KR20140092803A - Refrigeration cycle apparatus and air conditioner provided with same - Google Patents

Refrigeration cycle apparatus and air conditioner provided with same Download PDF

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Publication number
KR20140092803A
KR20140092803A KR1020147005247A KR20147005247A KR20140092803A KR 20140092803 A KR20140092803 A KR 20140092803A KR 1020147005247 A KR1020147005247 A KR 1020147005247A KR 20147005247 A KR20147005247 A KR 20147005247A KR 20140092803 A KR20140092803 A KR 20140092803A
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KR
South Korea
Prior art keywords
heat exchanger
compressor
refrigerant
way valve
refrigeration cycle
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Application number
KR1020147005247A
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Korean (ko)
Inventor
노리아키 야마모토
히로카즈 가모다
도미유키 노마
마사오 이누이
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파나소닉 주식회사
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Publication of KR20140092803A publication Critical patent/KR20140092803A/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
    • F25B2313/0211—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during defrosting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02731—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one three-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor

Abstract

A pipe 25 for directing the refrigerant from the four-way valve 8 to the suction pipe of the compressor 6, a pipe 25 for supplying refrigerant from the four-way valve 8 to the suction pipe of the compressor 6, Way valve (switching device) that allows the refrigerant to be switched to the piping 38 through which the refrigerant passes through the heat exchanger (the heat storage tank 32, the heat storage exchanger 34, and the heat storage material 36) (First heat exchanger) 16 and an outdoor heat exchanger (second heat exchanger) 14, and controls the three-way valve (switching device) 42 in the defrosting operation, (Heat storage tank 32, heat storage exchanger 34, and heat storage material 36) through the four-way valve 8, and is led to the suction pipe of the compressor 6. [

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a refrigeration cycle apparatus and an air conditioner having the same,

The present invention relates to a refrigeration cycle apparatus and an air conditioner provided with a mechanism for switching between a path through which a frost-melted refrigerant adhered to an evaporator flows directly to a compressor and a path through which the refrigerant flows to a compressor through an auxiliary heat exchanger for heating the refrigerant .

Conventionally, when the heat pump type air conditioner is frosted in the outdoor heat exchanger during the heating operation, the four-way valve is switched from the heating cycle to the cooling cycle to perform defrosting. In this defrosting system, the indoor fan is stopped, but cold air is gradually released from the indoor unit.

Therefore, it has been proposed to provide a heat storage tank that uses a compressor provided in an outdoor unit as a heat source, and to defrost by using the waste heat of the compressor that is stored in the heat storage tank during heating operation (for example, see Patent Documents 1 and 2).

Fig. 6 shows an example of a conventional refrigeration cycle apparatus according to Patent Document 1. The compressor 100, the four-way valve 102, the outdoor heat exchanger 104, and the capillary tube 106, which are provided in the outdoor unit, A first bypass circuit 110 for connecting the indoor heat exchanger 108 provided in the indoor unit with a refrigerant pipe and for bypassing the capillary tube 106, And the other end of which is connected to a piping that reaches the outdoor heat exchanger 104 from the capillary tube 106. The second bypass circuit 112 is connected to the outdoor heat exchanger 104 via a pipe line. The first bypass circuit 110 is provided with an anisotropic valve 114 and a check valve 116 and a regenerative heat exchanger 118. The second bypass circuit 112 is provided with an anisotropic valve 120, (Not shown).

A heat storage tank 124 is provided around the compressor 100 and a latent heat storage material 126 for heat exchange with the heat storage heat exchanger 118 is filled in the interior of the heat storage tank 124.

During the defrosting operation, the two anisotropic valves 114 and 120 are controlled to open. A part of the refrigerant discharged from the compressor 100 flows to the second bypass circuit 112, and the remaining refrigerant Way valve (102) and the indoor heat exchanger (108). Further, after the refrigerant flowing through the indoor heat exchanger 108 is used for heating, some refrigerant flows to the outdoor heat exchanger 104 through the capillary tube 106. On the other hand, most of the remaining refrigerant flows into the first bypass circuit 110, passes through the anisotropic valve 114 and flows into the heat storage heat exchanger 118 to take heat from the heat storage material 126, , Flows into the outdoor heat exchanger (104) while joining with the refrigerant passing through the capillary tube (106). Thereafter, the refrigerant is merged with the refrigerant flowing through the second bypass circuit 112 at the inlet of the outdoor heat exchanger 104, defrosting is performed using the heat of the refrigerant, the refrigerant passes through the four-way valve 102, (Not shown).

In this refrigeration cycle apparatus, the second bypass circuit 112 is provided to lead the hot gas discharged from the compressor 100 to the outdoor heat exchanger 104 while the outdoor heat exchanger 104 The defrosting capability is improved by keeping the pressure of the refrigerant flowing high.

Fig. 7 shows a configuration of a conventional air conditioner in Patent Document 2. Such an air conditioner is composed of an outdoor unit 2 and an indoor unit 4 connected to each other by a refrigerant pipe. A compressor 6, a four-way valve 8, a strainer 10, an expansion valve 12 and an outdoor heat exchanger 14 are provided in the outdoor unit 2, And these are connected to each other via a refrigerant pipe, thereby constituting a refrigeration cycle.

The compressor 6 and the indoor heat exchanger 16 are connected to each other through a first pipe 18 provided with a four-way valve 8. The indoor heat exchanger 16 and the expansion valve 12 are connected to each other through a strainer 10 And is connected via a second pipe 20 provided. The expansion valve 12 and the outdoor heat exchanger 14 are connected via a third pipe 22 and the outdoor heat exchanger 14 and the compressor 6 are connected via a fourth pipe 24.

A four-way valve 8 is disposed at an intermediate portion of the fourth pipe 24 and an accumulator (not shown) for separating the liquid refrigerant and the gaseous refrigerant from the fourth pipe 24 at the refrigerant suction side of the compressor 6 26 are provided. The compressor 6 and the third pipe 22 are connected to each other through a fifth pipe 28 and the fifth pipe 28 is provided with a first solenoid valve 30. The fifth pipe 28 and the first electromagnetic valve 30 constitute a discharge gas bypass mechanism.

A heat storage tank 32 is provided around the compressor 6 and a heat storage heat exchanger 34 is provided in the heat storage tank 32. A heat storage material 36 for heat exchange with the heat storage heat exchanger 34 And the heat storage tank 32, the heat storage heat exchanger 34, and the heat storage material 36 form an auxiliary heat exchanger.

