CN113280524B

CN113280524B - Large temperature difference heat exchange system provided with multiple ejectors

Info

Publication number: CN113280524B
Application number: CN202110603592.6A
Authority: CN
Inventors: 张承虎; 毕嘉桐; 薛贵钰; 吴雅玲
Original assignee: Harbin Institute of Technology
Current assignee: Harbin Institute of Technology
Priority date: 2021-05-31
Filing date: 2021-05-31
Publication date: 2022-06-10
Anticipated expiration: 2041-05-31
Also published as: CN113280524A

Abstract

The invention discloses a large-temperature-difference heat exchange system with a plurality of ejectors, relates to the technical field of jet type large-temperature-difference heat exchange systems, solves the problem of low heat exchange effect caused by low circulation efficiency of a jet type heat pump part in the traditional jet type large-temperature-difference heat exchange system, and realizes gradient utilization of energy. The invention is used in heat supply engineering, the injection type large temperature difference heat exchange system is improved, the throttling, cooling and pressure reducing liquid refrigerant is used for supercooling a part of liquid refrigerant at the outlet of a condenser, the refrigerating capacity is increased, the exhaust temperature is reduced, the large temperature difference heat exchange system is constructed by adopting a double-section injection type structure, the utilization of primary water energy is realized, the double-section cooling and heating of the primary water and the secondary water are realized, the utilization of heat energy in the system is effectively improved, an injector in each section can operate under a relatively proper and stable working condition, the large temperature difference heat exchange unit operates more stably, and the operating efficiency of the injection type heat pump cycle is improved.

Description

Large temperature difference heat exchange system provided with multiple ejectors

Technical Field

The invention relates to the technical field of jet type large-temperature-difference heat exchange systems, in particular to a large-temperature-difference heat exchange system with a plurality of ejectors.

Background

The jet heat pump is driven by high temperature heat source, the high pressure working fluid produced in the boiler ejects the low pressure ejection fluid produced by the evaporator, the two fluids are mixed to become medium pressure mixed fluid, and the medium pressure mixed fluid enters the condenser to condense and release heat, thereby extracting the heat in the low temperature heat source to high temperature heat source. Based on the characteristics, the jet type heat pump system is combined with an external debugging heat exchanger to construct a jet type large-temperature-difference heat exchange system, so that the deep heat exchange of primary water and secondary water in a heat supply engineering pipe network is realized. A conventional jet type large temperature difference heat exchange system is shown in fig. 1, and mainly comprises a boiler 1, a condenser 4, an evaporator 10, a first ejector 2, a commissioning heat exchanger 21 and associated pipeline equipment and transportation equipment. Under the action of high-temperature primary water, the boiler 1 boils a Freon refrigerant working medium in the high-temperature primary water to generate high-temperature and high-pressure working steam, and the high-temperature and high-pressure working steam enters the first ejector 2 through the first working steam pipeline 30; similarly, the evaporator 10 evaporates the refrigerant working medium therein into low-pressure injection steam under the action of the primary water with lower temperature, and the low-pressure injection steam enters the first injector 2 through the first injection steam pipeline 43. Under the action of high-pressure working steam, low-pressure injection steam is injected, the low-pressure injection steam is mixed into medium-pressure mixed steam after the pressure is increased, the medium-pressure mixed steam enters the condenser 4 through the first mixed steam pipeline 32 for condensation, the heat is released, the working medium steam changes into a liquid state, the medium-pressure mixed steam flows out of the condenser from the first condenser liquid refrigerant pipeline 36, enters the liquid collector 5 and is divided into two parts, and one part flows into the evaporator 10 through the evaporator liquid refrigerant throttling pipeline 42 and flows through the second throttling expansion valve 9; the other strand passes through a liquid refrigerant pipeline 37 of the boiler and enters the boiler 1 through a refrigerant pump 8, thereby completing the circulation of refrigerant working media. On the other hand, the high-temperature primary water flows into the system through the primary water inlet 70, passes through the boiler 1, the pilot heat exchanger 21, and the evaporator 10 in this order through the primary water pipe 72, decreases in temperature, releases heat, and then flows out of the system through the primary water outlet 75. The secondary water flows into the system through the secondary water inlet 80 and is divided into two streams, one stream passes through the first secondary water pipeline 81 and absorbs condensation heat through the condenser 4, and the other stream passes through the second secondary water pipeline 84, is subjected to heat exchange with the primary water through the heat exchanger 21, is mixed with the first stream of water, and then flows out of the system from the secondary water outlet 86. In the process, the primary water is cooled for many times, and the outlet temperature can be reduced to be lower than the inlet temperature of the secondary water under certain working conditions, so that the heat exchange process with large temperature difference is realized.

However, due to the influence of the self result of the ejector equipment and the injection mixing intensity, the injection coefficient of the ejector in the injection type heat pump cycle is always maintained at a lower level under the working condition of primary and secondary water heat exchange, so that the cycle efficiency of a single heat pump cycle is lower, and the heat exchange effect of the injection type large-temperature-difference heat exchange system is further influenced.

Disclosure of Invention

In view of the above-mentioned problems, it is an object of the present invention to provide a large temperature difference heat exchange system provided with a plurality of ejectors.

In order to achieve the purpose, the invention adopts the technical scheme that:

a large temperature difference heat exchange system provided with a plurality of ejectors, comprising: the heat exchanger comprises a first heat exchange system and a second heat exchange system, wherein the first heat exchange system is connected with the second heat exchange system through a plurality of pipelines;

the first heat exchange system comprises: the heat exchanger comprises a first boiler 1, a first ejector 2, a second ejector 3, a first condenser 4, a first heat exchanger 6, a first refrigerant pump 8 and a first evaporator 10, wherein the first boiler 1 comprises a first conveying channel and a second conveying channel, the first condenser 4 comprises a third conveying channel and a fourth conveying channel, the first heat exchanger 6 comprises a fifth conveying channel and a sixth conveying channel, the first evaporator 10 comprises a seventh conveying channel and an eighth conveying channel, the first ejector 2 comprises a first ejector inlet, a first ejector inlet and a first ejector outlet, and the second ejector 3 comprises a second ejector inlet, a second ejector inlet and a second ejector outlet;

the inlet of the first ejector and the inlet of the second ejector are both connected with the outlet of a first conveying channel, the outlet of the first ejector and the outlet of the second ejector are both connected with the inlet of a third conveying channel, the outlet of the third conveying channel is respectively connected with the inlet of a first refrigerant pump 8, the inlet of a fifth conveying channel and the inlet of a sixth conveying channel, the inlet of the first conveying channel is connected with the outlet of the first refrigerant pump 8, the outlet of the fifth conveying channel is connected with the second injection inlet, the outlet of the sixth conveying channel is connected with the inlet of a seventh conveying channel, and the outlet of the seventh conveying channel is connected with the first injection inlet;

the second heat exchange system comprises: a second boiler 11, a third ejector 12, a fourth ejector 13, a second condenser 14, a second heat exchanger 16, a second refrigerant pump 18 and a second evaporator 20, wherein the second boiler 11 comprises an eleventh delivery passage and a twelfth delivery passage, the second condenser 14 comprises a thirteenth delivery passage and a fourteenth delivery passage, the second heat exchanger 16 comprises a fifteenth delivery passage and a sixteenth delivery passage, the second evaporator 20 comprises a seventeenth delivery passage and an eighteenth delivery passage, the third ejector 12 comprises a third ejector inlet, a third ejector inlet and a third ejector outlet, and the fourth ejector 13 comprises a fourth ejector inlet, a fourth ejector inlet and a fourth ejector outlet;

the inlet of the third ejector and the inlet of the fourth ejector are both connected with the outlet of an eleventh conveying channel, the outlet of the third ejector and the outlet of the fourth ejector are both connected with the inlet of a thirteenth conveying channel, the outlet of the thirteenth conveying channel is respectively connected with the inlet of a second refrigerant pump 18, the inlet of a fifteenth conveying channel and the inlet of a sixteenth conveying channel, the inlet of the eleventh conveying channel is connected with the outlet of the second refrigerant pump 18, the outlet of the fifteenth conveying channel is connected with the fourth injection inlet, the outlet of the sixteenth conveying channel is connected with the inlet of a seventeenth conveying channel, and the outlet of the seventeenth conveying channel is connected with the third injection inlet.

