JP2861296B2 - Heat pump equipment - Google Patents

Description

Description: FIELD OF THE INVENTION The present invention relates to improvements in heat pump devices for obtaining higher or lower temperatures, such as heating and cooling, refueling or cryogenic devices.

2. Description of the Related Art An apparatus as shown in FIG. 2 has been proposed as a heat pump apparatus that uses a non-azeotropic mixed refrigerant and varies the refrigerant composition in a refrigeration cycle by composition separation.

FIG. 2 shows a first refrigeration cycle A by connecting a first compressor 1, a condenser 2, a first main throttle device 3, an evaporator 4, etc., and a second compressor 5, a four-way valve 6, a four-way valve A water-side heat exchanger 7 acting as a condenser or an evaporator by switching the valve 6, a second main throttle device 8, an air-side heat exchanger 9 acting as an evaporator or a condenser by switching the four-way valve 6, and the like are connected. Thus, the second refrigeration cycle B is configured. By performing heat exchange between the evaporator 4 of the first refrigeration cycle A and the water-side heat exchanger 7 of the second refrigeration cycle B as required, it is possible to operate as a so-called binary refrigeration cycle. It is also possible to operate only the cycle. Further, a rectification separator 11 is connected to an outlet of the condenser 2 through a first auxiliary throttle device 10.
And the bottom of the fractionator 11 is connected to the suction side of the first compressor 1 via the second auxiliary expansion device 12 and the evaporator 4, and the water-side heat exchanger 7 and the second main The rectification separator 11 branches off from the expansion device 8 via a third auxiliary expansion device 13.
And the top of the rectification separator 11 is connected to the four-way valve 6 via the fourth auxiliary expansion device 14 and the air-side heat exchanger 9 to form a composition separation circuit.

When both the first refrigeration cycle A and the second refrigeration cycle B of such a heat pump device are operated, the first refrigeration cycle A and the second refrigeration cycle B are connected via the rectifier 11. Rectification occurs and the rectification separator 11
The high-boiling refrigerant is concentrated and circulated in the first refrigeration cycle A connected to the bottom of the rectifier, and the low-boiling refrigerant is concentrated and circulated in the second refrigeration cycle B connected to the top of the rectifier 11. Since the evaporator 4 of the first refrigeration cycle and the water-side heat exchanger 7 of the second refrigeration cycle exchange heat, the condenser 2 of the first refrigeration cycle suppresses an increase in the condensing pressure and increases the second temperature. In the air-side heat exchanger 9 of the refrigeration cycle, a decrease in evaporation pressure is suppressed, and a lower temperature can be obtained.

Problems to be Solved by the Invention In the above conventional example, when the composition separation is performed, the high-boiling refrigerant is always concentrated in the first refrigeration cycle A, and the low-boiling refrigerant is always concentrated in the second refrigeration cycle B. For this reason, the first refrigeration cycle A is suitable for heating, but when used for cooling, the specific volume of the refrigerant increases, and it is inevitable that the apparatus becomes larger and the efficiency decreases. The second refrigeration cycle B side is suitable for cooling, but when used for heating, the refrigerant condensing pressure increases, and it is inevitable that the apparatus is increased in size, and also poses a problem in terms of safety.

Means for Solving the Problems A heat pump device according to the present invention includes a first refrigeration cycle including a first compressor, a first main four-way valve, a use side heat exchanger, a first main throttle device, a first heat exchanger, and the like. And a second refrigeration cycle including a second compressor, a second main four-way valve, a second heat exchanger, a second main expansion device, a heat source side heat exchanger, and the like, and a rectifying separator as main components. By switching the one sub four-way valve, the top of the rectifying separator is connected between the utilization side heat exchanger and the first main throttling device via the first auxiliary throttle device and the first sub four-way valve or the 2 Between the main throttle device and the heat source side heat exchanger, the bottom of the rectifying separator is connected to the second main throttle device and the heat source side heat through a fourth auxiliary throttle device and the first sub four-way valve. Connected between the heat exchanger and the use side heat exchanger and the first main throttle device to switch the second sub four-way valve Thereby, the top of the rectifying separator is connected between the first main throttle device and the first heat exchanger or the second heat exchanger and the second auxiliary throttle device via the second auxiliary four-way valve. Between the second main throttle device, the lower part of the rectifying separator is connected between the second heat exchanger and the second main throttle device via the third auxiliary throttle device and the second sub four-way valve. Alternatively, it is connected between the first main expansion device and the first heat exchanger, and the first heat exchanger and the second heat exchanger are configured to be capable of exchanging heat. Characterized by a non-azeotropic mixed refrigerant.

