CN113280523A - Injection type heat pump circulating device with supercooling and preheating functions - Google Patents
Injection type heat pump circulating device with supercooling and preheating functions Download PDFInfo
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- CN113280523A CN113280523A CN202110601098.6A CN202110601098A CN113280523A CN 113280523 A CN113280523 A CN 113280523A CN 202110601098 A CN202110601098 A CN 202110601098A CN 113280523 A CN113280523 A CN 113280523A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
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Abstract
The invention discloses an injection type heat pump circulating device with supercooling and preheating, relates to the technical field of injection type heat pump circulating devices, and solves the problem that the operation effect cannot be improved due to the fact that the heating capacity of an injection type heat pump part under unit power is too low in the traditional injection type. The invention is used in heat supply engineering, improves the traditional jet heat pump circulating device, and can improve the efficiency of jet heat supply circulation by supercooling a part of liquid refrigerant at the outlet of a condenser by the liquid refrigerant with throttling, temperature reducing and pressure reducing, improve the heating capacity of the jet heat pump circulating system under unit power, and simultaneously recover the heat of the overheated working medium steam at the outlet of the jet device, so as to heat the liquid working medium flowing into a boiling device, reduce the heat consumed in the boiling device, further improve the heating capacity of the jet heat pump circulating system under unit power, and play a role in enhancing the heat exchange effect of the whole system.
Description
Technical Field
The invention relates to the technical field of jet type heat pump circulating devices, in particular to a jet type heat pump circulating device with supercooling and preheating functions.
Background
The jet heat pump circulating device is one kind of heat energy driven heat pump, and under the drive of high temperature heat source, the high pressure work fluid produced in the boiling device jets the low pressure jet fluid produced in the evaporator, and the two flows are mixed to form medium pressure mixed fluid and the mixed fluid is condensated in the condensator to release heat, so as to extract the heat from the low temperature heat source to the high temperature heat source. A conventional ejector cycle system is shown in fig. 1 and consists primarily of a boiler, condenser, evaporator, ejector, liquid trap and associated piping and transport equipment. Under the action of high-temperature primary water, the boiling device 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 ejector through the working steam pipeline; similarly, under the action of a low-temperature heat source with lower temperature, the evaporator evaporates the refrigerant working medium in the evaporator into low-pressure injection steam which enters the ejector through the injection steam pipeline. 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 a condenser through a mixed steam pipeline to be condensed to release heat, the working steam is changed into liquid, however, in the traditional injection heat pump cycle, due to the influence of the self structure of injector equipment and the injection mixing intensity degree, the total injection coefficient of the injector in the injection heat pump cycle is maintained at a lower level under the condition of a refrigeration working condition, so that the operation efficiency of the heat pump cycle is lower, and the problem of low heating capacity of the whole system under unit power is caused.
Disclosure of Invention
In view of the above-mentioned problems, it is an object of the present invention to provide an ejector heat pump cycle having subcooling and preheating.
In order to achieve the purpose, the invention adopts the technical scheme that:
an ejector heat pump cycle with subcooling and preheat comprising: the system comprises a boiler 3, an evaporator 6, a condenser 9, a first heat exchanger 27, a first ejector 11, a second ejector 22 and a refrigerant pump 18, wherein a first conveying pipeline and a first temperature control pipeline are arranged in the boiler 3, a second conveying pipeline and a second temperature control pipeline are arranged in the evaporator 6, a third conveying pipeline and a third temperature control pipeline are arranged in the condenser 9, and a fourth conveying pipeline and a fifth conveying pipeline are arranged in the first heat exchanger 27;
an exhaust port of the first conveying pipeline is respectively connected with a main air inlet of the first ejector 11 and a main air inlet of the second ejector 22, an outlet of the first ejector 11 and an outlet of the second ejector 22 are both connected with an inlet of a third conveying pipeline, an outlet of the third conveying pipeline is connected with one end of a refrigerant pump 18, and the other end of the refrigerant pump 18 is connected with an inlet of the first conveying pipeline;
two ports of the fourth conveying pipeline are respectively connected with an outlet of the third conveying pipeline and an auxiliary air inlet of the second ejector 22, two ports of the fifth conveying pipeline are respectively connected with an outlet of the third conveying pipeline and an inlet of the second conveying pipeline, and an outlet of the second conveying pipeline is connected with an auxiliary air inlet of the first ejector 11;
two ports of the first temperature control pipeline are respectively provided with a high-temperature heat source inlet 1 and a high-temperature heat source outlet 2, two ports of the second temperature control pipeline are respectively provided with a low-temperature heat source inlet 4 and a low-temperature heat source outlet 5, and two ports of the third temperature control pipeline are respectively provided with a cooling heat source inlet 7 and a cooling heat source outlet 8.
In the above injection heat pump cycle apparatus with subcooling and preheating, the outlet of the third conveying line is connected to the liquid trap 13, and the liquid discharge port of the liquid trap 13 is connected to the refrigerant pump 18, the inlet of the fourth conveying line, and the inlet of the fifth conveying line, respectively.
The ejector heat pump cycle having subcooling and preheating as described above, wherein the inlet of the second transfer line is provided with an expansion throttling device 17.
The ejector heat pump cycle having subcooling and preheating as described above, wherein the inlet of the fourth delivery line is provided with a zero-stage expansion throttling device 26.
The above ejector heat pump cycle with subcooling and preheating further includes: a sixth conveying pipeline and a seventh conveying pipeline are arranged in the second heat exchanger 32, the outlet of the first ejector 11 and the outlet of the second ejector 22 are connected with the inlet of the third conveying pipeline through the sixth conveying pipeline, and the refrigerant pump 18 is connected with the liquid inlet of the first conveying pipeline through the seventh conveying pipeline.