The aforesaid big difference in temperature heat transfer system that is provided with a plurality of sprayers, wherein, first heat transfer system still includes: the system comprises a first liquid collector 5, a first throttle expansion valve 7 and a second throttle expansion valve 9, wherein the first liquid collector 5 is connected to an outlet of a third conveying channel, the first throttle expansion valve 7 is connected to an inlet of a fifth conveying channel, and the second throttle expansion valve 9 is connected to an inlet of a seventh conveying channel.

The aforesaid big difference in temperature heat transfer system that is provided with a plurality of sprayers, wherein, the second heat transfer system still includes: the second liquid collector 15 is connected to an outlet of the thirteenth conveying channel, the third throttle expansion valve 17 is connected to an inlet of the fifteenth conveying channel, and the fourth throttle expansion valve 19 is connected to an inlet of the seventeenth conveying channel.

The aforesaid is provided with big difference in temperature heat transfer system of a plurality of sprayers, wherein, still includes: the secondary water inlet 80 is connected with one end of a fourth conveying channel, the other end of the fourth conveying channel is connected with one end of a fourteenth conveying channel, and the other end of the fourteenth conveying channel is connected with the secondary water outlet 86.

The aforesaid big difference in temperature heat transfer system that is provided with a plurality of sprayers, wherein, first heat transfer system still includes: and the third heat exchanger 22 comprises a ninth conveying channel and a tenth conveying channel, the outlet of the first ejector and the outlet of the second ejector are both connected with one end of the ninth conveying channel, the other end of the ninth conveying channel is connected with the inlet of the third conveying channel, and the two ends of the tenth conveying channel are respectively connected with the inlet of the first conveying channel and the outlet of the first refrigerant pump 8.

The aforesaid big difference in temperature heat transfer system that is provided with a plurality of sprayers, wherein, the second heat transfer system still includes: and the fourth heat exchanger 23 comprises a nineteenth conveying channel and a twentieth conveying channel, the third ejector outlet and the fourth ejector outlet are both connected with one end of the nineteenth conveying channel, the other end of the nineteenth conveying channel is connected with the inlet of the thirteenth conveying channel, and two ends of the twentieth conveying channel are respectively connected with the inlet of the eleventh conveying channel and the outlet of the second refrigerant pump 18.

The aforesaid is provided with big difference in temperature heat transfer system of a plurality of sprayers, wherein, still includes: the primary water inlet 70, the primary water outlet 75 and the debugging heat exchanger 21, wherein the debugging heat exchanger 21 comprises a twenty-first conveying channel and a twenty-second conveying channel, the primary water inlet 70 is connected with the inlet of the second conveying channel, the outlet of the second conveying channel is connected with the inlet of the twelfth conveying channel, the outlet of the twelfth conveying channel is connected with the inlet of the twenty-second conveying channel, the outlet of the twenty-second conveying channel is connected with the inlet of the eighteenth conveying channel, the outlet of the eighteenth conveying channel is connected with the inlet of the eighth conveying channel, the outlet of the eighth conveying channel is connected with the primary water outlet 75, and the two ends of the twenty-first conveying channel are respectively connected with the secondary water inlet 80 and the secondary water outlet 86.

The aforesaid is provided with big difference in temperature heat transfer system of a plurality of sprayers, wherein, still includes: the primary water inlet 70, the primary water outlet 75 and the debugging heat exchanger 21, wherein the debugging heat exchanger 21 comprises a twenty-first conveying channel and a twenty-second conveying channel, the primary water inlet 70 is connected with the inlet of the twelfth conveying channel, the outlet of the twelfth conveying channel is connected with the inlet of the second conveying channel, the outlet of the second conveying channel is connected with the inlet of the twenty-second conveying channel, the outlet of the twenty-second conveying channel is connected with the inlet of the eighteenth conveying channel, the outlet of the eighteenth conveying channel is connected with the inlet of the eighth conveying channel, the outlet of the eighth conveying channel is connected with the primary water outlet 75, and the two ends of the twenty-first conveying channel are respectively connected with the secondary water inlet 80 and the secondary water outlet 86.

The aforesaid is provided with big difference in temperature heat transfer system of a plurality of sprayers, wherein, still includes: a fifth heat exchanger 24 and a sixth heat exchanger 25, wherein the fifth heat exchanger 24 comprises a twenty-third conveying channel and a twenty-fourth conveying channel, and the sixth heat exchanger 25 comprises a twenty-fifth conveying channel and a twenty-sixth conveying channel;

one end of a twenty-third conveying channel is connected with the tenth conveying channel, the other end of the twenty-third conveying channel is connected with the inlet of the first conveying channel, one end of a twenty-fifth conveying channel is connected with the twentieth conveying channel, and the other end of the twenty-fifth conveying channel is connected with the inlet of the eleventh conveying channel;

the outlet of the second conveying channel is connected with the inlet of a twenty-fourth conveying channel, the outlet of the twenty-fourth conveying channel is connected with the inlet of a twenty-sixth conveying channel, and the outlet of the twenty-sixth conveying channel is connected with the inlet of the twenty-second conveying channel.

Due to the adoption of the technology, compared with the prior art, the invention has the following positive effects:

(1) according to the invention, a traditional jet type large-temperature-difference heat exchange system is improved, a supercooling device consisting of a first throttling expansion valve and a first heat exchanger is installed, and working media in a liquid refrigerant supercooling pipeline of a first evaporator are supercooled, so that the working media in the throttling pipeline of the first liquid refrigerant is heated, the throttled and reduced-temperature liquid refrigerant is supercooled by a part of liquid refrigerant at the outlet of a condenser, the refrigerating capacity is increased, the exhaust temperature is reduced, and the circulation efficiency of the jet type refrigeration circulation system is improved.

(2) The large-temperature-difference heat exchange system is constructed by adopting a double-section injection type structure, so that the utilization of primary water energy of temperature-to-mouth and gradient utilization is realized, the double-section cooling and heating of the primary water and the secondary water are carried out, the utilization of heat energy in the system is effectively improved, the circulating operation efficiency of the injection type heat pump in each section is improved, and the heat exchange effect and the heat exchange quantity of the whole heat exchange unit are enhanced.

(3) Due to the segmented arrangement, the ejector in each segment can operate under relatively suitable and stable working conditions, so that the large-temperature-difference heat exchanger unit can operate more stably as a whole.

Drawings

Fig. 1 is a schematic structural diagram of a conventional injection type large temperature difference heat exchange system.

Fig. 2 is a schematic structural diagram of a first embodiment of a large temperature difference heat exchange system provided with a plurality of ejectors.

Fig. 3 is a schematic structural diagram of a second embodiment of the large temperature difference heat exchange system provided with a plurality of ejectors.

Fig. 4 is a schematic structural diagram of a third embodiment of the large temperature difference heat exchange system provided with a plurality of ejectors.

In the drawings: 1. a first boiler; 2. a first ejector; 3. a second ejector; 4. a first condenser; 5. a first liquid trap; 6. a first heat exchanger; 7. a first throttle expansion valve; 8. a first refrigerant pump; 9. a second throttle expansion valve; 10. a first evaporator; 11. a second boiler; 12. a third ejector; 13. a fourth ejector; 14. a second condenser; 15. a second liquid trap; 16. a second heat exchanger; 17. a third throttle expansion valve; 18. a second refrigerant pump; 19. a fourth throttle expansion valve; 20. a second evaporator; 21. debugging a heat exchanger; 22. a third heat exchanger; 23. a fourth heat exchanger; 24. a fifth heat exchanger; 25. a sixth heat exchanger; 30. a first working vapor line; 31. a second working vapor line; 32. a first mixed vapor line; 33. a second working vapor line; 34. a first mixed vapor line; 35. a second mixed vapor line; 36. a first condenser liquid refrigerant line; 37. a first boiler liquid refrigerant line; 38. a second condenser liquid refrigerant line; 39. a first liquid refrigerant throttling line; 40. a second ejector vapor line; 41. a first evaporator liquid refrigerant subcooling line; 42. a first evaporator liquid refrigerant throttling line; 43. a first injection steam pipeline; 44. a fifth mixed vapor line; 45. a third boiler liquid refrigerant line; 46. a fourth boiler liquid refrigerant line; 47. a third boiler liquid refrigerant line; 50. a third working vapor line; 51. a fourth working vapor line; 52. a third mixed vapor line; 53. a fourth working vapor line; 54. a third mixed vapor line; 55. a fourth mixed vapor line; 56. a third condenser liquid refrigerant line; 57. a second boiler liquid refrigerant line; 58. a fourth condenser liquid refrigerant line; 59. a second liquid refrigerant throttling line; 60. a fourth injection vapor line; 61. a second evaporator liquid refrigerant subcooling line; 62. a second evaporator liquid refrigerant throttling line; 63. a third injection steam pipeline; 64. a sixth mixed vapor line; 65. a fifth boiler liquid refrigerant line; 66. a sixth boiler liquid refrigerant line; 67. a fourth boiler liquid refrigerant line; 70. a primary water inlet; 71. a first primary water line; 72. a second primary water line; 73. a third primary water line; 74. a fourth primary water line; 75. a primary water outlet; 80. a secondary water inlet; 81. a first primary water pipeline; 82. a first secondary water line and a second secondary water line; 83. a first secondary water line; 84. a second secondary water line; 85. a second secondary water line; 86. and a secondary water outlet.

Detailed Description

The invention is further described with reference to the following drawings and specific examples, which are not intended to be limiting.

Referring to fig. 1, there is shown a large temperature difference heat exchange system provided with a plurality of ejectors, comprising: the heat exchanger comprises a first heat exchange system and a second heat exchange system, wherein the first heat exchange system is connected with the second heat exchange system through a plurality of pipelines;

the first heat exchange system comprises: the first boiler 1 comprises a first conveying channel and a second conveying channel, the first condenser 4 comprises a third conveying channel and a fourth conveying channel, the first heat exchanger 6 comprises a fifth conveying channel and a sixth conveying channel, the first evaporator 10 comprises a seventh conveying channel and an eighth conveying channel, the first ejector 2 comprises a first ejector inlet, a first ejector inlet and a first ejector outlet, and the second ejector 3 comprises a second ejector inlet, a second ejector inlet and a second ejector outlet;

the inlet of the first ejector and the inlet of the second ejector are both connected with the outlet of the first conveying channel, the outlet of the first ejector and the outlet of the second ejector are both connected with the inlet of the third conveying channel, the outlet of the third conveying channel is respectively connected with the inlet of the first refrigerant pump 8, the inlet of the fifth conveying channel and the inlet of the sixth conveying channel, the inlet of the first conveying channel is connected with the outlet of the first refrigerant pump 8, the outlet of the fifth conveying channel is connected with the second injection inlet, the outlet of the sixth conveying channel is connected with the inlet of the seventh conveying channel, and the outlet of the seventh conveying channel is connected with the first injection inlet;

the second heat exchange system comprises: the second boiler 11, the third ejector 12, the fourth ejector 13, the second condenser 14, the second heat exchanger 16, the second refrigerant pump 18 and the second evaporator 20, the second boiler 11 comprises an eleventh delivery passage and a twelfth delivery passage, the second condenser 14 comprises a thirteenth delivery passage and a fourteenth delivery passage, the second heat exchanger 16 comprises a fifteenth delivery passage and a sixteenth delivery passage, the second evaporator 20 comprises a seventeenth delivery passage and an eighteenth delivery passage, the third ejector 12 comprises a third ejector inlet, a third ejector inlet and a third ejector outlet, and the fourth ejector 13 comprises a fourth ejector inlet, a fourth ejector inlet and a fourth ejector outlet;

the inlet of the third ejector and the inlet of the fourth ejector are both connected with the outlet of the eleventh conveying channel, the outlet of the third ejector and the outlet of the fourth ejector are both connected with the inlet of the thirteenth conveying channel, the outlet of the thirteenth conveying channel is respectively connected with the inlet of the second refrigerant pump 18, the inlet of the fifteenth conveying channel and the inlet of the sixteenth conveying channel, the inlet of the eleventh conveying channel is connected with the outlet of the second refrigerant pump 18, the outlet of the fifteenth conveying channel is connected with the fourth injection inlet, the outlet of the sixteenth conveying channel is connected with the inlet of the seventeenth conveying channel, and the outlet of the seventeenth conveying channel is connected with the third injection inlet.

Further, in a preferred embodiment, the first heat exchange system further comprises: the first liquid collector 5, the first throttle expansion valve 7 and the second throttle expansion valve 9 are connected at the outlet of the third conveying channel, the first liquid collector 5 is connected at the inlet of the fifth conveying channel, the first throttle expansion valve 7 is connected at the inlet of the fifth conveying channel, and the second throttle expansion valve 9 is connected at the inlet of the seventh conveying channel.

Further, in a preferred embodiment, the second heat exchange system further comprises: a second liquid collector 15, a third throttle expansion valve 17 and a fourth throttle expansion valve 19, wherein the second liquid collector 15 is connected to the outlet of the thirteenth transfer channel, the third throttle expansion valve 17 is connected to the inlet of the fifteenth transfer channel, and the fourth throttle expansion valve 19 is connected to the inlet of the seventeenth transfer channel.

Further, in a preferred embodiment, the method further comprises: the secondary water inlet 80 is connected with one end of a fourth conveying channel, the other end of the fourth conveying channel is connected with one end of a fourteenth conveying channel, and the other end of the fourteenth conveying channel is connected with the secondary water outlet 86.

Further, in a preferred embodiment, the first heat exchange system further comprises: and the third heat exchanger 22 comprises a ninth conveying channel and a tenth conveying channel, an outlet of the first ejector and an outlet of the second ejector are both connected with one end of the ninth conveying channel, the other end of the ninth conveying channel is connected with an inlet of the third conveying channel, and two ends of the tenth conveying channel are respectively connected with an inlet of the first conveying channel and an outlet of the first refrigerant pump 8.

Further, in a preferred embodiment, the second heat exchange system further comprises: and the fourth heat exchanger 23 comprises a nineteenth conveying channel and a twentieth conveying channel, an outlet of the third ejector and an outlet of the fourth ejector are both connected with one end of the nineteenth conveying channel, the other end of the nineteenth conveying channel is connected with an inlet of the thirteenth conveying channel, and two ends of the twentieth conveying channel are respectively connected with an inlet of the eleventh conveying channel and an outlet of the second refrigerant pump 18.

Further, in a preferred embodiment, the method further comprises: the primary water inlet 70, the primary water outlet 75 and the debugging heat exchanger 21, wherein the debugging heat exchanger 21 comprises a twenty-first conveying channel and a twenty-second conveying channel, the primary water inlet 70 is connected with the inlet of the second conveying channel, the outlet of the second conveying channel is connected with the inlet of the twelfth conveying channel, the outlet of the twelfth conveying channel is connected with the inlet of the twenty-second conveying channel, the outlet of the twenty-second conveying channel is connected with the inlet of the eighteenth conveying channel, the outlet of the eighteenth conveying channel is connected with the inlet of the eighth conveying channel, the outlet of the eighth conveying channel is connected with the primary water outlet 75, and two ends of the twenty-first conveying channel are respectively connected with the secondary water inlet 80 and the secondary water outlet 86.

Further, in a preferred embodiment, the method further comprises: the primary water inlet 70, the primary water outlet 75 and the debugging heat exchanger 21, wherein the debugging heat exchanger 21 comprises a twenty-first conveying channel and a twenty-second conveying channel, the primary water inlet 70 is connected with the inlet of the twelfth conveying channel, the outlet of the twelfth conveying channel is connected with the inlet of the second conveying channel, the outlet of the second conveying channel is connected with the inlet of the twenty-second conveying channel, the outlet of the twenty-second conveying channel is connected with the inlet of the eighteenth conveying channel, the outlet of the eighteenth conveying channel is connected with the inlet of the eighth conveying channel, the outlet of the eighth conveying channel is connected with the primary water outlet 75, and two ends of the twenty-first conveying channel are respectively connected with the secondary water inlet 80 and the secondary water outlet 86.

