JPH0861804A - Heat pump equipment - Google Patents

Abstract

(57) [Summary] [Purpose] To improve the coefficient of performance of heat pump operation. [Constitution] Condenser 12 for air radiating heat to supply air A
And a condenser 11 for the liquid that radiates heat to the heat radiating liquid L, in a heat pump device, the heat transfer from the supply air A to the heat radiating liquid L is blocked, and the heat radiating liquid L to the supply air is blocked. A heat transfer means 14 which allows only heat transfer to A is provided. Further, in a heat pump device provided with an evaporator 12 for air to collect heat from the supply air A and an evaporator 11 for liquid to collect heat from the heat collecting liquid L, the supply air A from the heat collecting liquid L is provided. A heat transfer means 14 is provided for preventing heat transfer to the heat collecting liquid L from the supply air A to prevent heat transfer to the heat collecting liquid L.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump device for generating cold heat provided with a condenser for air to radiate heat to supply air, and a condenser for liquid to radiate heat to a heat radiating liquid, and to supply air. The present invention relates to a heat pump device for generating heat, which is provided with an evaporator for air collection for collecting heat and an evaporator for liquid collection for collecting heat from a heat collection liquid.

[0002]

2. Description of the Related Art Conventionally, in a heat pump device for generating cold heat as described above, as shown in FIG. 16, the supply air A is targeted for heat transfer only to the air condenser 12, and the heat radiating liquid L is used for heat exchange. The device configuration is such that only the liquid condenser 11 is subjected to heat transfer, and heat transfer between the supply air A and the heat dissipation liquid L is not considered at all.

Similarly, in the heat pump device for generating heat as described above (see FIG. 16), the supply air A is targeted for heat transfer only to the evaporator 12 for the air, and the liquid L for heat collection is the same. The device configuration is such that only the liquid evaporator 11 is targeted for heat transfer, and heat transfer between the supply air A and the heat collection liquid L is not considered at all.

[0004]

However, in the above heat pump device for generating cold heat, the supply air A (for example, outside air) is used.
Although the temperature is low and the heat radiation acceptance amount is large, the heat radiation amount may be limited by the device capacity of the condenser 12 for air, and the improvement of the coefficient of performance of the heat pump device as a whole may be restricted. In order to avoid this, if the condenser 12 for air is equipped with one having a large apparatus capacity, the condenser 12 for air and the condenser 11 for liquid 11
The overall heat pump configuration including and increases in size, and the cost of the device increases.

On the other hand, also in the heat pump device for generating heat, the evaporator for air is also in spite of the fact that the temperature of the supply air A (for example, the outside air) is high and the amount of collected heat is large. There is a case where the heat collection amount is limited by the device capacity of 12 and the improvement of the coefficient of performance of the entire heat pump device is restricted, and in order to avoid this, if the evaporator 12 for air is equipped with a large device capacity,
The overall heat pump configuration including the air-to-air evaporator 12 and the liquid-to-liquid evaporator 11 is increased in size, and the cost of the apparatus is increased.

In view of the above circumstances, the object of the present invention is as follows.

A first object of the present invention is to obtain a high coefficient of performance in cold heat generation operation while avoiding an increase in the size of the condenser for air.

A second object of the present invention is to utilize the constitution for achieving the above-mentioned first object so that the heat exhaust heat accompanying the cold heat generating operation can be released with a delay relative to the time of generation.
This is to improve the coefficient of performance.

A third object of the present invention is to obtain a high coefficient of performance in the heat generation operation while avoiding an increase in the size of the evaporator for air.

A fourth object of the present invention is to utilize the constitution for achieving the above-mentioned third object so that the cold heat exhaustion due to the heat generating operation can be released with a delay from the time of the generation.
This is to improve the coefficient of performance.

A fifth object of the present invention is to provide a heat pump device for switching between a cold heat generating operation and a hot heat generating operation.
The point is to achieve both the first and third objects.

A sixth object of the present invention is to achieve the above fifth object with a simple device construction using a heat pipe.

[0013]

[Means for Solving the Problems]

[First Characteristic Configuration] A first characteristic configuration of the present invention is a configuration in which a condenser for air that radiates heat to supply air and a condenser for liquid that radiates heat to a heat radiating liquid are provided, and the heat radiation from the supply air is performed. The heat transfer means is provided to prevent heat transfer to the working liquid and to allow only heat transfer from the heat radiating liquid to the supply air.

[Second Characteristic Configuration] A second characteristic configuration of the present invention is to identify a preferable configuration in the implementation of the first characteristic configuration, and a retaining means for retaining the heat radiation liquid is provided. Especially.

[Third Characteristic Configuration] A third characteristic configuration of the present invention is a configuration in which an evaporator for air collecting heat from supply air and an evaporator for liquid collecting heat from a heat collecting liquid are provided. There is provided heat transfer means for preventing heat transfer from the heat collecting liquid to the supply air and allowing only heat transfer from the supply air to the heat collecting liquid.

[Fourth Characteristic Configuration] A fourth characteristic structure of the present invention is to identify a preferable structure for carrying out the third characteristic structure, and a holding means for holding the heat collecting liquid is provided. There is something.