The second pipe 20 and the regenerative heat exchanger 34 are connected via a sixth pipe 38. The regenerative heat exchanger 34 and the fourth pipe 24 are connected via a seventh pipe 40 And the sixth solenoid valve 31 is provided in the sixth pipe 38. [

An indoor heat exchanger 16 is provided in the indoor unit 4 and the indoor heat exchanger 16 is connected to the indoor air sucked into the indoor unit 4 by an air blowing fan 16, and heats the air heated by heat exchange to the room while exchanging heat with the refrigerant flowing through the inside of the room.

In the conventional air conditioner configured as described above, the mutual connection relations and functions of the components will be described together with the flow of the refrigerant, for example, during the heating operation.

The refrigerant discharged from the discharge port of the compressor (6) passes through the first pipe (18) and reaches the indoor heat exchanger (16) from the four - way valve (8). The refrigerant condensed by heat exchange with the indoor air in the indoor heat exchanger 16 flows through the indoor heat exchanger 16 and passes through the second pipe 20 and is supplied to the strainer 10 for preventing foreign matter from entering the expansion valve 12 And reaches the expansion valve 12. [ The refrigerant decompressed in the expansion valve 12 passes through the third pipe 22 and reaches the outdoor heat exchanger 14. The refrigerant evaporated by heat exchange with the outdoor air in the outdoor heat exchanger 14 flows through the fourth pipe 24, the four-way valve 8 and the accumulator 26, and returns to the suction port of the compressor 6.

The fifth piping 28 branched from the discharge port of the compressor 6 of the first piping 18 and the four-way valve 8 is connected to the third piping 22 via the first electromagnetic valve 30, The heat accumulating tank 32 which houses the heat accumulating material 36 and the regenerative heat exchanger 34 therein is disposed so as to be in contact with the compressor 6 so as to be surrounded by the expansion valve 12 and the outdoor heat exchanger 14 And the heat generated in the compressor 6 is accumulated in the heat storage material 36. The sixth piping 38 branched from the second piping 20 between the indoor heat exchanger 16 and the strainer 10 passes through the second solenoid valve 31 to the inlet of the heat storage heat exchanger 34 And the seventh pipe 40 emerging from the outlet of the heat storage heat exchanger 34 joins the four-way valve 8 and the accumulator 26 in the fourth pipe 24.

During the normal heating operation, the first electromagnetic valve 30 and the second electromagnetic valve 31 are controlled to be closed, and no refrigerant flows through the refrigerant circuit.

Next, the operation during defrosting and heating and the flow of the refrigerant will be described.

When the concealed frost grows on the outdoor heat exchanger 14 during the above-described normal heating operation, the ventilation resistance of the outdoor heat exchanger 14 increases to decrease the air volume, and the evaporation temperature in the outdoor heat exchanger 14 becomes . When it is detected by the temperature sensor (not shown) that detects the piping temperature of the outdoor heat exchanger 14 that the evaporation temperature has lowered compared with the case of no impregnation, the control device performs the defrosting / heating operation Quot;

The first solenoid valve 30 and the second solenoid valve 31 are opened and controlled so that the refrigerant flowing through the compressor 6 in addition to the flow of the refrigerant during the normal heating operation A part of the gaseous refrigerant discharged from the discharge port passes through the fifth piping 28 and the first electromagnetic valve 30 and joins the refrigerant passing through the third piping 22 to heat the outdoor heat exchanger 14, Is condensed and liquefied and then returned to the inlet of the compressor (6) through the fourth pipe (24) and the four-way valve (8) and the accumulator (26).

A part of the liquid refrigerant classified between the indoor heat exchanger 16 and the strainer 10 in the second piping 20 passes through the sixth piping 38 and the second solenoid valve 31, Heat is absorbed from the heat storage material 36 in the heat storage heat exchanger 34 to evaporate and vaporize and joins the refrigerant passing through the fourth piping 24 through the seventh piping 40 to be discharged from the accumulator 26 to the compressor 6).

The temperature of the outdoor heat exchanger 14 below the freezing point due to the attachment of the frost at the start of the defrosting and heating is heated by the gaseous refrigerant discharged from the discharge port of the compressor 6 and the frost melts near the zero point, The temperature of the outdoor heat exchanger 14 starts to rise again. When the temperature rise of the outdoor heat exchanger 14 is detected by a temperature sensor (not shown), it is determined that the defrosting is completed, and the control device outputs an instruction from the defrosting / heating operation to the normal heating operation.

Japanese Patent Application Laid-Open No. 1991-31666 Japanese Patent No. 4666111

However, in the above-described conventional configuration, when the amount of heat of the heat source is small, it is necessary to introduce most of the hot gas discharged from the compressor to the outdoor heat exchanger, and accordingly, the pressure of the indoor heat exchanger lowers, There has been a problem of deteriorating the comfort. In a case where the refrigerant flows through the indoor heat exchanger and then leads to the outdoor heat exchanger via the heat storage tank or the refrigerant flows through the outdoor heat exchanger and is delivered to the outdoor heat exchanger and the heat storage tank for delivery , The temperature of the refrigerant flowing through the heat storage tank becomes high, the heat absorption from the heat storage tank becomes insufficient, and there is a problem that defrosting takes time if the capacity of the indoor unit is secured.

An object of the present invention is to provide an air conditioner which can shorten the defrosting time and which is provided with the refrigeration cycle device to improve the comfort in the heating operation.

In order to achieve the above object,

A compressor,

A first heat exchanger connected to the compressor,

An expansion valve connected to the first heat exchanger,

A second heat exchanger connected to the expansion valve,

A four-way valve to which the second heat exchanger and the compressor are connected,

An auxiliary heat exchanger for heating the refrigerant disposed around the compressor,

The switching of the refrigerant flow from the four-way valve to the suction pipe of the compressor directly between the suction pipe of the compressor and the four-way valve and the refrigerant flow from the four-way valve through the auxiliary heat exchanger to the suction pipe of the compressor A switching device,

Wherein the refrigerant flowing through the first heat exchanger and the second heat exchanger flows through the auxiliary heat exchanger through the four-way valve while the defrosting device is operated to defrost the frost attached to the second heat exchanger, To the suction pipe of the engine.

According to the present invention, in the defrosting operation, since the refrigerant passing through the first heat exchanger and the second heat exchanger passes through the auxiliary heat exchanger, the first heat exchanger can be kept at a high temperature and the auxiliary heat exchanger can be set at a low temperature. Therefore, by quickly performing the heat absorption from the heat source, the defrosting time can be shortened, and the room temperature can be prevented from lowering at the defrosting operation during the heating operation, thereby improving the comfort.

