JP2000130877A - Air conditioning equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make equipment small in size and also to lessen power for carriage by using a heating medium such as cold-hot water. SOLUTION: In this equipment, a primary-side circuit 1A for cooling or heating a secondary-side heating medium is formed and a circulation circuit 30 is constructed by connecting sequentially a pump 31 for carrying the secondary-side heating medium and an indoor heat exchanger 32 making the secondary-side heating medium and indoor air exchange heat between them. The indoor heat exchanger 32 is formed to have a constitution wherein the secondary-side heating medium and the indoor air become flows opposite substantially at least so that the temperature efficiency be 50% or above and that an outlet-inlet temperature difference of the secondary-side heating medium be 10 deg.C or above.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner, and more particularly to an air conditioner using a heat medium such as cold and hot water.

[0002]

2. Description of the Related Art Conventionally, as an air conditioner using cold and hot water as a heat medium, there is an ice regenerative air conditioner as disclosed in Japanese Patent Application Laid-Open No. 5-141721. This ice regenerative air conditioner has a heat storage tank for storing ice and hot water, an air conditioning unit with a cold and hot water coil and a fan, and a radiant cooling and heating unit with a cold and hot water channel and a radiant panel. They are connected in order.

[0003] Ice or hot water is stored in the above-mentioned heat storage tank using electric power at midnight. Then, utilizing this heat storage, cold or hot water is supplied to the air conditioning unit to generate conditioned air and supply it indoors. At the same time, the cold or hot water is supplied to the radiant cooling and heating unit to cool and heat the room by radiant heat.

[0004]

As described above, an air conditioner using cold and hot water as a heat medium has the advantage of less environmental problems since it does not directly use a chlorofluorocarbon-based refrigerant.

However, since the above-mentioned heat medium cools or heats the air by a change in sensible heat, there is a problem that the heat transfer capacity is smaller than that of a CFC-based refrigerant utilizing a change in latent heat. As a result, there is a problem that the circulation amount of the heat medium is required to be larger than that of the CFC-based refrigerant, and the pipe diameter of the circulation passage is increased. Further, since the power for transporting the heat medium is increased, there is a problem that the equipment cost and the operating cost are increased as compared with the CFC-based refrigerant.

Therefore, a large-temperature-difference-based air-conditioning system has been proposed in which a means for increasing the number of cold / hot water coils of the air-conditioning unit is used to increase the temperature difference between the inlet and outlet of the cold water. In this air conditioning system, it is possible to reduce the pipe diameter of the circulation passage, etc., but there is a problem that it cannot be downsized as much as an air conditioner using a CFC-based refrigerant.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-described circumstances, and has as its object to further reduce the size by using a heat medium such as cold and hot water and to reduce the transfer power.

[0008]

Means for Solving the Problems-Solution Means- Specifically, as shown in FIG. 1, a first solution means is a heat source means (1A) for cooling or heating a heat medium, and a conveyance means for conveying the heat medium. And a use-side heat exchanger (32) for exchanging heat between the heat medium and air, the heat medium circulates, and air conditioning is performed based on the sensible heat change of the heat medium. It is assumed that the air conditioner has a circulation circuit (30) configured to perform the operation. And the said circulation circuit (30) is comprised in the circuit structure which performs heat conveyance corresponding to the circuit structure of the refrigerant | coolant which performs air conditioning based on a latent heat change.

The second solution is the first solution, wherein the use side heat exchanger (32) has a temperature efficiency of 5%.
It is configured to be 0% or more.

[0010] The third solution is the first or second embodiment.
In the above solution, the use-side heat exchanger (32) is formed so that the heat medium and the air have at least a substantially opposite flow so that the temperature difference between the inlet and the outlet of the heat medium is 10 ° C. or more. It is.

According to a fourth aspect of the present invention, in the first aspect, the heat source means (1A) comprises a refrigerator (20) using a non-azeotropic mixed refrigerant as a working fluid. And
The main heat exchanger (11) is configured to exchange heat between the refrigerant of the refrigerator (20) and the heat medium at least in a substantially countercurrent flow.

According to a fifth aspect of the present invention, in the fourth aspect, the circulation circuit (30) is arranged so that the refrigerant and the heat medium of the main heat exchanger (11) always flow in opposite directions. Switching means (34) for changing the circulating direction of the heat medium in accordance with the circulating direction.

According to a sixth aspect of the present invention, in the fourth aspect, the heat source means (1A) is provided so that the refrigerant and the heat medium of the main heat exchanger (11) always have a countercurrent flow. Switching means (2C) for changing the circulation direction of the refrigerant in accordance with the circulation direction of the medium is provided.

According to a seventh aspect of the present invention, in the fourth aspect, the heat source means (1A) includes a multistage compression cycle refrigerator (20).

An eighth aspect of the present invention is the apparatus according to any one of the first to third aspects, wherein the heat source means (1A) includes a refrigerator (50, 6) having a multi-stage absorption cycle or a multi-stage adsorption cycle.
0).

According to a ninth solution, the heat source means (1A) is an absorption cycle or an adsorption cycle using a high evaporation temperature and a low heat as a driving source. A first refrigerator (50, 60), and a first refrigerator (50, 6) having a lower evaporation temperature than the first refrigerator (50, 60).
0) At least a second refrigerator (50, 60) of an absorption cycle or an adsorption cycle using higher heat as a driving source. And each said refrigerator (50, 60) is arrange | positioned so that heat may be exchanged with a heat medium in order of a high evaporation temperature.

The tenth solving means is the first to third aspects.
In any one of the above solutions, the heat source means (1A) comprises: a first refrigerator (50) of an absorption cycle having a low condensation temperature or an absorption temperature and low heat as a driving source; and the first refrigerator (50). )
Higher condensing or absorbing temperature and first refrigerator (50)
A second refrigerator (50) having an absorption cycle driven by higher heat. And each said refrigerator (50) is arrange | positioned so that heat may be exchanged with a heat medium in order of a low condensing temperature.

The eleventh solving means is the first to third means.
In any one of the above solutions, the heat source means (1A) comprises: a first refrigerator (60) of an adsorption cycle having a low condensation temperature or an adsorption temperature and low heat as a driving source; and the first refrigerator (60). )
Higher condensing or adsorption temperature and first refrigerator (60)
A second refrigerator (60) of an adsorption cycle using higher heat as a driving source. And each said refrigerator (60) is arrange | positioned so that heat exchange with a heat medium may be carried out in order of a low condensing temperature.

According to a twelfth solution, in the ninth solution, the refrigerators (50, 60) are configured in a multistage cycle.

The thirteenth solving means is the eighth to first aspects.
In any one of the first means, the all refrigerators (50, 60) of the heat source means (1A) are configured to use cogeneration waste heat as a heat source.

Further, a fourteenth solving means is the eighth to first aspects.
In any one of the solution means, a part of the refrigerators (50, 60) of the heat source means (1A) is configured to use the waste heat of the cogeneration as a heat source.

The fifteenth solving means is the eighth to the first.
In any one of the first means, the heat source means (1A)
After the refrigerators (50, 60) apply heat to the heat medium, the refrigerators (20) of the vapor compression cycle further apply heat to the heat medium.
It is provided with.

-Operation- According to the above-mentioned specific items, in the first to third solving means, the heat medium is circulated in the circulation circuit (30) by the conveying means (31), and the cooling medium or the heat obtained from the heat source means (1A) is obtained. The heat is transferred to the use-side heat exchanger (32). The heat medium exchanges heat with air to change sensible heat, and cools or heats the air.

At this time, the temperature difference between the inlet and outlet of the heat medium in the use-side heat exchanger (32) increases, and air conditioning is performed with a small amount of heat medium circulated. The pipe diameter and the like can be made the same as when used.

In particular, according to the third solution, the heat medium and the air exchange heat in a substantially opposite flow in the use-side heat exchanger (32), and the temperature difference between the inlet and the outlet of the heat medium is large. Heat exchange with air efficiently.

In a fourth solution, the heat source means (1
The non-azeotropic refrigerant circulates in the refrigerator (20) of A),
In the main heat exchanger (11), the heat medium and the non-azeotropic mixed refrigerant exchange heat in counterflow. As a result, a Lorentz cycle is realized, and the compressor input of the refrigerator (20) is reduced.

In the fifth and sixth solving means, the heat medium and the non-azeotropic mixed refrigerant exchange heat in the main heat exchanger (11) by the switching means (34, 2C) at all times.

In the seventh solution, the non-azeotropic mixed refrigerant is compressed in multiple stages to exchange heat between the heat medium and the non-azeotropic mixed refrigerant, thereby cooling or superheating the heat medium. As a result, the effect of the Lorentz cycle is more exhibited.

In the eighth solution, the heat source means (1
Since A) is a refrigerator (50, 60) of a multi-stage absorption cycle or a multi-stage adsorption cycle, the heat medium exchanges heat with a solvent, a refrigerant, or the like in multiple stages, and cools or superheats the heat medium. As a result,
The heat medium is adjusted to a predetermined temperature efficiently.

In the ninth solution means, the heat source means (1
A) A refrigerator with multiple absorption or adsorption cycles (5
0, 60), the heat medium and the refrigerant exchange heat a plurality of times to cool the heat medium. At this time, since the heat medium exchanges heat with the refrigerant having a high evaporation temperature, the temperature of the heating heat source of the refrigerator (50, 60) having a high evaporation temperature becomes low.

