JPS6218933Y2 - - Google Patents

Description

[Detailed explanation of the idea] The present invention relates to a cooling refrigeration device.

Generally, in a cooling refrigeration system, in order to increase the cooling capacity per unit input, so-called EER, it is necessary to increase the evaporation pressure and reduce the compression ratio of the compressor. For example, when using Freon refrigerant R-22 as the refrigerant, the discharge pressure is generally 19.8
Kg/cm ² abs, suction pressure is 6.0Kg/cm ² abs, and the compression ratio is set to 3.3, but in order to increase this value compared to the EER value in this case, for example, the evaporation pressure is set to a high pressure of 9.3Kg/cm ² abs, and the compression ratio is set to a smaller value than the compression ratio of 3.3.
It needs to be 2.1.

However, if the evaporation pressure is increased from 6.0 to 9.3, the evaporation temperature will also increase from 5℃ to 20℃, reducing the dehumidification ability, resulting in the problem of not being able to provide comfortable cooling. Simply doing so will not provide a fundamental solution.

On the other hand, the device shown in FIG. 3 has been provided as a device that can exhibit dehumidifying ability while increasing the EER value.

That is, this device uses two first and second compressors 21 and 22, one outdoor heat exchanger 23, and two first and second indoor heat exchangers 24 and 25. , the discharge side passages of the two compressors 21 and 22 are joined together and connected to the outdoor heat exchanger 23, and the outlet side passage of the heat exchanger 23 is branched, and one passage is connected to the above-mentioned one through the expansion mechanism 26. First indoor heat exchanger 2
4 is connected to the suction side of the first compressor 21, and the second indoor heat exchanger 25 is connected to the other passage through the expansion mechanism 27 to connect the second compressor 22.
This contact was made to the intake side of the system.

Then, while using the fluorocarbon refrigerant R22, the evaporation pressure of the first indoor heat exchanger 24 in the refrigerant system of the first compressor 21 was set to 6 kg/cm ² abs, and the evaporation temperature was set to a low level that can exhibit sufficient dehumidifying ability. While setting the temperature to, for example, 5° C., the evaporation pressure of the second indoor heat exchanger 25 in the refrigerant system of the second compressor 22 is set to the above-mentioned small value of 2.1, and the EER High pressure that can increase the value of 9.3
Kg/cm ² abs.

Note that 28 is an indoor fan.

However, in the refrigerant system of the second compressor 22, the EER value becomes high, but in the refrigerant system of the first compressor 21, the value of EER becomes high.
The evaporation pressure corresponding to the evaporation temperature of 5℃ in 4 is EER
Therefore, there was a problem that the ^overall EER value could not be made sufficiently high. Furthermore, it is necessary to use two compressors, which increases the initial cost.

However, the present invention was devised to solve the above problems, and the purpose is to have sufficient dehumidification capacity, provide comfortable cooling, and increase the EER value, while also eliminating the need for expensive compressors. It is an object of the present invention to provide an economically advantageous cooling refrigeration device that does not require the use of a single unit and only requires one unit.

That is, the present invention includes one compressor, an outdoor heat exchanger, and two first and second indoor heat exchangers, and a gas-liquid separator is connected to the outlet side of the outdoor heat exchanger. The first gas pipe is connected to the gas area and liquid area of the separator.
a liquid pipe having an expansion mechanism, and a heat exchanger for exchanging heat between the refrigerant flowing through the gas pipe and the liquid pipe, and an outlet side of the heat exchanger connected to the gas pipe, The outlet side of the heat exchanger connected to the inlet side of the first indoor heat exchanger via a second expansion mechanism and connected to the liquid pipe is connected to the suction side of the compressor, and A branch pipe from the pipe is connected to the inlet side of the second heat exchanger via a third expansion mechanism, and is filled with two types of refrigerants having different saturation pressures. .

Embodiments of the refrigeration system of the present invention will be described below based on the drawings.

The one shown in FIG. 1 includes one compressor 1, an outdoor heat exchanger 2, and two first and second indoor heat exchangers 3, 4, and the discharge side of the compressor 1 is connected to the outdoor heat exchanger 2. A gas-liquid separator 5 is connected to the inlet side of the outdoor heat exchanger 2, and a gas pipe 6 is connected to the gas region of the gas-liquid separator 5, and a gas pipe 6 is connected to the liquid region of the gas-liquid separator 5. 1. Liquid pipes 8 each having an expansion mechanism 7 are connected to each other.

