CN111854225A - Multi-pressure-stage air supplementing type high-temperature heat pump steam system - Google Patents
Multi-pressure-stage air supplementing type high-temperature heat pump steam system Download PDFInfo
- Publication number
- CN111854225A CN111854225A CN202010741387.1A CN202010741387A CN111854225A CN 111854225 A CN111854225 A CN 111854225A CN 202010741387 A CN202010741387 A CN 202010741387A CN 111854225 A CN111854225 A CN 111854225A
- Authority
- CN
- China
- Prior art keywords
- evaporator
- heat
- flash
- outlet
- condenser
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
-
- 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
- F25B31/00—Compressor arrangements
-
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Sorption Type Refrigeration Machines (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The invention relates to a multi-pressure-stage air-supplementing type high-temperature heat pump steam system, belonging to the field of application expansion of high-temperature heat pump systems, the heat pump steam system comprises a heat source inlet, a heat source throttle valve, an evaporator, a heat source outlet, an air supply compressor, a main compressor, a condenser, a heat return control valve bank, a first heat regenerator, a subcooler, a first-stage expansion valve, a first flash evaporator, a second-stage expansion valve and the like, through multistage pressure regulation and control in the system, effectively improve system heating effect and system steam efficiency, the operating condition of high temperature heat pump circulation module part adoption low pressure, middling pressure, high pressure and tonifying qi pressure level four pressure effective control circulation refrigerant reduces the power consumption of the compressor in the system, and the effect of system heating is then promoted the efficiency of system steam, is favorable to the further development in high temperature heat pump system structure optimization and heat pump system steam field.
Description
Technical Field
The invention relates to a high-temperature heat pump steam system, in particular to a multi-pressure-stage air supplementing type high-temperature heat pump steam system.
Background
With the increasing application of heat pump technology, people hope to apply the heat pump technology to the field of steam production, so the requirement for the heat supply temperature of a heat pump system is gradually increased, and the pressure ratio of a system compressor under the working condition is increased, however, the research on a high-temperature heat pump system is relatively immature at the present stage, especially, the traditional heat pump system is still used for research under the working condition with a large pressure ratio, so that the performance parameters such as isentropic efficiency, volume efficiency and the like of the compressor in the heat pump system under the working condition with the large pressure ratio are low, the heating performance of the system is not ideal, and in addition, when the condensation temperature is too high, the phenomenon that the adopted refrigerant hits the compressor by liquid easily occurs in the working process, and the service life of the. The invention provides a multi-pressure-stage air-supplementing type high-temperature heat pump steam system, four-stage pressures are set through two compressors and respectively comprise high-pressure condensation pressure, low-pressure evaporation pressure, medium-pressure flash evaporation pressure and air-supplementing pressure, when high-pressure and low-pressure conditions are selected, the optimal threshold value of the system is further accurate through the thermodynamic property of a system which is adjusted and controlled by the medium-pressure and air-supplementing pressure, the power consumption of the compressors is reduced in an air-supplementing mode, the exhaust superheat degree of a refrigerant is adjusted and controlled, the heating capacity of a high-temperature heat pump system in the system is improved, and therefore the steam-making efficiency of the system is improved.
Disclosure of Invention
In order to solve the technical problems in the prior art, the invention provides a multi-pressure-stage air-supplementing type high-temperature heat pump steam system.
A multi-pressure-level air supplement type high-temperature heat pump steam system is composed of a heat supply source module, a high-temperature heat pump circulation module and an evaporation module, wherein the heat supply source module, the high-temperature heat pump circulation module and the evaporation module are composed of a heat source inlet, a heat source throttle valve, an evaporator, a heat source outlet, an air supplement compressor, a main compressor, a condenser, a subcooler, a heat return control valve group, a first heat regenerator, a first-level expansion valve, a first flash evaporator, a second heat regenerator, a second expansion valve, an evaporation system expansion valve, a second flash evaporator, a steam outlet, a first throttle valve, a confluence tee joint, a second throttle valve, a supplementary water inlet and a water pump, and the evaporator, the condenser, the subcooler, the first heat regenerator and the second heat regenerator all comprise a hot end and a cold end;
the heat supply source module is as follows: the heat source inlet, the heat source throttle valve, the hot end of the evaporator and the heat source outlet are sequentially connected to form a heat supply source module;
the high-temperature heat pump circulating module is as follows: the cold end outlet of the evaporator, the air supply compressor, the main body compressor, the condenser hot end and the subcooler hot end are sequentially connected to perform refrigerant air supply and primary subcooling, one side of the heat return control valve bank is connected with the hot end of the first reheater to form a heat return side, the other side of the heat return control valve bank is connected with the hot end outlet of the subcooler to form an overflow side, the overflow side and the heat return side are converged and then are connected with the first flash evaporator through a primary expansion valve, one end of the first flash evaporator is connected with the main body compressor through the cold end of the first reheater, the other end of the first flash evaporator is connected with the hot end inlet of the second reheater, the hot end outlet of the second reheater is connected with a secondary expansion valve, the secondary expansion valve is connected with the cold end of the second reheater through the evaporator cold end, and;
the evaporation module is as follows: the cold end of the subcooler is connected with the cold end of the condenser, the cold end outlet of the condenser is connected with a second flash evaporator through an expansion valve of an evaporation system, one side of the second flash evaporator is connected with a steam outlet, the other side of the second flash evaporator is connected with a first throttling valve, a supplementing water inlet is connected with a second throttling valve, the second throttling valve is connected with one side of a confluence tee joint, the other two sides of the confluence tee joint are respectively connected with the first throttling valve and a water pump, and the water pump is connected with the cold end inlet.
