JPS58104467A - Heat pump device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a heat pump device using a non-azeotropic mixed refrigerant that, in combination with improvements in the refrigeration cycle, achieves high efficiency and makes it possible to obtain a lower temperature. The purpose is to provide

Conventionally, in a heat pump device using a non-azeotropic mixed refrigerant, in a refrigeration cycle in which a compressor, a condenser, a throttle device, an evaporator, etc. are simply connected, the heated fluid and the heat source are connected to the condenser and evaporator. It is a known technique to reduce the irreversible loss in the heat exchange process by causing the fluid to be cooled and the non-azeotropic mixed refrigerant to exchange heat in countercurrent flows.

However, in such a heat pump device, when the purpose is to obtain a higher exit temperature of the fluid to be heated and a lower exit temperature of the fluid to be cooled, although the irreversible loss in the heat exchange process is reduced, the compressor The compression ratio becomes excessive, and therefore the compressor input increases, making it difficult to ensure sufficiently high efficiency. For example, when the fluid to be heated is used for hot water supply and the fluid to be cooled is used for cooling, the exit temperature of the heated fluid is preferably 70 to 80°C, and the exit temperature of the cooled fluid is preferably 6 to 16°C, but both If an attempt is made to simultaneously obtain an outlet temperature of , the compressor input will be considerably increased. Even if an attempt is made to reduce irreversible loss in the heat exchange process using a non-azeotropic mixed refrigerant, if the inlet temperature of the heated fluid is 70 to 30°C, approximately 1 Odo
It is necessary to obtain a temperature difference of about 150 deg, and if you try to reduce the irreversible loss with a non-azeotropic mixed refrigerant,
Although it is desirable to mix refrigerants with boiling point differences of This is extremely difficult due to the critical temperature, critical pressure, specific heat, etc., and the effect of reducing irreversible loss is also reduced.

The present invention eliminates the drawbacks of the above-mentioned insulating heat pump device, and will be described in detail below along with examples. FIG. 1 shows an embodiment of a heat pump device using a non-azeotropic mixed refrigerant according to the present invention, and 1 is a compressor.

2 is a first condenser, 3 is a gas-liquid separator, and when a non-azeotropic mixed refrigerant is used, the liquid phase side contains more high boiling point refrigerant and the gas phase side contains more low boiling point refrigerant. Become. 4 is a second condenser for liquefying the gas phase components; 6 and 6 are throttle devices; 7 and 8 are first and second evaporators for components containing more low-boiling point refrigerant and higher boiling point refrigerant, respectively; 9 is a second condenser for liquefying the gas phase component; Both evaporators 7
．． This is an achievator that combines and stores 8 refrigerants, and its output is connected to the suction port of the compressor 1.

Here, the fluid to be heated exchanges heat in the condensers 2 and 4 in the order of the second condenser 4 and the first condenser 2 so as to have counterflow in each condenser, and the fluid to be cooled is in the evaporator 7,
8 is characterized in that heat is exchanged in the order of the second evaporator 8 and the first evaporator 7 so as to form counterflows in each evaporator.

Next, the operation of the above-described embodiment will be explained with reference to the graph of low boiling point refrigerant concentration versus temperature at constant pressure shown in FIG. In FIG. 2, for convenience of explanation, graphs of constant condensation pressure and evaporation pressure are arranged vertically. Points 8 to 1 shown on the top of FIG.
It corresponds to the pressure, temperature, and concentration at point −j. That is, points a-b are the condensation process of the first condenser 2, and since a non-azeotropic mixed refrigerant is used, a decrease in temperature is observed.

Points C and d are state points of the gas phase and liquid phase separated by the gas-liquid separator 3. Points a-e are the condensation process of the second condenser 4, which contains more low-boiling point refrigerant, so the temperature decreases at a lower temperature level even though the condensation pressure is the same as that of the first condenser 2. It happens.

Points e-f and ci-c represent the inlet and outlet, respectively, of the throttling device 6.6, which can bring about a temperature drop as well as a pressure drop from the condensing pressure to the evaporation pressure. point f-h
Point g-i and point g-i are the evaporation process of evaporator 7°8, and a temperature rise is observed in contrast to condensers 2 and 4, but point f-
Since h contains more low-boiling refrigerant, it is easier to evaporate at lower temperature levels. Point j represents the state point at the outlet of the accumulator 9, where the refrigerant from the evaporator 7°8 is mixed, and is drawn into the compressor 1 in the state of superheated vapor, in which the refrigerant flows from point j (evaporation pressure) to point a. (condensation pressure).

Therefore, one of the features of the present invention is that the fluid to be heated flows between points a-c-b-a so that the fluid to be heated flows counter-currently to the non-azeotropic mixed refrigerant as shown by the broken line in the upper part of FIG. By sequentially exchanging heat with the refrigerant, it is possible to reduce the temperature difference between the fluid to be heated and the refrigerant over a wide temperature range, thereby reducing irreversible loss. Especially point C-
Since heat is effectively recovered from the condensation process of e, there is no need to use a combination of refrigerants with a large boiling point difference as in the heat pump water heater described above, and a combination of refrigerants with a boiling point difference of about 30 to 1100 de is suitable. , it will be easier to find these combinations among fluorocarbons.

