided in the fixed scroll 11. When the pressure of the refrigerant sent to the discharge port 11c exceeds a preset pressure, the refrigerant in the discharge port 11c pushes the discharge valve 11f upward to pass through the discharge valve 11f and is sent to the discharge pipe 24. It is.

[Refrigeration cycle apparatuses 100 and 101]
FIG. 3 is a configuration example diagram of the

refrigeration cycle apparatuses

100 and 101 including the scroll compressor 1 shown in FIG. 1 and a Mollier diagram of the

refrigeration cycle apparatuses

100 and 101.
FIG. 3A1 is an example of the refrigeration cycle apparatus 100 in the case of injecting the bypass refrigerant whose pressure has been reduced to the intermediate pressure into the scroll compressor 1. 3 (b1) shows that the bypass refrigerant decompressed to the intermediate pressure is heat-exchanged with the remaining mainstream refrigerant to increase the degree of supercooling of the mainstream refrigerant before the expansion valve, and then the scroll compressor 1 It is an example of the refrigeration cycle apparatus 101 in the case of performing injection. 3 (a2) is a Mollier diagram of the refrigeration cycle apparatus 100 in FIG. 3 (a1), and FIG. 3 (b2) is a Mollier diagram of the refrigeration cycle apparatus 101 in FIG. 3 (b1).

As shown in FIG. 3 (a1), the refrigeration cycle apparatus 100 is connected to the refrigerant discharge side of the scroll compressor 1, and condenses the refrigerant flowing out from the scroll compressor 1, and one is the condenser 2. A first expansion valve 3 connected to depressurize the refrigerant flowing out of the condenser 2; one connected to the first expansion valve 3; the other connected to the refrigerant suction side of the scroll compressor 1; The evaporator 4 which evaporates the refrigerant | coolant which flows out out of it, and the 2nd expansion valve 28 connected to the injection piping 27 of the scroll compressor 1 are provided.
The injection pipe 27 is connected between the condenser 2 and the first expansion valve 3 on the side opposite to the side to which the scroll compressor 1 is connected, and a part of the refrigerant flowing out of the condenser 2 2. Supply to the compression chamber A through the expansion valve 28.

In the refrigeration cycle apparatus 100 of FIG. 3 (a1), at the outlet of the condenser 2, it is divided into a refrigerant that flows into the injection pipe 27 and a refrigerant that does not. The refrigerant flowing into the injection pipe 27 is reduced to an intermediate pressure by the second expansion valve 28. Then, the refrigerant reduced to the intermediate pressure is supplied into the compression chamber A.
On the other hand, the mainstream refrigerant that does not flow into the injection pipe 27 is decompressed to a low pressure by the first expansion valve 3. Then, the mainstream refrigerant is sucked from the suction pipe 23 into the scroll compressor 1 through the evaporator 4 and merges in the compression chamber A.

Here, as shown in FIG. 3 (a2), the refrigeration cycle apparatus 100 will be described using a Mollier diagram in which the vertical axis represents pressure and the horizontal axis represents specific enthalpy.
The refrigerant that has flowed out of the condenser 2 having the high pressure Pd corresponds to the point exp, but the refrigerant that has flowed out of the condenser 2 flows into the injection portion Yinj flowing into the injection pipe 27 and into the first expansion valve 3. The main stream (1-Yinj) is divided.
The main flow component (1-Yinj) is reduced to the low pressure Ps by the first expansion valve 3, and the injection component Yinj is reduced to the intermediate pressure Pm by the second expansion valve 28.
The intermediate pressure Pm is determined according to the position of the injection port 11e. That is, the volume of the compression chamber A in which the injection port 11e is open changes during one revolution of the orbiting scroll 12, but the intermediate pressure Pm is an average value during the one revolution. The intermediate pressure Pm is determined by the compression ratio from when the suction into the compression chamber A is completed.