Furthermore, the evaporator comprises an evaporator tube pass and an evaporator shell pass, the hot end of the evaporator is provided with two openings which are respectively a hot end inlet and an outlet of the evaporator, the cold end of the evaporator is provided with two openings which are respectively a cold end inlet and an outlet of the evaporator, and the heat source throttle valve is connected with the evaporator tube pass through the inlet of the hot end of the evaporator and transfers heat to the evaporator shell pass through the evaporator tube pass.
Furthermore, the air supply compressor is provided with two ports which are respectively an air inlet and an air outlet of the air supply compressor, a cold end outlet of the evaporator is connected with the air inlet of the air supply compressor, the main body compressor comprises a stage compression cavity, a mixing cavity and a high-stage compression cavity, the main body compressor is correspondingly provided with the air inlet, the air supply port and the air outlet of the main body compressor respectively, the low-stage compression cavity is connected with the high-stage compression cavity through the mixing cavity, the mixing cavity is connected with the air outlet of the air supply compressor through the air supply port of the main body compressor, the high-stage compression cavity is connected with the condenser through the air outlet of the main body compressor, and the low-stage; the first heat regenerator comprises a first heat regenerator tube pass and a first heat regenerator shell pass, the hot end of the first heat regenerator is provided with two communicated ports which are respectively a hot end inlet and an outlet of the first heat regenerator, the cold end of the first heat regenerator is provided with two communicated ports which are respectively a cold end inlet and an outlet of the first heat regenerator, the inlet and the outlet of the hot end of the first heat regenerator and the first heat regenerator tube pass form the hot end of the first heat regenerator, the cold end inlet and the outlet of the first heat regenerator and the first heat regenerator shell pass form the cold end of the first heat regenerator, the condenser comprises a condenser shell pass and a condenser tube pass, the hot end of the condenser is provided with two communicated ports which are respectively connected with the condenser shell pass, and the cold end of the condenser is provided with two communicated ports which are respectively connected with the condenser tube pass; the subcooler comprises a subcooler shell side and a subcooler tube side, the hot end of the subcooler is provided with two through holes which are communicated and respectively connected with the subcooler shell side, the cold end of the subcooler is provided with two through holes which are communicated and respectively connected with the subcooler tube side, the heat return control valve group comprises a heat return first throttle valve and a heat return second throttle valve, the first throttle valve is communicated with the hot end of the first reheater through the hot end inlet of the first reheater, the first throttle valve is connected with the first-stage expansion valve through the hot end outlet of the first reheater, the heat return second throttle valve is connected with the first-stage expansion valve and is in parallel connection with the heat return first throttle valve of the first reheater in series connection, the first flash device comprises a first flash device tank cavity and a first flash device pressure control device, five through holes are arranged on the first flash device and respectively are a first flash device a, a first flash device b and a first flash device through hole b, The first flash vessel cavity is connected with the first flash vessel pressure control device through the first flash vessel port e, the first flash vessel port a is communicated with the primary expansion valve, the first flash vessel port d is communicated with the hot end inlet of the first regenerator, the first flash vessel port c is communicated with the pressure sensor to monitor the internal pressure of the first flash vessel, the first flash vessel cavity is connected with the second regenerator through the first flash vessel port b, the second heat regenerator comprises a second heat regenerator tube side and a second heat regenerator shell side, the hot end of the second heat regenerator is provided with two ports which are communicated and respectively connected with the second heat regenerator tube side, and the cold end of the second heat regenerator is provided with two through ports which are communicated with each other and are respectively connected with the shell side of the second heat regenerator, and the secondary expansion valve is connected with the evaporator through a cold end inlet of the evaporator.
Furthermore, an outlet in an opening at the cold end of the subcooler is communicated with an inlet in an opening at the cold end of the condenser, so that the tube side of the subcooler is connected with the tube side of the condenser, the tube side of the condenser is connected with an expansion valve of an evaporation system through an outlet in an opening at the cold end of the condenser, the second flash evaporator comprises a second flash evaporator tank cavity and a second flash evaporator pressure control device, the second flash evaporator is provided with five openings which are respectively a first opening, a second opening, a third opening, a fourth opening and a fifth opening, the second flash evaporator tank cavity is respectively connected with the second flash evaporator pressure control device through the fifth opening, is connected with the expansion valve of the evaporation system through the first opening, is connected with a steam outlet through the second opening, is connected with the first throttle valve through the third opening and is connected with the pressure sensor through the fourth opening, the confluence tee is provided with a first interface, a second interface and a third interface, the first interface and the first interface are confluence ports, the third interface is outflow ports, the confluence tee joint is respectively connected with the first throttling valve through the first interface, the second throttling valve through the second interface and the water pump through the third interface, and the water pump is connected with a pipe pass of the subcooler through an inlet of a hot end port of the subcooler.
Has the advantages that: the invention provides a multi-pressure-stage air-supplementing type high-temperature heat pump steam system, which adopts a high-temperature heat pump steam making technology under multi-stage pressure, which is formed by a heat source, a high-temperature heat pump system and an evaporation system together, compared with the structure of the traditional heat pump system, the system has a multi-pressure-stage air supplementing process, and has obvious advantages in heating performance under the working environment of a high-temperature heat pump with large temperature span and large pressure ratio.
The working state of the circulating refrigerant is effectively controlled by four stages of pressure of low pressure, medium pressure, high pressure and air supply pressure through the double compressors, the operation power consumption of the compressors is reduced, the heating efficiency of a high-temperature heat pump system under the condition of large pressure ratio is improved, the steam making efficiency of the system is improved, the liquid impact phenomenon in the main compressor is avoided by arranging the first heat regenerator, the efficiency and the income of the system for making steam are improved under the condition of meeting the whole process flow of the system, the process technology for efficiently producing hot product steam is realized, and the double compressors are environment-friendly and wide in application range.
