KR20090052793A - Refrigerating device and compressor - Google Patents

Abstract

The present invention is to provide a refrigeration apparatus that can reduce the discharge gas temperature of the compressor even when an R32 refrigerant is used, and can improve the reliability and operation ability by securing the heat resistance and the wear resistance of the compressor. In a solution for achieving the above, the compressor (1), the outdoor heat exchanger (3), the gas-liquid separator (5), the first expansion valve (7), and the indoor heat exchanger (I) in a sealed container are discharge pressure atmospheres. 9) A refrigeration apparatus using a mixed refrigerant having at least 60% mass of R32 or R32 refrigerant as a refrigerant, wherein a part of the refrigerant is injected into the compressor 1 as flash gas, which is a saturated refrigerant in two-phase gas phase, from the gas-liquid separator outlet. The injection circuit 40 is provided.

Refrigeration unit, compressor

Description

Refrigeration Units and Compressors {REFRIGERATING DEVICE AND COMPRESSOR}

The present invention relates to a refrigerating device using an R32 refrigerant and a compressor used for the refrigerating device.

Conventionally, there is a refrigeration apparatus having a refrigeration cycle in which a compressor, a condenser, an expansion valve, and an evaporator are sequentially connected to a refrigerant pipe. In this type of refrigerating device, when the R32 refrigerant is used as the refrigerant, its thermal properties increase the discharge gas temperature by 10 to 20 ° C. due to its thermal properties compared to the R22 refrigerant or the R410A refrigerant. . Thus, when discharge gas temperature becomes high, there exists a problem that the temperature of a compressor rises at the time of overload operation | operation, such as in low outside air heating, and overheats the heat resistance temperature of a motor insulation material, and causes the fall of reliability.

As a compressor of a refrigerating device, a hermetic compressor in which lubricating oil is enclosed in a hermetic container is used. In this type of compressor, operation is performed while supplying lubricating oil to a sliding point of a compression element inside the compressor. That is, a compression operation | movement is performed, preventing abrasion by supplying lubricating oil to a slide point. However, when the discharge gas temperature increases, the internal temperature of the whole compressor also rises, so that the temperature of the lubricating oil also rises. As a result, the viscosity of the lubricating oil decreases, resulting in poor lubrication, resulting in reliability problems. In addition, there is a problem that causes a decrease in driving ability.

Therefore, in recent years, a bypass tube for bypassing the gas side and the liquid side of the refrigerant circuit through a refrigerant circuit comprising a compressor, a condenser, an expansion valve, and an evaporator, a supercooled heat exchanger disposed between the condenser and an expansion valve, and a supercooled heat exchanger. And a refrigerating device using an R32 refrigerant having a subcooling decompression means disposed on an upstream side of the subcooling heat exchanger of the bypass pipe, wherein the discharge temperature of the compressor reaches a certain temperature or more. By controlling the means, there is a method of reducing the discharge temperature of the compressor by flowing a part of the refrigerant at the condenser outlet through the bypass pipe to the evaporator outlet side (see Patent Document 1, for example).

Patent Document 1: Japanese Patent Application Laid-Open No. 2001-227823

However, in the technique of Patent Literature 1, the liquid refrigerant depressurized through the subcooling heat exchanger is sometimes injected into the gas refrigerant on the evaporator outlet side while remaining the liquid refrigerant. In this case, the compressor is used to compress the liquid refrigerant as it is, and there is a problem in that an excessive load is applied to the compression element portion and the reliability is lowered.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and even when the R32 refrigerant is used, the discharge gas temperature of the compressor can be lowered, and the heat resistance and wear resistance of the compressor can be ensured, thereby improving reliability and driving ability. It is an object of the present invention to provide a refrigeration apparatus which can be used and a compressor used in the refrigeration apparatus.

The refrigerating device according to the present invention includes a mixed refrigerant having an airtight atmosphere in a sealed container, a condenser, a gas-liquid separator, an expansion valve, and an evaporator, and containing at least 60% by mass of R32 or R32 refrigerant as the refrigerant. A refrigeration apparatus used is provided with an injection circuit for injecting a part of the refrigerant from the gas-liquid separator outlet into the compressor as a flash gas which is a saturated refrigerant in two-phase gas-liquid phase.

