JP2008082214A - Hermetic scroll compressor and refrigeration cycle equipped with the same - Google Patents

Abstract

【Task】
In the refrigeration cycle, leakage of refrigerant gas between the compression chambers is prevented, and re-expansion loss during full power operation is prevented.
[Solution]
The hermetic scroll compressor 30 for the refrigeration cycle includes a fixed scroll 6 in which a wrap is formed on a base plate, and a turning scroll 7 in which a wrap that engages with the wrap of the fixed scroll is formed on the base plate. The fixed scroll and the orbiting scroll are held in the sealed container 1. A capacity control unit 48 is provided for communicating a compression chamber formed inside the fixed scroll with a suction unit of the hermetic scroll compressor. The capacity control unit has a valve body 13 held in communication holes 14 and 15 penetrating from the outer peripheral side of the fixed scroll to a compression chamber formed inside the fixed scroll.
[Selection] Figure 1

Description

  The present invention relates to a hermetic scroll compressor, and more particularly, to a hermetic scroll compressor suitable for a product having a refrigeration cycle such as a heat pump water heater, an air conditioner, and a cold air application product.

  Conventionally, in refrigeration equipment, especially air conditioning equipment, in order to improve overall efficiency, so-called power save operation is performed in which the equipment is operated at full power when the equipment is started up and maintained at the set temperature. is doing. There are various power saving operation methods, such as a method of changing the capacity of the compressor and a method of changing the rotational speed of the compressor. The method of changing the capacity of the compressor is mainly used when the electric motor is operated at a constant speed.

  Examples of compressors used for conventional capacity control are described in Patent Documents 1 and 2. In the scroll compressor described in Patent Document 1, a circular vent hole having a diameter of about the size between laps is formed in the base plate of the fixed scroll. When the power saving operation is performed, the refrigerant gas being compressed is returned to the suction chamber.

  On the other hand, in the scroll described in Patent Document 2, a groove-like gas vent hole having a width smaller than the thickness of the wrap is formed near the side surface of the wrap provided upright on the fixed scroll base plate. When the power saving operation is performed, the refrigerant gas being compressed is returned to the suction chamber.

JP-A-9-170573 JP 2000-161263 A

  However, in the conventional scroll compressor described in Patent Document 1, the bypass flow path is closed with a bypass valve in order to operate at full power when the device is started up. By the way, when closing by using the bypass valve, if the bypass valve is protruded from the fixed scroll base plate, it interferes with the wrap tip of the orbiting scroll. Therefore, it is necessary that the bypass valve does not protrude from the fixed scroll base plate. Therefore, in reality, a slight gap is formed between the tip of the bypass valve and the surface of the fixed scroll base plate. If there is a gap, refrigerant gas between the compression chambers leaks through the gap, resulting in a problem that the performance of the compressor deteriorates.

  In the scroll compressor described in Patent Document 2, in order to eliminate the problem of leakage of compressed gas due to the gap formation of Patent Document 1, a groove having a width smaller than the wrap thickness near the wrap side surface of the fixed scroll base plate Shaped refrigerant gas vent holes are drilled. However, forming this groove increases the processing time. In addition, since a dead volume region that does not contribute to compression is formed in the bypass valve portion, re-expansion loss occurs during full power operation.

  The present invention has been made in view of the above-mentioned problems of the prior art, and an object thereof is to prevent leakage of refrigerant gas between compression chambers and to prevent occurrence of reexpansion loss during full power operation. Another object of the present invention is to achieve the above object with a simple configuration.

  A feature of the present invention that achieves the above object is that it has a fixed scroll in which a wrap is formed on a base plate, and a turning scroll in which a wrap that engages with the wrap of the fixed scroll is formed on the base plate. In the sealed scroll compressor for the refrigeration cycle in which the orbiting scroll is held in the sealed container, a capacity control unit is provided for communicating the compression chamber formed in the fixed scroll with the suction portion of the sealed scroll compressor, In this capacity control unit, a communication hole penetrating from the outer peripheral side of the fixed scroll to the compression chamber formed inside the fixed scroll is formed in the side surface portion of the wrap of the fixed scroll, and the valve body is held in this communication hole. It is in.

