JP2839066B2 - Heat pump defrost system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plurality of condensers for condensing high-pressure gas refrigerant sent from a compressor and radiating heat to an object to be heated, and for evaporating the condensed refrigerant sent from these condensers to absorb heat. An evaporator and a defrosting means for defrosting the frosted evaporator using a high-pressure gaseous refrigerant sent from the compressor as a defrosting heat medium are provided. A normal operation state in which the supply of the refrigerant is stopped to supply the high-pressure gas refrigerant from the compressor to the condenser side, and the supply amount of the high-pressure gas refrigerant to the condenser side is reduced to reduce the amount of the high-pressure gas refrigerant supplied to the compressor. The present invention relates to a defrosting system for a heat pump provided with a switching means for switching a refrigerant path to a defrosting operation state in which a high-pressure gas refrigerant supplied from a diverter is supplied.

[0002]

2. Description of the Related Art Conventionally, in this type of heat pump defrosting system, high-pressure gas refrigerant supplied to a defrosting means is supplied to one of a plurality of condensers in order. It was configured to stop and supply the corresponding amount of refrigerant to the defrosting means.

For example, a plurality of condensers and a plurality of evaporators constitute a plurality of independent heat pump circuits, and when performing a defrosting operation, any one of the heat pump circuits is sequentially selected and selected. The high pressure gas refrigerant to the condenser of the heat pump circuit is supplied to the defrosting means.

[0004]

However, according to the above prior art, when the defrosting operation is performed, the above-mentioned selected condensation is performed regardless of the operation request from the object to be heated and the necessity of heat radiation to the object to be heated. Since the operation of the vessel is stopped, there is a problem that the demand for the operation from the side to be heated and the necessity of heat radiation (hereinafter, simply referred to as “radiation necessity”) are not satisfied.

[0005] In particular, in the case of a defrosting system for a heat pump such as an air conditioner, the heating operation of the air conditioning target area selected in order is performed irrespective of the necessity of heating as the degree of heat radiation and the necessity of heating temperature control. Is stopped on its own, so that the response performance of the air conditioner to the user's heating request is significantly deteriorated.

An object of the present invention is to eliminate the above-mentioned conventional disadvantages.

[0007]

According to a first aspect of the present invention, there is provided a heat pump defrosting system comprising: a judging means for judging a necessity of heat radiation of each of the condensers based on a heating state of the object to be heated; Adjusting means for adjusting the ratio of the refrigerant reduction rate of each of the condensers in the reduction of the high-pressure gas refrigerant on the condenser side by switching from the state to the defrosting operation state, and determination information of the determination means in the defrosting operation state And control means for controlling the adjusting means so that the refrigerant reduction rate of the condenser having a high heat radiation necessity is smaller than the refrigerant reduction rate of the condenser having a low heat radiation necessity. .

[0008] A second characteristic configuration is that, when the high-pressure gas refrigerant on the condenser side is reduced by switching from the normal operation state to the defrost operation state, adjusting means for adjusting the ratio of the refrigerant reduction rate of each of the condensers, In the defrosting operation state, control means for controlling the adjusting means so that the ratio of the refrigerant reduction rate of each of the condensers becomes a set ratio, and changing means for changing the set ratio according to an artificial command are provided. It is in the point.

A third characteristic configuration is that when the high pressure gas refrigerant on the condenser side is reduced by switching from the normal operation state to the defrosting operation state, the ratio of the refrigerant reduction rate of each of the condensers is always specified to a predetermined constant ratio. That is, a defining means is provided.

[0010]

According to the first aspect of the present invention, in the defrosting operation state, the adjusting means for adjusting the ratio of the refrigerant reduction rate of each of the condensers requires the refrigerant reduction rate of the condenser having a high heat radiation necessity to be determined. Since the refrigerant is controlled so as to be smaller than the refrigerant reduction rate of the condenser having a low degree, a decrease in the amount of heat radiation during the defrost operation with respect to the degree of heat radiation of each condenser can be suppressed as much as possible.