[Fifth Characteristic Configuration] A fifth characteristic configuration of the present invention is to identify a preferable configuration in the implementation of the first, second, third or fourth characteristic configuration, and in the cold heat generation operation, Provide a refrigerant heat exchanger for air to function as a condenser for air to radiate heat to the supply air and to function as an evaporator for air to take heat from the supply air in the heat generation operation, and to perform the cold heat generation operation. In the above, the refrigerant heat exchange for liquid is caused to function as a condenser for liquid to radiate heat to the heat collecting liquid, and to function as an evaporator for liquid to collect heat from the heat collecting liquid in the heat generation operation. And a heat transfer means for preventing heat transfer from the supply air to the heat-collecting liquid and allowing only heat transfer from the heat-collecting liquid to the supply air. And the supply air from the heat collection liquid And prevents heat transfer to, in said that from the feed air are then configured to be able to switched and heat for switching state adopted allows only the heat transfer to the release Tonetsu liquid.

[Sixth Characteristic Configuration] A sixth characteristic configuration of the present invention is to identify a preferable configuration in the implementation of the fifth characteristic configuration, wherein the heat transfer means makes contact with the supply air at a low temperature end. And a heat-dissipating heat pipe for bringing a high-temperature end into contact with the heat-collecting liquid, and a heat-collecting heat for bringing a high-temperature end into contact with the supply air and bringing a low-temperature end into contact with the heat-collecting liquid. A pipe and the heat dissipation heat pipe,
And a switching means for switching each of the heat collecting heat pipes between the heat transfer function state and the heat transfer function stopped state.

[0019]

[Action]

[Operation of First Characteristic Configuration] In the first characteristic configuration, when the temperature of the supply air is lower than the temperature of the heat-dissipating liquid, as heat dissipation (that is, release of heat exhaust heat) accompanying cold heat generation operation,
Part or all of the heat radiated from the liquid condenser to the heat radiating liquid in parallel with the heat radiating to the air supply condenser and the heat radiating liquid from the liquid condenser. It is possible to adopt a mode in which the heat transfer means discharges the heat dissipation liquid to the supply air.

Further, regarding the heat transfer from the supply air to the heat dissipation liquid when the temperature of the supply air is higher than the temperature of the heat dissipation liquid, the heat transfer means prevents heat transfer in that direction, thereby radiating heat. The heat dissipation function of the condenser for liquid against the working liquid is kept high.

[Operation of Second Characteristic Configuration] In the second characteristic configuration, when the temperature of the supply air is high and the heat radiation acceptance amount is small, the heat exhaust heat released from the liquid condenser to the heat radiation liquid. The cold heat generation operation can be performed by temporarily storing a part or all of the heat storage liquid as the stored heat of the heat radiating liquid in the storage means.

Then, when the temperature of the supply air becomes lower than the temperature of the heat dissipation liquid, the above-mentioned retained heat is released from the heat dissipation liquid to the supply air by the heat transfer means, whereby the holding means is It is possible to adopt an operation mode in which the heat is temporarily recovered in preparation for the temporary heat storage.

[Operation of Third Characteristic Configuration] In the third characteristic configuration, when the temperature of the supply air is higher than the temperature of the heat collecting liquid, heat collection (in other words, discharge of cold heat exhaust heat) accompanying the heat generation operation is performed. ), Heat is collected from the heat collecting liquid to the liquid evaporator in parallel with heat collection from the supply air of the air collecting evaporator and heat collection of the liquid collecting liquid to the heat collecting liquid. It is possible to adopt a form in which a part or all of the heat is collected from the supply air into the heat collecting liquid by the heat transfer means.

Regarding heat transfer from the heat collecting liquid to the supply air when the temperature of the supply air is lower than the temperature of the heat collecting liquid, the heat transfer means prevents heat transfer in that direction. The heat collection function of the evaporator for liquid with respect to the liquid for heat collection is maintained high.

[Operation of Fourth Characteristic Configuration] In the fourth characteristic configuration, when the temperature of the supply air is low and the heat collection capacity thereof is small, the cold heat released from the evaporator for liquid to the heat collecting liquid. The heat generation operation can be performed in a form in which a part or all of the exhaust heat is temporarily stored as retained cold heat of the heat collecting liquid in the retaining means.

When the temperature of the supply air becomes higher than the temperature of the heat-collecting liquid, the stored cold heat is released from the heat-collecting liquid to the supply air by means of the heat transfer means. It is possible to adopt an operation mode in which the fuel is thermally recovered in preparation for the next temporary storage of cold heat.

[Operation of Fifth Characteristic Configuration] In the fifth characteristic configuration, the refrigerant heat exchanger for air is caused to function as a condenser for air to radiate heat to the supply air, and a refrigerant heat exchanger for liquid is used. In the cold heat generation operation that functions as a condenser for liquid to radiate heat to the heat-collecting liquid, the heat transfer means is switched to heat-dissipation (that is, a switch state that allows only heat transfer from the heat-collecting liquid to the supply air). With this, the action of the first characteristic configuration can be obtained.

Further, the refrigerant heat exchanger for air is made to function as an evaporator for air to collect heat from the supply air, and the refrigerant heat exchanger for liquid is collected to heat liquid from the heat collecting liquid. In the heat generation operation for functioning as an evaporator, the heat transfer means is set to a heat collection switching state (that is, a switching state in which only heat transfer from the supply air to the heat collection liquid is allowed), whereby the third characteristic configuration is achieved. The action of can be obtained.

[Operation of Sixth Characteristic Configuration] In the sixth characteristic configuration, in the case of the cold heat generation operation, the heat transfer heat transfer pipe is switched to the heat transfer function stopped state by the heat transfer device in the heat transfer switching state. In addition, by setting the heat radiation heat pipe to the heat transfer function state, heat transfer from the supply air to the free heat collecting liquid is blocked, and only heat transfer from the free heat collecting liquid to the supply air is allowed.

