JPS62272040A - Multiroom heating and cooling device - Google Patents

Abstract

PURPOSE:To obtain a constantly stable high performance of the title device and to improve the reliability thereof by providing a heat supply side coolant cycle, and a utilization side coolant cycle consisting of a second auxiliary heat exchanger formed integrally with a first auxiliary heat exchanger, a coolant conveyor, and a plurality of utilization side heat exchangers. CONSTITUTION:At the time of a space cooling operation, in a heat supply side coolant cycle, a high-temperature and high-pressure gas passes through a four-way valve 12, radiates heat at a heat supply side heat exchanger 13 and is condensed and liquefied. Then, the gas passes through a check valve 16 and is reduced in its pressure at a space cooling expansion valve 14, being evaporated in a first auxiliary heat exchanger 18, passing through a four way valve 12 and being circulated to a compressor 12. In this case, a second auxiliary heat exchanger 19 of the utilization coolant cycle is heat exchanged with the first auxiliary heat exchanger 18, the gas coolant within the utilization side coolant cycle is cooled and liquefied, passing a coolant amount adjusting tank 20 and being sent to a coolant conveyor 21. Then, the gas coolant is sent to utilization side heat exchangers 22a and 22b via connecting pipelines i and j, and is absorbed of its heat and evaporated, and then gasified and via connecting pipelines i' and j' and is circulated to the second auxiliary heat exchanger 19. Thus it is possible to prevent damages of the compressor due to characteristic lowering of the compressor, the liquid compression, poor recurrence of compressor oil.

Description

Detailed Description of the Invention 3. Detailed Description of the Invention Field of Industrial Application The present invention relates to a refrigerant cycle for a multi-room air conditioning system.

Conventional technology The refrigerant cycle of conventional multi-room heat pump air conditioning systems is as follows:
It is configured as shown in FIG. 1 is a compressor, 2 is a four-way valve, 3 is a heat source side heat exchanger, 4 is a pressure reducing device for heating, 5 is a reverse valve that forms a passage that bypasses the pressure reducing device 4 for heating during cooling, 6a and eb are cooling devices 7a and 7b are pressure reducing devices for air conditioning during heating, check valves forming passages that bypass 6a and 6b, 8a and 8b are user side heat exchangers, and 9 is an accumulator; , indoor unit) b, c, and connecting pipes d, d'
.

e and e', and constitute the entire well-known refrigerant cycle.

Problems to be Solved by the Invention However, with the above configuration, if the connecting piping between the outdoor unit and the indoor unit becomes long, the amount of refrigerant sealed in the refrigerant/stem increases, and there is a risk of damage to the compressor due to liquid compression. There is a problem in that the capacity is greatly reduced due to pressure loss in the piping. In addition, stopping the operation of the indoor unit requires refrigerant control using a solenoid valve, and controlling the capacity of the indoor unit requires controlling the capacity of the compressor and controlling the pressure reducing device, creating a complicated method. had.

Unfortunately, there was a problem in that installation work had to be restricted because there was a large imbalance in capacity due to the length and height of the piping between indoor units.

Means for Solving the Problems In order to solve the above problems, the multi-room air conditioning system of the present invention comprises a compressor, a heat source side heat exchanger, a pressure reducing device and a first auxiliary heat exchanger connected in a ring shape. A heat source side refrigerant cycle, a second auxiliary heat exchanger that is formed integrally with the first auxiliary heat exchanger and exchanges heat, a refrigerant conveyance device, and a user side refrigerant cycle that includes a plurality of user side heat exchangers. It is.

Effect of the present invention Due to the above-described configuration, the configuration of the heat source side refrigerant cycle does not change, so even if the length or height difference between the heat source side heat exchanger or compressor and the user side heat exchanger becomes large, the characteristics of the compressor remain unchanged. Since the amount of refrigerant sealed in the heat source side refrigerant cycle does not decrease, damage to the pressure MvA due to liquid compression or regression failure of refrigerating machine oil can be prevented.

Moreover, there is no unbalance in capacity due to piping length or height differences between the heat exchangers on the user side, and the capacity control of the indoor unit can be easily adjusted by adjusting the air volume of the indoor unit.