  In this feature, the capacity control unit has a pipe attached to the fixed scroll, and it is preferable to provide means for selectively supplying the discharge gas and the suction gas of the hermetic scroll compressor to the pipe. Further, when the orbiting scroll is turned, the orbiting scroll and the fixed scroll are formed so that the compression is started from the compression chamber formed by the outer peripheral surface of the outermost peripheral portion of the orbiting scroll and the inner peripheral surface of the outermost peripheral portion of the fixed scroll. It is good to do. Furthermore, a driving means for electrically driving the valve body may be provided, and the working gas may be an HFC refrigerant or an R744 refrigerant. A groove extending in the circumferential direction communicating with the suction chamber of the scroll compressor may be formed in the flow rate control unit, and the valve body may be movable across the groove.

  Another feature of the present invention that achieves the above object is to provide a control means that is equipped with any of the above-mentioned hermetic scroll compressors and enables both capacity control and rotational speed control for this hermetic scroll compressor. The refrigeration cycle has.

  According to the present invention, in the compressor capable of capacity control operation, the refrigerant gas being compressed is returned to the suction space from the bypass passage provided on the inner wall surface of the fixed scroll, so that the refrigerant between the compression chambers partitioned by the wrap of the orbiting scroll Gas leakage can be prevented. In addition, a sufficient area of the refrigerant gas channel can be secured. Furthermore, since one communication hole for accommodating the valve body that can be opened and closed is formed and communicated with the suction space, the number of processing steps can be reduced. Moreover, the dead volume which does not contribute to the compression which arises at the front-end | tip part of a valve body at the time of full power operation can be reduced, and the loss which the gas of the part which does not contribute to these compressors re-expands can be suppressed.

  The use of compressors with capacity control is mainly used from the viewpoint of improving energy efficiency in air conditioning equipment. The reason for this is that a constant speed electric motor can output full power promptly at startup. In addition, when the transition from the transient operation to the stable operation is shifted to the stable operation, it is possible to perform the power saving operation that is the capacity control operation, and in that case, higher efficiency is obtained than when the intermittent operation is performed at full power. In addition, since the heating operation requires a larger refrigeration capacity than the cooling operation, the capacity control is also convenient in this respect. That is, full power operation may be performed during heating operation, and power save operation may be performed during cooling operation.

  On the other hand, in recent years, an air conditioner that uses a DC motor as an electric motor that drives a compressor of the air conditioner and can control the rotation speed has been used. This is because variable speed motors can be used relatively inexpensively. By the way, in the positive displacement compressor used for the air conditioner, the efficiency is remarkably lowered unless it is within a predetermined rotational speed range. Due to the increasing demand for energy saving, this predetermined rotational speed range is expanding, especially on the small capacity operation range side.

When the rotational speed range of the compressor is expanded to the low rotational speed side, for example, the rotational speed of the electric motor is 500.
When it is reduced to about min ⁻¹ , the motor efficiency is significantly reduced. At the same time, the ratio of the leakage loss of the compressor increases, and the compressor efficiency is greatly reduced. As a result, even if the refrigerant circulation rate is reduced to improve the efficiency of the refrigeration cycle, the efficiency improvement is offset by the reduction in motor efficiency and compressor efficiency, and the air conditioning equipment cannot be saved. Therefore, the overall efficiency can be improved by controlling the pump capacity of the compressor, for example, by setting the amount of seizure to 50% and the number of revolutions of the motor to 1000 min ⁻¹ .

In a device having a refrigeration cycle other than an air conditioner, for example, a heat pump hot water supply device using an R744 (CO ₂ ) refrigerant, the hot water supply capacity in the case of the instantaneous type is 20 kW or more. However, in an operation in which hot water is circulated using this hot water supply apparatus as floor heating, a hot water supply of about 2 kW is sufficient. Even during operations such as floor heating that require only a low capacity, if the compressor is capacity-controlled and the amount of seizure is reduced to maintain the motor rotation speed at a predetermined rotation speed or higher, the overall equipment can save energy. can get.