Drawings
FIG. 1 is a schematic view of the cycle architecture of the system of the present invention;
FIG. 2 is a schematic diagram of a portion of a heat supply source of the system of the present invention;
FIG. 3 is a schematic diagram of a portion of a high temperature heat pump system of the present invention;
FIG. 4 is a schematic view of a portion of the vaporization system of the present system;
FIG. 5 is a state node at various stages in the system of the present invention;
FIG. 6 shows the temperature entropy change of the high temperature refrigerant during the heating cycle of the high temperature heat pump;
FIG. 7 is a graph of the change in temperature entropy of the hot product water from liquid to vapor in a steam evaporation cycle system.
In the figure: 1. heat source inlet, 2, heat source throttle valve, 3, evaporator, 301, evaporator pass, 302, evaporator shell pass, 311, evaporator port a, 312, evaporator port b, 313, evaporator port c, 314, evaporator port d, 4, heat source outlet, 5, make-up air compressor, 51, make-up air compressor inlet, 52, make-up air compressor outlet, 6, body compressor, 601, low stage compression chamber, 602, mixing chamber, 603, high stage compression chamber, 611, body compressor port a, 612, body compressor port b, 613, body compressor port c, 7, condenser, 711, condenser port a, 712, condenser port b, 713, condenser port c, 714, condenser d, 701, condenser shell pass, 702, condenser pass, 8, 811, subcooler port a, 812, subcooler port b, 813, 811, subcooler port a, subcooler port b, 813, Subcooler port c, 814, subcooler port d, 801, subcooler shell side, 802, subcooler tube side, 9, regenerative control valve set, 901, regenerative first throttle valve, 902, regenerative second throttle valve, 10, first regenerator, 101, first regenerator port a, 102, first regenerator port b, 103, first regenerator port c, 104, first regenerator port d, 1001, first regenerator tube side, 1002, first regenerator shell side, 11, one-level expansion valve, 12, first flash, 121, first flash port a, 122, first flash port b, 123, first flash port c, 124, first flash port d, 125, first flash port e, 1201, first flash tank cavity, 1202, first flash pressure controller, 13, second flash, 131, second regenerator port a, 132, second flash port b, 133, second flash tank cavity, 1202, first flash pressure controller, 13, second flash tank pressure controller, The second heat regenerator port c, 134, the second heat regenerator port d, 1301, the first heat regenerator tube side, 1302, the second heat regenerator shell side, 14, the second-stage expansion valve, 15, the evaporation system expansion valve, 16, the second flash evaporator, 1611, the first port, 1612, the second port, 1613, the third port, 1614, the fourth port, 1615, the fifth port, 1601, the second flash evaporator tank cavity, 1602, the second flash evaporator pressure control device, 17, the steam outlet, 18, the first throttle valve, 19, the confluence tee joint, 191, the first interface, 192, the second interface, 193, the third interface, 20, the second throttle valve, 21, the make-up water inlet, 22, the water pump.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail with reference to the following embodiments. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are intended for purposes of illustration only and are not intended to limit the scope of the invention.
The invention is further described below with reference to the accompanying drawings:
as shown in fig. 1, a multi-pressure-stage air-supplement type high-temperature heat pump steam system is composed of a heat supply source module, a high-temperature heat pump cycle module and an evaporation module, wherein the heat supply source module, the high-temperature heat pump cycle module and the evaporation module are composed of a heat source inlet 1, a heat source throttle valve 2, an evaporator 3, a heat source outlet 4, an air supplement compressor 5, a main body compressor 6, a condenser 7, a subcooler 8, a heat regeneration control valve group 9, a first heat regenerator 10, a first-stage expansion valve 11, a first flash evaporator 12, a second heat regenerator 13, a second-stage expansion valve 14, an evaporation system expansion valve 15, a second flash evaporator 16, a steam outlet 17, a first throttle valve 18, a confluence tee 19, a second throttle valve 20, a make-up water inlet 21 and a water pump 22, wherein the heat source inlet 1 is connected with the heat source throttle valve 2, the heat releasing end of the evaporator 3 is a hot, the heat source throttle valve 2 is connected with a heat source outlet 4 through the hot end of an evaporator 3, the cold end outlet of the evaporator 3 is connected with an air supplement compressor 5, the air supplement compressor 5 is connected with a main compressor 6 to play a role of refrigerant air supplement, the heat release end of a condenser 7 is a hot end, the heat absorption end of the condenser 7 is a cold end, the exhaust port of the main compressor 6 is connected with the hot end of the condenser 7, a subcooler 8 at the hot end outlet of the condenser 7 is connected for primary subcooling, the subcooler 8 is connected with a heat regeneration control valve bank 9, one side of the heat regeneration control valve bank 9 is connected with the hot end of a first heat regenerator 10, which is called a heat regeneration side and is used for controlling the heat regeneration degree of system circulation, the other side of the heat regeneration control valve bank 9 is connected with the subcooler 8, which is called an overflow side, the small regulation and control of the heat regeneration degree of a refrigerant are realized through combining the heat regeneration side, the first-time pressure reduction of the working medium is realized, a first-stage expansion valve 11 is connected with a first flash evaporator 12, one end of the first flash evaporator 12 is connected with a main compressor 6 through a cold end of a first regenerator 10, the other end of the first flash evaporator is connected with a second regenerator 13, the saturated liquid refrigerant is subcooled, a hot end of the second regenerator 13 is connected with a second-stage expansion valve 14, the second-stage expansion valve 14 is connected with a cold end of the second regenerator 13 through a cold end of an evaporator 3 to further overheat the refrigerant, an outlet side of the cold end of the second regenerator 13 is connected with a gas supplementing compressor 5, the cold end of a subcooler 8 is connected with a cold end of a condenser 7 to realize twice heat exchange with different temperature differences, an outlet of the cold end of the condenser 7 is connected with a second flash evaporator 16 through an evaporation system expansion valve 15, one side of the second flash evaporator 16 is connected with a steam, the second throttle valve 20 is connected with the first throttle valve 18 through a confluence tee joint 19, the confluence tee joint 19 is connected with a water pump 22, and the water pump 22 is connected with a cold end inlet of the subcooler 8, so that a multi-pressure-stage air supplementing type high-temperature heat pump steam system is formed.