1 is a configuration diagram of an air conditioner having a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
2 is a schematic diagram showing the flow of refrigerant during normal heating in an air conditioner having the same refrigeration cycle apparatus.
3 is a schematic diagram showing the flow of refrigerant during defrosting and heating in an air conditioner having the same refrigeration cycle apparatus.
4 is a refrigerating cycle configuration diagram according to Embodiment 2 of the present invention.
5 is a control time chart according to the second embodiment of the present invention.
6 is a configuration diagram of an air conditioner having a conventional refrigeration cycle apparatus.
7 is a refrigerating cycle configuration diagram of a conventional example.

According to a first aspect of the present invention,

A compressor,

A first heat exchanger connected to the compressor,

An expansion valve connected to the first heat exchanger,

A second heat exchanger connected to the expansion valve,

A four-way valve to which the second heat exchanger and the compressor are connected,

An auxiliary heat exchanger for heating the refrigerant disposed around the compressor,

It is possible to switch between a path through which the refrigerant flows directly from the four-way valve to the suction pipe of the compressor and a path through which the refrigerant flows from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger, between the suction pipe of the compressor and the four- And a switching device

Wherein the refrigerant flowed through the first heat exchanger and the second heat exchanger flows through the auxiliary heat exchanger through the four-way valve when the defrosting operation for melting the frost attached to the second heat exchanger is performed, To the suction pipe of the refrigeration cycle apparatus.

As a result, the refrigerant that has passed through the first heat exchanger and the second heat exchanger passes through the auxiliary heat exchanger during the defrosting operation, so that the first heat exchanger can be kept at a high temperature and the auxiliary heat exchanger can be made at a low temperature, It is possible to shorten the defrost time and shorten the room temperature of the defrosting operation in the heating operation, thereby improving the comfort.

In a second aspect of the refrigeration cycle apparatus of the first aspect of the invention, the switching device is a three-way valve. With such a configuration, it is possible to store the apparatus in a space-saving manner, and the apparatus can be made compact.

A third aspect of the present invention is a refrigerating cycle apparatus according to the first or second aspect of the invention, further comprising a discharge gas bypass mechanism connected between the expansion valve and the second heat exchanger from a discharge pipe of the compressor have. With this configuration, the high-temperature refrigerant from the compressor can be supplied to the second heat exchanger, and the defrosting time can be greatly shortened.

In a fourth aspect of the present invention, in the refrigeration cycle apparatus according to any one of the first to third aspects of the present invention, the heat source of the auxiliary heat exchanger for heating the refrigerant is disposed so as to surround the compressor, Thereby forming a heat storage material for heat storage. With this configuration, the defrosting of the second heat exchanger can be terminated in a short period of time without the auxiliary power of the heater or the like, or by supplying the minimum auxiliary power. Further, in the case of this configuration, since the temperature of the auxiliary heat exchanger that performs heat exchange with the heat storage material can be made low, it becomes possible to increase the maximum amount of heat absorbed from the heat storage material, thereby shortening the defrosting time, For example, the room temperature can be prevented from lowering and the comfort can be improved.

A fifth aspect of the invention is a refrigerating cycle apparatus according to any one of the first to fourth aspects of the present invention, wherein refrigerant pressure loss is generated between the switching device provided between the four-way valve and the auxiliary heat exchanger, The throttle mechanism is provided. By providing such a mechanism, the refrigerant flowing through the auxiliary heat exchanger can be cooled to a lower temperature, and the heat absorption rate from the heat source can be improved.

A sixth aspect of the present invention is the refrigerating cycle apparatus according to any one of the first to fifth aspects of the present invention, further comprising: a temperature sensor for detecting a pipe temperature of the second heat exchanger; And a refrigeration cycle control device electrically connected to the temperature sensor. When the temperature sensor detects that the temperature in the second heat exchanger is lower than that at the time of non-injection at the time of the normal heating operation, the refrigeration cycle control device outputs a switching instruction from the normal heating operation to the defrosting / heating operation . In the defrosting / heating operation, when the temperature sensor detects that the temperature in the second heat exchanger has melted in the vicinity of the zero point and the temperature of the second heat exchanger has increased due to the melting of the frost, The refrigeration cycle control device outputs a switching instruction from the defrosting / heating operation to the normal heating operation. Thus, the start and completion of the defrosting / heating operation can be performed efficiently, and the defrosting / heating operation can be performed efficiently.

In a seventh aspect of the present invention, in the refrigeration cycle apparatus according to the sixth aspect of the present invention, after the refrigerating cycle control device determines the defrosting operation end, the operation speed of the compressor is once lowered, After the expansion valve opening degree of the expansion valve is adjusted to such an extent that one liquid refrigerant can be held in the tube of the first heat exchanger, the switching device of the refrigerant path is passed from the four- way valve through the auxiliary heat exchanger, And the refrigerant is directly supplied to the suction pipe of the compressor from the four-way valve in the path of the refrigerant flowing through the suction pipe. Thus, at the time of switching from the defrosting operation to the normal heating operation, the pressure difference at the inlet outlet of the switching device is suppressed to be smaller than the allowable pressure difference of the switching device while suppressing the decrease of the heating capacity to be extremely small, Can be switched. Further, it is possible to provide a rational refrigerating cycle device which can employ a switching device itself which is comparatively low in cost and small in allowable pressure difference.

An eighth invention is an air conditioner in which the first heat exchanger of the first to seventh invention is used as an indoor heat exchanger and the second heat exchanger is used as an outdoor heat exchanger. The pressure difference at the inlet outlet of the switching device can be suppressed to be smaller than the allowable pressure difference of the switching device while the deterioration of the heating capacity is suppressed to be extremely small at the time of switching from the defrosting operation to the normal heating operation, have. Also, the switching device itself can provide a reasonable air conditioner which can adopt a relatively low cost and a small allowable pressure difference.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment of a refrigeration cycle apparatus of the present invention will be described with reference to the drawings as an example mounted on an air conditioner. The present invention is not limited by these embodiments.

(Embodiment 1)

Fig. 1 shows a configuration of an air conditioner having a refrigeration cycle apparatus according to Embodiment 1 of the present invention. The air conditioner is composed of an outdoor unit 2 and an indoor unit 4 connected to each other by a refrigerant pipe .

14, a compressor 6, a four-way valve 8, a strainer 10, an expansion valve 12 and an outdoor heat exchanger (second heat exchanger) 14 are provided in the outdoor unit 2, Respectively. Inside the indoor unit 4, an indoor heat exchanger (first heat exchanger) 16 is provided. They are connected to each other through a refrigerant pipe to constitute a refrigeration cycle.