According to the present invention, since the flash gas which is the saturated refrigerant of two-phase gas-liquid is injected into the compressor, the internal temperature of the compressor can be reduced and the discharge temperature can be reduced. As a result, it is possible to improve the reliability of the compressor and to improve the driving ability, as compared with the case of not performing injection injection.

EMBODIMENT OF THE INVENTION Hereinafter, the refrigeration apparatus of this invention is demonstrated, referring drawings.

Embodiment 1.

BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows schematic structure of the air conditioner as a refrigeration apparatus of Embodiment 1 of this invention.

The air conditioner shown in FIG. 1 uses an R32 refrigerant (including a mixed refrigerant containing at least 60% by mass or more of R32 refrigerant) as a working refrigerant, and includes a sealed rotary refrigerant compressor (1) and a four-way valve (2). , Outdoor heat exchanger (3), bridge circuit (4), gas-liquid separator (5), internal heat exchanger (6), first expansion valve (7), indoor heat exchanger (9) and accumulator (10) It is connected in order and comprises a refrigeration cycle. The hermetic rotary refrigerant compressor 1 is configured such that the inside of the hermetic container becomes a discharge pressure atmosphere, and has a high pressure. Further, a portion of the refrigerant from the gas-liquid separator 5 to the internal heat exchanger 6 is transferred to the hermetic rotary refrigerant compressor 1 through the second expansion valve 8 and the internal heat exchanger 6 as throttle portions. It has the injection circuit 40 which passes. The bridge circuit 4 has four check valves 4a, 4b, 4c, and 4d, and has two input / output ports, an input port, and an output port one by one.

Moreover, inside the air conditioner, the discharge temperature sensor 11 which detects the temperature of the discharge side of the sealed rotary refrigerant compressor 1, the temperature sensor 12 which detects the refrigerant temperature of an outdoor heat exchanger, and an indoor heat exchanger A temperature sensor 13 for detecting the coolant temperature is provided.

FIG. 2 is a block diagram showing the electrical configuration of the air conditioner of FIG. In addition, in FIG. 2, the part required for description of the characteristic part of this invention is shown, and illustration other than a required part is abbreviate | omitted.

The air conditioner is provided with the control part 14 which consists of microcomputers, The control part 14 has the discharge temperature sensor 11, the temperature sensor 12, the temperature sensor 13, and the 1st expansion valve 7. The second expansion valve 8 and the four-way valve 2 are electrically connected to each other. The control unit 14 includes a CPU, a RAM for storing various data, and a R0M (all not shown) for storing a program for performing operation control in each operation mode to be described later, and each temperature sensor 11. Based on the temperature information from 13 to 13), the first expansion valve 7, the second expansion valve 8 and the four-way valve 2 are appropriately controlled in accordance with the program in R0M, and the cooling operation and heating operation described later. Various operation control including a.

In the air conditioner comprised as mentioned above, a cooling operation and a heating operation are demonstrated one by one.

<Cooling operation>

When performing cooling operation, the 4-way valve 2 is switched to the switching position shown by the solid line of FIG. When the hermetic rotary refrigerant compressor 1 is started, the high temperature and high pressure refrigerant is discharged from the hermetic rotary refrigerant compressor 1, and the check of the four-way valve 2, the outdoor heat exchanger 3, and the bridge circuit 4 is performed. It passes through the valve 4a one by one, and flows into the gas-liquid separator 5, where it is separated into gaseous phase and liquid phase.

In normal cooling operation, the liquid refrigerant separated by the gas-liquid separator 5 flows into the internal heat exchanger 6 as it is, and thereafter, the first expansion valve 7 reduces the pressure from the high pressure to the low pressure. And it passes through the check valve 4d of the bridge circuit 4, heat-exchanges with room air in the indoor heat exchanger 9, and absorbs heat, and performs a cooling effect. The refrigerant passes through the four-way valve 2 again and returns to the main body of the sealed rotary refrigerant compressor 1 through the accumulator 10 of the sealed rotary refrigerant compressor 1. This cycle is repeated to cool the room.