The main stream (1-Yinj) is heated by the evaporator 4 to increase the specific enthalpy. This corresponds to the point s. Then, the refrigerant sucked into the scroll compressor 1 from the evaporator 4 is compressed by the fixed scroll 11 and the swing scroll 12, but when compressed to a certain pressure, that is, from the point s to the point d1. When compressed, Yinj refrigerant for injection is injected from the injection port 11e.
At this time, the refrigerant having the specific enthalpy corresponding to the point d1 (main stream component (1-Yinj)) and the refrigerant having the specific enthalpy corresponding to Yinj (injection component Yinj) are mixed to the point s2. The corresponding specific enthalpy refrigerant.
The “specific enthalpy refrigerant corresponding to the point s2” is compressed in the compression chamber A and discharged from the discharge port 11c. This corresponds to the point d2.
In addition, as shown in FIG. 3 (b2), if injection is not made, it turns out that a refrigerant | coolant is compressed and it transfers to the point d from the point s. That is, it can be seen that the specific enthalpy can be lowered and the temperature of the refrigerant discharged from the scroll compressor 1 can be lowered when the injection is performed than when the injection is not performed.

3 (b1), the refrigeration cycle apparatus 101 is different from the refrigeration cycle apparatus 100 in that an internal heat exchanger 29 having two refrigerant channels is provided. The internal heat exchanger 29 has a first flow path connected between the condenser 2 and the first expansion valve 3, and a second flow path connected downstream of the second expansion valve 28 in the injection pipe 27. The heat exchanger has a flow path and can exchange heat between the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path.

The refrigeration cycle apparatus 101 is provided with an internal heat exchanger 29 that exchanges heat between the refrigerant that has passed through the second expansion valve 28 and the mainstream refrigerant before flowing into the first expansion valve 3. The degree of cooling can be increased.
On the Mollier diagram, as shown in FIG. 3 (b2), the injection amount Yinj is depressurized by the second expansion valve 28 from the point exp of the high pressure Pd to become a refrigerant having the intermediate pressure Pm.
On the other hand, the mainstream refrigerant is supercooled by exchanging heat with the reduced injection pressure Yinj of the intermediate pressure Pm by the internal heat exchanger 29 and moves from the point exp of the high pressure Pd to the point exp2 of the high pressure Pd.
After the mainstream refrigerant flows into the evaporator 4 and the specific enthalpy increases, it is sucked into the scroll compressor 1 and compressed by the fixed scroll 11 and the orbiting scroll 12, but is compressed to a certain pressure. By the way, when compressed from the point s to the point d1, the refrigerant corresponding to the injection amount Yinj is injected from the injection port 11e.
At this time, the refrigerant having the specific enthalpy corresponding to the point d1 (main stream component (1-Yinj)) and the refrigerant having the specific enthalpy corresponding to Yinj (injection component Yinj) are mixed to the point s2. The corresponding specific enthalpy refrigerant. Thereafter, the “refrigerant having a specific enthalpy corresponding to the point s2” is compressed in the compression chamber A and becomes a refrigerant corresponding to the point d2.
Thus, it can be seen that the refrigeration cycle apparatus 101 can also lower the specific enthalpy when injection is performed and lower the temperature of the refrigerant discharged from the scroll compressor 1 than when it is not performed.