The compressor 6 and the indoor heat exchanger 16 are connected via a pipe 18 provided with a four-way valve 8 and the indoor heat exchanger 16 and the expansion valve 12 are connected to each other through a strainer 10 via a piping 20 provided with a pipe. The expansion valve 12 and the outdoor heat exchanger 14 are connected to each other through a pipe 22. The outdoor heat exchanger 14 and the compressor 6 are connected via a pipe 24 and a pipe 25. A four-way valve 8 is disposed between the pipe 24 connecting the outdoor heat exchanger 14 and the compressor 6 and the pipe 25. A three-way valve (switching device) 42 is connected between the four-way valve 8 and the compressor 6 via a pipe 25. An accumulator 26 for separating the liquid refrigerant and the gaseous refrigerant is provided in the three-way valve 42 and the piping 25 on the compressor refrigerant suction side. The piping 22 connecting the outdoor heat exchanger 14 and the indoor heat exchanger 16 is connected to the compressor 6 via the piping 28. The piping 28 is provided with a solenoid valve 30 Lt; / RTI > These piping 28 and the solenoid valve 30 constitute a discharge gas bypass mechanism.

Around the compressor 6, a heat storage tank 32 is provided. A heat storage heat exchanger 34 is provided in the heat storage tank 32 and a heat storage material (for example, ethylene glycol aqueous solution) 36 for heat exchange with the heat storage heat exchanger 34 is filled. Thus, the heat accumulating device 32, the heat accumulating heat exchanger 34, and the heat accumulating material 36 constitute a heat accumulating device comprising an auxiliary heat exchanger.

Way valve 42 and the regenerative heat exchanger 34 are connected via a pipe 38 including a capillary tube (throttle mechanism) 43, and the three-way valve 42 and the compressor 6 are connected Is connected to the heat storage heat exchanger (34) via a pipe (40).

The indoor unit 4 is provided with a blowing fan (not shown), upper and lower blades (not shown), and left and right blades (not shown) in addition to the indoor heat exchanger 16. The indoor heat exchanger 16 performs heat exchange between the indoor air sucked into the indoor unit 4 by the blowing fan and the refrigerant flowing through the interior of the indoor heat exchanger 16 and is heated by heat exchange The air is taken out into the room while the air cooled by the heat exchange is taken out into the room during the cooling. The upper and lower wings change the direction of the air taken out from the indoor unit 4 up and down as necessary. The left and right wings change the direction of the air taken out from the indoor unit 4 to the left and right as needed.

The compressor 6, the blowing fan, the upper and lower wings, the left and right wings, the four-way valve 8, the expansion valve 12, the electromagnetic valve 30, For example, a microcomputer), and is controlled and operated by a control device.

In the refrigerating cycle apparatus according to the present invention having the above configuration, the mutual connection relations and functions of the components will be described together with the flow of the refrigerant, for example, during the heating operation.

The refrigerant discharged from the discharge port of the compressor (6) passes through the piping (18) from the four-way valve (8) and reaches the indoor heat exchanger (16). The refrigerant that has been heat-exchanged with the indoor heat exchanger 16 through the heat exchange with the indoor air passes through the indoor heat exchanger 16 and the strainer 10 passing through the pipe 20 to prevent foreign matter from entering the expansion valve 12 , And reaches the expansion valve (12). The refrigerant decompressed in the expansion valve (12) passes through the pipe (22) and reaches the outdoor heat exchanger (14). The refrigerant vaporized by heat exchange with outdoor air in the outdoor heat exchanger 14 passes through the piping 24, the four-way valve 8 and the three-way valve 42, the piping 25 and the accumulator 26, And returns to the compressor 6 through the inlet of the compressor 6.

The piping 28 branched from the discharge port of the compressor 6 of the piping 18 and between the four-way valve 8 is connected to the expansion valve 12 of the piping 22 via the electromagnetic valve 30, (14).

The heat storage tank 32 housing the heat storage material 36 and the heat storage heat exchanger 34 therein is disposed so as to be in contact with the compressor 6 so as to store heat generated in the compressor 6 in the heat storage material 36 do.

Way valve 42 is connected to the suction pipe of the four-way valve 8 and the other is connected to the pipe 25 connecting the three-way valve 42 and the suction port of the compressor 6, Way valve 42 and a pipe 38 connected to the regenerative heat exchanger 34. The three- A path for passing the refrigerant from the four-way valve 8 through the piping 25 to the suction port of the compressor 6 and a path from the four-way valve 8 through the piping 38 to the heat storage heat exchanger 34 to pass the refrigerant to the suction port of the compressor 6. [

Next, the operation at normal heating will be described with reference to Fig. 2 schematically showing the operation of the air conditioner during normal heating and the flow of the refrigerant.

The refrigerant discharged from the discharge port of the compressor 6 as described above flows from the four-way valve 8 through the pipe 18 to the indoor heat exchanger 16 ). The refrigerant heat-exchanged with the indoor air in the indoor heat exchanger 16 is condensed and flows out of the indoor heat exchanger 16, passes through the pipe 20, and reaches the expansion valve 12. The refrigerant decompressed in the expansion valve (12) passes through the pipe (22) and reaches the outdoor heat exchanger (14). The refrigerant vaporized by heat exchange with the outdoor air in the outdoor heat exchanger (14) passes through the pipe (24) and reaches the four-way valve (8). Way valve 42 is controlled such that the refrigerant is led from the outdoor heat exchanger 14 to the suction port of the compressor 6, that is, the piping 24 is connected to the piping 25, The refrigerant that has passed through the valve 8 passes through the three-way valve 42 and returns to the suction port of the compressor 6.

The heat generated in the compressor 6 is stored in the heat storage material 36 accommodated in the heat storage tank 32 through the inner wall of the heat storage tank 32 from the outer wall of the compressor 6.

Next, the operation during defrosting and heating will be described with reference to Fig. 3 schematically showing the operation of defrosting and heating of the air conditioner and the flow of the refrigerant. In the figure, a solid line arrow indicates the flow of the refrigerant supplied to the heating, and a dashed arrow indicates the flow of the refrigerant provided to the defrost.

The frost resistance of the outdoor heat exchanger 14 is increased and the amount of air is decreased and the evaporation temperature in the outdoor heat exchanger 14 is increased . As shown in FIG. 3, the air conditioner of the present invention is provided with a temperature sensor 51 for detecting the temperature of the piping of the outdoor heat exchanger 14. When the temperature sensor 51 detects that the evaporation temperature has been lowered compared to the case where the evaporation is not performed, an instruction to switch from the normal heating operation to the defrosting / heating operation is output by the control device.