Here, when cooling operation continues, when the discharge temperature of the sealed rotary refrigerant compressor 1 becomes more than the predetermined temperature preset, the control part 14 will open the 2nd expansion valve 8, and will open | release the gas-liquid separator 5 here. A part of the refrigerant flowing out is bypassed to the sealed rotary refrigerant compressor 1 through the second expansion valve 8 and the internal heat exchanger 6. As a result, a part of the refrigerant leaving the gas-liquid separator 5 is decompressed from the high pressure to the medium pressure in the second expansion valve 8, flows into the internal heat exchanger 6, and enters the internal heat exchanger 6 from the normal circulation flow path. Heat exchange in the internal heat exchanger (6) and the high pressure refrigerant introduced into. As a result, the medium pressure refrigerant which flowed into the internal heat exchanger 6 becomes a flash gas which is a saturated refrigerant state of two-liquid gas phase, and is injected into the sealed rotary refrigerant compressor 1.

In the hermetic rotary refrigerant compressor (1), a refrigerant circulating through a refrigeration cycle regularly flows in through the accumulator 10 and is compressed at a high temperature and high pressure in a compression chamber (see the compression chamber 27 of FIG. 4 to be described later). In addition, a flash gas of two-phase gas liquid is injected. Thereby, the discharge temperature of the hermetic rotary refrigerant compressor 1 can be lowered as compared with the case where no flash gas is injected. Control of the discharge temperature can be performed by adjusting the opening degree of the second expansion valve 8 and adjusting the amount of refrigerant to be bypassed from the gas-liquid separator 5 outlet.

Here, it is preferable that the dryness (ratio of gas) of the flash gas injected into the sealed rotary refrigerant compressor 1 is 0.2-0.8 for the following reasons. That is, in the dryness range of 0 to 0.2, since the proportion of the liquid becomes excessive, liquid compression occurs in the hermetic rotary refrigerant compressor 1, which causes a problem of a lowered reliability as in the prior art. On the other hand, in the range of 0.8 to 1, since the latent heat of the flash gas is small, the discharge gas temperature cannot be effectively lowered. Therefore, it is preferable to set it as 0.2-0.8. The dryness degree is calculated by the control part 14 based on the temperature information of the temperature sensor 12 which detects the temperature of the outdoor heat exchanger 3 which functions as a condenser, and the control part 14 calculates the dryness degree computed. The opening degree of the second expansion valve 8 is adjusted to converge in the above range. Thereby, it becomes possible to reduce discharge temperature more effectively.

<Heating driving>

When heating operation is performed, the four-way valve 2 is switched to the switching position shown by the dotted line in FIG. 1. When the sealed rotary refrigerant compressor 1 is started, the high temperature and high pressure refrigerant is discharged from the sealed rotary refrigerant compressor 1 and flows into the indoor heat exchanger 9 through the four-way valve 2. In the indoor heat exchanger 9, heat is exchanged with indoor air to radiate heat, and the heating is performed. Then, the refrigerant passes through the check valve 4b of the bridge circuit 4 in order to flow into the gas-liquid separator 5, where the refrigerant is separated into the gas phase and the liquid phase.

In normal heating operation, the liquid refrigerant separated by the gas-liquid separator 5 flows into the internal heat exchanger 6 as it is, and is then decompressed from the high pressure to the low pressure by the first expansion valve 7. Then, after passing through the check valve 4c of the bridge circuit 4, exchanging heat with outdoor air in the outdoor heat exchanger 3, and passing through the four-way valve 2 again, the sealed rotary refrigerant compressor 1 It flows into the accumulator 10.