According to the second characteristic configuration, the adjusting means for adjusting the ratio of the refrigerant reduction rate of each condenser in the defrosting operation state controls the ratio of the refrigerant reduction rate of each condenser to the set ratio. In addition, since there is provided changing means for changing the set ratio in accordance with the artificial command, by giving the changing means an artificial command in accordance with the heat dissipation requirement of each condenser, the heat dissipation requirement of each condenser is provided. , A decrease in the amount of heat released during the defrosting operation can be suppressed as much as possible.

[0012] According to the third characteristic configuration, the regulating means for always regulating the ratio of the refrigerant reduction rate of each condenser to a predetermined constant ratio in the defrosting operation state is provided. By determining the ratio of the specified refrigerant reduction rate according to the heat radiation necessity of each condenser, it is possible to minimize the decrease in the heat radiation amount during the defrosting operation with respect to the heat radiation necessity of each condenser. Can be.

[0013]

According to the first characteristic configuration of the present invention, it is possible to minimize the decrease in the amount of heat radiation during the defrosting operation with respect to the heat radiation necessity of each condenser. It is possible to provide a heat pump defrosting system in which the inconvenience that the heat radiation necessity of the vessel is not satisfied is solved.

[0014] According to the second characteristic configuration, an artificial command corresponding to the necessity of heat radiation of each condenser is given to the changing means, so that the heat radiation amount during the defrosting operation with respect to the heat radiation necessity of each condenser is provided. Since the reduction can be suppressed as much as possible, it is possible to provide a heat pump defrosting system in which the inconvenience that the heat radiation requirement of the condenser is not satisfied in the defrosting operation state is eliminated.

According to the third characteristic configuration, the ratio of the refrigerant reduction rate defined by the defining means to a fixed ratio is determined according to the degree of need for heat radiation of each condenser. Therefore, it is possible to provide a heat pump defrosting system in which the inconvenience that the heat release requirement of the condenser is not satisfied in the defrosting operation state has been eliminated, since a decrease in the amount of heat radiation during the defrosting operation with respect to the temperature can be suppressed as much as possible. it can.

[0016]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a separate type heat pump air conditioner, where Uo is an outdoor unit, Ua is a first indoor unit for a first air conditioning target area Za, Ub is a second indoor unit for a second air conditioning target area Zb, and Uc is a second indoor unit. The third indoor unit for the three air conditioning target areas Zc.

The outdoor unit Uo has two outdoor heat exchangers N1 and N2 that use the outside air OA as the air to be absorbed and released, and an outdoor fan F1 and an outdoor fan F1 that ventilate the outside air OA to the outdoor heat exchangers N1 and N2. F2, the compressor Cmp, the accumulator Ac, the oil separator Os, the receiver R, the first expansion valve ex1 for the outdoor heat exchanger N1, and the second expansion valve ex2 for the outdoor heat exchanger N2. Equipped.

Reference numerals v1 to v4 denote switching valves for switching the refrigerant circuit according to the operation mode. The switching valves v1 and v3 are
The low pressure gas refrigerant Rc from the outdoor heat exchanger N1 or N2 is provided in a path returning to the compressor Cmp via the accumulator Ac. The switching valves v2 and v4 are provided in a path for supplying the high-pressure gas refrigerant Rh from the compressor Cmp to the outdoor heat exchanger N1 or N2.

The first expansion valve ex1 and the second expansion valve ex2
Functions as the original refrigerant expansion means when the liquid refrigerant Rw flows toward the outdoor heat exchanger N1 or N2,
On the other hand, when the liquid refrigerant Rw flows toward the side away from the outdoor heat exchanger N1 or N2, it is configured to be switchable so as to simply function as a flow control valve.

The outdoor heat exchangers N1 and N2 are provided with temperature sensors S1 and S2 for detecting the respective refrigerant outlet temperatures T1 and T2.

