CN115574480A - System for many contrary carnot circulation are alternately heat transfer medium altogether - Google Patents
System for many contrary carnot circulation are alternately heat transfer medium altogether Download PDFInfo
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- CN115574480A CN115574480A CN202211083641.9A CN202211083641A CN115574480A CN 115574480 A CN115574480 A CN 115574480A CN 202211083641 A CN202211083641 A CN 202211083641A CN 115574480 A CN115574480 A CN 115574480A
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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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
- F25B31/00—Compressor arrangements
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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
- F25B39/00—Evaporators; Condensers
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses a system for multi-inverse Carnot circulation cross heat exchange medium, wherein a main circulation system is communicated with a first auxiliary circulation system to form a loop, the output end of the first auxiliary circulation system is communicated with the input end of an external heat exchange device through a heat exchange circulation pump, the output end of the external heat exchange device is communicated with the first auxiliary circulation system, and the output end of the main circulation system is communicated with a user terminal through a terminal circulation pump. Compared with the scheme of the overlapping heat pump used in the prior art, the temperature difference between the heat exchange medium fluid and the outside air is larger, the structure of the circulating flow is inconsistent, the temperature difference between the condenser and the evaporator can reach a higher level, and the temperature difference between the heat transfer medium and the outside heat source can be improved by a mode of heating and cooling for multiple times, so that the heat exchange speed can be increased, and the efficiency of the system can be improved.
Description
Technical Field
The invention relates to the technical field of thermal engineering and fluid machinery, in particular to a system of a multi-inverse Carnot cycle cross heat exchange medium.
Background
Building energy consumption now accounts for 46.7% of the energy consumption of the whole society, and a heating air conditioner accounts for more than 20% of the energy consumption of the whole society, if an advanced air energy heat pump can be researched to solve the problem of defrosting and can obtain stable and higher heating temperature under the condition of extremely cold weather, the heating device can completely replace the heating of a traditional gas boiler, change the existing heating mode of a gas boiler or an electric boiler which mainly converts energy into heat energy, and change the heating mode into the heating mode of a heat pump which completely adopts an energy transfer mode, 3.35 million tons of standard coal can be saved for China every year, and one trillion of electric power construction investment cost can also be saved. This will have a very important significance for carbon peak carbon neutralization.
At present, the heat pump unit operation efficiency of various heat pumps under the condition of lower ambient temperature is still lower, and the phenomenon of instability still appears in the operation at the same time, great efforts have been made for relevant scientific and technological workers for this purpose, many technical means have been adopted to improve, such as tonifying qi enthalpy increasing technology, electric auxiliary enthalpy increasing technology, overlapping heat pump, multistage compression, etc., although several heat exchangers can be reduced in multistage compression, its efficiency and stability are not as good as overlapping scheme, still it is still unsatisfactory, it is difficult to deal with extremely low ambient temperature, the reason is that because the evaporation temperature and the condensation temperature are greatly different during the refrigeration and heating process, the compression ratio is too large, the compressor is difficult to bear such large pressure difference, and the transfer of low temperature heat to high temperature place becomes very difficult. The heat pump is just like a carrier, the lower articles are more difficult to carry higher articles, that is, the heat pump is required to carry the low-temperature heat to the high-temperature place and also has the same problems, the heat is easy to carry in a plurality of steps, the larger the temperature difference between the low-temperature place and the high-temperature place is, the more difficult the heat is to carry, the lower the energy efficiency ratio during the operation is, and if the temperature difference is large to a certain degree, the heat pump unit cannot normally operate. Therefore, the related technical scheme of the overlapping heat pump is developed, the overlapping heat pump has good economic value for transferring low-temperature heat at the ambient temperature below-20 ℃, the traditional heat pump is not available, the efficiency of the overlapping heat pump is 24.4% higher than that of the traditional heat pump, the overlapping scheme is to connect two heat pump circulating systems in series to achieve the purpose of carrying the low-temperature heat, the overlapping scheme can reduce the temperature difference between a condenser and an evaporator, but still exchanges heat with air in a small temperature difference large flow mode when an external low-temperature heat source is obtained, the size of heat exchange equipment is increased, the flow of a heat exchange medium is increased, the power of a circulating pump and the power of an axial flow fan motor are increased, and the service life of the heat exchanger is shortened.