In addition, in the case of the heat generation operation, the heat transfer switching state of the heat transfer means is set to the heat transfer function stop state of the heat radiating heat pipe and the heat transfer heat pipe is set to the heat transfer function state. By so doing, heat transfer from the heat-collecting liquid to the supply air is blocked, and only heat transfer from the supply air to the heat-collecting liquid is allowed.

[0031]

【The invention's effect】

[Effects of the first characteristic configuration] According to the first characteristic configuration, when the temperature of the supply air is low and the heat radiation acceptance amount is large, the heat dissipation to the supply air of the condenser for air and the condenser for liquid are performed. Since part or all of the heat radiated from the heat radiating liquid to the heat radiating liquid can be combined and released to the supply air having a large heat radiating capacity, the heat radiating ability of the heat pump device as a whole can be ensured to be high. It is possible to obtain a high coefficient of performance in the cold heat generation operation while avoiding an increase in size.

[Effect of Second Characteristic Configuration] According to the second characteristic configuration, when the temperature of the supply air is high and the heat radiation acceptance amount is small, the thermal exhaust heat released from the liquid condenser to the heat radiation liquid. It is possible to carry out the cold heat generation operation in the form of temporarily storing a part or all of the heat as the held heat of the heat-dissipating liquid in the holding means (that is, the form of releasing the heat exhaust heat with a delay relative to the time of occurrence). A high coefficient of performance can be obtained in generative operation.

[Effect of Third Characteristic Configuration] According to the third characteristic configuration, when the temperature of the supply air is high and the heat collection amount thereof is large, the heat of the supply air of the evaporator for air is collected, By collecting a part or all of the heat to be collected from the heat collecting liquid by the liquid-to-liquid evaporator from the supply air having a large heat collection capacity, it is possible to secure a high heat collecting capacity of the heat pump device as a whole, This makes it possible to obtain a high coefficient of performance in the heat generation operation while avoiding an increase in the size of the evaporator for air.

[Effect of Fourth Characteristic Configuration] According to the fourth characteristic configuration, when the temperature of the supply air is low and the heat collection capacity is small, the evaporator for liquid discharges to the liquid for heat collection. By performing a heat generation operation in a form in which a part or all of the cold heat exhaustion is temporarily stored as retained cold heat of the heat collecting liquid in the holding means (that is, a form in which the cold heat exhaust heat is released after being delayed) A high coefficient of performance can be obtained in the heat generation operation.

[Effect of Fifth Characteristic Configuration] According to the fifth characteristic configuration, the heat transfer means is switched between the heat radiation switching state and the heat collection switching state with the switching between the cold heat generating operation and the hot heat generating operation. Thus, it is possible to obtain a high coefficient of performance in both the cold heat generating operation and the hot heat generating operation while avoiding an increase in the size of the refrigerant heat exchanger for air.

[Effect of Sixth Characteristic Configuration] According to the sixth characteristic structure, the heat transfer means is configured by utilizing the heat transfer function originally possessed by the heat pipe, thereby simplifying the apparatus structure. However, the effect of the fifth characteristic configuration can be obtained.

[0037]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows the overall equipment configuration, FIG. 2 shows the equipment layout configuration, FIGS. 6 to 10 show the operating state of a typical operation mode in the cooling operation, and FIGS. 12 to 15 show the heating operation. The operation state of a typical operation mode is shown.

In the figure, reference numeral 1 denotes an indoor temperature control unit for controlling the temperature of the room as a cooling / heating target area. The indoor temperature control unit 1 includes a cold / hot water heat exchanger 2 and its cold / hot water heat exchanger 2. A fan 3 for supplying the temperature-controlled air IA to the room is equipped.

Regarding the indoor temperature control unit 1, a mode in which a plurality of units are arranged corresponding to each floor and each room of a building, or as a whole facility
Any of the forms in which only the unit is equipped may be adopted.

Reference numeral 4 denotes an indoor refrigerant unit equipped to adjust the indoor temperature as necessary. The indoor refrigerant unit 4 includes a refrigerant heat exchanger 5 and air whose temperature is adjusted by the refrigerant heat exchanger 5. It is equipped with a fan 6 that sends the IA indoors.

Reference numeral 7 denotes a hot / cold water faucet, which may be arranged in a distributed manner or may be equipped with only one faucet as a whole facility.

An outdoor unit 8 is installed on a rooftop together with a brine cooling tower 9 which will be described later.
Includes a brine heat exchange tank 10, a refrigerant heat exchanger 11 for brine, a refrigerant heat exchanger 12 for air, a fan 13,
A brine / air heat transfer means 14, a brine / refrigerant heat exchanger 15, and a compressor 16 are provided, and an expansion valve (or a capillary tube) 17, a four-way valve 18, and an economizer unit 19 are provided as valves. is there.

The refrigerant heat exchanger 11 for the brine, the refrigerant heat exchanger 12 for the air, the brine / refrigerant heat exchanger 15, the compressor 16, the expansion valve 17, the four-way valve 18, and the economizer unit 19 are the above-mentioned indoor refrigerants. A heat pump circuit is configured together with the refrigerant heat exchanger 5 in the unit 4, and the refrigerant heat exchanger 11 for brine is immersed in the brine L of the brine heat exchange tank 10 and the refrigerant for air is also used. The heat exchanger 12 is arranged in the internal air passage 20 through which air is ventilated by the fan 13.