  An example of a device having a refrigeration cycle in which the rotation speed of the compressor is set to a predetermined rotation speed or more and the capacity of the compressor is controlled will be described below with reference to the drawings. FIG. 1 is a diagram of an embodiment of a refrigeration cycle 50 according to the present invention, in which a scroll compressor is used as the compressor 30. In FIG. 1, the scroll compressor 30 is shown in a longitudinal sectional view. 1 represents the flow of the refrigerant gas in the refrigeration cycle 50. In addition, an HFC refrigerant is used as the refrigerant.

  The scroll compressor 30 is a capacity-controlled compressor formed on the vertical axis, and a compression mechanism portion is accommodated in the upper portion of the metal hermetic container 1 and an electric motor portion is accommodated in the lower portion. The compression mechanism section includes a fixed scroll 6 in which a spiral wrap 6a is erected on a base plate, and a turning scroll 7 in which a wrap 7a that forms a compression chamber together with the wrap 6a of the fixed scroll 6 is erected on the base plate. Have The frame 5 is arranged so as to hold the fixed scroll 6. The orbiting scroll 7 is driven by the crankshaft 4 via the Oldham ring 16. A suction pipe 9 and a discharge pipe 10 communicating with the outside of the compressor are hermetically connected to the sealed container 1. These constitute a compressor section.

An outer peripheral portion of the frame 5 is fixed to the sealed container 1, and a bearing for rotating and supporting the crankshaft 4 is held by the frame 5. A fixed scroll 6 is fastened to the frame 5 with bolts 8. A turning scroll 7 is rotatably attached to the eccentric part of the crankshaft 4. Projections (not shown) formed on the Oldham ring 16 are slidably disposed in the grooves formed on the frame 5 and the grooves formed on the opposite side of the orbiting scroll 7. By the Oldham ring 16, the orbiting scroll 7 revolves without rotating.

  A discharge hole 22 for guiding the refrigerant compressed in the compression chamber into the hermetic container 1 from the compression chamber is formed in a substantially central portion of the fixed scroll 6. Communication holes 14 and 15, which will be described in detail later, are formed from the outer peripheral surface of the fixed scroll 6 to the inner peripheral surface of the compression chamber formed by the wrap of the fixed scroll 6 and the wrap of the orbiting scroll 7. The communication holes 14 and 15 pass through a groove 23 formed from the suction portion 21 to the suction chamber 45. A valve body 13 for opening and closing the communication hole 15 formed on the inner peripheral side is inserted into the communication hole 14 formed on the outer peripheral side. A stopper 12 is also press-fitted into the communication hole 14, and a pipe 11 that guides the refrigerant from the outside of the compressor 30 is press-fitted into the stopper 12.

  The electric motor unit includes a stator 2 held in the sealed container 1 by shrink fitting or the like, and a rotor 3 disposed on the inner peripheral side of the stator 2 with a slight gap in the radial direction. The rotor 3 is fixed to the crankshaft 4 of the compressor portion by press fitting or the like. The crankshaft 4 extends downward through the rotor 3, and the lowermost end reaches the oil reservoir formed in the sealed container 1.

The scroll compressor 30 configured in this manner is connected to the three-way valve 20, the evaporator 19, the pressure reducing valve 18, and the condenser 17 in order by piping, thereby constituting a refrigeration cycle 50. The flow of the refrigerant gas in the refrigeration cycle 50 will be described below. The refrigerant gas sucked from the suction pipe 9 is compressed in the compression chamber of the compressor 30 and is discharged into the sealed container 1 from the discharge hole 22 formed in the fixed scroll 6. Then, it is led out of the compressor 30 through the discharge pipe 10. The refrigerant gas guided outside the compressor 30 is radiated and liquefied by a condenser (a water / refrigerant heat exchanger in the case of a heat pump type hot water heater) 17, and then depressurized by a pressure reducing valve 18. The low-temperature and low-pressure refrigerant is evaporated by the evaporator 19 and absorbs heat. The evaporated refrigerant gas is again sucked into the compressor 30 from the suction pipe 9. Thereafter, the refrigerant circulates in the refrigeration cycle 50 which is this closed cycle.