Here, when the discharge temperature of the sealed rotary refrigerant compressor 1 becomes equal to or higher than a predetermined temperature while the heating operation is continued, the control unit 14 opens the second expansion valve 8 as in the cooling operation, A part of the refrigerant after the gas-liquid separator 5 outlet is bypassed to the hermetic rotary refrigerant compressor 1 through the second expansion valve 8 and the internal heat exchanger 6. As a result, a part of the refrigerant exiting the gas-liquid separator 5 is decompressed from the high pressure to the medium pressure in the second expansion valve 8, flows into the internal heat exchanger 6, and enters the internal heat exchanger 6 from the normal circulation flow path. Heat exchange in the internal heat exchanger (6) and the high pressure refrigerant introduced into. As a result, the medium pressure refrigerant which flowed into the internal heat exchanger 6 turns into the flash gas which is a saturated refrigerant state of two gas-liquid phases, and is injected into the sealed rotary refrigerant compressor 1. Also in the case of this heating operation, the flash gas injected into the hermetic rotary refrigerant compressor 1 is preferably 0.2 to 0.8 in the same manner as in the cooling operation.

In the hermetic rotary refrigerant compressor (1), a refrigerant circulating a refrigeration cycle regularly flows in through the accumulator (10) and is compressed at a high temperature and a high pressure in a compression chamber. Will be. Thereby, the discharge temperature of the hermetic rotary refrigerant compressor 1 can be lowered as compared with the case where no flash gas is injected. Control of the discharge temperature can be performed by adjusting the opening degree of the second expansion valve 8 and adjusting the amount of refrigerant to be bypassed from the gas-liquid separator 5 outlet.

3 is a Moliere diagram in which the lateral axis is the enthal ratio h and the vertical axis is the pressure P in the air conditioner of FIG. 1. 3 shows the Moliere diagram in a state where the discharge temperature of the hermetic rotary refrigerant compressor 1 is equal to or higher than the predetermined temperature and the second expansion valve 8 is opened.

The refrigerant in the state (A) on the inlet side of the sealed rotary refrigerant compressor (1) changes to the high pressure (B) state by the sealed rotary refrigerant compressor (1), and then the condensation in the outdoor heat exchanger (3). As a result, entropy decreases with a constant pressure. Then, after passing through the outdoor heat exchanger 3 and before branching to the normal circulation circuit and the injection circuit 40, the state E is reached. The refrigerant passing through the normal circulation circuit flows into the internal heat exchanger 6 via the second expansion valve 8. Here, in the internal heat exchanger 6, since a part of the medium in the state E flows in through the second expansion valve 8, the refrigerant passing through the normal circulation circuit is the second expansion valve 8. By the heat exchange with the medium pressure refrigerant | coolant after passage, the enthal ratio becomes further lower (C). After passing through the first expansion valve 7, the pressure is lowered and the state D is maintained while the enthalpy is constant, and then the enthalpy is increased while the pressure is constant by evaporation in the indoor heat exchanger 9, thereby improving the state ( Becomes A).

On the other hand, a part of the medium of state E passes through the 2nd expansion valve 8, and the pressure falls, it becomes state F, and flows into the internal heat exchanger 6, with enthalpy being constant. Then, the internal heat exchanger 6 exchanges heat with the refrigerant passing through the normal circulation circuit, and the enthalpy ratio rises while the pressure is constant, resulting in a state G. In this state G, that is, the flash gas of two-phase gas-liquid flow is introduced into the hermetic rotary refrigerant compressor 1, the state is changed from the state A to the high pressure state B in the hermetic rotary refrigerant compressor 1 The enthalth ratio of the refrigerant which has been set to (B1) is lowered, and the state (G) is changed from the state (B1). And at the exit of the sealed rotary refrigerant compressor 1, it becomes the state H whose enthal ratio is smaller than the state B. FIG. In other words, the discharge temperature is lowered.

Here, the effect by injecting the flash gas of the gas-liquid two-phase flash gas into the hermetic rotary refrigerant compressor 1 is considered based on FIG. As shown in FIG. 3, the refrigerant in the state E is in the state C by heat-exchanging in the internal heat exchanger 6 with the medium pressure refrigerant after passing through the second expansion valve 8. The change of the enthal ratio between this state E and the state C becomes an increase of driving ability.

