A heat pump main unit with dual evaporation temperature and dual condensation temperature

Abstract

The present invention relates to the technical field of geothermal heating and waste heat recovery heating, and specifically to a heat pump main unit with dual evaporation temperatures and dual condensation temperatures, comprising a condenser, provided with a condenser refrigerant inlet 1, a condenser refrigerant outlet 1 connected to the condenser refrigerant inlet 1, a condenser refrigerant inlet 2, and a condenser refrigerant outlet 2 connected to the condenser refrigerant inlet 2; and an evaporator, provided with an evaporator refrigerant inlet 1, an evaporator refrigerant outlet 1 connected to the evaporator refrigerant inlet 1, an evaporator refrigerant inlet 2, and an evaporator refrigerant outlet 2 connected to the evaporator refrigerant inlet 2. When the temperature of geothermal water or waste hot water on the evaporator side needs to be reduced to a large extent and the temperature on the condenser side needs to be increased to a high level, the heat pump main unit can achieve the cascade utilization of geothermal and waste heat by creating two different evaporation temperatures and condensation temperatures, thereby effectively improving the energy efficiency ratio of the heat pump main unit.

Description

Technical Field

[0001] The invention relates to the technical field of geothermal heating and waste heat recovery heating, and in particular to a heat pump host with dual evaporation temperatures and dual condensation temperatures. Background Art

[0002] At present, in deep geothermal and waste heat recovery heating, in order to make full use of geothermal and waste heat, plate heat exchangers are usually used to directly heat the heating circulating water, and then the heat in the geothermal water or waste heat is fully recovered through the heat pump host and then re-injected into the re-injection well. Usually, the temperature of geothermal water or waste heat after passing through the plate heat exchanger is about 40℃, and the temperature of geothermal water or waste heat is reduced to 15℃ through the heat pump host.

[0003] At present, the heat pump mainframes produced on the market can only create one evaporation temperature. For example, if the outlet temperature of geothermal water is required to be 15°C, the evaporation temperature must be lower than 10°C. Through the reverse Carnot cycle, it can be seen that for every 1°C increase in evaporation temperature, the energy efficiency ratio of the heat pump mainframe increases by 3% to 5%. The inlet temperature of geothermal water or waste water is 40°C, and the evaporator temperature is 10°C, resulting in energy waste.

[0004] In the field of heating, especially large-scale regional heating, the temperature difference between the supply and return water of the heating network is often required to be large, so as to reduce the flow of water in the heating network and achieve energy saving. However, the current heat pump host only has one condensing temperature, which causes energy waste. Through the Carnot cycle, it is known that the energy efficiency ratio can be increased by 2% to 3% for every 1°C reduction in the condensing temperature.

[0005] How to improve the existing heat pump host to improve the energy efficiency ratio of the heat pump host and thus save energy is a technical problem that needs to be solved. Summary of the invention

[0006] In view of the problems existing in the prior art, the present invention proposes a heat pump host with double evaporation temperatures and double condensation temperatures which can effectively improve the energy efficiency ratio.

[0007] The technical solution adopted by the present invention to solve the technical problem is: a heat pump host with double evaporation temperatures and double condensation temperatures, comprising

[0008] A condenser, provided with a condenser refrigerant inlet 1, a condenser refrigerant outlet 1 connected to the condenser refrigerant inlet 1, a condenser refrigerant inlet 2, and a condenser refrigerant outlet 2 connected to the condenser refrigerant inlet 2;

[0009] An evaporator, provided with an evaporator refrigerant inlet 1, an evaporator refrigerant outlet 1 connected to the evaporator refrigerant inlet 1, an evaporator refrigerant inlet 2, and an evaporator refrigerant outlet 2 connected to the evaporator refrigerant inlet 2;

[0010] A first refrigerant circulation system, for forming a first evaporation temperature and a first condensation temperature, comprises

[0011] A first compressor, an inlet of which is connected to a refrigerant outlet of the evaporator through a pipeline;

[0012] a first check valve, an inlet of which is connected to the outlet of the first compressor through a pipeline, and an outlet of which is connected to the refrigerant inlet of the condenser through a pipeline;