Operation The present invention operates the rectifying separator by switching the mixed refrigerant to the first refrigeration cycle and the second refrigeration cycle or switching the first four-way valve and the second four-way valve in accordance with the operating temperature condition by the above configuration. As a result, the non-azeotropic mixed refrigerant in which the high-boiling-point refrigerant is concentrated,
A non-azeotropic mixed refrigerant in which a low boiling point refrigerant is concentrated in the refrigeration cycle, or a non-azeotropic mixed refrigerant in which the low boiling point refrigerant is concentrated in the first refrigeration cycle, and a high boiling point refrigerant is concentrated in the second refrigerant cycle. The obtained non-azeotropic refrigerant mixture is circulated to improve the coefficient of performance under a wide range of operating conditions.

Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

FIG. 1 shows an embodiment of the heat pump device of the present invention. Reference numeral 21 denotes a first compressor, 22 denotes a first main four-way valve, 23 denotes a use side heat exchanger, 24 denotes a first main throttle device, and 25 denotes a first heat exchanger. The first refrigeration cycle C is configured.

26 is a second compressor, 27 is a second main four-way valve, 28 is a second heat exchanger, 29 is a second main throttle device, 30 is an air-side heat exchanger,
The second refrigeration cycle D is configured by sequentially connecting these with piping.

Reference numeral 31 denotes a rectifying separator, and the top of the rectifying separator 31 is connected to the first auxiliary expansion device 32 by the switching of the first sub four-way valve 34.
User side heat exchanger 23 and first main throttle device via sub four-way valve 34
24 or the second main throttle device 29 and the heat source side heat exchanger 30
Between the second main expansion device 29 and the heat source side heat exchanger 30 or the use side heat exchange through the fourth auxiliary expansion device 37 and the first auxiliary four-way valve 34. Connected between the vessel 23 and the first main throttle device 24, and by switching the second sub four-way valve 35, the top of the rectifying separator 31 is connected via the second auxiliary throttle device 33 and the second sub four-way valve 35. Between the first main expansion device 24 and the first heat exchanger 25 or between the second heat exchanger 28 and the second main expansion device 29, the bottom of the rectifying separator 31 is connected to a third auxiliary expansion device 36. The first heat exchanger 28 is connected between the second heat exchanger 28 and the second main throttle device 29 or between the first main throttle device 24 and the first heat exchanger 25 via a second sub four-way valve 35. The heat exchanger 25 and the second heat exchanger 26 are configured to be able to exchange heat.

An operation of such a heat pump device when a non-azeotropic mixed refrigerant in which, for example, R12 is mixed as a high-boiling refrigerant and R22 is mixed as a low-boiling refrigerant will be described.

First, when only the first refrigeration cycle C is operated,
The mixed refrigerant of the low-boiling refrigerant and the high-boiling refrigerant circulates, and the cooling and heating capacity is increased as compared with the case where only the high-boiling refrigerant is circulated, and the second refrigeration cycle D stores the surplus refrigerant of the mixed refrigerant. .

Next, the case where both the first refrigeration cycle C and the second refrigeration cycle D are operated will be described in order of the case where the use side heat exchanger 23 is used for heating and the case where it is used for cooling.