Preferably, the multi-pressure-stage air-supplementing high-temperature heat pump steam system is characterized in that: the evaporator 3 comprises an evaporator tube pass 301 and an evaporator shell pass 302, and four ports of an evaporator port a311, an evaporator port b312, an evaporator port c313 and an evaporator port d314, the evaporator port a311, the evaporator port b312 and the evaporator tube pass 301 form a hot end of the evaporator 3, wherein the evaporator port a311 and the evaporator port b312 are respectively an inlet and an outlet of the hot end of the evaporator 3, the evaporator port c313, the evaporator port d314 and the evaporator shell pass 302 form a cold end of the evaporator 3, the evaporator port c313 and the evaporator port d314 are respectively an inlet and an outlet of the cold end of the evaporator 3, a heat source inlet 1, a heat source throttle valve 2, the evaporator tube pass 301 and the heat source outlet 4 jointly form a heat supply source of a multi-pressure-level air-supplementing high-temperature heat pump steam system, as shown in fig. 2, the heat source inlet 1 is connected with the heat source throttle valve 2, the mass flow of the heat supply source is controlled by the heat source throttle valve 2, therefore, the heat supply of the heat source end of the system is controlled, the heat source throttling valve 2 is connected with the evaporator tube pass 301, heat is transferred to the evaporator shell pass 302 through the evaporator tube pass 301, the evaporator tube pass 301 is connected with the heat source outlet 4, when the heat source control system works, a heat source flows in from the heat source inlet 1, the flow is controlled by the heat source throttling valve 2, the heat supplied by the heat source is controlled, and then the heat enters the evaporator tube pass 301 through the evaporator opening a311 to release heat and then flows out from the evaporator opening b to the heat source outlet 4 to be discharged.
Preferably, the multi-pressure-stage air-supplementing high-temperature heat pump steam system is characterized in that: the cold end of the evaporator 3 is connected with the air supply compressor 5 through a port 3d, the system realizes multi-pressure-level pressure control by combining the air supply compressor 5 and the main body compressor 6 to adjust the energy efficiency coefficient COP of the high-temperature heat pump system, the system realizes multi-pressure-level pressure control by the air supply compressor 5 and the main body compressor 6 to adjust the COP of the high-temperature heat pump system, the air supply compressor 5 comprises two ports of an air supply compressor air inlet 51 and an air supply compressor air outlet 52, the air supply compressor air inlet 51 is used as an air inlet of the air supply compressor 5, the air supply compressor air outlet 52 is used as an air outlet of the air supply compressor 5, the main body compressor 6 comprises a low-level compression cavity 601, a mixing cavity 602 and a high-level compression cavity 603, and comprises three ports of a main body compressor port 611, a main body compressor port b612 and a main, the main body compressor port b612 is used as a supplementary air port, the low-level compression cavity 601 is connected with the high-level compression cavity 603 through the mixing cavity 602, the high-level compression cavity 603 is connected with the condenser 7 through the main body compressor port c613, the low-level compression cavity 601 is connected with the first heat regenerator 10 through the main body compressor port a611, the first heat regenerator 10 comprises a first heat regenerator tube side 1001 and a first heat regenerator shell side 1002 and comprises four ports of a first heat regenerator port a101, a first heat regenerator port b102, a first heat regenerator port c103 and a first heat regenerator port d104, the first heat regenerator port a101 is communicated with the first heat regenerator port b102, the first heat regenerator tube side 1001 forms the hot end of the first heat regenerator 10, the first heat regenerator port c103 is communicated with the first heat regenerator port d104, the first heat regenerator shell side 1002 forms the cold end of the first heat regenerator 10, the mixing cavity 602 is connected with the supplementary air compressor 5 through the main body compressor port b612, the condenser 7 comprises a condenser shell pass 701 and a condenser tube pass 702, and comprises four ports of a condenser port a711, a condenser port b712, a condenser port c713 and a condenser port d714, the condenser port a711 is communicated with the condenser port b712 and forms a hot end of the condenser 7 with the condenser shell pass 701, the condenser port c713 is communicated with the condenser port d714 and forms a cold end of the condenser 7 with the condenser tube pass 702, the condenser 7 is connected with a subcooler 8, wherein the subcooler 8 comprises a subcooler shell pass 801 and a subcooler tube pass 802 and comprises four ports of a subcooler port a811, a subcooler port b812, a subcooler port 813 c and a subcooler port d814, the subcooler port a811 is communicated with the subcooler port b812 and forms a hot end of the subcooler 8 with the subcooler shell pass 801, the subcooler port c813 is communicated with the subcooler port 814 d and forms a cold end of the subcooler 8 with the subcooler tube pass 802, the hot end of the subcooler 8 is connected with a regenerative control valve group 9, the regenerative control valve group 9 comprises a regenerative first throttle valve 901 and a regenerative second throttle valve 902, the regenerative first throttle valve 901 is communicated with the hot end of the first regenerator 10 through a first regenerator port a101, the regenerative first throttle valve 901 is connected with the primary expansion valve 11 through the hot end of the first regenerator 10, the regenerative second throttle valve 902 is connected with the primary expansion valve 11 and is in parallel connection with the regenerative first throttle valve 901 of the first regenerator 10 in series, and the regenerative