When the normal heating operation is changed to the defrosting / heating operation, the electromagnetic valve 30 is controlled to open. A part of the gaseous refrigerant discharged from the discharge port of the compressor 6 in addition to the flow of the refrigerant during the normal heating operation described above passes through the piping 28 and the electromagnetic valve 30 and flows into the refrigerant passing through the piping 22 The outdoor heat exchanger 14 is heated, condensed and liquefied, and then reaches the four-way valve 8.

Way valve 42 is controlled so that the pipe 38 leads to the path through which the refrigerant is led from the outdoor heat exchanger 14 to the regenerative heat exchanger 34. That is, The refrigerant having passed through the four-way valve 8 is reduced in pressure by the capillary tube 43 and becomes low temperature. The heat of the heat storage material 36 is absorbed by the heat storage heat exchanger 34, Reaches the accumulator (26), and returns to the suction port of the compressor (6).

With this configuration, the temperature of the heat storage heat exchanger (34) for performing heat exchange with the heat storage material (36) can be made low. The maximum absorption heat amount from the heat storage material 36 is proportional to the temperature difference between the temperature of the compressor 6 and the temperature of the heat storage heat exchanger 34. If the temperature of the heat storage heat exchanger 34 can be made low It is possible to increase the temperature difference between the temperature of the compressor 6 and the temperature of the heat storage heat exchanger 34 so that the maximum amount of heat absorbed from the heat storage material 36 can be increased, It is possible to suppress the room temperature drop due to the defrosting operation at the time of the heating operation and to improve the comfort.

Further, evaporation of the liquid refrigerant in the heat storage heat exchanger 34 is promoted, so that the liquid refrigerant does not return to the compressor 6, and the reliability of the compressor 6 can be improved.

6, when the refrigerant passing through the heat storage heat exchanger 118 is a bypass path, the amount of circulation of the refrigerant passing through the heat storage heat exchanger 118 is reduced. In the case where the temperature of the heat storage material 126 is high, the degree of superheat increases at the rear half of the heat storage heat exchanger 118, so that the amount of heat exchange is reduced and the defrosting ability can not be sufficiently exhibited. However, in this configuration, since the refrigerant is made to flow through the heat storage heat exchanger 34 in one path, it is possible to prevent a decrease in the amount of heat exchange due to excessive superheat degree, and the defrosting ability can be sufficiently exhibited.

The temperature of the outdoor heat exchanger 14 which is lower than the freezing point due to the attachment of the frost during the defrosting and heating is lower than the temperature of the refrigerant discharged from the discharge port of the compressor 6 and the refrigerant discharged from the indoor heat exchanger 16 Is heated by the mixed refrigerant, the frost melts near the zero point, and when the frost melts, it begins to rise again. When the temperature sensor 51 detects the temperature rise of the outdoor heat exchanger 14, it is determined that defrosting has been completed, and an instruction to switch from the defrosting / heating operation to the normal heating operation is outputted from the controller.

The discharge gas bypass path from the compressor 6 through the piping 28 to the outdoor heat exchanger 14 through the electromagnetic valve 30 is not necessarily required and a case where a very large defrosting capability is required But may be omitted.

In this case, the gas-phase refrigerant flows from the discharge port of the compressor 6 through the pipe 18, the indoor heat exchanger 16, the pipe 20 and the pipe 22 to the outdoor heat exchanger 14, The defrosting capability is reduced slightly, but a compact configuration can be achieved at low cost.

In this configuration, the capillary tube 43 is provided in the pipe 38 reaching the heat storage heat exchanger 34 from the three-way valve 42. However, instead of this configuration, the heat storage heat exchanger 34, Way valve 42, which communicates with the valve body 42, may be connected. In this case, the capillary tube 43 can be excluded, and a compact configuration can be realized at low cost.

(Embodiment 2)

≪ Process to reach one form of the present invention >

The air conditioner of the first embodiment shown in Fig. 1 is proposed as an improved version of the conventional air conditioner shown in Fig. 7, and Fig. 1 shows an example of a refrigeration cycle apparatus improved in the defrosting method.

The air conditioner of Embodiment 1 of the present invention has a three-way valve 42 as a switching device connected between a four-way valve 8 and a compressor 6 via a pipe 25, And the accumulator 26 for separating the liquid refrigerant and the gaseous refrigerant are provided in the piping 25 on the suction side of the compressor refrigerant. The three-way valve 42 and the regenerative heat exchanger 34 are connected via a pipe 38 including a capillary tube 43 serving as a throttle mechanism and connected to the regenerative heat exchanger 34 and the three- And the pipe (25) connecting the compressor (6) are connected via a pipe (40).

Way valve 42 is connected to the suction pipe of the four-way valve 8 and the other is connected to the pipe 25 connecting the three-way valve 42 and the suction port of the compressor 6, One side of which is connected to a piping 38 connected to the three-way valve 42 and the regenerative heat exchanger 34. The refrigerant is led from the four-way valve 8 through the piping 25 to the suction port of the compressor 6 It is possible to switch the path through which the refrigerant is led from the four-way valve 8 through the pipe 38 to the inlet of the compressor 6 through the heat storage heat exchanger 34.

During normal heating operation, the refrigerant discharged from the discharge port of the compressor (6) passes through the pipe (18) and reaches the indoor heat exchanger (16) from the four - way valve (8). The refrigerant that has been condensed by heat exchange with the indoor air in the indoor heat exchanger 16 is discharged from the indoor heat exchanger 16 and reaches the expansion valve 12 through the pipe 20 and is decompressed by the expansion valve 12 The refrigerant passes through the pipe (22) and reaches the outdoor heat exchanger (14). The refrigerant vaporized by heat exchange with the outdoor air in the outdoor heat exchanger (14) passes through the pipe (24) and reaches the four-way valve (8). The three-way valve 42 is controlled so that the refrigerant is led from the outdoor heat exchanger 14 to the inlet of the compressor 6, that is, the piping 24 is connected to the piping 25, The refrigerant passes through the three-way valve (42) and returns to the suction port of the compressor (6).

The heat generated in the compressor 6 is accumulated in the heat storage material 36 accommodated in the heat storage tank 32 through the outer wall of the heat storage tank 32 from the outer wall of the compressor 6. [

When the concealed frost grows on the outdoor heat exchanger 14 during the above-described normal heating operation, the ventilation resistance of the outdoor heat exchanger 14 increases to decrease the amount of air and the evaporation temperature in the outdoor heat exchanger 14 . (Not shown) for detecting the temperature of the piping of the outdoor heat exchanger 14. When the temperature sensor detects that the evaporation temperature has lowered compared with the case where the evaporation temperature is lower than that at the time of non-injection, An instruction to the heating operation is output.