[0013] A first throttling expansion valve, an inlet of which is connected to the refrigerant outlet of the condenser through a pipeline, and an outlet of which is connected to the refrigerant inlet of the evaporator through a pipeline;

[0014] The second refrigerant circulation system is used to form a second evaporation temperature and a second condensation temperature, including

[0015] a second compressor, the inlet of which is connected to the second refrigerant outlet of the evaporator through a pipeline;

[0016] a second check valve, the inlet of which is connected to the outlet of the second compressor through a pipeline, and the outlet of which is connected to the second refrigerant inlet of the condenser through a pipeline;

[0017] The second throttling expansion valve has an inlet connected to the second refrigerant outlet of the condenser through a pipeline, and an outlet connected to the second refrigerant inlet of the evaporator through a pipeline.

[0018] When the temperature of geothermal water or waste hot water on the evaporator side needs to be lowered significantly and the temperature on the condenser side needs to be raised higher, the heat pump host of the present application can achieve the cascade utilization of geothermal energy and waste heat by creating two different evaporation temperatures and condensation temperatures, effectively improving the energy efficiency ratio of the heat pump host and thus saving energy.

[0019] As a preference, it also includes

[0020] a first electric two-way valve, one valve port of which is connected to the first refrigerant outlet of the evaporator through a pipeline, and the other valve port of which is connected to the second refrigerant outlet of the evaporator through a pipeline;

[0021] The second electric two-way valve has one valve port connected to the first refrigerant inlet of the condenser through a pipeline, and the other valve port connected to the second refrigerant inlet of the condenser through a pipeline.

[0022] Preferably, the condenser is further provided with a heating circulating water inlet connected to the heating circulating water return pipe, and a heating circulating water outlet connected to the heating circulating water supply pipe.

[0023] Preferably, a condenser water pipe connecting the heating circulating water inlet and the heating circulating water outlet is provided in the condenser.

[0024] Preferably, the condenser further comprises a first condenser circulation pipeline connecting the condenser refrigerant inlet 1 and the condenser refrigerant outlet 1.

[0025] Preferably, the condenser further comprises a second condenser circulation pipeline connecting the second refrigerant inlet of the condenser and the second refrigerant outlet of the condenser.

[0026] Preferably, the evaporator is further provided with a geothermal water / waste hot water inlet connected to the geothermal water / waste hot water return pipe, and a geothermal water / waste hot water outlet connected to the geothermal water reinjection / waste hot water withdrawal pipe.

[0027] Preferably, an evaporator water pipe connecting the geothermal water / waste hot water inlet and the geothermal water / waste hot water outlet is provided in the evaporator.

[0028] Preferably, the evaporator further comprises a first evaporator circulation pipeline connecting the evaporator refrigerant outlet 1 and the evaporator refrigerant inlet 2.

[0029] Preferably, the evaporator further comprises a second evaporator circulation pipeline connecting the second refrigerant inlet of the evaporator and the second refrigerant outlet of the evaporator.

[0030] Beneficial Effects

[0031] In the present application, when the temperature of the geothermal water or waste hot water on the evaporator side needs to be reduced by a large margin and the temperature on the condenser side needs to be increased by a higher margin, the heat pump host of the present application can achieve the step-by-step utilization of geothermal energy and waste heat by creating two different evaporation temperatures and condensation temperatures, effectively improving the energy efficiency of the heat pump host and thus saving energy; when the temperature of the geothermal water or waste hot water on the evaporator side needs to be reduced by a small margin and the temperature on the condenser side needs to be increased by a small margin, the present application can make full use of the evaporator and the condenser by only starting the first compressor of the first refrigerant circulation system or the second compressor of the second refrigerant circulation system to significantly reduce the heat exchange end difference between the evaporator and the condenser, thereby improving the energy efficiency of the heat pump host at partial load. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 This is a schematic diagram of the structure of the heat pump host with dual evaporation temperatures and dual condensation temperatures for this application. DETAILED DESCRIPTION

[0033] The technical solution of the present invention is further described below with reference to the accompanying drawings and through specific implementation methods.

[0034] like Figure 1 As shown, a heat pump host with dual evaporation temperatures and dual condensation temperatures includes a condenser 1, an evaporator 2, a first refrigerant circulation system and a second refrigerant circulation system.