control valve group controls the refrigerant flow entering the first regenerator 10 through flow division control, thereby controlling the regenerative supercooling degree of the first regenerator and further controlling the superheat degree of saturated gaseous refrigerant in the second flash evaporator 12. The first stage expansion valve 11 is connected to the first flash vessel 12, wherein the first flash vessel 12 comprises a first flash vessel cavity 1201 and a first flash vessel pressure control device 1202, and further comprises a first flash vessel port a121, a first flash vessel port b122, a first flash vessel port c123, a first flash vessel port d124 and a first flash vessel port e125, the first flash vessel cavity 1201 is connected to the first flash vessel pressure control device 1202 through the first flash vessel port e125, the first flash vessel port a121 is connected to the first flash vessel expansion valve 11, the first flash vessel port d124 is connected to the first flash vessel port c103, so that the first flash vessel cavity 1201 is connected to the first flash vessel tank 1001, the first flash vessel port c123 is connected to a pressure sensor, the internal pressure of the first flash vessel 12 is monitored, the first flash vessel cavity 1201 is connected to the second flash vessel 13 through the first flash vessel port b122, and the second flash vessel heat regenerator 13 comprises a second flash vessel heat regenerator shell 1301, and contains four ports of a second regenerator port a131, a second regenerator port b132, a second regenerator port c133 and a second regenerator port d134, the second regenerator port a131 is communicated with the second regenerator port b132, and forms the hot end of the second regenerator 13 with the second regenerator tube pass 1301, the second regenerator port c133 is communicated with the second regenerator port d134, and forms the cold end of the second regenerator 13 with the second regenerator shell pass 1302, the second regenerator 13 is connected with the secondary expansion valve 14, and the secondary expansion valve 14 is connected with the evaporator 3 through the evaporator port c, thereby forming the high temperature heat pump system of the multi-pressure-stage air-supplementing type high temperature heat pump steam system, as shown in fig. 3. The high-temperature heat pump system comprises 4 different pressure stages, namely low-pressure stage, medium-pressure stage and high-pressure stage air supplement pressure, and is used for regulating and controlling the power consumption of a compressor and the heating capacity of a refrigerant, when the system works stably, high-pressure superheated refrigerant gas enters the hot end of a condenser 7 to release heat, then the refrigerant is in a high-pressure saturated liquid state, the refrigerant passes through a subcooler 8 and transfers the heat to an evaporation system, the saturated liquid refrigerant is subcooled for the first time, the subcooled refrigerant enters a regenerative control valve group 9 to be divided, a part of refrigerant enters the hot end of a first heat regenerator 10 from a regenerative side to release heat, the other part of refrigerant flows through a flow side to be converged with the refrigerant after the heat is released by the hot end of the first heat regenerator 10, the refrigerant realizes secondary subcooling under the action of the first heat regenerator 10, then the refrigerant is decompressed in an equal enthalpy by a primary expansion valve 11 and then is discharged to a first flash refrigerant 12, and, wherein a part of medium pressure saturated gaseous refrigerant enters the cold end of the first regenerator 10 through the airflow end of the first flash evaporator 12 to absorb heat and then is overheated, and then enters the low-stage compression cavity 601 of the main compressor 6 to be compressed for the first stage, wherein the overheating process is mainly to avoid the liquid impact phenomenon easily occurring in the compression process of the high-temperature refrigerant, the refrigerant is compressed to the air-supplementing pressure and enters the mixing cavity 602 to be mixed with the air-supplementing refrigerant, in order to further improve the system performance, the other part of saturated liquid refrigerant in the first flash evaporator 12 is supercooled through the hot end of the second regenerator 13, on one hand, the heat absorption capacity of the refrigerant in the evaporator is improved, on the other hand, the ignition loss of the refrigerant in the secondary expansion process is reduced, therefore, the supercooled refrigerant enters the secondary expansion valve 14 to be further decompressed in equal enthalpy, and finally enters the cold end of the evaporator 3 in a two-phase state under low, the refrigerant enters a cold end of a second heat regenerator 13 after being discharged from an evaporator 3 to be overheated, the overheated gaseous refrigerant enters an air-supplementing compressor 5 to be compressed, the gaseous refrigerant is compressed to air-supplementing pressure and enters a mixing cavity 602 to be mixed with the gaseous refrigerant discharged from a low-stage compression cavity 601, the gaseous refrigerant enters a high-stage compression cavity 603 to be compressed for the second stage after being mixed, the gaseous refrigerant is compressed to a high-pressure overheated state and is discharged from a main compressor 6 to enter a condenser 7 to form a closed loop type process cycle, A to M serve as state nodes of the refrigerant on a high-temperature heat pump system, as shown in figure 5, temperature-entropy changes of the refrigerant of the system at different nodes are shown in figure 6 by taking a refrigerant R245fa as an example, and compared with a steam single-stage type compression system, on the premise of avoiding the problems of liquid impact of. In addition, as the thermodynamic property of the refrigerant is improved, the circulation structure can also be applied to the heat pump operation in the environment with larger temperature difference, and is not limited to the refrigerant R245 fa.
Preferably, the multi-pressure-stage air-supplementing high-temperature heat pump steam system is characterized in that: an outlet 8 at the cold end of the subcooler 8 is communicated with a subcooler port d of a condenser 7, an inlet condenser port c at the cold end of the condenser 7 is communicated, a subcooler tube side 802 is connected with a condenser tube side 702, the condenser tube side 702 is connected with an evaporation system expansion valve 15 through the condenser port d, the evaporation system expansion valve 15 is connected with a second flash evaporator 16, the second flash evaporator 16 comprises a second flash evaporator tank cavity 1601 and a second flash evaporator pressure control device 1602, and the second flash evaporator tank cavity 1601 comprises five ports including a first port 1611, a second port 1612, a third port 1613, a fourth port 1614 and a fifth port 1615, when the operation is stable, the pressure in the second flash evaporator tank cavity 1601 is determined as production pressure, so that state parameters for producing saturated steam are determined, the second flash evaporator tank cavity 1601 is connected with the second flash evaporator pressure control device 1602 through the fifth port, the second flash evaporator pressure control device 1602 is used for adjusting the production pressure of the second flash evaporator tank 1601, the second flash evaporator tank cavity 1601 is connected with an evaporation system expansion valve 15 through a first port, the second flash evaporator tank cavity 1601 is connected with a steam outlet 17 through a second port, the second flash evaporator tank cavity 1601 is connected with a first throttle valve 18 through a third port, the fourth port is connected with a pressure sensor for monitoring the pressure state in the second flash evaporator 16, the first throttle valve 18 is connected with a confluence tee 19 through a first interface 191, the confluence tee 19 comprises three interfaces of a first interface 191, a second interface 192 and a third interface 193, wherein the first interface 191 and the second interface 192 are confluence ports, the third interface 193 is an outflow port, a make-up water inlet 21 is connected with the second throttle valve 20, the make-up water amount is controlled through the second throttle valve 20, the second throttle valve 20 is connected with the confluence tee 19 through the second interface 192, the confluence tee 19 is connected with a water pump 22 through the third interface, the water pump 22 is connected with a subcooler pipe pass 802 through a subcooling port c, an evaporation system in the form of a semi-open loop constituting a multi-pressure stage air make-up type high temperature heat pump steam system is shown in fig. 4. When the system works stably, make-up water is added from a make-up water inlet 21, the flow rate of the make-up water is controlled by a second throttle valve 20, saturated water under the production pressure in a second flash evaporator 16 passes through a first throttle valve 18 and is converged with the make-up water in a converging tee joint 19, then mixed hot water is pressurized by a water pump 22 to provide power to enter a subcooler tube pass 802 for preheating, the preheated hot water enters a condenser tube pass 702 for absorbing heat again, the hot water after absorbing heat is changed into a gas-liquid two-phase state and enters an evaporation system expansion valve 15 for equal enthalpy pressure reduction, saturated steam discharged from the gas flow end of the second flash evaporator 16 is discharged out of the system through a steam outlet 17 to be used as a hot product of a production target, saturated liquid water discharged from the liquid flow end of the second flash evaporator 16 is subjected to the next round of steam generation operation along with the process to form a half-open loop type process cycle, and A 'to H' are, as shown in fig. 5, the temperature entropy changes of the hot water and steam in the system at different nodes are as shown in fig. 7, and the quality of the hot steam can be regulated and controlled along with the change of the condensing temperature in the high-temperature heat pump system and the pressure drop proportion of the expansion valve 15 of the evaporation system.
It is to be understood that the above description is not intended to limit the present invention, and the present invention is not limited to the above examples, and those skilled in the art may make modifications, alterations, additions or substitutions within the spirit and scope of the present invention.
Claims (4)
1. A multi-pressure-level air supplement type high-temperature heat pump steam system is composed of a heat supply source module, a high-temperature heat pump circulation module and an evaporation module and is characterized in that the heat supply source module, the high-temperature heat pump circulation module and the evaporation module are composed of a heat source inlet, a heat source throttle valve, an evaporator, a heat source outlet, an air supplement compressor, a main body compressor, a condenser, a subcooler, a heat return control valve bank, a first heat regenerator, a first-stage expansion valve, a first flash evaporator, a second heat regenerator, a second-stage expansion valve, an evaporation system expansion valve, a second flash evaporator, a steam outlet, a first throttle valve, a confluence tee joint, a second throttle valve, a supplementary water inlet and a water pump, wherein the evaporator, the condenser, the subcooler, the first heat regenerator and the second heat regenerator all comprise a hot end and a cold end;
the heat supply source module is as follows: the heat source inlet, the heat source throttle valve, the hot end of the evaporator and the heat source outlet are sequentially connected to form a heat supply source module;
the high-temperature heat pump circulating module is as follows: the cold end outlet of the evaporator, the air supply compressor, the main body compressor, the condenser hot end and the subcooler hot end are sequentially connected to perform refrigerant air supply and primary subcooling, one side of the heat return control valve bank is connected with the hot end of the first reheater to form a heat return side, the other side of the heat return control valve bank is connected with the hot end outlet of the subcooler to form an overflow side, the overflow side and the heat return side are converged and then are connected with the first flash evaporator through a primary expansion valve, one end of the first flash evaporator is connected with the main body compressor through the cold end of the first reheater, the other end of the first flash evaporator is connected with the hot end inlet of the second reheater, the hot end outlet of the second reheater is connected with a secondary expansion valve, the secondary expansion valve is connected with the cold end of the second reheater through the evaporator cold end, and;
the evaporation module is as follows: the cold end of the subcooler is connected with the cold end of the condenser, the cold end outlet of the condenser is connected with a second flash evaporator through an expansion valve of an evaporation system, one side of the second flash evaporator is connected with a steam outlet, the other side of the second flash evaporator is connected with a first throttling valve, a supplementing water inlet is connected with a second throttling valve, the second throttling valve is connected with one side of a confluence tee joint, the other two sides of the confluence tee joint are respectively connected with the first throttling valve and a water pump, and the water pump is connected with the cold end inlet.
2. The multi-pressure-stage air-supplementing high-temperature heat pump steam system according to claim 1, wherein the evaporator comprises an evaporator tube side and an evaporator shell side, the hot end of the evaporator is provided with two ports which are respectively a hot end inlet and an outlet of the evaporator, the cold end of the evaporator is provided with two ports which are respectively a cold end inlet and an outlet of the evaporator, and the heat source throttle valve is connected with the evaporator tube side through the inlet of the hot end of the evaporator and transfers heat to the evaporator shell side through the evaporator tube side.
3. The multi-pressure stage air-supplementing high-temperature heat pump steam system of claim 1, wherein the air-supplementing compressor is provided with two ports, namely an air inlet and an air outlet of the air-supplementing compressor, the cold-end outlet of the evaporator is connected with the air inlet of the air-supplementing compressor, the main body compressor comprises a stage compression chamber, a mixing chamber and a high stage compression chamber, and the stage compression chamber, the mixing chamber and the high stage compression chamber are correspondingly provided with the air inlet, the air supplementing port and the air outlet of the main body compressor respectively, the low stage compression chamber is connected with the high stage compression chamber through the mixing chamber, the mixing chamber is connected with the air outlet of the air-supplementing compressor through the air supplementing port of the main body compressor, the high stage compression chamber is connected with the condenser through the air outlet of the; the first heat regenerator comprises a first heat regenerator tube pass and a first heat regenerator shell pass, the hot end of the first heat regenerator is provided with two communicated ports which are respectively a hot end inlet and an outlet of the first heat regenerator, the cold end of the first heat regenerator is provided with two communicated ports which are respectively a cold end inlet and an outlet of the first heat regenerator, the inlet and the outlet of the hot end of the first heat regenerator and the first heat regenerator tube pass form the hot end of the first heat regenerator, the cold end inlet and the outlet of the first heat regenerator and the first heat regenerator shell pass form the cold end of the first heat regenerator, the condenser comprises a condenser shell pass and a condenser tube pass, the hot end of the condenser is provided with two communicated ports which are respectively connected with the condenser shell pass, and the cold end of the condenser is provided with two communicated ports which are respectively connected with the condenser tube pass; the subcooler comprises a subcooler shell side and a subcooler tube side, the hot end of the subcooler is provided with two through holes which are communicated and respectively connected with the subcooler shell side, the cold end of the subcooler is provided with two through holes which are communicated and respectively connected with the subcooler tube side, the heat return control valve group comprises a heat return first throttle valve and a heat return second throttle valve, the first throttle valve is communicated with the hot end of the first reheater through the hot end inlet of the first reheater, the first throttle valve is connected with the first-stage expansion valve through the hot end outlet of the first reheater, the heat return second throttle valve is connected with the first-stage expansion valve and is in parallel connection with the heat return first throttle valve of the first reheater in series connection, the first flash device comprises a first flash device tank cavity and a first flash device pressure control device, five through holes are arranged on the first flash device and respectively are a first flash device a, a first flash device b and a first flash device through hole b, The first flash vessel cavity is connected with the first flash vessel pressure control device through the first flash vessel port e, the first flash vessel port a is communicated with the primary expansion valve, the first flash vessel port d is communicated with the hot end inlet of the first regenerator, the first flash vessel port c is communicated with the pressure sensor to monitor the internal pressure of the first flash vessel, the first flash vessel cavity is connected with the second regenerator through the first flash vessel port b, the second heat regenerator comprises a second heat regenerator tube side and a second heat regenerator shell side, the hot end of the second heat regenerator is provided with two ports which are communicated and respectively connected with the second heat regenerator tube side, and the cold end of the second heat regenerator is provided with two through ports which are communicated with each other and are respectively connected with the shell side of the second heat regenerator, and the secondary expansion valve is connected with the evaporator through a cold end inlet of the evaporator.