In the refrigeration cycle 50, the pipe 25a from the evaporator 19 to the compressor 30 is branched in the middle. Via the three-way valve 20, a pipe 25 d that communicates with the pipe 11 of the compressor 30 and a pipe 25 c that communicates with the condenser 17 are connected to the branch pipe 25 b. A control device (not shown) controls the three-way valve 20 so that suction pressure or discharge pressure can be applied to the pipe 11.

  The operation of the valve body 13 during capacity control will be described using the longitudinal sectional view of the capacity control unit of the scroll compressor 30 shown in FIGS. 2 and 3. FIG. 2 shows a state in which the suction pressure is applied to the pipe 11. The communication hole 14 formed on the outer peripheral side of the fixed scroll 6 is a stepped hole, and the large diameter portion acts as a guide for the valve body 13 to move in the left-right direction in FIG. The small diameter portion of the communication hole 14 forms a sealing portion together with the valve body 13.

The pipe 11 has a tip projecting into the sealed container 1, and a stopper 12 is fixed to the projecting portion. The stopper 12 is fixed and held at the end of the communication hole 14 of the fixed scroll 6. The valve body 13 is a two-stage stepped member, and a concave portion is formed on the large diameter side to avoid interference with the tip of the pipe 11. The peripheral surface of the large diameter portion of the stopper 12 is a moving surface of the stopper 12, and the medium diameter portion is a sealing portion of the groove 23. The small diameter portion of the stopper 12 is a sealing portion that seals the groove 23 and the compression chamber formed on the inner peripheral side of the fixed scroll 6. The communication hole 15 on the inner side also has a stepped shape, and the stepped portion acts as a stopper for the valve body 13.

  When the suction pressure acts on the pipe 11 by switching the three-way valve 20, the valve body 13 moves to the stopper 12 side (left side in the figure) with the large diameter portion as a guide, and its movement is restricted by the stopper 12 and stopped. As a result, although the communication hole 14 is sealed by the middle diameter portion of the valve body 13, the communication hole 15 is opened and communicates with the groove 23. In this state, the refrigerant gas in the chamber on the outermost peripheral side of the compression chamber is bypassed by the suction portion 21 formed at a position that is substantially the same radial position as the communication holes 14 and 15 and has a different phase (FIG. 4). See), not compressed. This is power saving operation.

  On the other hand, the three-way valve 20 is switched, and the refrigerant discharged from the scroll compressor 30 is applied to the pipe 11. This state is shown in FIG. When the discharge pressure of the compressor 30 acts on the valve body 13, the valve body 13 moves to the communication hole 15 side (right side in the figure) with the large diameter portion as a guide. Then, the stepped portion of the communication hole 15 formed in the fixed scroll 6 is stopped as a stopper. In this state, both the communication holes 14 and 15 are sealed by the valve body 13. The communication hole 15 and the groove 23 are blocked. This is the same situation as a normal compression process and is a full power operation.

  FIG. 4 is a cross-sectional view showing the positional relationship between the orbiting scroll 7 and the fixed scroll 6 when the scroll compressor 30 is in a power saving operation. The base material of the fixed scroll 6 is processed by a mill or the like, and a spiral wrap 6a is formed on the fixed scroll 6 with the vicinity of the suction portion 21 as a start point or an end point. Further, a groove-like suction chamber 45 that is long in the circumferential direction is formed in the vicinity of the suction portion 21. The suction chamber 45 is formed deeper as the cutting depth becomes closer to the suction portion 21, and alleviates the sudden change of the gas guided from the suction portion 21 in the flow direction. Continuing from the suction chamber 45, the above-described groove 23 extends in the circumferential direction beyond the capacity controller 48.