Way valve 42 is controlled so that the refrigerant is led from the outdoor heat exchanger 14 to the heat storage heat exchanger 34 or the piping 24 and the pipe 38 are communicated with each other, The refrigerant having passed through the valve 8 is reduced in pressure by the capillary tube 43 and becomes low temperature. The heat of the heat storage material 36 is absorbed by the heat storage heat exchanger 34, Reaches the accumulator (26), and returns to the suction port of the compressor (6).

The temperature of the outdoor heat exchanger 14 which is lower than the freezing point due to the attachment of the frost at the start of the defrosting and heating is lower than the temperature of the gaseous refrigerant coming out of the discharge port of the compressor 6 and the liquid phase or gas-liquid two phase returning from the indoor heat exchanger 16 The refrigerant is heated by the mixed refrigerant, and the frost melts near the zero point. When the frost is completely melted, the temperature of the outdoor heat exchanger 14 starts to rise again. When the temperature rise of the outdoor heat exchanger 14 is detected by the temperature sensor, it is determined that the defrosting is completed, and the control device outputs an instruction from the defrosting / heating operation to the normal heating operation.

The use of the three-way valve 42 is advantageous in that the refrigerant flowing through the indoor heat exchanger 16 and the outdoor heat exchanger 14 flows through the heat storage heat exchanger 34 via the four-way valve 8 during the defrosting operation, 6, the operation is performed in which the indoor heat exchanger 16 is kept at a high temperature and the heat accumulating heat exchanger 34 is kept at a low temperature so as to quickly perform the heat absorption from the heat source, It is possible to reduce the room temperature of the defrosting operation during the heating operation and to improve the comfort.

In the configuration of the first embodiment of the present invention described above, when the refrigerant flows from the inlet of the three-way valve 42 to the inlet of the compressor 6 during defrosting / heating operation, the pressure at the inlet outlet of the three- There is a problem that the difference between the allowable pressure of the three-way valve 42 and the normal heating operation can not be switched, and that the use of a three-way valve having a large allowable pressure difference there was.

In order to solve the above problems, the inventors of the present invention have found that, when switching from defrosting / heating operation to normal heating operation, the pressure difference at the inlet / outlet of the three-way valve is reduced by three- Side valve is reliably suppressed to be smaller than the permissible pressure difference of the refrigerating cycle device of the second embodiment and the three-way valve itself is comparatively small and the allowable pressure difference is small and the cost is low. I reached one air conditioner.

Fig. 4 is a refrigerating cycle configuration diagram showing the configuration of an air conditioner having a refrigeration cycle apparatus according to Embodiment 2 of the present invention, and the same constituent elements as those in Embodiment 1 of the present invention shown in Fig. And detailed description thereof will be omitted.

In Fig. 4, in this air conditioner, in addition to the configuration of the first embodiment, a refrigeration cycle control device 50 for controlling the operation thereof is additionally provided. The refrigeration cycle control device 50 is electrically connected to the temperature sensor 51 and detects the temperature of the outdoor heat exchanger (first heat exchanger) 14. The refrigerating cycle control device 50 is also electrically connected to the compressor 6, the expansion valve 12 and the three-way valve 42 serving as the switching device and is connected to the expansion valve 12, Throttle amount of the three-way valve 42, and switching of the refrigerant path of the three-way valve 42 to drive control.

The refrigerant discharged from the discharge port of the compressor 6 passes through the pipe 18 and reaches the indoor heat exchanger 16 from the four-way valve 8. The refrigerant that has been heat-exchanged with the indoor air in the indoor heat exchanger 16 and condenses is discharged from the indoor heat exchanger 16 and reaches the expansion valve 12 through the pipe 20. Further, the refrigerant decompressed in the expansion valve (12) passes through the pipe (22) and reaches the outdoor heat exchanger (14). The refrigerant vaporized by heat exchange with the outdoor air in the outdoor heat exchanger (14) passes through the pipe (24) and reaches the four-way valve (8). The three-way valve 42 is controlled so that the refrigerant is led from the outdoor heat exchanger 14 to the inlet of the compressor 6, that is, the piping 24 is connected to the piping 25, The refrigerant passes through the three-way valve (42) and returns to the suction port of the compressor (6).

The heat generated in the compressor 6 is accumulated in the heat storage material 36 accommodated in the heat storage tank 32 through the outer wall of the heat storage tank 32 constituting the auxiliary heat exchanger from the outer wall of the compressor 6. [

When the concealed frost grows on the outdoor heat exchanger 14 during the above-described normal heating operation, the ventilation resistance of the outdoor heat exchanger 14 increases to decrease the air volume, and the evaporation temperature in the outdoor heat exchanger 14 becomes . When the temperature sensor 51 detects that the evaporation temperature has lowered compared with the case where the evaporation is not performed, the refrigeration cycle control device 50 outputs an instruction to switch from normal heating operation to defrosting / heating operation.

When the normal heating operation is changed to the defrosting / heating operation, the electromagnetic valve 30 is controlled to open. A part of the gaseous refrigerant discharged from the discharge port of the compressor 6 in addition to the flow of the refrigerant during the normal heating operation described above passes through the piping 28 serving as the discharge gas bypass mechanism and the electromagnetic valve 30, 22, and the outdoor heat exchanger 14 is heated, condensed and liquefied, and then reaches the four-way valve 8.

Way valve 42 is controlled so that the refrigerant is led from the outdoor heat exchanger 14 to the heat accumulation heat exchanger 34, that is, the piping 24 and the pipe 38 communicate with each other. The refrigerant passing through the four-way valve 8 is reduced in pressure by the capillary tube 43 serving as a throttle mechanism and becomes low in temperature. The heat of the heat storage material 36 is absorbed by the heat storage heat exchanger 34, Reaches the accumulator (26) in a high dry state, and returns to the suction port of the compressor (6).

The temperature of the outdoor heat exchanger 14 which is lower than the freezing point due to the attachment of the frost at the start of the defrosting and heating is lower than the temperature of the gaseous refrigerant coming out of the discharge port of the compressor 6 and the liquid phase or gas-liquid two phase returning from the indoor heat exchanger 16 The refrigerant is heated by the mixed refrigerant, and the frost melts near the zero point. When the frost melts, it begins to rise again. When the temperature sensor 51 detects the temperature rise of the outdoor heat exchanger 14, it is determined that the defrosting is completed, and the refrigeration cycle control device 50 outputs a switching instruction from the defrosting / heating operation to the normal heating operation .