Here, in both FIG. 3 (a2) and FIG. 3 (b2), the specific enthalpy at the point s2 when compression is started after injection is determined by the following equation (1). However, the specific enthalpy at each point in FIGS. 3 (a2) and 3 (b2) is h. For example, the specific enthalpy at the point s2 is expressed as h _s2 .
h _s2 = (1−Yinj) · h _d1 + Yinj · h _inj (1)
In the case of FIG. 3 (a2), the following relationship (2) is established.
h _inj = h _exp (2)
In the case of FIG. 3 (b2), the following relationship (3) is established.
h _inj = h _exp + (1−Yinj) / Yinj · (h _exp −h _exp2 ) (3)
Therefore, the intermediate pressure Pm (point d1) is given at the position of the injection port 11e from the operating conditions Pd (point exp) and Ps (point s), and the point d2 → point s2 is known from the allowable discharge temperature. Thus, Yinj is uniquely determined from h _{s2 in} FIG. _3A2 and in FIG. _3B2 according to he _xp2 .
Thus, by controlling the opening degree of the first expansion valve 3 and the second expansion valve 28, the size of the injection component Yinj and the main flow component (1-Yinj) is changed, that is, the scroll compression ratio is changed. The temperature of the refrigerant discharged from the machine 1 can be adjusted.

[Effects of the scroll compressor according to Embodiment 1]
In the scroll compressor 1 according to the first embodiment, an injection port 11 e is provided in the fixed scroll 11, and a portion of the injection pipe 27 in the sealed container 21 is a boundary between the swing scroll 12 and the fixed scroll 11. Thus, it is provided so as to be located on the side opposite to the side where the electric motor 139 which is a power mechanism is provided.
For this reason, it suppresses that the refrigerant | coolant which flows through the injection piping 27 by the friction heat which generate | occur | produces on the sliding surface of the rocking scroll 12 and the flame | frame 14, and the heat | fever which arises with the electric current supplied to the electric motor 139, etc. Therefore, it is possible to suppress the temperature of the refrigerant discharged from the scroll compressor 1 from being hardly lowered.

The scroll compressor 1 according to the first embodiment has an injection port 11e connected in the middle of the compression chamber A, and is used as a sliding member such as the frame 14, the fixed scroll 11, and the swinging scroll 12. The refrigerant is configured not to merge at a stage before the refrigerant is supplied. For this reason, it is possible to prevent the refrigerant before being supplied to the sliding member from being diluted, so that the refrigerating machine oil contained in the refrigerant is prevented from being diluted. Damage can be suppressed.

Since the

refrigeration cycle apparatuses

100 and 101 including the scroll compressor 1 according to the first embodiment include the scroll compressor 1, it is difficult to reduce the temperature of the refrigerant discharged from the scroll compressor 1. Can be suppressed.
And even when R32 refrigerant is employed in the

refrigeration cycle apparatuses

100 and 101, it is possible to prevent the temperature of the refrigerant discharged from the scroll compressor 1 from becoming difficult to decrease, and to increase the reliability of the apparatus. be able to.
Further, since the

refrigeration cycle apparatuses

100 and 101 can suppress the temperature of the refrigerant discharged from the scroll compressor 1 from being difficult to decrease as described above, a mixed refrigerant of HFO-1123 and R32, Alternatively, even when a mixed refrigerant of HFO-1123 and HFO-1234yf is employed, the occurrence of disproportionation reaction can be suppressed. That is, the

refrigeration cycle apparatuses

100 and 101 not only can suppress the disproportionation reaction by reducing the proportion of HFO-1123 by using HFO-1123 mixed with R32 or HFO-1234yf, Since it can suppress that it becomes difficult to reduce the temperature of the refrigerant | coolant discharged from the scroll compressor 1, disproportionation reaction can be suppressed further.

Embodiment 2. FIG.
FIG. 4 is a schematic longitudinal sectional view of a scroll compressor 1A according to the second embodiment. FIG. 5 is an explanatory diagram of the fixed spiral body 11b and the swinging spiral body 12b, the discharge port 11c, the injection port 11e, and the sub discharge port 11g shown in FIG. In the second embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and differences from the first embodiment will be mainly described.