In addition, as shown by the broken line at the bottom of FIG.
By exchanging heat with the refrigerant in the order of −f, irreversible loss can be reduced as in the condensation process. Especially when using hot water supply and cooling at the same time as mentioned above,
Compared to a conventional simple refrigeration cycle, when the compression ratio is the same, a lower temperature can be obtained by exchanging heat with the lower temperature level at point f - h, and conversely, when obtaining a lower temperature at the same temperature level, the compression ratio is reduced, making it possible to maintain high-temperature operation.

Next, a different example of the present invention is shown in Figure 3.

In FIG. 3, 10 to 16 and 18 are components having the same functions as 1 to 7 and 9 in the embodiment in FIG. 1, respectively.The embodiment in FIG. The first evaporator 7 and the second evaporator 8 for high-boiling components are arranged in parallel and merge into the accumulator 9, whereas in FIG. to join the device 16 and the second evaporator 17 in the middle,
The purpose of the second evaporator 17 is to evaporate the non-azeotropic refrigerant mixture, which has its original composition. In the embodiment shown in FIG. 3 as well, the heated fluid is supplied to the second condenser 13 and the first condenser 1
1 and in each condenser so that the flow is counter-current, and the fluid to be cooled is heat-exchanged in the order of the second evaporator 17 and the first evaporator 16 so that the flow is counter-current in each evaporator. Therefore, the same effect as the embodiment shown in FIG. 1 can be expected. In particular, in the embodiment shown in FIG. It is possible to exchange heat between the evaporative refrigerant, which changes in a narrow overall temperature range, and the stream/body to be cooled.

In the embodiments shown in FIGS. 1 and 3, the basic configuration is shown. For example, in order to subcool the refrigerant flowing into the expansion devices 6, 6 and the expansion devices 14 and 16, One equipped with a heat exchanger (not shown) or a four-way valve (
The present invention also includes a heat pump device that is devised to switch the cycle by providing a heat pump (not shown), and a heat pump device that integrates a single condenser and a natural generator. Examples of practical applications include heat pump hot water supply equipment and hot water supply cooling equipment, but when used at high temperature levels such as hot water supply, from the viewpoint of equipment pressure resistance, it is recommended to use non-azeotropic mixed refrigerant combinations. , chlorodifluoromethane (Freon 22. Boiling point -41°C) and Freon with a higher boiling point, preferably with a boiling point difference of about 30 to 100 degrees, and in order to avoid negative pressure in the equipment, preferably about 40 to 8 degrees Freon with a boiling point difference of ゜dog, specifically,
1,2-dichlorotetrafluoroethane (Freon 114
．． boiling point 4℃), dichlorofluoromethane (Freon 21
゜boiling point 9℃), trichlorofluoromethane (Freon 11
, boiling point 24°C), etc. are suitable.

0 As explained above, the heat pump device of the present invention includes a compressor, a first condenser, a gas-liquid separator, a second condenser, a throttle device, a first and a first condenser, in a refrigeration cycle using a non-azeotropic mixed refrigerant. 2
It consists of an evaporator, etc., and a component containing a large amount of low boiling point refrigerant separated by a gas-liquid separator flows into the second condenser and the first evaporator, and the fluid to be heated flows between the second condenser and the first condenser. By configuring the cooling fluid to be heat exchanged in order and in counterflow in each condenser, and for the fluid to be cooled to be heat exchanged in order in the second evaporator and the first evaporator and in counterflow in each evaporator. In addition to being highly efficient, it is also possible to operate at both high and low temperatures, making it easier to combine non-azeotropic refrigerants especially when the fluid to be heated is used at high temperature levels such as hot water supply. It also has the following effects.

[Brief explanation of the drawing]

FIG. 1 is a circuit configuration diagram of an embodiment of a heat pump device according to an embodiment of the present invention, and FIG. 2 is a characteristic diagram of low boiling point refrigerant concentration versus temperature for explaining each state point of the heat pump device. FIG. 3 is a circuit diagram of a heat pump device according to a different embodiment of the present invention. 1,1o... Compressor, 2,11... ・First condenser, 3.12... Gas-liquid separator, 4.13...
...Second condenser, 5,6,14.15... Throttle device, 716 ...First evaporator, 8,17...
...Second evaporator. Name of agent: Patent attorney Toshio Nakao and one other person...
] 11 Figure 2 侭麊Se, ) 庺泉儂廣

Claims (1)

[Claims] (1) At least a compressor using a non-azeotropic mixed refrigerant. A first condenser, a gas-liquid separator, a second condenser, and a throttling device. A refrigeration cycle is formed by the first and second evaporators, and the second evaporator
A component containing a large amount of low boiling point refrigerant separated by a gas-liquid separator is introduced into the condenser and the first evaporator, and the fluid to be heated is passed through the second condenser and the first condenser in that order and facing each other in each condenser. A heat pump device in which the fluid to be cooled is supplied to the second evaporator and the first evaporator in order, and heat is exchanged in each evaporator so that the fluid flows counter-currently. (2) The heat pump device according to claim 1, wherein a component containing a large amount of high-boiling refrigerant separated by a gas-liquid separator flows into the second evaporator. (3) The heat pump according to claim 1, wherein the low boiling point components flowing through the first evaporator and the high boiling point components separated and depressurized by the gas-liquid separator are combined and flowed into the second evaporator. Device. (4) The heat pump device according to claim 1, 2, or 3, wherein at least one of the first and second condensers or the first and second evaporators is integrated. (6) The heat pump device according to any one of claims 1 to 4, wherein chlorodifluoromethane and a second fluorocarbon having a boiling point higher than that of chlorodifluoromethane are mixed as a non-azeotropic refrigerant combination.