Generally, the content of water vapor in the whole air is 0.003-4%, but the heat can account for more than 99% of the heat of an air source, when the relative humidity of air reaches more than 60%, a large amount of latent heat of water vapor energy can be obtained only by cooling at most 5 ℃, the latent heat of water vapor energy at least accounts for more than 80% of the whole air energy, and the sensible heat ratio of air is very low and can be ignored sometimes. According to the comparison table of the relative humidity and the absolute moisture content of the air, the absolute moisture content and the corresponding dew point temperature of the air under the conditions of the relative humidity and different temperatures can be found, and the latent heat of the water vapor in the air can be obtained by knowing how much the temperature is reduced. For example, when the relative humidity is 60%, the latent heat of water vapor in the air can be obtained only by cooling the ambient temperature at-10 ℃ to below-15 ℃, because the dew point temperature is-15 ℃, the latent heat of water vapor which can be obtained when the ambient temperature is cooled to-20 ℃ is more than 98 times of the equivalent air volume, the sensible heat of the air can be almost ignored, if the relative humidity reaches 100%, the absolute moisture contents of the air at-10 ℃ and the air at-15 ℃ are respectively 2.3g/m < 3 > and 1.6g/m < 3 >, and if the relative humidity is 100%, the absolute moisture content of the air at the current temperature is the dew point temperature, the latent heat of the released water vapor can be 277 times of the equivalent air volume sensible heat, because the sensible heat released when the air is cooled at 5 ℃ is = 1.003J/(Kg · K) × 1.29Kg/m < 3 >/m < 1.29Kg/m < 3 > 3 ×5m 3 1k =6.46935j =0.0015kcal. That is to say, we only need to reduce the temperature by 2-3 ℃ under the condition that the relative humidity reaches one hundred percent, so as to obtain the sensible heat which is one hundred times of the equivalent air volume. The relative humidity of air in south of China generally exceeds 70% in winter, and the relative humidity of most of the inhabited places in north of China also exceeds 60% in most of time periods, so that the temperature reduction of 5-10 ℃ has strong economic value. If small temperature difference is adopted for heat exchange with air, the system is difficult to obtain the latent heat of water vapor in the air under the condition of low relative humidity, and the air cannot be obtained without large temperature difference heat exchangeAnother advantage of the latent heat of water vapor is attributed to it.
Based on the fact that temperature difference is the only power for heat exchange, the larger the temperature difference is, the faster the system extracts heat to air is, the larger the temperature difference is, the larger the heat exchange quantity is under the condition of the same heat exchange area and the same flow, the existing overlapping heat pump can deal with the condition of insufficient heating temperature in extremely cold weather to some extent, but does not have the advantage of heat exchange with air with large temperature difference, heat exchange with ambient air with large temperature difference can accelerate heat dissipation, if the air is absorbed, latent heat of water vapor in the air can be obtained, if the temperature difference is too small, the latent heat of water vapor in the air cannot be obtained, heat exchange equipment is relatively large, the needed air quantity and the flow quantity of heat exchange media are also large, the power of a circulating pump and the power of an axial flow fan motor are large, and the service life of the heat exchanger is shortened due to overlarge fluid flow.
In order to obtain high-efficiency heat exchange of the system, namely, the system can perform powerful heat exchange with the outside air, the heat dissipation to the air is good, and the heat is collected to the air, so that the purpose is to exhaust the heat into the atmosphere quickly, and the temperature difference between the heat exchange medium and the environment is the only heat transfer power, namely, a thermodynamic cycle system does not perform heat exchange with the outside air.
Therefore, it is necessary to design a system capable of improving the heat exchange process of the existing overlapping heat pump, and the system becomes a direction for further improvement.
Disclosure of Invention
In order to solve the technical problems, the invention provides a system for multi-inverse Carnot cycle cross heat exchange medium sharing, which comprises a main cycle system, a first auxiliary cycle system, a heat exchange cycle pump, an external heat exchange device, a terminal cycle pump and a user terminal, wherein the main cycle system is communicated with the first auxiliary cycle system to form a non-refrigerant side loop, the output end of the first auxiliary cycle system is communicated with the input end of the external heat exchange device through the heat exchange cycle pump, the output end of the external heat exchange device is communicated with the first auxiliary cycle system, and the output end of the main cycle system is communicated with the user terminal through the terminal cycle pump.
Preferably, the main circulation system comprises a main compressor, a main circulation valve, main circulation heat exchangers and a main refrigerant circulation throttling device, the main compressor is respectively communicated with the two main circulation heat exchangers through the main circulation valve to form a refrigerant circulation loop, the main refrigerant circulation throttling device is arranged between the main circulation heat exchangers, one of the main circulation heat exchangers is communicated with the non-refrigerant side of the first auxiliary circulation system, and the other main circulation heat exchanger is communicated with a user terminal through a terminal circulation pump.