Reference symbol ro denotes an oil return pipe that joins the compressor oil captured by the oil separator Os with the low-pressure gas refrigerant Rc sucked by the compressor Cmp and returns the refrigerant into the compressor Cmp.

From the outdoor unit Uo, a high-pressure gas main pipe Gh for sending the high-pressure gas refrigerant Rh to the indoor unit, a low-pressure gas main pipe Gc for returning the low-pressure gas refrigerant Rc from the indoor unit to the outdoor unit Uo,
Three pipes including a liquid main pipe W through which the liquid refrigerant Rw flows are extended.

Each of the first, second and third indoor units Ua, Ub and Uc is provided with an indoor heat exchanger Na for adjusting air supply SAa, SAb and SAc to the corresponding air conditioning target zones Za, Zb and Zc. Nb and Nc and their indoor heat exchangers Na and N
b, Nc, the air supply fan F3 for supplying the air supply SAa, SAb, SAc adjusted to the corresponding air-conditioning target zones Za, Zb, Zc, and the first indoor unit Ua includes an indoor heat exchanger Na. Is equipped with a third expansion valve Exa for the indoor heat exchanger Nb.
b, and the third indoor unit Uc includes an indoor heat exchanger Nc.
Is equipped with a fifth expansion valve Exc.

V5 and v6 are switching valves for switching the refrigerant circuit according to the operation mode. The switching valve v5 transfers the high-pressure gas refrigerant Rh from the high-pressure gas main pipe Gh to the indoor heat exchanger N.
a, Nb or Nc is provided in the high pressure gas branch pipe rh. The switching valve v6 is connected to the indoor heat exchangers Na, Nb, and Nc.
A low-pressure gas recirculation pipe rc that returns the low-pressure gas refrigerant Rc from the low-pressure gas main pipe Gc to the low-pressure gas main pipe Gc.

Third, fourth and fifth expansion valves Exa, Ex
b, Exc are provided in the liquid branch recirculation pipe rw that flows the liquid refrigerant Rw between the indoor heat exchangers Na, Nb, Nc and the liquid main pipe W, and the liquid refrigerant Rw converts the indoor heat exchanger Na, When flowing toward Nb or Nc, it functions as the original refrigerant expansion means, while when the liquid refrigerant Rw flows toward the liquid main pipe W, it functions as a flow regulating valve. It is configured to be switchable.

The indoor heat exchangers Na, Nb, Nc are provided with temperature sensors Sa, Sb, Sc for detecting the refrigerant outlet temperatures Ta, Tb, Tc of the liquid refrigerant Rw.

Each high pressure gas branch pipe rh is connected to a high pressure gas main pipe Gh via a refrigerant distributor A, and a low pressure gas recirculation pipe rc is connected to a low pressure gas main pipe G via a refrigerant merger B.
c, and the liquid branch reflux pipe rw is connected to
Is connected to the liquid main pipe W. When the fourth and subsequent indoor units are installed, the fourth main unit and the third main tube G are also connected in the same branch connection form as described above.
h, Gc and W.

FIG. 1 shows an outdoor heat exchanger N of an outdoor unit Uo.
1 and N2 function as an evaporator Ev, and
A, while absorbing the heat from the indoor units Ua,
Ub, Uc indoor heat exchangers Na, Nb, Nc are connected to condenser C
In the "heating mode" operating state in which the supply air SAa, SAb and SAc are heated and controlled by functioning as d, a state is shown in which the outdoor heat exchanger N2 is being defrosted.

A specific refrigerant flow in the "heating mode" in a normal operation state in which the defrosting operation is not performed will be described below. Oil separator O discharged from compressor Cmp
s, the high-pressure gas refrigerant Rh (shown by a thick black line in the figure) passing through the high-pressure gas main pipe Gh and the high-pressure gas branch pipe rh passes through the indoor heat exchangers N of the indoor units Ua, Ub, and Uc.
a, Nb, and Nc are distributed and condensed, and the heating temperature is adjusted.

The indoor heat exchanger N functioning as the condenser Cd
a, Nb, Nc condensed liquid refrigerant Rw (in the figure,
(Thick lines with hatching) indicate third, fourth and fifth expansion valves Exa, Exb, and E functioning as flow control valves.
The liquid is returned to the liquid receiver R of the outdoor unit Uo via xc, the liquid branch reflux pipe rw, and the liquid main pipe W. The condensed liquid refrigerant Rw returned to the receiver R is distributed and supplied to the first and second expansion valves ex1 and ex2 in the state of functioning as the original refrigerant expansion means, and then the outdoor heat exchange functioning as the evaporator Ev It is evaporated in the devices N1 and N2, and heat is absorbed from the outside air OA.

The evaporative low-pressure gas refrigerant Rc sent from the outdoor heat exchangers N1 and N2 (shown by a thick white line in the figure)
Is returned to the compressor Cmp via the switching valve v1 or v3 and the accumulator Ac. (Note that, in the figure, a black valve indicates a closed state.)

In FIG. 1, a defrosting operation is performed in the outdoor heat exchanger N2. In the heat pump circuit of the present embodiment, by switching the switching valves v3 and v4,
The high-pressure gas refrigerant Rh from the compressor Cmp is configured to flow through the outdoor heat exchanger N2, and the frost is defrosted by the heat of the high-pressure gas refrigerant Rh. Even when the outdoor heat exchanger N1 becomes frosted,
By switching the switching valves v1 and v2, the defrosting operation is similarly performed.

Therefore, the outdoor heat exchangers N1 and N2 themselves use the high-pressure gas refrigerant Rh delivered from the compressor Cmp as a heat medium for defrosting, and the outdoor heat exchanger N1 as an evaporator in a frosted state. , N2.

The high-pressure gas refrigerant Rh flowing through the outdoor heat exchanger N1 or N2 during the defrosting operation is supplied to the indoor heat exchangers Na and N.
The high pressure gas refrigerant Rh supplied to b and Nc is reduced and supplied in a divided flow. Accordingly, the switching valves v1, v2 and v3, v4 stop the supply of the high-pressure gas refrigerant Rh to the defrosting means 1 and supply the high-pressure gas refrigerant Rh from the compressor Cmp to the condenser Cd side, and The supply amount of the high-pressure gas refrigerant to the condenser Cd is reduced, and the high-pressure gas refrigerant R from the compressor Cmp is supplied to the defrosting means 1.
The switching means 2 is configured to switch the refrigerant path to a defrosting operation state in which h is diverted and supplied.

The switching operation of the switching valves v1 to v4 is controlled by a defrosting control means 101, which will be described later, and is applied to both the outdoor heat exchanger N1 and the outdoor heat exchanger N2.
Control is performed so that the defrosting operation is not performed at the same time.

The indoor heat exchangers Na and N during the defrosting operation
The amount of reduction of the high-pressure gas refrigerant Rh from b and Nc is determined by the third, fourth and fifth expansion valves Exa and E functioning as flow control valves.
The adjustment is performed by adjusting the refrigerant flow rates of xb and Exc.

As shown in FIG. 2, the switching valves v1 to v4, and the third, fourth and fifth expansion valves Exa, Exb, Exc
Is connected to a control unit H that controls various operation operations of the heat pump air conditioner of the present embodiment. The control unit H
The temperature sensors S1 and S2 and the temperature sensor S
a, Sb and Sc are connected.

The control section H is mainly composed of a microcomputer, and is configured to perform various control operations by software incorporated therein. The control unit H includes, as a function thereof, a defrost control unit 10 that controls a defrosting operation of the heat pump air conditioner of the present embodiment.
1 is configured.

The defrosting control means 101 determines whether the temperature T1 or T2 detected by the temperature sensor S1 or S2 has dropped to a predetermined temperature lower than the normal value in the "heating mode" operating state, and the outdoor heat exchange It is determined that frost has occurred on the device N1 or N2, and the switching valve v1 as the switching means 2 is determined.
And v2 or the switching valves v3 and v4 are operated to start the defrosting operation.