(Intermediate cooling pipe 9 and sub discharge port 11g, etc.)
1 A of scroll compressors are provided over the inside and outside of the airtight container 21, and have the intermediate | middle cooling pipe 9 with which one communicates with the compression chamber A side and the other communicates with the injection piping 27 side. The intermediate cooling pipe 9 is connected to a side surface of the sealed container 21 so as to communicate with a flow path (a first passage 11k and a second passage 11l described later) in the fixed scroll 11 in the sealed container 21.
1 A of scroll compressors have the following structure in addition to the discharge port 11c in which the fixed scroll 11 is formed in the center part of the fixed scroll 11, and discharges the refrigerant | coolant compressed by the compression chamber A. As shown in FIG. That is, in the fixed scroll 11, the first opening 11 i that opens into the compression chamber A is formed between the discharge port 11 c and the injection port 11 e in the radial direction of the fixed scroll 11 and communicates with the intermediate cooling pipe 9. It has a port 11g.

The sub discharge port 11g is formed so as to extend in the vertical direction of the fixed scroll 11, and the second opening 11j that opens to the first opening 11i and the concave portion 50a having the discharge side space of the discharge port 11c. The first passage 11k communicates with the first passage 11k.
Two sub discharge ports 11g are provided in the same manner as the injection port 11e. One sub discharge port 11g is provided in the first intermediate chamber of the first compression chamber Aa. The other sub discharge port 11g is provided in the second intermediate chamber of the second compression chamber Ab.
At this time, in the state shown in FIG. 5, one injection port 11 e is provided at a position about one and a half halves along the inward surface side from the end of winding of the involute of the fixed scroll 11. The other injection port 11e is provided at a position about one and a half times along the inward surface side from the end of winding of the involute of the orbiting scroll 12.

The sub discharge port 11g is formed so as to extend in the radial direction of the fixed scroll 11, and has a second passage 11l in which one communicates with the first passage 11k and the other communicates with the intermediate cooling pipe 9. The sub discharge port 11g is provided with a check valve 11h provided to close the first passage 11k.
The check valve 11h is provided in the second opening 11j, and when the refrigerant in the first passage 11k becomes larger than a preset pressure, a concave portion that is a space on the discharge side of the discharge port 11c from the first passage 11k side. It has a function of flowing a refrigerant to the 50a side.

In this way, the scroll compressor 1A is provided with the sub discharge port 11g at a position higher than the injection port 11e, and a part of the refrigerant in the compression chamber A is transferred to the intermediate cooling pipe 9 under an operation condition of a high compression ratio. It is comprised so that it can extract out of the airtight container 21 via.
That is, under the high compression ratio operating conditions, the temperature of the refrigerant discharged from the scroll compressor 1A rises, so the extracted refrigerant is cooled and the injection port 27e passes through the injection port 11e into the compression chamber A. The specific enthalpy of the refrigerant in the compression chamber A is lowered. Thereby, the temperature of the refrigerant discharged from the scroll compressor 1 can be suppressed.

Further, the sub discharge port 11g communicates with the high pressure side after the discharge valve 11f via the check valve 11h. That is, the sub discharge port 11g communicates with the concave portion 50a. For this reason, under low compression ratio operating conditions in which the temperature of the refrigerant discharged from the scroll compressor 1 does not increase, the overcompression loss can be reduced by bypass discharge to the high pressure side via the check valve 11h. it can.

(About refrigeration cycle devices 102 and 103)
FIG. 6 is a schematic diagram for explaining the operation during the intermediate cooling operation of the scroll compressor 1A according to the second embodiment. FIG. 7 is a configuration example diagram of the

refrigeration cycle apparatuses

102 and 103 including the scroll compressor 1A shown in FIG. 4 and a Mollier diagram of the

refrigeration cycle apparatuses

102 and 103.
It should be noted that both the refrigeration cycle apparatus 102 shown in FIG. 7A and the refrigeration cycle apparatus 103 shown in FIG. 7B are the same in terms of cycle, resulting in the Mollier diagram shown in FIG. 7C.