Preferably, the first auxiliary circulating system comprises a first auxiliary compressor, a first auxiliary circulating valve, a first auxiliary circulating heat exchanger and a first auxiliary refrigerant circulating throttling device, the first auxiliary compressor is respectively communicated with the two first auxiliary circulating heat exchangers through the first auxiliary circulating valve to form a refrigerant loop, the first auxiliary circulating heat exchangers are connected in series with one main circulating heat exchanger to form a non-refrigerant side loop, the first auxiliary circulating heat exchangers are further communicated with the first auxiliary refrigerant circulating throttling device, one first auxiliary circulating heat exchanger is communicated with an external heat exchange device through a pipeline, and the other first auxiliary circulating heat exchanger is communicated with the external heat exchange device through a heat exchange circulating pump to form a non-refrigerant side loop.
Preferably, the external heat exchange device is one of a finned tube heat exchanger, a closed heat exchange tower or an open air heat exchange tower.
Preferably, the main circulation heat exchanger is one of a double-pipe heat exchanger, a shell-and-tube heat exchanger and a finned tube heat exchanger or a combination of the two.
Preferably, the first auxiliary circulation heat exchanger is one of a double-pipe heat exchanger, a shell-and-tube heat exchanger and a finned tube heat exchanger or a combination of the two.
Preferably, the main circulating valve is an electric four-way valve or four parallel electric angle valves.
Preferably, the first auxiliary circulation valve is an electric four-way valve or four parallel electric angle valves.
Preferably, the auxiliary circulation system further comprises a second auxiliary circulation system, the second auxiliary circulation system comprises a second auxiliary compressor, a second auxiliary circulation valve, a second auxiliary circulation heat exchanger and a second auxiliary refrigerant circulation throttling device, the second auxiliary compressor is communicated with the second auxiliary circulation heat exchanger through a plurality of second auxiliary circulation valves which are circumferentially connected in parallel, a second auxiliary refrigerant circulation throttling device is connected between the second auxiliary circulation heat exchangers, and the second auxiliary circulation heat exchanger and the first auxiliary circulation heat exchanger are arranged in series.
Compared with the prior art, the invention has the following beneficial effects:
(1) The main circulation system is communicated with the first auxiliary circulation system to form a loop, the output end of the first auxiliary circulation system is communicated with the input end of an external heat exchange device through a heat exchange circulating pump, the output end of the external heat exchange device is communicated with the first auxiliary circulation system, and the output end of the main circulation system is communicated with a user terminal through a terminal circulating pump;
(2) The first auxiliary circulation system and the second auxiliary circulation system can provide more than two times of heat source heating (or more than two times of cooling process nodes) for the heat exchanger of the main circulation system, and the heat of the heat-sharing medium fluid of the front process of the main circulation heat exchanger node is positively fed back (or negatively fed back) to the rear process of the node by means of the first auxiliary circulation system and the second auxiliary circulation system, so that the heating of the heat source is realized more than two times, or the temperature is reduced more than two times with the air heat-exchanging medium, and the heat-exchanging advantage of the heat-sharing medium fluid to the outside air with large temperature difference is obtained, thereby achieving the purposes of fast heat extraction or efficient heat absorption, realizing the stable operation of a heat pump under the condition of extremely cold weather, having higher heating temperature, and carrying out extremely low temperature refrigeration in the reverse operation, also having very strong economic value for low-temperature defrosting, and having very good economic effect for liquefied hydrogen.
Drawings
Fig. 1 is a schematic structural diagram of embodiment 1 of the present invention.
Fig. 2 is a schematic structural diagram of embodiment 2 of the present invention.
Fig. 3 is a schematic structural diagram of embodiment 3 of the present invention.
Fig. 4 is a schematic structural diagram of embodiment 4 of the present invention.
Detailed Description
The invention is further described with reference to the following drawings and detailed description.
As shown in fig. 1 to 4, a heat exchange circulation pump 1, an external heat exchange device 2, a terminal circulation pump 3, a user terminal 4, a main compressor 5, a main circulation valve 6, a main circulation heat exchanger 7, a main refrigerant circulation throttling device 8, a first auxiliary compressor 9, a first auxiliary circulation valve 10, a first auxiliary circulation heat exchanger 11, a first auxiliary refrigerant circulation throttling device 12, a second auxiliary compressor 13, a second auxiliary circulation valve 14, a second auxiliary circulation heat exchanger 15, and a second auxiliary refrigerant circulation throttling device 16.
In the description of the present invention, "a plurality" means two or more unless otherwise specified; the terms "upper", "lower", "left", "right", "inner", "outer", "front", "rear", "head", "tail", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present invention and to simplify the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," "third," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly stated or limited otherwise, the terms "connected" and "connected" are to be interpreted broadly, e.g., as being fixed or detachable or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood in a specific case to those of ordinary skill in the art.
Example 1
As shown in fig. 1, the main circulation system is communicated with the first auxiliary circulation system to form a loop, the output end of the first auxiliary circulation system is communicated with the input end of the external heat exchange device 2 through the heat exchange circulation pump 1, the output end of the external heat exchange device 2 is communicated with the first auxiliary circulation system, and the output end of the main circulation system is communicated with the user terminal 4 through the terminal circulation pump 3.
Specifically, the main circulation system comprises a main compressor 5, a main circulation valve 6, main circulation heat exchangers 7 and a main refrigerant circulation throttling device 8, the main compressor 5 is respectively communicated with the two main circulation heat exchangers 7 through the main circulation valve 6 to form a refrigerant loop, the main refrigerant circulation throttling device 8 is arranged between the main circulation heat exchangers 7, one main circulation heat exchanger 7 is communicated with the non-refrigerant side of the first auxiliary circulation system, and the other main circulation heat exchanger 7 is communicated with a user terminal 4 through a terminal circulation pump 3. The first auxiliary circulating system comprises a first auxiliary compressor 9, a first auxiliary circulating valve 10, first auxiliary circulating heat exchangers 11 and first auxiliary refrigerant circulating throttling devices 12, the first auxiliary compressor 9 is respectively communicated with the two first auxiliary circulating heat exchangers 11 through the first auxiliary circulating valve 10 to form a refrigerant loop, the first auxiliary circulating heat exchangers 11 are connected in series with one main circulating heat exchanger 7 to form a non-refrigerant side loop, the first auxiliary circulating heat exchangers 11 are further communicated with the first auxiliary refrigerant circulating throttling devices 12, one first auxiliary circulating heat exchanger 11 is communicated with the external heat exchange device 2 through a pipeline, and the other first auxiliary circulating heat exchanger 11 is communicated with the external heat exchange device 2 through a heat exchange circulating pump 1 to form a non-refrigerant side loop.
The embodiment is suitable for small-scale household central air-conditioning refrigeration or heat pump units, and is suitable for small-scale refrigeration and heating, the left main circulation heat exchanger 7 in the embodiment is a double-pipe heat exchanger, and the right main circulation heat exchanger 7 is a shell-and-tube heat exchanger; the first auxiliary circulating heat exchangers 11 are sleeve-type heat exchangers, the external heat exchange device 2 is a finned tube heat exchanger, a heat exchange medium fluid of the external heat exchange device is antifreeze fluid, and the main circulating valve 6 and the first auxiliary circulating valve 10 are both electric four-way valves;
the working principle of the embodiment is as follows: when the main compressor 5 and the first auxiliary compressor 9 work, under a refrigeration condition, the main compressor 5 and the first auxiliary compressor 9 press refrigerant into the main circulation heat exchanger 7 and the first auxiliary circulation heat exchanger 11 (both of which are condensers) through the respective main circulation valve 6 and the first auxiliary circulation valve 10, respectively, the refrigerant in the respective circulation releases latent heat in the main circulation heat exchanger 7 and the first auxiliary circulation heat exchanger 11 to the respective external heat exchange medium fluid, and then is condensed into liquid refrigerant, and the respective liquid refrigerant flows through the main refrigerant circulation throttling device 8 and the first auxiliary refrigerant circulation throttling device 12 to enter the main circulation heat exchanger 7 and the first auxiliary circulation heat exchanger 11 (both of which are evaporators) above, respectively, and the liquid refrigerant in the main circulation heat exchanger 7 connected with the user terminal 4 absorbs latent heat of refrigerant water on the other side and evaporates, the cooled refrigerant water can be conveyed to a user terminal 4 through a terminal circulating pump 3, a liquid refrigerant of a main circulating heat exchanger 7 connected with the user terminal 4 absorbs latent heat of a heat transfer medium fluid outside the liquid refrigerant to evaporate and cool the other main circulating heat exchanger 7, each gasified refrigerant is pressed into the main circulating heat exchanger 7 and a first auxiliary circulating heat exchanger 11 through a main circulating valve 6 and a low-pressure inlet of a first auxiliary circulating valve 10 by a main compressor 5 and a first auxiliary compressor 9 to complete the phase change circulation process of the refrigerant, the refrigerant inside the first auxiliary circulating heat exchanger 11 communicated with an external heat exchange device 2 evaporates to cause the temperature of the heat transfer medium fluid to be reduced along with the temperature, and finally the temperature reduction of the main circulating heat exchanger 7 (which is a condenser) connected with the first auxiliary circulating heat exchanger 11 in series is influenced, if the temperature of the main circulating heat exchanger 7 connected in series with the first auxiliary circulating heat exchanger 11 is reduced, the temperature of the other main circulating heat exchanger 7 (at this time, the evaporator) is correspondingly reduced, so that the temperature difference between the main circulating heat exchanger 7 and the condenser is reduced, and the advantage of large temperature difference heat exchange between the heat exchange medium fluid and the outside air can be obtained, because the heat of the heat exchange medium fluid for reducing the temperature of the main circulating heat exchanger 7 is transferred to the first auxiliary circulating heat exchanger 11 (at this time, the condenser) below by the first auxiliary circulating heat exchanger 11 above, and the temperature of the heat exchange medium fluid is increased by the first auxiliary circulating heat exchanger 11 below, which is the heat negative feedback. Under the operation condition of the heat exchange circulating pump 1, the main circulating valve 6 and the first auxiliary circulating valve 10 act to enable the first auxiliary circulating heat exchanger 11 above and the main circulating heat exchanger 7 connected with the user terminal 4 to become condensers, and the other first auxiliary circulating heat exchanger 11 and the main circulating heat exchanger 7 to become evaporators, so that the main compressor 5 and the first auxiliary compressor 9 work to press the circulating refrigerants into the other first auxiliary circulating heat exchanger 11 and the main circulating heat exchanger 7 respectively through the electric four-way valves, the latent heat is released to the refrigerant on the other side of the main circulating heat exchanger 7 connected with the user terminal 4 by the refrigerant in the main circulating heat exchanger 7, the temperature of the refrigerant is increased and then is conveyed into the user terminal 4 by the terminal circulating pump 3, the cooled refrigerant becomes a liquid refrigerant, and flows back to the corresponding main circulating heat exchanger 7 through the main refrigerant circulating throttling device 8, and is pressed into the main circulating heat exchanger 7 connected with the user terminal 4 again through the low-pressure inlet of the electric four-way valve 5 corresponding to complete the circulating process of the refrigerant of the main circulating system.
The refrigerant in the upper first auxiliary circulation heat exchanger 11 releases latent heat to the external heat exchange medium fluid and then is condensed into liquid refrigerant, the liquid refrigerant flows through the first auxiliary refrigerant circulation throttling device 12 and then enters the lower first auxiliary circulation heat exchanger 11 in the first auxiliary circulation system again, and is pressed into the lower first auxiliary circulation heat exchanger 11 again through the electric four-way valve by the first auxiliary compressor 9 again to complete the circulation process of the auxiliary circulation refrigerant, and the lower first auxiliary circulation heat exchanger 11 heats the corresponding main circulation heat exchanger 7 in the main circulation system, so that the temperature difference between an evaporator and a condenser is reduced in the operation process of the heat exchange circulation pump 1, the energy efficiency ratio is correspondingly improved, the heat of the main circulation heat exchanger 7 communicated with the first auxiliary circulation heat exchanger 11 is transferred from the low-temperature heat exchange medium by the lower first auxiliary circulation heat exchanger 11, the heat of the heat exchange medium fluid is continuously fed back to the main circulation heat exchanger 7 to further improve, the temperature of the heat exchange medium fluid is lower than that of the external air, the heat exchange medium and the heat exchange medium are more favorable for accelerating the heat exchange, the heat exchange medium is more suitable for the low-temperature environment of the heating and the heat exchange medium 1 is more stable.
Example 2
As shown in fig. 2, the present embodiment is different from embodiment 1 in that: the external heat exchanger 2 of the embodiment is a closed heat exchange tower, and the main circulation heat exchanger 7 and the first auxiliary circulation heat exchanger 11 are shell-and-tube heat exchangers; the other workflow steps were identical to example 1.
Example 3
As shown in fig. 3, the present embodiment is different from embodiment 1 in that: in this embodiment, the external heat exchanger 2 is an open air heat exchange tower, the main circulation heat exchanger 7 and the first auxiliary circulation heat exchanger 11 are shell-and-tube heat exchangers, and the main circulation valve 6 and the first auxiliary circulation valve 10 are four parallel electric angle valves.
The working principle of the embodiment is as follows: in the refrigeration working condition, the lower left and upper right main circulating valves 6 are opened, the upper left and lower right main circulating valves 6 are closed, the lower left and upper right first auxiliary circulating valves 10 are opened, the upper left and lower right first auxiliary circulating valves 10 are closed, when the main compressor 5 and the first auxiliary compressor 9 work, the respective refrigerants are respectively pressed into the corresponding main circulating heat exchanger 7 and the first auxiliary circulating heat exchanger 11 through the lower left main circulating valve 6 and the lower right first auxiliary circulating valve 10, the gaseous refrigerant releases latent heat to the outside fluid of the respective main circulating heat exchanger 7 and the first auxiliary circulating heat exchanger 11, then is condensed into liquid refrigerant, passes through the main refrigerant circulating throttling device 8 and the first auxiliary refrigerant circulating throttling device 12, then flows through the upper right main refrigerant 6 and the lower left first auxiliary circulating valve 10, then flows into the right main circulating heat exchanger 7 and the upper first auxiliary circulating heat exchanger 11, absorbs the latent heat of the respective outside media, evaporates, and is again pressed into the left main circulating heat exchanger 7 and the left first auxiliary circulating heat exchanger 7 through the respective left first auxiliary circulating valve 6 and the right auxiliary circulating heat exchanger 9, and the other side circulating water is evaporated and then is evaporated into the left first auxiliary circulating heat exchanger 7, and the respective auxiliary circulating water is evaporated and then is injected into the main refrigerant circulating heat exchanger (the respective main refrigerant circulating water circulating process) to complete the evaporation and the evaporation of the liquid refrigerant circulation process of the main refrigerant circulation heat exchanger 4;
and the first auxiliary circulating heat exchanger 11 on the upper side (the evaporator at this moment) can provide cooling service for the main circulating heat exchanger 7 on the left side, so that the temperature difference of the two main circulating heat exchangers 7 of the main circulating system is reduced and the energy efficiency ratio is improved, specifically, the heat of the heat-sharing medium fluid of the front section of the main circulating heat exchanger 7 on the left side is transferred to the first auxiliary circulating heat exchanger 11 on the lower side through the first auxiliary circulating heat exchanger 11 on the upper side to realize heat negative feedback, the outflow temperature of the heat-sharing medium fluid is caused to be much higher than the ambient temperature, and the heat is discharged into the atmospheric environment by being brought into the external heat exchange device 2 by the heat-sharing medium fluid through the heat-sharing circulating pump 1.
In the case of the heat pump operation, the lower left and upper right main circulation valves 6 are closed, the upper left and lower right main circulation valves 6 are opened, the lower left and upper right first auxiliary circulation valves 10 are closed, and the upper left and lower right first auxiliary circulation valves 10 are opened, when the main compressor 5 and the first auxiliary compressor 9 are operated, the respective refrigerants are pressed into the right main circulation heat exchanger 7 and the upper first auxiliary circulation heat exchanger 11 by the respective compressors through the respective lower right main circulation valves 6 and upper left first auxiliary circulation valves 10, and release latent heat to the respective other side fluid to become liquid refrigerants, the liquid refrigerants respectively flow through the respective main refrigerant circulation throttling devices 8 and first auxiliary refrigerant circulation throttling devices 12 and then respectively enter the left main circulation heat exchanger 7 and the lower first auxiliary circulation heat exchanger 11 to absorb the respective external fluid latent heat for evaporation, and the evaporated refrigerants respectively flow through the upper left main circulation valves 6 and the lower right first auxiliary circulation valves 10 and are pressed into the right main circulation heat exchanger 7 and the upper first auxiliary circulation heat exchanger 11 by the compressors again to complete the respective refrigerant circulation processes.
The right main circulation heat exchanger 7 obtains latent heat of refrigerant by warm medium water on the non-refrigerant side and then is driven into a user terminal 4 by a terminal circulation pump 3, the upper first auxiliary circulation condenser 11 is used for providing a heat source for the left main circulation heat exchanger 7, the heat source is a heat source obtained after two times of temperature rise, firstly, the external heat exchange device 2 asks for latent heat of water vapor in air and sensible heat of air to the external air, then the heat of the heat exchange medium fluid in the front flow of the left main circulation heat exchanger 7 is transferred to the rear flow of the left main circulation heat exchanger 7 by the first auxiliary circulation system, so that positive feedback of heat is realized, the two times of temperature rise of the heat exchange medium fluid are both at the rear part of the flow node of the left main circulation heat exchanger 7, and the two times of temperature drop of the heat exchange medium fluid are both at the front part of the flow node of the left main circulation heat exchanger 7, so that the energy efficiency ratio of the system is improved by reducing the temperature difference of the two main circulation heat exchangers, and more latent heat of the external air are easy to be taken by the lower temperature of the heat exchange medium fluid, and the heat exchange medium fluid is taken out to the external air by the external heat exchange device 2 by the heat exchange pump 1.
Example 4
As shown in fig. 4, the present embodiment is different from embodiment 3 in that: in this embodiment, the first auxiliary circulation heat exchanger 11 and the second auxiliary circulation heat exchanger are fin tube heat exchangers, the main circulation heat exchanger 7 on the left is a fin tube heat exchanger, the main circulation heat exchanger 7 on the right is a shell-and-tube heat exchanger, in this embodiment, all fin tube heat exchangers are arranged in the same volume device, a second auxiliary circulation system is added, the second auxiliary circulation system comprises a second auxiliary compressor 13, a second auxiliary circulation valve 14, a second auxiliary circulation heat exchanger 15 and a second auxiliary refrigerant circulation throttling device 16, the second auxiliary compressor 13 is communicated with the second auxiliary circulation heat exchanger 15 through a plurality of second auxiliary circulation valves 14 which are circumferentially connected in parallel, the second auxiliary refrigerant circulation throttling device 16 is connected between the second auxiliary circulation heat exchangers 15, and the second auxiliary circulation heat exchanger 15 is connected in series with the first auxiliary circulation heat exchanger 11.
The working principle of the present embodiment is substantially the same as that of embodiment 3, except that a second auxiliary circulation system is added to cooperate with the first auxiliary circulation system, the opening and closing direction of the second auxiliary circulation valve 14 is the same as that of the first auxiliary circulation valve 10 in the first auxiliary circulation system, and the working principle of the second auxiliary circulation system is parallel and the same as that of the first auxiliary circulation system. This embodiment is more suitable for heating under the extreme low temperature environment, also can carry out the utmost point deep refrigeration, make heat transfer medium fluid altogether can carry out the cubic and heat up, only cool down twice (except that outside heat transfer device 2 is to the outside air heat extraction cooling), this is also that the order realizes two cold quantities to feed back to main circulation heat exchanger 7 on the left side on different heat transfer nodes around utilizing heat transfer medium fluid altogether, make main circulation heat exchanger 7 temperature on the left side become lower, so the main circulation heat exchanger 7 temperature on the right side can be lower, can make cold medium fluid obtain lower cold source and be used for the freezer, or be used for liquefied hydrogen, state in return can make heat transfer medium fluid temperature altogether become higher than the outside air after refrigerant release latent heat respectively, this is favorable to the system to the outside air heat extraction.
The invention forms a non-refrigerant side loop by communicating the main circulating system and the first auxiliary circulating system, the output end of the first auxiliary circulating system is communicated with the input end of an external heat exchange device 2 through a heat exchange circulating pump 1, the output end of the external heat exchange device 2 is communicated with the first auxiliary circulating system, and the output end of the main circulating system is communicated with a user terminal 4 through a terminal circulating pump 3.
The above-mentioned embodiments are only preferred embodiments of the present invention, and the scope of the present invention is not limited thereto, and therefore, modifications, equivalent changes, improvements, etc. made in the claims of the present invention are still included in the scope of the present invention.
Claims (9)
1. A system of multi-inverse Carnot cycle cross heat exchange medium is characterized in that: including main circulation system, first auxiliary circulation system, heat transfer circulating pump (1), outside heat transfer device (2), terminal circulating pump (3) and user terminal (4), main circulation system and the non-refrigerant side intercommunication of first auxiliary circulation system form the return circuit, the input intercommunication of heat transfer circulating pump (1) and outside heat transfer device (2) is passed through to first auxiliary circulation system's output, the output of outside heat transfer device (2) with first auxiliary circulation system intercommunication, main circulation system's output passes through terminal circulating pump (3) and communicates with user terminal (4).
2. The system of multiple reverse carnot cycle cross recuperating media of claim 1, wherein: the main circulating system comprises a main compressor (5), a main circulating valve (6), main circulating heat exchangers (7) and a main refrigerant circulating throttling device (8), wherein the main compressor (5) is respectively communicated with the two main circulating heat exchangers (7) through the main circulating valve (6) to form a refrigerant loop, the main refrigerant circulating throttling device (8) is arranged between the main circulating heat exchangers (7), one main circulating heat exchanger (7) is communicated with the non-refrigerant side of the first auxiliary circulating system, and the other main circulating heat exchanger (7) is communicated with a user terminal (4) through a terminal circulating pump (3).
3. The system of multiple reverse carnot cycle cross-recuperating media of claim 2, wherein: the first auxiliary circulating system comprises a first auxiliary compressor (9), a first auxiliary circulating valve (10), first auxiliary circulating heat exchangers (11) and first auxiliary refrigerant circulating throttling devices (12), wherein the first auxiliary compressor (9) is respectively communicated with the two first auxiliary circulating heat exchangers (11) through the first auxiliary circulating valve (10) to form a loop, the first auxiliary circulating heat exchangers (11) are connected with one main circulating heat exchanger (7) in series to form a non-refrigerant side loop, the first auxiliary circulating heat exchangers (11) are further communicated with one other auxiliary refrigerant circulating throttling device (12), one first auxiliary circulating heat exchanger (11) is communicated with the external heat exchange device (2) through a pipeline, and the other first auxiliary circulating heat exchanger (11) is communicated with the external heat exchange device (2) through the circulating pump (1) to form a non-refrigerant side loop.
4. The system of multiple reverse carnot cycle cross recuperating media of claim 3, wherein: the external heat exchange device (2) is one of a finned tube heat exchanger, a closed heat exchange tower or an open air heat exchange tower.
5. The system of multiple reverse carnot cycle cross-recuperating media of claim 4, wherein: the main circulation heat exchanger (7) is one or the combination of two of a double-pipe heat exchanger, a shell-and-tube heat exchanger and a finned tube heat exchanger.
6. The system of multiple reverse carnot cycle cross recuperating media of claim 5, wherein: the first auxiliary circulating heat exchanger (11) is one or the combination of two of a double-pipe heat exchanger, a shell-and-tube heat exchanger and a finned tube heat exchanger.
7. The system of multiple reverse carnot cycle cross recuperating media of claim 6, wherein: the main circulating valve (6) is an electric four-way valve or four parallel electric angle valves.
8. The system of multiple reverse carnot cycle cross recuperating media of claim 3, wherein: the first auxiliary circulating valve (10) is an electric four-way valve or four parallel electric angle valves.
9. The system of multiple reverse carnot cycle cross recuperating media of claim 3, wherein: the secondary refrigerant circulation system is characterized by further comprising a second auxiliary circulation system, wherein the second auxiliary circulation system comprises a second auxiliary compressor (13), a second auxiliary circulation valve (14), a second auxiliary circulation heat exchanger (15) and a second auxiliary refrigerant circulation throttling device (16), the second auxiliary compressor (13) is communicated with the second auxiliary circulation heat exchanger (15) through a plurality of second auxiliary circulation valves (14) which are circumferentially connected in parallel, the second auxiliary refrigerant circulation throttling device (16) is connected between the second auxiliary circulation heat exchangers (15), and the second auxiliary circulation heat exchanger (15) is connected with the first auxiliary circulation heat exchanger (11) in series.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211083641.9A CN115574480A (en) | 2022-09-06 | 2022-09-06 | System for many contrary carnot circulation are alternately heat transfer medium altogether |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211083641.9A CN115574480A (en) | 2022-09-06 | 2022-09-06 | System for many contrary carnot circulation are alternately heat transfer medium altogether |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116592536A (en) * | 2023-06-09 | 2023-08-15 | 森创中汇(北京)热电科技有限公司 | Dual-cycle refrigerating and heating system |
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2022
- 2022-09-06 CN CN202211083641.9A patent/CN115574480A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116592536A (en) * | 2023-06-09 | 2023-08-15 | 森创中汇(北京)热电科技有限公司 | Dual-cycle refrigerating and heating system |
| CN116592536B (en) * | 2023-06-09 | 2024-09-20 | 森创中汇(北京)热电科技有限公司 | Dual-cycle refrigerating and heating system |
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