EXAMPLE Hereinafter, a heating and cooling system according to an example of the present invention will be described with reference to the drawings. FIG. 1 shows a refrigerant cycle of a multi-room air conditioning system according to an embodiment of the present invention. 1st
In the figure, 11 is a compressor, 12 is a four-way valve, 13 is a heat source side heat exchanger, 14 is a cooling pressure reducing device, 15 is a heating pressure reducing device, and 16 is a check that closes the cooling pressure reducing device 14 during heating. The valve 17 is a check valve that closes the pressure reducing device 15 for heating during cooling, and the first auxiliary heat exchanger 18 is connected in an annular manner to form a heat source side refrigerant cycle. A second auxiliary heat exchanger 19 is integrally formed to exchange heat with the first auxiliary heat exchanger 18. Reference numeral 20 is a refrigerant amount adjustment tank that adjusts refrigeration dissipation during cooling and heating. 21 is a refrigerant transport device that has a reversible characteristic in which the flow direction of the refrigerant is opposite during cooling and heating.
These are housed in the outdoor unit f. l.

" + ] + ]', 22a, 22b are user-side heat exchangers, which are stored in the indoor unit F q + h and connected to the outdoor unit F q + h through connection piping. The second auxiliary heat exchanger 19 and the amount of refrigerant Adjustment tank 20. Refrigerant conveyance device 21° user side heat exchangers 22a, 22b and connection piping i.

" + ] + ]' are connected in a ring to form a user-side refrigerant cycle.

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

During cooling operation, the refrigerant cycle is indicated by the solid line in the figure. In the refrigerant cycle on the heat source side, the high-temperature, high-pressure gas from the compressor 11 passes through the four-way valve 12, dissipates heat in the heat exchanger 13 on the heat source side, becomes 1-condensation liquefaction, and reverses the cycle. It passes through the stop valve 16 for cooling, is depressurized by the expansion valve 14, is evaporated in the first auxiliary heat exchanger 18, and is circulated through the four-way valve 12 to the compressor 12.

At this time, the second auxiliary heat exchanger 19 of the user-side refrigerant cycle and the first auxiliary heat exchanger 18 exchange heat, and the gas refrigerant in the user-side refrigerant cycle is cooled and liquefied, and passes through the refrigerant amount adjustment tank 20. The refrigerant is sent to the refrigerant conveying device 21, and by this refrigerant conveying device 21, it is sent to the user-side heat exchangers 22a and 22b through the connecting piping '+], where it is endothermically evaporated, gasified, and transferred to the connecting piping 1'.

j' to the second auxiliary heat exchanger 19.

On the other hand, during heating operation, the refrigerant cycle is indicated by the broken line in the figure, and in the heat source side refrigerant cycle, the high-temperature, high-pressure refrigerant from the compressor 11 is sent from the four-way valve 12 to the first auxiliary heat exchanger 18, radiates heat and condenses. It is liquefied, the pressure is reduced by the heating pressure reducing device 16 from the check valve 17, and it is endothermically evaporated in the heat source side heat exchanger 13.
It circulates through the four-way valve 12 to the compressor 11. At this time, the second auxiliary heat exchanger 19 of the user-side refrigerant cycle and the first auxiliary heat exchanger 18 exchange heat, and the liquid refrigerant in the user-side refrigerant cycle is heated and gasified, and the connecting pipes 1 / , ] /
The refrigerant is sent to the user-side heat exchanger 22 through heating, radiating heat, liquefied, connecting pipe i+], is sent to the refrigerant conveying device 21, and circulated from the refrigerant amount adjustment tank 2o to the second auxiliary heat exchanger 19. .

As described above, according to this embodiment, the heat source side refrigerant cycle and the user side refrigerant cycle are separated, and the heat source side refrigerant cycle is housed in the outdoor unit and the piping route does not change, so the same stable performance can always be obtained. In addition, since the piping route of the heat source side refrigerant cycle is short, pressure loss in the piping route is significantly reduced, resulting in high performance. In addition, since the amount of refrigerant charged is small and the amount of refrigerant stored in the compressor is small, there is no liquid compression, and the refrigeration oil discharged from the compressor does not stay in the refrigerant cycle and returns to the compressor quickly, improving the reliability of the compressor. Significantly improved. Furthermore, since the amount of refrigerant sealed is small and constant, there is no need for an accumulator. On the other hand, in the user-side refrigerant cycle, the refrigerant is circulated by a refrigerant transport device, so the amount of refrigerant circulation does not decrease significantly even if the connection piping connecting the outdoor unit and indoor unit becomes longer or the height difference becomes larger. Therefore, the restrictions can be significantly relaxed. Further, since the performance of the outdoor unit is separated, it is not affected by the connecting pipes and is always constant, so that the performance of the indoor unit can also be stable and high.

