JP2003194434A - Heat pump system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve an output of a heat pump, in a system allowing a hot water supply and air conditioning by means of using the heat pump which uses a material of a liquid phase at a normal temperature and a normal pressure, such as water, as a refrigerant. <P>SOLUTION: A system S1 comprises a first heat pump 10 including an air conditioner 10X and a second heat pump 20. In each of cooling mode and heating mode, chlorofluorocarbon (a first refrigerant) is circulated between an outdoor unit 11 and an indoor unit 12 of the air-conditioner 10X. In a hot water supply mode, by driving the heat pump 20, water (a second refrigerant) is evaporated at an evaporation means 22 and condensed in a second condensation means 24, and water for a hot water supply of a heating passage 44 is heated. In addition, while circulating the chlorofluorocarbon between the outdoor unit 11 and a first condensation means 31, it is evaporated at the outdoor unit 11 and condensed at a condensation means 31, and the evaporation means 22 is heated. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a system for cooling and heating or supplying hot water using a heat pump which uses a liquid phase substance (for example, water) as a refrigerant at room temperature and atmospheric pressure.

[0002]

BACKGROUND OF THE INVENTION Heat pumps using water as a refrigerant are known. In such a water-refrigerant heat pump, a compressor sucks an evaporator to a negative pressure to evaporate water and discharge the water to a condenser to obtain condensation heat. On the other hand, water is in the liquid phase at room temperature and atmospheric pressure, and the vapor pressure in the evaporator is considerably low. Therefore, in order to obtain the required output, the compressor must have a large capacity, and it was difficult to apply it to a general house.

[0003]

In order to solve the above problems, the heat pump system for hot water supply / cooling according to the present invention comprises first and second heat pumps. The first heat pump has an outdoor unit and an indoor unit that form an air conditioner, and a first condensing unit. This first
As the refrigerant of the heat pump, the first refrigerant in the gas phase at room temperature and atmospheric pressure such as CFC is used. The second heat pump is formed by sequentially connecting an expansion means, an evaporation means (second evaporation means), a compression means, and a second condensation means, and uses a second refrigerant in a liquid phase at room temperature and normal pressure, such as water, as a refrigerant. Evaporating means for evaporating the second refrigerant is thermally connected to the first condensing means. This thermal connection may be configured by circulating the second refrigerant between the evaporating means and the first condensing means, or may be configured by housing the first condensing means inside the evaporating means. . In the former thermal connection configuration, the amount of heat exchange can be adjusted by the circulation amount of the second refrigerant, and in the latter thermal connection configuration, the heat of condensation of the first refrigerant can be directly given to the second refrigerant, which improves thermal efficiency. Can be improved. The second condensing means for condensing the second refrigerant includes:
The hot water supply system is thermally connected. This hot water supply / cooling heat pump system has a cooling mode and a heating mode (first
Heating submode) and hot water supply mode are selectively executed. In the cooling mode, the first refrigerant of the first heat pump is circulated between the outdoor unit and the indoor unit while being condensed in the outdoor unit,
The room is cooled by evaporating it in the indoor unit. In the heating mode (first heating submode), the first refrigerant of the first heat pump is circulated between the outdoor unit and the indoor unit, evaporated in the outdoor unit, and condensed in the indoor unit to heat the interior of the room. I do. In the hot water supply mode, by driving the second heat pump, the second refrigerant is evaporated by the evaporation means and condensed by the second condensation means while passing through the expansion means, the evaporation means, the compression means, and the second condensation means in this order. , This condensing heat heats the hot water for hot water supply. Further, in the hot water supply mode, the first refrigerant of the first heat pump is supplied to the outdoor unit and the first refrigerant.
While circulating with the condensing means, evaporate in the outdoor unit,
The first refrigerant is condensed by the first condenser, and the heat of condensation heats the second refrigerant before evaporation by the evaporator. As a result, the vapor pressure of the second refrigerant can be increased, the output of the second heat pump can be increased, and the compression means need not be upsized. Moreover, since the first heat pump can be configured by an air conditioner generally provided in a house, the facility cost can be reduced.

The first heat pump may further have a third condensing means thermally connected to the hot water supply system.
Then, in the hot water supply mode, the first refrigerant is supplied to the outdoor unit and the first refrigerant.
The condenser means and the third condenser means are circulated in this order, evaporated by the outdoor unit, condensed by the first condenser means to heat the evaporation means of the second heat pump, and then further condensed by the third condenser means. Thus, the hot water for the hot water supply system can be heated to some extent prior to the heating by the second condensing means, and the hot water for hot water supply can be further heated.

The first heat pump may further have a first evaporation means thermally connected to the hot water supply system.
Then, in the heating mode, a second heating sub mode is set in addition to the first heating sub mode. When selecting the heating mode, one of the first and second heating sub modes is further selected and executed. In the second heating sub-mode, while circulating the first refrigerant between the first evaporating means and the indoor unit, the first evaporating means evaporates the hot water of the hot water supply system to condense it in the indoor unit. As a result, a large amount of heat can be dissipated into the room by using the heat supplied from the hot water supply system, and the heating can be quickly started. As a result, the load on the outdoor unit in the first heating sub mode can be reduced. It is desirable to select a sub-mode other than the first heating, that is, a second heating sub-mode when the heating starts, and to select the first heating sub-mode when the heating is steady. As a result, the heating can be started up quickly and the load on the outdoor unit in a steady state can be reduced.

Further, as the heating mode, a third heating sub mode may be set in addition to the first and second heating sub modes. When selecting the heating mode,
Further, one of the first to third heating sub modes is selected and executed. In the third heating submode, the first refrigerant discharged from the indoor unit is divided into two hands, one of which is passed through the first evaporating means to be vaporized, and the other of which is passed through the outdoor unit to be vaporized. The first refrigerants in the hands are brought together and condensed in the indoor unit. At the start of heating, the first
It is desirable to select a sub mode other than heating, that is, one of the second and third heating sub modes, and to select the first heating sub mode when the heating is stationary. As a result, a larger amount of heat can be dissipated into the room, heating can be started up more quickly, and the load on the outdoor unit in a steady state can be further reduced.

It is desirable that the third condensing means and the first evaporating means are constituted by a common heat exchange means. As a result, the structure can be simplified and the manufacturing cost can be reduced.