When the use side heat exchanger 23 is used for heating, the first sub four-way valve
34, the second sub-four-way valve 35 is switched as shown by the solid line in FIG. 1 to connect the bottom of the rectifying separator 31 and the first refrigeration cycle C, and the top of the rectifying separator 31 and the second refrigeration cycle D. Connecting.
In the first refrigeration cycle C, the first compressor 21 and the first main four-way valve 2
2. A part of the refrigerant that has passed through the use-side heat exchanger 23 passes through the first auxiliary four-way valve 34 and is decompressed to a certain extent by the fourth auxiliary expansion device 37 to be in a gas-liquid two-phase state. vessel
Ascend from the bottom of 31. On the other hand, in the second refrigeration cycle D, a part of the refrigerant that has passed through the second compressor 26, the second main four-way valve 27, and the second heat exchanger 28 passes through the second sub-four-way valve 35 and the second auxiliary throttle device 33. The pressure is reduced to a certain extent to a gas-liquid two-phase state,
In particular, the liquid refrigerant descends from the top of the fractionator 31. At this time, inside the rectifying separator 31, rectifying action occurs due to sufficient gas-liquid contact between the rising gas refrigerant and the descending liquid refrigerant,
The liquid refrigerant is enriched with R12, a high-boiling refrigerant, and the gas refrigerant is enriched with R22, a low-boiling refrigerant. Thus, R
The liquid refrigerant in which 12 has been concentrated is mixed with the liquid refrigerant supplied by the second auxiliary throttle device 37 at the bottom of the rectification separator 31 and passes through the third auxiliary throttle device 36 and the second sub four-way valve 35 to the first heat pump. The gas refrigerant, which is led to the exchanger 25 and is enriched in R22, is mixed with the gas refrigerant supplied by the second auxiliary expansion device 33 at the top of the rectification separator 31, and is mixed with the first auxiliary expansion device 32 and the first auxiliary expansion device. It is guided to the heat source side heat exchanger 30 via the four-way valve 34. By continuing the above operation, the non-azeotropic mixed refrigerant in which the low-boiling-point refrigerant R22 is concentrated circulates in the second refrigeration cycle D, so that the heat-source-side heat exchanger on the bottom pressure side in the heat pump device Since the decrease in the evaporation pressure at 30 is suppressed and the specific volume of the refrigerant gas at the time of suction into the second compressor 26 is reduced, the circulation amount is increased, and the amount of circulation is increased from the second heat exchanger 28 to the first heat exchanger 25. Since the amount of heat given to the first refrigeration cycle increases, the size of the equipment of the second refrigeration cycle can be avoided, and the temperature of the use side heat exchanger 23 can be efficiently increased. Further, since the non-azeotropic mixed refrigerant in which the high-boiling-point refrigerant R12 is concentrated circulates in the first refrigeration cycle C, the condensing pressure in the use-side heat exchanger 23 which is on the high pressure side in the heat pump device rises. Therefore, the size of the equipment can be avoided from the viewpoint of the pressure resistance design, and the temperature of the use side heat exchanger 23 can be efficiently increased to a higher temperature.

When the use side heat exchanger 23 is used for cooling, the first sub four-way valve
34, the second sub four-way valve 35 is switched as shown by the broken line in FIG.
The top of the rectifier 31 is connected to the first refrigeration cycle C, and the bottom of the rectifier 31 is connected to the second refrigeration cycle D. First
In the refrigeration cycle C, a part of the refrigerant that has passed through the first compressor 21, the first main four-way valve 22, and the first heat exchanger 25 is depressurized to some extent by the second auxiliary throttle device 33 through the second sub-four-way valve 35. It becomes a gas-liquid two-phase state, and the liquid refrigerant in particular descends from the top of the rectification separator 31. On the other hand, in the second refrigeration cycle D, the second compressor
26, a part of the refrigerant that has passed through the second main four-way valve 27 and the heat source side heat exchanger 30 passes through the first sub-four-way valve 34, and is decompressed to some extent by the fourth auxiliary throttle device 37 to be in a gas-liquid two-phase state. In particular, the gas refrigerant rises from the bottom of the fractionator 31. At this time, inside the rectification separator 31, rectification occurs due to sufficient gas-liquid contact between the ascending gas refrigerant and the descending liquid refrigerant, and the gas refrigerant is concentrated in R22, which is a low-boiling refrigerant, and the liquid refrigerant is R12, which is a high boiling point refrigerant, is concentrated. In this way, the gas refrigerant enriched in R22 is mixed with the gas refrigerant supplied by the second auxiliary throttle device 33 at the top of the rectification separator 31, and is mixed with the first auxiliary throttle device 32 and the first sub four-way valve 34. The liquid refrigerant enriched with R12 is led to the use side heat exchanger 23 through the
At the bottom of the first auxiliary throttle device 36, the second auxiliary four-way valve is mixed with the liquid refrigerant supplied by the fourth auxiliary throttle device 37.
It is led to the second heat exchanger 28 via 35. If the above operation is continued, the second refrigeration cycle D is a high boiling point refrigerant.
Since the non-azeotropic refrigerant mixture enriched with R12 circulates, the rise in condensation pressure in the heat source side heat exchanger 30, which is on the high pressure side in the heat pump device, is suppressed. Is avoided, and the operation of the second compressor 26 can be performed efficiently. Further, since the non-azeotropic mixed refrigerant in which the low-boiling-point refrigerant R22 is concentrated circulates in the first refrigeration cycle C, the evaporation pressure in the use-side heat exchanger 23 on the bottom pressure side in the heat pump device decreases. And the first compressor 21
Since the specific volume of the refrigerant gas at the time of suction into the refrigerant decreases, the circulation amount increases, and the second refrigerant passes through the second heat exchanger 28 from the first heat exchanger 25 to the second
Since the waste heat to the refrigeration cycle is promoted, it is possible to avoid an increase in the size of the equipment of the first refrigeration cycle, and to efficiently lower the temperature of the use-side heat exchanger 23.