[0035] The condenser 1 is provided with a condenser refrigerant inlet 11, a condenser refrigerant outlet 12 connected to the condenser refrigerant inlet 11, a condenser refrigerant inlet 2 14, and a condenser refrigerant outlet 2 13 connected to the condenser refrigerant inlet 2 14. The condenser 1 is also provided with a heating circulation water inlet 15 connected to a heating circulation water return pipe, and a heating circulation water outlet 16 connected to a heating circulation water supply pipe. A condenser water pipe connecting the heating circulation water inlet 15 and the heating circulation water outlet 16 is provided in the condenser 1. The condenser 1 also includes a first condenser circulation pipe connecting the condenser refrigerant inlet 11 and the condenser refrigerant outlet 12, and a second condenser circulation pipe connecting the condenser refrigerant inlet 2 14 and the condenser refrigerant outlet 2 13.

[0036] The evaporator 2 is provided with an evaporator refrigerant inlet 1 22, an evaporator refrigerant outlet 1 21 connected to the evaporator refrigerant inlet 1 22, an evaporator refrigerant inlet 2 23, and an evaporator refrigerant outlet 2 24 connected to the evaporator refrigerant inlet 2 23. The evaporator 2 is also provided with a geothermal water / waste water inlet 25 connected to the geothermal water / waste water return pipe, and a geothermal water / waste water outlet 26 connected to the geothermal water recharge / waste water withdrawal pipe. An evaporator water pipe connecting the geothermal water / waste water inlet 25 and the geothermal water / waste water outlet 26 is provided in the evaporator 2. The evaporator 2 also includes a first evaporator circulation pipe connecting the evaporator refrigerant outlet 1 21 and the evaporator refrigerant inlet 2 22, and a second evaporator circulation pipe connecting the evaporator refrigerant inlet 2 23 and the evaporator refrigerant outlet 2 24.

[0037] The first refrigerant circulation system is used to form a first evaporation temperature and a first condensation temperature, including a first compressor 3-1 whose inlet is connected to the evaporator refrigerant outlet 21 through a pipeline, a first check valve 5-1 whose inlet is connected to the outlet of the first compressor 3-1 through a pipeline and whose outlet is connected to the condenser refrigerant inlet 11 through a pipeline, and a first throttling expansion valve 6-1 whose inlet is connected to the condenser refrigerant outlet 12 through a pipeline and whose outlet is connected to the evaporator refrigerant inlet 22 through a pipeline.

[0038] The second refrigerant circulation system is used to form a second evaporation temperature and a second condensation temperature, including a second compressor 3-2 whose inlet is connected to the evaporator refrigerant outlet 24 through a pipeline, a second check valve 5-2 whose inlet is connected to the outlet of the second compressor 3-2 through a pipeline and whose outlet is connected to the condenser refrigerant inlet 14 through a pipeline, and a second throttling expansion valve 6-2 whose inlet is connected to the condenser refrigerant outlet 13 through a pipeline and whose outlet is connected to the evaporator refrigerant inlet 23 through a pipeline.

[0039] When the heat pump main unit of the present application is working, in the first refrigerant circulation system, the first compressor 3-1 compresses the low-temperature and low-pressure gaseous refrigerant in the first evaporator circulation pipeline of the evaporator 2 to become a high-temperature and high-pressure gaseous refrigerant working medium. The high-temperature and high-pressure refrigerant working medium enters the first condenser circulation pipeline of the condenser 1, and becomes a high-temperature and high-pressure liquid refrigerant working medium after condensation. The high-temperature and high-pressure liquid refrigerant coming out of the first condenser circulation pipeline of the condenser 1 passes through the first throttling expansion valve 6-1 and becomes a low-temperature and low-pressure gas-liquid mixed refrigerant working medium, and then enters the first evaporator circulation pipeline of the evaporator 2 again, and completes a cycle after being heated and evaporated to become a low-temperature and low-pressure gaseous refrigerant. In the second refrigerant circulation system, the second compressor 3-2 compresses the low-temperature and low-pressure gaseous refrigerant in the second evaporator circulation pipeline of the evaporator 2 to become a high-temperature and high-pressure gaseous refrigerant working medium. The high-temperature and high-pressure refrigerant working medium enters the second condenser circulation pipeline of the condenser 1, and becomes a high-temperature and high-pressure liquid refrigerant working medium after condensation. The high-temperature and high-pressure liquid refrigerant coming out of the second condenser circulation pipeline of the condenser 1 passes through the second throttling expansion valve 6-2 and becomes a low-temperature and low-pressure gas-liquid mixed refrigerant working medium, and then enters the second evaporator circulation pipeline of the evaporator 2 again, and is heated and evaporated to become a low-temperature and low-pressure gaseous refrigerant to complete a cycle.

[0040] When the temperature on the evaporator 2 side needs to be reduced from 40°C to 15°C, the temperature on the evaporator 2 side can be reduced from 40°C to 25°C through the first refrigerant circulation system of the heat pump host, and then the temperature on the evaporator 2 side can be reduced from 40°C to 25°C through the second refrigerant circulation system of the heat pump host, and then the temperature on the evaporator 2 side can be reduced from 25°C to 15°C through the second refrigerant circulation system of the heat pump host, thus generating two evaporation temperatures, one evaporation temperature of 20°C and the other evaporation temperature of 10°C. Compared with the heat pump host with the same evaporation temperature of 10°C, its energy efficiency ratio is improved. When the temperature on the condenser side needs to be increased from 40°C to 50°C, the water temperature of condenser 1 can be increased from 40°C to 45°C through the first refrigerant circulation system of the heat pump host, and then the water temperature of condenser 1 can be increased from 45°C to 50°C through the second refrigerant circulation system of the heat pump host, thus generating two condensation temperatures of 45°C and 50°C, respectively. Compared with the heat pump host with a condensation temperature of 50°C, its energy efficiency ratio is improved. That is, compared with the traditional heat pump host with only one evaporating temperature and condensing temperature, when the temperature of geothermal water or waste hot water on the evaporator side needs to be lowered by a large margin and the temperature on the condenser side needs to be raised by a larger margin, the heat pump host of the present application can achieve the cascade utilization of geothermal energy and waste heat by creating two different evaporating temperatures and condensing temperatures, thereby effectively improving the energy efficiency ratio of the heat pump host and saving energy.

[0041] In addition, the present application also includes a first electric two-way valve 4-1, one valve port of which is connected to the evaporator refrigerant outlet 1 21 through a pipeline, and the other valve port is connected to the evaporator refrigerant outlet 2 24 through a pipeline, and a second electric two-way valve 4-2, one valve port of which is connected to the condenser refrigerant inlet 11 through a pipeline, and the other valve port is connected to the condenser refrigerant inlet 2 14 through a pipeline.

[0042] The water side inlet 15 of the condenser 1 is connected to the heating circulation water return pipe, and the water side outlet 16 of the condenser 1 is connected to the heating circulation water supply pipe. The first refrigerant inlet 11 of the condenser 1 is respectively connected to the inlet of the first check valve 5-1 and the second electric two-way valve 4-2, the first refrigerant outlet 12 of the condenser 1 is connected to the inlet 6-1 of the first throttling expansion valve, the outlet of the first throttling valve 6-1 is connected to the first refrigerant inlet 22 of the evaporator 2, the first refrigerant outlet 21 of the evaporator 2 is respectively connected to the inlet of the first compressor 3-1 and the inlet of the first electric two-way valve 4-1, and the outlet of the first compressor 3-1 is connected to the inlet of the first check valve 5-1. The second refrigerant inlet 14 of the condenser 1 is connected to the outlet of the second check valve 5-2 and the outlet of the second electric two-way valve 4-2 respectively, the second refrigerant outlet 13 of the condenser 1 is connected to the inlet of the second throttling expansion valve 6-2, the outlet of the second throttling expansion valve 6-2 is connected to the second refrigerant inlet 23 of the evaporator 2, the second refrigerant outlet 24 of the evaporator 2 is connected to the outlet of the first electric two-way valve 4-1 and the inlet of the second compressor 3-2 respectively, the outlet of the second compressor 3-2 is connected to the inlet of the second check valve 5-2. The water side inlet 25 of the evaporator 2 is connected to the geothermal water or waste hot water return pipe, and the water side outlet 26 of the evaporator 2 is connected to the geothermal water reinjection or waste hot water withdrawal pipe.

[0043] When the temperature of the hot water or waste water on the evaporator side needs to be lowered not too much and the temperature on the condenser side needs to be raised not too much, only the first compressor 3-1 of the first refrigerant cycle system or the second compressor 3-2 of the second refrigerant cycle system can be started while the first electric two-way valve 4-1 and the second electric two-way valve 4-2 are opened at the same time. When the first refrigerant cycle system and the second refrigerant cycle system need to be operated separately at the same time, it is only necessary to close the first electric two-way valve 4-1 and the second electric two-way valve 4-2 at the same time.

[0044] When only the first compressor 3-1 of the first refrigerant cycle system is started, the first compressor 3-1 compresses the low-temperature and low-pressure gaseous refrigerant from the evaporator 2 system one and system two into a high-temperature and high-pressure gaseous refrigerant working medium, and the high-temperature and high-pressure refrigerant working medium enters the condenser 1 of the system one and system two respectively, and becomes a high-temperature and high-pressure liquid refrigerant working medium after condensation. The high-temperature and high-pressure liquid refrigerant coming out of the condenser 1 of the system one and system two passes through the first throttling expansion valve 6-1 of the system one and the second throttling expansion valve 6-2 of the system two respectively, and becomes a low-temperature and low-pressure gas-liquid mixed refrigerant working medium, and then enters the evaporator 2 of the system one and system two respectively, evaporates by heat and becomes a low-temperature and low-pressure gaseous refrigerant, thereby completing a cycle.

[0045] When only the second compressor 3-2 of the second refrigerant cycle system is started, the second compressor 3-2 compresses the low-temperature and low-pressure gaseous refrigerant from the evaporator 2 system one and system two into a high-temperature and high-pressure gaseous refrigerant working medium, and the high-temperature and high-pressure refrigerant working medium enters the condenser 1 of the system one and system two respectively, and becomes a high-temperature and high-pressure liquid refrigerant working medium after condensation. The high-temperature and high-pressure liquid refrigerant coming out of the condenser 1 of the system one and system two passes through the first throttling expansion valve 6-1 of the system one and the second throttling expansion valve 6-2 of the system two respectively, and becomes a low-temperature and low-pressure gas-liquid mixed refrigerant working medium, and then enters the evaporator 2 of the system one and system two respectively, evaporates by heat and becomes a low-temperature and low-pressure gaseous refrigerant, thereby completing a cycle.

[0046] When only the first compressor 3-1 of the first refrigerant cycle system or the second compressor 3-2 of the second refrigerant cycle system needs to be started, the evaporator 2 and the condenser 1 can be fully utilized to significantly reduce the heat exchange end difference between the evaporator 2 and the condenser 1, thereby improving the energy efficiency ratio of the heat pump host at partial load.

[0047] The above-described embodiments are only descriptions of preferred implementations of the present invention, and are not intended to limit the concept and scope of the present invention. Without departing from the design concept of the present invention, various modifications and improvements made by ordinary persons in the art to the technical solution of the present invention should fall within the protection scope of the present invention, and the technical contents for which protection is sought in the present invention have been fully recorded in the claims.