It is desirable that the first heat pump has a flow passage control means for controlling the flow passage of the first refrigerant according to the selected mode. That is, the cooling mode and the first
In the heating sub mode, the outdoor unit and the indoor unit are connected by the flow path control unit. The first condensing means and the third condensing means are shut off from the outdoor unit and the indoor unit. In the hot water supply mode, the outdoor unit and the first condensing unit are connected by the flow path control unit, and the indoor unit is shut off from the outdoor unit. In the second heating submode, the indoor unit and the second evaporation unit are communicated by the flow path control unit, and the outdoor unit is shut off from the indoor unit. In the third heating submode, the first refrigerant discharged from the indoor unit is split into the second evaporation unit and the outdoor unit by the flow dividing unit of the flow path control unit. Further, the second evaporating means and the first refrigerant discharged from the outdoor unit are combined by the merging portion of the flow path controlling means, and are sent to the indoor unit. This makes it possible to reliably control the flow path of the first refrigerant for each mode.

It is desirable that each means of the first heat pump (that is, the first and third condensing means, the first evaporating means and the flow path controlling means) and the second heat pump are housed in one casing. As a result, the system can be made compact and the installation work can be made efficient.

The heat pump system for hot water supply according to the present invention comprises first and second heat pumps and a hot water supply system. The first heat pump is for evaporating a first refrigerant in a gas phase at room temperature and normal pressure, such as CFCs, and then compressing the first refrigerant. The first heat pump includes a first condensing means for condensing the compressed first refrigerant and the first condensing means. And a third condensing means for further condensing the first refrigerant that has passed through. The second heat pump is for evaporating a second refrigerant in a liquid phase at room temperature and normal pressure such as water and then compressing it. The second heat pump evaporating means (second evaporating means) and the second refrigerant after compression are compressed. And a second condensing means for condensing. The evaporation means is thermally connected to the first condensing means of the first heat pump. This thermal connection may be configured by circulating the second refrigerant between the evaporating means and the first condensing means, or may be configured by housing the first condensing means inside the evaporating means. . In the former thermal connection configuration, the amount of heat exchange can be adjusted by the circulation amount of the second refrigerant, and in the latter thermal connection configuration, the heat of condensation of the first refrigerant can be directly given to the second refrigerant, which improves thermal efficiency. Can be improved. The hot water supply system is
It has a heating path for passing hot water. The heating path is thermally connected to the third condensing means of the first heat pump and the second condensing means of the second heat pump sequentially from the upstream side.
According to this hot water supply heat pump system, the vapor pressure of the second refrigerant of the second heat pump can be increased by the condensation heat of the first refrigerant of the first heat pump. This makes it possible to obtain a large amount of the second refrigerant vapor, which can be condensed by the second condensing means to sufficiently heat the hot water. Thus, the efficiency of hot water supply can be increased,
As a result, it is possible to reduce the size of the compression means in the heat pump that uses a liquid-phase substance as a refrigerant at room temperature and atmospheric pressure, such as water. Further, the hot water for hot water supply can be heated to some extent prior to the heating by the second condensing means, and the hot water for hot water supply can be further heated.

In the second heat pump of the hot water supply heat pump system, the second refrigerant is water, and the evaporating means has a vertically extending container shape and stores water up to its upper side. By accommodating the first condensing means of the first heat pump, these means are thermally connected to each other, and by accommodating the third condensing means in the lower side part of the evaporating means, the lower side of the evaporating means is accommodated. Part is provided as a thermal connection part to the third condensing means in the heating path, and the heating path further reduces the pressure of the hot water to be heated and sends it to the lower side of the evaporation means. Part and
It may have a water intake passage part which takes in water from an intermediate part of the evaporation means and sends it to the second condensing means. Thereby, the thermal efficiency can be further improved.

In the hot-water supply / cooling / heating heat pump system and the hot-water supply heat pump system, a gas injection mechanism for injecting a non-condensable gas such as air in an unsaturated state into the second refrigerant before evaporation in the evaporation means of the second heat pump. Is preferably connected. In this specification, the case where the gas phase molecules of the second refrigerant are contained in the non-saturated state in the non-condensable gas and the case where they are contained at all are collectively referred to as “unsaturated”. This non-condensable gas becomes bubbles and the second liquid phase
In the process of moving in the refrigerant, the second refrigerant molecules are evaporated into the bubbles. That is, the second refrigerant of the evaporation means evaporates not only from the free liquid surface of the second refrigerant but also into bubbles. afterwards,
The non-condensable gas is further sucked into the compression means and discharged to the condensation means. As a result, the amount of evaporation of the second refrigerant and thus the heat of condensation can be further increased, and the output of the second heat pump can be improved. Further, not only the evaporated second refrigerant molecules but also the injected gas can be sucked into the compression means, and the compression ratio can be reduced, so that the compression means can be further downsized.

[0013]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a heat pump system S1 for hot water supply / cooling of a house according to a first embodiment of the present invention. The system S1 includes a CFC heat pump 10 (first heat pump) and a water-refrigerant heat pump 2
It is provided with 0 (second heat pump) and a hot water supply system 40.

First, the hot water supply system 40 will be described. The hot water supply system 40 includes a hot water storage tank (hot water storage tank) 41, a water supply path 42 connected to the lower end of the hot water storage tank 41, and a hot water storage tank 41.
Hot water supply passage 43 extending from the upper end of the hot water storage tank 4
A heating passage 44 connected to both upper and lower ends of the No. 1 and a water feed pump 45 provided in the heating passage 44 are provided. The inside of the hot water storage tank 41 is filled with hot water for hot water supply supplied from the water supply pipe 42. The water in the lower part of the hot water storage tank 41 is guided to the heating passage 44 by the water supply pump 45, heated by passing through the condenser 24 described later, and then sent to the upper part of the hot water storage tank 41. Has become. As a result, the upper water in the hot water storage tank 41 is hot water. This hot water is supplied to the hot water through the hot water supply passage 43.