An ejector heat pump cycle with subcooling and preheat comprising: the system comprises a boiler 3, an evaporator 6, a condenser 9, a first heat exchanger 27, a first ejector 11, a second ejector 22 and a refrigerant pump 18, wherein a first conveying pipeline and a first temperature control pipeline are arranged in the boiler 3, a second conveying pipeline and a second temperature control pipeline are arranged in the evaporator 6, a third conveying pipeline and a third temperature control pipeline are arranged in the condenser 9, and a fourth conveying pipeline and a fifth conveying pipeline are arranged in the first heat exchanger 27;
an exhaust port of the first conveying pipeline is respectively connected with a main air inlet of the first ejector 11 and a main air inlet of the second ejector 22, an outlet of the first ejector 11 and an outlet of the second ejector 22 are both connected with an inlet of a third conveying pipeline, an outlet of the third conveying pipeline is connected with one end of a refrigerant pump 18, and the other end of the refrigerant pump 18 is connected with an inlet of the first conveying pipeline;
two ports of the fifth conveying pipeline are respectively connected with an outlet of the third conveying pipeline and an inlet of the second conveying pipeline, an outlet of the second conveying pipeline is connected with an auxiliary air inlet of the first ejector 11, and two ports of the fourth conveying pipeline are respectively connected with an outlet of the fifth conveying pipeline and an auxiliary air inlet of the second ejector 22;
two ports of the first temperature control pipeline are respectively provided with a high-temperature heat source inlet 1 and a high-temperature heat source outlet 2, two ports of the second temperature control pipeline are respectively provided with a low-temperature heat source inlet 4 and a low-temperature heat source outlet 5, and two ports of the third temperature control pipeline are respectively provided with a cooling heat source inlet 7 and a cooling heat source outlet 8.
In the above injection heat pump cycle with subcooling and preheating, the outlet of the third conveying line is connected to the liquid trap 13, and the liquid discharge port of the liquid trap 13 is connected to the refrigerant pump 18 and the inlet of the fifth conveying line, respectively.
The ejector heat pump cycle having subcooling and preheating as described above, wherein the inlet of the second transfer line is provided with an expansion throttling device 17.
The ejector heat pump cycle having subcooling and preheating as described above, wherein the inlet of the fourth delivery line is provided with a zero-stage expansion throttling device 26.
The above ejector heat pump cycle with subcooling and preheating further includes: a sixth conveying pipeline and a seventh conveying pipeline are arranged in the second heat exchanger 32, the outlet of the first ejector 11 and the outlet of the second ejector 22 are connected with the inlet of the third conveying pipeline through the sixth conveying pipeline, and the refrigerant pump 18 is connected with the liquid inlet of the first conveying pipeline through the seventh conveying pipeline.
Due to the adoption of the technology, compared with the prior art, the invention has the following positive effects:
(1) according to the invention, the supercooling device consisting of the first heat exchanger and the zero-level expansion throttling device is installed to supercool the working medium in the fifth conveying pipeline and heat the working medium in the fourth conveying pipeline, so that the circulation efficiency of the jet heat pump can be improved, and the heat supply amount of the jet heat pump circulation system under the unit power is increased;
(2) in the invention, the supercooling device consisting of the second heat exchanger is installed to preheat the working medium in the seventh conveying pipeline and recover part of heat of the working medium in the sixth conveying pipeline, so that the heat consumed in the boiler is reduced, the heating capacity of the jet heat pump in unit power is further improved, and the integral heating effect of the system is enhanced.
Drawings
Fig. 1 is a schematic view of a conventional ejector heat pump cycle.
Fig. 2 is a schematic structural diagram of a first embodiment of the ejector heat pump cycle with subcooling and preheat according to the present invention.
Fig. 3 is a schematic structural diagram of a second embodiment of the ejector heat pump cycle having subcooling and preheating according to the present invention.
Fig. 4 is a schematic structural diagram of a third embodiment of the ejector heat pump cycle having subcooling and preheating according to the present invention.
Fig. 5 is a schematic structural diagram of a fourth embodiment of the ejector heat pump cycle with subcooling and preheating according to the present invention.
In the drawings: 1. a high temperature heat source inlet; 2. a high temperature heat source outlet; 3. a boiler; 4. a low temperature heat source inlet; 5. a low temperature heat source outlet; 6. an evaporator; 7. a cooling heat source inlet; 8. a cooling heat source outlet; 9. a condenser; 10. a first working vapor line; 11. a first ejector; 12. a first mixed vapor line; 13. a liquid collector; 14. a liquid cryogen line; 15. an evaporator liquid refrigerant line; 16. a boiler liquid refrigerant line; 17. an expansion throttling device; 18. a refrigerant pump; 19. an injection steam pipeline; 20. a zero-level working vapor line; 21. a second working vapor line; 22. a second ejector; 23. a second mixed vapor line; 24. a third mixed vapor line; 25. an evaporator liquid refrigerant throttling pipeline; 26. a zero-level expansion throttling device; 27. a first heat exchanger; 28. a second ejector vapor line; 29. a liquid refrigerant supercooling pipeline of the evaporator; 30. the evaporator is provided with a sub-cooling refrigerant pipeline; 31. a zero-level boiler liquid refrigerant line; 32. a second heat exchanger; 33. a fourth mixed vapor line; 34. a super-cooled refrigerant throttling pipeline; 35. the zero-order evaporator subcools the refrigerant line.
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. 2 and 3, there is shown a ejector heat pump cycle with subcooling and preheating, comprising: the heat pump water heater comprises a boiler 3, an evaporator 6, a condenser 9, a first heat exchanger 27, a first ejector 11, a second ejector 22 and a refrigerant pump 18, wherein a first conveying pipeline and a first temperature control pipeline are arranged in the boiler 3, a second conveying pipeline and a second temperature control pipeline are arranged in the evaporator 6, a third conveying pipeline and a third temperature control pipeline are arranged in the condenser 9, and a fourth conveying pipeline and a fifth conveying pipeline are arranged in the first heat exchanger 27.