Furthermore, since there is no need for refrigerating machine oil in the user side refrigerant cycle, there is no need for an oil trap in the middle of the gas side connection piping, which simplifies the connection piping work. Furthermore, even when multiple outdoor units 23 are installed as shown in FIG.
4 can be connected with two pipes, making the construction easier and cheaper.

In the embodiment, the cooling pressure reducing device 14 and the heating pressure reducing device 17 of the heat source side refrigerant cycle are separated, but a reversible pressure reducing device such as an electric expansion valve may be used. Further, although the refrigerant transport device 21 of the user-side refrigerant cycle is reversible, two unidirectional refrigerant transport devices may be used. In the embodiment, the refrigerant conveying bag @21 is provided on the liquid pipe, but it may also be provided on the gas side pipe. Further, the refrigerant amount adjustment tank may be provided anywhere in the refrigerant cycle, or may be provided in plural numbers or in plural numbers.

Effects of the Invention As described above, the present invention provides a heat source side refrigerant cycle in which a compressor, a heat source side heat exchanger, a pressure reducing device, and a first auxiliary heat exchanger are connected in an annular manner, and the first auxiliary heat exchanger is integrated with the heat source side refrigerant cycle. The second auxiliary heat exchanger that is formed to exchange heat and the user-side refrigerant cycle, which is formed by connecting the refrigerant transport device and the user-side heat exchanger in an annular manner, are provided separately, so the heat source-side refrigerant cycle has a piping route. Since the refrigerant does not change, the same stable performance can always be obtained, and since the piping route of the heat source side refrigerant cycle is short, pressure loss in the piping route is significantly reduced, resulting in high performance. In addition, the amount of refrigerant charged is reduced, and the amount of refrigerant trapped in the compressor is small, so there is no liquid compression, and the refrigerating machine oil discharged from the compressor does not stay in the refrigerant cycle and returns to the compressor quickly, improving the reliability of the compressor. performance is greatly improved. On the other hand, in the user-side refrigerant cycle, the refrigerant is circulated by a refrigerant conveying device, so even if the distance between the second auxiliary heat exchanger and the user-side heat exchanger is long or the height difference is large, the refrigerant will continue to circulate. Since the amount does not decrease significantly, it has the effect of significantly easing restrictions. Further, since the heat source side refrigerant cycle is separated, the performance is always constant, and therefore the performance of the user side heat converter has the effect of obtaining stable and high performance.

[Brief explanation of the drawing]

FIG. 1 is a refrigerant cycle diagram of an air conditioning system according to an embodiment of the present invention, FIG. 2 is a connection diagram of an indoor unit according to another embodiment of the invention, and FIG. 3 is a refrigerant cycle diagram of a conventional air conditioning system. 13... Heat source side heat exchanger, 18... First auxiliary heat exchanger, 19... Second auxiliary heat exchanger, 2
1... Refrigerant conveyance device, 22... User-side heat exchanger. Name of agent: Patent attorney Toshio Nakao and one other person,
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1II Jyuukohaku 1 Figure 2

Claims (4)

[Claims] (1) A heat source side refrigerant cycle 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 is formed integrally with this first auxiliary heat exchanger to exchange heat. A multi-room air-conditioning/heating system comprising a second auxiliary heat exchanger, a refrigerant conveying device, and a user-side refrigerant cycle having a plurality of user-side heat exchangers. (2) The multi-room air conditioning system according to claim 1, wherein the compressor is equipped with a capacity control compressor. (3) The multi-room air conditioning system according to claim 1, wherein the heat source side refrigerant cycle and the usage side refrigerant cycle use different refrigerants. (4) The multi-room air conditioning system according to claim 1, wherein a stacked heat exchanger is used as the first auxiliary heat exchanger and the second auxiliary heat exchanger.