Next, the water-refrigerant heat pump 20 will be described. The water-refrigerant heat pump 20 is configured by sequentially connecting a pressure reducing valve 21 (expansion means), an evaporator 22 (evaporation means), a compressor 23 (compression means), and a condenser 24 (second condensation means) in an annular shape. There is. The evaporator 22 has a tank shape, and stores water for the refrigerant (second refrigerant in liquid phase at normal temperature and pressure). After the vapor evaporated from the water surface (gas phase molecule of the second refrigerant) is sucked into the compressor 23 and compressed,
It is adapted to be discharged to the condenser 24. Condenser 24
Is a counterflow heat exchanger having a pair of heat transfer coils 24a and 24b. The discharge port of the compressor 23 and the primary port of the pressure reducing valve 21 are connected to both ends of the heat transfer coil 24a. The water vapor is condensed in the heat transfer coil 24a to generate heat of condensation. The heat transfer coil 24b is interposed in the heating passage 44 downstream of the water feed pump 45. As a result, the heat of condensation is transferred to the hot water supply water in the heating passage 44. The condensed refrigerant water is decompressed by the decompression valve 21 and then returned to the evaporator 22.

Next, the chlorofluorocarbon heat pump 10 will be described. The Freon heat pump 10 is a heat pump that uses Freon (first refrigerant in a gas phase at room temperature and normal pressure) as a refrigerant,
Air conditioner 10X commonly used in homes
And a condenser 31 (first condensing means). As is well known, the air conditioner 10X includes an outdoor unit 11 and an indoor unit 12. The outdoor unit 11 is provided with a compressor 13, an outdoor evaporative condenser 15 connected to the compressor 13 via an electromagnetic directional control valve 14, and an expansion valve 16 connected to the outdoor evaporative condenser 15. Has been.

The directional control valve 14 of the outdoor unit 11 is a 2-position 4-port valve having a heating hot water supply position 14a and a cooling position 14b. At the hot water supply position 14a, the outdoor evaporative condenser 15 is connected to the suction port of the compressor 13, and
The discharge port of the compressor 13 is connected to the electromagnetic directional control valve 17 described later. On the other hand, in the cooling position 14b,
The electromagnetic directional control valve 17 is connected to the suction port of the compressor 13, and the discharge port of the compressor 13 is connected to the outdoor evaporative condenser 15.

The outdoor unit 11 of the air conditioner 10X
Between the indoor unit 12 and the indoor unit 12, a pair of electromagnetic directional control valves 17, 1
8 (flow path control means) is interposed. The electromagnetic directional control valve 17 is a two-position three-port valve having a cooling / heating position 17a and a hot water supply position 17b. At the cooling / heating position 17a, the valve 14 of the outdoor unit 11 and thus the compressor 13 is connected to the one end 12a of the indoor unit 12. On the other hand, at the hot water supply position 17b, the valve 14 and thus the compressor 13 are connected to the condenser 3
1 is connected to one end of a heat transfer coil 31a described later.

Similarly, another electromagnetic directional control valve 18
Is also a 2-position 3-port valve having a cooling / heating position 18a and a hot water supply position 18b. Then, at the cooling / heating position 18 a, the expansion valve 16 of the outdoor unit 11 and the other end 12 b of the indoor unit 12
It is designed to connect with. On the other hand, the hot water supply position 18b
Then, the other end of the heat transfer coil 31a described later is connected to the expansion valve 16. The electromagnetic directional control valves 17, 1
Any one of 8 may be provided, and the other may be omitted.

The condenser 31 of the Freon heat pump 10 is
It is composed of a counterflow heat exchanger having a pair of heat transfer coils 31a and 31b. As described above, the heat transfer coil 3
Both ends of 1a are connected to electromagnetic directional control valves 17 and 18, respectively. The upstream end of the heat transfer coil 31b is connected to the evaporator 22 of the water-refrigerant heat pump 20 via the water pump 39.
It is connected to the lower part of. The downstream end of the heat transfer coil 31b is connected to the upper end of the evaporator 22.

Further, the hot water supply / cooling heat pump system S1 is provided with a controller 90 (control device) which controls the whole. The controller 90 operates the compressors 13, 23, the water pumps 39, 45, the directional control valves 14, 17, 18 and the like according to a user's instruction, time zone, etc., and selects a cooling mode, a heating mode, a hot water supply mode (hot water storage mode). ) Is selectively executed. The contents of execution in each mode will be described below.

When the user gives an instruction for cooling operation (including timer reservation) by a remote controller (not shown) attached to the air conditioner 10X, the controller 90
Executes the cooling mode. In this mode, the directional control valve 14 is located at the cooling position 14b, and the directional control valves 17 and 18 are located at the cooling and heating positions 17a and 18a. Then, the compressor 13 of the outdoor unit 11 is driven. As a result, the first refrigerant (CFC) of the air conditioner 10X is compressed by the compressor 13 → the directional control valve 14 → the outdoor evaporative condenser 15 → the expansion valve 16 → the directional control valve 18 → the indoor unit 12
-> Direction control valve 17-> Direction control 14-> Compressor 13 is circulated in order. Then, it is condensed in the outdoor evaporative condenser 15 to radiate heat to the outside, and evaporated in the indoor unit 12 to collect heat from the room. Thereby, the room can be cooled.

When the user gives an instruction for heating operation (including timer reservation) using the remote controller or the like, the controller 90 executes the heating mode. In this mode, the directional control valve 14 is located at the heating / hot water supply position 14a, and the directional control valves 17 and 18 are located at the cooling / heating positions 17a and 18a.
Is located in. Then, the compressor 13 is driven. As a result, the first refrigerant (CFC) of the air conditioner 10X moves from the compressor 13 to the directional control valve 14 to the directional control valve 1.
It is circulated in the order of 7 → indoor unit 12 → directional control valve 18 → expansion valve 16 → outdoor evaporative condenser 15 → directional control valve 14 → compressor 13. Then, it is evaporated in the outdoor evaporative condenser 15 to collect heat from the outside, is condensed in the indoor unit 12, and is radiated indoors. As a result, the room can be heated.

The controller 90 monitors the time with a built-in clock function, and automatically executes a hot water supply mode (hot water storage mode) at midnight every night, for example. At this point, if the cooling mode or the heating mode is being executed, for example, the cooling mode or the heating mode and the hot water supply mode are alternately executed at regular time intervals. By running the hot water supply mode at midnight, the electricity usage fee can be reduced.