Thus, according to Embodiment 1, since the flash gas which is saturated gaseous two-phase saturated refrigerant was injected into the sealed rotary refrigerant compressor 1, the internal temperature of the sealed rotary refrigerant compressor 1 can be reduced, The discharge temperature can be lowered. As a result, the driving ability can be improved as compared with the case where injection injection is not performed.

In addition, since it is possible to prevent deterioration of the motor insulating material of the hermetic rotary refrigerant compressor 1 and to prevent a decrease in the lubricating oil viscosity accompanying the increase in the internal temperature, the sliding point of the compression element portion 23 is prevented. Abrasion of (sliding part, bearing part, etc. in a compression chamber) can be prevented, and it becomes possible to improve reliability.

In addition, since the refrigerant injected into the hermetic rotary refrigerant compressor 1 is a flash gas of two-liquid gas liquid, it is possible to avoid the liquid compression caused by the liquid refrigerant being injected into the hermetic rotary refrigerant compressor 1 as in the prior art. As a result, the reliability of the hermetic rotary refrigerant compressor 1 can be improved, and furthermore, the reliability of the refrigerating device can be improved.

In addition, since the dryness of the flash gas is set to 0.2 to 0.8, it is possible to effectively lower the discharge temperature.

In addition, conventionally, there is a hermetically sealed rotary refrigerant compressor having a liquid injection cycle. However, according to the first embodiment, since a liquid refrigerant having a dryness of 0 is not directly injected into the compression chamber like these, liquid refrigerant compression The problem that a slide point (sliding part in a compression chamber, a bearing part, etc.) is damaged by the excessive pressure which generate | occur | produces can be solved.

Embodiment 2.

In the first embodiment, the timing of injecting the flash gas of the gas-liquid two-phase flash gas into the hermetic rotary refrigerant compressor 1 has not been described in particular. In the second embodiment, an effective injection timing and a specific hermetic rotary type for injecting at the timing are given The refrigerant compressor structure will be described.

First, the specific structure of the hermetic rotary refrigerant compressor 1 will be described below.

4 and 5 are cross-sectional views of the sealed rotary refrigerant compressor 1 of FIG. 1 according to the first embodiment, and a cross-sectional structure inside the compression chamber.

The hermetic rotary refrigerant compressor (1) includes an electric element (21) composed of a stator (21a) and a rotor (21b) in a hermetic container (20), and a rotating shaft integrally mounted with the rotor (21b). The compression element part 23 driven by the crankshaft 38 is provided, and the refrigeration oil (not shown) accommodated in the airtight container 20 is provided. The scroll compression element 23 has a cylinder 24 having a cylindrical opening through which the crankshaft 38 penetrates, and closes the opening of the cylinder 24 from the top and bottom, while bearing the crankshaft 38. The upper bearing 25 and the lower bearing 26 are provided. The space surrounded by the inner circumferential sidewall of the opening of the cylinder 24, the upper bearing 25 and the lower bearing 26 constitutes a compression chamber 27 through which the refrigerant is compressed.

The crank pin 28 is eccentrically formed in the outer periphery of the crankshaft 38, and the roller 29 is fitted to the outer periphery of this crank pin 28. As shown in FIG. And when the crankshaft 38 rotates, the roller 29 will contact in the inner peripheral surface of the compression chamber 27, and will eccentrically rotate and perform a compression action. Moreover, the ben 31 is inserted in the cylinder 24 to the ben groove 30 freely, and the ben 31 abuts on the roller 29, following the movement of the roller 29, and the compression chamber ( 27) The inside is divided into a high pressure space and a low pressure space. In the example of FIG. 5, the chamber on the left side of the compression chamber 27 has a high pressure space, and the chamber on the right side of the ben 31 is a suction space, and the suction port 33 opens in the suction space. have.