Here, FIG. 6A shows a state in which the sub discharge port 11g is opened to the second intermediate chamber and the injection port 11e is opened to the second outermost chamber. FIG. 6B shows a state in which the upper end side of the swinging spiral body 12b that seals between the second innermost chamber and the second intermediate chamber is at a position facing the sub discharge port 11g. ing. Further, FIG. 6C shows a state in which the sub discharge port 11g and the injection port 11e are both opened to the second intermediate chamber.
Here, the second innermost chamber and the second intermediate chamber communicate with each other between FIG. 6A and FIG. 6B to become the innermost chamber. Further, what has been the second outermost chamber until then becomes the second intermediate chamber. And after FIG.6 (c) and before Fig.6 (a), the winding end of the rocking | vortex spiral body 12b becomes a sealing point, and forms a 2nd outermost chamber newly.

As shown in FIGS. 7A and 7B, one of the refrigeration cycle apparatuses 102 is connected to the refrigerant discharge side of the scroll compressor 1, and condenses the refrigerant flowing out from the scroll compressor 1A. One is connected to the condenser 2 and the first expansion valve 3 for reducing the pressure of the refrigerant flowing out of the condenser 2 is connected to the first expansion valve 3 and the other is connected to the refrigerant suction side of the scroll compressor 1. The evaporator 4 is connected and evaporates the refrigerant flowing out from the first expansion valve 3, and the intermediate cooling flow rate adjusting valve 7 is connected to the intermediate cooling pipe 9 of the scroll compressor 1.
In the refrigeration cycle apparatus 102 in FIG. 7A, the evaporator 4 includes a third flow path connected between the first expansion valve 3 and the refrigerant suction side of the scroll compressor 1, one of which is intermediate cooled. Heat having a fourth flow path and a fifth flow path connected to the pipe 9 and the other connected to the injection pipe 27, and heat exchange between the refrigerant flowing through the third flow path and the refrigerant flowing through the fourth flow path. It is an exchanger.
In addition, in the refrigeration cycle apparatus 103 of FIG.7 (b), the evaporator 4 is not provided with the 5th flow path.

The injection pipe 27 can supply the refrigerant supplied through the intermediate cooling pipe 9 and the fourth flow path to the compression chamber A.
Thus, the evaporator 4 includes the refrigerant flowing through the third flow path connected to the first expansion valve 3 and the fourth flow path (or fourth flow path) connected to the intermediate cooling pipe 9 of the scroll compressor 1. And the refrigerant flowing through the fifth flow path) have a function of cooling the refrigerant flowing through the fourth flow path (or the fourth flow path and the fifth flow path) by exchanging heat.
Here, the configuration corresponding to the fourth flow path (or the fourth flow path and the fifth flow path) is also referred to as an intercooler 10 in the following description.

The intermediate cooling flow rate adjustment valve 7 maintains a differential pressure between the sub discharge port 11g and the injection port 11e, and is injected from the refrigerant extracted from the intermediate cooling pipe 9, the refrigerant cooled by the evaporator 4, and the injection pipe 27. It is used to adjust the amount of refrigerant. The intermediate cooling flow rate adjusting valve 7 is provided one by one in the injection pipe 27 in FIG. 7A, and is connected to a portion of the injection pipe 27 before branching in FIG. 7B.

In FIG. 7A, the refrigerant flowing out from both intermediate cooling pipes 9 is supplied to the injection pipe 27 via the evaporator 4 without being merged, and in FIG. The refrigerant that has flowed out of the cooling pipe 9 is joined and supplied to the injection pipe 27 via the evaporator 4, and is divided by the injection pipe 27.