In the hot water supply mode, the water refrigerant heat pump 20
The compressor 23 is driven. As a result, the second refrigerant (water) of the heat pump 20 is compressed by the compressor 23 → the condenser 24 →
The pressure reducing valve 21 is circulated in the order of the evaporator 22 and the compressor 23. Then, it is evaporated in the evaporator 22 and condensed in the condenser 24 to release the heat of condensation. Further, the water supply pump 4 of the hot water supply system 40
5 is driven. As a result, the hot water supply water in the lower part of the hot water storage tank 41 is taken into the heating passage 44, the condenser 24 receives the condensation heat, and becomes hot water and is stored in the upper part of the hot water storage tank 41.

Further, in the hot water supply mode, the water supply pump 39
Is driven. As a result, the liquid phase water in the lower portion of the evaporator 22 is guided to the heat transfer coil 31b of the condenser 31. Also,
The directional control valve 14 is located at the heating / hot water supply position 14a, and the directional control valves 17 and 18 are at the hot water supply positions 17b and 18b.
Is located in. Then, the compressor 13 is driven. As a result, the CFC of the air conditioner 10X is compressed by the compressor 13, the directional control valve 14, the directional control valve 17, and the condenser 3.
1 heat transfer coil 31a → direction control valve 18 → expansion valve 16 →
The outdoor evaporative condenser 15 is circulated in the order of the directional control valve 14 and the compressor 13. Then, it is evaporated in the outdoor evaporative condenser 15,
It condenses with the heat transfer coil 31a. The heat of condensation heats the water passing through the heat transfer coil 31b to, for example, about 60 ° C., and then returns the water to the evaporator 22. As a result, the vapor pressure of water in the evaporator 22 can be increased. Therefore, even if the compressor 23 is small, a large amount of steam can be obtained, and thus a large amount of heat of condensation can be generated in the condenser 24 to sufficiently heat the hot water. In the present system S1, the evaporator 22 is heated by using the outdoor unit 11 of the air conditioner 10X that is generally provided in a house, so a new heat source for heating the evaporator 22 is newly installed. There is no need, and the equipment cost can be reduced.

Next, another embodiment of the present invention will be described.
In the following embodiments, the same reference numerals will be given to the drawings for the configurations overlapping with the above-described embodiments, and the description will be simplified. FIG. 2 shows a heat pump system S2 for hot water supply / cooling according to the second embodiment. In this system S2, the water-refrigerant heat pump 20 has an air injection mechanism 25.
(Gas injection mechanism) is provided. Air injection mechanism 25
Is an air injection path 26 (gas injection path) and this injection path 26
And an air pressure reducing valve 27 (gas expanding means) provided in the. The upstream end of the air injection path 26 is open to the atmosphere, and the downstream end is connected to the lower end of the evaporator 22.

A gas-liquid separator 28 is provided between the condenser 24 and the pressure reducing valve 21 of the system S2. The lower part of the gas-liquid separator 28 is connected to the pressure reducing valve 21, and the upper part is open to the atmosphere.

In the hot water supply mode of the system S2, when the compressor 23 of the water refrigerant heat pump 20 is driven, the outside air (non-condensable gas) is taken into the injection path 26 by the suction action, and the pressure is reduced by the pressure reducing valve 27. To be done. This ensures that the air is in an unsaturated state.
This unsaturated air flows from the downstream end of the injection path 26 to the evaporator 2
(2) It is mixed with water before evaporation (liquid-phase second refrigerant) in the lower part, and rises as bubbles in water. Surrounding water molecules (molecules of the second refrigerant) evaporate in the bubbles during the ascent. That is,
Evaporation of water molecules occurs not only from the water surface (free liquid surface) of the evaporator 22 but also in water. Thereby, the evaporation amount can be further increased.

Eventually, the bubbles will emerge from the water surface to the top of the evaporator 22. As a result, the compressor 23 sucks not only water molecules but also air molecules. Therefore, the suction pressure increases and the compression ratio (= discharge pressure / suction pressure) decreases. Therefore, the compressor 23 can be reliably downsized. And
A large amount of water molecules can be compressed and condensed in the condenser 24 to obtain a large amount of heat of condensation. As a result, the water for hot water supply in the heating passage 4 can be heated more sufficiently, and the efficiency of hot water storage and hot water supply can be improved.

The air and water that have passed through the condenser 24 are sent to a gas-liquid separator 28 and separated into upper and lower parts. Then, the air in the upper portion is connected to the outside air, and the water in the lower portion is sent as a refrigerant toward the pressure reducing valve 21. The upper end of the injection path 26 may be connected to the upper part of the gas-liquid separator 28 so that the air in the upper part of the gas-liquid separator 28 is recirculated and injected into the lower part of the evaporator 22. This allows a closed system to be constructed. Alternatively, the injection passage 26, the pressure reducing valve 27, and the gas-liquid separator 28 may be omitted, and air may be mixed into the refrigerant water from the beginning. In this case, the decompression valve 21 decompresses not only the refrigerant water but also the air to an unsaturated state, and this unsaturated air is injected into the evaporator 22 via the refrigerant passage downstream of the decompression valve 21, The pressure reducing valve 21 and the refrigerant passage downstream thereof are provided as a “gas injection mechanism”. Then, the injection passage 26 and the pressure reducing valve 27 dedicated to the non-condensable gas are unnecessary, and the cost can be reduced.

FIG. 3 shows a hot water supply / cooling heat pump system S3 according to a third embodiment of the present invention. In this system S3, the air conditioner 10
Between the outdoor unit 11 and the indoor unit 12 of X, the casing 50
Are arranged. The casing 50 accommodates the direction control valves 17, 18, the condenser 31, the water-refrigerant heat pump 20, and the water supply pumps 39, 45, which are unitized. As a result, the system can be made compact and the installation work in the house can be easily performed. The water refrigerant heat pump 2 of the system S3
0, the gas injection mechanism described in the second embodiment may be provided.

FIG. 4 shows a heat pump system S4 for hot water supply / cooling / heating according to a fourth embodiment of the present invention. The chlorofluorocarbon heat pump 10 of this system S4 further includes a counter-flow type heat exchanger 32 (a common heat exchange unit that also serves as a first evaporation unit and a third condensation unit) having a pair of heat transfer coils 32a and 32b. ing. One end of one heat transfer coil 32a is connected to the heat transfer coil 31a of the condenser 31 (first condensing means), and the other end is connected to the first refrigerant circulation pump 19 which is a variable channel pump. This circulation pump 19 is connected to the electromagnetic directional control valve 18X.