Further, in a preferred embodiment, the method further comprises: a fifth heat exchanger 24 and a sixth heat exchanger 25, the fifth heat exchanger 24 comprising a twenty-third conveying channel and a twenty-fourth conveying channel, the sixth heat exchanger 25 comprising a twenty-fifth conveying channel and a twenty-sixth conveying channel;

The above are merely preferred embodiments of the present invention, and the embodiments and the protection scope of the present invention are not limited thereby.

The present invention also has the following embodiments in addition to the above:

in a further embodiment of the invention, the jet heat pump belongs to one type of heat energy driving heat pump, under the driving of a high-temperature heat source, high-pressure working fluid generated in a boiler is used for ejecting low-pressure ejection fluid generated by an evaporator, and the two fluids are mixed to form medium-pressure mixed fluid which enters a condenser for condensation and heat release, so that heat in the low-temperature heat source is extracted into a high-level heat source. Based on the characteristics, the jet type heat pump system is combined with an external debugging heat exchanger to construct a jet type large temperature difference heat exchange system, so that the deep heat exchange of primary water and secondary water in a heat supply engineering pipe network is realized. A conventional ejector type large temperature difference heat exchange system is shown in fig. 1, and mainly comprises a boiler 1, a condenser 4, an evaporator 10, a first ejector 2, a heat exchanger 21 and associated piping and transportation equipment. Under the action of high-temperature primary water, the boiler 1 boils a Freon refrigerant working medium in the high-temperature primary water to generate high-temperature and high-pressure working steam, and the high-temperature and high-pressure working steam enters the first ejector 2 through the first working steam pipeline 30; similarly, the evaporator 10 evaporates the refrigerant working medium therein into low-pressure injection steam under the action of the primary water with lower temperature, and the low-pressure injection steam enters the first injector 2 through the first injection steam pipeline 43. Under the action of high-pressure working steam, low-pressure injection steam is injected, the low-pressure injection steam is mixed into medium-pressure mixed steam after the pressure is increased, the medium-pressure mixed steam enters the condenser 4 through the first mixed steam pipeline 32 for condensation, the heat is released, the working medium steam changes into a liquid state, the medium-pressure mixed steam flows out of the condenser from the first condenser liquid refrigerant pipeline 36, enters the liquid collector 5 and is divided into two parts, and one part flows into the evaporator 10 through the evaporator liquid refrigerant throttling pipeline 42 and flows through the second throttling expansion valve 9; the other strand passes through a liquid refrigerant pipeline 37 of the boiler and enters the boiler 1 through a refrigerant pump 8, thereby completing the circulation of refrigerant working media. On the other hand, the high-temperature primary water flows into the system through the primary water inlet 70, passes through the boiler 1, the pilot heat exchanger 21, and the evaporator 10 in this order through the primary water pipe 72, decreases in temperature, releases heat, and then flows out of the system through the primary water outlet 75. Secondary water flows into the system through a secondary water inlet 80 and is divided into two streams, one stream is condensed heat absorbed by the condenser 4 through a first secondary water pipeline 81, and the other stream is mixed with the first stream of water and flows out of the system from a secondary water outlet 86 after heat exchange is carried out on the secondary water and the primary water through a second secondary water pipeline 84 and a debugging heat exchanger 21. In the process, the primary water is cooled for many times, and the outlet temperature can be reduced to be lower than the inlet temperature of the secondary water under certain working conditions, so that the heat exchange process with large temperature difference is realized.

In a further embodiment of the present invention, as described in fig. 2, a large temperature difference heat exchange system with a plurality of ejectors includes: the system comprises a first boiler 1, a first ejector 2, a second ejector 3, a first condenser 4, a first liquid collector 5, a first heat exchanger 6, a first throttle expansion valve 7, a first refrigerant pump 8, a second throttle expansion valve 9, a first evaporator 10, a second boiler 11, a third ejector 12, a fourth ejector 13, a second condenser 14, a second liquid collector 15, a second heat exchanger 16, a third throttle expansion valve 17, a second refrigerant pump 18, a fourth throttle expansion valve 19, a second evaporator 20, a debugging heat exchanger 21, a first working vapor pipeline 30, a second working vapor pipeline 31, a first-to-mixed vapor pipeline 32, a second working vapor pipeline 33, a first-to-mixed vapor pipeline 34, a second mixed vapor pipeline 35, a first condenser liquid refrigerant pipeline 36, a first boiler liquid refrigerant pipeline 37, a second condenser liquid refrigerant pipeline 38, a first condenser liquid refrigerant pipeline 33, a second boiler liquid refrigerant pipeline 34, a second condenser liquid refrigerant pipeline 38, A first liquid refrigerant throttling pipeline 39, a second injection steam pipeline 40, a first evaporator liquid refrigerant supercooling pipeline 41, a first evaporator liquid refrigerant throttling pipeline 42, a first injection steam pipeline 43, a third working steam pipeline 50, a fourth working steam pipeline 51, a third mixed steam pipeline 52, a fourth working steam pipeline 53, a third mixed steam pipeline 54, a fourth mixed steam pipeline 55, a third condenser liquid refrigerant pipeline 56, a second boiler liquid refrigerant pipeline 57, a fourth condenser liquid refrigerant pipeline 58, a second liquid refrigerant throttling pipeline 59, a fourth injection steam pipeline 60, a second evaporator liquid refrigerant supercooling pipeline 61, a second evaporator liquid refrigerant throttling pipeline 62, a third injection steam pipeline 63, a primary water inlet 70, a first primary water pipeline 71, a second primary water pipeline 72, A third primary water line 73, a fourth primary water line 74, a primary water outlet 75, a secondary water inlet 80, a first primary water line 81, a first secondary water line 82, a first tertiary water line 83, a second secondary water line 84, a second secondary water line 85, and a secondary water outlet 86.

The connection mode of the internal circulation working medium pipeline is as follows: the outlet of the first boiling device 1 is connected with a first working vapor pipeline 30, the first working vapor pipeline 30 is divided into two paths, one path is communicated with the first ejector 2 through a second working vapor pipeline 31, the outlet of the first ejector 2 is connected with a first mixed vapor pipeline 32, the other path is communicated with the second ejector 3 through a second working vapor pipeline 33, the outlet of the second ejector 3 is connected with a first mixed vapor pipeline 34, the first mixed vapor pipeline 32 and the first mixed vapor pipeline 34 are converged into one path to be communicated with a second mixed vapor pipeline 35, the second mixed vapor pipeline 35 is communicated with the condenser 4, the condenser 4 is communicated with the two paths of the liquid collecting device 5 through a first condenser liquid refrigerant pipeline 36, the first condenser liquid refrigerant pipeline 36 is divided into two paths, and one path is communicated with the boiling device 1 through a first boiling device liquid refrigerant pipeline 37 and a refrigerant pump 8, the other path is divided into two paths through a second condenser liquid refrigerant pipeline 38, one path is connected to a first liquid refrigerant throttling pipeline 39 and enters a first heat exchanger 6 through a first throttling expansion valve 7, the outlet of the first heat exchanger 6 returns to a second ejector 3 through a second injection vapor pipeline 40, the other path enters the first heat exchanger 6 through a first evaporator liquid refrigerant supercooling pipeline 41, the outlet of the first heat exchanger 6 passes through a first evaporator liquid refrigerant throttling pipeline 42 and is communicated with a first evaporator 10 through a second throttling expansion valve 9, the outlet of the first evaporator 10 returns to a first ejector 2 through a first injection vapor pipeline 43, the outlet of the second evaporator 11 is connected with a third working vapor pipeline 50, the third working pipeline 50 is divided into two paths, one path is communicated with a third ejector 12 through a fourth working vapor pipeline 51, the outlet of the third ejector 12 is connected with a third mixed vapor pipeline 52, the other path is communicated with a fourth ejector 13 through a fourth second working vapor pipeline 53, the outlet of the fourth ejector 13 is connected with a third mixed vapor pipeline 54, the third mixed vapor pipeline 52 and the third mixed vapor pipeline 54 are converged into one path and communicated with a fourth mixed vapor pipeline 55, the fourth mixed vapor pipeline 55 is communicated with a second condenser 14, the second condenser 14 is communicated with a second liquid collector 15 through a third condenser liquid refrigerant pipeline 56, the third condenser liquid refrigerant pipeline 56 is divided into two paths, one path is communicated with a second boiler 11 through a second boiler liquid refrigerant pipeline 57 and a second boiler 18, the other path is divided into two paths through a fourth condenser liquid refrigerant pipeline 58, one path is connected to a second liquid refrigerant throttling pipeline 59 and enters a second heat exchanger 16 through a third throttling valve 17, the outlet of the second heat exchanger 16 returns to the fourth ejector 13 through a fourth ejector vapor expansion valve 60, the other path of the refrigerant liquid enters the second heat exchanger 16 through a second evaporator liquid refrigerant supercooling pipeline 61, the outlet of the second heat exchanger 16 passes through a second evaporator liquid refrigerant throttling pipeline 62 and is communicated with the second evaporator 20 through a fourth throttling expansion valve 19, and the outlet of the second evaporator 20 returns to the third ejector 12 through a third ejector steam pipeline 63.