A heat exchanger 9 for exchanging heat between the refrigerant flowing through the gas pipe 6 and the liquid pipe 8 is provided, and the heat exchanger 9 is connected to the gas pipe 6 and the liquid pipe 8. Also,
The outlet side of the heat exchanger 9 connected to the gas pipe 6 is
It is connected to the inlet side of the first indoor heat exchanger 3 via the second expansion mechanism 10, and the outlet side of the heat exchanger 9, which is connected to the liquid pipe 8, is connected to the suction side of the compressor 1. . Further, a branch pipe 12 having a third expansion mechanism 11 is provided from a position between the gas-liquid separator 5 and the first expansion mechanism 7 in the liquid pipe 8, and the branch pipe 12 is connected to the second chamber. It is connected to the inlet side of the heat exchanger 4, and the suction sides of the first and second indoor heat exchangers 3, 4 are merged and connected to the suction side of the compressor 1.

In addition, the refrigerant circuit configured as above is filled with two types of refrigerants having different values of saturation pressure corresponding to saturation temperature, and as these refrigerants, the use of fluorocarbon refrigerants R22 and R32 will be explained below. .

Note that 13 is an indoor fan.

However, in the above configuration, the compressor 1
In addition to setting the discharge pressure to 19.8Kg/cm ² abs, the suction pressure set by the expansion mechanism
The pressure is set at 9.3Kg/cm ² abs, which is higher than 6.0Kg/cm ² abs. By the way, the refrigerants R22 and R32
When the saturation pressure is the set pressure 19.8Kg/cm ² abs, the equivalent saturation temperature is 50℃ and 30℃, respectively.
Furthermore, when the saturation pressure is the set pressure 9.3Kg/cm ² abs, the equivalent saturation temperatures are 20°C and 5°C, respectively.

As described above, the discharge pressure of compressor 1 is set to 19.8Kg/cm ²
abs, and the suction pressure of the refrigerant sucked into the compressor 1 is maintained at 9.3Kg/cm ² abs, the discharge gas of the refrigerant R22 is
It condenses and liquefies at ℃ and flows into the liquid region of the gas-liquid separator 5. After flowing out from the separator 5 to the liquid pipe 8, the liquid pipe 8 and the branch pipe 12 are separated, and the pressure is 9.3 Kg/cm ² abs by the first and third expansion mechanisms 7 and 11, respectively.
The pressure is reduced to 20.degree. C. in the heat exchanger 9 and the second indoor heat exchanger 4 at a saturation temperature of 20.degree. C., which corresponds to the pressure, and the cycle is repeated.

On the other hand, the discharge pressure of the discharge gas of refrigerant R32 is
When 19.8Kg/cm ² abs, its equivalent saturation temperature is 30℃
Therefore, it passes through the outdoor heat exchanger 2 at 50° C. without condensing and reaches the gas region of the gas-liquid separator 5. Then, the refrigerant R32 flows out into the gas pipe 6, changes its state in the outdoor heat exchanger 2, and enters the heat exchanger 9 with the refrigerant R22, which has been reduced in pressure to 9.3 Kg/cm ² abs by the expansion mechanism 7. It exchanges heat. In other words, gaseous refrigerant R32 has a pressure of 9.3Kg/cm ²
Equivalent saturation temperature of abs Exchanges heat with refrigerant R22 which evaporates at 20℃, and the pressure is 19.8Kg/cm ² Equivalent saturation temperature of abs
It condenses and liquefies at 30℃. The liquefied refrigerant R32 then reaches a pressure of 9.3 in the second expansion mechanism 10.
The pressure is reduced to Kg/cm ² abs, enters the first indoor heat exchanger 3, is evaporated in the heat exchanger 3 at a saturation temperature of 5° C., and is sucked into the compressor 1, where the cycle is repeated. . Therefore, each of the above refrigerants
Cooling can be performed by the cycle of R22 and R32, and the pressure of the refrigerant R32 in the first heat exchanger 3
Dehumidification can be performed at an evaporation temperature of 5°C, which corresponds to a saturation temperature of 9.3Kg/cm ² abs, and a compression ratio of 2.1 can be achieved.

Next, changes in the state of indoor air will be explained with reference to FIG. That is, if the condition of the indoor air is, for example, a temperature of 30
℃, relative humidity 75%, and absolute humidity 0.020 (Kg/Kg), the indoor air first flows through the second indoor heat exchanger 4 and reaches the saturation line as shown by the thick solid line, resulting in a dew point temperature of 25 After the sensible heat changes to state B of ℃, the temperature decreases along the saturation line, and the sensible heat changes to state C, where the dew point temperature is 24℃, and then the latent heat changes and the absolute humidity decreases.
It decreases slightly by 0.001 (Kg/Kg) to 0.019.