The exhaust port of the first conveying pipeline is respectively connected with the main air inlet of the first ejector 11 and the main air inlet of the second ejector 22, the outlet of the first ejector 11 and the outlet of the second ejector 22 are both connected with the inlet of the third conveying pipeline, the outlet of the third conveying pipeline is connected with one end of the refrigerant pump 18, and the other end of the refrigerant pump 18 is connected with the liquid inlet of the first conveying pipeline.
Two ports of the fourth delivery line are connected to the outlet of the third delivery line and the auxiliary inlet of the second injector 22, two ports of the fifth delivery line are connected to the outlet of the third delivery line and the inlet of the second delivery line, and the outlet of the second delivery line is connected to the auxiliary inlet of the first injector 11.
Two ports of the first temperature control pipeline are respectively provided with a high-temperature heat source inlet 1 and a high-temperature heat source outlet 2, two ports of the second temperature control pipeline are respectively provided with a low-temperature heat source inlet 4 and a low-temperature heat source outlet 5, and two ports of the third temperature control pipeline are respectively provided with a cooling heat source inlet 7 and a cooling heat source outlet 8.
Further, in a preferred embodiment, the outlet of the third delivery line is connected to the accumulator 13, and the drain of the accumulator 13 is connected to the refrigerant pump 18, the inlet of the fourth delivery line and the inlet of the fifth delivery line, respectively.
Further, in a preferred embodiment, the inlet of the second transfer line is provided with an expansion throttling device 17.
Further, in a preferred embodiment, the inlet of the fourth delivery line is provided with a zero stage expansion throttling device 26.
Further, in a preferred embodiment, the method further comprises: a sixth conveying pipeline and a seventh conveying pipeline are arranged in the second heat exchanger 32, the outlet of the first ejector 11 and the outlet of the second ejector 22 are connected with the inlet of the third conveying pipeline through the sixth conveying pipeline, and the refrigerant pump 18 is connected with the liquid inlet of the first conveying pipeline through the seventh conveying pipeline.
Referring to fig. 4 and 5, there is shown a ejector heat pump cycle with subcooling and preheating, comprising: the heat pump water heater comprises a boiler 3, an evaporator 6, a condenser 9, a first heat exchanger 27, a first ejector 11, a second ejector 22 and a refrigerant pump 18, wherein a first conveying pipeline and a first temperature control pipeline are arranged in the boiler 3, a second conveying pipeline and a second temperature control pipeline are arranged in the evaporator 6, a third conveying pipeline and a third temperature control pipeline are arranged in the condenser 9, and a fourth conveying pipeline and a fifth conveying pipeline are arranged in the first heat exchanger 27.
The exhaust port of the first conveying pipeline is respectively connected with the main air inlet of the first ejector 11 and the main air inlet of the second ejector 22, the outlet of the first ejector 11 and the outlet of the second ejector 22 are both connected with the inlet of the third conveying pipeline, the outlet of the third conveying pipeline is connected with one end of the refrigerant pump 18, and the other end of the refrigerant pump 18 is connected with the liquid inlet of the first conveying pipeline.
Two ports of the fifth delivery line are connected to the outlet of the third delivery line and the inlet of the second delivery line, respectively, the outlet of the second delivery line is connected to the auxiliary inlet of the first ejector 11, and two ports of the fourth delivery line are connected to the outlet of the fifth delivery line and the auxiliary inlet of the second ejector 22, respectively.
Two ports of the first temperature control pipeline are respectively provided with a high-temperature heat source inlet 1 and a high-temperature heat source outlet 2, two ports of the second temperature control pipeline are respectively provided with a low-temperature heat source inlet 4 and a low-temperature heat source outlet 5, and two ports of the third temperature control pipeline are respectively provided with a cooling heat source inlet 7 and a cooling heat source outlet 8.
Further, in a preferred embodiment, the outlet of the third transfer line is connected to the accumulator 13, and the drain of the accumulator 13 is connected to the refrigerant pump 18 and the inlet of the fifth transfer line, respectively.
Further, in a preferred embodiment, the inlet of the second transfer line is provided with an expansion throttling device 17.
Further, in a preferred embodiment, the inlet of the fourth delivery line is provided with a zero stage expansion throttling device 26.
Further, in a preferred embodiment, the method further comprises: a sixth conveying pipeline and a seventh conveying pipeline are arranged in the second heat exchanger 32, the outlet of the first ejector 11 and the outlet of the second ejector 22 are connected with the inlet of the third conveying pipeline through the sixth conveying pipeline, and the refrigerant pump 18 is connected with the liquid inlet of the first conveying pipeline through the seventh conveying pipeline.
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 circulating device belongs to a heat energy driven heat pump, under the drive 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. A conventional ejector cycle system is shown in fig. 1 and is mainly composed of a boiler 3, a condenser 9, an evaporator 6, a first ejector 11, a liquid collector 13, and associated piping and transportation equipment. Under the action of high-temperature primary water, the boiler 3 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 11 through the working steam pipeline 10; similarly, the evaporator 6 evaporates the refrigerant working medium therein into low-pressure injection steam under the action of a low-temperature heat source with a lower temperature, and the low-pressure injection steam enters the first injector 11 through the injection steam pipeline 19. Under the effect 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 9 through the first mixed steam pipeline 12 to be condensed to release heat, the working steam is changed into liquid, however, in the traditional injection heat pump cycle, due to the influence of the structure of the injector equipment and the injection mixing intensity degree, the total injection coefficient of the injector in the injection heat pump cycle is maintained at a lower level under the condition of a heat supply working condition, and therefore the operation efficiency of the heat pump cycle is lower. If the structure of the jet heat pump cycle can be improved, the heating capacity under the unit power of the cycle is improved, and the operation effect of the system is greatly improved.