The connection relationship of the external water circulation is as follows: the first boiler 1 is connected to the second boiler 11 through a first primary water line 71, the second boiler 11 is connected to the pilot heat exchanger 21 through a second primary water line 72, the pilot heat exchanger 21 is connected to the second evaporator 20 through a third primary water line 73, and the second evaporator 20 is connected to the first evaporator 10 through a fourth primary water line 74. The secondary water entering the system is divided into two paths, wherein one path flows through the debugging heat exchanger 21 through a second secondary water pipeline 84 and continues to pass through a second secondary water pipeline 85, the other path flows through the first condenser 4 through a first primary water pipeline 81, continues to flow through the second condenser 14 through a first secondary water pipeline 82, continues to pass through a first tertiary water pipeline 83, and the two paths are mixed and then flow out of the system from a secondary water outlet 86.

In a further embodiment of the present invention, according to this structure, the first boiler 1, the second boiler 11, the first evaporator 10, and the second evaporator 20 are heated by the primary water, and the first condenser 4 and the second condenser 14 are cooled by the secondary water. The primary water exchanges heat with the secondary water in the second primary and secondary water pipe 84 in the trim heat exchanger.

In a further embodiment of the invention, in the first technical scheme of the invention, a two-section jet type large temperature difference heat exchange system is adopted, and part of working medium at the outlet of a liquid collector 5 is subcooled through a first heat exchanger 6, a first throttle expansion valve 7 and a second throttle expansion valve 9, so that the operation efficiency of heat pump circulation in the jet type large temperature difference heat exchange system is improved, the integral heat exchange effect of the heat exchange system is improved through energy cascade utilization, and in addition, in the system, secondary water respectively passes through a debugging heat exchanger 21, a first condenser 4 and a second condenser 14 through parallel pipelines.

In a further embodiment of the present invention, an operation flow of a large temperature difference heat exchange system provided with a plurality of ejectors comprises an external water flow and an internal working medium circulation flow, wherein the external water flow is as follows:

the primary water of high temperature flows into the large-temperature-difference heat exchange unit through the primary water inlet 70 of the system, sequentially flows through the first boiler 1, the second boiler 11, the debugging heat exchanger 21, the second evaporator 20 and the first evaporator 10 through the primary water pipeline, and flows out from the primary water outlet 75 after the temperature is gradually reduced. Secondary water enters the large-temperature-difference heat exchange unit through the secondary water inlet 80 and then is divided into two streams, one stream enters the first condenser 4 through the first one-to-one secondary water pipeline 81 to absorb condensation heat and continues to enter the second condenser 14 through the first two-to-two secondary water pipeline 82 to absorb condensation heat, the other stream enters the debugging heat exchanger 21 through the second one-to-two secondary water pipeline 84 to exchange heat with primary water, and finally the two streams of water are mixed and then flow out of the unit through the secondary water outlet 86.

The ejector heat pump cycle of the first stage and the ejector heat pump cycle of the second stage have the same structure, so the operation flows of the two are the same, and the operation flow of the internal circulation working medium is described by taking the ejector heat pump cycle of the first stage as an example:

under the action of high-temperature primary water, a liquid working medium is converted into a high-temperature high-pressure gaseous working medium in a first boiling device 1, the high-temperature high-pressure gaseous working medium is divided into two paths through a first working steam pipeline 30, one path enters a first ejector 2 through a second working steam pipeline 31 to eject low-pressure steam from a first ejection steam pipeline 43, the two fluids are mixed to form medium-pressure fluid, the medium-pressure fluid flows out of the first ejector 2 to enter a first one-to-one mixed steam pipeline 32, the other path enters a second ejector 3 through a second working steam pipeline 33 to eject low-pressure steam from a second ejection steam pipeline 40, the two fluids are mixed to form the medium-pressure fluid, the medium-pressure fluid flows out of the second ejector 3 to enter a first two-to-two mixed steam pipeline 34, the medium-pressure fluid from the first one-to-one-way and the first two-to-two mixed steam pipeline 34 is converged into a first mixed steam pipeline 35 to enter a first condenser 4, the gaseous working medium is condensed and releases heat in the first condenser 4 to form the liquid working medium, the refrigerant is further divided into two paths through a first condenser liquid refrigerant pipeline 36, one path enters a first boiler 1 through a first boiler liquid refrigerant pipeline 37 under the action of a first refrigerant pump 8 to be continuously boiled, the other path is divided into two paths through a second condenser liquid refrigerant pipeline 38, one path enters a first heat exchanger 6 through a first evaporator liquid refrigerant supercooling pipeline 41, the liquid refrigerant is supercooled in the first heat exchanger 6, the supercooled liquid refrigerant enters a first evaporator 10 after being cooled and decompressed through a second throttling expansion valve 9 to be evaporated and absorbed into low-pressure gaseous refrigerant, the low-pressure gaseous refrigerant enters a first ejector 2 through a first injection steam pipeline 43, the other path enters a first throttling expansion valve 7 through a first liquid refrigerant throttling pipeline 39 to be cooled and decompressed, the liquid refrigerant after being cooled and decompressed enters the first heat exchanger 6 to be evaporated and absorbed into low-pressure gaseous refrigerant, the low-pressure gas refrigerant enters the second ejector 3 through the second injection steam pipeline 40, so that the working medium circulation is completed, and in the working medium circulation, due to the arrangement of the supercooling device, the redundant heat of the condensed liquid working medium is recovered, and the circulation efficiency of the heat pump system is improved.

In a further embodiment of the present invention, a second technical solution is described with reference to fig. 3, and a large temperature difference heat exchange system with a plurality of ejectors includes: a first boiler 1, a first ejector 2, a second ejector 3, a first condenser 4, a first liquid collector 5, a first heat exchanger 6, a first throttle expansion valve 7, a first refrigerant pump 8, a second throttle expansion valve 9, a first evaporator 10, a second boiler 11, a third ejector 12, a fourth ejector 13, a second condenser 14, a second liquid collector 15, a second heat exchanger 16, a third throttle expansion valve 17, a second refrigerant pump 18, a fourth throttle expansion valve 19, a second evaporator 20, a pilot heat exchanger 21, a third heat exchanger 22, a fourth heat exchanger 23, a first working vapor pipeline 30, a second working vapor pipeline 31, a first one-to-one mixed vapor pipeline 32, a second working vapor pipeline 33, a first two-to-mixed vapor pipeline 34, a second mixed vapor pipeline 35, a first condenser vapor pipeline 36, a first boiler liquid refrigerant pipeline 37, a second boiler liquid refrigerant pipeline 15, a second boiler liquid refrigerant pipeline 13, a second boiler liquid refrigerant pump 18, a second evaporator 19, a third evaporator, a fourth evaporator, a second condenser liquid refrigerant line 38, a first liquid refrigerant throttling line 39, a second ejector vapor line 40, a first evaporator liquid refrigerant subcooling line 41, a first evaporator liquid refrigerant throttling line 42, a first ejector vapor line 43, a fifth mixed vapor line 44, a third boiler liquid refrigerant line 45, a fourth boiler liquid refrigerant line 46, a third working vapor line 50, a fourth working vapor line 51, a third mixed vapor line 52, a fourth working vapor line 53, a third mixed vapor line 54, a fourth mixed vapor line 55, a third condenser liquid refrigerant line 56, a second boiler liquid refrigerant line 57, a fourth condenser liquid refrigerant line 58, a second liquid refrigerant throttling line 59, a fourth ejector vapor line 60, a second evaporator liquid refrigerant subcooling line 61, a first evaporator liquid refrigerant subcooling line 45, a second evaporator liquid refrigerant subcooling line 45, a fourth boiler liquid refrigerant line 50, a fourth working vapor line 51, a third mixed vapor line 52, a fourth working vapor line 53, a third mixed vapor line 54, a fourth mixed vapor line 55, a third condenser liquid refrigerant line 56, a second boiler liquid refrigerant line 57, a fourth condenser liquid refrigerant throttling line 59, a fourth ejector vapor line 60, a second evaporator liquid refrigerant line 61, a second ejector vapor line 60, a second evaporator liquid refrigerant subcooling line 61, a fourth evaporator liquid refrigerant line, A second evaporator liquid refrigerant throttling line 62, a third ejector steam line 63, a sixth mixed vapor line 64, a fifth boiler liquid refrigerant line 65, a sixth boiler liquid refrigerant line 66, a primary water inlet 70, a first primary water line 71, a second primary water line 72, a third primary water line 73, a fourth primary water line 74, a primary water outlet 75, a secondary water inlet 80, a first primary secondary water line 81, a first secondary water line 82, a first tertiary secondary water line 83, a second primary water line 84, a second secondary water line 85, and a secondary water outlet 86.

The connection mode of the internal circulation working medium pipeline is as follows: the outlet of the first boiling device 1 is connected with a first working vapor pipeline 30, the first working vapor pipeline 30 is divided into two paths, one path is communicated with a first ejector 2 through a second working vapor pipeline 31, the outlet of the first ejector 2 is connected with a first mixed vapor pipeline 32, the other path is communicated with a second ejector 3 through a second working vapor pipeline 33, the outlet of the second ejector 3 is connected with a first mixed vapor pipeline 34, the first mixed vapor pipeline 32 and the first mixed vapor pipeline 34 are converged into one path to be communicated with a fifth mixed vapor pipeline 44, the fifth mixed vapor pipeline 44 is communicated with a third heat exchanger 22, the outlet of the third heat exchanger 22 is connected with a second mixed vapor pipeline 35, the second mixed vapor pipeline 35 is communicated with a first condenser 4, the first condenser 4 is communicated with a liquid collector 5 through a first condenser liquid refrigerant pipeline 36, the first condenser liquid refrigerant pipeline 36 is divided into two paths, one path is communicated with a first refrigerant pump 8 through a fourth boiler liquid refrigerant pipeline 46, the outlet of the first refrigerant pump 8 is connected with a third boiler liquid refrigerant pipeline 45, the third boiler liquid refrigerant pipeline 45 is communicated with a third heat exchanger 22, the outlet of the third heat exchanger 22 is connected with a first boiler liquid refrigerant pipeline 37, the first boiler liquid refrigerant pipeline 37 is communicated with a first boiler 1, the other path is divided into two paths through a second condenser liquid refrigerant pipeline 38, one path is connected to a first liquid refrigerant throttling pipeline 39 and enters a first heat exchanger 6 through a first throttling expansion valve 7, the outlet of the first heat exchanger 6 returns to a second ejector 3 through a second ejector vapor pipeline 40, the other path enters the first heat exchanger 6 through a first evaporator liquid refrigerant supercooling pipeline 41, the outlet of the first heat exchanger 6 passes through a first evaporator liquid refrigerant throttling pipeline 42, the outlet of the evaporator 10 returns to the first ejector 2 through a first injection steam pipeline 43, the outlet of the second boiler 11 is connected with a third working steam pipeline 50, the third working steam pipeline 50 is divided into two paths, one path is communicated with the third ejector 12 through a fourth working steam pipeline 51, the outlet of the third ejector 12 is connected with a third mixed steam pipeline 52, the other path is communicated with the fourth ejector 13 through a fourth working steam pipeline 53, the outlet of the fourth ejector 13 is connected with a third mixed steam pipeline 54, the third mixed steam pipeline 52 and the third mixed steam pipeline 54 are converged into one path and communicated with a sixth mixed steam pipeline 64, the sixth mixed steam pipeline 64 is communicated with a fourth heat exchanger 23, the outlet of the fourth heat exchanger 23 is connected with a fourth mixed steam pipeline 55, the fourth mixed steam pipeline 55 is communicated with a second condenser 14, the second condenser 14 is communicated with the second liquid collector 15 through a third condenser liquid refrigerant pipeline 56, the third condenser liquid refrigerant pipeline 56 is divided into two paths, one path is communicated with the second refrigerant pump 18 through a sixth boiler liquid refrigerant pipeline 66, the outlet of the second refrigerant pump 18 is connected with a fifth boiler liquid refrigerant pipeline 65, the fifth boiler liquid refrigerant pipeline 65 is communicated with the fourth heat exchanger 23, the outlet of the fourth heat exchanger 23 is connected with a second boiler liquid refrigerant pipeline 57, the second boiler liquid refrigerant pipeline 57 is communicated with the second boiler 11, the other path is divided into two paths through a fourth condenser liquid refrigerant pipeline 58, one path is connected to a second liquid refrigerant throttling pipeline 59, enters the second heat exchanger 16 through a third throttling expansion valve 17, the outlet of the second heat exchanger 16 returns to the fourth ejector 13 through a fourth ejector vapor pipeline 60, the other path of the refrigerant liquid enters the second heat exchanger 16 through a second evaporator liquid refrigerant supercooling pipeline 61, the outlet of the second heat exchanger 16 passes through a second evaporator liquid refrigerant throttling pipeline 62 and is communicated with the second evaporator 20 through a fourth throttling expansion valve 19, and the outlet of the second evaporator 20 returns to the third ejector 12 through a third ejector steam pipeline 63.

In a further embodiment of the present invention, according to this structure, the first boiler 1, the second boiler 11, the first evaporator 10, and the second evaporator 20 are heated by the primary water, and the first condenser 4 and the second condenser 14 are cooled by the secondary water. The primary water exchanges heat with the secondary water in the second primary and secondary water line 84 in the trim heat exchanger.

In a further embodiment of the present invention, the external water operation flow of the present embodiment is identical to the first embodiment, and the ejector heat pump cycle of the first stage and the ejector heat pump cycle of the second stage have the same structure, so that the operation flows of the two are identical, and taking the ejector heat pump cycle of the first stage as an example, the operation flow of the internal cycle working medium is described as follows:

a high-temperature heat source flows into the first boiler 1 through the high-temperature heat source inlet 70 and then flows out from the high-temperature heat source outlet 75, heat is released in the high-temperature heat source, a liquid refrigerant is converted into a high-temperature high-pressure gaseous refrigerant in the first boiler 1 and is divided into two paths through the first working vapor pipeline 30, one path enters the first ejector 2 through the second working vapor pipeline 31 to inject a low-pressure gaseous refrigerant from the first evaporator 10, the two fluids are mixed to form a medium-pressure gaseous refrigerant and flow out of the first ejector 2, the other path enters the second ejector 3 through the second working vapor pipeline 33 to inject a low-pressure gaseous refrigerant from the first heat exchanger 6, the two fluids are mixed to form a medium-pressure gaseous refrigerant and flow out of the second ejector 3, the fluid flowing out of the first ejector 2 and the fluid flowing out of the second ejector 3 are mixed to enter the third heat exchanger 22, heat is released in the third heat exchanger 22 to preheat the liquid working medium entering the boiler, so that the heat consumed in the first boiler 1 is reduced, high-temperature steam flows out of the third heat exchanger 22 and then enters the first condenser 4, the high-temperature and high-pressure gaseous working medium is condensed in the first condenser 4 to release heat and is changed into the liquid working medium, and the liquid working medium is divided into two paths through a first condenser liquid refrigerant pipeline 36; one path enters the third heat exchanger 22 through the fourth boiler liquid refrigerant pipeline 46 under the action of the first refrigerant pump 8 to absorb heat and then enters the first boiler 1 through the first boiler liquid refrigerant pipeline 37 to continue boiling, the other path is divided into two paths through the second condenser liquid refrigerant pipeline 38, one path is cooled and decompressed under the action of the first throttle expansion valve 7, enters the first heat exchanger 6 to absorb heat to become low-pressure gaseous refrigerant and then returns to the second ejector 3 to complete a part of working medium circulation, the other path directly enters the first heat exchanger 6 to be subcooled, is cooled and decompressed under the action of the second throttle expansion valve 9, flows into the first evaporator 10 to continue evaporating to become low-pressure gaseous refrigerant, and returns to the first ejector 2 through the first ejector steam pipeline 43 to complete the working medium circulation, and in the working medium circulation, the liquid working medium entering the boiler is preheated by the heat of superheated steam, therefore, the heat consumed in the first boiling device 1 is reduced, the circulation efficiency of the heat pump system is further improved, and the operation effect of the jet type large-temperature-difference heat exchange system is further improved.