5 (a) to 5 (f) show control time charts according to the second embodiment of the present invention. In particular, from the time when it is judged that the defrosting has been completed, , The expansion valve opening degree, the three-way valve path state, the refrigerant pressure (high and low pressure), and the heating capacity with time elapsed. 5 (a), 5 (b) and 6 (c) are diagrams showing the defrost determination, the expansion valve opening degree, the three- High and low pressure), and (f) shows the change of the heating capacity.

First, a control time chart in the case where the expansion valve opening degree of the expansion valve 12 is not reduced when switching from the defrosting / heating operation to the normal heating will be described.

As shown in Fig. 5 (a), it is determined that the defrosting is completed at the timing of time T1 and the normal heating operation is started. Here, the time T1 represents the time when the temperature of the outdoor heat exchanger 14 becomes equal to or higher than the predetermined temperature. The predetermined temperature refers to the temperature at which the frost attached to the outdoor heat exchanger 14 melts and the temperature in the outdoor heat exchanger 14 starts to rise. The temperature of the outdoor heat exchanger (14) is detected by the temperature sensor (51). 5 (b), the refrigeration cycle control device 50 issues an instruction to lower the number of revolutions of the compressor 6 and sets the number of revolutions Gradually decreases from F1, and reaches the number of rotations F2 until time T2. Here, the time T2 represents a time point after a predetermined time has elapsed from the time T1. The refrigeration cycle control device 50 instructs the three-way valve 42 to switch from the top side to the heating side at the timing of time T2 as shown in Fig. 5 (d). Specifically, the three-way valve 42 is connected to the suction pipe of the compressor 6 from the four-way valve 8 in the path for passing the refrigerant from the four-way valve 8 through the heat storage heat exchanger 34 to the suction pipe of the compressor 6 Switch directly to the path of refrigerant flow. 5 (e), the number of revolutions of the compressor 6 is lowered, the pressure on the high pressure side of the refrigerant pressure is lowered, and the pressure on the low pressure side is increased. At this time, the high and low pressure difference DELTA P between the high pressure side and the low pressure side of the refrigerant pressure at time T2 becomes smaller than the high and low pressure difference at time T1. That is, since the inlet outlet pressure of the three-way valve 42 can be made smaller than the allowable pressure difference of the three-way valve 42 with respect to the time T2, the three-way valve 42 can be reliably switched. 5 (f), there is a problem that the temperature of the indoor heat exchanger 16 is lowered due to the lowering of the pressure on the high-pressure side of the refrigerant pressure, thereby lowering the heating capacity (the broken line in the drawing ).

In the second embodiment of the present invention, the above problem is solved by controlling the opening degree of the expansion valve of the expansion valve (12). A control time chart when the expansion valve opening degree of the expansion valve 12 is adjusted when switching from the defrosting / heating operation to the normal heating will be described.

In the second embodiment of the present invention, as shown in Fig. 5A, it is determined that defrosting is completed at the timing of time T1 and the normal heating operation is started. As shown in Fig. 5 (b), the refrigeration cycle control device 50 instructs the refrigerating cycle control device 50 to be lowered from the rotational speed F1 of the compressor 6. [ At the same time, the refrigeration cycle control device 50 instructs the expansion valve 12 to tighten the expansion valve opening degree. In particular, as shown in Fig. 5C, the expansion valve 12 is gradually tightened from the expansion valve opening P1, which is a set value at the time of completion of the defrosting / heating operation, and is supercooled by the indoor heat exchanger 16 until time T2 The liquid refrigerant in the indoor heat exchanger 16 is condensed to the expansion valve opening P2 to such an extent that it can be held in the pipe of the indoor heat exchanger 16. As a result, as shown in FIG. 5 (e) and FIG. 5 (f), as the expansion valve opening degree of the expansion valve 12 is tightened, the pressure drop on the high pressure side of the refrigerant pressure is reduced, The lowering of the heating ability is reduced (indicated by a solid line in the drawing). In addition, the high and low pressure difference DELTA P between the high pressure side and the low pressure side of the refrigerant pressure at time T2 becomes smaller than the high and low pressure difference at time T1. As shown in Fig. 5 (d), the refrigeration cycle control device 50 instructs to switch the three-way valve 42 from the top side to the heating side at the timing of time T2. Way valve 42 to the suction pipe of the compressor 6 from the four-way valve 8 in the path of passing the refrigerant from the four-way valve 8 through the heat storage heat exchanger 34 to the suction pipe of the compressor 6, To the flow path. In the second embodiment of the present invention, the high and low pressure difference ΔP between the high pressure side and the low pressure side of the refrigerant pressure is increased as compared with the case where the expansion valve opening degree of the expansion valve 12 is not tightened. Can be executed without any problem if the high and low pressure difference DELTA P is smaller than the allowable pressure difference of the three-way valve 42. [

5 (b) and 5 (c), the number of revolutions of the compressor 6 and the expansion valve opening degree of the expansion valve 12 are controlled so as to operate normally as the heating operation after the time T2 , And is controlled to be the initial set value at the normal heating start time T3. Here, time T3 represents the time at which the rotation speed of the compressor 6 and the expansion valve opening degree of the expansion valve 12 become the initial set values at the time of the normal heating start. After the time T3, the rotation speed of the compressor 6 and the expansion valve opening degree of the expansion valve 12 are controlled so as to be constant at the initial set value at the time of the normal heating start. However, The value may be changed.

5 (e) and Fig. 5 (f), in the refrigerant pressure (high and low pressure) and the heating capacity, the time T3 is higher than the time T1 and the high pressure side of the refrigerant pressure is high, It is going up. This is because, after time T2, in order to increase the heating capacity more quickly, the number of revolutions of the compressor 6 is increased and the tightening of the expansion valve 12 is controlled to increase the difference between the high and low pressure of the refrigerant pressure. On the other hand, since the defrosting cycle (the portion where the frost is melted by the high-temperature and high-pressure gas) is cooled by the frost, the high-pressure side of the refrigerant pressure is lowered and the heating capacity is also lowered.

Way valve 42 to the allowable pressure difference of the three-way valve 42 when the operation mode is switched from the defrosting / heating operation to the normal heating operation by suppressing the deterioration of the heating capacity to an extremely small level, Way valve 42 can be reliably suppressed and the three-way valve itself can be employed at a relatively low cost with a relatively small allowable pressure difference.

The discharge gas bypass path from the compressor 6 through the piping 28 to the outdoor heat exchanger (first heat exchanger) through the electromagnetic valve 30 is not necessarily required, and an extremely large defrost But may be configured so as to be eliminated except when the capability is required.

In the second embodiment, the heat storage heat exchanger 34 provided as an auxiliary heat exchanger so as to surround the compressor 6 has been described as an example. However, the present invention is not limited to this, and other configurations may be used.

While the refrigeration cycle applied to the air conditioner has been described in the second embodiment, the same effect can be obtained in other devices such as a heat pump type water heater.

The refrigerating cycle apparatus according to the present invention improves the heat absorbing ability from the heat source to improve the defrosting ability and also greatly reduce the return of liquid refrigerant to the compressor and improve the reliability of the compressor. Further, since the reduction in the heating capacity during defrosting can be suppressed to a minimum, a low-cost refrigerant path switching device can be employed, which is useful for an air conditioner, a refrigerator, a heat pump type hot water heater, and the like.

2: outdoor unit 4: indoor unit
6: compressor 8: four-way valve
10: Strainer 12: Expansion valve
14: outdoor heat exchanger (second heat exchanger) 16: indoor heat exchanger (first heat exchanger)
18, 20, 22, 24, 25: piping 26: accumulator
28: Piping (discharge gas bypass mechanism)
30: Solenoid valve (discharge gas bypass mechanism)
31: Solenoid valve 32: Heat storage tank (auxiliary heat exchanger)
34: heat storage heat exchanger (auxiliary heat exchanger) 36: heat storage material (auxiliary heat exchanger)
38, 40: piping 42: three-way valve (switching device)
43: capillary tube (throttle mechanism) 50: refrigeration cycle control device
51: Temperature sensor

Claims (8)

A compressor,
A first heat exchanger connected to the compressor,
An expansion valve connected to the first heat exchanger,
A second heat exchanger connected to the expansion valve,
A four-way valve to which the second heat exchanger and the compressor are connected,
An auxiliary heat exchanger for heating the refrigerant disposed around the compressor,
The switching of the refrigerant flow from the four-way valve to the suction pipe of the compressor directly between the suction pipe of the compressor and the four-way valve and the refrigerant flow from the four-way valve through the auxiliary heat exchanger to the suction pipe of the compressor A switching device,
Wherein the refrigerant flowed through the first heat exchanger and the second heat exchanger flows through the auxiliary heat exchanger through the four-way valve when the defrosting operation for melting the frost attached to the second heat exchanger is performed, To be guided to the suction pipe
Refrigeration cycle equipment. The method according to claim 1,
And the three-way valve is used for the switching device
Refrigeration cycle equipment. 3. The method according to claim 1 or 2,
And a discharge gas bypass mechanism connected between the expansion valve and the second heat exchanger from the discharge pipe of the compressor
Refrigeration cycle equipment. 4. The method according to any one of claims 1 to 3,
Wherein the heat source of the auxiliary heat exchanger is a heat storage material disposed to surround the compressor and storing heat generated in the compressor
Refrigeration cycle equipment. 5. The method according to any one of claims 1 to 4,
And a throttle mechanism for increasing the refrigerant pressure loss between the switching device provided between the four-way valve and the auxiliary heat exchanger and the auxiliary heat exchanger is provided
Refrigeration cycle equipment. 6. The method according to any one of claims 1 to 5,
A temperature sensor for detecting a pipe temperature of the second heat exchanger,
Further comprising a refrigeration cycle control device electrically connected to the compressor, the expansion valve, the switching device, and the temperature sensor,
When the temperature sensor detects that the temperature in the second heat exchanger is lowered at the time of the normal heating operation than at the time of the non-injection, the refrigeration cycle control device outputs a switching instruction from the normal heating operation to the defrosting / heating operation,
In the defrosting / heating operation, when the temperature sensor detects that the temperature in the second heat exchanger melts in the vicinity of the zero point and the temperature of the second heat exchanger is increased after the melting of the frost is completed, , And the refrigeration cycle control device outputs a switching instruction from the defrosting / heating operation to the normal heating operation
Refrigeration cycle equipment. The method according to claim 6,
Wherein the refrigerating cycle control device is capable of temporarily lowering the operation speed of the compressor and making it possible to hold liquid refrigerant supercooled in the first heat exchanger in the pipe of the first heat exchanger Of the refrigerant path from the four-way valve to the suction pipe of the compressor through the auxiliary heat exchanger and to flow the refrigerant to the suction pipe of the compressor after the switching device of the refrigerant path joins the opening of the expansion valve of the compressor And the refrigerant is switched to a path through which the refrigerant flows
Refrigeration cycle equipment. 8. The method according to any one of claims 1 to 7,
The first heat exchanger may be an indoor heat exchanger, and the second heat exchanger may be an outdoor heat exchanger
Air conditioner.
KR1020147005247A 2011-11-04 2012-10-02 Refrigeration cycle apparatus and air conditioner provided with same KR20140092803A (en)

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JP6380455B2 (en) * 2015-07-14 2018-08-29 株式会社デンソー Refrigeration cycle equipment
CN107388663B (en) * 2017-08-03 2019-03-26 珠海格力电器股份有限公司 The control method and heat pump system of heat pump system
CN109520169A (en) * 2018-09-11 2019-03-26 珠海格力电器股份有限公司 A kind of control method of air conditioner and air conditioner
JP2020111193A (en) * 2019-01-11 2020-07-27 サンデン・オートモーティブクライメイトシステム株式会社 Vehicular air conditioner
JP7398617B2 (en) 2020-02-17 2023-12-15 パナソニックＩｐマネジメント株式会社 air conditioner
CN111503928A (en) * 2020-05-15 2020-08-07 珠海格力电器股份有限公司 Air conditioning unit capable of effectively improving energy utilization rate and control method and device thereof
CN114508891A (en) * 2020-11-16 2022-05-17 合肥美的电冰箱有限公司 Refrigerator refrigerating system and refrigerator defrosting method

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JPS5912265A (en) * 1982-07-13 1984-01-21 太平洋工業株式会社 Cooling circuit combining air-conditioning
JPS5988655U (en) * 1982-12-07 1984-06-15 三菱電機株式会社 Refrigeration equipment
JPS6122161A (en) * 1984-07-06 1986-01-30 株式会社東芝 Air conditioner
JPS6246166A (en) * 1985-08-21 1987-02-28 株式会社日立製作所 Refrostation control method of air conditioner
JPH0528439Y2 (en) * 1987-04-01 1993-07-21
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