JPH1183086A - Refrigerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize an intermediate heat exchanger for heat exchanging a user side circuit with a heat source side circuit, in a so-called secondary refrigerant system having the heat source side circuit and the user side circuit. SOLUTION: This refrigerator comprises a primary side refrigerant circuit A and a secondary side refrigerant circuit B. In this case, secondary side refrigerant is taken out from an intermediate heat exchanger 13 in the circuit B in a gas-liquid two phase state in a so-called secondary refrigerant system for heat exchanging refrigerant of the circuit A with refrigerant of the circuit B in the exchanger 13. An auxiliary heat source circuit 30 is provided at a downstream side of the exchanger 13 to cool secondary side refrigerant of the gas-liquid two phase state flowing out from the exchanger 13 to liquid phase.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a refrigeration system,
In particular, the present invention relates to an improvement of a so-called secondary refrigerant system that can transfer heat between a heat source side circuit and a use side circuit.

[0002]

2. Description of the Related Art Conventionally, for example, Japanese Patent Publication No. 6-84828.
As disclosed in Japanese Unexamined Patent Publication, a secondary refrigerant system including a heat source side circuit and a use side circuit, and capable of exchanging heat between the two is known. Hereinafter, this type of system will be described. The heat source side circuit includes a compressor, a heat source side heat exchanger, an expansion mechanism, and a heat source side heat transfer tube of an intermediate heat exchanger connected by a refrigerant pipe so that the heat source side refrigerant can be circulated.
On the other hand, the use-side circuit includes a pump, a use-side heat transfer tube of an intermediate heat exchanger, and a use-side heat exchanger disposed in an air-conditioning room connected by a refrigerant pipe so that the use-side refrigerant can circulate.

[0003] In the case of performing heat absorption operation in a use side heat exchanger such as indoor cooling, in a heat source side circuit, a heat source side refrigerant compressed by a compressor and condensed in the heat source side heat exchanger is decompressed by an expansion mechanism. In the heat source side heat transfer tube of the intermediate heat exchanger, a circulation operation is performed in which the heat exchange with the use side refrigerant flowing through the use side heat transfer tube evaporates and returns to the compressor. In the use-side circuit, the use-side refrigerant circulates by driving the pump, and the use-side refrigerant is condensed in the use-side heat transfer tube of the intermediate heat exchanger by receiving cold heat from the heat-source-side refrigerant. Thereafter, the room is cooled by evaporating the condensed liquid refrigerant in the use-side heat exchanger.

Conversely, when the heat-dissipating operation is performed in the use-side heat exchanger such as indoor heating, the heat-source-side refrigerant condenses in the heat-source-side heat transfer tube of the intermediate heat exchanger, and the heat-source-side heat Evaporate in the exchanger. On the other hand, in the use side circuit, the use side refrigerant evaporates in the use side heat transfer tube of the intermediate heat exchanger,
By condensing in the use side heat exchanger, the room is heated.

[0005]

FIG. 2 shows such a 2
The temperature change state between refrigerant | coolants in the intermediate heat exchanger in a secondary refrigerant system is shown. In this drawing, a non-azeotropic refrigerant mixture is used as the refrigerant circulating in the utilization side circuit.
The left end of the graph shows the inlet side of the intermediate heat exchanger, and the right end shows the outlet side of the intermediate heat exchanger. The straight line I indicates the heat source side refrigerant, and the curve II indicates the temperature change state of the use side refrigerant.

As described above, at the inlet portion of the intermediate heat exchanger, a sufficient amount of heat exchange is obtained because the temperature difference between the respective refrigerants is large, and an efficient heat exchange operation is performed. However, the temperature of the use-side refrigerant approaches the temperature of the heat-source-side refrigerant toward the outlet side (the right side in the figure) of the intermediate heat exchanger, and the temperature difference gradually decreases. And
Near the outlet, there is almost no temperature difference, and the heat exchange efficiency is significantly reduced.

That is, in the conventional configuration, although the heat exchange efficiency is significantly reduced at the outlet of the intermediate heat exchanger, the use side refrigerant is completely liquefied at the time of cooling at the outlet of the intermediate heat exchanger. However, at the time of heating, the use side refrigerant needs to be completely gasified, so that the intermediate heat exchanger becomes large, and there is a limit in reducing the size of the intermediate heat exchanger.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object thereof is to provide an intermediate heat exchanger for performing heat exchange between a heat source side circuit and a use side circuit in a secondary refrigerant system. Is to reduce the size of the device.

[0009]

In order to achieve the above object, the present invention provides a so-called secondary refrigerant system having a heat source side circuit and a utilization side circuit capable of exchanging heat with each other, from an intermediate heat exchanger. By making the outflowing use-side refrigerant into a gas-liquid two-phase state, the size of the intermediate heat exchanger is reduced.

Specifically, as shown in FIGS. 1 and 7, the invention according to claim 1 comprises a heat source side means (A) through which a heat source side fluid flows and a use side means (B) through which the use side fluid circulates. Prepared, each means
By exchanging the fluids of (A, B) with each other in the intermediate heat exchanger (13), the use-side fluid undergoes a phase change between the gas phase and the liquid phase, and heat is exchanged between the two means (A, B). It is assumed that a refrigerating device that exchanges the information is used. And the above-mentioned use side means
The configuration is such that the utilization-side fluid in a gas-liquid two-phase state flows out from the outlet side of the intermediate heat exchanger (13) in (B).

According to this particular matter, the intermediate heat exchanger (13)
Since the amount of heat exchange in the heat exchanger is relatively small, the size of the intermediate heat exchanger (13) can be reduced.

According to a second aspect of the present invention, there is provided an intermediate heat exchanger (13).
Means for processing the use-side fluid in a gas-liquid two-phase state flowing out of the apparatus. That is, in the refrigeration apparatus according to claim 1, the intermediate heat exchanger (1
The same phase change as that in the intermediate heat exchanger (13) is performed at the outlet side of (3) at this outlet side, and the gas-liquid two-phase utilization side fluid flowing out of the intermediate heat exchanger (13) is vaporized. An auxiliary heat source means (30) for providing a single-phase state of a phase or a liquid phase is provided.

The invention according to claims 3 and 4 specifies the function of the auxiliary heat source means (30). That is, as shown in FIG. 3, in the refrigeration apparatus according to the second aspect, the use side means (B) includes the intermediate heat exchanger (13) and the use side heat exchanger (20). , 20) and the liquid line
(LL) and gas line (LG) to form a closed circuit. Also, the use side heat exchanger (20, 20) is connected to the intermediate heat exchanger (1
It is assumed that the use-side fluid flowing out from 3) to the liquid line (LL) is introduced and the heat-absorbing operation is performed by evaporation of the use-side fluid.
Further, the auxiliary heat source means (30) cools the gas-liquid two-phase use-side fluid flowing out of the intermediate heat exchanger (13) to liquefy the gas-phase use-side fluid.

According to a fourth aspect of the present invention, as shown in FIG. 8, the use-side means (B) is configured in the same manner as the third aspect of the present invention. In addition, the use side heat exchangers (20, 20) perform a heat radiation operation by introducing the use side fluid flowing out from the intermediate heat exchanger (13) to the gas line (LG) and condensing the use side fluid. . Further, the auxiliary heat source means (30) heats the gas-liquid two-phase use side fluid flowing out of the intermediate heat exchanger (13) to gasify the liquid use side fluid.

According to these specific items, the intermediate heat exchanger (13)
The use-side fluid in the gas-liquid two-phase state flowing out of the apparatus is changed to a predetermined liquid phase or gas phase and circulated to the use-side means (B). In particular, according to the third aspect of the invention, the use-side fluid in the gas-liquid two-phase state is liquefied and supplied to the use-side heat exchanger (20, 20). The heat-absorbing operation of) is performed well. On the other hand, in the invention according to claim 4, the use-side fluid in the gas-liquid two-phase state is gasified and the use-side heat exchanger (2
(0,20)
The heat radiation operation of (20, 20) is performed favorably.

According to the present invention, the refrigeration apparatus according to the third aspect is provided with an auxiliary heat source means (3).
(0) is embodied. That is, as shown in FIG. 3, in the refrigeration apparatus according to claim 3, the auxiliary heat source means (30) includes a compressor (33), a condenser (34), and an expansion mechanism ( EV-3), evaporator (32) and refrigerant pipe (35)
And a refrigeration circuit for connecting the auxiliary refrigerant in order so as to enable a refrigeration cycle of a vapor compression type. Also evaporator
The use-side fluid flowing out of the intermediate heat exchanger (13) to the liquid line (LL) is cooled by the auxiliary refrigerant evaporated in (32).

According to a sixth aspect of the present invention, there is provided a refrigeration apparatus according to the fifth aspect, as shown in FIG.
(34) performs heat exchange with the outside air.

According to a seventh aspect of the present invention, as shown in FIG. 4, in the refrigerating apparatus according to the fifth aspect, a cooling water pipe (A3) through which cooling water flows is provided, and a condenser (34) is provided. Heat is exchanged with the cooling water flowing through the cold water pipe (A3).

According to an eighth aspect of the present invention, as shown in FIG. 5, in the refrigeration apparatus according to the fifth aspect, the condenser (34)
Is to exchange heat with the use side fluid cooled by the auxiliary refrigerant of the evaporator (32).

According to a ninth aspect of the present invention, as shown in FIG. 6, in the refrigeration apparatus according to the fifth aspect, the condenser (34)
Is evaporated in the use side heat exchanger (20, 20), and then
(LG) exchanges heat with the use side fluid flowing toward the intermediate heat exchanger (13).

According to these specific items, the auxiliary heat source means (3
(0) The intermediate heat exchanger by the auxiliary refrigerant evaporating in the evaporator (32)
The two-phase use side fluid flowing out of the liquid line (LL) from (13) is cooled, and the use side fluid is liquefied. Excess heat of the refrigerant circulating in the auxiliary heat source means (30) is radiated to the outside air and other fluids. In particular, according to the seventh and eighth aspects of the present invention, it is possible to condense the refrigerant of the auxiliary heat source means (30) at a relatively low temperature.

According to the tenth to thirteenth aspects, the configuration of the auxiliary heat source means (30) is embodied in the refrigeration apparatus according to the fourth aspect. That is, as shown in FIG. 8, in the refrigeration apparatus according to the fourth aspect, the auxiliary heat source means (30) is connected to the compressor (3).
3) A refrigeration circuit that connects a condenser (34), an expansion mechanism (EV-3), and an evaporator (32) in order so that auxiliary refrigerant can be circulated by a refrigerant pipe (35) to perform a vapor compression refrigeration cycle. Composed of Also,
The auxiliary refrigerant condensing in the condenser (34) causes the intermediate heat exchanger (1
The configuration is such that the use side fluid flowing out from 3) to the gas line (LG) is heated.