In the tenth solution, since the heat source means (1A) is a plurality of absorption cycle refrigerators (50),
The heat medium and the refrigerant exchange heat a plurality of times to heat the heat medium. At this time, since the heat medium exchanges heat with a solvent having a low absorption temperature or the like, the temperature of the heating heat source of the refrigerator (50) having a high evaporation temperature becomes low.

In the eleventh solution, the heat source means (1A) is a plurality of adsorption cycle refrigerators (60).
The heat medium and the refrigerant exchange heat a plurality of times to heat the heat medium. At this time, the heat medium exchanges heat with the refrigerant having a low condensing temperature, so that the temperature of the heating heat source of the refrigerator (60) having a high evaporation temperature becomes low.

In the twelfth solution, since the refrigerators (50, 60) in the absorption cycle or the adsorption cycle have multiple stages, each of the refrigerators (50, 60) exchanges heat between the heat medium and the refrigerant a plurality of times. Then, the heat medium is cooled or heated.

In the thirteenth or fourteenth solution, the waste heat of the cogeneration is used, so that the energy can be effectively used.

In the fifteenth solution, a vapor compression type refrigerator (20) is provided in addition to the absorption cycle or adsorption cycle refrigerators (50, 60). Cooling or heating is assured.

[0036]

According to the present invention, the circulation circuit (30) has a structure corresponding to the conventional circuit structure of the CFC-based refrigerant, so that the overall shape can be reduced in size.

Further, since the amount of circulation of the heat medium does not increase, the transport power does not increase, and the equipment cost and the operating cost can be reduced.

In particular, since a copper pipe or the like can be used for the pipe (33) of the circulation circuit (30), the installation and the like can be facilitated.

According to the second solution, since the heat medium and the air of the use side heat exchanger (32) are substantially counter-current, the temperature difference between the inlet and the outlet of the heat medium is set to 10 ° C. or more. Since the temperature efficiency can be increased to 50% or more, it is possible to reduce the transfer power without increasing the size of the heat exchanger itself.

According to the fourth solution, a non-azeotropic mixed refrigerant is used as the refrigerant of the heat source means (1A), and the non-azeotropic mixed refrigerant and the heat medium are caused to flow in opposite directions. Thus, the Lorentz cycle is realized, and the compressor input of the refrigerator (20) is reduced.

According to the fifth and sixth solutions,
Since the refrigerant and the heat medium of the main heat exchanger (11) are always in countercurrent flow by the switching means (34, 2C), the heat exchange efficiency can be reliably improved both during cooling and during heating. Can be.

According to the seventh solution, since the refrigerant is compressed in multiple stages, the COP (coefficient of performance) can be improved.

According to the eighth and twelfth solutions,
Since the multi-stage absorption cycle refrigerator (50) is applied to the heat source means (1A), the solution temperature at the outlet of the high pressure absorber (51) (see point 1 in FIG. 13) can be increased.
The concentration of the dilute solution can be reduced, and the concentration difference from the concentrated solution can be increased.

Further, since the refrigerators (50, 60) of the multi-stage absorption cycle and the multi-stage adsorption cycle are applied, the amount of heating heat can be reduced, so that the COP can be improved.

Further, in the case of the refrigerator (50) having a multi-stage absorption cycle, the high-pressure absorber (51) is compared with the single-stage absorption cycle.
Since the solution temperature of the evaporator (56) can be increased, the temperature of the refrigerant in the high-pressure evaporator (56) can be increased, and the temperature difference with the heat medium can be sufficiently ensured.
The shape of itself can be reduced in size.

According to the ninth, tenth, eleventh, and twelfth solutions, the heat medium is exchanged by the plurality of refrigerators (50, 60) in the order of a solution having a small temperature difference. Refrigerators (50, 60) with a low temperature can be used. As a result, the energy efficiency of the entire device can be improved.

Further, according to the thirteenth and thirteenth solutions, the exhaust heat is used for the heat source means (1A), so that the energy can be effectively used.

Further, according to the fifteenth solution, the refrigerator (20) of the vapor compression cycle is added to the refrigerator (50) of the absorption cycle, etc., so that low-temperature cold heat and high-temperature heat can be reduced. It can be generated reliably.

[0049]

Embodiment 1 Hereinafter, Embodiment 1 of the present invention will be described in detail with reference to the drawings.

As shown in FIG. 1, the air conditioner (10)
Is composed of a primary side circuit (1A) and a secondary side circuit (1B), so that the heat of the primary side circuit (1A) is transferred to the secondary side circuit (1B) so that the room is air-conditioned. It is configured.

The primary circuit (1A) is constituted by a refrigerator (20) of a vapor compression cycle and constitutes a heat source means. The primary circuit (1A) includes a compressor (21), a four-way switching valve (22), an outdoor heat exchanger (23), an expansion valve (24), and a primary passage of a main heat exchanger (11). (12) is the primary side pipe in order (25)
And is filled with a non-azeotropic mixed refrigerant, for example, R407C. The primary-side refrigerant is configured so that the circulation direction of the primary-side refrigerant is reversible between the cooling operation and the heating operation.

The secondary circuit (1B) includes a pump (31) as a conveying means and a secondary passage (13) of the main heat exchanger (11).
And a room heat exchanger (32), which is a use side heat exchanger, is connected in order by a secondary pipe (33).
0). The secondary circuit (1B) is configured so that a heat medium such as cold and hot water is filled and the secondary heat medium circulates.

The main heat exchanger (11) in the secondary circuit (1B) is connected to the pump (31) and the indoor heat exchanger (32) via a four-way switching valve (34). . That is, while the main heat exchanger (11) is formed of, for example, a plate heat exchanger, the four-way switching valve (34) is connected to the primary refrigerant of the main heat exchanger (11) and the secondary refrigerant. The switching means for switching the circulation direction of the secondary heat medium is configured so that the side heat medium always has a counterflow in both the cooling operation and the heating operation.

Further, as a feature of the present invention, the secondary side circuit (1B) is configured to perform air conditioning by utilizing a sensible heat change of the secondary side heat medium. It is configured in a circuit structure that carries heat in accordance with the circuit structure of the refrigerant that performs harmony. Specifically, for example, when the conventional apparatus transports cold and hot water using a steel pipe having an inner diameter of 41.6 mm, the secondary circuit (1B) of the present embodiment uses an inner diameter of 26.
A 2 mm copper tube or a 29.0 mm copper tube is used as a secondary pipe (33) to convey the secondary heat medium so that it has the same shape and capacity as the conventional chlorofluorocarbon refrigerant. ing.

Therefore, the indoor heat exchanger (32) is formed in the same shape or the like as a conventional CFC-based refrigerant. That is, as shown in FIG. 2, the indoor heat exchanger (32) heats the secondary heat exchanger so that the temperature efficiency is 50% or more and the temperature difference between the inlet and the outlet of the secondary heat medium is 10 ° C. or more. The medium and the room air are formed so as to have at least a substantially opposite flow.

More specifically, the indoor heat exchanger (32) has a plurality of plate-like fins (41) arranged in parallel at a predetermined interval and penetrates the fins (41). And a plurality of heat transfer members (42) extending in the left-right direction perpendicular to the fins (41). The indoor heat exchanger (32)
2 is configured such that the right side in FIG. 2 into which room air flows is a front surface, and the room air flows from the front surface to the back surface in parallel with the fins (41).

Each of the heat transfer members (42) is composed of two rows, a rear row and a front row, arranged vertically, and the heat transfer members (42) in both rows are arranged in a staggered manner. In each of the heat transfer members (42), a plurality of medium passages (43) through which the secondary-side heat medium flows in the left-right direction that the secondary-side heat medium traverses the flow of room air are arranged in the front-rear direction. (Four in FIG. 2).

The left and right ends of each medium passage (43) are 2
The secondary heat medium is continuous so as to meander right and left from the downstream side to the upstream side with respect to the flow of the room air, that is, the secondary heat medium flows from the rear medium passage (43). It is configured to sequentially flow to the medium passage (43) on the front side and move toward the air upstream while flowing left and right with respect to the air flow.

Further, for example, the heat transfer members (42) of the rear row and the front row are paired to form one path, and for example,
The uppermost heat transfer member (42) in the rear row and the uppermost heat transfer member (42) in the front row constitute one path. The two heat transfer members (42) forming a pair of the rear row and the front row are configured such that the secondary-side heat medium flows in a meandering manner from the most downstream side of the room air to the most upstream side. I have.

Next, basics relating to the above-mentioned configuration of the secondary side circuit (1B) having a predetermined pipe diameter and the configuration of the indoor heat exchanger (32) configured to be in a counterflow, etc. The reason will be described.

In a conventional cold / hot water air conditioner,
Similarly to the present invention, the secondary heat medium of the cold water or hot water generated in the main heat exchanger is transported to the indoor heat exchanger to cool or heat the room. The air conditioner for cold and hot water having a heat transfer amount of 28.7 KW has, for example, a flow velocity in the secondary pipe of 1.0 m / s, a temperature difference between the entrance and exit of the secondary heat medium in the indoor heat exchanger, That is, assuming that the use temperature difference is 5 ° C., 2
Considering the piping pressure loss, it is appropriate to set the secondary piping to 40A steel pipe (inner diameter 41.6 mm), and the piping pressure loss per unit length is 39.4 mmAq / m.

Accordingly, in the conventional air conditioner, as shown in FIG. 3A, the pipe pressure loss decreases as the difference in the use temperature increases. That is, 2
As the temperature difference between the inlet and outlet of the secondary heat medium increases,
The circulation amount of the secondary-side heat medium flowing through the indoor heat exchanger is reduced, the flow velocity in the pipe is reduced, and the pressure loss is reduced.

FIG. 7 shows the relationship between the conventional secondary-side heat medium and room air. For example, cold water 2
While the secondary heat medium flows into the indoor heat exchanger at an inlet temperature Tw1 of 7 ° C. and flows out at an outlet temperature Tw2 of 12 ° C., the indoor air that exchanges heat with the secondary heat medium is supplied to the indoor heat exchanger. 26 ℃
At an inlet temperature Ta1, and blows out at an outlet temperature Ta2 of 14 ° C. Therefore, the temperature efficiency ε of the conventional indoor heat exchanger was 0.26 (26%).

In the present invention, instead of the conventional 40A steel pipe,
The secondary circuit (1B) is constituted by using a copper tube (inner diameter 26.2 mm) having an inner diameter similar to that of the air conditioner (10) using a CFC-based refrigerant, and as shown in FIG. Is maintained at 39.2 mmAq / m which is almost the same as the conventional case. In this case, it is necessary to set the difference between the inlet and outlet temperatures of the secondary heat medium, which is the difference in the use temperature, to 15 ° C. In this case, the flow velocity in the secondary pipe (33) is 0.85 m / s.

On the other hand, if the temperature condition of the indoor air in the indoor heat exchanger (32) is to be maintained in the same manner as in the prior art (inlet temperature Ta1 = 26 ° C., outlet temperature Ta2 = 14 ° C.),
As shown in FIG. 4, the relationship between the secondary heat medium and the indoor air is as follows.
For example, the secondary heat medium, which is cold water, is supplied to the indoor heat exchanger (3
It is necessary to flow into 2) at an inlet temperature Tw1 of 5 ° C. and to flow out at an outlet temperature Tw2 of 20 ° C. In this case, the temperature efficiency ε of the indoor heat exchanger (32) needs to be maintained at 0.71 (71%).

As shown in FIG. 5, the temperature conditions of the indoor air were made the same (inlet temperature Ta1 = 26 ° C., outlet temperature Ta2).
= 14 ° C.), when the secondary-side heat medium, which is cold water, flows into the indoor heat exchanger (32) at an inlet temperature Tw1 of 6 ° C., it needs to flow out at an outlet temperature Tw2 of 21 ° C. In this case, it is necessary to maintain the temperature efficiency ε of the indoor heat exchanger (32) at 0.75 (75%).

Further, as shown in FIG.
When an 8.0 mm copper tube is used, if the pressure loss is maintained at 39.2 mmAq / m, which is almost the same as the conventional one, the temperature difference between the inlet and outlet of the secondary side heat medium, which is the difference in use temperature, is reduced to 12 ° C. There is a need to.

In this case, if it is attempted to maintain the temperature condition of the indoor air in the indoor heat exchanger (32) as in the prior art (inlet temperature Ta1 = 26 ° C., outlet temperature Ta2 = 14 ° C.)
As shown in FIG. 6, for example, the relationship between the secondary heat medium and the indoor air is such that the secondary heat medium, which is cold water, flows into the indoor heat exchanger (32) at an inlet temperature Tw1 of 6 ° C. It is necessary to flow out at an outlet temperature Tw2 of 18 ° C. Then, it is necessary to maintain the temperature efficiency ε of the indoor heat exchanger (32) at 0.60 (60%).

From the above, in order to maintain the temperature relationship between the secondary-side heat medium and the indoor air, the indoor heat exchanger (3
2) The secondary heat medium and the room air are formed so as to have at least a substantially countercurrent flow, and the temperature efficiency is 5%.
The temperature difference between the inlet and the outlet of the secondary heat medium is 0% or more and 10 ° C. or more.

In the main heat exchanger (11), 1
The secondary-side refrigerant and the secondary-side heat medium flow in opposite directions, and the primary-side refrigerant is a non-azeotropic mixed refrigerant. As a result, as shown in FIG. 8, for example, during the cooling operation, the primary-side refrigerant evaporates during the evaporation process (R1 in FIG. 8), while the cold water as the secondary-side heat medium is heated in the counterflow. The temperature is lowered by replacement (W1 in FIG. 8). Therefore, in this case, the average evaporation temperature increases as compared with the case where a single refrigerant is used.

That is, conventionally, a single refrigerant such as R22 is used as the primary refrigerant. In this case, as shown in FIG. 9, for example, during the cooling operation, the primary-side refrigerant has an almost constant evaporation temperature during the evaporation process (R2 in FIG. 9), and the temperature of the cold water as the secondary-side heat medium is changed by heat exchange. (W2 in FIG. 9).
In this case, as compared with the non-azeotropic refrigerant mixture, since the evaporation temperature is reduced even if the logarithmic average temperature is equal, the compressor work increases,
Efficiency decreases.

In the present invention, since the non-azeotropic refrigerant mixture is used as the primary refrigerant, the efficiency is improved and the average evaporation temperature of the primary refrigerant is higher than before.

Next, the operation of the air conditioner (10) will be described.

First, during the cooling operation, the primary side circuit (1A)
Then, the four-way switching valve (22, 34) of the secondary circuit (1B) is switched to the solid line side in FIG. When the compressor (21) of the primary circuit (1A) is driven, the high-temperature and high-pressure primary refrigerant compressed by the compressor (21) is supplied from the four-way switching valve (22) to the outdoor heat exchanger. After flowing to (23) and condensing in the outdoor heat exchanger (23), the pressure is reduced by the expansion valve (24). Thereafter, the primary refrigerant flows into the main heat exchanger (11), evaporates, and returns to the compressor (21). This circulation operation is repeated.

On the other hand, when the pump (31) of the secondary circuit (1B) is driven, the secondary heat medium flows to the main heat exchanger (11) through the four-way switching valve (34). In the main heat exchanger (11), the secondary heat medium is cooled by evaporation of the primary refrigerant. Thereafter, the low-temperature secondary-side heat medium flows into the indoor heat exchanger (32) through the four-way switching valve (34), and the secondary-side heat medium exchanges heat with the indoor air to the pump (31). Return. This circulation operation is repeated. Then, the cooled room air blows out into the room.

During the heating operation, the primary side circuit (1A)
Then, the four-way switching valve (22, 34) of the secondary circuit (1B) is switched to the broken line side in FIG. When the compressor (21) of the primary circuit (1A) is driven, the high-temperature and high-pressure primary refrigerant compressed by the compressor (21) is supplied from the four-way switching valve (22) to the main heat exchanger. After flowing to (11) and condensing in the main heat exchanger (11), the pressure is reduced by the expansion valve (24). Thereafter, the primary refrigerant is
After flowing to the outdoor heat exchanger (23) and evaporating, the compressor (21)
Return to This circulation operation is repeated.

On the other hand, when the pump (31) of the secondary circuit (1B) is driven, the secondary heat medium flows to the main heat exchanger (11) through the four-way switching valve (34). In the main heat exchanger (11), the secondary heat medium is heated by condensation of the primary refrigerant. Thereafter, the high-temperature secondary-side heat medium flows into the indoor heat exchanger (32) through the four-way switching valve (34), and the secondary-side heat medium exchanges heat with room air to the pump (31). Return. This circulation operation is repeated. Then, the heated room air blows out into the room.

In the main heat exchanger (11), the primary-side refrigerant and the secondary-side heat medium exchange heat in opposite flows, so that, for example, during a cooling operation, as shown in FIG. Of 1
The temperature of the secondary refrigerant rises during evaporation (R1), and the fluctuation of the temperature difference between the primary refrigerant and the secondary heat medium is small.

In the indoor heat exchanger (32),
The indoor air flows in parallel with the fins (41), while the secondary-side heat medium flows through the medium passage (43), meanders left and right with respect to the air flow, and flows from the downstream side to the upstream side. As a result, the secondary-side heat medium and the room air substantially exchange air as a counterflow, and the secondary-side heat medium rises in temperature during, for example, a cooling operation, and the room air is cooled.

-Effects of First Embodiment- As described above, according to the present embodiment, the secondary circuit (1B)
Is configured in a structure corresponding to a conventional CFC-based refrigerant circuit, so that the overall shape can be reduced in size.

Further, since the amount of circulation of the secondary side heat medium does not increase, the transport power does not increase, and the equipment cost and the operating cost can be reduced.

In particular, since a copper pipe or the like can be used for the secondary side pipe (33), the installation and the like can be facilitated.

Further, since the secondary heat medium of the indoor heat exchanger (32) and the indoor air are substantially in counterflow, the temperature difference between the inlet and the outlet of the secondary heat medium can be set to 10 ° C. or more. As a result, the temperature efficiency can be increased to 50% or more, so that the transfer power can be reduced without increasing the size of the heat exchanger itself.

Further, since the primary-side refrigerant and the secondary-side heat medium of the main heat exchanger (11) are made to flow in opposite directions, the heat exchange efficiency can be improved.

Also, since the non-azeotropic mixed refrigerant is used as the primary refrigerant, for example, the evaporation temperature of the primary refrigerant changes when the primary refrigerant evaporates, so that the Lorentz cycle can be realized. it can. As a result, as compared with the case where a single refrigerant is used, the average evaporation temperature is improved, and the work of the compressor can be reduced.

Further, since the refrigerant and the heat medium of the main heat exchanger (11) are always made to flow in opposite directions by the four-way switching valve (34), the heat can be surely obtained during both cooling and heating. Exchange efficiency can be improved.

-Variations- In the above embodiment, a single-stage vapor compression cycle having only one compressor (21) is provided.
1) may be provided to configure a multi-stage vapor compression cycle. Thereby, the effect of the Lorentz cycle can be increased, and the COP can be improved.

[0088]

[Embodiment 2] As shown in FIG. 10, Embodiment 1 has a four-way switching valve (22, 34) provided in each of a primary side circuit (1A) and a secondary side circuit (1B). Instead of having the primary-side refrigerant and the secondary-side heat medium in the exchanger (11) flow in opposite directions, the present embodiment provides the primary-side circuit (1A) with the first circuit.
In addition to the four-way switching valve (22), a second four-way switching valve (2C) as switching means is provided.

More specifically, the primary side circuit (1A) is provided with a first four-way switching valve (22) similar to that of the first embodiment, and the primary heat exchanger (11) has a primary four-way switching valve (22). Side passage (1
Both ends of 2) are connected to a first four-way switching valve (22) and an expansion valve (24) via a second four-way switching valve (2C).
The second four-way switching valve (2C) constitutes switching means.

Therefore, the two-way switching valves (22, 2C) of the primary circuit (1A) are switched to the solid line side in FIG. 10 during the cooling operation, and the primary refrigerant flows from the compressor (21). It flows from the outdoor heat exchanger (23) to the expansion valve (24) through the first four-way switching valve (22). Thereafter, the primary-side refrigerant flows through the second four-way switching valve (2C) to the main heat exchanger (11),
From the four-way switching valve (2C) to the compressor (21) through the first four-way switching valve (22).

The two-way switching valves (22, 2C) of the primary circuit (1A) are switched to the broken line side in FIG. 10 during the heating operation, and the primary refrigerant is supplied from the compressor (21). It flows to the main heat exchanger (11) through the first four-way switching valve (22) and the second four-way switching valve (2C) in order. Thereafter, the primary-side refrigerant flows from the second four-way switching valve (2C) through the expansion valve (24), passes through the outdoor heat exchanger (23), and then passes through the first four-way switching valve (22). Through the compressor and return to the compressor (21).

On the other hand, the secondary circuit (1B) does not include the four-way switching valve (22) of the first embodiment. As a result, the primary-side refrigerant flows upward from the bottom in FIG. 10 in both the cooling operation and the heating operation, and the primary-side refrigerant and the secondary-side heat medium are supplied in both the cooling operation and the heating operation. , The flow is always countercurrent. Other configurations, operations, and effects are the same as those of the first embodiment.

[0093]

Third Embodiment As shown in FIG. 11, the first embodiment provides a four-way switching valve (22, 34) in each of a primary circuit (1A) and a secondary circuit (1B) to provide main heat. In the present embodiment, the primary circuit (1A) of the first embodiment is replaced with the main circuit (1A) instead of having the primary-side refrigerant and the secondary-side heat medium in the exchanger (11) in counterflow. 2M) and a switching means (2C) is provided.

More specifically, the switching means (2C) comprises four on-off valves (V1 to V4) and two heating passages (2a, 2b). The main circuit (2
M) is provided with a four-way switching valve (22) similar to that of the first embodiment, and a first cooling on-off valve (V1) between the expansion valve (24) and the main heat exchanger (11). A second cooling on-off valve (V2) is provided between the main heat exchanger (11) and the four-way switching valve (22).

On the other hand, the first heating passage (2a)
A heating on-off valve (V3) is provided in the second heating passage (2b).
A heating on-off valve (V4) is provided for each. One end of the first heating passage (2a) is between the four-way switching valve (22) and the second cooling on-off valve (V2), and the other end is connected to the main heat exchanger (11). It is connected between each of the cooling on-off valves (V1). Further, the second heating passage (2b)
One end of the second cooling on-off valve (V2) and the main heat exchanger (11)
The other end is connected between the first cooling on-off valve (V1) and the expansion valve (24).

The secondary circuit (1B) is the same as the second embodiment except that the four-way switching valve (34) of the first embodiment is omitted.
It is configured similarly to.

Therefore, the four-way switching valve (22) of the primary circuit (1A) switches to the solid line side in FIG. 11 during the cooling operation, and opens both cooling on-off valves (V1, V2). Close both heating valves (V3, V4). In this state, 1
The secondary refrigerant flows through the main circuit (2M), flows from the compressor (21) through the four-way switching valve (22), and flows from the outdoor heat exchanger (23) to the expansion valve (24). After that, the primary refrigerant flows into the main heat exchanger (11) through the first cooling on-off valve (V1),
Circulation is performed from the second cooling on-off valve (V2) to the compressor (21) through the four-way switching valve (22).

On the other hand, the four-way switching valve (22) of the primary circuit (1A) switches to the broken line side in FIG. 11 during the heating operation, and opens both heating on-off valves (V3, V4). Close both cooling on-off valves (V1, V2). In this state, the primary-side refrigerant flows from the compressor (21) through the four-way switching valve (22), through the first heating passage (2a), and to the main heat exchanger (11). Thereafter, the primary-side refrigerant passes through the second heating passage (2b), flows through the expansion valve (24), passes through the outdoor heat exchanger (23), and then passes through the four-way switching valve (22). Circulate back to the compressor (21).

As a result, the primary-side refrigerant flows upward from the bottom in FIG. 11 during both the cooling operation and the heating operation, and the primary-side refrigerant and the secondary-side heat medium flow during the cooling operation and the heating operation. In both cases, there is always countercurrent. Other configurations, operations, and effects are the same as those of the first embodiment.

[0100]

Fourth Embodiment As shown in FIG. 12, Embodiment 1 includes a refrigerator (5A) of a vapor compression cycle in a primary circuit (1A).
Instead of using the primary circuit (1), the present embodiment
A) uses a two-stage absorption cycle refrigerator (50). Further, the present embodiment is an air conditioner (10) dedicated to cooling that does not perform a heating operation, and includes a secondary circuit (1B)
Are described in Embodiment 2 (see FIG. 10) and Embodiment 3 (see FIG. 11).
As shown in (1), the secondary heat medium flows only in one direction.

The refrigerator (50) of the primary side circuit (1A)
The refrigerator (50) comprises a double-effect absorption cycle,
It comprises two absorbers (51, 52), a high temperature regenerator (53), a low temperature regenerator (54), a condenser (55), and two evaporators (56, 57). The refrigerator (50) uses water as a refrigerant and an aqueous solution of lithium bromide as an absorbing solution. Further, the refrigerator (50) is configured as a two-stage absorption cycle, and the two absorbers (51, 52) are configured as a high-pressure absorber (51) and a low-pressure absorber (52). The evaporators (56, 57) are composed of a high-pressure evaporator (56) and a low-pressure evaporator (57).

The high-temperature regenerator (53) includes a solution pump (5
According to a), a part of the absorbing solution is supplied from the high-pressure absorber (51). The high-temperature regenerator (53) is configured to heat a low-concentration absorbing solution, that is, a dilute solution by a burner (not shown). Then, the high-temperature regenerator (53) evaporates the primary-side refrigerant (water) in the solution by heating and concentrates the dilute solution to generate a high-concentration absorption solution, that is, a concentrated solution.

The low-temperature regenerator (54) includes a solution pump (5
According to a), the remainder of the dilute solution is branched and supplied from the high-pressure absorber (51). Since the low temperature regenerator (54) is guided by the refrigerant vapor generated in the high temperature regenerator (53), the low temperature regenerator (54) is configured to condense the refrigerant vapor and heat the dilute solution,
Heating causes the refrigerant (water) in the solution to evaporate and concentrates the dilute solution to produce a concentrated solution.

The high-temperature regenerator (53) and the low-temperature regenerator (5)
The concentrated solution generated in 4) is combined into a low-pressure absorber (52)
Supplied to The low-pressure absorber (52) is configured such that the concentrated solution absorbs the refrigerant, and the medium-absorbing solution having absorbed the refrigerant, that is, the intermediate-concentration solution is supplied to the solution pump (5).
b) returns to the high-pressure absorber (51). The high-pressure absorber (5
1) is configured such that the intermediate-concentration solution absorbs the refrigerant, and the dilute solution having absorbed the refrigerant is, as described above, the high-temperature regenerator (53) and the low-temperature regenerator (54) by the solution pump (5a). And supplied to.

The primary circuit (1A) includes a first solution heat exchanger (5c) and a second solution heat exchanger (5d). The first solution heat exchanger (5c) includes a dilute solution supplied to the high-temperature regenerator (53) and the low-temperature regenerator (54) and a lower-pressure absorber than the high-temperature regenerator (53) and the low-temperature regenerator (54). The concentrated solution flowing in (52) is configured to exchange heat.

The second solution heat exchanger (5d) exchanges heat between the dilute solution supplied to the high-temperature regenerator (53) and the concentrated solution flowing from the high-temperature regenerator (53) to the low-pressure absorber (52). It is configured to be.

The concentrated solution flowing out of the high-temperature regenerator (53) is decompressed by the decompression mechanism (5e), while the concentrated solution supplied to the low-pressure absorber (52) is decompressed by the decompression mechanism (5f). Is done.

In the high-temperature regenerator (53), the refrigerant vapor separated from the dilute solution is guided to the low-temperature regenerator (54) to heat the dilute solution, and is supplied to the condenser (5h) via the pressure reducing mechanism (5h). Enter 55). In the low-temperature regenerator (54),
The refrigerant vapor separated from the dilute solution merges with the refrigerant vapor from the high-temperature regenerator (53) and enters the condenser (55).

The condenser (55) is configured to cool and condense the refrigerant vapor, and the condensed water refrigerant is
Return to the high-pressure evaporator (56) via the pressure reducing mechanism (5i).

The high-pressure evaporator (56) is configured such that water as a refrigerant evaporates and refrigerant vapor is absorbed by the high-pressure absorber (51). Mechanism (5
g) to the low pressure evaporator (57).

The low-pressure evaporator (57) is configured such that water as a refrigerant evaporates and refrigerant vapor is absorbed by the low-pressure absorber (52).

On the other hand, the high-pressure evaporator (56) and the low-pressure evaporator (57) of the primary circuit (1A) constitute a main heat exchanger (11). Although not shown, the coils introduced into the high-pressure evaporator (56) and the low-pressure evaporator (57) constitute a secondary-side passage, through which the secondary-side heat medium flows and one of the secondary-side circuits (1B). Part is formed. The high-pressure evaporator (56) and the low-pressure evaporator (57) constitute a primary passage through which the refrigerant flows. The high-pressure evaporator (56) and the low-pressure evaporator (57) evaporate the refrigerant. Then, the secondary heat medium is cooled.

The high-pressure evaporator (56) and the low-pressure evaporator (57) are arranged so that the high-temperature secondary-side heat medium flows into the low-pressure evaporator (57) after flowing through the high-pressure evaporator (56). Are located. In other words, the high-temperature secondary-side heat medium heat-exchanged in the indoor heat exchanger (32) flows into the high-pressure evaporator (56), exchanges heat with a refrigerant having a high evaporation temperature, and is cooled. Flows into the low-pressure evaporator (57) and is cooled by exchanging heat with a refrigerant having a low evaporation temperature.

-Operation- Next, the cooling operation of the air conditioner (10) will be described.

First, the operation of the primary side circuit (1A) will be described with reference to the During diagram of FIG. In the high-pressure inhaler, the dilute solution that has absorbed the refrigerant vapor is in the state shown at point 1 in FIG. When this dilute solution is sucked by the solution pump (5a), the dilute solution exchanges heat with the first solution heat exchanger (5c), and the temperature rises to point 2 in FIG. 13, and a part of the dilute solution is regenerated at a low temperature. Enter the vessel (54).

The remaining part of the dilute solution exchanges heat in the second solution heat exchanger (5d) and enters the high temperature regenerator (53), where it is heated by a gas burner or the like, and the temperature rises to point 3 in FIG. At the same time, in the high-temperature regenerator (53), it boils and is concentrated to a concentrated solution until the state of point 4 in FIG.

The concentrated solution in the high-temperature regenerator (53) exchanges heat with the second solution heat exchanger (5d) to lower the temperature to the point 5 in FIG. Since the refrigerant vapor generated in the high-temperature regenerator (53) is guided to the low-temperature regenerator (54), the refrigerant is heated by the refrigerant vapor and concentrated into a concentrated solution until the state of point 6 in FIG.

Thereafter, the concentrated solution in the high-temperature regenerator (53) that has exchanged heat in the second solution heat exchanger (5d) is subjected to a decompression mechanism (5e).
Through the first solution heat exchanger (5c) to lower the temperature to point 7 in FIG. 13 and to absorb the low pressure through the pressure reducing mechanism (5f). Enter the vessel (52).

Subsequently, in the low pressure absorber (52),
The refrigerant vapor of the low-pressure evaporator (57) is absorbed and diluted to the state of the point 8 in FIG. Thereafter, the intermediate-concentration solution is sent to the high-pressure absorber (51) in the state of point 9 in FIG. 13 by the solution pump (5b), absorbs the refrigerant vapor of the high-pressure evaporator (56), and returns to point 1 in FIG. And diluted to a dilute solution.

The refrigerant vapor of the high-temperature regenerator (53) condenses in the low-temperature regenerator (54), passes through the pressure reducing mechanism (5h), and joins with the refrigerant vapor generated in the low-temperature regenerator (54). Enters the condenser (55). In the condenser (55), the refrigerant vapor is cooled by cooling water or the like and condensed. Thereafter, the condensed refrigerant water enters the high-pressure evaporator (56) via the pressure reducing mechanism (5i), and a part of the refrigerant water exchanges heat with the secondary-side heat medium and evaporates.

Furthermore, the refrigerant water of the high-pressure evaporator (56)
It enters the low-pressure evaporator (57) via the decompression mechanism (5g) and evaporates by exchanging heat with the secondary-side heat medium.

On the other hand, when the pump (31) is driven in the secondary circuit (1B), the secondary heat medium is supplied to the main heat exchanger (1B).
It flows to 1) the high pressure evaporator (56). The high pressure evaporator (5
In 6), the secondary heat medium is cooled by evaporation of the refrigerant. Further, the secondary heat medium is a low-pressure evaporator (5
7), and in the low-pressure evaporator (57), the secondary-side heat medium is cooled by evaporation of the refrigerant. Thereafter, the low-temperature secondary-side heat medium flows into the indoor heat exchanger (32), and the secondary-side heat medium exchanges heat with room air to return to the pump. This circulation operation is repeated. Then, the cooled room air blows out into the room.

-Effects of Embodiment 4- As described above, according to the present embodiment, the primary side circuit (1A)
To apply a two-stage absorption cycle refrigerator (50) to
Since the solution temperature at the outlet of the high-pressure absorber (51) (see point 1 in FIG. 13) can be increased, the concentration of the dilute solution can be reduced, and the difference in concentration from the concentrated solution can be increased. .

Further, since the amount of heat for heating can be reduced, the COP can be improved.

Further, since the solution temperature of the high-pressure absorber (51) can be increased as compared with the single-stage absorption cycle,
The refrigerant temperature in the high-pressure evaporator (56) can be increased, a sufficient temperature difference from the secondary-side heat medium can be ensured, and the shape of the evaporator (56) itself can be reduced in size. Other effects related to the secondary circuit (1B), such as a reduction in transfer power, are the same as in the first embodiment.

-Modifications- In this embodiment, a refrigerator (50) having a two-stage absorption cycle is used, but a refrigerator (50) having three or more stages of a multi-stage absorption cycle may be used.

In this embodiment, it is desired to use water as the refrigerant and an aqueous solution of lithium bromide as the absorbing solution. However, various substances such as ammonia and water may be used in combination with the refrigerant and the absorbing solution.

[0128]

Fifth Embodiment As shown in FIG. 14, a fourth embodiment has a two-stage absorption cycle refrigerator (5A) in the primary circuit (1A).
Instead of using the primary circuit (1), the present embodiment
A) uses multiple single-stage absorption cycle refrigerators (50). Note that the present embodiment is an air conditioner (10) dedicated to cooling, as in the fourth embodiment.

That is, the primary side circuit (1A) is provided with n absorption cycle refrigerators (50-1, 50-2,..., 50-n). This refrigerator (50-1, 50-2, ..., 50-n)
Is, for example, a single-effect absorption refrigerator (not shown), but a high-temperature regenerator (5) of the double-effect refrigerator (50) in the fourth embodiment.
3) Without the low-pressure evaporator (57) and the low-pressure absorber (52), in addition to the absorber (51) (high-pressure absorber in FIG. 12) and the regenerator (53) (high-temperature regenerator in FIG. 12), It has a condenser (55) and an evaporator (56) (high-pressure evaporator in FIG. 12). And the said evaporator (56) comprises the main heat exchanger (11).

This single-effect refrigerator (50-1, 50-2,..., 50)
-n), as shown in FIG. 15, the dilute solution having absorbed the refrigerant in the absorber (51) is heated in the solution heat exchanger (5c) and the regenerator (53), and boils to become a concentrated solution. , And then return to the absorber (51) via the solution heat exchanger (5c). on the other hand,
The refrigerant vapor generated in the regenerator (53) is cooled in the condenser (55), and exchanges heat with the secondary-side heat medium in the evaporator (56) to evaporate.

On the other hand, the evaporator (56) in each refrigerator (50-1, 50-2,..., 50-n) of the primary circuit (1A) constitutes a main heat exchanger (11). ing. Although not shown, the coil introduced into each of the evaporators (56) forms a secondary passage, and the secondary heat medium flows to form a part of the secondary circuit (1B). The inside of the evaporator (56) forms a primary side passage through which the refrigerant flows, and the evaporator (56) cools the secondary side heat medium by evaporating the refrigerant.

Each of the refrigerators (50-1, 50-2,..., 50)
The evaporator (56) of -n) is disposed so as to exchange heat with the secondary side heat medium from a refrigerant having a high evaporation temperature. That is, as shown in FIG. 15, the high-temperature secondary-side heat medium heat-exchanged in the indoor heat exchanger (32) exchanges heat with the refrigerant in the evaporator (56) of the first refrigerator (50-1). And then cooled by the evaporator (56) of the second refrigerator (50-2).
From the evaporator (56) of the refrigerator (50-3) to the n-th refrigerator (50-3).
-n) is cooled in the evaporator (56).

Therefore, according to the present embodiment, a refrigerator (50) having a low heat source temperature can be used, that is, a refrigerator (50) having a low heating heat source temperature of the regenerator (53).
Can be used, so that the energy efficiency of the entire apparatus can be improved.

The other configurations and operations, and the effects of the secondary circuit (1B) such as the reduction of the transport power are described in the fourth embodiment.
Is the same as

[0135]

Sixth Embodiment As shown in FIG. 16, a fifth embodiment has a plurality of single-effect absorption cycle refrigerators (50-1, 50-2,..., 50-n) in a primary circuit (1A). ), The air conditioner (10) dedicated to cooling is used instead of this embodiment.
Refrigerators with multiple double-effect absorption cycles (50-1, 50-2,
, 50-n) to form an air conditioner (10) dedicated to heating.

Refrigerator (50) of the above double effect absorption cycle
Is basically a refrigerator (50) shown in FIG.
The refrigerator (50) of the fourth embodiment does not include the low-pressure absorber (52) and the low-pressure evaporator (57). Therefore, the reference numerals in FIG.
The same reference numerals are given to the same functional parts as the refrigerator (50).

Refrigerator (50) of the double effect absorption cycle
Consists of an absorber (51), a low-temperature regenerator (54) and a high-temperature regenerator (5
3), a condenser (55) and an evaporator (56), wherein water is used as a refrigerant and an aqueous solution of lithium bromide is used as an absorbing solution.

The low-temperature regenerator (54) includes a solution pump (5
The absorption solution is supplied from the absorber (51) by a).
Since the refrigerant vapor generated in the high-temperature regenerator (53) is guided to the low-temperature regenerator (54), the low-temperature regenerator (54) is configured to heat the dilute solution with the refrigerant vapor, and the refrigerant (water) in the solution is heated. Is evaporated and the dilute solution is concentrated to produce an intermediate concentration solution.

The high-temperature regenerator (53) includes a solution pump (5
The intermediate concentration solution is supplied from the low temperature regenerator (54) by j). The high-temperature regenerator (53) is configured to heat the intermediate-concentration solution with a burner (not shown), and by this heating, the refrigerant (water) in the solution is evaporated, and the intermediate-concentration solution is further concentrated to generate a concentrated solution. I do.

The concentrated solution generated in the high-temperature regenerator (53) is supplied to the absorber (51). The absorber (51) is configured such that the concentrated solution absorbs the refrigerant vapor, and the diluted solution that has absorbed the refrigerant is supplied to the solution pump (5a) as described above.
Is supplied to the low-temperature regenerator (54).

The refrigerator (50) includes a first solution heat exchanger (5c) and a second solution heat exchanger (5j).
The first solution heat exchanger (5c) is configured to exchange heat between the dilute solution supplied to the low temperature regenerator (54) and the concentrated solution flowing from the high temperature regenerator (53) to the absorber (51). ing.

The second solution heat exchanger (5j) comprises an intermediate concentration solution supplied to the high temperature regenerator (53) and the high temperature regenerator (5j).
3) It is configured to exchange heat with the concentrated solution flowing through the absorber (51).

The high-temperature regenerator (53) is used to remove the absorber (5).
The concentrated solution flowing in 1) is depressurized by the decompression mechanism (5f).

In the low-temperature regenerator (54), the refrigerant vapor separated from the dilute solution enters the condenser (55) and condenses, while in the high-temperature regenerator (53), the refrigerant vapor separated from the intermediate-concentration solution is discharged. The dilute solution is guided to the low-temperature regenerator (54) and is condensed by heating. This condensed refrigerant water joins with the refrigerant water from the condenser (55) via the pressure reducing mechanism (5h),
Return to the evaporator (56) via the pressure reducing mechanism (5i).

The evaporator (56) is configured so that refrigerant water evaporates and refrigerant vapor is absorbed by the absorber (51). The heat source of the evaporator (56) is the outside air, and the outside air evaporates the refrigerant water.

On the other hand, the absorber (5) of the primary side circuit (1A)
1) and the condenser (55) constitute a main heat exchanger (11). The coil introduced into the absorber (51) and the condenser (55) forms a secondary passage (13), and the secondary heat medium flows to form a part of the secondary circuit (1B). ing. Although not shown, the interiors of the absorber (51) and the condenser (55) constitute a primary passage through which the solution and the refrigerant flow, and the heat of absorption of the solution in the absorber (51) and the condenser ( The secondary heat medium is heated by the condensation heat of the refrigerant in 55).

Each of the refrigerators (50-1, 50-2,..., 50)
-n) is arranged so as to exchange heat with the secondary side heat medium from the one having the lowest absorption temperature and condensation temperature of the absorber (51) and the condenser (55). That is, since the absorption temperature and the condensing temperature are almost equal, as shown in FIG. 17, the high-temperature secondary-side heat medium heat-exchanged in the indoor heat exchanger (32) is supplied to the first refrigerator (50-1). Is heated by exchanging heat with the refrigerant in the condenser (55) of the second refrigerator (50-2), and then heated by the condenser (55) of the second refrigerator (50-2). -3) The condenser (55) and the like are heated by the condenser (55) and the like of the n-th refrigerator (50-n).

-Operation- Next, the heating operation of the air conditioner (10) will be described.

First, in the absorber (51), the dilute solution having absorbed the refrigerant vapor is sucked by the solution pump (5a) and
The heat is exchanged in the solution heat exchanger (5c) and the solution enters the low-temperature regenerator (54). In the low temperature regenerator (54), the refrigerant is concentrated to an intermediate concentration solution by the refrigerant vapor from the high temperature regenerator (53). Further, the intermediate-concentration solution enters the high-temperature regenerator (53) via the second solution heat exchanger (5d), is heated by a gas burner or the like, boils, and is concentrated into a concentrated solution.

Thereafter, the concentrated solution in the high-temperature regenerator (53) is supplied to two solution heat exchangers (5c, 5d) and a pressure reducing mechanism (5f).
And enters the absorber (51). In the absorber (51), the refrigerant vapor in the evaporator (56) is absorbed and diluted into a dilute solution.

The refrigerant vapor of the high temperature regenerator (53) is condensed by the low temperature regenerator (54) and decompressed by the pressure reducing mechanism (5h), while the refrigerant vapor of the low temperature regenerator (54) is condensed. It is cooled and condensed in the vessel (55). After these refrigerant waters join, they enter the evaporator (56) via the pressure reducing mechanism (5i), evaporate using the outside air as a heat source, and the refrigerant vapor is absorbed by the absorber (51).

On the other hand, when the pump is driven in the secondary circuit (1B), the secondary heat medium flows to the absorber (51) and the condenser (55), which are the main heat exchanger (11). In the absorber (51) and the condenser (55), the secondary-side heat medium is heated by heat of absorption and heat of condensation. Thereafter, the secondary heat medium is sequentially supplied to the refrigerator (50-2, 50-1) of the primary circuit (1A).
, 50-n), the high-temperature secondary-side heat medium flows into the indoor heat exchanger (32), and the secondary-side heat medium exchanges heat with room air to return to the pump (31). This circulation operation is repeated.
Then, the heated room air blows out into the room.

Therefore, according to the present embodiment, as in the fifth embodiment, a refrigerator (50) having a low heat source temperature can be used, so that the energy efficiency of the entire apparatus can be improved. Other configurations, operations, and effects are the same as those of the fifth embodiment.

In this embodiment, each of the refrigerators (50-1, 50-
The main heat exchanger (11) was used for both the absorber (51) and the condenser (55) for each of the refrigerators (50-1, 50-n).
-2,..., 50-n), only one of the absorber (51) and the condenser (55) may be configured as the main heat exchanger (11).

In this embodiment, a refrigerator (50) having a multi-stage absorption cycle may of course be used.

[0156]

Seventh Embodiment As shown in FIG. 18, the fourth embodiment has a two-stage absorption cycle refrigerator (5A) in the primary side circuit (1A).
Instead of using only one of the refrigerators (50-) in the primary circuit (1A), a plurality of two-stage absorption cycle refrigerators (50-
1, 50-2, 50-3). This embodiment is similar to the fourth embodiment in that the air conditioner (10) dedicated to cooling is used.
It is.

That is, the primary side circuit (1A) is provided with three two-stage absorption cycle refrigerators (50-1, 50-2, 50-3). In addition, each of the above refrigerators (50-1, 50-2, 50-
3) is arranged so as to exchange heat with the secondary side heat medium from a refrigerant having a high evaporation temperature. That is, as shown in FIG. 18, the high-temperature secondary-side heat medium heat-exchanged in the indoor heat exchanger (32) exchanges heat with the refrigerant in each evaporator (56) of the first refrigerator (50-3). After being cooled by the evaporators (56) of the second refrigerator (50-2), the evaporators (56) of the third refrigerator (50) are sequentially cooled from the evaporators (56) of the third refrigerator (50). It is cooled in each evaporator (56) of the refrigerator (50-3). Other configurations, operations, and effects are the same as those of the fourth embodiment.

[0158]

Eighth Embodiment FIG. 19 shows an eighth embodiment,
This uses exhaust heat as the heat source for the primary circuit (1A). The primary side circuit (1A) is constituted by any one of the fifth to seventh embodiments, that is, the refrigerators (50-1, 50-2,..., 50-n) having a plurality of absorption cycles. It is composed of

As a heating means of the regenerator or the high-temperature regenerator (53) as a heat source, waste heat generated from cogeneration is used. The exhaust heat includes exhaust heat of a fuel cell, a gas turbine, a gas engine, and a gas heat pump.

Further, the primary circuit (1
Each of the refrigerators (50-1, 50-2,..., 50-n) in A) is configured to use exhaust heat as a heat source.

Therefore, according to the present embodiment, since the primary side circuit (1A) uses the exhaust heat, the energy can be effectively used.

In particular, since the low-temperature exhaust heat can be used, the energy efficiency can be further improved. Other configurations, operations, and effects are the same as those of the fourth to seventh embodiments.

[0163]

Ninth Embodiment FIG. 20 shows a ninth embodiment,
Different from the eighth embodiment, two refrigerators (50-1 and 50-2)
In this case, two refrigerators (50-n, 50-n + 1) use gas or heavy oil. Then, for example, the exhaust heat is used for the refrigerators (50-1 and 50-2) that first cool the high-temperature secondary-side heat medium returned from the indoor heat exchanger (32). Refrigerators (50-n, 50-n) that cool the medium to low temperatures
+1) uses gas or heavy oil.

Therefore, according to the present embodiment, energy can be effectively used as in the eighth embodiment.

In particular, since a heat source such as gas is used in combination, low-temperature cold heat or high-temperature heat can be reliably generated, and the secondary-side heat medium can be reliably cooled or heated. Other configurations, operations, and effects are the same as those of the eighth embodiment.

[0166]

[Embodiment 10] Fig. 21 shows Embodiment 10 in which a gas or heavy oil according to Embodiment 9 is used.
Instead of the two refrigerators (50-n, 50-n + 1), two refrigerators (50-n, 50-n + 1) of the vapor compression cycle as in Embodiment 1 etc.
It is a thing using.

That is, two absorption cycle refrigerators (50
-1, 50-2) is configured as a refrigerator that uses waste heat and has a relatively high evaporation temperature. In addition, the refrigerators (50-n, 50-n + 1) of the two vapor compression cycles are configured as refrigerators that use electricity as a heat source and have a relatively low evaporation temperature. The refrigerators (50-n, 50-n + 1) of the vapor compression cycle are configured to perform only a cooling operation or a heating operation, for example.

Therefore, for example, for cooling operation,
The high-temperature secondary heat medium from the indoor heat exchanger (32) is first cooled by the absorption cycle refrigerators (50-1, 50-2), and then
This secondary heat medium is transferred to a refrigerator (50-n,
Cool by 50-n + 1). As a result, according to the present embodiment,
As in the ninth embodiment, energy can be effectively used.

In particular, since a heat source such as gas is used in combination, low-temperature cold heat and high-temperature heat can be reliably generated, and the secondary-side heat medium can be reliably cooled or heated. Other configurations, operations, and effects are the same as those of the ninth embodiment.

[0170]

Eleventh Embodiment FIG. 22 shows an eleventh embodiment, in which a refrigerator (50) utilizing waste heat in the ninth embodiment is used.
-1, 50-2) and a refrigerator using gas or heavy oil (50-n, 50
-n + 1) and two refrigerators (50-n + m, 50-n + m + 1) of a vapor compression cycle as in the first embodiment.

Therefore, for example, for cooling operation,
The high-temperature secondary heat medium from the indoor heat exchanger (32) is first cooled by the refrigerators (50-1, 50-2) in the absorption cycle using waste heat, and then the secondary heat medium is cooled by gas. Alternatively, it is cooled by a refrigerator (50-n, 50-n + 1) of an absorption cycle using heavy oil, and then the secondary heat medium is cooled by a refrigerator (50-n, 50-n + 1)
-n + m, 50-n + m + 1). As a result, according to the present embodiment, as in the ninth embodiment, effective use of energy can be achieved.

In particular, since a heat source such as gas is used in combination, low-temperature cold heat and high-temperature heat can be reliably generated, and the secondary-side heat medium can be reliably cooled or heated. Other configurations, operations, and effects are the same as those of the ninth embodiment.

[0173]

Twelfth Embodiment As shown in FIGS. 23 and 24, the fifth embodiment is different from the fifth embodiment in that a refrigerator (50) having a plurality of absorption cycles is used in the primary circuit (1A). The form is
Refrigerator with multiple adsorption cycles in primary circuit (1A) (60)
Is used. Note that the present embodiment is also an air conditioner (10) dedicated to cooling, as in the fifth embodiment.

The refrigerator (60) of the adsorption cycle includes a condenser (61), an evaporator (62), a first adsorbent heat exchanger (63), and a second adsorbent heat exchanger (64). ing. And
The refrigerator (60) of the adsorption cycle uses, for example, silica gel or zeolite activated carbon as a fixed adsorbent,
Water vapor or alcohol vapor is used as the refrigerant.

The above condenser (55) and both adsorbent heat exchangers (6
3, 64) is a desorption passage (6a, 6) with an on-off valve (SV).
b), and the evaporator (56) and the adsorbent heat exchangers (63, 64) are connected via adsorption passages (6c, 6d) having an on-off valve (SV). Have been. The condenser (55) and the evaporator (56) are connected via a refrigerant passage (6f) having a pressure reducing mechanism (6e).

Although not shown, the adsorbent heat exchangers (63, 64) each contain an adsorbent and are provided with coils for heating and cooling the adsorbent.

On the other hand, the evaporator (56) constitutes a main heat exchanger (11). Although not shown, the coil introduced into the evaporator (56) constitutes a secondary passage, and The secondary heat medium flows to form a part of the secondary circuit (1B). The inside of the evaporator (56) forms a primary side passage through which the refrigerant flows, and the evaporator (56) cools the secondary side heat medium by evaporating the refrigerant.

In addition, the evaporator (56) of each of the refrigerators (60)
Are disposed so as to exchange heat with the secondary side heat medium from a refrigerant having a high evaporation temperature.

The operation of the adsorption cycle will now be described. For example, as shown in FIG. 23, the first adsorbent heat exchanger (63) is in the process of desorption (regeneration) and the second adsorbent heat exchanger (63) 64) is in the adsorption process, the condenser (55) communicates with the first adsorbent heat exchanger (63) through the desorption passage (6a), and the evaporator (56) exchanges heat with the second adsorbent. The vessel (64) communicates with the suction passage (6d). In FIGS. 23 and 24, each on-off valve (SV) has a black solid state indicating a closed state.

In the first adsorbent heat exchanger (63),
The adsorbent is heated to desorb refrigerant vapor as an adsorbate, and the refrigerant vapor moves to the condenser (55), radiates heat and condenses into refrigerant water. This refrigerant water moves to the evaporator (56) via the pressure reducing mechanism (6e).

On the other hand, in the second adsorbent heat exchanger (64), since the adsorbent is cooled and adsorbs refrigerant vapor, the pressure in the evaporator (56) is reduced, and the refrigerant water absorbs heat and evaporates.

When the desorption of the first adsorbent heat exchanger (63) and the adsorption of the second adsorbent heat exchanger (64) are completed, FIG.
As shown in FIG. 4, the on-off valve (SV) is switched so that the second adsorbent heat exchanger (64) communicates via the desorption passage (6b),
The evaporator (56) and the first adsorbent heat exchanger (63) communicate with each other via the adsorption passage (6c). This operation is repeated.

Therefore, while the evaporator (56) generates cold heat, the adsorbent is heated by an external heat source in the adsorbent heat exchangers (63, 64) in the desorption process. As the external heat source, for example, waste heat of cogeneration is used.

Further, the refrigerators (60) of the plurality of adsorption cycles sequentially cool the secondary heat medium in a plurality of stages. Other configurations, operations, and effects are the same as those of the fifth embodiment.

[0185]

Embodiment 13 As shown in FIGS. 25 and 26, Embodiment 4 is different from Embodiment 4 in that a refrigerator (60) having a two-stage absorption cycle is used for the primary circuit (1A). The form is 1
This uses a two-stage adsorption cycle refrigerator (60) for the secondary circuit (1A).

That is, the refrigerator (60) of the two-stage adsorption cycle is different from the refrigerator (60) of Embodiment 12 shown in FIGS. 23 and 24 in that the low-pressure evaporator (65) and the first adsorbent on the low-pressure side are used. A heat exchanger (66) and a second adsorbent heat exchanger (67) are provided. That is, in the present embodiment, the evaporator (62) of the twelfth embodiment is a high-pressure evaporator (62), and both the adsorbent heat exchangers (63, 64) of the twelfth embodiment are the first adsorbent heat exchange on the high pressure side. (63) and a second adsorbent heat exchanger (64).

The low-pressure evaporator (65) is a high-pressure evaporator (6
2) is connected via a refrigerant passage (6h) having a pressure reducing mechanism (6g). Further, in the low-pressure evaporator (57), a first adsorbent heat exchanger (66) and a second adsorbent heat exchanger (67) on the low pressure side are provided with an adsorption passage (6c) having an on-off valve (SV). , 6d)
Connected through.

In the condenser (55), the first adsorbent heat exchanger (66) and the second adsorbent heat exchanger (67) on the low pressure side have a desorption passage (SV) having an on-off valve (SV). 6a, 6b).

On the other hand, the high-pressure evaporator (62) and the low-pressure evaporator (65) constitute a main heat exchanger (11). Although not shown, the high-pressure evaporator (62) and the low-pressure evaporator (65) The coil introduced into the second side constitutes a secondary side passage, and the secondary side heat medium flows to form a part of the secondary side circuit (1B). And
The inside of the high-pressure evaporator (62) and the low-pressure evaporator (65)
The high-pressure evaporator (62) forms a primary side passage through which a refrigerant flows.
The low-pressure evaporator (65) evaporates the refrigerant and cools the secondary-side heat medium.

The high-pressure evaporator (62) and the low-pressure evaporator (65) are arranged so as to exchange heat with the secondary-side heat medium from the refrigerant having the highest evaporation temperature.

The operation of the adsorption cycle will now be described. As shown in FIGS. 25 and 26, the condenser (61), the high-pressure evaporator (62), and the high-pressure side adsorbent heat exchangers (63, 64) ) Is carried out in the same manner as in the twelfth embodiment, and between the condenser (61), the low-pressure evaporator (65), and the low-pressure-side adsorbent heat exchangers (66, 67). Embodiment 12
Adsorption and desorption are performed in the same manner as described above. On the other hand, the refrigerant water condensed in the condenser (61) first enters the high-pressure evaporator (62), partially evaporates and cools the secondary-side heat medium, and then enters the low-pressure evaporator (65). Then, the secondary heat medium is cooled. Other configurations, operations, and effects are the same as those of the fourth embodiment.

[0192]

Other Embodiments of the Invention Embodiments 5, 7, 12, and 13 are air conditioners (10) dedicated to cooling, and Embodiment 6 is an air conditioner (10) dedicated to heating. However, both the cooling operation and the heating operation may be performed.

That is, for example, when the refrigerator (50) of the absorption cycle shown in FIG. 16 is applied to the primary circuit (1A), the main heat exchanger (11) is connected to the evaporator (56) and the condenser. (55)
Or an evaporator (56) and an absorber (51), or an evaporator (56), a condenser (55) and an absorber (51). The secondary heat medium flows through the evaporator (56) during the cooling operation, and the condenser (55) during the heating operation.
Alternatively, it may flow through one or both of the absorbers (51).

When the refrigerator (60) of the adsorption cycle shown in FIG. 23 is applied to the primary side circuit (1A), the main heat exchanger (11) includes the evaporator (62) and the condenser (61). ) Or an evaporator (62) and an adsorbent heat exchanger (63, 6) in the adsorption process.
4) or an evaporator (62) and a condenser (61)
And an adsorbent heat exchanger (63, 64) in the adsorption process. The secondary heat medium is supplied to the evaporator (6
2), and may flow through one or both of the condenser (61) and the adsorbent heat exchangers (63, 64) in the adsorption process during the heating operation.

[Brief description of the drawings]

FIG. 1 is a refrigerant circuit diagram showing Embodiment 1 of the present invention.

FIG. 2 is a schematic perspective view of the indoor heat exchanger according to the first embodiment.

FIG. 3 is a characteristic diagram of a pressure loss for each diameter of a secondary pipe and a temperature difference between an inlet and an outlet of an indoor heat exchanger.

FIG. 4 is a psychrometric diagram showing a relationship between a secondary-side heat medium and room air under a first temperature condition.

FIG. 5 is a psychrometric diagram showing a relationship between a secondary-side heat medium and room air under a second temperature condition.

FIG. 6 is a psychrometric diagram showing a relationship between a secondary-side heat medium and room air under a third temperature condition.

FIG. 7 is a psychrometric chart showing a conventional relationship between a secondary heat medium and room air.

FIG. 8 is a characteristic diagram showing heat exchange between a primary refrigerant and a secondary heat medium.

FIG. 9 is a characteristic diagram showing heat exchange between a conventional primary-side refrigerant and a secondary-side heat medium.

FIG. 10 is a refrigerant circuit diagram showing Embodiment 2 of the present invention.

FIG. 11 is a refrigerant circuit diagram showing Embodiment 3 of the present invention.

FIG. 12 is a circuit configuration diagram of an absorption refrigerator showing a fourth embodiment of the present invention.

FIG. 13 is a During diagram of a refrigerator according to a fourth embodiment.

FIG. 14 is a schematic configuration diagram of an air conditioner showing a fifth embodiment of the present invention.

FIG. 15 is a During diagram of a refrigerator according to a fifth embodiment.

FIG. 16 is a circuit configuration diagram of an absorption refrigerator showing a sixth embodiment of the present invention.

FIG. 17 is a During diagram of a refrigerator showing a sixth embodiment.

FIG. 18 is a During diagram of a refrigerator according to a seventh embodiment.

FIG. 19 is a circuit configuration diagram of an absorption refrigerator showing an eighth embodiment of the present invention.

FIG. 20 is a circuit configuration diagram of an absorption refrigerator showing a ninth embodiment of the present invention.

FIG. 21 is a circuit configuration diagram of an absorption refrigerator showing a tenth embodiment of the present invention.

FIG. 22 is a circuit configuration diagram of an absorption refrigerator showing an eleventh embodiment of the present invention.

FIG. 23 is a circuit configuration diagram of an adsorption refrigerator showing a twelfth embodiment of the present invention.

FIG. 24 is a circuit diagram showing another operation state of the adsorption refrigerator of the twelfth embodiment.

FIG. 25 is a circuit configuration diagram of an adsorption refrigerator showing a thirteenth embodiment of the present invention.

FIG. 26 is a circuit configuration diagram showing another operation state of the adsorption refrigerator of the thirteenth embodiment.

[Explanation of symbols]

 10 Air conditioner 1A Primary circuit 1B Secondary circuit 11 Main heat exchanger 12 Primary path 13 Secondary path 20, 50, 60 Refrigerator 2C Switching means 30 Circulation circuit 31 Pump 32 Indoor heat exchanger 34 Four-way switching valve (switching means)

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI Theme coat ゛ (Reference) F25B 25/02 F25B 25/02 Z 27/02 27/02 K 39/04 39/04 MF term (reference 3L092 AA01 AA02 BA06 BA11 BA26 FA22 3L093 AA05 BB13 BB22 BB29 BB43 LL03

Claims (15)

[Claims] A heat source means (1) for cooling or heating a heat medium.
A), a conveying means (31) for conveying the heat medium, and a use side heat exchanger (32) for exchanging heat between the heat medium and air are connected in order, and the heat medium circulates, An air conditioner in which a circulation circuit (30) for performing air conditioning based on a change in sensible heat is configured, wherein the circulation circuit (30) corresponds to a circuit structure of a refrigerant that performs air conditioning based on a change in latent heat. An air conditioner characterized by having a circuit structure for carrying. 2. The air conditioner according to claim 1, wherein the use side heat exchanger (32) is configured to have a temperature efficiency of 50% or more. 3. The air conditioner according to claim 1, wherein the use side heat exchanger (32) has a temperature difference between the inlet and the outlet of the heat medium of 10 or less.
An air conditioner, wherein the heat medium and the air are formed so as to be at least substantially in countercurrent so that the temperature is equal to or higher than ° C. 4. The air conditioner according to claim 1, wherein the heat source means (1A) comprises a refrigerator (20) using a non-azeotropic mixed refrigerant as a working fluid, and the main heat exchange means. The air conditioner (11), wherein the unit (11) is configured to exchange heat between the refrigerant of the refrigerator (20) and the heat medium in at least a substantially countercurrent flow. 5. The air conditioner according to claim 4, wherein the circulation circuit (30) corresponds to a direction in which the refrigerant circulates so that the refrigerant and the heat medium of the main heat exchanger (11) always flow in opposite directions. An air conditioner comprising a switching means (34) for changing the direction of circulation of the heat medium. 6. The air conditioner according to claim 4, wherein the heat source means (1A) is arranged in the circulation direction of the heat medium so that the refrigerant and the heat medium of the main heat exchanger (11) always flow in opposite directions. An air conditioner comprising a switching means (2C) for correspondingly changing the circulation direction of the refrigerant. 7. The air conditioner according to claim 4, wherein the heat source means (1A) includes a refrigerator (20) of a multi-stage compression cycle. 8. The air conditioner according to claim 1, wherein the heat source means (1A) includes a multistage absorption cycle or a multistage adsorption cycle refrigerator (50, 60). And air conditioners. 9. The air conditioner according to claim 1, wherein the heat source means (1A) is a first refrigerator of an absorption cycle or an adsorption cycle using a high evaporation temperature and low heat as a driving source. (Five
0,60) and a second refrigerator (5, 60) of an absorption cycle or an adsorption cycle, having a lower evaporation temperature than the first refrigerator (50, 60) and a heat source higher than that of the first refrigerator (50, 60). 50, 60)
An air conditioner, characterized in that the refrigerators (50, 60) are arranged so as to exchange heat with a heat medium in ascending order of evaporation temperature. 10. The air conditioner according to any one of claims 1 to 3, wherein the heat source means (1A) is a first refrigerator of an absorption cycle having a low condensing or absorption temperature and a low heat as a driving source. (50)
And at least a second refrigerator (50) in an absorption cycle having a higher condensation temperature or absorption temperature than the first refrigerator (50) and a higher heat than the first refrigerator (50) as a driving source. An air conditioner, wherein each refrigerator (50) is arranged to exchange heat with a heat medium in ascending order of condensation temperature. 11. The air conditioner according to any one of claims 1 to 3, wherein the heat source means (1A) is a first refrigerator of an adsorption cycle having a low condensing temperature or an adsorption temperature and a low heat as a driving source. (60)
And at least a second refrigerator (60) in an adsorption cycle having a higher condensation temperature or adsorption temperature than the first refrigerator (60) and a heat source higher than that of the first refrigerator (60) as a driving source. An air conditioner, wherein each refrigerator (60) is arranged to exchange heat with a heat medium in ascending order of condensation temperature. 12. The air conditioner according to claim 9, wherein the refrigerators (50, 60) are configured in a multi-stage cycle. 13. The air conditioner according to any one of claims 8 to 11, wherein all the refrigerators (50, 60) of the heat source means (1A) are configured to use waste heat of cogeneration as a heat source. An air conditioner, comprising: 14. The air conditioner according to claim 8, wherein some of the refrigerators (50, 60) of the heat source means (1A) use the waste heat of the cogeneration as a heat source. An air conditioner, comprising: 15. The air conditioner according to any one of claims 8 to 11, wherein the heat source means (1A) further applies heat to the heat medium after the refrigerator (50, 60) applies heat to the heat medium. An air conditioner comprising a vapor compression cycle refrigerator (20) for applying heat.