Effect of the Invention As described above, the heat pump device of the present invention switches the four-way valve connected to the rectifier to circulate the high-boiling-point refrigerant in the first refrigeration cycle during the heating operation, thereby allowing the heat pump device to operate in the condenser. During the cooling operation, the pressure in the evaporator is increased by circulating a low-boiling refrigerant in the first refrigeration cycle during the cooling operation, so that the operation can be performed efficiently and safely under a wide range of temperature conditions.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of one embodiment of a heat pump device of the present invention, and FIG. 2 is a configuration diagram of a conventional heat pump device. 21 ... first compressor, 22 ... first main four-way valve, 23 ... use side heat exchanger, 24 ... first main throttle device, 25 ... first heat exchanger, 26 ... second
Compressor, 27: second main four-way valve, 28: second heat exchanger, 29: second main throttle device, 30: heat source side heat exchanger, 31: rectifying separator,
32: first auxiliary throttle device, 33: second auxiliary throttle device, 34: first auxiliary four-way valve, 35: second auxiliary four-way valve, 36: third auxiliary throttle device, 37: fourth auxiliary throttle device, C ... First refrigeration cycle, D
... Second refrigeration cycle.

Claims (1)

(57) [Claims] 1. A first refrigeration cycle comprising a first compressor, a first main four-way valve, a use side heat exchanger, a first main throttle device, a first heat exchanger, etc .; A second refrigeration cycle including a four-way valve, a second heat exchanger, a second main expansion device, a heat source side heat exchanger, and the like, and a rectifying separator as main components,
By switching the sub four-way valve, the top of the rectifying separator is connected between the utilization side heat exchanger and the first main throttle device or the second main throttle device via the first auxiliary throttle device and the first sub four-way valve.
Between the main expansion device and the heat source side heat exchanger, the bottom of the rectifying separator is connected to the second main expansion device and the heat source side heat exchange via a fourth auxiliary expansion device and the first sub four-way valve. Connected between the heat exchanger and the use side heat exchanger and the first main throttle device, and by switching a second sub four-way valve, the top of the rectifying separator is connected to the second auxiliary throttle device and the second auxiliary throttle device. Between the first main throttle device and the first heat exchanger or between the second heat exchanger and the second main throttle device via two sub-four-way valves,
The bottom of the rectifying separator is connected between the second heat exchanger and the second main throttle device or between the first main throttle device and the first auxiliary throttle device via a third auxiliary throttle device and the second sub four-way valve. Connected to a heat exchanger, the first heat exchanger and the second heat exchanger are configured to be capable of exchanging heat, and a non-azeotropic mixed refrigerant comprising a low-boiling refrigerant and a high-boiling refrigerant is sealed therein. Characteristic heat pump device.