According to an eleventh aspect of the present invention, as shown in FIG. 8, in the refrigerating apparatus according to the tenth aspect, the evaporator (32) exchanges heat with the outside air.

According to a twelfth aspect of the present invention, as shown in FIG. 9, in the refrigerating apparatus according to the tenth aspect, a hot water pipe (A4) through which hot water flows is provided, and the evaporator (32) is connected to the hot water pipe. Heat is exchanged with the hot water flowing through the pipe (A4).

According to a thirteenth aspect of the present invention, as shown in FIG. 10, in the refrigeration apparatus according to the tenth aspect, an evaporator is provided.
(32) performs heat exchange with the use-side fluid condensed in the use-side heat exchangers (20, 20).

According to these specific items, the auxiliary heat source means (3
0) Intermediate heat exchanger by auxiliary refrigerant condensing in condenser (34)
The two-phase use side fluid flowing out from (13) to the gas line (LG) is heated, and the use side fluid is gasified. Also,
The surplus cold heat of the refrigerant circulating in the auxiliary heat source means (30) is radiated to the outside air and other fluids. In particular, in the twelfth aspect, the refrigerant of the auxiliary heat source means (30) can be evaporated at a relatively high temperature.

[0027] The invention according to claim 14 is the invention according to claim 8.
The refrigerating apparatus according to claim 1, further comprising a recovery means (70) for performing heat exchange with the auxiliary refrigerant of the condenser (34) and recovering the gasified use side fluid in the gas line (LG) of the use side means (B). ing.

According to this specific matter, the use side heat exchanger (20,
The gas refrigerant flowing toward 20) is recovered by the recovery means (70) to the gas line (LG). In other words, the use side heat exchanger
By flowing by bypassing (20, 20), it becomes possible to favorably perform the heat absorbing operation in the use side heat exchanger (20, 20).

According to the present invention, the gas phase and the liquid phase of the use side fluid flowing out of the intermediate heat exchanger (13) are separated and one of them is bypassed. That is,
According to a fifteenth aspect of the present invention, as shown in FIG. 20, in the refrigerating apparatus according to the first aspect, the use-side means (B) includes an intermediate heat exchanger (13) and a use-side heat exchanger (20, 20). ) And liquid line
(LL) and a closed circuit connected by a gas line (LG). In addition, the intermediate heat exchanger (1
The use side fluid flowing out from 3) to the liquid line (LL) is introduced, and the heat absorption operation is performed by evaporation of the use side fluid. on the other hand,
The liquid line (LL) is provided with a mechanical pump (21) for obtaining a driving force for circulating the use-side fluid. And
Flow from the intermediate heat exchanger (13) to the liquid line (LL) and pump (2
A bypass means (75) for bypassing the gas-phase fluid of the utilization-side fluid in the gas-liquid two-phase state flowing toward 1) to the discharge side of the pump (21) is provided.

According to a sixteenth aspect of the present invention, as shown in FIG. 21, the use-side means (B) and the use-side heat exchangers (20, 20) are configured in the same manner as the above-described claim 15. In addition, the gas-phase fluid of the gas-liquid two-phase use side fluid flowing out from the intermediate heat exchanger (13) to the liquid line (LL) and flowing toward the pump (21) is used as the gaseous fluid of the use side means (B). The gas line (LG) is provided with a bypass means (75) for bypassing.

According to these specific items, the mechanical pump (21)
It is possible to avoid the gas-phase use-side fluid from flowing into the suction side of the pump, thereby ensuring the reliability of the pump.

According to a seventeenth aspect of the present invention, as shown in FIG. 22, in the refrigerating apparatus according to the first aspect, the use-side means (B) includes an intermediate heat exchanger (13) and a use-side heat exchanger ( 20, 20) in a closed circuit connected by a liquid line (LL) and a gas line (LG). Further, the use-side fluid that has flowed out of the intermediate heat exchanger (13) into the gas line (LG) is introduced into the use-side heat exchangers (20, 20), and a heat radiation operation is performed by condensing the use-side fluid. On the other hand, the liquid line (LL) is provided with a mechanical pump (21) for obtaining a driving force for circulating the use-side fluid. Then, the liquid-phase fluid of the gas-liquid two-phase use-side fluid flowing from the intermediate heat exchanger (13) to the gas line (LG) and flowing toward the use-side heat exchanger (20, 20) is pumped. A configuration is provided in which bypass means (75) for bypassing is provided on the discharge side of (21).

According to an eighteenth aspect of the present invention, as shown in FIG. 23, the use-side means (B) and the use-side heat exchangers (20, 20) are configured in the same manner as in the above-described claim 17. In addition, the liquid-phase fluid of the gas-liquid two-phase usage-side fluid flowing from the intermediate heat exchanger (13) to the gas line (LG) and flowing toward the usage-side heat exchanger (20, 20) is pumped. The bypass means (75) for bypassing the suction side of (21) is provided.

According to these specific items, the use side heat exchanger (2
The liquid-side use-side fluid can be prevented from flowing into the use-side heat exchanger (20, 20), and the heat-dissipating operation of the use-side heat exchanger (20, 20) can be performed well.

The inventions of claims 19 to 23 specify the structure of the means for conveying the use side fluid.
According to a nineteenth aspect of the present invention, as shown in FIG. 11, in the refrigeration apparatus according to any one of the first to fourteenth aspects, the utilization side means (B) obtains a driving force for circulating the utilization side fluid. Transport means (40, 60). In addition, this transport means (4
(0,60), at least a pressurizing means (42) for generating a high pressure by heating the liquid-side use-side fluid and a pressure-reducing means (43) for generating a low pressure by cooling the gas-phase use-side fluid. One of them is provided, and the driving force for circulating the use-side fluid is generated by the difference between the pressure generated by the means (42), (43) and the pressure in the use-side means (B).

This particularity results in a circulating drive without the use of mechanical means.

[0037] The twentieth aspect of the present invention provides the above-described first to the first aspects.
14. The refrigeration apparatus according to one of claims 14, wherein
(B) shows a conveying means for obtaining a circulation driving force of the use side fluid.
(40,60). Further, the transport means (40, 60) is provided with a driving force generating circuit (40) capable of storing the liquid-side use-side fluid. The driving force generation circuit (40) is configured to be capable of exchanging heat with the driving source means (60), and to extrude the liquid-side utilization side fluid of the driving force generation circuit (40) to the utilization side means (B). Pressurizing means (42) for generating a high pressure by heating the liquid-side use side fluid of the driving force generation circuit (40), and driving force generation of the liquid phase use side fluid of the use side means (B). A pressure reducing means (43) for generating a low pressure by cooling the gas-phase use-side fluid of the driving force generation circuit (40) so as to be sucked into the circuit (40) is provided.

According to the twenty-first aspect of the present invention, the above-mentioned twenty-second aspect is provided.
In the refrigerating apparatus described above, the driving force generation circuit (40) is provided with tank means (T1, T2) capable of storing the liquid-side use-side fluid. The high pressure generated by the pressurizing means (42) due to the heating of the use side fluid acts on the tank means (T1, T2) to cause the tank means (T
(T1, T2) and a low pressure generated by the decompression means (43) due to the cooling of the use-side fluid, and the tank means (T1, T2). , T2)
The use-side fluid is circulated to the use-side means (B) by a pressure-reducing operation for collecting the liquid-side use-side fluid.

According to these specific items, the circulating driving force of the use side fluid in the use side means (B) can be reliably obtained by the pressurizing operation by the pressurizing means (42) and the pressure reducing operation by the pressure reducing means (43). become.

[0040] The invention of claim 22 provides the above-mentioned claim 20.
In the refrigeration apparatus described above, the drive source means (60) is constituted by a refrigeration circuit capable of circulating a refrigerant. The refrigerant in the refrigeration circuit and the utilization-side fluid in a gas-liquid two-phase state flowing out of the intermediate heat exchanger (13) exchange heat with the utilization-side fluid to be in a gas phase or a liquid phase single phase state.

According to this specific matter, the means for obtaining the driving force for circulating the use-side fluid in the use-side means (B) is changed into a single-phase two-side use-side refrigerant flowing out of the intermediate heat exchanger (13). The structure can be simplified.

According to the twenty-third aspect of the present invention,
In the refrigeration apparatus described above, the tank means is constituted by first and second tank means (T1, T2) connected in parallel with each other. High pressure is applied to the first tank means (T1) and the second tank means
(T2) is alternately switched between a first pressure action operation for applying a low pressure to the first tank means (T1) and a second pressure action action for applying a low pressure to the second tank means (T2). During the first pressure action operation, a liquid-phase use-side fluid is supplied from the first tank means (T1) to the use-side means (B), and the use-side means (B) is supplied from the use-side means (B) to the second tank means (T2). While collecting the liquid-phase use-side fluid, during the second pressure action operation, the liquid-phase use-side fluid is supplied from the second tank means (T2) to the use-side means (B), and the use-side means (B ) To the first tank means (T1)
The use-side fluid is circulated so as to collect the liquid-phase use-side fluid.

According to this specific matter, the liquid-side use-side fluid is pushed out from one of the tank means, and the liquid-phase use-side fluid is recovered into the other tank means. The circulation operation of the use side fluid in B) is performed continuously. Therefore, when the present invention is applied to an air conditioner or the like, the indoor air-conditioning state can be favorably maintained for a long time.

[0044] The invention according to claims 24 to 26 specifies the structure of the heat source side means (A). That is, claim 2
According to a fourth aspect of the present invention, in the refrigeration apparatus according to any one of the first to twenty-third aspects, the heat source side means (A) performs an absorption refrigeration cycle.

According to the twenty-fifth aspect of the present invention,
23. The refrigeration apparatus according to one of 23, wherein the heat source side means
(A) is to perform a vapor compression refrigeration cycle.

According to the twenty-sixth aspect of the present invention,
23. The refrigeration apparatus according to one of 23, wherein the heat source side means
(A) uses the heat of the district heating and cooling system.

By these specific items, the heat source side means (A) can be embodied. In particular, when a system that performs a vapor compression refrigeration cycle is adopted, the reliability of the device can be ensured, and when a system that performs an absorption refrigeration cycle is employed, there is no need to use a refrigerant such as chlorofluorocarbon. A heat source suitable for a problem or the like can be realized, and a relatively large amount of heat can be easily secured when a district cooling / heating system is adopted.

According to the twenty-seventh aspect of the present invention,
26. The refrigeration apparatus according to any one of 26, wherein the use side fluid is a non-azeotropic refrigerant mixture.

In this type of refrigerant, a temperature gradient occurs due to the heat exchange operation, so in the conventional configuration, the temperature difference between the fluids becomes extremely small, especially near the outlet of the intermediate heat exchanger. By causing the use-side refrigerant to flow out of the intermediate heat exchanger in a gas-liquid two-phase state as in the present invention, high heat exchange efficiency can be obtained even when this kind of refrigerant is used.

According to the twenty-eighth aspect of the present invention, the above-mentioned third to third aspects are provided.
In the refrigeration apparatus described in any one of 14, 19 to 27, the use-side heat exchangers (20, 20) are indoor heat exchangers arranged in an air-conditioned room.

According to the specific items, an apparatus to which the refrigeration apparatus according to the present invention is applied is embodied.

[0052]

Embodiment 1 Hereinafter, Embodiment 1 of the present invention will be described with reference to the drawings. In the first embodiment, a case will be described in which the present invention is applied to an air conditioner for cooling a plurality of air conditioning rooms.

-Explanation of Refrigerant Circuit- As shown in FIG. 1, the air conditioner of the present embodiment is provided with one outdoor unit (1) and two indoor units (2, 2), so-called cooling only. As an indoor multi-unit.
These units (1, 2, 2) are connected to the liquid and gas side
(LL, LG). In other words, the indoor side of the liquid side communication pipe (LL) as a liquid line is branched and the indoor side of the gas side communication pipe (LG) as a gas line is also branched to the liquid side of each indoor unit (2, 2). It is connected to the gas side of each indoor unit (2, 2).

The outdoor unit (1) contains a primary refrigerant circuit (A) as a heat source side means as a heat source side means. The primary refrigerant circuit (A) is configured by a refrigerator that performs an absorption type refrigeration cycle. In the primary refrigerant circuit (A), for example, water is used as a refrigerant, and a lithium bromide aqueous solution is used as an absorbing liquid.

The primary refrigerant circuit (A) includes a pump (10), a regenerator (11), a condenser (12), an expansion valve (EV-1), and an intermediate heat exchanger.
(13) A primary heat transfer tube (13A) and an absorber (14) are provided. These devices are connected by a pipe (15) to form a closed circuit. At the outlet side of the regenerator (11), a rectifier (16) for separating a refrigerant as a heat source side fluid and an absorbing liquid is provided. The rectifier (16) and the absorber (14) are connected by an absorbent pipe (17).

The regenerator (11) is supplied from the absorber (14) to the pump (1).
0), a low-concentration absorbing solution (a solution in which a refrigerant is absorbed in an absorbing solution) is supplied. Further, in the regenerator (11), a heating gas is supplied from outside so as to evaporate the refrigerant by heating the low-concentration absorption solution and concentrate the absorption solution.

The condenser (12) liquefies the evaporative refrigerant supplied from the regenerator (11) via the rectifier (16). An air-cooling fan (not shown) for introducing cooling air is provided. Is provided.

The primary heat transfer tube (13) of the intermediate heat exchanger (13)
A) is supplied with a refrigerant that is liquefied through a condenser (12) and decompressed by an expansion valve (EV-1), and the refrigerant is used as a use-side means by the refrigerant.
Heat is taken from the secondary refrigerant circuit (B).

The absorber (14) converts the refrigerant vaporized by the heat taken from the secondary refrigerant circuit (B) by the primary heat transfer tube (13A) of the intermediate heat exchanger (13) into the rectifier (16). ) Is absorbed by a high-concentration absorbing solution supplied through an absorbing solution pipe (17), and the concentration of the absorbing solution is reduced.

Next, the secondary refrigerant circuit (B) will be described. Each of the indoor units (2, 2) includes an indoor electric valve (EV-2) and an indoor heat exchanger (20) as a use-side heat exchanger. The liquid side of the indoor electric valve (EV-2) is connected to the liquid side connection pipe (L
L), and the gas side of the indoor heat exchanger (20) is connected to the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) through the gas side communication pipe (LG). . Further, a pump (21) for circulating a refrigerant in the secondary-side refrigerant circuit (B) is provided in the liquid-side communication pipe (LL) of the secondary-side refrigerant circuit (B). Further, the refrigerant as the use-side fluid filled in the secondary-side refrigerant circuit (B) is a non-azeotropic mixed refrigerant (for example, R407C) composed of a plurality of types of refrigerants having different boiling points.

With such a configuration, the intermediate heat exchanger (13)
In this configuration, heat can be exchanged between the primary heat transfer tube (13A) and the secondary heat transfer tube (13B). That is, the primary heat transfer tube (13A)
The heat exchange is performed between the primary refrigerant flowing through the secondary heat transfer tube (13B) and the primary refrigerant flowing through the secondary heat transfer tube (13B). That is, via the intermediate heat exchanger (13), the primary refrigerant circuit (A)
This circuit is configured as a so-called secondary refrigerant system in which a heat transfer member and a secondary refrigerant circuit (B) are connected.

The feature of this embodiment lies in the size of the intermediate heat exchanger (13) and the auxiliary heat source circuit (30) as auxiliary heat source means connected to the liquid side communication pipe (LL). Hereinafter, these will be described.

The intermediate heat exchanger (13) includes a secondary refrigerant circuit (B)
Of the secondary refrigerant circulating through the gas side communication pipe (LG) and reaching the secondary heat transfer pipe (13B) is small enough to obtain a heat exchange amount that does not liquefy Things have been adopted. That is, a part of the refrigerant flowing through the gas side communication pipe (LG) and reaching the secondary side heat transfer pipe (13B) is liquefied, and the other is led out to the liquid side communication pipe (LL) in a gas phase. It has become.

The auxiliary heat source circuit (30) comprises a heat source section (31) and an evaporator.
(32) are connected so that circulation of the auxiliary refrigerant is possible. The heat source section (31) is a means for generating cold heat (for example, a Peltier element or the like), while the evaporator (32) is connected to the liquid side communication pipe (L
L) is heat-exchangeably connected to a part thereof, and cools the secondary refrigerant flowing through the liquid communication pipe (LL). Therefore, as described above, the gas-liquid two-layer refrigerant derived from the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) is cooled by the auxiliary refrigerant evaporating in the evaporator (32), and the gas-phase refrigerant is cooled. Is condensed and liquefied, and a secondary refrigerant consisting of only a liquid phase is introduced into the pump (21).

-Description of Refrigerant Circulation Operation- Next, the refrigerant circulation operation of the present embodiment will be described. During indoor cooling operation, in the primary refrigerant circuit (A), a low-concentration absorbing solution is supplied from the absorber (14) to the regenerator (11) via the pump (10). In the regenerator (11), the low concentration absorption solution is heated and evaporated, and the absorption solution is separated into vapor and high concentration absorption solution in the rectifier (16). The separated steam is
The condenser (12) exchanges heat with the outside air to condense. The condensed refrigerant is decompressed by the expansion valve (EV-1), and then the intermediate heat exchanger (1
3), the heat is exchanged with the secondary-side refrigerant of the secondary-side heat transfer tube (13B), and heat is taken from the secondary-side refrigerant and vaporized. The vaporized primary-side refrigerant and the high-concentration absorbent supplied from the rectifier (16) via the absorbent pipe (17) are supplied to the absorber (14). Here, the high-concentration absorbing solution absorbs the primary refrigerant and has a low concentration. This low-concentration absorption solution passes through a pump (10) and is
(11). Such a circulation operation is performed in the primary refrigerant circuit (A).

On the other hand, in the secondary refrigerant circuit (B), as indicated by the arrow in FIG. 1, the liquid-phase secondary refrigerant discharged from the pump (21) is supplied to the outdoor electric expansion valves (EV-2, EV-2). After passing through -2), heat is exchanged with indoor air in the indoor heat exchangers (20, 20) to evaporate. This cools the room air. After that, the secondary refrigerant passes through the gas side connection pipe (LG)
Return to the secondary heat transfer tube (13B) in (13). This intermediate heat exchanger (1
In 3), a part of the secondary refrigerant in the gas phase exchanges heat with the primary refrigerant to liquefy, and the others remain in the gas phase and remain in the liquid connection pipe (L
L). That is, at the outlet side of the secondary heat transfer tube (13B), the secondary refrigerant is discharged in a two-phase state of gas and liquid. The secondary-side refrigerant derived from the secondary-side heat transfer tube (13B) exchanges heat with the auxiliary refrigerant evaporated in the evaporator (32) of the auxiliary heat source circuit (30). As a result, the gas phase of the secondary refrigerant in the two-phase state is liquefied, and all of the secondary refrigerant becomes a liquid phase and is introduced into the pump (21). Such a refrigerant circulation operation is performed in the secondary refrigerant circuit (B).

Because of the refrigerant circulation operation described above,
In the intermediate heat exchanger (13), not only at the inlet but also at the outlet, the temperature difference between the refrigerants is large. Therefore, a sufficient amount of heat exchange can be obtained in the entire intermediate heat exchanger (13), and an efficient heat exchange operation is performed. This will be described with reference to the graph of FIG. 2. When the outlet position of the intermediate heat exchanger (13) is set to a point α in FIG. 2, the outlet portion between the primary refrigerant and the secondary refrigerant Has a temperature difference of only β. For this reason, heat exchange is performed with high efficiency also at this outlet portion. Also, the straight line I
The area of the part sandwiched between the curve II and the curve II indicates the total heat exchange amount between the respective refrigerants. The exit position of the intermediate heat exchanger (13) was set at the point α in FIG. Even in this case, a sufficient heat exchange amount (the shaded portion in FIG. 2) is obtained, and a large intermediate heat exchanger (from the left end in FIG. 2) is used to liquefy all of the secondary refrigerant as in the conventional case. It is not necessary to use a heat exchanger having a pipe to the right end. That is, the intermediate heat exchanger (1
The size of the intermediate heat exchanger (13) can be reduced while obtaining high efficiency in (3). In particular, as in the present embodiment, when a non-azeotropic mixed refrigerant is employed as the refrigerant to be charged into the secondary-side refrigerant circuit (B), this type of refrigerant has a temperature gradient accompanying heat exchange, so that the effect is remarkable. It is. Also, the intermediate heat exchanger (1
The auxiliary heat source circuit (30) is located on the outlet side of the secondary heat transfer tube (13B) in 3).
And the refrigerant in the two-phase state is made into the liquid phase, so that the gas refrigerant is not sucked into the pump (21) and a highly reliable refrigerant circulation operation can be performed. It is.

An intermediate heat exchanger having the same size as the conventional one
When (13) is adopted and the outlet side of the secondary refrigerant is brought into a two-phase state, the pressure inside the secondary refrigerant circuit (B) is set to be low. By employing the above, the evaporation temperature of the secondary-side refrigerant in the indoor heat exchanger (20, 20) can be lowered, and the indoor cooling can be efficiently performed.

[0069]

[Modification of Auxiliary Heat Source Circuit] Next, a specific example of the auxiliary heat source circuit (30) will be described as a modification of the first embodiment.

(Modification 1) The auxiliary heat source circuit (30) of Modification 1 shown in FIG. 3 performs a vapor compression refrigeration cycle. That is, the compressor (33), the condenser (34), the electric expansion valve (E
V-3) and an evaporator (32) are connected in order by a refrigerant pipe (35). The condenser (34) is an air-cooled type that exchanges heat between the auxiliary refrigerant and the outside air. The evaporator (32) is heat-exchangeably connected to a part of the liquid-side communication pipe (LL) in the same manner as described above, and cools the secondary refrigerant of the liquid-side communication pipe (LL). It has become. Therefore, also in this example, the gas-liquid two-layer refrigerant derived from the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) is cooled by the evaporator (32), and the gas-phase refrigerant is condensed and liquefied. The pump (21) has a configuration in which a refrigerant composed of only a liquid phase is introduced.

(Modification 2) A modification 2 shown in FIG. 4 employs a district cooling / heating system as the heat source side means (A).
That is, the inlet side of the primary heat transfer tube (13A) of the intermediate heat exchanger (13) is connected to the cold water pipe (A1), and the outlet side is connected to the hot water pipe (A2). The cold water flowing into the heat pipe (13A) functions as a heat source side fluid. Further, the auxiliary heat source circuit (30) is configured such that the condenser (34) exchanges heat with cooling water flowing through the other cold water pipe (A3) to condense the auxiliary refrigerant.

According to this configuration, the condenser (34) exchanges heat with the comparatively low-temperature cooling water, so that the condensing temperature of the auxiliary refrigerant can be set low and the COP can be improved. is there.

(Modification 3) In the auxiliary heat source circuit (30) of Modification 3 shown in FIG. 5, the condenser (34) is connected to a pipe () located downstream of the pump (21) of the secondary refrigerant circuit (B). (Liquid side communication pipe) so that heat exchange is possible. In other words, after being cooled by the evaporator (32), the secondary refrigerant passed through the pump (21) and the condenser (34)
It is possible to exchange heat with. Also in this case, the condenser (34) is compared with the air-cooled type such as the first modification.
The COP can be set low and the COP can be improved.

(Modification 4) In the auxiliary heat source circuit (30) of Modification 4 shown in FIG. 6, the condenser (34) is connected to the gas side communication pipe (LG) of the secondary refrigerant circuit (B). It is connected so that heat exchange is possible.
In this case, since the secondary-side refrigerant is not heated downstream of the pump (21), the low-temperature secondary refrigerant is supplied to the indoor unit.
The secondary refrigerant can be supplied, and the indoor cooling can be performed well.

[0075]

Second Embodiment Next, a second embodiment of the present invention will be described with reference to the drawings. In the second embodiment, a case will be described in which the present invention is applied to an air conditioner for heating a plurality of air conditioning rooms. In the present embodiment, only differences from the above-described first embodiment will be described.

-Explanation of Refrigerant Circuit- As shown in FIG. 7, the air conditioner of the present embodiment is configured such that the intermediate heat exchanger (13) is connected to the hot water pipe (A2) of the district cooling / heating system by two heat exchangers.
The heat is supplied to the secondary refrigerant. That is, hot water flows through the primary heat transfer tube (13A) of the intermediate heat exchanger (13), and the secondary refrigerant evaporates through the secondary heat transfer tube (13B). In the secondary refrigerant circuit (B) of the present embodiment, the secondary refrigerant circulates in the opposite direction to the secondary refrigerant circuit (B) of the first embodiment. That is, the secondary-side refrigerant evaporated in the secondary-side heat transfer tube (13B) of the intermediate heat exchanger (13) is condensed in the indoor heat exchanger (20) to heat the room.

The feature of this embodiment is that the intermediate heat exchanger (13)
Size and auxiliary heat source circuit (30). Hereinafter, these will be described.

The intermediate heat exchanger (13) includes a secondary refrigerant circuit (B)
Adopts a small refrigerant that circulates through the liquid side communication pipe (LL) and reaches the secondary heat transfer pipe (13B), so that all of the refrigerant exchanges enough heat to prevent gasification. Have been. That is, a part of the refrigerant flowing through the liquid side communication pipe (LL) and reaching the secondary side heat transfer pipe (13B) is gasified, and the other is led out to the gas side communication pipe (LG) in a liquid phase. It has become.

The auxiliary heat source circuit (30) comprises a secondary refrigerant circuit (B)
Of the heat source (31) and the condenser
(34) are connected so that circulation of the auxiliary refrigerant is possible. The heat source section (31) is a means for generating heat (Peltier element, boiler, etc.), while the condenser (34) is connected to a part of the gas side communication pipe (LG) so as to be able to exchange heat. The secondary side refrigerant of the gas side communication pipe (LG) is heated. Therefore, as described above, the secondary refrigerant of the gas-liquid two-layer derived from the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) is heated by the auxiliary refrigerant condensed in the condenser (34). The liquid-phase secondary-side refrigerant is evaporated to be gasified and introduced into the indoor heat exchanger (20).

-Description of Refrigerant Circulation Operation- Next, the refrigerant circulation operation of the present embodiment will be described. During the indoor heating operation, hot water is supplied to the primary-side heat transfer tube (13A) of the intermediate heat exchanger (13) as shown by the dashed arrow in FIG.

On the other hand, in the secondary refrigerant circuit (B), as shown by the solid arrow in FIG. 7, the liquid secondary refrigerant discharged from the pump (21) is supplied to the intermediate heat exchanger (13). Secondary side heat transfer tube (13B)
Will be introduced. In the intermediate heat exchanger (13), a part of the liquid-phase secondary-side refrigerant exchanges heat with hot water on the primary side to gasify, and the others remain in the liquid phase as gas-side connecting pipes (LG) Is derived.
In other words, at the outlet side of the secondary heat transfer tube (13B),
The secondary refrigerant is discharged in the phase state. This secondary heat transfer tube (1
The secondary refrigerant derived from 3B) exchanges heat with the auxiliary refrigerant condensed in the condenser (34) of the auxiliary heat source circuit (30). Thereby, the liquid phase of the secondary refrigerant in the two-phase state is gasified, and all of the secondary refrigerant becomes a gas phase and is introduced into the indoor heat exchanger (20, 20). In the indoor heat exchanger (20, 20), the gas-phase refrigerant exchanges heat with indoor air to condense. This heats the room air. This indoor heat exchanger
The secondary refrigerant liquefied in (20, 20) is recovered by the pump (21). Such a refrigerant circulation operation is performed in the secondary refrigerant circuit (B).

Because of the refrigerant circulation operation described above,
Also in the present embodiment, the temperature difference between the refrigerants is large at the outlet portion of the intermediate heat exchanger (13), and the intermediate heat exchanger (1
A sufficient amount of heat exchange is obtained in the whole of 3), and efficient heat exchange operation is performed. That is, the size of the intermediate heat exchanger (13) can be reduced while obtaining high efficiency in the intermediate heat exchanger (13).

[0083]

[Modification of Auxiliary Heat Source Circuit] Next, a specific example of the auxiliary heat source circuit (30) will be described as a modification of the second embodiment.

(Modification 1) The auxiliary heat source circuit (30) of Modification 1 shown in FIG. 8 performs a vapor compression refrigeration cycle. That is, the compressor (33), the condenser (34), the electric expansion valve (E
V-3) and an evaporator (32) are connected in order by a refrigerant pipe (35). The evaporator (32) is an air-cooled type that exchanges heat between the auxiliary refrigerant and the outside air. The condenser (34) is heat-exchangeably connected to a part of the gas-side communication pipe (LG) as described above, and heats the secondary refrigerant of the gas-side communication pipe (LG). It has become. Therefore, also in this example, the gas-liquid two-layer secondary refrigerant derived from the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) is heated by the condenser (34) to evaporate the liquid-phase refrigerant. Then, the refrigerant is gasified and introduced into the indoor heat exchanger (20) with a refrigerant consisting of only a gas phase.

(Modification 2) In the auxiliary heat source circuit (30) of Modification 2 shown in FIG. 9, the evaporator (32) exchanges heat with the hot water flowing through the hot water pipe (A4) of the district cooling and heating system. Thus, the auxiliary refrigerant is evaporated.

[0086] According to this configuration, since the evaporator (32) exchanges heat with hot water having a comparatively high temperature, the evaporating temperature of the auxiliary refrigerant can be set high and the COP can be improved. .

(Modification 3) In the auxiliary heat source circuit (30) of Modification 3 shown in FIG. 10, the evaporator (32) is connected to the liquid side communication pipe (LL) of the secondary refrigerant circuit (B). It is connected so that heat exchange is possible.
In this case, since the secondary refrigerant is cooled on the upstream side of the pump (21), it is possible to reliably prevent the gas refrigerant from being sucked into the pump (21).

[0088]

Embodiment 3 Hereinafter, Embodiment 3 of the present invention will be described with reference to the drawings. In the third embodiment, means for obtaining a circulating driving force of the secondary refrigerant in the secondary refrigerant circuit (B) is improved. Other configurations are the same as those of the first embodiment. Therefore, in this embodiment, only the means for obtaining the circulating driving force will be described. Note that the air conditioner of the present embodiment is configured as an air conditioner capable of switching between indoor cooling operation and heating operation.

-Description of Refrigerant Circuit- As shown in FIG. 11, the secondary refrigerant circuit (B) of the present embodiment
A driving force generation circuit (40) instead of the pump (21) provided in the liquid side communication pipe (LL) of the first embodiment described above and a driving source circuit (60) connected to the driving force generation circuit (40) It has. Hereinafter, each circuit (40, 60) will be described.

The driving force generating circuit (40) is connected to the liquid side communication pipe (LL) of the secondary refrigerant circuit (B) via the four way switching valve (41). One port of the four-way switching valve (41) is connected to the liquid side of the indoor unit, and the other port is connected to the liquid side of the secondary heat transfer tube (13B) of the intermediate heat exchanger (13). I have.

The driving force generating circuit (40) includes a heat absorbing portion (42B) of a circulating heater (42) as a pressurizing means, and a heat radiating portion (43B ), First and second tanks (T1, T2) as tank means, and a cooler for cooling the secondary-side refrigerant recovered from the liquid-side communication pipe (LL) to the driving force generation circuit (40) ( 44) is provided.

More specifically, a gas supply pipe (45) is connected to the upper end of the heat absorbing section (42B) of the circulation heater (42). The gas supply pipe (45) is branched into two branch pipes (45a, 45b), each of which is individually connected to the upper end of each tank (T1, T2). Each of these branch pipes (45a, 45b) is provided with first and second tank pressurizing solenoid valves (SV-P1, SV-P2). Further, liquid refrigerant push-out pipes (47, 47) are connected to lower ends of the tanks (T1, T2). The liquid refrigerant push-out pipes (47, 47) join and are connected to one port of the four-way switching valve (41). Each of the liquid refrigerant push-out pipes (47, 47) is provided with a check valve (CV, CV) that allows only the flow of the refrigerant from the tank (T1, T2) to the four-way switching valve (41). One end of a liquid recovery pipe (48) is connected to the lower end of the heat absorbing section (42B) of the circulation heater (42). The other end of the liquid recovery pipe (48) is connected to the liquid refrigerant extrusion pipe (47). The height of the circulation heater (42) is set at each tank (T1, T2).
It is set below.

On the other hand, a gas recovery pipe (46) is connected to the upper end of the radiator (43B) of the circulation cooler (43). This gas recovery pipe (46) is also branched into two branch pipes (46a, 46b), each of which is connected to each branch pipe (45a, 45b) of the gas supply pipe (45), so that each tank ( T1, T2) are individually connected to the upper end. These branch pipes (46a, 46b) are provided with first and second tank pressure reducing solenoid valves (SV-V1, SV-V2). The lower end of each tank (T1, T2) is connected to the liquid refrigerant return pipe (4
9,49). The other end of the liquid refrigerant return pipe (49) joins and is connected to one port of the four-way switching valve (41) via the heat radiator (44B) of the cooler (44). Each of the liquid refrigerant return pipes (49, 49) is provided with a check valve (CV, CV) that allows only the flow of the refrigerant from the cooler (44) to the tank (T1, T2). In addition, one end of a liquid supply pipe (50) is connected to a lower end of the heat radiating portion (43B) of the circulation cooler (43). The other end of the liquid supply pipe (50) is branched, and each is individually connected to a liquid refrigerant push-out pipe (47, 47). In addition, the liquid supply pipe (50) has a check valve (C) that allows only the flow of the refrigerant from the radiator (43B) of the circulation cooler (43) to each of the tanks (T1, T2).
V, CV). Note that the arrangement height position of the circulation cooler (43) is set above each tank (T1, T2).

When the four-way switching valve (41) is switched to the solid line side in the figure, the liquid refrigerant push-out pipes (47, 47) communicate with the indoor unit and the intermediate heat exchanger (13) The secondary heat transfer tube (13B) communicates with the heat radiating portion (44B) of the cooler (44). On the other hand, when the four-way switching valve (41) is switched to the broken line side in the figure, the liquid refrigerant push-out pipes (47, 47) communicate with the secondary heat transfer pipe (13B) of the intermediate heat exchanger (13). In addition, the indoor unit is configured to communicate with the radiator (44B) of the cooler (44).

Next, a driving source circuit (60) for generating a circulation driving force of the refrigerant in the driving force generation circuit (40).
Will be described.

The drive source circuit (60) includes a compressor (61), a radiator (42A) of the circulating heater (42), a plurality of electric valves (EV-4).
~ EV-6), heat absorbing part (44A) of cooler (44), cooler for circulation (43)
And an air condenser (34), which are connected by a refrigerant pipe (62). In particular,
The discharge side of the compressor (61) is branched, and each is circulated by a circulation heater (4
It is connected to the radiator (42A) and the air condenser (34) of 2). A capillary tube (CP) is provided on the outlet side of the radiator (42A) of the circulation heater (42), and a motor-operated valve (EV-4) is provided on the outlet side of the air condenser (34). These outlet-side pipes are merged once, then branched, and one of them is connected to an electric expansion valve (EV-
5) through the heat absorbing portion (43A) of the circulation cooler (43), and the other also through the electric expansion valve (EV-6), and the heat absorbing portion (44A) of the cooler (44).
Connected to each other. Heat absorption part of circulation cooler (43) (4
The outlet sides of the heat absorbing section (44A) of the cooler (44) and the cooler (44) are merged and connected to the suction side of the compressor (61).

With such a structure, the compressor (61)
With the driving of the circulating heater (42), the refrigerant of the driving force generating circuit (40) is heated by the circulation heater (42), and the air condenser (34)
While the heat is dissipated, the circulation cooler (43) and the cooler (44) are configured to deprive the refrigerant of the driving force generation circuit (40) of the heat.

The above is the configuration of the refrigerant circuit of the air conditioner according to the present embodiment.

-Cooling operation- Next, the indoor cooling operation will be described. During this operation, first, the four-way switching valve (41) is switched to the solid line side in the figure. Further, each of the electric valves (EV-1 to EV-6) is adjusted to a predetermined opening. Furthermore, the pressurized solenoid valve (SV-P1) of the first tank (T1)
Then, the pressure reducing solenoid valve (SV-V2) of the second tank (T2) is opened. On the other hand, the pressurized solenoid valve (SV-P2) of the second tank (T2)
The pressure reducing solenoid valve (SV-V1) of the tank (T1) is closed.

In this state, in the drive source circuit (60),
As shown by the solid arrows in FIG. 12, a part of the high-temperature and high-pressure gas refrigerant discharged from the compressor (61) is supplied to the radiator (42A) of the circulation heater (42) by the refrigerant of the driving force generation circuit (40). Give heat to condense. The other gas refrigerant condenses by performing heat exchange with the outside air in the air condenser (34). These condensed refrigerants are merged once, then decompressed by the electric expansion valves (EV-5, EV-6), and then cooled by the heat absorbing part (44A) of the cooler (44) and the circulation cooler.
In the heat absorbing section (43A) of (43), the refrigerant in the driving force generation circuit (40) takes heat from the refrigerant and evaporates. Thereafter, the evaporated refrigerant is merged and sucked into the compressor (61). Such a circulation operation is repeated.

Due to the transfer of heat in the circulation heater (42) and the circulation cooler (43), a high pressure is generated in the heat absorbing portion (42B) of the circulation heater (42) as the refrigerant evaporates. A low pressure is generated in the heat radiating portion (43B) of the circulation cooler (43) as the refrigerant condenses. Therefore, in the driving force generating circuit (40), the internal pressure of the first tank (T1) becomes high (pressurizing operation),
Conversely, the internal pressure of the second tank (T2) becomes low (pressure reduction operation). Thereby, as shown by the dashed arrow in FIG.
The liquid refrigerant pushed out from the first tank (T1) is a four-way switching valve
(41) After passing through the liquid side connection pipe (LL), the electric expansion valve (EV-2, E
After passing through V-2), heat is exchanged with the indoor air in the indoor heat exchangers (20, 20), and the indoor air is evaporated to cool the indoor air. After that, this refrigerant passes through the gas side connection pipe (LG) and exchanges heat with the cold water on the primary side (cold water from the district cooling and heating system) in the intermediate heat exchanger (13), and a part of the refrigerant condenses. The gas-liquid two-phase state is reached, and the liquid side communication pipe (LL) and the four-way switching valve (41)
And reaches the radiator (44B) of the cooler (44). Where 2
The secondary refrigerant exchanges heat with the refrigerant in the drive source circuit (60), and the gas phase is liquefied and collected in the second tank (T2). Also, a part of the liquid refrigerant pushed out from the first tank (T1) is supplied to the liquid recovery pipe (48).
Is supplied to the circulation heater (42) to be used as a refrigerant for pressurization. Further, the liquid refrigerant condensed in the circulation cooler (43) is recovered in the second tank (T2) by the liquid supply pipe (50).

After performing such an operation for a predetermined time, the solenoid valve of the driving force generating circuit (40) is switched. That is, the pressurizing solenoid valve (SV-P1) of the first tank (T1) and the depressurizing solenoid valve (SV-V2) of the second tank (T2) are closed. On the other hand, the pressurized solenoid valve (SV-P2) of the second tank (T2) and the depressurized solenoid valve (SV-V1) of the first tank (T1)
Open the pressurized solenoid valve (SV-P3).

As a result, the internal pressure of the first tank (T1) becomes low, and conversely, the internal pressure of the second tank (T2) becomes high. Therefore, the liquid refrigerant extruded from the second tank (T2) circulates in the same manner as described above, and enters a refrigerant circulation state in which the liquid refrigerant is collected in the first tank (T1).

By repeating the switching operation of each solenoid valve as described above, the refrigerant is circulated in the driving force generation circuit (40), and the room is continuously cooled.

-Heating Operation- On the other hand, during the indoor heating operation, the four-way switching valve (41) is switched to the broken line side in the figure. Other states of the electric valves are substantially the same as those in the cooling operation described above. Further, hot water is supplied from the district cooling / heating system to the primary heat transfer tube (13A) of the intermediate heat exchanger (13) (this hot water / cold water switching mechanism is not shown).

The transfer of heat in the circulating heater (42) and the circulating cooler (43) as described above allows the one tank (T1)
High pressure inside, low pressure inside the other tank (T2),
As shown by a dashed line arrow in FIG. 12, one tank (T
After the liquid refrigerant extruded from 1) passes through the four-way switching valve (41) and the liquid-side communication pipe (LL), the secondary-side heat transfer tube (13B) of the intermediate heat exchanger (13) passes through the primary side. Heat exchange with hot water to evaporate. Then, this gas refrigerant is connected to the gas side connection pipe (LG)
After that, heat is exchanged with the indoor air in the indoor heat exchangers (20, 20) of the indoor units, condensed, and the indoor air is heated. After that, the refrigerant is recovered to the other tank (T2) via the liquid side communication pipe (LL), the four-way switching valve (41), and the cooler (44). Subsequent operations (switching operation of the tank pressurizing solenoid valve and the tank depressurizing solenoid valve, etc.) are the same as those in the above-described cooling operation, and will not be described.

As described above, according to the present embodiment, the heat exchange between the refrigerant circulating in the drive source circuit (60) and the refrigerant in the drive power generation circuit (40) causes the drive power generation circuit ( The refrigerant is extruded and recovered from the tanks (T1, T2) by heating and cooling of the refrigerant in (40), thereby obtaining a driving force for circulating the refrigerant in the secondary refrigerant circuit (B).
For this reason, it is possible to perform the refrigerant circulation operation with higher efficiency and higher reliability as compared with the one using the mechanical pump, while securing the same effect as the first embodiment described above. Further, in this embodiment, the drive source circuit (60) also has the function of the auxiliary heat source circuit (30) of each of the above-described embodiments. It is possible to liquefy the secondary refrigerant in the state.

[0108]

[Modification of Auxiliary Heat Source Circuit] Next, another embodiment of the drive source circuit (60) will be described as a modification of the third embodiment.

(Modification 1) A drive source circuit (60) of Modification 1 shown in FIG. 13 is configured such that the condenser (34) exchanges heat with the cooling water of the district cooling / heating system to condense the refrigerant. It has become. That is, the condenser (34) is configured to be capable of exchanging heat with the cooling pipe (A3) of the district heating / cooling system. Other configurations are the same as those of the above-described embodiment.

According to this configuration, since heat is exchanged with the comparatively low-temperature cooling water in the condenser (34), the condensing temperature of the auxiliary refrigerant can be set low, and the COP can be improved. is there.

(Modification 2) In a drive source circuit (60) of Modification 2 shown in FIG. 14, the condenser (34) is a liquid-side communication pipe (LL) of the secondary-side refrigerant circuit (B). Adjacent to the pipe between the four-way switching valve (41) and the indoor unit, it is configured to be able to exchange heat with the secondary refrigerant. Also in this case, the condensation temperature in the condenser (34) can be set lower than that of the air-cooled type described above, and the COP can be improved.

(Modification 3) Modification 3 is an improvement of the circuit of Modification 2 described above. That is, in the circuit of the second modification, the secondary refrigerant that is pushed out of the tank (T1) and flows toward the indoor unit is supplied to the condenser (3) of the drive source circuit (60).
There is a possibility that it will be heated by 4) and a part of it will be gasified to lower the indoor cooling efficiency. In order to solve this problem, in this example, as shown in FIG. 15, the liquid-side communication pipe (LL) is provided with a gas-liquid separator (71),
The gas refrigerant of the secondary refrigerant recovered in (71) is
The gas is recovered to the gas side connection pipe (LG) by (72). This constitutes the collecting means (70) according to the present invention. That is, the secondary-side refrigerant heated and gasified by the condenser (34) is caused to flow by bypassing the indoor unit, thereby maintaining high indoor cooling efficiency.

(Modification 4) In Modification 4, a driving force generating circuit is provided with a sub tank in addition to the first and second tanks. In the present modification, only differences from the third embodiment will be described.

As shown in FIG. 16, the gas supply pipe (45) and the gas recovery pipe (46) each have three branch pipes (45a, 45b, 45c),
(46a, 46b, 46c), two of which are communicated with the upper ends of the first and second tanks (T1, T2) as described above. The remaining one (45c, 46c) communicates with the upper end of the sub tank (ST). The tank pressurizing solenoid valve (SV-P3) is connected to the branch pipe (45c) of the gas supply pipe (45) communicating with the upper end of the sub tank (ST), and the branch pipe (46c) of the gas recovery pipe (46). Is provided with a tank pressure reducing solenoid valve (SV-V3). Further, a refrigerant recovery pipe (80) is connected to a lower end of the sub tank (ST). One end of the refrigerant recovery pipe (80) is connected to the liquid refrigerant extrusion pipe (47). The refrigerant recovery pipe (80) is provided with a check valve (CV) that allows only the flow of the refrigerant from the liquid refrigerant push-out pipe (47) to the sub tank (ST).

The upstream end of the liquid recovery pipe (48) extending from the lower end of the heat absorbing portion (42B) of the circulation heater (42) is connected to the refrigerant recovery pipe (48).
Connected to (80). This liquid recovery pipe (48) has a sub tank
A check valve (CV) that allows only the flow of the refrigerant from (ST) to the heat absorbing portion (42B) of the circulation heater (42) is provided.

Further, the driving force generating circuit (40) of this embodiment is provided with a heat radiating circuit (81). The heat dissipation circuit (81) has one end connected to the liquid refrigerant push-out pipe (47) and the other end connected to the gas side communication pipe (LG). The heat radiation circuit (81) is provided with a heat absorbing portion (82B) of a heat radiation heat exchanger (82) for exchanging heat with a refrigerant of a drive source circuit (60) described later.

Next, the drive source circuit (60) in this embodiment will be described. The discharge side of the compressor (61) passes through the heat radiating portion (42A) of the circulation heater (42) and the heat radiating portion (82A) of the heat radiating heat exchanger (82).
Connected to The downstream side of the heat radiating portion (82A) is branched, one of which branches to the heat absorbing portion (43A) of the circulation cooler (43) via the electric expansion valve (EV-5), and the other of which is also the electric expansion valve (EV-6). ) Are connected to the heat absorbing portion (44A) of the cooler (44). Heat absorption part (43A) of circulation cooler (43) and heat absorption part of cooler (44)
The outlet side of (44A) merges and is connected to the suction side of the compressor (61).

In the refrigerant circulation operation in this embodiment, the open / close state of the solenoid valves (SV-P3, SV-V3) of the branch pipes (45c, 46c) connected to the upper end of the sub tank (ST) is alternately switched. . That is, when the tank pressure reducing solenoid valve (SV-P3) is open and the tank pressurizing solenoid valve (SV-P3) is closed, a low pressure acts on the sub tank (ST). As a result, a part of the refrigerant extruded from the tank (T1) on the side where the high pressure acts to the liquid refrigerant extrusion pipe (47) passes through the refrigerant recovery pipe (80) to the sub tank.
(ST) (see the arrow indicated by the solid line in FIG. 16). Thereafter, when the tank pressure reducing electromagnetic valve (SV-V3) is closed and the tank pressurizing electromagnetic valve (SV-P3) is open, high pressure acts on the sub tank (ST). With this, the sub tank (ST)
The internal liquid refrigerant is extruded into the liquid recovery pipe (48) and is supplied to the heat absorbing portion (42B) of the circulation heater (42), and is used as a refrigerant for generating high pressure (see an arrow indicated by a broken line in FIG. 16). ). As described above, since the liquid refrigerant is supplied to the heat absorbing portion (42B) of the circulation heater (42) by the sub tank (ST), a high pressure for pushing the liquid refrigerant from the tank (T1) to the secondary refrigerant circuit (B) is provided. Is favorably obtained.

A part of the liquid refrigerant extruded from the tank (T1) flows through the heat radiating circuit (81) and flows into the heat absorbing portion (82B) of the heat radiating heat exchanger (82). Here, the refrigerant exchanges heat with the refrigerant in the drive source circuit (60) to evaporate. The evaporated gas refrigerant is supplied from the heat radiation circuit (81) to the gas side communication pipe (LG). That is, the excess heat of the refrigerant in the drive source circuit (60) is radiated to the secondary refrigerant in the heat radiation heat exchanger (82).

The other refrigerant circulating operations are the same as those in the third embodiment described above, and the description is omitted here.

[0121]

Embodiment 4 Hereinafter, Embodiment 4 of the present invention will be described with reference to the drawings. In the fourth embodiment, similarly to the above-described third embodiment, the refrigerant is heated and cooled to obtain the circulation driving force of the secondary refrigerant in the secondary refrigerant circuit (B). In particular, this embodiment is an intermediate heat exchanger (13) during the heating operation.
The secondary side refrigerant in a gas-liquid two-phase state is caused to flow out of the apparatus. Therefore, in the present embodiment, only differences from the third embodiment will be described.

-Description of Refrigerant Circuit- As shown in FIG. 17, the condenser (34) of the drive source circuit (60)
Heat exchange is possible with the gas side communication pipe (LG) of the secondary refrigerant circuit (B).

Therefore, during the heating operation in this embodiment,
Refrigerant that is condensed in the condenser (34) of the drive source circuit (60) with the secondary refrigerant derived in a gas-liquid two-phase state from the outlet side of the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) Heat exchange between As a result, the liquid phase of the secondary refrigerant in the two-phase state is gasified, and all of the secondary refrigerant becomes a gas phase and is introduced into the indoor heat exchanger (20, 20). Will be done.

The other structure is the same as that of the third embodiment.

[0125]

[Modification of Auxiliary Heat Source Circuit] Next, a modification of the above-described fourth embodiment will be described.

(Modification 1) The drive source circuit (60) of Modification 1 shown in FIG. 18 is provided with an air-cooled evaporator (32) instead of the cooler (44). That is, the configuration is such that surplus heat of the refrigerant circulating in the drive source circuit (60) is released to the outside air.

(Modification 2) The drive source circuit (60) of Modification 2 shown in FIG. 19 has a configuration in which heat exchange is performed between the refrigerant of the drive source circuit (60) and the cooling water of the district cooling / heating system. It was done. That is, the evaporator (32) of the drive source circuit (60) is placed adjacent to the hot water pipe (A4) of the district heating / cooling system, and the drive source circuit (6
The heat exchange is performed between the refrigerant and the hot water of 0).

[0128]

Embodiment 5 Hereinafter, Embodiment 5 of the present invention will be described with reference to the drawings. In the fifth embodiment, a gas refrigerant among gas-liquid two-phase secondary refrigerants flowing out of a secondary heat transfer tube (13B) of an intermediate heat exchanger (13) is supplied to an air conditioner performing a cooling operation. By recovering, the gas refrigerant is prevented from flowing into the pump (21). That is, as shown in FIG. 20, the intermediate heat exchanger (13) in the secondary refrigerant circuit (B)
A gas-liquid separator (76) is provided at the outlet side of the secondary heat transfer tube (13B), and the gas-phase secondary refrigerant separated by the gas-liquid separator (76) is pumped by a bypass pipe (77). It is configured to bypass to the discharge side of 21). An ejector (78) is provided at the downstream end of the bypass pipe (77) so that the bypass operation of the gas refrigerant is smoothly performed. This constitutes the bypass means (75) according to the present invention.

According to this configuration, it is possible to prevent the gas refrigerant from flowing into the pump (21), and it is possible to ensure the reliability of the operation of the pump (21).

(Modification) As a modification of the fifth embodiment described above, FIG. 21 shows a modification in which the downstream end of the bypass pipe (77) is connected to the gas-side communication pipe (LG) of the secondary refrigerant circuit (B). Connected. This also ensures the reliability of the operation of the pump (21), and also prevents the gas refrigerant from flowing into the indoor heat exchangers (20, 20), thus ensuring sufficient indoor cooling capacity. it can.

[0131]

Embodiment 6 Hereinafter, Embodiment 6 of the present invention will be described with reference to the drawings. In the sixth embodiment, the liquid refrigerant among the gas-liquid two-phase secondary refrigerant flowing out of the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) is supplied to the air conditioner performing the heating operation. The liquid refrigerant is prevented from flowing into the indoor heat exchanger (20, 20) by being recovered. That is, FIG.
As shown in the figure, a gas-liquid separator (76) is provided on the outlet side of the secondary heat transfer tube (13B) of the intermediate heat exchanger (13) in the secondary refrigerant circuit (B), and the gas-liquid separator ( The secondary refrigerant in the liquid phase separated in (76) is bypassed to the discharge side of the pump (21) by the bypass pipe (77).

According to this configuration, the indoor heat exchanger (20, 20)
The liquid refrigerant can be prevented from flowing into the room, and the indoor cooling capacity can be sufficiently ensured.

The inside heating capacity can be sufficiently ensured.

(Modification) As a modification of the sixth embodiment, the downstream end of the bypass pipe (77) shown in FIG. 23 is connected to the suction side of the pump (21). This can also prevent the liquid refrigerant from flowing into the indoor heat exchangers (20, 20), and also ensure a sufficient indoor heating capacity.

In each of the above-described embodiments, the primary side employs an absorption refrigeration cycle or a district cooling / heating system. However, the present invention is not limited to this. May be adopted. Similarly, as the auxiliary heat source for cooling or heating the refrigerant in the secondary refrigerant circuit, one that performs a vapor compression refrigeration cycle is employed, but one that performs an absorption refrigeration cycle or a district cooling and heating system is used. It is also possible.

Although the case where the refrigeration apparatus according to the present invention is applied to an air conditioner has been described, the invention can also be applied to other refrigeration equipment.

[0137]

As described above, according to the present invention, the following effects are exhibited. The invention according to claim 1 provides an intermediate heat exchanger (13) for a so-called secondary refrigerant system including a heat source side means (A) and a use side means (B) capable of exchanging heat with each other.
By making the use side fluid flowing out from the gas-liquid two-phase state,
The miniaturization of the intermediate heat exchanger (13) was realized. In other words, by adopting a configuration in which the amount of heat exchange in the intermediate heat exchanger (13) is relatively small, the size of the intermediate heat exchanger (13) can be reduced. And reduction of manufacturing cost can be achieved.

[0138] The invention according to claims 2 to 4 is an intermediate heat exchanger.
The use-side fluid in the gas-liquid two-phase state flowing out of (13) is cooled or heated so as to be circulated to the use-side means (B) in a single phase of a liquid phase or a gaseous phase. .
Therefore, the use-side heat exchanger (20, 20) is supplied with the use-side fluid suitable for the heat absorbing operation or the heat radiating operation, so that a sufficient refrigeration capacity can be exhibited.

The invention according to claims 5 to 9 is characterized in that an auxiliary heat source means (3
(0) is embodied. On the other hand, claim 10
According to a thirteenth aspect, the configuration of the auxiliary heat source means (30) is embodied in the refrigeration apparatus according to the fourth aspect. According to the invention as set forth in claims 5 to 9, the two-phase state flowing out of the intermediate heat exchanger (13) to the liquid line (LL) by the auxiliary refrigerant evaporated in the evaporator (32) of the auxiliary heat source means (30). Since the use side fluid is cooled and this use side fluid liquefies,
The heat exchange efficiency of the use side heat exchangers (20, 20) performing the heat absorbing operation can be obtained well. Similarly, according to the tenth to thirteenth aspects, the auxiliary refrigerant condensed in the condenser (34) of the auxiliary heat source means (30) flows out of the intermediate heat exchanger (13) to the gas line (LG) by the auxiliary refrigerant. The use-side fluid in the phase state is heated and the use-side fluid is gasified, so that the use-side heat exchanger (2
0,20) is obtained.

The invention according to claim 14 is an auxiliary heat source means.
The use side fluid gasified by heat exchange with the condenser (34) of (30) is collected in the gas line (LG) of the use side means (B). Therefore, the gas-phase use-side fluid is transferred to the use-side heat exchanger (20,
The heat exchanger (20, 20) is prevented from flowing into the heat exchanger (20).
Endothermic operation can be performed satisfactorily.

According to the present invention, the gas phase and the liquid phase of the use side fluid flowing out of the intermediate heat exchanger (13) are separated and one of them is bypassed. That is,
If the heat-side heat exchangers (20, 20) perform an endothermic operation, the gas phase of the usage-side fluid flowing out of the intermediate heat exchanger (13) is pumped.
It is bypassed to the discharge side of (21) or to the gas line (LG) of the use side means (B). On the other hand, the heat-side heat exchanger
If (20, 20) performs an endothermic operation, the intermediate heat exchanger (13)
The liquid phase of the use side fluid flowing out of the pump is bypassed to the discharge side and the suction side of the pump (21). For this reason, the side heat exchanger
When (20, 20) performs endothermic operation, the mechanical pump
It is possible to prevent the gas-phase use-side fluid from flowing into the suction side of (21), to ensure the reliability of the pump (21), and to perform the heat dissipation operation of the heat-side heat exchangers (20, 20). In this case, it is possible to prevent the liquid-side use-side fluid from flowing into the use-side heat exchangers (20, 20), and it is possible to satisfactorily perform the heat radiation operation of the use-side heat exchangers (20, 20).

According to the present invention, the circulation driving force of the use side fluid is obtained by utilizing the pressure change accompanying the heating and cooling of the use side fluid. For this reason, a circulating driving force can be obtained without using mechanical means, so that the number of failure-causing factors can be reduced and the reliability of the device can be improved. In particular, in the inventions according to the twentieth and twenty-first aspects, since the circulating driving force is obtained by using both the pressurized and depressurized pressure, the circulating driving force of the use-side fluid in the use-side means (B) is reliably obtained. be able to. Further, in the invention according to claim 22, the means for obtaining the driving force for circulating the use-side fluid in the use-side means (B) is a single-phase use-side refrigerant flowing out of the intermediate heat exchanger (13). Since it is also used as a means for changing the phase, the configuration of the entire apparatus can be simplified. Further, in the invention according to claim 23, since a pair of tank means is provided, the liquid-side use-side fluid is pushed out from one tank means, and the liquid-phase use-side fluid is recovered to the other tank means. The circulating operation of the use side fluid can be performed continuously, and the refrigeration capacity can be stably exhibited.

In the twenty-fourth aspect, the heat source side means
By performing (A) an absorption-type refrigeration cycle, it is not necessary to use a refrigerant such as chlorofluorocarbon, so that a heat source suitable for global environmental problems and the like can be realized.

In the twenty-fifth aspect, the heat source side means
By performing (A) a vapor compression refrigeration cycle, heat can be stably exchanged with the use-side means (B), and the reliability of the apparatus can be ensured.

According to the twenty-sixth aspect, the heat source side means
By using the heat of the district heating / cooling system for (A), a relatively large amount of heat can be easily secured, and the refrigeration capacity can be easily expanded.

[0146] In the invention according to claim 27, the use side fluid is a non-azeotropic mixed refrigerant. In this type of refrigerant, since a temperature gradient occurs due to the heat exchange operation, in the conventional configuration, the temperature difference between the fluids has become extremely small, especially near the outlet of the intermediate heat exchanger. In this way, the use-side refrigerant flows out of the intermediate heat exchanger in a gas-liquid two-phase state,
Even when this type of refrigerant is used, high heat exchange efficiency can be obtained.

[0147] The invention according to claim 28 is the use side heat exchanger.
(20, 20) was an indoor heat exchanger arranged in the air-conditioned room.
That is, the refrigeration apparatus according to the present invention is applied to an air conditioner. For this reason, an apparatus to which the refrigeration apparatus according to the present invention is applied is embodied.

[Brief description of the drawings]

FIG. 1 is a piping diagram of an air conditioner according to a first embodiment.

FIG. 2 is a diagram showing a change state of a refrigerant temperature in an intermediate heat exchanger.

FIG. 3 is a piping system diagram in a first modified example.

FIG. 4 is a piping system diagram in a second modified example.

FIG. 5 is a piping system diagram in a third modified example.

FIG. 6 is a piping system diagram in a fourth modified example.

FIG. 7 is a piping system diagram of the air-conditioning apparatus according to Embodiment 2.

FIG. 8 is a piping system diagram in a first modified example.

FIG. 9 is a piping system diagram in a second modified example.

FIG. 10 is a piping system diagram in a third modified example.

FIG. 11 is a piping diagram of an air conditioner according to Embodiment 3.

FIG. 12 is a diagram for explaining a refrigerant circulation operation.

FIG. 13 is a piping system diagram in a first modified example.

FIG. 14 is a piping system diagram in a second modified example.

FIG. 15 is a piping system diagram in a third modified example.

FIG. 16 is a piping system diagram in a fourth modified example.

FIG. 17 is a piping diagram of the air-conditioning apparatus according to Embodiment 4.

FIG. 18 is a piping system diagram in a first modified example.

FIG. 19 is a piping system diagram in a second modified example.

FIG. 20 is a piping diagram of the air-conditioning apparatus according to Embodiment 5.

FIG. 21 is a piping system diagram in a modified example.

FIG. 22 is a piping diagram of an air-conditioning apparatus according to Embodiment 6.

FIG. 23 is a piping system diagram in a modified example.

[Explanation of symbols]

 (13) Intermediate heat exchanger (20) Indoor heat exchanger (use side heat exchanger) (21) Pump (30) Auxiliary heat source circuit (auxiliary heat source means) (32) Evaporator (33) Compressor (34) Condenser (35) Refrigerant piping (40) Driving force generating circuit (42) Circulating heater (pressurizing means) (43) Circulating cooler (Depressurizing means) (60) Driving source circuit (Driving source means) (70) Recovery means (75) Bypass means (A) Primary refrigerant circuit (heat source means) (B) Secondary refrigerant circuit (use side means) (LL) Liquid side communication pipe (liquid line) (LG) Gas side communication Piping (gas line) (A3) Cold water piping (A4) Hot water piping (EV-3) Electric expansion valve (expansion mechanism) (T1, T2) Tank

Claims (28)

[Claims] A heat source side means (A) through which a heat source side fluid flows and a use side means (B) through which a use side fluid circulates, wherein each means (A,
By exchanging the fluids of (B) with each other in the intermediate heat exchanger (13), the use-side fluid exchanges heat between the two means (A, B) while changing the phase between the gas phase and the liquid phase. In the refrigeration apparatus, the refrigeration apparatus is characterized in that a utilization side fluid in a gas-liquid two-phase state flows out of an exit side of the intermediate heat exchanger (13) in the utilization side means (B). . 2. The refrigeration system according to claim 1, wherein a phase change similar to that in the intermediate heat exchanger (13) is provided at an outlet side of the intermediate heat exchanger (13) in the use-side means (B). Gas-liquid 2 that was discharged at the outlet side and flowed out of the intermediate heat exchanger (13)
A refrigeration system comprising an auxiliary heat source means (30) for converting a utilization side fluid in a phase state into a single phase of a gas phase or a liquid phase. 3. The refrigeration system according to claim 2, wherein the use side means (B) includes an intermediate heat exchanger (13) and a use side heat exchanger (2).
0,20) is a closed circuit connected by a liquid line (LL) and a gas line (LG), and the use side heat exchanger (20,20) is a liquid line from the intermediate heat exchanger (13). The use-side fluid that has flowed out into the (LL) is introduced, and the heat-absorbing operation is performed by evaporating the use-side fluid. The auxiliary heat source means (30) includes a gas-liquid 2 that flows out of the intermediate heat exchanger (13). A refrigeration apparatus characterized in that a use-side fluid in a phase state is cooled to liquefy a use-side fluid in a gas phase. 4. The refrigeration system according to claim 2, wherein the use side means (B) includes an intermediate heat exchanger (13) and a use side heat exchanger (2).
0,20) is a closed circuit connected by a liquid line (LL) and a gas line (LG), and the use side heat exchanger (20,20) is a gas line from the intermediate heat exchanger (13). The use-side fluid that has flowed out to the (LG) is introduced, and a heat-dissipating operation is performed by condensing the use-side fluid. The auxiliary heat source means (30) includes a gas-liquid 2 that flows out of the intermediate heat exchanger (13). A refrigeration apparatus characterized in that a use state fluid in a phase state is heated to gasify a use state fluid in a liquid phase. 5. The refrigeration apparatus according to claim 3, wherein the auxiliary heat source means (30) is a compressor (33), a condenser (34), an expansion mechanism (EV-3), and an evaporator (32) is a refrigerant pipe. The refrigeration circuit performs a vapor compression refrigeration cycle by circulating auxiliary refrigerant in order by (35), and the auxiliary refrigerant evaporating in the evaporator (32) flows from the intermediate heat exchanger (13) to the liquid line. A refrigeration system characterized in that the refrigeration system is configured to cool the use side fluid flowing out to the (LL). 6. The refrigerating apparatus according to claim 5, wherein the condenser (34) exchanges heat with outside air. 7. The refrigeration apparatus according to claim 5, further comprising a chilled water pipe (A3) through which cooling water flows, wherein the condenser (34) exchanges heat with the cooling water flowing through the chilled water pipe (A3). A refrigeration apparatus characterized by performing: 8. The refrigeration apparatus according to claim 5, wherein the condenser (34) exchanges heat with the use side fluid cooled by the auxiliary refrigerant of the evaporator (32). And refrigeration equipment. 9. The refrigeration apparatus according to claim 5, wherein the condenser (34) evaporates in the use side heat exchanger (20, 20),
A refrigeration system for performing heat exchange with a utilization side fluid flowing through a gas line (LG) toward an intermediate heat exchanger (13). 10. The refrigeration system according to claim 4, wherein the auxiliary heat source means (30) is a compressor (33), a condenser (34), an expansion mechanism (EV-3), and an evaporator (32) is a refrigerant pipe. (35) consists of a refrigeration circuit that is connected in order so that the auxiliary refrigerant can be circulated, and performs a vapor compression refrigeration cycle.The auxiliary refrigerant condensed in the condenser (34) passes from the intermediate heat exchanger (13) to the gas line. A refrigerating apparatus characterized in that the use side fluid flowing out to (LG) is heated. 11. The refrigerating apparatus according to claim 10, wherein the evaporator (32) exchanges heat with outside air. 12. The refrigeration apparatus according to claim 10, further comprising a hot water pipe (A4) through which hot water flows, and wherein the evaporator (32) exchanges heat with hot water flowing through the hot water pipe (A4). A refrigeration apparatus characterized in that: 13. The refrigerating apparatus according to claim 10, wherein the evaporator (32) exchanges heat with the use side fluid condensed in the use side heat exchangers (20, 20). Characterized refrigeration equipment. 14. The refrigeration system according to claim 8, wherein the use side fluid gasified by performing heat exchange with the auxiliary refrigerant of the condenser (34) is recovered to the gas line (LG) of the use side means (B). A refrigeration apparatus comprising a collecting means (70). 15. The refrigeration system according to claim 1, wherein the use-side means (B) comprises an intermediate heat exchanger (13) and a use-side heat exchanger (2).
0,20) is a closed circuit connected by a liquid line (LL) and a gas line (LG), and the use side heat exchanger (20,20) is a liquid line from the intermediate heat exchanger (13). The use side fluid flowing out to the (LL) is introduced, and a heat absorbing operation is performed by evaporating the use side fluid, and the liquid line (LL) is provided with a machine for obtaining a circulating driving force of the use side fluid. A pump (21) is provided, which flows out of the intermediate heat exchanger (13) to the liquid line (LL) and the pump (2).
A refrigerating apparatus comprising a bypass means (75) for bypassing a gas-phase fluid of a utilization-side fluid in a gas-liquid two-phase state flowing toward 1) to a discharge side of a pump (21). 16. The refrigeration system according to claim 1, wherein the use side means (B) includes an intermediate heat exchanger (13) and a use side heat exchanger (2).
0,20) is a closed circuit connected by a liquid line (LL) and a gas line (LG), and the use side heat exchanger (20,20) is a liquid line from the intermediate heat exchanger (13). The use side fluid flowing out to the (LL) is introduced, and a heat absorbing operation is performed by evaporating the use side fluid, and the liquid line (LL) is provided with a machine for obtaining a circulating driving force of the use side fluid. A pump (21) is provided, which flows out of the intermediate heat exchanger (13) to the liquid line (LL) and the pump (2).
A bypass means (75) for bypassing a gaseous phase fluid of the gas-liquid two-phase use side fluid flowing toward 1) to the gas line (LG) of the use side means (B) is provided. And refrigeration equipment. 17. The refrigeration system according to claim 1, wherein the use-side means (B) comprises an intermediate heat exchanger (13) and a use-side heat exchanger (2).
0,20) is a closed circuit connected by a liquid line (LL) and a gas line (LG), and the use side heat exchanger (20,20) is a gas line from the intermediate heat exchanger (13). The use-side fluid that has flowed out into the (LG) is introduced, and a heat-dissipating operation is performed by condensing the use-side fluid. A gas-liquid two-phase use side which is provided with a pump (21) and flows out from the intermediate heat exchanger (13) to the gas line (LG) and flows toward the use side heat exchanger (20, 20) A refrigeration system comprising a bypass means (75) for bypassing a liquid phase fluid of a fluid to a discharge side of a pump (21). 18. The refrigeration system according to claim 1, wherein the use-side means (B) comprises an intermediate heat exchanger (13) and a use-side heat exchanger (2).
0,20) is a closed circuit connected by a liquid line (LL) and a gas line (LG), and the use side heat exchanger (20,20) is a gas line from the intermediate heat exchanger (13). The use-side fluid that has flowed out to the (LG) is introduced, and a heat-dissipating operation is performed by condensing the use-side fluid.The liquid line (LL) is provided with a machine for obtaining a circulating drive force of the use-side fluid. A gas-liquid two-phase use side which is provided with a pump (21) and flows out from the intermediate heat exchanger (13) to the gas line (LG) and flows toward the use side heat exchanger (20, 20) A refrigeration system comprising a bypass means (75) for bypassing a liquid phase fluid of a fluid to a suction side of a pump (21). 19. The refrigeration apparatus according to claim 1, wherein the use-side means (B) includes transport means (40, 60) for obtaining a circulating drive force of the use-side fluid. The conveying means (40, 60) comprises a pressurizing means (42) for generating a high pressure by heating the liquid-side use-side fluid and a low pressure by cooling the gas-phase use-side fluid. At least one of the pressure reducing means (43) for causing
(2) A refrigeration system that generates a driving force for circulating the use-side fluid by a difference between the pressure generated by (43) and the pressure in the use-side means (B). 20. The refrigeration apparatus according to claim 1, wherein the use-side means (B) includes transport means (40, 60) for obtaining a driving force for circulating the use-side fluid. The transfer means (40, 60) includes a driving force generation circuit (40) capable of storing a liquid-side use-side fluid, and the driving force generation circuit (40) includes a driving source means (60) Heat exchange between the driving force generation circuit (40) and the liquid phase usage side of the driving force generation circuit (40) so as to push out the liquid phase usage side fluid of the driving force generation circuit (40) to the usage side means (B). A pressurizing means (42) for generating a high pressure by heating the fluid, and a driving force generation circuit (40) to draw the liquid use side fluid of the liquid phase of the use side means (B) to the driving force generation circuit (40). 40. A refrigerating apparatus comprising: a pressure reducing means (43) for generating a low pressure by cooling a gas-phase use-side fluid of (40). 21. The refrigeration apparatus according to claim 20, wherein the driving force generation circuit (40) is provided with tank means (T1, T2) capable of storing a liquid-phase use-side fluid, and heating the use-side fluid. The high pressure generated by the pressurizing means (42) acts on the tank means (T1, T2) to cause the tank means (T1, T2
2) The low pressure generated by the pressure reducing means (43) due to the pressurizing operation for pushing out the liquid-side use-side fluid from the liquid phase and the cooling of the use-side fluid is applied to the tank means (T1, T2) to cause the tank means (T1, T2) ) A refrigeration apparatus characterized in that the use-side fluid is circulated to the use-side means (B) by a pressure-reducing operation for recovering the liquid-side use-side fluid. 22. The refrigeration apparatus according to claim 20, wherein the drive source means (60) comprises a refrigeration circuit capable of circulating the refrigerant, and the refrigerant in the refrigeration circuit and the air flowing out of the intermediate heat exchanger (13). A refrigerating apparatus characterized in that a heat-exchange with a use-side fluid in a liquid two-phase state brings the use-side fluid into a gaseous phase or a liquid phase single-phase state. 23. The refrigeration apparatus according to claim 21, wherein the tank means comprises first and second tank means (T1, T2) connected in parallel with each other, and applies a high pressure to the first tank means (T1). A first pressure action operation for applying a low pressure to the second tank means (T2), and a second pressure action operation for applying a high pressure to the second tank means (T2) while applying a low pressure to the first tank means (T1). Switch alternately,
At the time of the first pressure action operation, the liquid-side use-side fluid is supplied from the first tank means (T1) to the use-side means (B), and the liquid is supplied from the use-side means (B) to the second tank means (T2). On the other hand, during the second pressure action operation, the liquid-side use-side fluid is supplied from the second tank means (T2) to the use-side means (B), and the use-side means (B) is recovered. From the first tank means (T
(1) A refrigeration system characterized by circulating a use-side fluid so as to collect a liquid-phase use-side fluid. 24. The refrigeration apparatus according to claim 1, wherein the heat source side means (A) performs an absorption refrigeration cycle. 25. The refrigeration apparatus according to claim 1, wherein the heat source side means (A) performs a vapor compression refrigeration cycle. 26. The refrigeration apparatus according to claim 1, wherein the heat source side means (A) utilizes heat of a district cooling / heating system. 27. The refrigeration apparatus according to claim 1, wherein the use-side fluid is a non-azeotropic mixed refrigerant. 28. One of claims 3 to 14, 19 to 27
The refrigeration apparatus according to any one of the first to third aspects, wherein the use-side heat exchanger (20, 20) is an indoor heat exchanger disposed in an air-conditioned room.