6 (a) and 6 (b), the sub discharge port 11g opens into the compression chamber A having a higher pressure than the injection port 11e. For this reason, the refrigerant in the compression chamber A in which the sub discharge port 11g is opened can be extracted and mixed with the refrigerant in the compression chamber A in which the injection port 11e is opened.
By cooling with the intermediate cooler 10 provided in the middle of the injection port 11e from the sub discharge port 11g, the specific enthalpy of the compression chamber A in which the injection port 11e is open can be lowered.
In the state shown in FIG. 6C, the sub discharge port 11g and the injection port 11e open to the same compression chamber A, so that intermediate cooling is not performed between the two ports in a pressure-equalized state.
That is, the operations of “extraction of refrigerant from intermediate cooling pipe 9”, “cooling of refrigerant in intermediate cooler 10” and “injection into compression chamber A by injection pipe 27” are intermittent. As a result, the “temporal ratio between the differential pressure state and the pressure equalized state” and “the magnitude of the differential pressure” between the sub discharge port 11g and the injection port 11e depend on the formation positions of the sub discharge port 11g and the injection port 11e. To do.
Therefore, by setting the port formation position and opening degree control of the intermediate cooling flow rate adjustment valve 7, the intermediate cooling amount can be increased and decreased, and the temperature of the refrigerant discharged from the scroll compressor 1 can be adjusted.

7A and 7B, the refrigerant discharged from the scroll compressor 1 is heat-exchanged by the condenser 2 when viewed from the Mollier diagram of FIG. 7C. After condensation (point exp), the pressure is reduced by the first expansion valve 3 and heat is exchanged by the evaporator 4 to absorb heat. A part of the heat exchange amount in the evaporator 4 absorbs heat from the intermediate cooler 10.
When the refrigerant exiting the evaporator 4 and sucked into the scroll compressor 1 (point s) is compressed to the intermediate pressure Pms corresponding to the injection port 11e, the refrigerant is compressed at the intermediate pressure Pmd corresponding to the sub discharge port 11g with the compression chamber A. (Point md2).
Then, the refrigerant extracted from the compression chamber A via the intermediate cooling pipe 9 is supplied to the intermediate cooler 10 and is cooled by the refrigerant passing through the evaporator 4 (point md1). The cooled refrigerant is returned to the compression chamber A through the injection pipe 27 and mixed, whereby the specific enthalpy is reduced (point s2).
Therefore, the specific enthalpy is lower than when the intermediate cooling is not performed (point d), that is, the refrigerant discharged from the scroll compressor 1 can be discharged at a low temperature (point d2).

FIG. 8 is a simplified version of the Mollier diagram of FIG. 7C for explaining the compression process. In FIG. 8, the specific enthalpy h _s of the high pressure Pd, the low pressure Ps, and the suction (point s) is given from the operating conditions, and the intermediate pressure depends on the port position.

The intermediate pressure Pms is determined by the pressure increase amount due to compression up to the average volume during one rotation of the compression chamber A opened at the injection port 11e (IJP) and the intermediate pressure Pmd at the sub discharge port 11g (SP).
At this time, the state quantity after injection (point s2) at the intermediate pressure Pms is uniquely determined so that the temperature of the refrigerant (point d2) discharged from the scroll compressor 1 becomes a preset value.
The extraction amount from SP at the intermediate pressure Pmd during the compression process from the point s2 to the point d2 is the diversion ratio Ybp with respect to the circulation amount 1 of the entire cycle, and the refrigerant at the outlet of the intermediate cooler (point md1) for the diversion ratio Ybp. When the specific enthalpy and h _md1, state quantity after injection in IJP is, with respect to that constraint becomes s2 a point such that the predetermined discharge temperature at point d2, be given a specific enthalpy h _md1 shunt The ratio Ybp is determined.
Since the refrigerant having a specific enthalpy h _d1 of 1 and the refrigerant having a diversion ratio Ybp of the specific enthalpy h _md1 are mixed, the specific enthalpy h _s2 is obtained.
(1 + Ybp) · h _s2 = h _d1 + Ybp · h _md1 (4)
That is, h _d1 −h _s2 = Y _bp · (h _s2 −h _md1 ) (5)
In order to satisfy the above, when the specific enthalpy h _md1 is larger than the given specific enthalpy h _s2 and specific enthalpy h _d1 (intermediate cooling amount is small), the diversion ratio Ybp is increased and the specific enthalpy h _md1 is decreased (intermediate cooling) If the amount is large), the diversion ratio Ybp is made small.

At this time, the enthalpy difference Δh _W corresponding to the compression work in the compressor is
Δh _W = 1 · (h _d1 −h _s ) + (1 + Ybp) (h _md2 −h _s2 ) + 1 · (h _d2 −h _md2 )
= (H _d1 −h _s ) + (h _d2 −h _s2 ) + Ybp · (h _md2 −h _s2 ) (6)
The enthalpy difference Δh _Q corresponding to the refrigeration capacity in the evaporator 4 (see also the point exp in FIG. 7C)
Δh _Q = 1 · (h _s −h _exp ) − Ybp · (h _md2 −h _md1 ) (7)
Δh _Q / Δh _W becomes cycle C. O. P. It corresponds to.

The specific enthalpy h _md1 affects only the numerator, whereas when the diversion ratio Ybp increases, both the denominator and the numerator affect C.I. O. P. Therefore, from the viewpoint of efficiency, it is desirable to increase the enthalpy difference in the intercooler 10 to keep the diversion ratio Ybp low.

For the purpose of reducing the specific enthalpy during the compression process, when the refrigerant enters and exits the scroll compressor 1 such as extraction from the compression chamber A and injection into the compression chamber A, the refrigerant is heated by heat transfer in the middle of entering and exiting. This will reduce the cooling effect. That is, in order to suppress the discharge temperature to be set in advance, it is necessary to increase the diversion ratio Ybp commensurate with the influence of heating, leading to a decrease in performance.

[Effects of scroll compressor 1A and the like according to Embodiment 2]
The scroll compressor 1A according to the second embodiment and the

refrigeration cycle apparatuses

102 and 103 having the same are the same effects as the scroll compressor 1 according to the first embodiment and the

refrigeration cycle apparatuses

100 and 101 having the same. Play.

1, 1A scroll compressor, 2 condenser, 1st expansion valve, 4 evaporator, 6 check valve, 7 intermediate cooling flow rate adjustment valve, 9 intermediate cooling pipe, 10 intermediate cooler, 11 fixed scroll, 11A fixed swirl Internal side surface, 11B fixed spiral body outer surface, 11a base plate, 11b fixed spiral body, 11c discharge port, 11d concave portion, 11e injection port, 11f discharge valve, 11g sub discharge port, 11h check valve, 11i first opening, 11j 2nd opening, 11k 1st passage, 11l 2nd passage, 12 rocking scroll, 12A rocking spiral outer surface, 12B rocking spiral side, 12a base plate, 12b rocking spiral, 12c boss, 13 Oldham ring, 14 frames, 15 shafts, 15a eccentric part, 15b 1st balancer, 18 b 18a, 2nd balancer, 19 stator, 20 sub bearing, 21 sealed container, 22 bottom oil reservoir, 23 suction pipe, 24 discharge pipe, 25 discharge valve, 27 injection pipe, 28 second expansion valve, 29 internal heat exchanger 50, discharge pipe connection, 50a concave part, 50b concave part, 91 oil pump, 100-103 refrigeration cycle apparatus, 110 subframe, 139 electric motor, A compression chamber, Aa first compression chamber, Ab second compression chamber, B Inhalation chamber.