In addition, a suction pipe 32 communicating with the accumulator 10 and the compression chamber 27 is connected to the side surface of the sealed rotary refrigerant compressor 1, and is compressed from the suction port 33 through the suction pipe 32. The refrigerant is injected into the suction space of the chamber 27. An injection tube 34 is further connected to the side surface of the sealed rotary refrigerant compressor 1, and the flash gas, which is a saturated gaseous two-phase saturated refrigerant from the injection tube 34, is injected into the compression chamber 27. Is injected into the cavity). Moreover, the discharge pipe 36 which discharges a refrigerant out of the sealed rotary refrigerant compressor 1 is connected to the upper part of the sealed rotary refrigerant compressor 1. In addition, the lower bearing 26 is covered with the discharge muffler 37.

6 (a), 6 (b), 6 (c) and 6 (d) show a compression chamber composed of a cylinder 24, a crankshaft 38, a roller 29 and a ben 31; Is a detailed diagram showing the relationship between the ejection position with the injection hole 35.

6 (a), 6 (b), 6 (c), and 6 (d) respectively show that the rotation angles of the crankshaft 38 are 0 °, 150 °, 180 ° and 270 °, respectively. The cross section of the compression element part 23 seen from the lower bearing 26 side is shown.

As shown in FIG. 6A, in the state where the rotation angle of the crankshaft 38 is 0 °, a low pressure refrigerant is present in the compression chamber 27. And as the crankshaft 38 rotates and its rotation angle becomes large, as shown to FIG. 6 (b)-(d), the pressure of the refrigerant | coolant in the high pressure space of the compression chamber 27 becomes high.

Here, the timing of injecting the flash gas of the gas-liquid two-phase flash into the hermetic rotary refrigerant compressor 1 is preferably set while the refrigerant pressure in the compression chamber reaches a low to medium pressure (medium pressure step). This is because, for example, when the refrigerant pressure in the compression chamber is high, the internal temperature of the compression chamber, and further, the sealed rotary refrigerant compressor 1, is already at a high temperature and the high temperature cannot be prevented. Therefore, it is preferable to inject before it becomes a high temperature and high pressure state. It is also necessary to start the injection of the flash gas while the refrigerant pressure in the compression chamber is lower than the pressure of the flash gas. This is because if the flash gas is to be injected when the refrigerant pressure in the compression chamber is higher than the flash gas pressure, the refrigerant in the compression chamber may flow back toward the injection tube 34.

As a structure for injecting flash gas into the compression chamber at the timing described above, in this embodiment, a straight line A connecting the crankshaft 38 and the ben 31 and a straight line perpendicular to the straight line A. When the inside of the compression chamber 27 is divided into four by (B) (refer FIG. 6 (a)), the area | region which becomes 3rd in order of the rotation direction of the crankshaft 38 (the position of the ben 31 is 0). The injection hole 35 is arrange | positioned in the position which opens and closes with the roller 29 as a rotation angle of the crankshaft 38 at the time of 180 degrees-270 degrees. In addition, the injection hole 35 is disposed at a position not in communication with the ineffective volume space 27a (see FIG. 4) inside the roller 29, so that the flash gas is reliably injected into the compression chamber, and effectively discharged. It is possible to lower the temperature.

By arrange | positioning at such a position, it becomes possible to inject flash gas when the refrigerant | coolant in a compression chamber is low to medium pressure. Referring to the example of Fig. 6, the refrigerant in each of the compression chambers of Figs. 6 (a) to 6 (d) is in a state of low pressure, medium pressure, high pressure, and high pressure, and in the state of Fig. 6 (a), Since the injection hole 35 is open, the flash gas is injected into the compression chamber from the injection hole 35. And even in the state of FIG. 6 (b), since it is still partially open, injection of flash gas is continued. 6C and 6D, the injection hole 35 is completely blocked, and no flash gas is injected into the compression chamber. In addition, the flash gas is not injected into the compression chamber even while the crankshaft 38 further rotates from the position shown in FIG. 6 (d) until the refrigerant becomes higher in pressure and discharged from the compression chamber.