In the warming passage 44 of the system S4, in place of the water feeding pump 45 for flowing water only in the forward direction of the warming passage 44, a water feeding pump 45X composed of a variable flow pump capable of flowing water in both forward and reverse directions. Is provided. This water pump 45
The other heat transfer coil 32 b of the heat exchanger 32 is interposed in the heating path 44 between the condenser 24 and the condenser 24. Heat exchanger 32
The pumps 19 and 45X are housed in a casing 50.

In the system S4, as the flow path control means,
4 in place of 2-position 3-port electromagnetic directional control valves 17, 18
Three-position electromagnetic directional control valves 17X and 18X are used. The directional control valve 17X has, in addition to the cooling / heating position 17a and the hot water supply position 17b similar to those of the directional control valve 17,
It has a second heating position 17c and a third heating position 17d. At the second heating position 17c, the heat transfer coil 32a of the heat exchanger 32 is connected to the one end 12a of the indoor unit 12 via the heat transfer coil 31a of the condenser 31. Third
At the heating position 17d (merging portion of the flow path control means), the heat transfer coil 32a is connected to the one end 12a of the indoor unit 12 via the heat transfer coil 31a, and the valve 14 of the outdoor unit 11 and thus the compressor 13 is also indoors. It is adapted to be connected to one end 12a of the machine 12. That is, the CFCs from the heat exchanger 32 and the CFCs from the compressor 13 are merged and sent to the indoor unit 12.

The directional control valve 18X includes a cooling / heating position 18a,
Hot water supply position 18b, second heating position 18c, third heating position 1
It has 8d. At the cooling / heating position 18a, the expansion valve 16 of the outdoor unit 11 is connected to the indoor unit 1 in the same manner as the direction control valve 18 described above.
2 is connected to the other end 12b. At the hot water supply position 18b, the circulation pump 19 and thus the heat transfer coil 32a of the heat exchanger 32 and the heat transfer coil 31a of the condenser 31 are connected to the expansion valve 16. Second heating position 1
In 8c, the other end 12b of the indoor unit 12 is connected to the circulation pump 19 and further to the heat transfer coil 32a of the heat exchanger 32. At the third heating position 18d (the flow dividing portion of the flow path control means), the other end 12b of the indoor unit 12 is connected to the circulation pump 1
9 and the heat transfer coil 32a of the heat exchanger 32, and also the expansion valve 16 of the outdoor unit 11. That is, the chlorofluorocarbon from the indoor unit 12 is split into two hands, a part of the first refrigerant is sent to the heat exchanger 32, and the remaining chlorofluorocarbon is sent to the expansion valve 16.

In the system S4, in the cooling mode,
The same operation as that of the system S1 is executed. In the hot water supply mode, the compressor 23 of the water-refrigerant heat pump 20 is driven as in the system S1. The water pump 45X is
It is driven in the forward direction, that is, hot water supply water is taken from the lower part of the hot water storage tank 41 into the heating passage 44 and flows toward the upper part of the hot water storage tank 41. Further, the compressor 13 of the outdoor unit 11 is driven, the directional control valve 14 is located at the heating hot water supply position 14a, and the directional control valves 17X and 18X are located at the hot water supply positions 17b and 1b.
It is located at 8b. Further, the circulation pump 19 is driven so as to flow the Freon from the heat exchanger 32 toward the valve 18X.

As a result, the chlorofluorocarbon is transferred to the compressor 13, the directional control valve 14, the directional control valve 17X, the heat transfer coil 31a of the condenser 31, the heat transfer coil 32a of the heat exchanger 32, the flow pump 19 and the directional control valve 18X. → The expansion valve 16 → the outdoor evaporative condenser 15 → the directional control valve 14 → the compressor 13 is circulated in this order. Then, it is evaporated in the outdoor evaporative condenser 15, and the condenser 31
In the heat exchanger 32 and further in the heat exchanger 32. The heat of condensation in the condenser 31 is transferred to the evaporator 22 of the water-refrigerant heat pump 20 to increase the output of the water-refrigerant heat pump 20. The heat of condensation in the heat exchanger 32 is transferred to the hot water for hot water supply in the heating passage 44. Therefore, the water for hot water supply is slightly heated and then further heated by the condenser 24 of the water-refrigerant heat pump 20. This makes it possible to raise the temperature of the hot water for hot water supply further.

In the heating mode, the controller 90 of the system S4 further selects and executes one of the first to third heating sub modes. In the first heating submode, the same operation as in the heating mode of the system S1 is executed.

In the second heating sub mode, the water pump 45
X is driven in the opposite direction to the hot water supply mode. As a result, the hot water in the upper portion of the hot water storage tank 41 is guided to the heating passage 44 and passes through the heat transfer coil 32a of the heat exchanger 32,
Further, it is sent to the lower part of the hot water storage tank 41 via the water pump 45X. Further, the directional control valves 17X and 18X are located at the second heating positions 17c and 18c, and the flow pump 19 is in the direction opposite to the hot water supply mode (the CFC valve 18X is used).
The heat exchanger 32 is driven to the heat exchanger 32).

As a result, the chlorofluorocarbon is distributed to the circulation pump 19
The heat transfer coil 32a of the heat exchanger 32, the heat transfer coil 31a of the condenser 31, the directional control valve 17X, the indoor unit 12, the directional control valve 18X, and the circulation pump 19 are circulated in this order. This chlorofluorocarbon receives a large amount of heat from the hot water of the heat transfer coil 32b and evaporates while passing through the heat transfer coil 32a of the heat exchanger 32. As a result, a large amount of heat of condensation can be released during the condensation process in the indoor unit 12.

Therefore, if the second heating sub-mode is selectively executed when the heating is started, the room can be quickly warmed and the heating can be started in a short time. This can improve comfort. Then, when the heating is in a substantially steady state (when the room temperature is within the target temperature range), it is preferable to switch to the first heating sub mode. Thereby, the load on the compressor 13 of the outdoor unit 11 can be reduced and the economical efficiency can be improved.