Then, the indoor air that has passed through the second heat exchanger 4 flows through the first indoor heat exchanger 3, so that the air moves from state C to a desired dew point temperature of 20° C. along the saturation line as shown by the thick dotted line. Until state D, sensible heat changes and latent heat changes, and the absolute humidity significantly decreases by 0.004 (Kg/Kg) to 0.015 (Kg/Kg), making it possible to dehumidify as well as air condition.

As mentioned above, hot and humid indoor air is
Cooling can be reliably performed by the first indoor heat exchangers 4 and 3, and dehumidification can be performed mainly by the first indoor heat exchanger 3, thereby providing comfortable cooling.

Also, when performing air conditioning in this way, the discharge pressure of compressor 1 is 19.8Kg/cm ² abs, while the suction pressure is 9.3
Kg/cm ² abs and the compression ratio of compressor 1 is reduced to 2.1, making it possible to increase the EER value.

In the above explanation, the temperature of the indoor air is 30°C and the relative humidity is 75%, but cooling and dehumidification can be similarly performed under various other conditions. .

Furthermore, in the above description, Freon R22 and R32 were used as the combination of two types of refrigerants, but various other combinations may be used.

As described above, the present invention includes one compressor 1, an outdoor heat exchanger 2, and two first and second indoor heat exchangers 3, 4, and a gas-liquid separator on the outlet side of the outdoor heat exchanger 2. A gas pipe 6 and a liquid pipe 8 having a first expansion mechanism 7 are connected to the gas region and liquid region of the separator 5, respectively. A heat exchanger 9 is provided for the refrigerant, and the outlet side of the heat exchanger 9 connected to the gas pipe 6 is connected to the second expansion mechanism 1.
0 to the inlet side of the first indoor heat exchanger 3, and the outlet side of the heat exchanger 9, which is connected to the liquid pipe 8, is connected to the suction side of the compressor 1, and Since the branch pipe 12 is connected to the inlet side of the second heat exchanger 4 via the third expansion mechanism 11 and charged with two types of refrigerants having different saturation pressures, two compressors 1 are used. There is no need to use one, and the initial cost can be kept low with just one unit.
By setting the evaporation temperature of the first indoor heat exchanger 3 to a low temperature that can exhibit sufficient dehumidifying ability, the heat exchanger 3 can perform sufficient dehumidification, and the first and second indoor heat exchangers 3 and 4 can perform the desired dehumidification. It can be cooled down to as low as 200 degrees, providing comfortable air conditioning. Moreover, the suction pressure of the compressor 1 can be made high enough to increase the EER value sufficiently, and operation with a high EER can be performed.

[Brief explanation of the drawing]

FIG. 1 is a refrigerant piping system diagram showing an embodiment of the present invention, FIG. 2 is an psychrometric diagram, and FIG. 3 is a refrigerant piping system diagram showing a conventional example. 1... Compressor, 2... Outdoor heat exchanger, 3... First indoor heat exchanger, 4... Second indoor heat exchanger, 5...
... Gas-liquid separator, 6 ... Gas pipe, 7 ... First expansion mechanism, 8 ... Liquid pipe, 9 ... Heat exchanger, 10 ... Second
Expansion mechanism, 12... Branch pipe, 11... Third expansion mechanism.

Claims (1)

[Scope of utility model registration request] One compressor 1, outdoor heat exchanger 2 and two first
and second indoor heat exchangers 3 and 4, and a gas-liquid separator 5 is connected to the outlet side of the outdoor heat exchanger 2,
A gas pipe 6 and a first
A heat exchanger 9 is provided to connect the liquid pipes 8 each having an expansion mechanism 7 and to exchange heat between the refrigerant flowing through the gas pipe 6 and the liquid pipe 8.
The outlet side of the heat exchanger 9 is connected to the inlet side of the first indoor heat exchanger 3 via a second expansion mechanism 10, and the outlet side of the heat exchanger 9 is connected to the liquid pipe 8. side is connected to the suction side of the compressor 1,
Further, a branch pipe 12 from the liquid pipe 8 is connected to the inlet side of the second heat exchanger 4 via a third expansion mechanism 11, and two types of refrigerants having different saturation pressures are charged therein. A cooling refrigeration device featuring: