阅读说明：本技术 一种双增焓双冷凝三级压缩制冷系统、空调器和控制方法 (Double-enthalpy-increasing double-condensing three-stage compression refrigeration system, air conditioner and control method ) 是由 刘静雷 邓志扬 袁明征 张勇 邓伟彬 于 2020-04-26 设计创作，主要内容包括：本发明提供一种双增焓双冷凝三级压缩制冷系统、空调器和控制方法,制冷系统包括压缩机和蒸发器、一级冷凝器和二级冷凝器、第一节流装置和第二节流装置；在第一节流装置和二级冷凝器之间还设置有第一闪蒸器,第一闪蒸器的第一液体出口管路与二级冷凝器连通,第一液体出口管路上还设置有第六节流装置；在第二节流装置和二级冷凝器之间还设置有第二闪蒸器,第二闪蒸器的第二进口管路与二级冷凝器连通,第二进口管路上还设置有第七节流装置,且第一补气口的补气压力大于第二补气口的补气压力。根据本发明能够相比于一次节流、二次节流或三次节流制冷循环系统,极大提高了系统的制热量、制冷量、制热性能系数和制冷性能系数。(The invention provides a double enthalpy-increasing double condensing three-stage compression refrigeration system, an air conditioner and a control method, wherein the refrigeration system comprises a compressor, an evaporator, a first-stage condenser, a second-stage condenser, a first throttling device and a second throttling device; a first flash evaporator is arranged between the first throttling device and the secondary condenser, a first liquid outlet pipeline of the first flash evaporator is communicated with the secondary condenser, and a sixth throttling device is arranged on the first liquid outlet pipeline; and a second flash evaporator is also arranged between the second throttling device and the secondary condenser, a second inlet pipeline of the second flash evaporator is communicated with the secondary condenser, a seventh throttling device is also arranged on the second inlet pipeline, and the air supplementing pressure of the first air supplementing port is greater than that of the second air supplementing port. Compared with a primary throttling, secondary throttling or tertiary throttling refrigeration cycle system, the invention greatly improves the heating capacity, the refrigerating capacity, the heating performance coefficient and the refrigerating performance coefficient of the system.)

1. The utility model provides a three-level compression refrigerating system of two condensation of two enthalpies which characterized in that: the method comprises the following steps:

the compressor comprises a compressor (1) and an evaporator (6), and further comprises a first-stage condenser (2), a second-stage condenser (4), a first throttling device (3) and a second throttling device (5), wherein the first-stage condenser (2) is connected with an outlet of the compressor (1), an outlet of the first-stage condenser (2) is connected with an inlet of the second-stage condenser (4), the first throttling device (3) is further arranged on a pipeline between the first-stage condenser (2) and the second-stage condenser (4), an outlet of the second-stage condenser (4) is connected with the second throttling device (5), and the other end of the second throttling device (5) is connected with the evaporator (6);

a first flash device (25a) is further arranged between the first throttling device (3) and the secondary condenser (4), a first inlet pipeline (251) of the first flash device (25a) is communicated with the first throttling device (3), a first liquid outlet pipeline (252) of the first flash device (25a) is communicated with the secondary condenser (4), a first gas outlet pipeline (253) of the first flash device (25a) is communicated with a first air supplementing port of the compressor (1), and a sixth throttling device (26) is further arranged on the first liquid outlet pipeline (252);

a second flash evaporator (25b) is further arranged between the second throttling device (5) and the secondary condenser (4), a second inlet pipeline (251 ') of the second flash evaporator (25b) is communicated with the secondary condenser (4), a second liquid outlet pipeline (252') of the second flash evaporator (25b) is communicated with the evaporator (6), a second gas outlet pipeline (253 ') of the second flash evaporator (25b) is communicated with a second air supplementing port of the compressor (1), a seventh throttling device (27) is further arranged on the second inlet pipeline (251'), and the air supplementing pressure of the first air supplementing port is greater than the air supplementing pressure of the second air supplementing port.

2. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to claim 1, characterized in that:

the water-cooled condenser is characterized by further comprising a primary water inlet pipe (12) capable of being communicated with the primary condenser (2), wherein the primary water inlet pipe (12) is used for communicating water into the primary condenser (2) and exchanging heat with a refrigerant pipeline in the primary condenser (2), the outlet end of the primary condenser (2) is connected with a primary water outlet pipe (14), and a first control valve (13) is arranged on the primary water inlet pipe (12); and/or the presence of a gas in the gas,

the compressor (1) comprises a first compression unit (101), a second compression unit (102) and a third compression unit (103), the first compression unit (101), the second compression unit (102) and the third compression unit (103) are sequentially communicated in series from low to high along the pressure, a first air supplementing port is located between the second compression unit (102) and the third compression unit (103), and a second air supplementing port is located between the first compression unit (101) and the second compression unit (102).

3. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to any one of claims 1 to 2, wherein:

still including letting in second grade inlet tube (7) in second grade condenser (4), second grade inlet tube (7) let in water in second grade condenser (4) and with the refrigerant pipeline in second grade condenser (4) carries out the heat transfer, second grade outlet pipe (8) are connected to the exit end of second grade condenser (4) be provided with second control valve (9) on second grade outlet pipe (8).

4. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to claim 3, characterized in that:

when the water purifier comprises a primary water inlet pipe (12) and a secondary water outlet pipe (8), the water purifier further comprises a bypass pipe (10), one end of the bypass pipe (10) is communicated with the secondary water outlet pipe (8), the other end of the bypass pipe is communicated with the primary water inlet pipe (12), and a third control valve (11) is further arranged on the bypass pipe (10).

5. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to claim 4, characterized in that:

when a first control valve (13) is included, the first control valve (13) is an electromagnetic valve; and/or when a second control valve (9) is included, the second control valve (9) is a solenoid valve; and/or when a third control valve (13) is included, the third control valve (11) is a solenoid valve.

6. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to any one of claims 1 to 5, wherein:

the primary condenser (2) can release heat and cool in an air cooling mode, and the secondary condenser (4) can release heat and cool in an air cooling mode.

7. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to claim 6, characterized in that:

the air heated by the secondary condenser (4) can be conducted into the primary condenser (2) to be heated secondarily.

8. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to claim 2, characterized in that:

the refrigeration system also comprises a first intermediate heat exchanger (15) and a first branch (16), wherein the first intermediate heat exchanger (15) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), one end of the first branch (16) is connected to the pipeline between the secondary condenser (4) and the first intermediate heat exchanger (15), the other end of the first branch is communicated into the first intermediate heat exchanger (15), an outlet pipeline of a first compression unit (101) is communicated into the first intermediate heat exchanger (15), an outlet of the first intermediate heat exchanger (15) is communicated to an inlet of the second compression unit (102), a pipeline between the secondary condenser (4) and the second throttling device penetrates through the first intermediate heat exchanger (15) and exchanges heat with refrigerant inside the first intermediate heat exchanger (15), and a third throttling device (17) is also arranged on the first branch (16).

9. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to claim 2, characterized in that:

the refrigeration system further comprises a second intermediate heat exchanger (18) and a second branch (19), the second intermediate heat exchanger (18) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), one end of the second branch (19) is connected to a pipeline between the secondary condenser (4) and the second intermediate heat exchanger (18), the other end of the second branch penetrates through the second intermediate heat exchanger (18) and is communicated to a pipeline between an outlet of the first compression unit (101) and an inlet of the second compression unit (102), a pipeline between the secondary condenser (4) and the second throttling device (5) penetrates through the second intermediate heat exchanger (18) and exchanges heat with the second branch (19) inside the second intermediate heat exchanger (18), and a fourth throttling device (20) is also arranged on the second branch (19).

10. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to claim 2, characterized in that:

the refrigeration system further comprises a third branch (21), one end of the third branch (21) is connected to a pipeline between the secondary condenser (4) and the second throttling device (5), the other end of the third branch is communicated to a pipeline between an outlet of the first compression unit (101) and an inlet of the second compression unit (102), and a fifth throttling device (22) and a fourth control valve (23) are further arranged on the third branch (21).

11. The dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to any one of claims 1 to 10, wherein:

the refrigerating system further comprises a heat regenerator (24), the heat regenerator (24) is arranged on a pipeline between the secondary condenser (4) and the second throttling device (5), a pipeline between the secondary condenser (4) and the second throttling device (5) penetrates through the second intermediate heat exchanger (18), and a pipeline between the evaporator (6) and an inlet of the compressor (1) also penetrates through the heat regenerator (24) and a pipeline between the secondary condenser (4) and the second throttling device (5) penetrates through the heat regenerator (24) to exchange heat.

12. An air conditioner, characterized in that:

comprising the dual enthalpy increasing dual condensing three stage compression refrigeration system according to any one of claims 1 to 11.

13. A control method suitable for the dual enthalpy-increasing dual condensing three-stage compression refrigeration system according to any one of claims 1 to 11, characterized in that:

when the first control valve, the second control valve and the third control valve are included at the same time: and at least one of the first control valve, the second control valve and the third control valve is selectively controlled to act according to the requirements of different hot water temperatures.

14. The control method according to claim 13, characterized in that:

the second control valve (9) is arranged on the secondary water outlet pipe (8), and the first control valve (13) is arranged on the primary water inlet pipe (12):

when it is desired to make water at a first temperature T1 and a second temperature T2 simultaneously, the simultaneous opening of the first control valve (13) and the second control valve (9) and the simultaneous closing of the third control valve (11) are selected;

when water with a first temperature T1 and a third temperature T3 needs to be prepared at the same time, the second control valve (9) and the third control valve (11) are selectively opened at the same time, and the first control valve (13) is closed; wherein the second temperature T3> the second temperature T2> the first temperature T1;

when it is only necessary to make water at a third temperature T3, the third control valve (11) is selectively opened, while the first control valve (13) and the second control valve (9) are closed.

Technical Field

The invention relates to the technical field of air conditioners, in particular to a double enthalpy-increasing double condensation three-stage compression refrigeration system, an air conditioner and a control method.

Background

Disclosure of Invention

Therefore, the technical problem to be solved by the invention is to overcome the defect that the air conditioner in the prior art has the problem of low heating/refrigerating performance coefficient of a primary throttling refrigeration cycle system, so that the double enthalpy-increasing double-condensing three-stage compression refrigeration system, the air conditioner and the control method are provided.

In order to solve the above problems, the present invention provides a dual enthalpy-increasing dual condensing three-stage compression refrigeration system, which comprises:

the condenser comprises a compressor, an evaporator, a first-stage condenser, a second-stage condenser, a first throttling device and a second throttling device, wherein the first-stage condenser is connected with an outlet of the compressor, an outlet of the first-stage condenser is connected with an inlet of the second-stage condenser, the first throttling device is arranged on a pipeline between the first-stage condenser and the second-stage condenser, an outlet of the second-stage condenser is connected with the second throttling device, and the other end of the second throttling device is connected with the evaporator;

a first flash evaporator is further arranged between the first throttling device and the secondary condenser, a first inlet pipeline of the first flash evaporator is communicated with the first throttling device, a first liquid outlet pipeline of the first flash evaporator is communicated with the secondary condenser, a first gas outlet pipeline of the first flash evaporator is communicated with a first air supplementing port of the compressor, and a sixth throttling device is further arranged on the first liquid outlet pipeline;

the second throttling device and the second-stage condenser are further provided with a second flash evaporator, a second inlet pipeline of the second flash evaporator is communicated with the second-stage condenser, a second liquid outlet pipeline of the second flash evaporator is communicated with the evaporator, a second gas outlet pipeline of the second flash evaporator is communicated with a second air supplementing port of the compressor, a seventh throttling device is further arranged on the second inlet pipeline, and the air supplementing pressure of the first air supplementing port is greater than the air supplementing pressure of the second air supplementing port.

Preferably, the condenser also comprises a first-stage water inlet pipe which can be communicated with the first-stage condenser, the first-stage water inlet pipe is used for communicating water into the first-stage condenser and exchanging heat with a refrigerant pipeline in the first-stage condenser, the outlet end of the first-stage condenser is connected with a first-stage water outlet pipe, and a first control valve is arranged on the first-stage water inlet pipe; and/or the presence of a gas in the gas,

the compressor includes first compression unit, second compression unit and third compression unit, just first compression unit the second compression unit with the third compression unit is from low to high concatenates the intercommunication in proper order along pressure, first tonifying qi mouth is located the second compression unit with between the third compression unit, the second tonifying qi mouth is located first compression unit with between the second compression unit.

Preferably, the condenser also comprises a second-stage water inlet pipe which can be communicated with the second-stage condenser, the second-stage water inlet pipe is communicated with water in the second-stage condenser and exchanges heat with a refrigerant pipeline in the second-stage condenser, the outlet end of the second-stage condenser is connected with a second-stage water outlet pipe, and a second control valve is arranged on the second-stage water outlet pipe.

Preferably, when the water-saving device comprises a first-stage water inlet pipe and a second-stage water outlet pipe, the water-saving device further comprises a bypass pipe, one end of the bypass pipe is communicated with the second-stage water outlet pipe, the other end of the bypass pipe is communicated with the first-stage water inlet pipe, and the bypass pipe is further provided with a third control valve.

Preferably, when a first control valve is included, the first control valve is a solenoid valve; and/or when a second control valve is included, the second control valve is a solenoid valve; and/or when a third control valve is included, the third control valve is a solenoid valve.

Preferably, the first-stage condenser can release heat and cool in an air cooling mode, and the second-stage condenser can release heat and cool in an air cooling mode.

Preferably, the wind heated by the secondary condenser can be conducted into the primary condenser to be subjected to secondary heating.

Preferably, the compressor includes a first compression unit and a second compression unit, the refrigeration system further includes a first intermediate heat exchanger and a first branch, the first intermediate heat exchanger is arranged on a pipeline between the secondary condenser and the second throttling device, one end of the first branch is connected to a pipeline between the secondary condenser and the first intermediate heat exchanger, the other end of the first branch is communicated into the first intermediate heat exchanger, meanwhile, an outlet pipeline of the first compression unit is also communicated into the first intermediate heat exchanger, an outlet of the first intermediate heat exchanger is communicated to an inlet of the second compression unit, and a pipeline between the secondary condenser and the second throttling device penetrates through the first intermediate heat exchanger and exchanges heat with the refrigerant in the first intermediate heat exchanger, and a third throttling device is further arranged on the first branch.

Preferably, the compressor includes a first compression unit and a second compression unit, the refrigeration system further includes a second intermediate heat exchanger and a second branch, the second intermediate heat exchanger is disposed on a pipeline between the second-stage condenser and the second throttling device, one end of the second branch is connected to a pipeline between the second-stage condenser and the second intermediate heat exchanger, the other end of the second branch penetrates through the second intermediate heat exchanger and is communicated to a pipeline between an outlet of the first compression unit and an inlet of the second compression unit, a pipeline between the second-stage condenser and the second throttling device penetrates through the second intermediate heat exchanger and exchanges heat with the second branch inside the second intermediate heat exchanger, and a fourth throttling device is further disposed on the second branch.

Preferably, the compressor includes a first compression unit and a second compression unit, the refrigeration system further includes a third branch, one end of the third branch is connected to a pipeline between the two-stage condenser and the second throttling device, and the other end of the third branch is connected to a pipeline between an outlet of the first compression unit and an inlet of the second compression unit, and the third branch is further provided with a fifth throttling device and a fourth control valve.

Preferably, the refrigeration system further includes a heat regenerator, the heat regenerator is disposed on a pipeline between the secondary condenser and the second throttling device, the pipeline between the secondary condenser and the second throttling device penetrates through the second intermediate heat exchanger, and a pipeline between the evaporator and the inlet of the compressor also penetrates through the heat regenerator and exchanges heat with a pipe section between the secondary condenser and the second throttling device, which penetrates through the heat regenerator.

The invention also provides an air conditioner which comprises the refrigeration system.

The invention also provides a control method suitable for any one of the refrigeration systems, wherein:

when the first control valve, the second control valve and the third control valve are included at the same time: and at least one of the first control valve, the second control valve and the third control valve is selectively controlled to act according to the requirements of different hot water temperatures.

Preferably, the second control valve is arranged on the secondary water outlet pipe, and the first control valve is arranged on the primary water inlet pipe:

when water at a first temperature T1 and a second temperature T2 needs to be prepared at the same time, controlling to open the first control valve and the second control valve at the same time and close the third control valve at the same time;

when water with a first temperature T1 and a third temperature T3 needs to be prepared at the same time, controlling the second control valve and the third control valve to be opened at the same time, and closing the first control valve; wherein the second temperature T3> the second temperature T2> the first temperature T1;

when only water at a third temperature T3 needs to be produced, control opens the third control valve while closing the first and second control valves.

The double enthalpy-increasing double condensing three-stage compression refrigeration system, the air conditioner and the control method provided by the invention have the following beneficial effects:

1. the invention can effectively form secondary throttling and secondary condensation by arranging two condensers which are connected in series, arranging a throttling device between the two condensers, effectively realizing tertiary throttling and air-supplementing enthalpy increase by arranging a first flash evaporator and a sixth throttling device between the first throttling device and the secondary condenser, effectively realizing quartic throttling and secondary air-supplementing enthalpy increase by arranging a second flash evaporator and a seventh throttling device between the second throttling device and the secondary condenser, realizing a double-enthalpy-increasing double-condensing triple-compression cycle high-low temperature system with double-condensing double-enthalpy-increasing quartic throttling, compared with a primary throttling and secondary throttling refrigeration cycle system, fully utilizing the secondary condenser to release refrigerant and sensible heat after primary throttling under the condition of same evaporation pressure, superheat degree, supercooling degree and refrigerant circulation quantity, the supercooling degree of the refrigerant before entering the evaporator is further improved, so that the evaporation capacity is further improved, the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with a primary throttling (secondary throttling and tertiary throttling) refrigerating cycle system, and the heating capacity and the heating performance coefficient of the system are also greatly improved because the condensation heat dissipation capacity of the dual-enthalpy-increasing dual-condensation three-stage compression cycle high-low temperature system is larger.

2. Because the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system adopts double enthalpy, the operating environment temperature range of the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system is larger than that of a primary throttling refrigeration cycle system, and the evaporation temperature can be lower, so that the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system is suitable for lower environment temperature to heat.

3. Because the double enthalpy-increasing double-condensing three-level compression circulation high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.

4. Because the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, so that the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized;

5. the invention also adds the first intermediate heat exchanger device which is completely intercooled on the basis of the dual enthalpy-increasing dual condensation three-stage compression cycle high-low temperature system, compared with the single dual enthalpy-increasing dual condensation three-stage compression cycle system, the supercooling degree of the refrigerant before entering the evaporator is further increased, the refrigeration performance coefficient or the heating performance coefficient is further enhanced, and the temperature of the refrigerant after the first-stage compression unit is effectively reduced, so that the refrigerant is fully cooled to the saturation temperature (the superheat degree is 0), the exhaust superheat degree of the compressor can be effectively reduced, and the power consumption of the compressor is effectively reduced;

6. the invention also adds the first intermediate heat exchanger device of incomplete intermediate cooling on the basis of the dual enthalpy-increasing dual condensation three-stage compression cycle high-low temperature system, compared with the single dual enthalpy-increasing dual condensation three-stage compression cycle system, the supercooling degree of the refrigerant before entering the evaporator is further increased, the refrigeration performance coefficient or the heating performance coefficient is further enhanced, and the temperature of the refrigerant after the first-stage compression unit is effectively reduced, so that the refrigerant is cooled (not fully cooled to the saturation temperature), the exhaust superheat degree of the compressor can be effectively reduced, and the power consumption of the compressor is effectively reduced;

7. compared with an independent dual-enthalpy-increasing dual-condensing three-stage compression circulation system, the dual-enthalpy-increasing dual-condensing three-stage compression circulation system has the advantages that the temperature of the refrigerant behind the first-stage compression unit is effectively reduced, the refrigerant is cooled (to saturation temperature or not cooled to saturation temperature), the exhaust superheat degree of the compressor can be effectively reduced, the power consumption of the compressor is effectively reduced, and the refrigerating performance coefficient or the heating performance coefficient is further enhanced;

8. compared with a single double enthalpy-increasing double condensing three-stage compression cycle system, the double enthalpy-increasing double condensing three-stage compression cycle system has the advantages that the supercooling degree of the refrigerant before entering the evaporator can be further increased, the refrigeration performance coefficient or the heating performance coefficient can be further enhanced, the suction superheat degree of the refrigerant before entering an air suction port of the compressor can be improved, the liquid impact of the compressor is prevented, and the reliability of the compressor is improved.

Drawings

FIG. 1 is a schematic diagram of a dual enthalpy-increasing dual condensing three-stage compression cycle high and low temperature system according to the present invention;

FIG. 2 is a pressure-enthalpy diagram of a dual enthalpy-increasing dual condensing three-stage compression cycle high and low temperature system according to the present invention;

FIG. 3 is a comparison pressure-enthalpy diagram of the dual enthalpy-increasing dual condensing three-stage compression cycle high and low temperature system of the present invention and the existing one-time throttling refrigeration cycle system.

FIG. 4 is a schematic diagram of a double enthalpy-increasing double condensing three-stage compression and heat return circulating high and low temperature system of the present invention.

The reference numerals are represented as:

1. a compressor; 101. a first compression unit; 102. a second compression unit; 2. a first-stage condenser; 3. A first throttling device; 4. a secondary condenser; 5. a second throttling device; 6. an evaporator; 7. a second-stage water inlet pipe; 8. a secondary water outlet pipe; 9. a second control valve; 10. a bypass pipe; 11. a third control valve; 12. a first-stage water inlet pipe; 13. a first control valve; 14. a primary water outlet pipe; 15. a first intermediate heat exchanger; 16. a first branch; 17. a third throttling means; 18. a second intermediate heat exchanger; 19. a second branch circuit; 20. a fourth throttling device; 21. a third branch; 22. a fifth throttling device; 23. a fourth control valve; 24. a heat regenerator; 25a, a first flash evaporator; 251. a first inlet line; 252. a first liquid outlet line; 253. a first gas outlet line; 26. a sixth throttling means; 25b, a second flash evaporator; 251', a second inlet line; 252', a second liquid outlet line; 253', a second gas outlet line; 27. and a seventh throttling means.

Detailed Description

As shown in fig. 1-3, the present invention provides a dual enthalpy-increasing dual condensing three-stage compression refrigeration system, which includes:

the condenser comprises a compressor 1 and an evaporator 6, and further comprises a first-stage condenser 2, a second-stage condenser 3, a first throttling device 3 and a second throttling device 5, wherein the first-stage condenser 2 is connected with an outlet of the compressor 1, an outlet of the first-stage condenser 2 is connected with an inlet of the second-stage condenser 4, the first throttling device 3 is further arranged on a pipeline between the first-stage condenser 2 and the second-stage condenser 4, an outlet of the second-stage condenser 4 is connected with the second throttling device 5, and the other end of the second throttling device 5 is connected with the evaporator 6;

a first flash evaporator 25a is further arranged between the first throttling device 3 and the secondary condenser 4, a first inlet pipeline 251 of the first flash evaporator 25a is communicated with the first throttling device 3, a first liquid outlet pipeline 252 of the first flash evaporator 25a is communicated with the secondary condenser 4, a first gas outlet pipeline 253 of the first flash evaporator 25a is communicated with a first air supplementing port of the compressor 1, and a sixth throttling device 26 is further arranged on the first liquid outlet pipeline 252;

a second flash evaporator 25b is further arranged between the second throttling device 5 and the secondary condenser 4, a second inlet pipeline 251 'of the second flash evaporator 25b is communicated with the secondary condenser 4, a second liquid outlet pipeline 252' of the second flash evaporator 25b is communicated with the evaporator 6, a second gas outlet pipeline 253 'of the second flash evaporator 25b is communicated with a second air supplement port of the compressor 1, a seventh throttling device 27 is further arranged on the second inlet pipeline 251', and the air supplement pressure of the first air supplement port is greater than the air supplement pressure of the second air supplement port.

1. The invention can effectively form secondary throttling and secondary condensation by arranging two condensers which are connected in series, arranging a throttling device between the two condensers, effectively realizing tertiary throttling and air-supplementing enthalpy increase by arranging a first flash evaporator and a sixth throttling device between the first throttling device and the secondary condenser, effectively realizing quartic throttling and secondary air-supplementing enthalpy increase by arranging a second flash evaporator and a seventh throttling device between the second throttling device and the secondary condenser, realizing a double-enthalpy-increasing double-condensing triple-compression cycle high-low temperature system with double-condensing double-enthalpy-increasing quartic throttling, compared with a primary throttling and secondary throttling refrigeration cycle system, fully utilizing the secondary condenser to release refrigerant and sensible heat after primary throttling under the condition of same evaporation pressure, superheat degree, supercooling degree and refrigerant circulation quantity, the supercooling degree of the refrigerant before entering the evaporator is further improved, so that the evaporation capacity is further improved, the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with a primary throttling (secondary throttling and tertiary throttling) refrigerating cycle system, and the heating capacity and the heating performance coefficient of the system are also greatly improved because the condensation heat dissipation capacity of the dual-enthalpy-increasing dual-condensation three-stage compression cycle high-low temperature system is larger.

2. Because the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system adopts double enthalpy, the operating environment temperature range of the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system is larger than that of a primary throttling refrigeration cycle system, and the evaporation temperature can be lower, so that the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system is suitable for lower environment temperature to heat.

3. Because the double enthalpy-increasing double-condensing three-level compression circulation high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.

4. Because the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system adopts the double condensers, the condensing pressure of each condenser is different, the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized.

Preferably, still including letting in one-level inlet tube 12 in the one-level condenser 2, one-level inlet tube 12 let in water in the one-level condenser 2 and with the refrigerant pipeline in the one-level condenser 2 carries out the heat transfer, one-level outlet pipe 14 is connected to the exit end of one-level condenser 2 be provided with first control valve 13 on the one-level inlet tube 12. The first-stage water inlet pipe structure can effectively receive water from the outside, so that the water is heated and heated in the first-stage condenser to achieve the purpose of preparing hot water, the hot water is discharged from the first-stage water outlet pipe, and the water inlet passage of the first-stage water inlet pipe can be effectively controlled through the arrangement of the first control valve.

Preferably, the compressor 1 includes a first compression unit 101, a second compression unit 102 and a third compression unit 103, and the first compression unit 101, the second compression unit 102 and the third compression unit 103 are sequentially connected in series from low to high along with pressure, the first air supplement port is located between the second compression unit 102 and the third compression unit 103, and the second air supplement port is located between the first compression unit 101 and the second compression unit 102. The three-stage compression unit can effectively form three-stage compression effect, and meet the effect of twice middle air supplement, so that three-stage compression and twice middle air supplement are realized, the supercooling degree of the refrigerating system is further improved, the evaporation capacity is improved, and the refrigerating cycle coefficient and the heating cycle coefficient are improved.

Preferably, the system further comprises a second-stage water inlet pipe 7 capable of being communicated with the second-stage condenser 4, the second-stage water inlet pipe 7 is used for communicating water into the second-stage condenser 4 and exchanging heat with a refrigerant pipeline in the second-stage condenser 4, the outlet end of the second-stage condenser 4 is connected with a second-stage water outlet pipe 8, and a second control valve 9 is arranged on the second-stage water outlet pipe 8. The water inlet pipe is connected with the water outlet pipe, the water inlet pipe is connected with the water inlet pipe, the water inlet pipe is connected with the water outlet pipe, the water outlet pipe is connected with the water inlet pipe, the water inlet pipe is connected with the water outlet pipe, and the water outlet pipe is connected.

Preferably, when the water heater comprises a first-stage water inlet pipe 12 and a second-stage water outlet pipe 8, the water heater further comprises a bypass pipe 10, one end of the bypass pipe 10 is communicated with the second-stage water outlet pipe 8, the other end of the bypass pipe 10 is communicated with the first-stage water inlet pipe 12, and the bypass pipe 10 is further provided with a third control valve 11. The invention is a further preferable structure form, namely, hot water in a secondary water outlet pipe (with lower temperature) can be effectively guided into a primary water inlet pipe through the arrangement of the bypass pipe, so that hot water with higher temperature is produced in the primary condenser, and the purpose of two-stage hot water production is achieved.

Preferably, when the first control valve 13 is included, the first control valve 13 is a solenoid valve; and/or when a second control valve 9 is included, the second control valve 9 is a solenoid valve; and/or when a third control valve 13 is included, the third control valve 11 is a solenoid valve. The solenoid valve is the preferred structural form of several control valves, can form more intelligent accurate control.

Preferably, the primary condenser 2 can release heat and cool in an air cooling mode, and the secondary condenser 4 can release heat and cool in an air cooling mode. The air-cooled type air conditioner is another preferable structure form of the invention, namely, the air-cooled type air conditioner is used for forming cooling of the secondary condenser, effectively raising the temperature of the air, forming hot air, heating a room, drying and the like.

Preferably, the first and second electrodes are formed of a metal,

the wind heated by the secondary condenser 4 can be conducted into the primary condenser 2 to be heated secondarily. Through the structure, air can be effectively accessed from the outside, so that the air is heated and warmed in the secondary condenser, the purpose of preparing hot air (different from the hot air temperature of the primary condenser, lower secondary condensation pressure and slightly lower temperature) is achieved, the purpose of heating the air step by step is achieved, and the requirements of environments with air (hot air) at different temperatures are met.

Preferably, the compressor 1 comprises a first compression unit 101 and a second compression unit 102, the refrigeration system further comprises a first intermediate heat exchanger 15 and a first branch 16, the first intermediate heat exchanger 15 is arranged on the pipeline between the secondary condenser 4 and the second throttling device 5, one end of the first branch 16 is connected to the pipeline between the secondary condenser 4 and the first intermediate heat exchanger 15, the other end of the first branch leads into the first intermediate heat exchanger 15, meanwhile, the outlet pipeline of the first compression unit 101 also leads into the first intermediate heat exchanger 15, the outlet of the first intermediate heat exchanger 15 leads to the inlet of the second compression unit 102, the pipeline between the secondary condenser 4 and the second throttling device passes through the first intermediate heat exchanger 15 and exchanges heat with the refrigerant inside the first intermediate heat exchanger 15, and a third throttling device 17 is further arranged on the first branch 16. This embodiment is not shown in the figures.

Compared with an independent dual-enthalpy-increasing dual-condensing three-stage compression circulation system, the fully intercooled high-temperature and low-temperature system further increases the supercooling degree of the refrigerant before entering the evaporator, further enhances the refrigeration performance coefficient or the heating performance coefficient, effectively reduces the temperature of the refrigerant after the first-stage compression unit, fully cools the refrigerant to the saturation temperature (the superheat degree is 0), can effectively reduce the exhaust superheat degree of the compressor, and effectively reduces the power consumption of the compressor.

Preferably, the compressor 1 includes a first compression unit 101 and a second compression unit 102, the refrigeration system also comprises a second intermediate heat exchanger 18 and a second branch 19, the second intermediate heat exchanger 18 being arranged on the line between the secondary condenser 4 and the second throttling device 5, one end of the second branch 19 is connected to a pipeline between the secondary condenser 4 and the second intermediate heat exchanger 18, the other end penetrates through the second intermediate heat exchanger 18 and is communicated to a pipeline between an outlet of the first compression unit 101 and an inlet of the second compression unit 102, a pipeline between the secondary condenser 4 and the second throttling device 5 penetrates through the second intermediate heat exchanger 18 and exchanges heat with the second branch 19 in the second intermediate heat exchanger 18, and a fourth throttling device 20 is further arranged on the second branch 19. This embodiment is not shown in the figures.

Compared with an independent dual enthalpy-increasing dual condensation three-stage compression circulation system, the invention further increases the supercooling degree of the refrigerant before entering the evaporator, further enhances the refrigeration performance coefficient or the heating performance coefficient, and also effectively reduces the temperature of the refrigerant after the first-stage compression unit, so that the refrigerant is cooled (not fully cooled to the saturation temperature), the exhaust superheat degree of the compressor can be effectively reduced, and the power consumption of the compressor is effectively reduced.

Preferably, the compressor 1 comprises a first compression unit 101 and a second compression unit 102, the refrigeration system further comprises a third branch 21, one end of the third branch 21 is connected to a pipeline between the two-stage condenser 4 and the second throttling device 5, and the other end of the third branch 21 is communicated to a pipeline between an outlet of the first compression unit 101 and an inlet of the second compression unit 102, and a fifth throttling device 22 and a fourth control valve 23 are further arranged on the third branch 21. This embodiment is not shown in the figures.

Compared with a single dual enthalpy-increasing dual condensation three-stage compression circulation system, the dual enthalpy-increasing dual condensation three-stage compression circulation system has the advantages that the temperature of the refrigerant after the first-stage compression unit is effectively reduced, the refrigerant is cooled (to the saturation temperature or not cooled to the saturation temperature), the exhaust superheat degree of the compressor can be effectively reduced, the power consumption of the compressor is effectively reduced, and the refrigerating performance coefficient or the heating performance coefficient is further enhanced.

As shown in fig. 4, preferably, the refrigeration system further includes a heat regenerator 24, the heat regenerator 24 is disposed on a pipeline between the secondary condenser 4 and the second throttling device 5, the pipeline between the secondary condenser 4 and the second throttling device 5 penetrates through the second intermediate heat exchanger 18, and a pipeline between the evaporator 6 and the inlet of the compressor 1 also penetrates through the heat regenerator 24 and exchanges heat with a pipe section between the secondary condenser 4 and the second throttling device 5 penetrating through the heat regenerator 24.

Compared with a single double enthalpy-increasing double condensing three-stage compression cycle system, the double enthalpy-increasing double condensing three-stage compression cycle system has the advantages that the supercooling degree of the refrigerant before entering the evaporator can be further increased, the refrigeration performance coefficient or the heating performance coefficient can be further enhanced, the suction superheat degree of the refrigerant before entering an air suction port of the compressor can be improved, the liquid impact of the compressor is prevented, and the reliability of the compressor is improved.

The invention also provides an air conditioner which comprises the double enthalpy-increasing double condensing three-stage compression refrigeration system.

The invention also provides a control method suitable for any one of the double enthalpy-increasing double condensing three-stage compression refrigeration systems, wherein the method comprises the following steps:

when the first control valve, the second control valve and the third control valve are included at the same time: and at least one of the first control valve, the second control valve and the third control valve is selectively controlled to act according to the requirements of different hot water temperatures.

1. The invention adopts the double-enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system with double condensation and intermediate throttling, compared with a primary throttling refrigeration cycle system, the invention fully utilizes the latent heat and the sensible heat of the refrigerant after primary throttling released by the secondary condenser under the condition of the same evaporation pressure, superheat degree, supercooling degree and refrigerant circulation quantity, and greatly improves the heating capacity and the heating performance coefficient of the system.

2. Because the condensation heat dissipation capacity of the double enthalpy-increasing double-condensation three-stage compression cycle high-low temperature system is larger, the evaporation heat absorption refrigerating capacity and the refrigerating performance coefficient are greatly improved compared with a one-time throttling refrigerating cycle system.

3. Because the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system adopts double enthalpy, the operating environment temperature range of the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system is larger than that of a primary throttling refrigeration cycle system, and the evaporation temperature can be lower, so that the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system is suitable for lower environment temperature to heat.

4. Because the double enthalpy-increasing double-condensing three-level compression circulation high-low temperature system adopts double condensers, the condensing pressure of each condenser is different, the temperature of inlet and outlet water of each condenser can be freely controlled and adjusted, and the multifunctional working condition of water with different water temperatures can be realized.

5. Because the double enthalpy-increasing double-condensing three-stage compression cycle high-low temperature system adopts the double condensers, the condensing pressure of each condenser is different, the air inlet and outlet temperature of each condenser can be freely controlled and adjusted, and the multifunctional working condition of heating at different air outlet temperatures can be realized.

Preferably, the second control valve 9 is arranged on the secondary water outlet pipe 8, and the first control valve 13 is arranged on the primary water inlet pipe 12:

when water at a first temperature T1 and a second temperature T2 needs to be prepared at the same time, the first control valve 13 and the second control valve 9 are selected to be opened at the same time, and the third control valve 11 is closed at the same time;

when water with the first temperature T1 and the third temperature T3 needs to be prepared at the same time, the second control valve 9 and the third control valve 11 are selected to be opened at the same time, and the first control valve 13 is closed; wherein the second temperature T3> the second temperature T2> the first temperature T1;

when it is only necessary to make water at a third temperature T3, the third control valve 11 is selectively opened while the first control valve 13 and the second control valve 9 are closed.

The dual enthalpy-increasing dual-condensing three-stage compression cycle high-low temperature system is explained by combining the attached drawings 1-3 as follows:

referring to the attached figure 1, a schematic diagram of a dual enthalpy-increasing dual condensation three-stage compression cycle high-low temperature system and a pressure-enthalpy diagram of a dual enthalpy-increasing dual condensation three-stage compression cycle high-low temperature system are shown in the attached figure 2, a low-temperature superheated refrigerant b from an evaporator is sucked into a compressor for compression, and a compressed high-temperature high-pressure superheated refrigerant c is discharged into a first-stage condenser and condensed into a high-temperature high-pressure wet vapor refrigerant d by cooling water; the high-temperature high-pressure wet vapor refrigerant d after primary condensation is throttled by a first throttling device to become a medium-temperature medium-pressure wet vapor refrigerant e; the medium-temperature medium-pressure wet vapor refrigerant e after primary throttling enters a secondary condenser and is condensed to medium-temperature medium-pressure supercooling refrigerant g by cooling water; the medium-temperature medium-pressure subcooled refrigerant g after secondary condensation is throttled by a second throttling device to form a low-temperature low-pressure wet vapor refrigerant h; the low-temperature low-pressure wet vapor refrigerant h after double enthalpy increase enters the evaporator to absorb heat to a low-temperature superheated refrigerant state b, so that a double enthalpy increase double condensation three-stage compression cycle is completed.

Because two enthalpy double condensation tertiary compression circulation high low temperature system have two condensers, the condensing pressure of each condenser is different, so the cooling method of condenser is various for the business turn over temperature of every condenser can freely be controlled and adjusted, can realize the multi-functional operating mode of different temperature water.

The first cooling method is to open the first control valve and open the second control valve simultaneously, and close the third control valve 11 simultaneously. The water inlet source temperature of the first-stage water inlet pipe and the water inlet source temperature of the second-stage water inlet pipe can be different, and the condensation temperature of the second-stage condenser is lower than that of the first-stage condenser, so that the water outlet temperature of the second-stage water outlet pipe is generally lower than that of the first-stage water outlet pipe, and therefore multifunctional working conditions that hot water at the first temperature T1 and the second temperature T2 is prepared to be used are achieved.

In the second cooling method, the second control valve and the third control valve are opened at the same time, and the first control valve is closed. The cooling water enters from the secondary water inlet pipe, after the cooling water is heated by the refrigerant of the secondary condenser, one part of the heated cooling water flows out from the secondary water outlet pipe for users to use, the other part of the heated cooling water enters into the primary condenser and is continuously heated by the refrigerant of the primary condenser, and the heated high-temperature hot water flows out from the primary water outlet pipe for users to use, so that the multifunctional working condition that the hot water with the first temperature T1 and the third temperature T3 is prepared for use is realized.

The third cooling mode is to open the third control valve and close the first control valve and the second control valve at the same time. And cooling water enters from the secondary water inlet pipe, and is heated into high-temperature hot water by the refrigerant of the secondary condenser and the refrigerant of the primary condenser, so that the high-flow requirement of the hot water at the third temperature T3 can be realized.

Referring to the figure 3, the comparison pressure-enthalpy diagram of the dual enthalpy-increasing dual-condensation three-stage compression cycle high-temperature system and the existing primary throttling refrigeration cycle system is shown, under the condition of the same evaporation pressure, superheat degree and refrigerant circulation quantity, the condensation pressure of the primary throttling refrigeration cycle system is in the middle of two condensation pressures of the dual enthalpy-increasing dual-condensation three-stage compression cycle system. Compared with a primary throttling refrigeration cycle system, the double enthalpy-increasing double condensation three-stage compression cycle system has the advantages that the compression power consumption is increased by W (h)_c-h_hAnd is doubleThe enthalpy-increasing double-condensation three-stage compression cycle high-low temperature system fully utilizes the latent heat and sensible heat of the refrigerant after the secondary condenser releases the primary throttling, and has more heating quantity than the primary throttling refrigeration cycle system by Q_h＝h_i-h_fRefrigeration capacity is much Q_c＝h_j-h_g. Compared with a primary throttling refrigeration cycle system, the double-enthalpy double-condensation three-stage compression cycle system has the advantages that the amplification degree of the heating capacity and the refrigerating capacity is far greater than that of the compression power consumption, and therefore the double-enthalpy double-condensation three-stage compression cycle high-low temperature system has higher heating capacity, refrigerating capacity, heating performance coefficient and refrigerating performance coefficient.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.