In a further embodiment of the present invention, as shown in fig. 4, in a third technical solution, on the basis of the second technical solution, in order to further improve the operation efficiency of the jet heat pump cycle part in the two-stage jet large temperature difference heat exchanger unit, the liquid working mediums entering the first boiler 1 and the second boiler 11 are further preheated. Therefore, in this embodiment, the fifth heat exchanger 24 and the sixth heat exchanger 25 are added. The fifth heat exchanger 24 is disposed between the second primary water line 72 and the third primary water line 73, and the first boiler liquid refrigerant line 37 and the third boiler liquid refrigerant line 47, specifically, the device is disposed between the commissioning heat exchanger 21 and the first boiler 1 of the primary water line, and is disposed between the third heat exchanger 22 and the first boiler 1 on the boiler liquid refrigerant line, and the sixth heat exchanger 25 is disposed between the third primary water line 73 and the fourth primary water line 74, and the second boiler liquid refrigerant line 57 and the fourth boiler liquid refrigerant line 67 on the primary water line, and specifically, the device is disposed between the commissioning heat exchanger 21 and the first boiler 1 on the primary water line, and is disposed between the fourth heat exchanger 23 and the second boiler 11 on the boiler liquid refrigerant line.

the high-temperature primary water flows into the large-temperature-difference heat exchange unit through the primary water inlet 70 of the system, sequentially flows through the second boiler 11, the first boiler 1, the fifth heat exchanger 24, the sixth heat exchanger 25, the adapting heat exchanger 21, the second evaporator 20 and the first evaporator 10 through the primary water pipeline, and flows out from the primary water outlet 77 after the temperature is gradually reduced. Secondary water enters the large-temperature-difference heat exchange unit through a secondary water inlet 80 and then is divided into two streams, one stream enters the first condenser 4 through a first one-to-one secondary water pipeline 81 to absorb condensation heat and continues to enter the second condenser 14 through a first two-to-two secondary water pipeline 82 to absorb condensation heat, the other stream enters the debugging heat exchanger 21 through a second one-to-two secondary water pipeline 84 to exchange heat with primary water, and finally the two streams of water are mixed and then flow out of the unit through a secondary water outlet 86.

Similarly, a first-stage injection heat pump part is used to describe the circulation flow of internal working medium, a high-temperature heat source flows into the first boiler 1 through the high-temperature heat source inlet 70 and then flows out from the high-temperature heat source outlet 77, heat is released therein, the liquid refrigerant is converted into high-temperature high-pressure gaseous working medium in the first boiler 1 and is divided into two paths through the first working vapor pipeline 30, one path enters the first ejector 2 through the second working vapor pipeline 31 to eject the low-pressure gaseous refrigerant from the first evaporator 10, wherein the two fluids are mixed to become medium-pressure gaseous refrigerant and flow out of the first ejector 2, the other path enters the second ejector 3 through the second working vapor pipeline 33 to eject the low-pressure gaseous refrigerant from the first heat exchanger 6, wherein the two fluids are mixed to become medium-pressure gaseous refrigerant and flow out of the second ejector 3, the fluid flowing out of the first ejector 2 and the fluid flowing out of the second ejector 3 are mixed and flow into the third heat exchanger 22, heat is released in the third heat exchanger 22 to preheat the liquid working medium entering the boiler, so that the heat consumed in the first boiler 1 is reduced, high-temperature steam flows out of the third heat exchanger 22 and then enters the first condenser 4, the high-temperature and high-pressure gaseous working medium is condensed in the first condenser 4 to release heat and is changed into the liquid working medium, and the liquid working medium is divided into two paths through a first condenser liquid refrigerant pipeline 36; one path enters the third heat exchanger 22 through the fourth boiler liquid refrigerant pipeline 46 under the action of the first refrigerant pump 8 to absorb heat and then enters the fifth heat exchanger 24 through the third boiler liquid refrigerant pipeline 47 to absorb heat and then enters the first boiler 1 through the first boiler liquid refrigerant pipeline 37 to continue boiling, the other path is divided into two paths through the second condenser liquid refrigerant pipeline 38, one path enters the first heat exchanger 6 to absorb heat and become low-pressure gaseous refrigerant after being cooled and decompressed under the action of the first throttle expansion valve 7 and then returns to the second ejector 3 to complete a part of working medium circulation, the other path directly enters the first heat exchanger 6 to be supercooled, then is cooled and decompressed under the action of the second throttle expansion valve 9, flows into the first evaporator 10 to continue evaporation and then becomes low-pressure gaseous refrigerant through the first injection steam pipeline 43 to return to the first ejector 2, thereby accomplish the circulation of working medium, in the working medium circulation, adopt the heat of superheated steam to preheat the liquid working medium that gets into the boiling ware to reduce the heat that consumes in the first boiling ware 1, further promote heat pump system's circulation efficiency, and then promote the operation effect of big difference in temperature heat transfer system of injection formula.

In a further embodiment of the invention, compared with the traditional single-section jet type large-temperature-difference heat exchange system, the traditional jet type large-temperature-difference heat exchange system is improved, so that the throttling, cooling and depressurizing liquid refrigerant is used for supercooling a part of liquid refrigerant at the outlet of the condenser, the refrigerating capacity is increased, the exhaust temperature is reduced, and the circulation efficiency of the jet type refrigerating cycle system is improved.

In a further embodiment of the invention, compared with the traditional single-section jet type large-temperature-difference heat exchange system, the large-temperature-difference heat exchange system is constructed by adopting a double-section jet type structure, so that the utilization of the energy of primary water in a temperature-to-opening and gradient manner is realized, the primary water and secondary water are cooled and heated in a double-section manner, the utilization of heat energy in the system is effectively improved, the circulating operation efficiency of the jet type heat pump in each section is improved, and the heat exchange effect and the heat exchange quantity of the whole heat exchange unit are enhanced.

In a further embodiment of the invention, compared with the traditional single-section injection type large-temperature-difference heat exchange system, due to the segmented arrangement, the ejector in each section can operate under relatively appropriate and stable working conditions, so that the large-temperature-difference heat exchange unit operates more stably as a whole.

In a further embodiment of the invention, the jet type large-temperature-difference heat exchange system is used in a heat supply project, the jet type large-temperature-difference heat exchange system is improved, the throttling, cooling and depressurizing liquid refrigerant is used for supercooling a part of liquid refrigerant at the outlet of the condenser, the refrigerating capacity is increased, the exhaust temperature is reduced, the large-temperature-difference heat exchange system is constructed by adopting a two-section jet type structure, the utilization of primary water energy is realized, the two-section cooling and heating of the primary water and the secondary water are realized, the utilization of heat energy in the system is effectively improved, the jet in each section can operate under a relatively proper and stable working condition, the large-temperature-difference heat exchange unit operates more stably, and the operating efficiency of the jet type heat pump cycle is improved.

While the invention has been described with reference to a preferred embodiment, it will be understood by those skilled in the art that various changes in form and detail may be made therein without departing from the spirit and scope of the invention.