When the defrosting operation is started, the defrosting control means 1
01 is based on the detected refrigerant temperatures Ta, Tb, and Tc of the temperature sensors Sa, Sb, and Sc, and a predetermined setting function.
The refrigerant decrease rate of the indoor heat exchanger with a higher detected refrigerant temperature is
Third and fourth function as flow control valves to reduce the refrigerant flow rate to each of the indoor heat exchangers Na, Nb, and Nc so that the detected refrigerant temperature is higher than the refrigerant reduction rate of the indoor heat exchanger. And the fifth expansion valve Exa, Exb, Exc
The supply of the high-pressure gas refrigerant is stopped by adjusting the refrigerant flow rate or setting the valve opening to the fully closed state.

That is, the detected refrigerant temperature Ta, Tb or T
Since it is determined that the indoor heat exchangers Na, Nb or Nc having a lower c have a lower temperature of the air to be heated and controlled, the degree of heat radiation to the indoor heat exchangers Na, Nb or Nc is lower. It is determined to be higher, and during the defrosting operation,
The refrigerant flow rate is adjusted so as not to be reduced as much as possible. In addition, since the refrigerant circulation amount of the heat pump changes sequentially according to the rotation speed of the compressor Cmp, the defrost control unit 101 adjusts the ratio of the refrigerant reduction rate among the indoor heat exchangers Na, Nb, and Nc. It is configured to be.

Therefore, the third, fourth and fifth expansion valves Ex
a, Exb and Exc are the indoor heat exchangers Na and N as the condenser Cd when the high pressure gas refrigerant on the condenser Cd side is reduced by switching from the normal operation state to the defrosting operation state.
adjusting means 3 for adjusting the ratio of the refrigerant reduction rate of each of b and Nc
And the temperature sensors Sa, Sb, and Sc include first, second, and third air conditioning target zones Za, Z as heating targets.
Based on the heating states of b and Zc, each of the indoor heat exchangers Na, Nb, and Nc as the condenser Cd is configured as a determination unit that determines a heat radiation necessity.
Based on the determination information of the temperature sensors Sa, Sb, and Sc, the refrigerant reduction rate of the indoor heat exchangers Na, Nb, or Nc having a high heat radiation necessity is the refrigerant reduction rate of the indoor heat exchangers Na, Nb, or Nc having a low heat radiation necessity. Adjusting means 3 so as to be smaller than
Is configured as control means for controlling.

In this embodiment, the defrost control means 1
Numeral 01 is configured to perform a defrosting operation for a predetermined time by a built-in timer, and then automatically terminate the defrosting operation.

As the operation mode of the heat pump by the control unit H, a "cooling mode" and a "simultaneous cooling / heating mode" can be implemented in addition to the "heating mode".

The "cooling mode" is the switching valve v of the outdoor unit Uo.
2 and v4 are opened, and the switching valves v1 and v3 are closed, and the switching valves v6 of the indoor units Ua, Ub and Uc are opened,
In addition, by closing the switching valve v5, the outdoor heat exchangers N1 and N2 operate so as to function as the condenser Cd, and the indoor heat exchangers Na, Nb and Nc operate so as to function as the evaporator Ev.

The “simultaneous cooling / heating mode” is a mode in which the indoor units Ua, Ub
Or the indoor heat exchanger N functioning as the condenser Cd by opening and closing the respective switching valves v5 and v6 of Uc.
It is operated such that both a, Nb or Nc and the indoor heat exchanger Na, Nb or Nc functioning as the evaporator Ev are present. The “simultaneous cooling and heating mode” includes “simultaneous cooling and heating mode in which the outdoor heat exchanger functions as the evaporator Ev”.
And a “simultaneous cooling and heating mode in which the outdoor heat exchanger functions as the condenser Cd”.

[First Alternative Embodiment] In a heat pump type air conditioner similar to the above-described embodiment, as shown in FIG. 3, the condenser Cd side is switched from a normal operation state to a defrosting operation state. The adjusting means 3 for adjusting the ratio of the respective refrigerant reduction rates of the indoor heat exchangers Na, Nb, and Nc as the condenser Cd when the high-pressure gas refrigerant is reduced includes first, second, and third expansion valves ex1, ex2, and ex3, the control unit H controls the indoor heat exchangers Na and N in the defrosting operation state.
Defrosting control means 101 for controlling the adjusting means 3 so that the ratio of the refrigerant reduction rate of each of b and Nc becomes a set ratio, and changing means 4 for changing the set ratio in response to an artificial command may be provided. good.

The changing means 4 includes indoor heat exchangers Na and Nb.
And a change button 4b for setting and changing the refrigerant reduction rate by designating any one of the indoor heat exchangers, and a display section 4a for displaying each refrigerant reduction rate as a percentage value.
c is provided. The setting ratio of the refrigerant reduction rate is artificially set by operating the changing means 4 in consideration of the heat radiation necessity of each of the indoor heat exchangers Na, Nb, and Nc.

The defrosting control means 101 detects the refrigerant outlet temperature T1 detected by the temperature sensor S1 or S2 as in the above-described embodiment.
Alternatively, the defrosting operation is started as T2 decreases to a predetermined temperature lower than the normal value in the operation state of the “heating mode”. Then, the third, fourth and fifth expansion valves Ex as the adjusting means 3 are set in accordance with the set refrigerant reduction rate of the changing means 4.
The flow rates of the refrigerants a, Exb, and Exc are controlled.

[Second Alternative Embodiment] In a heat pump type air conditioner similar to the above-described embodiment, as shown in FIG. 4, the condenser Cd side is switched from a normal operation state to a defrost operation state. Condenser C
A regulating means 5 for always regulating the ratio of the respective refrigerant reduction rates of the indoor heat exchangers Na, Nb, Nc as d to a predetermined constant ratio may be provided.

In this embodiment, the defining means 5 comprises orifices Oa, Ob and Oc. The orifices Oa, Ob, and Oc are connected to detour paths sw provided in the liquid branch reflux pipes rw of the indoor units Ua, Ub, and Uc, respectively.
It is provided in.

In the bypass route sw and the liquid branch reflux tube rw,
Switching valves v7 and v8 as the switching means 2 are provided, and in conjunction with the switching valves v1 to v4 of the outdoor unit Uo, the refrigerant flow path is changed to the bypass path sw and the liquid branch return pipe. rw.

The defrost control means 101 reduces the detected refrigerant outlet temperature T1 or T2 of the refrigerant temperature sensor S1 or S2 to a predetermined temperature lower than the normal value in the "heating mode" operating state, as in the above-described embodiment. Then, the defrosting operation is started. During the defrosting operation, the third, fourth and fifth expansion valves Ex
The same control as in the normal operation state is performed for a, Exb, and Exc, but the flow rate of the refrigerant to the indoor heat exchangers Na, Nb, and Nc is interposed in the bypass path sw. Due to the action of the orifices Oa, Ob and Oc, the refrigerant is reduced at a specified constant refrigerant reduction ratio.

[Other Alternative Embodiments] (1) On the basis of the heating state of the first, second and third air conditioning target zones Za, Zb, Zc as heating targets, an indoor heat exchanger Na as a condenser Cd, The determination means for determining the necessity of heat release of each of Nb and Nc is not limited to the above-described temperature sensors Sa, Sb and Sc, and can be changed as appropriate. For example, the target air-conditioning temperature set by the remote controller installed in each of the air-conditioning target areas Za, Zb, and Zc, and the air-conditioning target areas Za, Zb,
The configuration may be such that the heat release necessity is determined based on the deviation of Zc from the air temperature.

(2) When the high pressure gas refrigerant on the condenser Cd side is reduced by switching from the normal operation state to the defrosting operation state, the indoor heat exchangers Na, Nb and Nc as the condenser Cd are used.
The adjusting means 3 for adjusting the ratio of the respective refrigerant reduction rates is not limited to the third, fourth and fifth expansion valves Exa, Exb and Exc for adjusting the refrigerant flow rate as in the above-described embodiment, but also for indoor heat exchange. It may be constituted by switching valves v5 and v6 for interrupting the flow of the refrigerant to the devices Na, Nb or Nc.

In this case, the defrost control means 101 determines the refrigerant outlet temperatures Ta, Ta detected by the condensation temperature sensors Sa, Sb and Sc.
Based on the values of Tb and Tc, or the set refrigerant reduction rate of the changing means 4, the indoor heat exchangers Na, which have the lowest degree of heat radiation,
The switching control of the switching valve v5 of each indoor unit Ua, Ub or Uc is performed so as to cut off the flow of the refrigerant to Nb or Nc.

(3) The defrosting means 1 is not limited to the one constituted by the outdoor heat exchangers N1 and N2 itself as in the above-described embodiment, but can be changed as appropriate. For example, high pressure gas refrigerant R
The heater through which h flows may be provided in the vicinity of the outdoor heat exchangers N1 and N2, or the defrosting stored water is heated and frosted by the heater through which the high-pressure gas refrigerant Rh flows. It may be configured such that water is sprayed to the outdoor heat exchanger N1 or N2. In the case of the heater-type defrosting means 1 described above, even if only one outdoor heat exchanger is configured, the defrosting operation can be performed without stopping the operation of the heat pump.

(4) The defrosting operation is started by the temperature sensor S1.
Alternatively, the present invention is not limited to the case based on the detected refrigerant outlet temperature T1 or T2 in S2, but can be changed as appropriate. For example, frost formation may be determined based on a change in the refrigerant outlet pressure to start the defrosting operation, or the timer may be used to start the defrosting operation at a set time. Further, the defrosting operation may be appropriately started by a manual operation.

(5) The air-conditioning target area does not need to be divided into the first, second and third air-conditioning target areas Za, Zb and Zc, and the air-conditioning target areas having the same air supply SAa, SAb and SAc. (For example, the same room).

Incidentally, reference numerals are written in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configuration of the attached drawings by the entry.

[Brief description of the drawings]

FIG. 1 is a configuration diagram showing the overall configuration of a heat pump air conditioner.

FIG. 2 is an explanatory diagram showing a control configuration of a defrosting unit.

FIG. 3 is an explanatory diagram illustrating a control configuration of a defrosting unit according to another embodiment.

FIG. 4 is an explanatory diagram showing a control configuration of a defrosting unit according to another embodiment.

[Explanation of symbols]

 Cd condenser Cmp compressor Ev evaporator Rh high-pressure gas refrigerant Rw condensed refrigerant Sa determining means Sb determining means Sc determining means Za heating object Zb heating object Zc heating object Ta heat radiation necessity Tb heat radiation necessity Tc heat radiation necessity 1 defrosting means 2 switching means 3 adjusting means 4 changing means 5 defining means 101 control means

Claims (3)