Next, the third heating submode will be described. In the third heating sub mode, the water supply pump 45X and the circulation pump 19 are driven in the same direction as the second heating sub mode. Further, the directional control valves 17X and 18X are located at the third heating positions 17d and 18d. Further, the direction control valve 14 of the outdoor unit 11 is located at the heating / hot water supply position 14a, and the compressor 13 is driven.

As a result, the chlorofluorocarbon coming out from the other end of the indoor unit 12 is divided into two hands at the directional control valve 18X, and a part of the chlorofluorocarbon is supplied to the directional control valve 18X → circulation pump 19 → heat exchanger 3
2 heat transfer coil 32a → heat transfer coil 31a of condenser 31
→ Direction control valve 17X flows in this order, and the rest is direction control valve 1
8X → expansion valve 16 → outdoor evaporative condenser 15 → direction control valve 1
It flows in order of 4 → compressor 13 → direction control valve 14 → direction control valve 17X. As a result, some of the CFCs receive a large amount of heat from the hot water in the heat exchanger 32 and evaporate, while the other CFCs collect heat from the outdoor in the outdoor evaporative condenser 15 and evaporate.

Then, these two first refrigerants merge at the direction control valve 17X and head for the indoor unit 12. This allows the indoor unit 12 to release a larger amount of condensation heat. Therefore, the room can be warmed more quickly, and the heating start-up time can be further shortened.

When the indoor temperature is much lower than the target temperature by a predetermined amount, such as in a cold winter morning, the third
The heating may be started up in the heating sub mode, and when it is within the predetermined amount, the heating may be started up in the second heating sub mode. The second heating submode or the third heating submode may be executed in advance before executing the hot water supply mode (hot water storage mode) at midnight. by this,
The inside of the hot water storage tank 41 can be heated to a low temperature and then boiled, and the coefficient of performance of the heat pump 20 can be improved. The water refrigerant heat pump 2 of the system S4
0, the gas injection mechanism described in the second embodiment may be provided.

FIG. 5 shows a heat pump system S5 dedicated to hot water supply according to a fifth embodiment of the present invention.
This hot water supply heat pump system S5 includes the indoor unit 12 and the direction control valve 14 in the system S4 of the fourth embodiment.
17X and 18X and the circulation pump 19 are omitted. Further, instead of the outdoor evaporative condenser 15, an evaporator 15A dedicated to evaporation is provided. In this system S5, the Freon heat pump 10 is configured by sequentially connecting the expansion valve 16, the evaporator 15A, the compressor 13, the condenser 31 (first condensing means), and the condenser 32X (third condensing means) in an annular shape. Has been done. The configuration itself of the condenser 32X is the same as that of the heat exchanger 32 which also serves as the first evaporating means and the third condensing means in the system S4.

In the water / refrigerant heat pump 20 of the system S5, air as a non-condensable gas is mixed in the refrigerant water from the beginning. Therefore, the decompression valve 21 decompresses not only the coolant water but also the air to bring it into an unsaturated state. This unsaturated air is injected into the evaporator 22 via the refrigerant passage 20a between the pressure reducing valve 21 and the evaporator 22. Thereby, the pressure reducing valve 21 and the refrigerant passage 20a are provided as a "gas injection mechanism". Condenser 24 and pressure reducing valve 21
An atmosphere opening passage 29 for letting air in and out is provided in the refrigerant passage between the and.

During hot water storage, the compressors 13, 23 of the heat pumps 10, 20 and the water pumps 39, 45 are driven.
By driving the compressor 13 of the freon heat pump 10, the freon is expanded by the expansion valve 16, evaporated by the evaporator 15A, and compressed by the compressor 13. Then, after being condensed by the heat transfer coil 31a of the condenser 31, it is further condensed by the heat transfer coil 32a of the condenser 32X. Further, by driving the water supply pump 29, the refrigerant water on the lower side of the evaporator 22 of the water-refrigerant heat pump 20 is passed through the heat transfer coil 31 b of the condenser 31 and returned to the upper side of the evaporator 22. As a result, the fourth
Similar to the hot water supply mode of the embodiment, the refrigerant water in the evaporator 22 can be heated by the condensation heat of the freon in the condenser 31 to increase the vapor pressure, and thus the water refrigerant heat pump 2
The output of 0 can be increased. Furthermore, water pump 4
By driving 5, the hot water supply water in the lower part of the hot water storage tank 41 is returned to the upper part of the hot water storage tank 41 through the heat transfer coil 32b of the condenser 32X and the heat transfer coil 24b of the condenser 24 in sequence. As a result, the hot water for hot water supply can be heated slightly by the condenser 32X and then heated further largely by the condenser 24. As a result, the hot water for hot water supply can be further heated.

FIG. 6 shows a hot water supply heat pump system S6 according to a sixth embodiment of the present invention. In this system S6, as the first condensing means of the Freon heat pump 10, instead of the condenser 31 composed of the counterflow heat exchanger of the system S5, a condenser 3 composed of heat transfer coils.
1X is provided. The condenser 31X is housed (thermally connected) in the evaporator 22 of the water-refrigerant heat pump 20 and immersed in the refrigerant water. Thereby, the heat of condensation of CFCs in the condenser 31X can be directly transferred to the coolant water, and the thermal efficiency can be improved. Further, the water supply pump 39 for heat exchange becomes unnecessary.

FIG. 7 shows a hot water supply heat pump system S7 according to a seventh embodiment of the present invention. In this system S7, the evaporator 2 of the water refrigerant heat pump 20
2 has a container shape extending vertically. This evaporator 2
Liquid refrigerant water is stored in 2 until it is almost full. A pressure reducing valve 2 is provided at a substantially middle portion in the vertical direction of the evaporator 22.
The refrigerant passages 20a from 1 are connected.

The heating passage 44 of the system S7 extends from the lower side portion of the hot water storage tank 41 and extends to the lower end portion of the evaporator 22, and the water passage portion 44a extends from substantially the middle portion of the evaporator 22 in the vertical direction to store hot water. It has a return water channel portion 44b (intake channel portion) connected to the upper side of the tank 41. Water passage section 44
A pressure reducing valve 46 (water supply passage partial pressure reducing means) is provided in a. A water supply pump 45 and a heat transfer coil 24b of the condenser 24 are sequentially interposed in the return water passage portion 44b from the evaporator 22 side.