Claims

1. A large temperature difference heat exchange system provided with a plurality of ejectors, comprising: the heat exchanger is characterized in that the first heat exchange system is connected with the second heat exchange system through a plurality of pipelines;

the first heat exchange system comprises: the heat exchanger comprises a first boiler (1), a first ejector (2), a second ejector (3), a first condenser (4), a first heat exchanger (6), a first refrigerant pump (8) and a first evaporator (10), wherein the first boiler (1) comprises a first conveying channel and a second conveying channel, the first condenser (4) comprises a third conveying channel and a fourth conveying channel, the first heat exchanger (6) comprises a fifth conveying channel and a sixth conveying channel, the first evaporator (10) comprises a seventh conveying channel and an eighth conveying channel, the first ejector (2) comprises a first ejector inlet, a first ejector inlet and a first ejector outlet, and the second ejector (3) comprises a second ejector inlet, a second ejector inlet and a second ejector outlet;

the inlet of the first ejector and the inlet of the second ejector are both connected with the outlet of a first conveying channel, the outlet of the first ejector and the outlet of the second ejector are both connected with the inlet of a third conveying channel, the outlet of the third conveying channel is respectively connected with the inlet of a first refrigerant pump (8), the inlet of a fifth conveying channel and the inlet of a sixth conveying channel, the inlet of the first conveying channel is connected with the outlet of the first refrigerant pump (8), the outlet of the fifth conveying channel is connected with a second injection inlet, the outlet of the sixth conveying channel is connected with the inlet of a seventh conveying channel, and the outlet of the seventh conveying channel is connected with a first injection inlet;

the second heat exchange system comprises: a second boiler (11), a third ejector (12), a fourth ejector (13), a second condenser (14), a second heat exchanger (16), a second refrigerant pump (18), and a second evaporator (20), wherein the second boiler (11) comprises an eleventh transfer passage and a twelfth transfer passage, the second condenser (14) comprises a thirteenth transfer passage and a fourteenth transfer passage, the second heat exchanger (16) comprises a fifteenth transfer passage and a sixteenth transfer passage, the second evaporator (20) comprises a seventeenth transfer passage and an eighteenth transfer passage, the third ejector (12) comprises a third ejector inlet, and a third ejector outlet, and the fourth ejector (13) comprises a fourth ejector inlet, and a fourth ejector outlet;

the inlet of the third ejector and the inlet of the fourth ejector are both connected with the outlet of an eleventh conveying channel, the outlet of the third ejector and the outlet of the fourth ejector are both connected with the inlet of a thirteenth conveying channel, the outlet of the thirteenth conveying channel is respectively connected with the inlet of a second refrigerant pump (18), the inlet of a fifteenth conveying channel and the inlet of a sixteenth conveying channel, the inlet of the eleventh conveying channel is connected with the outlet of the second refrigerant pump (18), the outlet of the fifteenth conveying channel is connected with the fourth injection inlet, the outlet of the sixteenth conveying channel is connected with the inlet of a seventeenth conveying channel, and the outlet of the seventeenth conveying channel is connected with the third injection inlet.

2. The large temperature differential heat exchange system provided with a plurality of ejectors as set forth in claim 1, wherein said first heat exchange system further comprises: the device comprises a first liquid collector (5), a first throttle expansion valve (7) and a second throttle expansion valve (9), wherein the first liquid collector (5) is connected to an outlet of a third conveying channel, the first throttle expansion valve (7) is connected to an inlet of a fifth conveying channel, and the second throttle expansion valve (9) is connected to an inlet of a seventh conveying channel.

3. The large temperature differential heat exchange system provided with a plurality of ejectors as set forth in claim 2, wherein the second heat exchange system further comprises: the liquid level control device comprises a second liquid collector (15), a third throttle expansion valve (17) and a fourth throttle expansion valve (19), wherein the outlet of the thirteenth conveying channel is connected with the second liquid collector (15), the inlet of the fifteenth conveying channel is connected with the third throttle expansion valve (17), and the inlet of the seventeenth conveying channel is connected with the fourth throttle expansion valve (19).

4. The large temperature difference heat exchange system provided with a plurality of ejectors, according to claim 3, further comprising: the secondary water inlet (80) is connected with one end of a fourth conveying channel, the other end of the fourth conveying channel is connected with one end of a fourteenth conveying channel, and the other end of the fourteenth conveying channel is connected with the secondary water outlet (86).

5. The large temperature difference heat exchange system provided with a plurality of ejectors, according to claim 4, wherein the first heat exchange system further comprises: and the third heat exchanger (22) comprises a ninth conveying channel and a tenth conveying channel, the outlet of the first ejector and the outlet of the second ejector are both connected with one end of the ninth conveying channel, the other end of the ninth conveying channel is connected with the inlet of the third conveying channel, and the two ends of the tenth conveying channel are respectively connected with the inlet of the first conveying channel and the outlet of the first refrigerant pump (8).

6. The large temperature differential heat exchange system provided with a plurality of ejectors as set forth in claim 5, wherein said second heat exchange system further comprises: and the fourth heat exchanger (23) comprises a nineteenth conveying channel and a twentieth conveying channel, the outlet of the third ejector and the outlet of the fourth ejector are both connected with one end of the nineteenth conveying channel, the other end of the nineteenth conveying channel is connected with the inlet of the thirteenth conveying channel, and the two ends of the twentieth conveying channel are respectively connected with the inlet of the eleventh conveying channel and the outlet of the second refrigerant pump (18).

7. The large temperature difference heat exchange system provided with a plurality of ejectors, according to claim 4, further comprising: the debugging heat exchanger (21) comprises a twenty-first conveying channel and a twenty-second conveying channel, the primary water inlet (70) is connected with the inlet of the second conveying channel, the outlet of the second conveying channel is connected with the inlet of the twelfth conveying channel, the outlet of the twelfth conveying channel is connected with the inlet of the twenty-second conveying channel, the outlet of the twenty-second conveying channel is connected with the inlet of the eighteenth conveying channel, the outlet of the eighteenth conveying channel is connected with the inlet of the eighth conveying channel, the outlet of the eighth conveying channel is connected with the primary water outlet (75), and the two ends of the twenty-first conveying channel are respectively connected with the secondary water inlet (80) and the secondary water outlet (86).

8. The large temperature difference heat exchange system provided with a plurality of ejectors, according to claim 6, further comprising: the debugging heat exchanger (21) comprises a twenty-first conveying channel and a twenty-second conveying channel, the primary water inlet (70) is connected with the inlet of the second conveying channel, the outlet of the second conveying channel is connected with the inlet of the twelfth conveying channel, the outlet of the twelfth conveying channel is connected with the inlet of the twenty-second conveying channel, the outlet of the twenty-second conveying channel is connected with the inlet of the eighteenth conveying channel, the outlet of the eighteenth conveying channel is connected with the inlet of the eighth conveying channel, the outlet of the eighth conveying channel is connected with the primary water outlet (75), and the two ends of the twenty-first conveying channel are respectively connected with the secondary water inlet (80) and the secondary water outlet (86).

9. The large temperature difference heat exchange system provided with a plurality of ejectors, according to claim 6, further comprising: the debugging heat exchanger (21) comprises a twenty-first conveying channel and a twenty-second conveying channel, the inlet of the primary water inlet (70) is connected with the inlet of the twelfth conveying channel, the outlet of the twelfth conveying channel is connected with the inlet of the second conveying channel, the outlet of the second conveying channel is connected with the inlet of the twenty-second conveying channel, the outlet of the twenty-second conveying channel is connected with the inlet of the eighteenth conveying channel, the outlet of the eighteenth conveying channel is connected with the inlet of the eighth conveying channel, the outlet of the eighth conveying channel is connected with the primary water outlet (75), and the two ends of the twenty-first conveying channel are respectively connected with the secondary water inlet (80) and the secondary water outlet (86).

10. The large temperature difference heat exchange system provided with a plurality of ejectors according to claim 9, further comprising: a fifth heat exchanger (24) and a sixth heat exchanger (25), the fifth heat exchanger (24) comprising a twenty-third conveyance channel and a twenty-fourth conveyance channel, the sixth heat exchanger (25) comprising a twenty-fifth conveyance channel and a twenty-sixth conveyance channel;