As described above, according to the second embodiment, the same effects as those of the first embodiment can be obtained, and the flash gas of the gas-liquid two-phase flash gas is injected while the medium pressure in the compression chamber reaches from low to medium pressure. The temperature in the compression chamber can be lowered at an effective timing.

In addition, the timing of injection of the flash gas two-phase flash gas is preferably the same as described above, but is not necessarily limited to the timing and structure. For example, the flash gas may be injected into the inlet portion of the coolant from the accumulator 10 in the sealed rotary refrigerant compressor 1 as an example of injecting at another timing. Also in this case, the temperature lowering effect in a compression chamber can be acquired.

Moreover, although each said embodiment mentioned mainly about the closed rotary refrigerant | coolant compressor which has a single stage closed rotary refrigerant | coolant compression mechanism, the same effect can be acquired even if injecting the said flash gas into the compressor of a two-stage compression. .

In the above embodiment, the case where the refrigerating device is applied to the air conditioner has been described as an example, but the present invention can also be applied to a refrigerator or the like.

BRIEF DESCRIPTION OF THE DRAWINGS The figure which shows schematic structure of the refrigeration apparatus of Embodiment 1 of this invention.

2 is a block diagram showing an electrical configuration of the air conditioner of FIG.

3 is a Moliere diagram in a state in which the discharge temperature of the hermetic rotary refrigerant compressor of FIG. 1 is equal to or higher than a predetermined temperature and the second expansion valve is opened.

4 is a cross-sectional view of the sealed rotary refrigerant compressor of FIG.

5 is a cross-sectional view showing the inside of a compression chamber of the hermetic rotary refrigerant compressor of FIG.

FIG. 6 is a detailed view showing the relationship between the excretion position between the compression chamber and the injection hole of the hermetic rotary refrigerant compressor of FIG. 1; FIG.

(Explanation of symbols for the main parts of the drawing)

1: hermetic rotary refrigerant compressor

3: outdoor heat exchanger

4: bridge circuit

4a: check valve

4b: check valve

4c: check valve

4d: check valve

5: gas-liquid separator

6: internal heat exchanger

7: first expansion valve

8: second expansion valve

9: indoor heat exchanger

10: Accumulator

11: discharge temperature sensor

12: temperature sensor

13: temperature sensor

14: control unit

20: airtight container

21: electric element part

21a: stator

21b: rotor

23: compression element

24: cylinder

25: upper bearing

26: lower bearing

27: compression chamber

27a: void volume space

28: crank pin

29: roller

30: Ben home

31: Ben

32: suction pipe

33: suction port

34: injection pipe

35: injection hole

36: discharge tube

37: discharge muffler

38: crankshaft

40: injection circuit

Claims (5)

A refrigeration apparatus using a mixed refrigerant containing at least 60% by mass of R32 or R32 refrigerant as a refrigerant having a compressor, a condenser, a gas-liquid separator, an expansion valve, and an evaporator. And an injection circuit for injecting a part of the refrigerant from the gas-liquid separator outlet into the compressor as a flash gas which is a saturated refrigerant in two-phase gas liquid. A compressor for use in the refrigeration apparatus of claim 1, And the compressor comprises an accumulator on the suction side of the compression element and injects the flash gas into the accumulator inlet. A compressor for use in the refrigeration apparatus of claim 1, The compression element of the compressor includes a compression chamber, a ben freely inserted into and out of a ben groove provided on a side wall of the compression chamber, a crank shaft, and the ben while being in contact with the ben, in the compression chamber along with rotation of the crank shaft. A roller for eccentric rotational movement and contact with the inner peripheral surface to compress the refrigerant, And the position of the ben in the compression chamber is 0 °, and the flash gas is injected at a position between 180 ° and 270 ° of the rotation angle of the crankshaft in the compression chamber. The method of claim 1, And a liquid refrigerant is bypassed by the gas-liquid separator provided at the outlet of the condenser, and the drying of the flash gas is made 0.2 to 0.8 through a throttle, and the flash gas is injected into the compressor. The method of claim 4, wherein An internal heat exchanger is provided on the outlet side of the throttle part.

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