4. The multi-pressure-stage air-supplementing high-temperature heat pump steam system according to claim 3, wherein an outlet of the opening at the cold end of the subcooler is communicated with an inlet of the opening at the cold end of the condenser, so that the connection between the subcooler tube pass and the condenser tube pass is realized, the condenser tube pass is connected with the expansion valve of the evaporation system through an outlet of the opening at the cold end of the condenser, the second flash evaporator comprises a second flash evaporator tank cavity and a second flash evaporator pressure control device, five openings are arranged on the second flash evaporator, namely a first opening, a second opening, a third opening, a fourth opening and a fifth opening, the second flash evaporator tank cavity is connected with the second flash evaporator pressure control device through the fifth opening, is connected with the expansion valve of the evaporation system through the first opening, is connected with the steam outlet through the second opening, is connected with the first throttle valve through the third opening, and is connected with the pressure sensor through the fourth opening, the three-way valve is characterized in that the confluence tee joint is provided with a first interface, a second interface and a third interface, the first interface and the first interface are confluence ports, the third interface is an outflow port, the confluence tee joint is respectively connected with the first throttling valve through the first interface, the second throttling valve through the second interface and the water pump through the third interface, and the water pump is connected with a pipe pass of the subcooler through an inlet of a hot end port of the subcooler.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010741387.1A CN111854225B (en) | 2020-07-29 | 2020-07-29 | Multi-pressure-stage air supplementing type high-temperature heat pump steam system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010741387.1A CN111854225B (en) | 2020-07-29 | 2020-07-29 | Multi-pressure-stage air supplementing type high-temperature heat pump steam system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111854225A true CN111854225A (en) | 2020-10-30 |
| CN111854225B CN111854225B (en) | 2022-01-28 |
Family
ID=72948775
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010741387.1A Active CN111854225B (en) | 2020-07-29 | 2020-07-29 | Multi-pressure-stage air supplementing type high-temperature heat pump steam system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111854225B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114909725A (en) * | 2022-05-30 | 2022-08-16 | 格力电器（合肥）有限公司 | High-efficiency energy-saving multi-split system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2088388A1 (en) * | 2008-02-06 | 2009-08-12 | STIEBEL ELTRON GmbH & Co. KG | Heat pump system |
| CN105466059A (en) * | 2015-12-21 | 2016-04-06 | 珠海格力电器股份有限公司 | Transcritical heat pump device |
| US20170016651A1 (en) * | 2015-07-15 | 2017-01-19 | Korea Institute Of Energy Research | Engery system |
| CN110793230A (en) * | 2019-10-30 | 2020-02-14 | 河南科技大学 | Large-temperature span high-temperature heat pump system |
| CN110986414A (en) * | 2019-11-25 | 2020-04-10 | 西安交通大学 | Multi-temperature-zone and large-temperature-span heat pump circulating system adopting ejector for increasing efficiency |
| CN111288679A (en) * | 2020-03-09 | 2020-06-16 | 中国轻工业武汉设计工程有限责任公司 | Single-stage and double-stage switching evaporation supercooling ejector refrigeration heat pump circulation system |
-
2020
- 2020-07-29 CN CN202010741387.1A patent/CN111854225B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP2088388A1 (en) * | 2008-02-06 | 2009-08-12 | STIEBEL ELTRON GmbH & Co. KG | Heat pump system |
| US20170016651A1 (en) * | 2015-07-15 | 2017-01-19 | Korea Institute Of Energy Research | Engery system |
| CN105466059A (en) * | 2015-12-21 | 2016-04-06 | 珠海格力电器股份有限公司 | Transcritical heat pump device |
| CN110793230A (en) * | 2019-10-30 | 2020-02-14 | 河南科技大学 | Large-temperature span high-temperature heat pump system |
| CN110986414A (en) * | 2019-11-25 | 2020-04-10 | 西安交通大学 | Multi-temperature-zone and large-temperature-span heat pump circulating system adopting ejector for increasing efficiency |
| CN111288679A (en) * | 2020-03-09 | 2020-06-16 | 中国轻工业武汉设计工程有限责任公司 | Single-stage and double-stage switching evaporation supercooling ejector refrigeration heat pump circulation system |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114909725A (en) * | 2022-05-30 | 2022-08-16 | 格力电器（合肥）有限公司 | High-efficiency energy-saving multi-split system |
| CN114909725B (en) * | 2022-05-30 | 2024-03-15 | 格力电器（合肥）有限公司 | Efficient energy-saving multi-split system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111854225B (en) | 2022-01-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107576085B (en) | Refrigerating system | |
| JP2012533046A (en) | Jet pump system, apparatus, arrangement, and method of use for heat and cold management | |
| CN109708337B (en) | Multistage series compression heat pump unit | |
| CN107576090B (en) | Refrigerating system | |
| CN105466061A (en) | Two-stage compression refrigerator system and working method thereof | |
| CN111288679B (en) | Single-stage and double-stage switching evaporation supercooling ejector refrigeration heat pump circulation system | |
| CN111854225B (en) | Multi-pressure-stage air supplementing type high-temperature heat pump steam system | |
| CN108759157B (en) | One-time throttling two-stage compression heat pump system | |
| CN212109059U (en) | Single-stage and double-stage switching evaporation supercooling refrigeration heat pump circulation system | |
| CN214701327U (en) | Centrifugal cascade high-pressure ratio series unit | |
| CN111288678B (en) | Single-stage and double-stage switching evaporation supercooling refrigeration heat pump circulation system | |
| CN212299531U (en) | Single-stage and double-stage switching evaporation supercooling ejector refrigeration heat pump circulation system | |
| CN111550944B (en) | Triple throttling enthalpy-increasing double-condensation refrigerating system, air conditioner and control method | |
| CN114739037A (en) | Double-ejector multi-loop evaporation vapor compression circulation system and working method | |
| CN217763967U (en) | Refrigerating system and air conditioning equipment | |
| CN115111808B (en) | Compression injection type dual-temperature heat pump system | |
| CN116147217B (en) | Ejector-liquid pump compound synergistic refrigeration cycle system for cooling data center | |
| CN112361646B (en) | Shunting regulation and control double-circulation coupling type high-temperature heat pump system | |
| CN215832229U (en) | High-temperature type gas heat pump system with mechanical supercooling function | |
| CN220169699U (en) | Air energy central air conditioner refrigerant circulation system | |
| CN112178977B (en) | Combined cooling heating and power system and method | |
| CN110748937B (en) | Compressor double-pressure working condition large-temperature-difference heat taking electric drive heat pump unit and working method | |
| CN114322365A (en) | Single-working medium combined cycle heat pump device | |
| Chi et al. | Performance Study of a Novel Ejector-Cascade Refrigeration System with Regenerator | |
| CN114279100A (en) | Single-working medium combined cycle heat pump device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |