JPH02122134A - Multi chamber cooling and heating device - Google Patents

Abstract

PURPOSE:To make it possible to minimize a drop in capacity due to long piping and carry out capacity control operation with efficiency by installing an on/off valve respectively in linear to all plural auxiliary heat exchangers excluding one and linear piping which comprises the second auxiliary heat exchangers and piping for the second auxiliary heat exchangers alone in parallel. CONSTITUTION:During cooling operation for example, high temperature and high pressure gas discharged from compressors 11a and 11b is irradiated and liquefied in heat source side heat exchangers 13a and 13b by way of four way valves 12 and 12b, and decompressed decompression device 16a and 16b for cooling service, passing through check valves 15a and 15b. The decompressed gas is heat adsorbed and vaporized in first auxiliary heat exchangers 18 and 18b, and returned to the compressors 11a and 11b from the four way valves 12a and 12b, thus forming a refrigerating cycle. During this cycle, a refrigerant transfer device 21 for a user side refrigerant cycle H is operated and the refrigerant cooled by second auxiliary heat exchangers 19a and 19b (by way of an on/off valve 20) which heat exchanges with the first heat exchangers 18a and 18b, is transferred into rooms 22a and 22b, thereby carrying out cooling operation. In this manner, the heat source side refrigerant cycle is separated from the user side refrigerating cycle so that the configuration of the heat side refrigerating cycle may not be subjected to any change all the time. It is, therefore, possible to minimize a drop in capacity, even if the length or height of a communication pipe is increased.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a refrigerant cycle for a multi-room heating and cooling system.

BACKGROUND ART Page 2 Conventionally, a multi-room heat pump type air-conditioning system having a plurality of refrigerant cycles including a plurality of compressors, a heat source side heat exchanger, etc. in one outdoor unit was constructed as shown in FIG.

In Fig. 2, 1a and 1b are compressors, 2a and 2b are four-way valves, 3a and 3b are heat exchangers on the heat source side, and 4a.

4b is a pressure reducing device for heating, sa and sb are check valves that form passages that bypass the heating pressure reducing devices 4a and 4b during cooling;
6a and eb are accumulators and these are outdoor units) A
It is set in. 7a and 7b are cooling pressure reducing devices, sa
, sb is a check valve that forms a passage that bypasses the cooling pressure reducing devices 7a and 7b during heating, and 9a and 9b are user-side heat exchangers, which are respectively installed in the indoor unit) BC and the outdoor unit) A. Indoor unit B has connecting pipes 10a, 10a
The outdoor unit A and the indoor unit C are connected by continuous pipes 10b and 10b' to form the well-known heat pump refrigerant cycle b, and each refrigerant cycle It is also possible to operate independently.

Page 3 Problems to be Solved by the Invention However, in the above configuration, the capacity of each refrigerant cycle is always constant, and there is a problem that the capacity cannot be controlled. However, if the length and height of the connecting pipe between the outdoor unit and the indoor unit become large, the capacity will decrease due to pressure loss in this connecting pipe, and the amount of refrigerant sealed in the refrigerant cycle will be large, and liquid compression There is a greater risk of damage to the compressor due to

Furthermore, there is a problem in that the capacity of each indoor unit varies depending on the length of the connecting pipe of each refrigerant cycle.

In addition, connecting pipes between the outdoor unit and each indoor unit are required for each refrigerant cycle, and there is also the problem that piping work is expensive.

In view of the above-mentioned problems, the present invention provides a multi-room air-conditioning and heating system that has less capacity drop with long piping, enables efficient capacity control operation, and reduces piping work.

Means for Solving the Problems In order to solve the above-mentioned problems, the multi-room air conditioning system of the present invention includes a plurality of user-side refrigerant cycles that are integrally formed with first auxiliary heat exchangers of a plurality of heat source-side refrigerant cycles to exchange heat. An on-off valve is provided in series for all but one of the plurality of second auxiliary heat exchangers, and a series piping consisting of the second auxiliary heat exchanger and the on-off valve and piping for only the second auxiliary heat exchanger are provided in parallel. , refrigerant conveyance equipment.

It has a configuration in which it has a usage-side refrigerant cycle consisting of a plurality of usage-side heat exchangers.

Function The present invention uses the above-described configuration to exchange heat between the heat source side and the user side refrigerant cycle with the auxiliary heat exchanger, and circulate the heat exchanged with the refrigerant conveying device for use. The degree of increase in loss is small, and the degree of deterioration of capacity can be reduced.

In addition, since the user-side refrigerant cycle having multiple heat source-side refrigerant cycles and multiple user-side heat exchangers is connected via an auxiliary heat exchanger, the number of operating user-side heat exchangers in the user-side refrigerant cycle can be reduced. If the amount is low, capacity control operation can be performed in which only the auxiliary heat exchanger and the heat source side refrigerant cycle are operated without the on-off valves connected in series.

EXAMPLE Hereinafter, a multi-room air conditioning system according to an example of the present invention will be described with reference to the drawings. In FIG. 1, 11a, 11
b is a compressor, 12a, 12b are four-way valves, 1sa, 1sb
is a heat source side heat exchanger, 14a.

14b is a pressure reducing device for heating, 1esa and 15b are check valves that form passages that bypass the heating pressure reducing devices 14a and 14b during cooling, 1aa and 1eb are pressure reducing devices for cooling, and 17a and 17b are pressure reducing devices for heating and cooling. Devices 16a, 16
check valves 18 each forming a passage bypassing b.
a, 1sb are first auxiliary heat exchangers that absorb heat during cooling and radiate heat during heating; these are connected to form heat source side refrigerant cycles Da and Db, respectively.

Here, the first auxiliary heat exchangers 18a and 18b are each integrally formed with a second auxiliary heat exchanger 19a for heat exchange.
, 19b are provided, and only the second auxiliary heat exchanger 19a is provided with an on-off valve 20 in series, and the second auxiliary heat exchanger 19a and on-off valve 2Q and the second auxiliary heat exchanger 19b are provided in parallel. The refrigerant conveying device 21 is connected to form an outdoor unit E. The indoor units F and G are provided with user-side heat exchangers 22a and 22b, and are connected to the outdoor unit E through connecting pipes 23 and 24. This connecting pipe j3, 24. Indoor unit F, G
, the second auxiliary heat exchanger 19a provided in the outdoor unit E
.

19b and the refrigerant transport device 21 are connected to form a user refrigerant cycle H.

Further, X is a throttling device that creates a pressure difference, and Y is a valve that prevents the inflow of refrigerant.

The operation of the multi-room heating and cooling system configured as described above will be described below.

During cooling operation, high-temperature, high-pressure gas discharged from the compressors 11a and 11b passes through four-way valves 12a and 12b, heat-radiates and liquefies in heat source-side heat exchangers 13a and 13b, and passes through check valves 16a and 16b to a cooling pressure reducing device. 16a.

The refrigerant is depressurized at 16b, endothermically evaporated at first auxiliary heat exchangers 18a and 18b, and returns to the four-way valves 12a and 12b to the compressor 7 pages 11a and 11b, forming a refrigerant cycle. At this time, the refrigerant transfer device 21 of the user-side refrigerant cycle H is in operation, and the second auxiliary heat exchanger 19a (via the on-off valve 2o) and 19b exchange heat with the first auxiliary heat exchanger 18a and 18b. The refrigerant is sent to the indoor rooms 22a and 22b for cooling operation.

On the other hand, during heating operation, the high-temperature, high-pressure gas discharged from the compressors 11a and 11b passes through the four-way valves 12a and 12b, and is liquefied by heat dissipation in the first auxiliary heat exchanger, and is then connected to the check valve 17a.

1, the pressure is reduced by the heating pressure reducing devices 14a and 14b, endothermic evaporation occurs in the heat source side heat exchangers 13a and 13b, and the compressor 11a is passed through the four-way valves 12a and 12b.

The refrigerant cycle returns to step 11b.

At this time, the refrigerant cycle H on the user side is circulated by the refrigerant conveying device 21, and the refrigerant is circulated through the first auxiliary heat exchanger 18a, 18b.
The refrigerant superheated in the second auxiliary heat exchangers 19a and 19b, which exchanges heat with the auxiliary heat exchangers 19a and 19b, is sent to the indoor units 22a and 22b through the on-off valve 2o for heating operation.

During cooling operation under capacity control, high-temperature, high-pressure gas discharged from the compressor 11b passes through the four-way valve 12a to the heat source side heat exchanger 13b.
The heat dissipates into liquid and passes through the check valve 15b to the cooling pressure reducing device 16.
It becomes a refrigerant cycle in which the pressure is reduced in step b, endothermic evaporation occurs in the first auxiliary heat exchanger 18b, and the refrigerant returns to the compressor 11b through the four-way valve 12b. At this time, the refrigerant transfer device 21 of the user-side refrigerant cycle H is operated and the on-off valve 2o is closed, so that cooling is performed only in the second auxiliary heat exchanger 19b, which exchanges heat with the first auxiliary heat exchanger 18b. The air is sent to the indoor rooms 22a and 22b for cooling operation.

On the other hand, during heating operation under capacity control, the high-temperature, high-pressure gas discharged from the compressor 11b passes through the four-way valve 12b, liquefies heat in the first auxiliary heat exchanger, passes through the check valve 17b, and passes through the heating pressure reducing device 1.
4b, and is endothermically evaporated in the heat source side heat exchanger 13b.
The refrigerant cycle returns from the four-way valve 12b to the compressor 11b.

At this time, the refrigerant cycle H on the user side is circulated by the refrigerant conveying device 21, and the on-off valve 20 is closed, so the first
Second auxiliary heat exchanger 1 that exchanges heat with auxiliary heat exchanger 18b
The refrigerant superheated in room 9b is sent to indoor units 22a and 22b for heating operation.

As described above, according to this embodiment, since the heat source side refrigerant cycle and the user side refrigerant cycle are separated, the configuration of the heat source side refrigerant cycle does not change at all times, so even if the length and height of the connecting pipe increases, There is little reduction in capacity, and the amount of refrigerant charged in the heat source side refrigerant cycle is small and will not increase, so there is no risk of damage due to liquid compression in the compressor. In addition, since there is one user-side refrigerant cycle for each heat source-side refrigerant cycle, capacity control is possible by stopping the operation of each heat source-side refrigerant cycle. Since they are installed in parallel, the refrigerant flows only to the auxiliary heat exchanger of each user-side refrigerant cycle corresponding to each heat source-side refrigerant cycle, so there is no heat loss in the stop-side auxiliary heat exchanger like in the case of series. This prevents the refrigerant transport device from being loaded due to pressure loss and reducing the flow rate of the refrigerant cycle on the user side, thereby enabling efficient capacity control operation.

1o9-Also, by limiting the number of auxiliary heat exchangers to be used during capacity control operation, it is possible to omit the on-off valve that prevents the flow of refrigerant when the operation is stopped, making it possible to provide a simple structure and low cost. .

Effects of the Invention As described above, the present invention provides a plurality of heat source side refrigerant cycles formed by connecting a compressor, a heat source side heat exchanger, and a first auxiliary heat exchanger in an annular manner, and a plurality of first auxiliary heat exchangers integrated with each other. a plurality of second auxiliary heat exchangers each having an on-off valve except one for heat exchange; a second auxiliary heat exchanger having no on-off valve; and a second auxiliary heat exchanger having an on-off valve. By providing a refrigerant transport device and a user-side refrigerant cycle having multiple user-side heat exchangers, the length and height of the heat source-side heat exchanger and the user-side heat exchanger become larger. However, there is little reduction in capacity due to pressure loss, and the amount of refrigerant sealed in the heat source side refrigerant cycle does not increase, so there is no risk of damage due to liquid compression in the compressor. In addition, capacity control is possible for one user-side refrigerant cycle for multiple heat source-side refrigerant cycles. Since the refrigerant is installed in parallel, the refrigerant flows to the second auxiliary heat exchanger on the stop side and causes heat loss, which is the case when the refrigerant is connected in series.It also causes pressure loss and reduces the capacity of the refrigerant cycle on the user side. In addition to enabling energy-saving operation, the number of pipes in the user-side refrigerant cycle is reduced, which has the effect of reducing piping work and piping space. Furthermore, by limiting the heat source side refrigerant cycle that is operated during the capacity control operation, at least one on-off valve in the user side refrigerant cycle is not required, resulting in a simple configuration and low cost.

[Brief explanation of drawings]

FIG. 1 is a refrigerant cycle diagram of a multi-room air conditioning system according to an embodiment of the present invention, and FIG. 2 is a refrigerant cycle diagram of a conventional multi-room air conditioning system. 11 a, 11 b-----Compressor, 13a,
1 sb---Heat source side heat exchanger, 18a, 18
b...First auxiliary heat exchanger, 19a, 19b...
...Second auxiliary heat exchanger, 2o...Opening/closing valve,
Da, Db...Heat source side refrigerant cycle, 21 ・
...Refrigerant conveyance device, 22a, 22b...Use side heat exchanger, H...Use side refrigerant cycle.

Claims (1)

[Claims] A plurality of heat source side refrigerant cycles formed by connecting a compressor, a heat source side heat exchanger, a pressure reducing device, and a first auxiliary heat exchanger in an annular manner are integrally formed with the plurality of first auxiliary heat exchangers, and each a plurality of second auxiliary heat exchangers and a refrigerant conveyance device to be exchanged;
a user-side refrigerant cycle having a plurality of user-side heat exchangers, and all but one of the plurality of second auxiliary heat exchangers are provided with on-off valves in series, and the second auxiliary heat exchanger and the on-off valve are provided in series. A multi-room air conditioning/heating system characterized in that a plurality of series circuits each consisting of valves and one second auxiliary heat exchanger without an on-off valve are provided in parallel.