The economizer unit 19 has a refrigerant heat exchanger for brine which is located upstream in the refrigerant path in the cooling operation in which the refrigerant heat exchanger for brine 11 and the refrigerant heat exchanger for air 12 function as condensers. Of the 11 passing refrigerants, the sufficiently condensed liquid refrigerant is sent to the expansion valve 17 by bypassing the air-to-air refrigerant heat exchanger 12 and the insufficiently condensed vapor refrigerant is to-air refrigerant heat exchange. In the heating operation in which the refrigerant separation function is performed such that the refrigerant is sufficiently condensed in the device 12 and then sent to the expansion valve 17, and the refrigerant heat exchanger 11 for brine and the refrigerant heat exchanger 12 for air function as an evaporator. Of the refrigerant passing through the refrigerant heat exchanger for air 12 located upstream in the refrigerant path, the fully evaporated dry vapor refrigerant is bypassed to the refrigerant heat exchanger for brine 11 and compressed. The refrigerant is returned to the suction side of the compressor 16, and the wet vapor refrigerant and a part of the liquid refrigerant that are insufficiently evaporated are sufficiently evaporated in the refrigerant heat exchanger 11 for brine and then returned to the intake side of the compressor 16. Thus, the refrigerant separation function is achieved, and the coefficient of performance of heat pump operation is effectively achieved by these refrigerant separation functions.

In the economizer unit 19 (see FIG. 3), 19A and 19B are gas-liquid separators,
In some cases, together with the economizer unit 19, one of the refrigerant heat exchanger 11 for brine and the refrigerant heat exchanger 12 for air is selectively cut off, and the refrigerant supply is cut off for one side and only the condenser for the other side is used. It is equipped with a selection valve mechanism that switches the refrigerant path so that it functions as an evaporator.

The brine / air heat transfer means 14 connects the ventilation air A in the internal air passage 20 and the brine L in the brine heat exchange tank 10 at a position upstream of the air-refrigerant heat exchanger 12 on the air path. In the cooling operation in which heat is exchanged only in the heat transfer direction that is selectively specified and heat is to be dissipated (that is, heat is discharged), only the heat transfer from the brine side to the ventilation air side is performed by the brine / air heat transfer means 14. While collecting heat (in other words, discharging cold heat)
In the heating operation that should be performed, the brine / air heat transfer means 14 allows only heat transfer from the ventilation air side to the brine side.

Regarding the concrete structure of the brine / air heat transfer means 14, as shown in FIGS. 3 and 4, the low temperature end (condensing end) is located in the upper half of the internal air passage 20, and the high temperature end is located. A plurality of heat-dissipating heat pipes 14A in which the (evaporation end) is immersed and placed in the brine L in the brine heat exchange tank 10,
Also, the high temperature end (evaporation end) is located in the lower half of the internal air passage 20, and the low temperature end (condensation end) is located in the brine heat exchange tank 10.
A plurality of heat-collecting heat pipes 14B, which are soaked in the brine L, are provided, and a lower part that allows air to pass through only the upper half of the internal air passage 20 with the ventilation in the lower half of the internal air passage 20 blocked. Inside the damper 21 is operated to switch between a wind-shielded state and, conversely, an upper wind-shielded state in which ventilation is blocked in the upper half of the internal air passage 20 while air is allowed to pass through only the lower half of the internal air passage 20. It is provided in the air passage 20.

That is, in the cooling operation, the damper 21 as the switching means is set in the lower air-shielding state and the air is intensively passed through the low temperature end arrangement portion of the heat radiating heat pipe 14A to be sent to the internal air passage 20. For the air A having a lower temperature than the brine L in the brine heat exchange tank 10, the heat radiating heat pipe 14A having a forward temperature gradient has a heat transfer function (that is, heat radiating function), while the internal wind The air A sent to the passage 20 is the brine heat exchange tank 10
In the situation where the temperature is higher than that of the brine L in the above, the heat collection heat pipe 14B whose temperature gradient becomes a forward gradient has a heat transfer function (that is, a heat collection function). By blocking the passage, it is blocked, so that in the cooling operation,
In a situation where the air A sent to the internal air passage 20 is at a temperature lower than that of the brine L in the brine heat exchange tank 10, while efficiently releasing the warm heat of the brine L to the blast air A by the heat radiating heat pipe 14A, In a situation where the air A sent to the air passage 20 has a higher temperature than the brine L in the brine heat exchange tank 10, the retained heat of the ventilated air A is prevented from being transferred to the brine side.

On the contrary, in the heating operation, the damper 21 as the switching means is in the upper wind-shielding state so that the air is intensively passed through the high temperature end arrangement portion of the heat collecting heat pipe 14B, so that the internal air passage is reduced. The air A sent to 20 is higher in temperature than the brine L in the brine heat exchange tank 10, but the heat collecting heat pipe 14B having a forward temperature gradient has a heat transfer function (that is, a heat collecting function). ,
On the other hand, the air A sent to the internal air passage 20 is the brine heat exchange tank 1
The heat transfer function (that is, the heat dissipation function) of the heat dissipation heat pipe 14A whose temperature gradient is a forward slope in a situation where the temperature is lower than that of the brine L in 0 is that air passage to the low temperature end arrangement portion of the heat dissipation heat pump 14A is performed. The air is sent to the internal air passage 20 during the heating operation so that the air is sent to the brine heat exchange tank 10 during the heating operation.
In a situation where the temperature is higher than that of the brine L in B, the heat L of the ventilation air A is efficiently collected by the brine L by the heat collecting heat pipe 14B, while the air A sent to the internal air passage 20 is in the brine heat exchange tank 10. When the temperature is lower than that of the brine L, the retained heat of the brine L is prevented from being transferred to the ventilation air side.

Internal air passage 20 and refrigerant heat exchanger 1 for air
The heat-exchanged air A that has passed through 2 is discharged into the atmosphere. On the other hand, regarding the air supply, 22 is a duct for feeding the air A as a heat radiation source or a heat collection source to the internal air passage 20, The duct 22 supplies outside air as a heat radiation source to the internal air passage 20 in the cooling operation, and also performs appropriate heat extraction as a heat collecting source in the heating operation (for example, air heated by a solar heat collector or indoors). The air that has recovered the hot exhaust heat) is fed to the internal air duct 20, or the outside air is fed to the internal air duct 20 as a heat release source for both the cooling operation and the heating operation.

Reference numerals 23, 24, 25, and 26 are a hot water tank, a cold water tank, a hot water discharge tank, and a brine tank which are formed / deployed in an underground foundation layer in a building, and the hot water tank 23 stores the stored water H in the tank. The brine heat exchanger 27 for hot water for exchanging heat with the brine L is equipped, and the cold water tank 24 is equipped with the brine heat exchanger 28 for cold water for exchanging heat between the stored water C in the tank and the brine L. There is.

V1 in the figure is a switching valve group for switching the brine path for the hot water brine heat exchanger 27 and for switching the brine path for the cold water brine heat exchanger 28. Specifically, Brine heat exchanger for hot water 2
7 and the brine heat exchanger 28 for cold water, a state in which the brine is circulated with the brine / refrigerant heat exchanger 15 for circulating brine, and a brine circulation with the brine heat exchange tank 10. Switch to the tank circulation state.

The hot water discharge bath 25 is used for the hot water E discharged from indoors.
This is a tank that collects the discharged hot water E for the purpose of utilizing the retained heat of the hot water (for example, bath water or general wash water). In this hot water discharge tank 25, the hot water in the tank E and the stored water C in the cold water tank 24 are stored. Is equipped with a heat exchanger 29 for the cold water tank for exchanging heat, and a heat exchanger 30 for the brine tank for exchanging heat between the hot water E in the tank and the storage brine L of the brine tank 26.

The brine tank 26 is a holding means for holding the above-mentioned brine L used as a heat-collecting liquid in the apparatus. In the cooling operation, the heat exhaust heat generated by the cold heat generation by the heat pump operation is used as the brine tank holding heat. The heat is temporarily stored, and in the heating operation, the cold exhaust heat generated by the heat generation due to the heat pump operation is temporarily stored as the cold heat stored in the brine tank.
In addition to the brine circulation between the hot water discharge tank 25 and the heat exchanger 30 for the brine tank, the brine circulation between the brine cooling tower 9 and the brine heat exchange tank 1 is also performed.
It allows brine circulation to and from zero.

In the brine cooling tower 9, a brine radiator 3 for radiating the circulating brine L with the brine tank 26 is radiated.
1, a fan 32 for ventilating the outside air as a heat radiation source to the brine radiator 31 and a sprinkler 33 for sprinkling water on the brine radiator 31 are provided, and the water sprinkled by the sprinkler 33 is used as a brine radiator. By evaporating the heat of vaporization from 31 to evaporate it into the open air, the brine radiator 31 can efficiently cool the circulating brine L.

Reference numeral 34 denotes a heat source water W collected as a heat radiation source or a heat collection source (for example, seawater, sewage, or river water).
On the other hand, a heat exchanger for a water heat source that radiates or collects the brine L, and 35 is a heat exchanger for an auxiliary heat source that radiates or collects the brine L to another air heat source, a water heat source, or an underground heat source. Yes, the brine heat exchange tank 10 in the outdoor unit 8 includes the brine heat exchanger 27 for hot water, the brine heat exchanger 28 for cold water, and the brine circulation between the brine heat exchanger 28 and the brine tank 26. Brine circulation is also appropriately performed between the exchanger 34 and the heat exchanger 35 for assisting heat source, whereby the air A guided by the duct 22, the hot water E collected in the hot water tank 25, or the brine cooling tower. In addition to the outside air ventilated in 9,
A heat radiation source or a heat collection source in various forms regardless of a gas phase, a liquid phase, or a solid phase can be applied to the heat pump operation.

V2 is a switching valve group for switching between a cooling state in which the cold / hot water heat exchanger 2 of the indoor temperature control unit 1 circulates water between the cold water tank 24 and a heating state in which water circulates between the hot water tank 23, P is a pump arranged in each flow path, and 36 is an auxiliary water heater such as a gas-fired type or an electric heating type.

Further, V3 is a switching valve group for switching between a cold water supply state in which the hot / cold water tap 7 is connected to the cold water tank 24 and a hot water supply state in which it is connected to the hot water tank 23. The description is omitted and only the valve symbols in the figure are shown.

Next, one embodiment of the cooling operation will be described in the following (A) to (F) according to the time chart shown in FIG.

(A) As "cold heat storage mode" (Fig. 6-
(See FIG. 9), between 22:00 and 08, the brine / refrigerant heat exchanger 15 circulates the circulating brine L by the evaporator function of the brine / refrigerant heat exchanger 15 in the heat pump operation.
And the brine circulating between the brine / refrigerant heat exchanger 15 and the cold water brine heat exchanger 28 cools the stored water C in the cold water tank 24 (for example, from 12 ° C. to 0 ° C.).

(A) As the "heat heat storage mode" (see FIG. 8), during the heat pump operation in the "cold heat storage mode" from 24:00 to 03:00, a state in which air ventilation in the internal air passage 20 is stopped ( Further, in some cases, the condenser L of the refrigerant heat exchanger 11 for brine (in a state where the refrigerant supply to the refrigerant heat exchanger 12 for air is also shut off) heats the brine L in the brine heat exchange tank 10, The brine heat exchange tank 10 and the hot water brine heat exchanger 27
The brine circulation between the hot water tank 23 and the stored water H
Is heated (for example, heated from 35 ° C. to 55 ° C.).

(C) As a "warm water tank recovery mode" (see FIG. 6) which is carried out before the above "heat heat storage mode" as necessary (see FIG. 6), the damper 21 is in the lower wind-shielding state from 22:00 to 24:00. As a condition in which air is ventilated into the internal air passage 20 (or in some cases, the refrigerant supply to the refrigerant heat exchanger 11 for brine is also cut off to allow only the refrigerant heat exchanger 12 for air to function as a condenser), In contrast to performing the heat pump operation in the “cold heat storage mode”, the brine heat exchange tank 1
0 and the brine heat exchanger 27 for hot water are circulated in brine, whereby the stored water H in the hot water tank 23 is cooled (for example, 55 ° C.) with the heat radiation function of the heat radiation heat pipe 14A.
To 35 ° C.).

This "warm water tank recovery mode" is generated by the heat pump operation for the subsequent generation of cold heat by previously releasing the hot water tank retained heat, which is one of the heat retained in the equipment, to the outside of the facility. The purpose is to secure a large amount of temporary storage in the equipment for heat exhaust heat, and thereby obtain a high coefficient of performance in the heat pump operation for subsequent cold heat generation. Therefore, this "hot water tank recovery mode" When the consumption amount of the hot water held by the hot water tank (for example, the amount of hot water supplied from the hot / cold water tap 7) before the execution of “” is large and the stored water temperature of the hot water tank 23 has already dropped to a certain level (for example, 35 ° C.) or less For this reason, it is not necessary to carry out this "warm water tank recovery mode".

When it is not necessary to carry out the "hot water tank recovery mode", the heat pump operation in the "cold heat storage mode" from 22:00 to 24:00 (see FIG. 7) causes the damper 21 to lower the wind. In the mode in which both the refrigerant heat exchanger 12 for air and the refrigerant heat exchanger 11 for brine are made to function as a condenser while the heat radiation pipe 14A is made to perform a heat radiation function by ventilating the internal air passage 20 as a state. carry out.

(D) As the "brine tank first recovery mode" (see FIGS. 6 to 9), the brine cooling tower 9 and the brine tank 26 are operated while operating the brine cooling tower 9 from 20:00 to 08:00. Circulate brine between and
The stored brine L in the brine tank 26 is cooled in cooperation with the “brine tank second recovery mode” described below (for example, from 37 ° C. to 2 ° C.).
Cool to 7 ° C).

(E) As the “brine tank second recovery mode” (see FIG. 9), the damper 2 is operated from 03:00 to 08: 00.
1 is a state where the lower wind is blocked and air is ventilated to the internal air passage 20 (or the refrigerant heat exchanger 11 for brine in some cases.
Refrigerant heat exchanger for air 1
In the state in which only 2 functions as a condenser), the brine is circulated between the brine heat exchange tank 10 and the brine tank 26 by performing the heat pump operation in the “cold heat storage mode”, and thereby the heat radiating heat pipe. Using the heat dissipation function of 14A, the stored brine L in the brine tank 26 is cooled in cooperation with the "brine tank first recovery mode".

That is, these "brine tank first recovery mode" and "brine tank second recovery mode" are similar to the above "hot water tank recovery mode" in that the brine tank retained heat, which is one of the retained heat in the equipment, is stored. By releasing it to the outside of the facility in advance, a large amount of temporary storage amount in the facility for the heat exhaust heat generated in the heat pump operation for subsequent cold heat generation is secured, which enables the subsequent heat pump operation for cold heat generation. The purpose is to obtain a high coefficient of performance.

(F) As "cooling execution mode" (see FIG. 10)
From 8 o'clock to 8 o'clock, while cooling the stored water C of the cold water tank 24 by the evaporator function of the brine / refrigerant heat exchanger 15 in the heat pump operation in the same manner as the "cold heat storage mode", the room temperature Water is circulated between the cold / hot water heat exchanger 2 of the conditioning unit 1 and the cold water tank 24, and the fan 3 of the indoor temperature conditioning unit 1 is operated, whereby the indoor space is consumed while the stored cold heat is consumed in the cold water tank 24. To cool.

Further, in the heat pump operation of this "cooling execution mode", the damper 21 is set to the lower air-shielding state to ventilate the internal air passage 20, and the brine is circulated between the brine heat exchange tank 10 and the brine tank 26. While doing so, the refrigerant heat exchanger 12 for the air and the refrigerant heat exchanger 11 for the brine
Functioning as a condenser, whereby a part of the hot heat exhaust heat in the heat pump operation is temporarily stored in the brine tank 26 while the ventilation air A in the internal air passage 20 is discharged.
Release against.

In this "cooling execution mode", even if the temperature of the air A sent to the internal air passage 20 is higher than the brine temperature of the brine heat exchange tank 10, the heat transfer of the heat collecting heat pipe 14B is performed. The heat transfer from the ventilation air side to the brine side due to the function is prevented by the damper 21 being in the lower wind shielding state, and the brine temperature of the brine heat exchange tank 10 is the temperature of the air A sent to the internal air passage 20. When the temperature becomes higher, the damper 21 is in the lower wind-shielding state, so that the heat transfer function of the heat radiating heat pipe 14A releases the retained heat of the brine L to the ventilation air A.

Next, one embodiment of the heating operation will be described in the following (A) to (K) according to the time chart shown in FIG.

(A) As the "heat storage mode" (see FIG. 12)
(See FIG. 13), between 22:00 and 08, the brine / refrigerant heat exchanger 15 heats the circulating brine L by the condenser function of the brine / refrigerant heat exchanger 15 in the heat pump operation. The brine circulation between the heat exchanger 15 and the hot water brine heat exchanger 27 heats the stored water H in the hot water tank 23 (for example, 30
Heat from 0 ° C to 55 ° C).

In the heat pump operation in the "heat storage mode", the damper 21 is set to the upper air-shielding state and the internal air passage 20 is ventilated, while the air-to-air refrigerant heat exchanger 12 is operated.
Also, the refrigerant heat exchanger 11 for brine is caused to function as an evaporator.

(Ii) As a "cold water tank recovery mode" (see FIG.
2 or FIG. 15), and between 14:00 and 05:00, the heat exchanger 29 for the cold water tank in the cold water tank 24 and the hot water discharge tank 25.
Water is circulated between the two, and thereby the stored water C in the cold water tank 24 is heated (for example, heated from 7 ° C. to 10 ° C.) using the retained heat of the discharged hot water E.

(V) In the "brine tank recovery mode" (see FIG. 12 or 15), between 14:00 and 05:00, between the brine tank 26 and the heat exchanger 30 for the brine tank in the hot water discharge tank 25. In this way, the brine is circulated, and thereby the stored brine L in the brine tank 26 is heated (for example, from -4 ° C to 6 ° C) using the retained heat of the discharged hot water E.

That is, the above-mentioned "cold water tank recovery mode" and "brine tank recovery mode" are performed by releasing the cold water tank cold energy and the brine tank cold energy, which are cold energy retained in the equipment, to the outside of the equipment in advance. The purpose is to secure a large amount of temporary storage in the equipment for cold heat exhaust heat generated in the heat pump operation for generating heat, and to obtain a high coefficient of performance in the subsequent heat pump operation for generating heat.

After the "cold water tank recovery mode" and the "brine tank recovery mode" are carried out, the total amount of the hot water E in the hot water discharge tank 25 is once drained, and then the indoor hot water E is again collected. .

(E) As a "cold heat storage mode", which is carried out as necessary after the "cold water tank recovery mode" (FIG. 13)
), From 05:00 to 08, in parallel with the heat pump operation of the "heat heat storage mode", brine is circulated between the brine heat exchange tank 10 and the cold water brine heat exchanger 28, thereby, The stored water C in the cold water tank 24 is cooled (for example, cooled from 10 ° C. to 0 ° C.).

This "cold heat storage mode" is carried out when it is predicted that the subsequent consumption of cold heat possessed by the cold water tank (for example, cold heat consumption due to the later-described cooling in winter, etc.) is large, and during the intermediate period, etc. When it is predicted that the consumption of the cold heat in the cold water tank is particularly large, in the parallel heat pump operation of the "heat storage mode", the air ventilation in the internal air passage 20 is stopped, or in some cases, the refrigerant for air is used. The refrigerant supply to the heat exchanger 12 may be cut off so that only the refrigerant heat exchanger 11 for brine functions as an evaporator, thereby further lowering the cooling temperature of the cold water tank stored water C.

(O) As "heating execution mode" (see FIG. 14)
(See FIG. 15), while heating the stored water H in the hot water tank 23 from 08 o'clock to 20 o'clock by the condenser function of the brine / refrigerant heat exchanger 15 in the heat pump operation in the same manner as in the "heat storage mode". The water is circulated between the cold / hot water heat exchanger 2 of the indoor temperature control unit 1 and the hot water tank 23, and the fan 3 of the indoor temperature control unit 1 is operated, whereby the stored heat in the hot water tank 23 is consumed. While heating the room.

Further, in this "heating execution mode", the damper 21 is set to the upper air-shielding state, and the refrigerant heat exchanger 12 for the air and the refrigerant heat exchanger 11 for the brine are evaporated while the internal air passage 20 is ventilated. In contrast to the functioning heat pump operation, between 08 o'clock and 14 o'clock, brine circulation between the brine heat exchange tank 10 and the brine tank 26 is performed in parallel (see FIG. 14) to cool the heat pump operation. A part of the exhaust heat is temporarily stored in the brine tank 26 and is discharged to the ventilation air A in the internal air passage 20.

In this "heating execution mode", even if the temperature of the air A sent to the internal air passage 20 is lower than the brine temperature of the brine heat exchange tank 10, the heat transfer function of the heat radiating heat pipe 14A is achieved. The heat transfer from the brine side to the ventilated air side due to is blocked by the damper 21 in the upper wind-blocking state, and the brine temperature of the brine heat exchange tank 10 is lower than the temperature of the air A sent to the internal air passage 20. When the temperature is low, the damper 21 is in the upper wind-shielding state, so that the retained heat of the ventilation air A is collected in the brine L by the heat transfer function of the heat collecting heat pipe 14B.

(Or) As a "winter cooling mode" to be carried out as necessary, when a cooling required room is generated, the cold / hot water heat exchanger 2 of the indoor temperature control unit 1 for the cooling required room (for example, the room where the OA equipment is installed). Water is circulated between the cold water tank 24 and the cold water tank 24, and the fan 3 of the indoor temperature control unit 1 is operated, whereby the room requiring cooling is cooled while the stored cold heat is consumed in the cold water tank 24.

In the above cooling operation and heating operation,
Although the usage example of the indoor refrigerant unit 4 is omitted, when cooling is performed in a situation where the stored cold heat of the cold water tank 24 is used up, when heating is performed in a situation where the stored hot heat of the hot water tank 23 is used up, or a water leakage accident occurs. When heating and cooling a room which is not allowed, for example, the fan 6 is operated to cool the target room while the refrigerant heat exchanger 5 of the indoor refrigerant unit 4 functions as an evaporator, and the refrigerant heat exchange of the indoor refrigerant unit 4 is performed. The fan 6 is operated to heat the target room while the container 5 is functioning as a condenser.

[Other Embodiments] Next, other embodiments will be listed.

(1) The heat-dissipating liquid or the heat-collecting liquid is not limited to brine, and may be mere water or another liquid.

(2) From the heat collecting liquid L and the heat transfer means for preventing heat transfer from the supply air A to the heat dissipation liquid L and allowing only heat transfer from the heat dissipation liquid L to the supply air A. The heat transfer means that blocks the heat transfer to the supply air A and only allows the heat transfer from the supply air A to the heat collecting liquid L is a heat pipe 14A such as the brine / air heat transfer means 14 in the above-described embodiment. , 14B is not limited to the configuration using, and various configuration changes are possible.

(3) The above heat transfer means 14 is in a heat radiation switching state in which only heat transfer from the heat collecting liquid L to the supply air A is allowed, and heat transfer from the supply air A to the heat collecting liquid L is performed. When it is configured to be able to switch to the heat collection switching state that allows only movement, the specific configuration for the switching can be changed in various ways.

It should be noted that reference numerals are given in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configurations of the accompanying drawings by the entry.

[Brief description of drawings]

FIG. 1 is a diagram showing a facility configuration

FIG. 2 is a diagram showing a schematic device arrangement.

FIG. 3 is an enlarged front view of a main part.

FIG. 4 is an enlarged side view of a main part.

FIG. 5 is a time chart diagram of cooling operation.

FIG. 6 is a diagram showing an operating state of a typical operating mode in cooling operation.

FIG. 7 is a diagram showing an operating state of a typical operating mode in cooling operation.

FIG. 8 is a diagram showing an operating state of a typical operating mode in cooling operation.

FIG. 9 is a diagram showing an operating state of a typical operating mode in cooling operation.

FIG. 10 is a diagram showing an operating state of a typical operating mode in cooling operation.

FIG. 11 is a time chart diagram of heating operation.

FIG. 12 is a diagram showing an operating state of a typical operating mode in heating operation.

FIG. 13 is a diagram showing an operating state of a typical operating mode in heating operation.

FIG. 14 is a diagram showing an operating state of a typical operating mode in heating operation.

FIG. 15 is a diagram showing an operating state of a typical operating mode in heating operation.

FIG. 16 is a device configuration diagram showing a conventional example.

[Explanation of symbols]

A air 12 condenser for air (evaporator, refrigerant heat exchanger) L heat dissipation liquid, heat collection liquid 11 condenser for liquid (evaporator, refrigerant heat exchanger) 14 heat transfer means 26 holding means 14A Heat dissipation heat pipe 14B Heat collection heat pipe 21 Switching means

Claims (6)

[Claims] 1. A heat pump device comprising a condenser (12) for air that radiates heat to supply air (A) and a condenser (11) for liquid that radiates heat to a heat radiating liquid (L). A heat transfer means (14) which blocks heat transfer from the supply air (A) to the heat dissipation liquid (L) and allows only heat transfer from the heat dissipation liquid (L) to the supply air (A). A heat pump device. 2. The heat pump device according to claim 1, wherein the holding means (26) holds the heat dissipation liquid (L).
A heat pump device. 3. A heat pump device provided with an evaporator (12) for air collecting heat from the supply air (A) and an evaporator (11) collecting liquid for collecting heat from the heat collecting liquid (L). A heat that prevents heat transfer from the heat collecting liquid (L) to the supply air (A) and allows only heat transfer from the supply air (A) to the heat collecting liquid (L). A heat pump device provided with a moving means (14). 4. The heat pump apparatus according to claim 3, wherein the holding means (26) holds the heat collecting liquid (L).
A heat pump device. 5. The heat pump device according to claim 1, 2, 3 or 4, wherein in the cold heat generating operation, it functions as a condenser for air radiating heat to the supply air (A), and in the heat generating operation. A refrigerant heat exchanger (12) for air, which functions as an evaporator for air that takes heat from the supply air (A), is provided, and in the cold heat generating operation, heat is radiated to the liquid (L) for releasing heat Refrigerant heat exchanger for liquid (11) that functions as a condenser for water and functions as an evaporator for liquid for collecting heat from the liquid for heat collection (L) in the heat generation operation.
The heat transfer means (14) blocks heat transfer from the supply air (A) to the heat-collecting liquid (L), and transfers the heat-collecting liquid (L) to the supply air. A heat radiation switching state that allows only heat transfer to (A) and heat transfer from the heat-collecting liquid (L) to the supply air (A) to prevent the heat from the supply air (A). A heat pump device configured to be switchable to a heat collection switching state that allows only heat transfer to a heat collection liquid (L). 6. The heat pump device according to claim 5, wherein the heat transfer means brings a low temperature end into contact with the supply air (A) and causes a high temperature end to come into contact with the heat collecting liquid (L). A heat-dissipating heat pipe (14A) to be brought into contact, and a heat-collecting heat pipe (14B) to be brought into contact with the supply air (A) at a high-temperature end, and at the same time a low-temperature end is brought into contact with the heat-release liquid (L). A heat pump device configured to include a heat radiating heat pipe (14A) and a switching means (21) for switching each of the heat collecting heat pipe (14B) between a heat transfer function state and a heat transfer function stopped state. .