In a further example of the present invention, a first embodiment is described with reference to fig. 2, and the first embodiment includes: a high-temperature heat source inlet 1, a high-temperature heat source outlet 2, a boiler 3, a low-temperature heat source inlet 4, a low-temperature heat source outlet 5, an evaporator 6, a cooling heat source inlet 7, a cooling heat source outlet 8, a condenser 9, a first working steam pipeline 10, a first ejector 11, a first mixed steam pipeline 12, a liquid collector 13, a liquid refrigerant pipeline 14 and an evaporator liquid refrigerant pipeline 15, the system comprises a boiler liquid refrigerant pipeline 16, an expansion throttling device 17, a refrigerant pump 18, an injection vapor pipeline 19, a zero-level working vapor pipeline 20, a second working vapor pipeline 21, a second ejector 22, a second mixed vapor pipeline 23, a third mixed vapor pipeline 24, an evaporator liquid refrigerant throttling pipeline 25, a zero-level expansion throttling device 26, a first heat exchanger 27, a second injection vapor pipeline 28, an evaporator liquid refrigerant supercooling pipeline 29 and an evaporator supercooling refrigerant pipeline 30. The connection mode of the refrigerant pipeline is as follows: the outlet of the boiler 3 is connected with a zero-level working vapor pipeline 20, the zero-level working vapor pipeline 20 is divided into two paths, one path is communicated with a first ejector 11 through a first working vapor pipeline 10, the other path is communicated with a second ejector 22 through a second working vapor pipeline 21, the outlet of the first ejector 11 is connected with a first mixed vapor pipeline 12, the outlet of the second ejector 22 is connected with a second mixed vapor pipeline 23, the first mixed vapor pipeline 12 and the second mixed vapor pipeline 23 are converged into one path which is communicated with a condenser 9 through a third mixed vapor pipeline 24, the condenser 9 is communicated with a liquid collector 13 through a liquid refrigerant pipeline 14, the outlet of the liquid refrigerant pipeline 14 is divided into two paths, the other path is communicated with the boiler 3 through a boiler liquid refrigerant pipeline 16 through a refrigerant pump 18, the other path is communicated with an evaporator liquid refrigerant pipeline 15, and the evaporator liquid refrigerant pipeline 15 is divided into two paths, one path is communicated with a first heat exchanger 27 through an evaporator liquid refrigerant throttling pipeline 25 and a zero-level expansion throttling device 26, the outlet of the first heat exchanger 27 is communicated with a second ejector 22 through a second ejection steam pipeline 28, the other path is communicated with the first heat exchanger 27 through an evaporator liquid refrigerant supercooling pipeline 29, the other outlet of the first heat exchanger 27 is communicated with an evaporator 6 through an expansion valve 17 through an evaporator supercooling refrigerant pipeline 30, and the evaporator 6 is communicated with the first ejector 11 through an ejection steam pipeline 19.
In a further embodiment of the present invention, the operation flow of the present embodiment is that a high temperature heat source flows into the boiler 3 through the high temperature heat source inlet 1 and then flows out from the high temperature heat source outlet 2, heat is released therein, a liquid refrigerant working medium is converted into a high temperature and high pressure gaseous working medium in the boiler 3 and is divided into two paths through the zero-level working vapor line 20, one path enters the first ejector 11 through the first working vapor line 10 to inject a low pressure gaseous refrigerant from the evaporator 6, the two fluids are mixed to become a medium pressure gaseous refrigerant and flow out of the first ejector 11, the other path enters the second ejector 22 through the second working vapor line 21 to inject a low pressure gaseous refrigerant from the first heat exchanger 27, wherein the two fluids are mixed to become a medium pressure gaseous refrigerant and flow out of the second ejector 22, the fluid flowing out of the first ejector 11 and the fluid flowing out of the second ejector 22 are mixed to enter the condenser 9, after the gaseous refrigerant with high temperature and high pressure is condensed and released in the condenser 9, the gaseous refrigerant is divided into two paths through a liquid refrigerant pipeline 14: one path enters the boiler 3 to continue boiling through a boiler liquid refrigerant pipeline 16 under the action of a refrigerant pump 18, the other path is divided into two paths through an evaporator liquid refrigerant pipeline 15, one path enters a first heat exchanger 27 to absorb heat and returns to a second ejector 22 after being cooled and decompressed under the action of a zero-level expansion throttling device 26 to become low-pressure gaseous refrigerant, a part of working medium circulation is completed, the other path directly enters the first heat exchanger 27 to be supercooled, then, the cooled and decompressed flows into the evaporator 6 to continue evaporating and extracting the heat of a low-temperature heat source flowing from a low-temperature heat source inlet 4 and then the low-pressure gaseous refrigerant returns to the first ejector 11 under the action of an expansion throttling device 17, and therefore the working medium circulation is completed.
In a further embodiment of the present invention, the beneficial effect of this embodiment is that, in the working medium circulation, due to the arrangement of the first heat exchanger 27, the working medium at the outlet of the thermal zero-level expansion throttling device 26 subcools the liquid working medium at the outlet of the condenser 9, so that the efficiency of the injection type heat supply circulation can be improved, and the heating capacity of the injection type heat pump circulation system under the unit power can be improved.