The Freon heat pump 10 of the system S7 is provided with a condenser 33 composed of one heat transfer coil. The condenser 33 is accommodated (thermally connected) inside the evaporator 22 of the water-refrigerant heat pump 20 so as to extend vertically, and is entirely immersed in the coolant water. The upper part of the condenser 33 is provided as the first condensing means 33a, and the lower part is provided as the third condensing means 33b. The upper end of the first condensing means 33a is connected to the discharge port of the compressor 13, and the lower end of the third condensing means 33b is connected to the primary port of the expansion valve 16.

The lower portion of the evaporator 22 in which the third condensing means 33b is housed is provided as a thermal connection portion of the heating passage 44 with the third condensing means 33b. The water supply passage portion 44a and the return water passage portion 44b of the heating passage are connected to each other via this thermal connection portion.

In the system S7, when storing hot water, the compressors 13 and 23 of the heat pumps 10 and 20 and the water supply pump 45 of the hot water supply system 40 are driven. As a result, in the heat pump 10, CFCs are evaporated in the evaporator 15A and the condenser 3
Condensate at 3. This heat of condensation, especially the upper first condensing means 3
The vapor pressure of water in the evaporator 22 can be increased by the heat of condensation at 3a, and thus the output of the water-refrigerant heat pump 20 can be increased.

Further, the water for hot water supply at the lower side of the hot water storage tank 41 is taken into the water supply passage portion 44a, decompressed by the pressure reducing valve 46, and then injected into the lower side of the evaporator 22, and mixed with the refrigerant water. The water on the lower side of the evaporator 22, that is, the water on the portion of the heating path 44 that is thermally connected to the third condensing means 33b is directly heated by condensing heat of the third condensing means 33b. Thereby, the thermal efficiency can be further improved. Then, by driving the water supply pump 45, the heated water is taken out from the intermediate portion of the evaporator 22 to the return water passage portion 44b as hot water supply water. This water can be further heated by the condenser 24 of the water-refrigerant heat pump 20. As a result, the hot water for hot water supply can be reliably heated to a high temperature and sent to the upper portion of the hot water storage tank 41.

The present invention is not limited to the above embodiment, and various forms can be adopted. For example, the upstream end of the pressure reducing valve 21 of the water-refrigerant heat pump 20 is connected to the water supply pipe (second refrigerant supply source) instead of the condenser 24, and the downstream end of the condenser 24 is opened or connected to the hot water storage tank 41. May be. The first condensing means of the first heat pump may be connected to the second refrigerant passage between the expanding means and the evaporating means of the second heat pump.

In the gas injection mechanism, the non-condensable gas is
In addition to air, helium or nitrogen may be used. In short, any substance that does not change its phase as a gas in the operating region of the second heat pump may be used. The communication position of the gas injection mechanism to the evaporation means is preferably in the lower part, but is not limited to the lower part as long as it is a part facing the liquid phase second refrigerant. The discharge path is preferably the upper part of the evaporating means, but is not limited to the upper part as long as it is a part capable of sucking gas from the evaporating means. As the expansion means for expanding and reducing the pressure of the non-condensable gas or the second refrigerant, an expander such as a turbine may be used instead of the pressure reducing valve (expansion valve). It is also possible to omit the pressure reducing valve 27 by reducing the flow cross-sectional area of the injection passage 26 to have a pressure reducing action.

In the fourth embodiment, a system without the third heating submode (the heating mode is only the first and second heating submodes) may be constructed. The first evaporating means and the third condensing means may be configured separately from each other instead of the common heat exchanging means. The first evaporation means may be in the form of a heat transfer coil and housed in the upper portion of the hot water storage tank 41.

[0060]

As described above, according to the heat pump system for hot water supply / cooling / heating according to the present invention, each mode of cooling, heating and hot water supply can be selectively executed.
In the hot water supply mode, the vapor pressure of the second refrigerant of the second heat pump can be increased by the heat of condensation of the first refrigerant of the first heat pump. As a result, a large amount of the vapor of the second refrigerant can be obtained, which can be condensed by the second condensing means to sufficiently heat the hot water for hot water supply. As a result, it is possible to reduce the size of the compression means in the heat pump that uses a liquid phase substance such as water at room temperature and atmospheric pressure as a refrigerant. Moreover, since the first heat pump can be configured by the air conditioner generally provided in the house, the facility cost can be reduced.

According to the heat pump system for hot water supply according to the present invention, the vapor pressure of the second refrigerant of the second heat pump can be increased by the heat of condensation of the first refrigerant of the first heat pump. As a result, a large amount of the vapor of the second refrigerant can be obtained, which can be condensed by the second condensing means to sufficiently heat the hot water for hot water supply. As a result, it is possible to reduce the size of the compression means in the heat pump that uses a liquid phase substance such as water at room temperature and atmospheric pressure as a refrigerant. Further, the hot water for hot water supply can be heated to some extent prior to the heating by the second condensing means, and the hot water for hot water supply can be further heated.

By providing the gas injection mechanism in the second heat pump, the second refrigerant molecules can be evaporated not only from the free liquid surface of the evaporation means but also inside the liquid phase second refrigerant. As a result, the evaporation amount of the second refrigerant can be increased, the output of the second heat pump can be improved, and the compression means can be reliably downsized.

[Brief description of drawings]

FIG. 1 is a schematic configuration diagram showing a hot-water supply / cooling / heating heat pump system according to a first embodiment of the present invention.

FIG. 2 is a schematic configuration diagram showing a hot-water supply / cooling / heating heat pump system according to a second embodiment of the present invention.

FIG. 3 is a schematic configuration diagram showing a hot water supply / cooling / heating heat pump system according to a third embodiment of the present invention.

FIG. 4 is a schematic configuration diagram showing a hot-water supply / cooling / heating heat pump system according to a fourth embodiment of the present invention.

FIG. 5 is a schematic configuration diagram showing a hot water supply heat pump system according to a fifth embodiment of the present invention.

FIG. 6 is a schematic configuration diagram showing a hot water supply heat pump system according to a sixth embodiment of the present invention.