Claims

A sealed container;
An orbiting scroll housed in the sealed container and having a first spiral body formed thereon;
A fixed scroll that is fixed to the inner peripheral surface of the hermetic container, forms a second spiral body that compresses the refrigerant together with the first spiral body, and forms a compression chamber with the orbiting scroll;
An injection pipe provided over the inside and outside of the sealed container and used to supply a refrigerant to the compression chamber;
A rotating shaft that is housed in the hermetic container and has one end connected to the side of the orbiting scroll opposite to the side on which the fixed scroll is provided, and that causes the orbiting scroll to oscillate;
A power mechanism housed in the sealed container, connected to the other of the rotating shafts, and rotating the rotating shaft;
Have
The injection pipe is
The portion in the sealed container is provided so as to be located on the side opposite to the side on which the power mechanism is provided, with the rocking scroll and the fixed scroll as a boundary,
The fixed scroll is
A scroll compressor having an injection port in which one communicates with the injection pipe and the other communicates with the compression chamber.
An intermediate cooling pipe provided over the inside and outside of the sealed container, one communicating with the compression chamber side and the other communicating with the injection piping side;
The fixed scroll is
A discharge port that is formed at the center of the fixed scroll and discharges the refrigerant compressed in the compression chamber;
The 1st opening part opened to the said compression chamber is formed between the said discharge port and the said injection port in the radial direction of the said fixed scroll, and has a sub discharge port connected with the said intermediate cooling pipe. The scroll compressor described.
The sub-discharge port is
A first passage formed so as to extend in a vertical direction of the fixed scroll and communicating the first opening and a second opening that opens to a discharge-side space of the discharge port;
The scroll compressor according to claim 2, further comprising: a second passage formed so as to extend in a radial direction of the fixed scroll, one communicating with the first passage and the other communicating with the intermediate cooling pipe.
A check valve that is provided in the second opening and allows the refrigerant to flow from the first passage side to the discharge-side space side of the discharge port when the refrigerant in the first passage exceeds a preset pressure; The scroll compressor according to claim 3.
A scroll compressor according to claim 1;
A condenser connected to a refrigerant discharge side of the scroll compressor and condensing refrigerant flowing out of the scroll compressor;
A first expansion valve, one of which is connected to the condenser and depressurizes the refrigerant flowing out of the condenser;
An evaporator, one of which is connected to the first expansion valve and the other is connected to a refrigerant suction side of the scroll compressor, and evaporates the refrigerant flowing out of the first expansion valve;
A second expansion valve connected to the injection pipe of the scroll compressor;
Have
The injection pipe is
The side opposite to the side to which the scroll compressor is connected is connected between the condenser and the first expansion valve, and a part of the refrigerant flowing out of the condenser passes through the second expansion valve. A refrigeration cycle apparatus that supplies the compression chamber.
The condenser is
A first flow path connected between the condenser and the first expansion valve;
A second flow path connected to the downstream side of the second expansion valve in the injection pipe, and heat exchange is performed between the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path. The refrigeration cycle apparatus according to claim 5, which is a heat exchanger.
A scroll compressor according to any one of claims 2 to 4,
One side is connected to the refrigerant discharge side of the scroll compressor, and a condenser that condenses the refrigerant flowing out of the scroll compressor;
A first expansion valve, one of which is connected to the condenser and depressurizes the refrigerant flowing out of the condenser;
An evaporator, one of which is connected to the first expansion valve and the other is connected to a refrigerant suction side of the scroll compressor, and evaporates the refrigerant flowing out of the first expansion valve;
A second expansion valve connected to the intermediate cooling pipe of the scroll compressor;
Have
The evaporator is
A third flow path connected between the first expansion valve and the refrigerant suction side of the scroll compressor;
One of which is connected to the intermediate cooling pipe and the other of which is connected to the injection pipe, and which exchanges heat between the refrigerant flowing through the third flow path and the refrigerant flowing through the fourth flow path. A heat exchanger,
The injection pipe is
A refrigeration cycle apparatus that supplies the refrigerant supplied through the intermediate cooling pipe and the fourth flow path to the compression chamber.
The refrigeration according to any one of claims 5 to 7, wherein the refrigerant circulating in the refrigeration cycle apparatus is an R32 refrigerant, a mixed refrigerant of HFO-1123 and R32, or a mixed refrigerant of HFO-1123 and HFO-1234yf. Cycle equipment.