In a further example of the present invention, a second embodiment is described with reference to fig. 3, and includes: a high-temperature heat source inlet 1, a high-temperature heat source outlet 2, a boiler 3, a low-temperature heat source inlet 4, a low-temperature heat source outlet 5, an evaporator 6, a cooling heat source inlet 7, a cooling heat source outlet 8, a condenser 9, a first working vapor pipeline 10, a first ejector 11, a first mixed vapor pipeline 12, a liquid collector 13, a liquid refrigerant pipeline 14, an evaporator liquid refrigerant pipeline 15, a boiler liquid refrigerant pipeline 16, an expansion throttling device 17, a refrigerant pump 18, an injection vapor pipeline 19, a zero-level working vapor pipeline 20, a second working vapor pipeline 21, a second ejector 22, a second mixed vapor pipeline 23, a third mixed vapor pipeline 24, an evaporator liquid refrigerant throttling pipeline 25, a zero-level expansion throttling device 26, a first heat exchanger 27, a second injection vapor pipeline 28, an evaporator liquid refrigerant supercooling pipeline 29, an evaporator supercooling refrigerant pipeline 30, a low-temperature refrigerant pipeline 30, A zero-order boiler liquid refrigerant line 31, a second heat exchanger 32, and a fourth mixed vapor line 33. The communication mode of the refrigerant pipeline is as follows: the outlet of the boiler 3 is connected with a zero-level working vapor pipeline 20, the zero-level working vapor pipeline 20 is divided into two paths, one path is communicated with a first ejector 11 through a first working vapor pipeline 10, the other path is communicated with a second ejector 22 through a second working vapor pipeline 21, the outlet of the first ejector 11 is connected with a first mixed vapor pipeline 12, the outlet of the second ejector 22 is connected with a second mixed vapor pipeline 23, the first mixed vapor pipeline 12 and the second mixed vapor pipeline 23 are converged into one path and communicated with a second heat exchanger 32 through a third mixed vapor pipeline 24, the outlet of the second heat exchanger 32 is connected with a fourth mixed vapor pipeline 33, the outlet of the fourth mixed vapor pipeline 33 is connected with a condenser 9, the condenser 9 is communicated with a liquid collector 13 through a liquid refrigerant pipeline 14, the outlet of the liquid refrigerant pipeline 14 is divided into two paths, and the other path is communicated with the second heat exchanger 32 through a liquid refrigerant pump 18 through a zero-level boiler liquid refrigerant pipeline 31, the other outlet of the second heat exchanger 32 is communicated with the boiler 3 through a boiler liquid refrigerant pipeline 16, one path of the second heat exchanger passes through an evaporator liquid refrigerant pipeline 15, the evaporator liquid refrigerant pipeline 15 is divided into two paths, one path of the second heat exchanger passes through an evaporator liquid refrigerant throttling pipeline 25 and is communicated with the first heat exchanger 27 through a zero-level expansion throttling device 26, the outlet of the first heat exchanger 27 is communicated with the ejector through a second injection vapor pipeline 28, the other path of the first heat exchanger is communicated with the first heat exchanger 27 through an evaporator liquid refrigerant supercooling pipeline 29, the other outlet of the first heat exchanger 27 is communicated with the evaporator 6 through an expansion valve 17 through an evaporator supercooling refrigerant pipeline 30, and the evaporator 6 is communicated with the first ejector 11 through an injection vapor pipeline 19.
In a further embodiment of the present invention, the operation flow of the present embodiment is that a high temperature heat source flows into the boiler 3 through the high temperature heat source inlet 1 and then flows out from the high temperature heat source outlet 2, heat is released therein, a liquid refrigerant working medium is converted into a high temperature and high pressure gaseous working medium in the boiler 3 and is divided into two paths through the zero-level working vapor line 20, one path enters the first ejector 11 through the first working vapor line 10 to eject a low pressure gaseous refrigerant from the evaporator 6, wherein the two fluids are mixed to become a medium pressure gaseous refrigerant and flow out of the first ejector 11, the other path enters the second ejector 22 through the second working vapor line 21 to eject a low pressure gaseous refrigerant from the first heat exchanger 27, wherein the two fluids are mixed to become a medium pressure gaseous refrigerant and flow out of the second ejector 22, the fluid flowing out of the first ejector 11 and the fluid flowing out of the second ejector 22 are mixed to enter the second heat exchanger 32, heat is released in the second heat exchanger 32 to preheat the liquid working medium entering the boiler 3, so that the heat consumed in the boiler 3 is reduced, high-temperature steam flows out of the second heat exchanger 32 and then enters the condenser 9, the high-temperature and high-pressure gaseous working medium is condensed in the condenser 9 to be changed into the liquid working medium, and the liquid working medium is divided into two paths through the liquid refrigerant pipeline 14; one path of the refrigerant enters a second heat exchanger 32 through a zero-level boiler liquid refrigerant pipeline 31 under the action of a refrigerant pump 18 to absorb heat and then enters a boiler 3 through a boiler liquid refrigerant pipeline 16 to be continuously boiled, the other path of the refrigerant is divided into two paths through an evaporator liquid refrigerant pipeline 15, one path of the refrigerant is cooled and decompressed under the action of a zero-level expansion throttling device 26, enters a first heat exchanger 27 to absorb heat to become low-pressure gaseous refrigerant and then returns to a second ejector 22, a part of working medium circulation is completed, the other path of the refrigerant directly enters the first heat exchanger 27 to be supercooled, then is cooled and decompressed under the action of an expansion throttling device 17, flows into an evaporator 6 to be continuously evaporated and extracted, the heat of a low-temperature heat source flowing from a low-temperature heat source inlet 4 is converted into low-pressure gaseous refrigerant, and returns to the first ejector 11, and accordingly working medium circulation is completed.
In a further embodiment of the present invention, the present embodiment has the beneficial effects that in the working medium circulation, the heat of the superheated steam is used to preheat the liquid working medium entering the boiler 3, so as to reduce the heat consumed in the boiler 3, further increase the heating capacity of the heat pump system in unit power, and further increase the operation effect of the jet heat pump circulation device.
In a further example of the present invention, a third embodiment is described with reference to fig. 4, and includes: the system comprises a high-temperature heat source inlet 1, a high-temperature heat source outlet 2, a boiler 3, a low-temperature heat source inlet 4, a low-temperature heat source outlet 5, an evaporator 6, a cooling heat source inlet 7, a cooling heat source outlet 8, a condenser 9, a first working vapor pipeline 10, a first ejector 11, a first mixed vapor pipeline 12, a liquid collector 13, a liquid refrigerant pipeline 14, an evaporator liquid refrigerant pipeline 15, a boiler liquid refrigerant pipeline 16, an expansion throttling device 17, a refrigerant pump 18, an injection vapor pipeline 19, a zero-level working vapor pipeline 20, a second working vapor pipeline 21, a second ejector 22, a second mixed vapor pipeline 23, a third mixed vapor pipeline 24, a zero-level expansion throttling device 26, a first heat exchanger 27, a second injection vapor pipeline 28, an evaporator super-cooling refrigerant pipeline 30, a super-cooling refrigerant throttling pipeline 34 and an evaporator zero-level super-cooling refrigerant pipeline 35. The communication mode of the refrigerant pipeline is as follows: the outlet of the boiler 3 is connected with a zero-level working vapor pipeline 20, the zero-level working vapor pipeline 20 is divided into two paths, one path is communicated with a first ejector 11 through a first working vapor pipeline 10, the other path is communicated with a second ejector 22 through a second working vapor pipeline 21, the outlet of the first ejector 11 is connected with a first mixed vapor pipeline 12, the outlet of the second ejector 22 is connected with a second mixed vapor pipeline 23, the first mixed vapor pipeline 12 and the second mixed vapor pipeline 23 are converged into one path and communicated with a condenser 9 through a third mixed vapor pipeline 24, the condenser 9 is communicated with a liquid collector 13 through a liquid refrigerant pipeline 14, the outlet of the liquid refrigerant pipeline 14 is divided into two paths, the other path is communicated with the boiler 3 through a boiler liquid refrigerant pipeline 16 through a refrigerant pump 18, the other path is communicated with a first heat exchanger 27 through an evaporator liquid refrigerant pipeline 15, the zero-level outlet of the first heat exchanger 27 is connected to an evaporator sub-cooling refrigerant pipeline 35, the outlet of the zero-level evaporator sub-cooling refrigerant pipeline 35 is divided into two paths, one path is communicated with a first heat exchanger 27 through a zero-level expansion throttling device 26, the other outlet of the first heat exchanger 27 is communicated with a second ejector 22 through a second ejection steam pipeline 28, the other path is communicated with the evaporator 6 through an evaporator sub-cooling refrigerant pipeline 30 and an expansion valve 17, and the evaporator 6 is communicated with the first ejector 11 through an ejection steam pipeline 19.
In a further embodiment of the present invention, the operation flow of the present embodiment is that a high temperature heat source flows into the boiler 3 through the high temperature heat source inlet 1 and then flows out from the high temperature heat source outlet 2, heat is released therein, a liquid refrigerant working medium is converted into a high temperature and high pressure gaseous working medium in the boiler 3 and is divided into two paths through the zero-level working vapor line 20, one path enters the first ejector 11 through the first working vapor line 10 to inject a low pressure gaseous refrigerant from the evaporator 6, the two fluids are mixed to become a medium pressure gaseous refrigerant and then flow out of the first ejector 11, the other path enters the second ejector 22 through the second working vapor line 21 to inject a low pressure gaseous refrigerant from the first heat exchanger 27, wherein the two fluids are mixed to become a medium pressure gaseous refrigerant and then flow out of the second ejector 22, the fluid flowing out of the first ejector 11 and the fluid flowing out of the second ejector 22 are mixed to enter the condenser 9, after the high-temperature and high-pressure gaseous refrigeration working medium is condensed and released in the condenser 9, the gaseous refrigeration working medium is divided into two paths through a liquid refrigerant pipeline 14; one path of the refrigerant enters the boiler 3 to be continuously boiled through the boiler liquid refrigerant pipeline 16 under the action of the refrigerant pump 18, the other path of the refrigerant flows into the first heat exchanger 27 to be supercooled through the evaporator liquid refrigerant pipeline 15, the supercooled liquid refrigerant is divided into two paths, one path of the refrigerant is cooled and decompressed under the action of the zero-level expansion throttling device 26, enters the first heat exchanger 27 to absorb heat and then becomes low-pressure gaseous refrigerant to return to the second ejector 22, and the other path of the refrigerant flows into the evaporator 6 to be continuously evaporated and extracted heat of a low-temperature heat source flowing from the low-temperature heat source inlet 4 to become low-pressure gaseous refrigerant to return to the first ejector 11 under the action of the expansion throttling device 17, so that the circulation of the working medium is completed.
In a further embodiment of the present invention, the beneficial effect of this embodiment is that, in the working medium circulation, due to the arrangement of the first heat exchanger 27, the working medium at the outlet of the thermal zero-level expansion throttling device 26 subcools the liquid working medium at the outlet of the condenser 9, so that the efficiency of the injection type heat supply circulation can be improved, and the heating capacity of the injection type heat pump circulation system under the unit power can be improved.
In a further example of the present invention, a fourth embodiment is described with reference to fig. 5, and the present embodiment includes: a high-temperature heat source inlet 1, a high-temperature heat source outlet 2, a boiler 3, a low-temperature heat source inlet 4, a low-temperature heat source outlet 5, an evaporator 6, a cooling heat source inlet 7, a cooling heat source outlet 8, a condenser 9, a first working vapor pipeline 10, a first ejector 11, a first mixed vapor pipeline 12, a liquid collector 13, a liquid refrigerant pipeline 14, an evaporator liquid refrigerant pipeline 15, a boiler liquid refrigerant pipeline 16, an expansion throttling device 17, a refrigerant pump 18, an injection vapor pipeline 19, a zero-level working vapor pipeline 20, a second working vapor pipeline 21, a second ejector 22, a second mixed vapor pipeline 23, a third mixed vapor pipeline 24, a zero-level expansion throttling device 26, a first heat exchanger 27, a second injection vapor pipeline 28, an evaporator super-cooling refrigerant pipeline 30, a zero-level boiler liquid refrigerant pipeline 31, a second heat exchanger 32, a fourth mixed vapor pipeline 33, A sub-cooling refrigerant throttling pipeline 34 and a zero-level evaporator sub-cooling refrigerant pipeline 35. The communication mode of the refrigerant pipeline is as follows: the outlet of the boiler 3 is connected with a zero-level working vapor pipeline 20, the zero-level working vapor pipeline 20 is divided into two paths, one path is communicated with a first ejector 11 through a first working vapor pipeline 10, the other path is communicated with a second ejector 22 through a second working vapor pipeline 21, the outlet of the first ejector 11 is connected with a first mixed vapor pipeline 12, the outlet of the second ejector 22 is connected with a second mixed vapor pipeline 23, the first mixed vapor pipeline 12 and the second mixed vapor pipeline 23 are converged into one path and communicated with a second heat exchanger 32 through a third mixed vapor pipeline 24, the outlet of the second heat exchanger 32 is connected with a fourth mixed vapor pipeline 33, the outlet of the fourth mixed vapor pipeline 33 is connected with a condenser 9, the condenser 9 is communicated with a liquid collector 13 through a liquid refrigerant pipeline 14, the outlet of the liquid refrigerant pipeline 14 is divided into two paths, and the other path is communicated with the second heat exchanger 32 through a liquid refrigerant pump 18 through a zero-level boiler liquid refrigerant pipeline 31, the other outlet of the second heat exchanger 32 is communicated with the boiler 3 through a boiler liquid refrigerant pipeline 16, the other outlet of the second heat exchanger is communicated with the first heat exchanger 27 through an evaporator liquid refrigerant pipeline 15, the outlet of the first heat exchanger 27 is connected to a zero-level evaporator sub-refrigerant pipeline 35, the outlet of the zero-level evaporator sub-refrigerant pipeline 35 is divided into two paths, one path of the two paths is communicated with the first heat exchanger 27 through a zero-level expansion throttling device 26, the other outlet of the first heat exchanger 27 is communicated with the second ejector 22 through a second ejector vapor pipeline 28, the other path of the two paths is communicated with the evaporator 6 through an expansion valve 17 through an evaporator sub-refrigerant pipeline 30, and the evaporator 6 is communicated with the first ejector 11 through an ejector vapor pipeline 19.
