JPS6246781B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION An object of the present invention is to provide a heat pump device that is highly efficient and energy-saving by using a non-azeotropic mixed refrigerant.

BACKGROUND ART Conventionally, there is a well-known technique for recovering waste heat energy such as domestic heat waste heat, solar heat, combustion heat, etc. using an evaporator of a heat pump device. In addition, due to its characteristics, such waste heat energy tends to be insufficient in calorific value even at high temperatures, and is also intermittent, so in order to use it in conjunction with heat recovery from the outside air, it is collected by two evaporators in series or in parallel. The techniques are also known.

However, in such known technology, a single refrigerant is used in a refrigeration cycle using one compressor, and the evaporation temperature in the evaporator is constant, and the constant evaporation temperature is equal to the exhaust heat energy. The temperature level will always be lower than the lower of the temperature level of the outside air and the temperature level of the outside air. Therefore, the current situation is that the evaporator simply becomes overheated or the cycle is switched to a higher temperature level, and the cycle efficiency is not necessarily improved.

The present invention aims to solve the above-described drawbacks of the prior art by using a non-azeotropic refrigerant mixture in a refrigeration cycle using one compressor and a plurality of evaporators. In other words, multiple evaporators with the same evaporation pressure but different temperature levels are manufactured, and in response to multiple heat sources with different temperature levels, an evaporator with a high evaporation temperature is created for a heat source with a high temperature level. exchange heat with
By exchanging heat with a low-temperature heat source using an evaporator with a low evaporation temperature, the system recovers heat from multiple heat sources, reduces compressor input compared to conventional technology, and achieves high efficiency. It enables energy saving, and has one compressor that uses a non-azeotropic mixed refrigerant. At the condenser outlet, a liquid phase component containing more high-boiling point refrigerant and an air containing more low-boiling point refrigerant are used. A gas-liquid separator is provided to separate the phase components, and a first evaporator is provided to exchange heat with outside air after the component containing more low-boiling point refrigerant is liquefied and expanded. It is characterized by the provision of a second evaporator that exchanges heat with a heat source at a higher temperature level than the outside air.

The configuration of the heat pump device of the present invention will be explained below based on the drawings. FIG. 1 shows an embodiment in which the heat pump device of the present invention is applied to a heat pump heating device that uses outside air and other heat sources. 1 is a compressor, 2
is a condenser, and 3 is a gas-liquid separator. When using a non-azeotropic mixed refrigerant, the liquid phase side contains more high-boiling point refrigerant, and the gas phase side contains more low-boiling point refrigerant. . 4 is a throttle device for the liquid phase component separated by the gas-liquid separator 3; 5 is a mixed refrigerant whose temperature has been lowered by the throttle device 4 in order to liquefy the gas phase component separated by the gas-liquid separator 3; 6 is a throttling device for the component containing more low boiling point refrigerant. 7 is an evaporator for the component containing more low boiling point refrigerant, 8 is the evaporator for the component containing more high boiling point refrigerant, 9 is both evaporator 7, 8
This is an accumulator that combines and stores refrigerant from the compressor 1, and its outlet is connected to the suction port of the compressor 1. 10 is a fan for exchanging heat between the indoor air and the refrigerant flowing through the condenser 2, 11 is a fan for exchanging heat between the outside air and the refrigerant flowing through the evaporator 7, and 12 is a domestic exhaust heat, solar heat, combustion heat. A carrier fluid such as water and an evaporator 8 that recover waste heat energy such as
This is a conveyor pipe for heat exchange of the refrigerant flowing through the pipe.

In this way, since the evaporators 7 and 8 communicate with the compressor 1 through the accumulator 9, they have the same evaporation pressure, so the refrigerant flowing through the evaporator 8 contains more high-boiling point refrigerant. Therefore, it is possible to maintain the temperature at a higher temperature than the evaporator 7 which contains a larger amount of low boiling point refrigerant. Therefore, if the condensation temperature in the condenser 2 and the evaporation temperature in the evaporator 7 are made approximately the same as the condensation temperature and evaporation temperature in a conventional refrigeration cycle using a single refrigerant, the exhaust heat energy at a higher temperature level is converted into heat. Since the evaporation temperature of the evaporator 8 for recovery is higher than the evaporation temperature of the evaporator 7, it is possible to reduce the input to the compressor 1.