FIG. 7 is a schematic configuration diagram showing a hot water supply heat pump system according to a seventh embodiment of the present invention.

[Explanation of symbols]

S1 to S4 Heat pump system for hot water supply / cooling / heating S5 to S7 Heat pump system for hot water supply 10 Freon heat pump (first heat pump) 10X Air conditioner 11 Outdoor unit 12 Indoor unit 17,18 Electromagnetic directional control valve (flux control means) 17X, 18X Electromagnetic Direction control valve (flow path control means) 20 Water refrigerant heat pump (second heat pump) 22 Evaporator (evaporation means of second heat pump) 24 Condenser (second condensing means) 25 Air injection mechanism (gas injection mechanism) 31, 31X Condenser (first condensing means) 32 Heat exchanger (first evaporating means, third condensing means, common heat exchanging means) 32X Condenser (third condensing means) 33a First condensing means 33b Third condensing means 40 Hot water supply System 44 Heating channel 44a Water channel section 44b Return channel section (intake channel section) 50 Casing

Claims (12)

[Claims] 1. A first heat pump having (A) an outdoor unit and an indoor unit that constitute an air conditioner, and a first condensing unit, and passing a first refrigerant in a vapor phase at room temperature and normal pressure, and (B) room temperature. A second heat pump having an evaporation means for evaporating the liquid-phase second refrigerant at normal pressure and a second condensing means for condensing, the evaporation means being thermally connected to the first condensing means; )
The hot water supply system thermally connected to the second condensing unit is provided, and the first refrigerant of the first heat pump is circulated between the outdoor unit and the indoor unit while being condensed in the outdoor unit to By evaporating, the cooling mode in which the room is cooled and the first refrigerant of the first heat pump is circulated between the outdoor unit and the indoor unit, and is evaporated in the outdoor unit and condensed in the indoor unit. A heating mode for heating the interior of the room, and by driving the second heat pump to evaporate the second refrigerant by the evaporation means and condense it by the second condensing means to heat the hot water for hot water supply in the hot water supply system, A hot water supply mode in which the first refrigerant of the first heat pump is evaporated in the outdoor unit while being circulated between the outdoor unit and the first condensing unit and is condensed by the first condensing unit to heat the evaporation unit is selectively selected. To do A heat pump system and butterflies. 2. The first heat pump further comprises a first evaporating means and a third condensing means which are thermally connected to the hot water supply system, and the heating mode includes first and second heating submodes. In the heating mode, one of the first and second heating sub modes is selectively executed, and in the first heating sub mode, the first of the first heat pumps is included.
While the refrigerant is circulated between the outdoor unit and the indoor unit, it is evaporated in the outdoor unit and condensed in the indoor unit to heat the room, and in the second heating submode, the first refrigerant is transferred to the first evaporation unit. While circulating between the means and the indoor unit, the first evaporation means evaporates by the heat of the hot water supply of the hot water supply system and condenses in the indoor unit to heat the room. In the hot water supply mode, the first refrigerant is the outdoor unit. , The first condensing means, and the third condensing means are circulated in this order, while being evaporated by the outdoor unit, condensed by the first condensing means to heat the evaporating means of the second heat pump, and then further condensed by the third condensing means. The heat pump system according to claim 1, wherein the hot water for the hot water supply system is heated before heating by the second condensing means. 3. The first evaporation means and the third condensation means,
The heat pump system according to claim 2, wherein the heat pump system is configured by a common heat exchange unit. 4. The heating mode includes a third heating submode in addition to the first and second heating submodes, and one of the first to third heating submodes is included in the heating mode. In the third heating sub-mode, the first operation from the indoor unit is selectively executed.
Refrigerant is divided into two hands, one of which is passed through the first evaporation means to be evaporated, and the other of which is passed through the outdoor unit to be evaporated, and the first refrigerants of these two hands are joined to be condensed in the indoor unit. The heat pump system according to claim 2 or 3, characterized in that. 5. The sub-mode other than the first heating is selected when the heating is started, and the first heating sub-mode is selected when the heating is steady.
The heat pump system according to any one of to 4. 6. The first heat pump according to any one of claims 1 to 5, wherein the first heat pump has flow passage control means for controlling a flow passage of the first refrigerant in accordance with a selected mode. The heat pump system described. 7. The heat pump system according to claim 1, wherein the respective means of the first heat pump and the second heat pump are housed in one casing. 8. (A) A heat pump for evaporating and compressing a vapor-phase first refrigerant at room temperature and atmospheric pressure, the first condensing means condensing the compressed first refrigerant, and the first condensing means. A first heat pump having third condensing means for further condensing the first refrigerant after passing through, and (B) a heat pump for evaporating and compressing the second refrigerant in the liquid phase at room temperature and normal pressure. A second heat pump having a second condensing means for condensing the compressed second refrigerant, and (C) a warming passage for passing hot water for hot water supply, while an evaporating means for the second refrigerant is thermally connected to the first condensing means. And the heating path is provided with a hot water supply system that is thermally connected to the third condensing means of the first heat pump and the second condensing means of the second heat pump sequentially from the upstream side. And heat pump system. 9. The second heat pump according to claim 1, wherein the second refrigerant is water, and the evaporation means has a vertically extending container shape and stores water up to the upper side thereof. By accommodating the first condensing means of the heat pump, these means are thermally connected to each other, and by accommodating the third condensing means under the evaporation means,
The lower part of the evaporation means is provided as a thermal connection portion with the third condensing means in the heating path, and the heating path further depressurizes the hot water for heating and the evaporation means. 9. The heat pump system according to claim 8, further comprising: a water supply passage portion that is sent to a lower side portion of the evaporator, and an intake passage portion that takes water from an intermediate portion of the evaporation means and sends the water to the second condensing means. 10. The second refrigerant is circulated between the evaporating means of the second heat pump and the first condensing means of the first heat pump to establish thermal connection between these means. The heat pump system according to any one of claims 1 to 8. 11. The evaporation means of the second heat pump accommodates the first condensing means of the first heat pump, so that these means are thermally connected to each other. The heat pump system according to any one of claims. 12. The gas injection mechanism for injecting a non-condensable gas in an unsaturated state into the second refrigerant before evaporation is connected to the evaporation means of the second heat pump. 11. The heat pump system according to any one of 11.