In a further embodiment of the present invention, the operation flow of the present embodiment is that a high temperature heat source flows into the boiler 3 through the high temperature heat source inlet 1 and then flows out from the high temperature heat source outlet 2, heat is released therein, a liquid refrigerant working medium is converted into a high temperature and high pressure gaseous working medium in the boiler 3 and is divided into two paths through the zero-level working vapor line 20, one path enters the first ejector 11 through the first working vapor line 10 to eject a low pressure gaseous refrigerant from the evaporator 6, wherein the two fluids are mixed to become a medium pressure gaseous refrigerant and flow out of the first ejector 11, the other path enters the second ejector 22 through the second working vapor line 21 to eject a low pressure gaseous refrigerant from the first heat exchanger 27, wherein the two fluids are mixed to become a medium pressure gaseous refrigerant and flow out of the second ejector 22, the fluid flowing out of the first ejector 11 and the fluid flowing out of the second ejector 22 are mixed to enter the second heat exchanger 32, heat is released in the second heat exchanger 32 to preheat the liquid working medium entering the boiler 3, so that the heat consumed in the boiler 3 is reduced, high-temperature steam flows out of the second heat exchanger 32 and then enters the condenser 9, the high-temperature and high-pressure gaseous working medium is condensed in the condenser 9 to be changed into the liquid working medium, and the liquid working medium is divided into two paths through the liquid refrigerant pipeline 14; one path of the refrigerant enters a second heat exchanger 32 through a zero-level boiler liquid refrigerant pipeline 31 under the action of a refrigerant pump 18 to absorb heat and then enters a boiler 3 through a boiler liquid refrigerant pipeline 16 to be continuously boiled, the other path of the refrigerant enters a first heat exchanger 27 through an evaporator liquid refrigerant pipeline 15 to be supercooled and then is divided into two paths, one path of the refrigerant is cooled and decompressed under the action of a zero-level expansion throttling device 26, enters the first heat exchanger 27 to absorb heat to become a low-pressure gaseous refrigerant and then returns to a second ejector 22, the other path of the refrigerant is cooled and decompressed under the action of an expansion throttling device 17, flows into an evaporator 6 to be continuously evaporated and extracted with the heat of a low-temperature heat source flowing from a low-temperature heat source inlet 4, and then the low-pressure gaseous refrigerant returns to the first ejector 11, and therefore the circulation of working media is completed.
In a further embodiment of the present invention, the present embodiment has the beneficial effects that in the working medium circulation, the heat of the superheated steam is used to preheat the liquid working medium entering the boiler 3, so as to reduce the heat consumed in the boiler 3, further increase the heating capacity of the heat pump system in unit power, and further increase the operation effect of the jet heat pump circulation device.
In a further embodiment of the invention, the injection type heat pump circulating device is used in a heat supply project, the traditional injection type heat pump circulating device is improved, a part of liquid refrigerant at the outlet of the condenser is supercooled by the liquid refrigerant with throttling, temperature reduction and pressure reduction, the circulation efficiency of the injection type heat pump can be improved, the heating capacity of the injection type heat pump circulating system under the unit power is improved, meanwhile, the heat of the overheated working medium steam at the outlet of the injector is recovered and used for heating the liquid working medium flowing into the boiler 3, the heat consumed in the boiler 3 is reduced, the heating capacity of the injection type heat pump circulating system under the unit power is further improved, and the integral heating effect of the system is enhanced.
In a further embodiment of the present invention, a supercooling device composed of the first heat exchanger 27 and the zero-level expansion throttling device 26 is installed to supercool the working medium in the fifth delivery pipeline and heat the working medium in the fourth delivery pipeline, so that the circulation efficiency of the jet heat pump can be improved, and the heat supply amount of the jet heat pump circulation system under the unit power can be increased.
In a further embodiment of the present invention, a supercooling device composed of the second heat exchanger 32 is installed to preheat the working medium in the seventh conveying pipeline, and part of the heat of the working medium in the sixth conveying pipeline is recovered, so that the heat consumed in the boiler 3 is reduced, the heating capacity of the jet heat pump cycle under unit power is further improved, and the overall heating effect of the system is enhanced.
In a further embodiment of the invention, the injection type heat pump circulating device is used in a heat supply project, the traditional injection type heat pump circulating device is improved, a part of liquid refrigerant at the outlet of the condenser 9 is supercooled by the liquid refrigerant with throttling, temperature reduction and pressure reduction, the efficiency of the injection type heat supply circulation can be improved, the heating capacity of the injection type heat pump circulating system under the unit power is improved, meanwhile, the heat of the overheated working medium steam at the outlet of the injector is recovered and used for heating the liquid working medium flowing into the boiler 3, the heat consumed in the boiler 3 is reduced, the heating capacity of the injection type heat pump circulation under the unit power is further improved, and the heat exchange effect of the whole system is enhanced.