The above action will be explained using the graph of low boiling point refrigerant concentration versus temperature at constant pressure shown in FIG. In addition,
In FIG. 2, graphs of constant condensation pressure and evaporation pressure are arranged vertically for convenience of explanation. Points (a) to (k) shown in FIG. 2 correspond to the pressure, temperature, and concentration at points (a) to (k) in FIG. 1. That is, the period between point (a) and point (b) is the condensation process in the condenser 2, and since a non-azeotropic refrigerant mixture 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. The process between point (d) and point (e) is the throttling process in the throttling device 4, which brings about a pressure drop from the condensing pressure to the evaporation pressure, as well as a temperature drop. Between points (e) and (f) and between points (c) and (g), heat exchange occurs between a component containing more high boiling point refrigerant and a component containing more low boiling point refrigerant in heat exchanger 5. The heat exchanger 5 is constructed so that the refrigerant is completely liquefied at point (g). The process between points (g) and (h) is the throttling process in the throttling device 6, which also causes a pressure drop from condensing pressure to evaporation pressure, and the refrigerant at point (f) contains more high-boiling point refrigerant. component, it is easy to configure the temperature at point (f) to be higher than the temperature at point (h). Between points (h) and (i) and between points (f) and (j) are evaporators 7 and 8, respectively.
In the case of non-azeotropic mixed refrigerants, a temperature rise is observed. (k) points are evaporators 7 and 8
This is the state point at the outlet of the accumulator 9 where the refrigerant from
is compressed from to point (a) (condensation pressure). Through this change in the state of the mixed refrigerant, it is possible to provide the above-described highly efficient and energy-saving heat pump heating device.

As can be seen from Figure 2, when a non-azeotropic refrigerant mixture is used, the temperature decreases during the condensation process.
Since a temperature rise is observed during the evaporation process, it is preferable that the condenser 2 and evaporators 7 and 8 have counterflow to the heat source, and the heat exchanger 5 should also have counterflow.

As explained above, the heat pump device of the present invention includes:
Using a non-azeotropic mixed refrigerant, it is separated into a component containing more high-boiling point refrigerant and a component containing more low-boiling point refrigerant, and the component containing more low-boiling point refrigerant is used in an evaporator as a low-heat source such as outside air. By exchanging heat, the component containing a larger amount of high boiling point refrigerant is configured to exchange heat with a heat source at a higher temperature level in the second evaporator, making it possible to provide a highly efficient and energy-saving heat pump device. It is something.

Although omitted in the examples, devices equipped with a heat exchanger for supercooling the inlet of the throttling device and heat pump devices used in water heaters, etc. are also included in the present invention. As the heat source, exhaust heat energy having a higher temperature level than outside air, such as household waste heat, solar heat, and combustion heat, is suitable.

[Brief explanation of the drawing]

FIG. 1 is a configuration diagram showing one embodiment of a heat pump device of the present invention, and FIG. 2 is a graph of low boiling point refrigerant concentration versus temperature for explaining each state point in FIG. 1. 1... Compressor, 2... Condenser, 3... Gas-liquid separator, 4... Throttle device, 5... Heat exchanger, 6... Throttle device, 7, 8... Evaporator.

Claims (1)

[Claims] 1. One compressor using a non-azeotropic mixed refrigerant, with a liquid phase component containing more high boiling point refrigerant and a gas phase component containing more low boiling point refrigerant at the condenser outlet. The first stage is equipped with a gas-liquid separator that separates the component containing a larger amount of low-boiling refrigerant into a gas-liquid separator that exchanges heat with outside air after liquefaction and expansion.
A heat pump device is provided with a second evaporator that exchanges heat with a heat source having a higher temperature level than outside air after expanding a component containing a larger amount of high boiling point refrigerant. 2. The heat pump device according to claim 1, wherein the gas phase component containing a larger amount of low boiling point refrigerant is liquefied by heat exchange with the expanded component containing a larger amount of high boiling point refrigerant.