  The communication holes 14 and 15 are formed at the end of the groove 23 on the side opposite to the suction chamber 45. In FIG. 4, the capacity control unit 48 in which the communication holes 14 and 15 are formed is shown in a partial cross section. A circumferential groove 46 is formed on the outer peripheral side of the wrap portion of the fixed scroll 6, and bolt holes 47 for fixing the fixed scroll 6 to the frame 5 are spaced in the circumferential direction further on the outer peripheral portion of the circumferential groove 46. A plurality are formed. In the fixed scroll 6 shown in FIG. 4, the part other than the part where the groove is formed corresponds to the surface 43 of FIG.

  On the other hand, the orbiting scroll 7 rotates eccentrically with respect to the fixed scroll 6 without rotating. The state of eccentric rotation of the orbiting scroll 7 is shown in FIGS. FIG. 6A shows a case where the orbiting scroll 7 is closest to the fixed scroll 6 in the q direction, and is the starting point of the orbit. Then, the turning is advanced by approximately 180 °, and the case where the turning scroll 7 is farthest from the fixed scroll in the q direction is shown in FIG. Further, when the turning of the turning scroll 7 is advanced, the case where the turning scroll 7 is closest to the fixed scroll in the p direction is shown in FIG. FIG. 4 shows a so-called asymmetric scroll.

  In the asymmetric scroll, two compression chambers 44 a and 44 b having different sizes are formed inside and outside the wrap 7 a of the orbiting scroll 7. At the starting point of the turning (the state shown in FIG. 4A), a space 45a that will become the compression chamber 44c in the future is formed on the suction chamber 45 side, and the wrap 7a of the turning scroll 7 with the suction chamber 45 as one end side. Extends from the outermost end to the inner peripheral surface. In this state, the space 45a is open on the suction chamber 45 side.

  One compression chamber 44a is in a state where the space communicating with the suction chamber 45 is just confined by the wrap 7a at the outermost peripheral end of the orbiting scroll 7 at the starting point of the orbiting to form a compression chamber. The compression chamber 44 a extends in the circumferential direction from the outer peripheral portion near the outermost end of the wrap 7 a of the orbiting scroll 7 to a little less than one turn of the wrap 7 a, and the end reaches the capacity control unit 48. The other compression chamber 44b is formed by a wrap 7a inside the orbiting scroll 7, and continues compression as a closed space.

In the state where the compression chamber 44a has just been formed, the gas in the compression chamber 44a is almost at the pressure sucked from the suction portion 21 because the compression process has hardly progressed. On the other hand, since the gas in the compression chamber 44b has been compressed to some extent, the gas is higher in pressure than when sucked from the suction portion 21. When the turning of the orbiting scroll 7 proceeds, the pressure acting on the communication hole 15 from the compression chamber 44a side becomes higher than the pressure of the suction portion 21 and the gas from the evaporator 19 which is the same as the suction portion 21 is guided to the pipe 11. For example, since these two pressure differences act on the valve body 13, the valve body 13 moves to the pipe 11 side. And the compression chamber 44a and the groove | channel 23 connected to the suction part 21 are connected. As a result, the pressure in the compression chamber 44a decreases, and power save operation is performed. FIG. 4A shows a state in which the compression chamber 44a starts to communicate with the groove 23. FIG.

  FIG. 4B shows a state in which the compression chamber 44a advances the compression process as it rotates and the communication with the groove 23 is still continued. In this case, the pressure in the compression chamber 44a is almost the suction pressure. On the other hand, the space 45a has changed from an open state to a new compression chamber 44c closed. In FIG. 4 (c), where the rotation has further progressed, the compression chamber 44a is no longer in communication with the groove 23 and becomes a sealed space, and the compression process proceeds. The compression chamber 44c advances the compression process while still being a sealed space, and plays the role of the compression chamber 44b in FIG. A space 45b to be a future compression chamber 44a is formed outside the outermost peripheral wrap 7a of the orbiting scroll 7. Thereafter, the steps of FIGS. 4A to 4C are repeated.

Here, in order to perform the power save operation, the compression chamber 44 c communicates with the suction side by the capacity control unit 48 as shown in FIG. Of the compression chamber 44a and the compression chamber 44c, the compression chamber 44a has a volume of about 30% larger at the time of starting compression. That is, two compression chambers 44a,
If the size of the compression chamber 44c is 1, the total capacity of 44c is 2.3 because the size of the compression chamber 44a is 1.3. If the capacity of 1.3 changes to the suction pressure, The capacity control rate is 1.3 / 2.3 = 0.56, and the capacity can be controlled as much as about 60%. Note that the capacity control rate can be changed by changing the circumferential position of the capacity control unit 48 and changing the relative position of the fixed scroll 6 to the lap 6a. That is, if the communication start position with the suction part 21 is changed, the capacity control rate also changes.

  FIG. 5 shows an example of a so-called symmetrical scroll in which the compression chambers 44d and 44e having the same volume are formed by shifting the phase by 180 degrees. Similar to the embodiment of FIG. 4, the capacity control unit 48 is provided on the side of the suction unit 21 opposite to the suction chamber 25. Fig.5 (a) is a figure corresponding to FIG.4 (b), and is a state at the time of the communication start with the suction side by a power saving driving | operation. FIG.5 (b) is a figure corresponding to FIG.4 (c), and is the time of completion | finish of communication with the suction side. The compression chamber 44d has the same shape as the asymmetric scroll, and the relative positional relationship with the fixed scroll wrap 6a of the capacity controller 48 is the same.

Therefore, if the scroll compressor has the same diameter and the same wrap height, the capacity controlled by the capacity control unit is the same as that of the embodiment shown in FIG. On the other hand, the capacity of the compression chamber 44d is increased on the side opposite to the suction chamber 45 in accordance with the capacity of the compression chamber 44e. FIG. 5A to FIG.
Before reaching (b), the orbiting scroll 7 has orbited about 120 degrees. The amount that can be controlled during the turning of about 120 ° is about 1/3 of the capacity of the compression chamber 44d. Therefore, the maximum capacity control rate in this case is about (1/3) / (1 + 1) = 16.7%. Also in the present embodiment, the capacity control rate can be changed by changing the circumferential position of the capacity controller 48 to change the relative position with respect to the fixed scroll wrap 6a.

  An example of an instantaneous heat pump water heater capable of floor heating using the refrigeration cycle shown in the above embodiment is shown in FIG. Since the refrigeration cycle 50 of the heat pump water heater 80 uses carbon dioxide (R744) as a refrigerant, water refrigerant heat exchangers 32 and 35 are used instead of the condenser 17. A three-way valve 31 is provided on the discharge side of the compressor 30 to switch between use of a water-refrigerant heat exchanger 32 for hot water supply and a water-refrigerant heat exchanger 35 for floor heating. The water-refrigerant heat exchanger 32 for hot water supply includes a plurality of water-side pipes, one of which is used for hot water supply of the tank 42 and the other of which is used for hot water supply of the bath 41.

  Hereinafter, the case of floor heating will be described in detail. The refrigerant compressed by the compressor 30 is guided to the water refrigerant heat exchanger 35 through the three-way valve 31. The refrigerant whose temperature has decreased due to heat exchange in the water refrigerant heat exchanger 35 is guided to the evaporator 19 through the check valve 36 and the pressure reducing valve 18. The evaporator 19 is provided with an outdoor fan 19b that promotes heat exchange with the atmosphere. In addition, when the evaporator 19 is frosted, a hot gas bypass circuit is branched from the discharge side of the compressor in order to flow the defrosting hot gas to the evaporator 19, and this hot gas bypass is provided. A two-way valve 38 is provided in the circuit.

  A pump 37 is provided in the water piping of the water refrigerant heat exchanger 35, and hot water that has been heat exchanged by the water refrigerant heat exchanger 35 is supplied to the floor heating panel 34. The floor heating panel 34 is provided with a floor heating remote controller 33, and a command from the remote controller 33 is input to the cycle control device 39. The cycle control device 39 controls the compressor 30 and the like.

  Here, a pipe branched from the suction side and the discharge side of the compressor 30 is connected to the three-way valve 20. The three-way valve 20 is connected to the capacity control unit 48 of the scroll compressor 30. Generally, in the heat pump water heater 80, the amount of heat required for floor heating is extremely small compared to the amount of heat required for tank hot water or bath hot water. For example, the amount of heat required for hot water supply is about 20 kW, while it is about 2 kW for floor heating.

  Thus, when the required heat quantity becomes 1/10, the efficiency of the compressor and the motor cannot be significantly reduced by simply controlling the rotation speed of the compressor, so that it does not become a so-called environmentally friendly device. According to the present embodiment, since the compressor can be operated in a power saving manner, the efficiency reduction of the compressor and the electric motor can be suppressed as much as possible, and it is economical.

  In the above embodiments, the valve body 13 is opened and closed by the pressure of the refrigerant gas. However, the valve body 13 may be opened and closed in synchronization with the three-way valve 20. In this case, the valve body 13 can be opened and closed more reliably. In addition, in the refrigeration cycle equipped with the compressor, by controlling both the capacity and the rotational speed of the compressor according to the operating conditions, various losses such as fluid loss, mechanical loss, motor loss, etc. can be reduced. Can improve the overall efficiency.

The longitudinal cross-sectional view of one Example of the scroll compressor based on this invention. The longitudinal cross-sectional view which shows the detail of the capacity | capacitance control part of the scroll compressor shown in FIG. The longitudinal cross-sectional view which shows the detail of the capacity | capacitance control part of the scroll compressor shown in FIG. The cross-sectional view in the figure explaining operation | movement of a scroll compressor. The cross-sectional view of another embodiment of the scroll compressor according to the present invention. 1 is a system diagram of an embodiment of an instantaneous heat pump water heater having a refrigeration cycle according to the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Stator 3 Rotor 4 Crankshaft 5 Frame 6, 6a Fixed scroll 7 Orbiting scroll 8 Bolt 9 Suction pipe 10 Discharge pipe 11 Pipe 12 Stopper 13 Valve body 14,15 Communication hole 16 Oldham ring 17 Condenser 18 Pressure reducing valve 19 Evaporator 20 Three-way valve 21 Suction part 22 Discharge hole 23 Groove 30 Scroll compressors 44a-44e Compression chamber 45 Suction chambers 45a, 45b Space 48 Capacity control unit 50 Refrigeration cycle 80 Heat pump water heater

Claims (7)

  A fixed scroll having a wrap formed on the base plate and a orbiting scroll having a wrap engaging with the wrap of the fixed scroll formed on the base plate, and the fixed scroll and the orbiting scroll are held in a sealed container. In the hermetic scroll compressor for the refrigeration cycle, a capacity control unit is provided for communicating the compression chamber formed in the fixed scroll with the suction part of the hermetic scroll compressor. A hermetic scroll compressor characterized in that a communication hole penetrating through a compression chamber formed inside the fixed scroll is formed in a side surface portion of the wrap of the fixed scroll, and a valve body is held in the communication hole.   The said capacity | capacitance control part has a pipe attached to the said fixed scroll, and provided with the means to selectively supply the discharge gas and suction gas of a hermetic scroll compressor to this pipe. Hermetic scroll compressor.   When the orbiting scroll is orbited, the orbiting scroll and the fixed scroll are fixed so that compression starts from a compression chamber formed by the outer peripheral surface of the outermost peripheral portion of the orbiting scroll and the inner peripheral surface of the outermost peripheral portion of the fixed scroll. The hermetic scroll according to claim 1, wherein a scroll is formed.   The hermetic scroll compressor according to claim 1, further comprising a driving unit that electrically drives the valve body.   The hermetic scroll compressor according to claim 1, wherein the working gas is an HFC refrigerant or an R744 refrigerant.   2. A groove extending in a circumferential direction communicating with a suction chamber of the scroll compressor is formed in the flow control unit, and the valve body is movable across the groove. Hermetic compressor. A hermetic scroll compressor according to any one of claims 1 to 5 is mounted, and a control means that enables both capacity control and rotational speed control is provided for the hermetic scroll compressor. A refrigeration cycle characterized by that.

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