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 (10)
1. A ejector heat pump cycle with subcooling and preheat comprising: the system comprises a boiler (3), an evaporator (6), a condenser (9), a first heat exchanger (27), a first ejector (11), a second ejector (22) and a refrigerant pump (18), wherein a first conveying pipeline and a first temperature control pipeline are arranged in the boiler (3), a second conveying pipeline and a second temperature control pipeline are arranged in the evaporator (6), a third conveying pipeline and a third temperature control pipeline are arranged in the condenser (9), and a fourth conveying pipeline and a fifth conveying pipeline are arranged in the first heat exchanger (27);
an exhaust port of the first conveying pipeline is respectively connected with a main air inlet of the first ejector (11) and a main air inlet of the second ejector (22), an outlet of the first ejector (11) and an outlet of the second ejector (22) are both connected with an inlet of a third conveying pipeline, an outlet of the third conveying pipeline is connected with one end of a refrigerant pump (18), and the other end of the refrigerant pump (18) is connected with a liquid inlet of the first conveying pipeline;
two ports of a fourth conveying pipeline are respectively connected with an outlet of the third conveying pipeline and an auxiliary air inlet of a second ejector (22), two ports of a fifth conveying pipeline are respectively connected with an outlet of the third conveying pipeline and an inlet of the second conveying pipeline, and an outlet of the second conveying pipeline is connected with an auxiliary air inlet of the first ejector (11);
two ports of the first temperature control pipeline are respectively provided with a high-temperature heat source inlet (1) and a high-temperature heat source outlet (2), two ports of the second temperature control pipeline are respectively provided with a low-temperature heat source inlet (4) and a low-temperature heat source outlet (5), and two ports of the third temperature control pipeline are respectively provided with a cooling heat source inlet (7) and a cooling heat source outlet (8).
2. The ejector heat pump cycle with subcooling and preheating according to claim 1, wherein the outlet of the third delivery line is connected to an accumulator (13), and the drain of the accumulator (13) is connected to the inlet of the refrigerant pump (18), the inlet of the fourth delivery line and the inlet of the fifth delivery line, respectively.
3. The ejector heat pump cycle with subcooling and preheat according to claim 2, wherein the inlet of the second transfer line is provided with an expansion throttling device (17).
4. The ejector heat pump cycle with subcooling and preheat according to claim 3, wherein the inlet of the fourth transfer line is provided with a zero stage expansion throttling device (26).
5. The ejector heat pump cycle with subcooling and preheat of claim 4, further comprising: a sixth conveying pipeline and a seventh conveying pipeline are arranged in the second heat exchanger (32), the outlet of the first ejector (11) and the outlet of the second ejector (22) are connected with the inlet of the third conveying pipeline through the sixth conveying pipeline, and the refrigerant pump (18) is connected with the liquid inlet of the first conveying pipeline through the seventh conveying pipeline.
6. A ejector heat pump cycle with subcooling and preheat comprising: the system comprises a boiler (3), an evaporator (6), a condenser (9), a first heat exchanger (27), a first ejector (11), a second ejector (22) and a refrigerant pump (18), wherein a first conveying pipeline and a first temperature control pipeline are arranged in the boiler (3), a second conveying pipeline and a second temperature control pipeline are arranged in the evaporator (6), a third conveying pipeline and a third temperature control pipeline are arranged in the condenser (9), and a fourth conveying pipeline and a fifth conveying pipeline are arranged in the first heat exchanger (27);
an exhaust port of the first conveying pipeline is respectively connected with a main air inlet of the first ejector (11) and a main air inlet of the second ejector (22), an outlet of the first ejector (11) and an outlet of the second ejector (22) are both connected with an inlet of a third conveying pipeline, an outlet of the third conveying pipeline is connected with one end of a refrigerant pump (18), and the other end of the refrigerant pump (18) is connected with a liquid inlet of the first conveying pipeline;
two ports of the fifth conveying pipeline are respectively connected with an outlet of the third conveying pipeline and an inlet of the second conveying pipeline, an outlet of the second conveying pipeline is connected with an auxiliary air inlet of the first ejector (11), and two ports of the fourth conveying pipeline are respectively connected with an outlet of the fifth conveying pipeline and an auxiliary air inlet of the second ejector (22);
two ports of the first temperature control pipeline are respectively provided with a high-temperature heat source inlet (1) and a high-temperature heat source outlet (2), two ports of the second temperature control pipeline are respectively provided with a low-temperature heat source inlet (4) and a low-temperature heat source outlet (5), and two ports of the third temperature control pipeline are respectively provided with a cooling heat source inlet (7) and a cooling heat source outlet (8).
7. The ejector heat pump cycle with subcooling and preheating according to claim 6, wherein the outlet of the third delivery line is connected to an accumulator (13) and the drain of the accumulator (13) is connected to the inlet of the refrigerant pump (18) and the inlet of the fifth delivery line, respectively.
8. The ejector heat pump cycle with subcooling and preheat according to claim 7, wherein the inlet of the second transfer line is provided with an expansion throttling device (17).
9. The ejector heat pump cycle with subcooling and preheat according to claim 8, wherein the inlet of the fourth transfer line is provided with a zero stage expansion throttling device (26).
10. The ejector heat pump cycle with subcooling and preheat of claim 9, further comprising: a sixth conveying pipeline and a seventh conveying pipeline are arranged in the second heat exchanger (32), the outlet of the first ejector (11) and the outlet of the second ejector (22) are connected with the inlet of the third conveying pipeline through the sixth conveying pipeline, and the refrigerant pump (18) is connected with the liquid inlet of the first conveying pipeline through the seventh conveying pipeline.
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