(57) [Claims] 1. A high-pressure gas refrigerant (Rh) delivered from a compressor (Cmp) is condensed to be heated (Za, Zb, Z).
c) a plurality of condensers (Cd) which radiate heat, and a condensed refrigerant (Rw) delivered from the condensers (Cd)
(Ev) that evaporates and absorbs heat, and a high-pressure gas refrigerant (R) sent from the compressor (Cmp).
h) as a heat medium for defrosting, a defrosting means (1) for defrosting the frosted evaporator (Ev) is provided, and a high-pressure gas refrigerant (Rh) for the defrosting means (1) is provided. ) Is stopped to supply the high-pressure gas refrigerant (Rh) from the compressor (Cmp) to the condenser (Cd) side and the supply amount of the high-pressure gas refrigerant to the condenser (Cd) side. A heat pump provided with a switching means (2) for switching a refrigerant path to a defrosting operation state in which the high pressure gas refrigerant (Rh) from the compressor (Cmp) is diverted and supplied to the defrosting means (1) in a reduced manner. The defrosting system according to any one of claims 1 to 3, wherein the heat radiation necessities (Ta, Tb, T) of the respective condensers (Cd) are based on the heating state of the objects to be heated (Za, Zb, Zc).
c) determining the high-pressure gas refrigerant on the condenser (Cd) side by switching from the normal operation state to the defrosting operation state, and determining the refrigerant of each of the condensers (Cd). Adjusting means (3) for adjusting the ratio of the reduction rate; and said determining means (Sa, S in said defrosting operation state).
b, Sc), the heat radiation necessity (Ta, T)
b, Tc), the refrigerant reduction rate of the condenser (Cd) is higher than that of the condenser (C) having a lower heat radiation requirement (Ta, Tb, Tc).
A defrost system for a heat pump, comprising: a control means (101) for controlling the adjusting means (3) so as to be smaller than the refrigerant reduction rate of d). 2. A high-pressure gas refrigerant (Rh) delivered from a compressor (Cmp) is condensed to be heated (Za, Zb, Z).
c) a plurality of condensers (Cd) which radiate heat, and a condensed refrigerant (Rw) delivered from the condensers (Cd)
(Ev) that evaporates and absorbs heat, and a high-pressure gas refrigerant (R) sent from the compressor (Cmp).
h) as a heat medium for defrosting, a defrosting means (1) for defrosting the frosted evaporator (Ev) is provided, and a high-pressure gas refrigerant (Rh) for the defrosting means (1) is provided. ) Is stopped to supply the high-pressure gas refrigerant (Rh) from the compressor (Cmp) to the condenser (Cd) side and the supply amount of the high-pressure gas refrigerant to the condenser (Cd) side. A heat pump provided with a switching means (2) for switching a refrigerant path to a defrosting operation state in which the high pressure gas refrigerant (Rh) from the compressor (Cmp) is diverted and supplied to the defrosting means (1) in a reduced manner. The defrosting system according to the above, wherein when the high pressure gas refrigerant on the condenser (Cd) side is reduced by switching from the normal operation state to the defrosting operation state, the ratio of the refrigerant reduction rate of each of the condensers (Cd) is adjusted. Means (3), in said defrosting operation state, Control means (101) for controlling the adjusting means (3) so that the ratio of the refrigerant reduction rates of the condensers (Cd) becomes a set ratio; and changing means (4) for changing the set ratio in response to an artificial command. )
And a defrosting system for a heat pump. 3. A high-pressure gas refrigerant (Rh) delivered from a compressor (Cmp) is condensed to be heated (Za, Zb, Z).
c) a plurality of condensers (Cd) which radiate heat, and a condensed refrigerant (Rw) delivered from the condensers (Cd)
(Ev) that evaporates and absorbs heat, and a high-pressure gas refrigerant (R) sent from the compressor (Cmp).
h) as a heat medium for defrosting, a defrosting means (1) for defrosting the frosted evaporator (Ev) is provided, and a high-pressure gas refrigerant (Rh) for the defrosting means (1) is provided. ) Is stopped to supply the high-pressure gas refrigerant (Rh) from the compressor (Cmp) to the condenser (Cd) side and the supply amount of the high-pressure gas refrigerant to the condenser (Cd) side. A heat pump provided with a switching means (2) for switching a refrigerant path to a defrosting operation state in which the high pressure gas refrigerant (Rh) from the compressor (Cmp) is diverted and supplied to the defrosting means (1) in a reduced manner. In the defrosting system according to the above, when the high pressure gas refrigerant on the condenser (Cd) side is reduced by switching from the normal operation state to the defrosting operation state, the ratio of the refrigerant reduction rate of each of the condensers (Cd) is always set to a predetermined value. A heat pump provided with a defining means (5) for defining a constant ratio Flop defrosting system.