Claims

1. A heat pump main engine with dual evaporation temperatures and dual condensation temperatures, characterized in that: include A condenser (1) having a condenser refrigerant inlet 1 (11), a condenser refrigerant outlet 1 (12) connected to the condenser refrigerant inlet 1 (11), a condenser refrigerant inlet 2 (14), and a condenser refrigerant outlet 2 (13) connected to the condenser refrigerant inlet 2 (14); The evaporator (2) is provided with an evaporator refrigerant inlet 1 (22), an evaporator refrigerant outlet 1 (21) connected to the evaporator refrigerant inlet 1 (22), an evaporator refrigerant inlet 2 (23), and an evaporator refrigerant outlet 2 (24) connected to the evaporator refrigerant inlet 2 (23); A first refrigerant circulation system, for forming a first evaporation temperature and a first condensation temperature, comprises A first compressor (3-1), the inlet of which is connected to the refrigerant outlet 1 (21) of the evaporator via a pipeline; A first check valve (5-1), an inlet of which is connected to the outlet of the first compressor (3-1) through a pipeline, and an outlet of which is connected to the first refrigerant inlet (11) of the condenser through a pipeline; A first throttling expansion valve (6-1), the inlet of which is connected to the first refrigerant outlet (12) of the condenser through a pipeline, and the outlet of which is connected to the first refrigerant inlet (22) of the evaporator through a pipeline; The second refrigerant circulation system is used to form a second evaporation temperature different from the first evaporation temperature and a second condensation temperature different from the first condensation temperature, including A second compressor (3-2), the inlet of which is connected to the second refrigerant outlet (24) of the evaporator via a pipeline; A second check valve (5-2), the inlet of which is connected to the outlet of the second compressor (3-2) through a pipeline, and the outlet of which is connected to the second refrigerant inlet (14) of the condenser through a pipeline; A second throttling expansion valve (6-2), the inlet of which is connected to the second refrigerant outlet (13) of the condenser through a pipeline, and the outlet of which is connected to the second refrigerant inlet (23) of the evaporator through a pipeline; A first electric two-way valve (4-1), one valve port of which is connected to the first refrigerant outlet (21) of the evaporator via a pipeline, and the other valve port of which is connected to the second refrigerant outlet (24) of the evaporator via a pipeline; A second electric two-way valve (4-2), one valve port of which is connected to the first refrigerant inlet (11) of the condenser via a pipeline, and the other valve port of which is connected to the second refrigerant inlet (14) of the condenser via a pipeline; When the temperature of the geothermal water or waste hot water on the evaporator side needs to be lowered to a small extent and the temperature on the condenser side needs to be raised to a small extent, only the first compressor (3-1) of the first refrigerant circulation system or the second compressor (3-2) of the second refrigerant circulation system is started while the first electric two-way valve (4-1) and the second electric two-way valve (4-2) are opened at the same time; when the first refrigerant circulation system and the second refrigerant circulation system need to be operated separately at the same time, the first electric two-way valve (4-1) and the second electric two-way valve (4-2) are closed at the same time.

2. A heat pump main unit with dual evaporation temperatures and dual condensation temperatures according to claim 1, characterized in that: The condenser (1) is also provided with a heating circulating water inlet (15) connected to the heating circulating water return pipe, and a heating circulating water outlet (16) connected to the heating circulating water supply pipe.

3. A heat pump main unit with dual evaporation temperatures and dual condensation temperatures according to claim 2, characterized in that: The condenser (1) is provided with a condenser water pipe connecting the heating circulating water inlet (15) and the heating circulating water outlet (16).

4. A heat pump main unit with dual evaporation temperatures and dual condensation temperatures according to claim 3, characterized in that: The condenser (1) further comprises a first condenser circulation pipeline connecting the condenser refrigerant inlet 1 (11) and the condenser refrigerant outlet 1 (12).

5. The heat pump main unit with double evaporation temperature and double condensation temperature according to claim 3, characterized in that: The condenser (1) further comprises a second condenser circulation pipeline connecting the second condenser refrigerant inlet (14) and the second condenser refrigerant outlet (13).

6. The heat pump main unit with dual evaporation temperatures and dual condensation temperatures according to claim 1, characterized in that: The evaporator (2) is also provided with a geothermal water / waste hot water inlet (25) connected to the geothermal water / waste hot water return pipe, and a geothermal water / waste hot water outlet (26) connected to the geothermal water reinjection / waste hot water withdrawal pipe.

7. The heat pump main unit with dual evaporation temperatures and dual condensation temperatures according to claim 6, characterized in that: An evaporator water pipe connecting the geothermal water / waste hot water inlet (25) and the geothermal water / waste hot water outlet (26) is provided in the evaporator (2).

8. The heat pump main unit with dual evaporation temperatures and dual condensation temperatures according to claim 7, characterized in that: The evaporator (2) further comprises a first evaporator circulation pipeline connecting the evaporator refrigerant outlet 1 (21) and the evaporator refrigerant inlet 1 (22).

9. The heat pump main unit with dual evaporation temperatures and dual condensation temperatures according to claim 7, characterized in that: The evaporator (2) further comprises a second evaporator circulation pipeline connecting the second evaporator refrigerant inlet (23) and the second evaporator refrigerant outlet (24).

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