CN215765836U - Multistage injection type heat pump system - Google Patents
Multistage injection type heat pump system Download PDFInfo
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- CN215765836U CN215765836U CN202121891518.0U CN202121891518U CN215765836U CN 215765836 U CN215765836 U CN 215765836U CN 202121891518 U CN202121891518 U CN 202121891518U CN 215765836 U CN215765836 U CN 215765836U
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Abstract
The utility model provides a multi-stage injection type heat pump system which comprises a first compressor, a second compressor, a condenser, a heat exchanger, a first evaporator, a second evaporator, a first ejector, a second ejector, a throttling element and a working medium filled in the system. The utility model solves the problem that the heat pump system with single-stage injection has limited capacity of reducing the work consumption of the system. According to the utility model, two-stage injection is formed by adopting the first injector and the second injector, so that the expansion work of the throttling element can be recovered to a greater extent, and the consumed work in the compression process is saved, thereby reducing the energy consumption of a circulating system and improving the efficiency of a heat pump system.
Description
Technical Field
The utility model relates to the technical field of heat pump energy conservation, in particular to a multi-stage injection type heat pump system.
Background
The heat pump cycle generally consists of four major thermodynamic processes, compression, condensation, throttling, and evaporation. Non-azeotropic working media are adopted in circulation, so that the temperature slippage can be utilized, the average heat exchange temperature difference is reduced, and the irreversible loss of the system can be effectively reduced. However, in some cases, due to the fact that the components of the non-azeotropic working medium are fixed and the temperature slippage is not changed, the temperature slippage cannot be adjusted to be matched with the heat exchange temperature change, the heat transfer effect is reduced, and the irreversible loss is increased; meanwhile, in the condensation process, the liquid phase working medium is continuously separated out, the thickness of a liquid film is continuously increased, the heat transfer resistance is increased, the heat transfer performance is reduced, and in the evaporation process, the heat transfer coefficient of the working medium is increased and then reduced along with the evaporation process, so that a peak value exists. Therefore, how to enhance the heat transfer efficiency of the cycle, reduce the irreversible loss of the heat transfer process, and reduce the energy loss of the cycle process is the main direction of research by those skilled in the art.
Chinese patent publication No. CN 110296543 a discloses a refrigeration or heat pump system with a function of gas-liquid separation and heat exchange for injection, which adopts a non-azeotropic mixed working medium, and simultaneously utilizes a liquid extraction pipe and an air extraction pipe to extract a saturated working medium, so as to adjust the components of the working medium in the thermodynamic cycle; the saturated liquid phase working medium is extracted through the condenser, so that the dryness of the residual working medium in the condenser is improved; pumping out saturated gas-phase working medium through the evaporator to reduce the dryness of the residual working medium in the evaporator; in addition, the saturated gas-phase working medium in the evaporator is injected by the ejector, so that the gas supplement amount of the middle stage of the compressor is increased, and the problem of heat production attenuation of an air source refrigeration or heat pump system at low ambient temperature is further effectively solved.
However, the above solutions still have some problems, and the expansion work that can be recovered by using the one-stage injection is limited, so that with the continuous increase of user demand, the energy-saving efficiency of the circulation system of the single-stage injection cannot meet the practical use demand, and an improvement scheme with more energy-saving, economical, environmental protection and high efficiency is required.
SUMMERY OF THE UTILITY MODEL
The utility model aims to overcome the defect that the single-stage injection heat pump system in the prior art is limited in the capacity of reducing the consumed work of the system, and provides a multi-stage injection heat pump system. The utility model can not only recover expansion work, but also save compression work, and compared with primary injection, the utility model further reduces the power consumption of the system and improves the operation efficiency of the system.
In order to solve the technical problems, the utility model adopts the technical scheme that:
a multi-stage injection type heat pump system comprises a second compressor, a condenser with an inlet connected with an outlet of the second compressor, wherein an outlet of the condenser is divided into two paths, the first path is connected with an injection inlet of a first injector, and the second path is connected with a cooling inlet of a heat exchanger; one end of the throttling element is connected with a cooling outlet of the heat exchanger, the inlet of a first evaporator at the other end of the throttling element is connected, the outlet of the first evaporator is divided into three paths, the first path is connected with an injected working medium inlet of a first ejector, the second path is connected with an injected working medium inlet of a second ejector, the third path is connected with an inlet of a first compressor, and the outlet of the first compressor is connected with the inlet of the second compressor; the mixing outlet of the first ejector is connected with the heating inlet of the heat exchanger, the heating outlet of the heat exchanger is connected with the injection inlet of the second ejector, the mixing outlet of the second ejector is connected with the inlet of the second evaporator, and the outlet of the second evaporator is also connected with the inlet of the second compressor; the system also comprises a working medium filled in the system.
Therefore, double-stage injection is formed by adopting the first ejector and the second ejector, the expansion work of the throttling element can be recovered to a greater extent, and the consumed work in the compression process is saved, so that the energy consumption of a circulating system is reduced, and the efficiency of a heat pump system is improved; meanwhile, two-stage injection is utilized to realize two-stage compression intercooling, and the problem that the heating capacity of the air source heat pump system is reduced at a lower ambient temperature is effectively solved.
Furthermore, the working medium is a non-azeotropic mixed working medium.
Therefore, by adopting the non-azeotropic mixed working medium, as the components of the non-azeotropic working medium are fixed, the non-azeotropic mixed working medium has the characteristic of temperature slippage, compared with a single working medium, the heat exchange temperature difference can be reduced, the irreversibility in the heat exchange process is reduced, the operation efficiency is improved, the non-reversibility of the system can be reduced when the non-azeotropic mixed working medium is applied to a heat pump system, the temperature slippage characteristic of the non-azeotropic mixed working medium is reasonably utilized, and the components of the non-azeotropic mixed working medium can be regulated and controlled by combining different heat exchange units to adjust the heat transfer coefficient of the non-azeotropic mixed working medium.
Further, the condenser is for dividing the liquid condenser, divides the liquid condenser to include the condensation header, locates the condensation heat exchange tube in the condensation header inner chamber to and connect being used for of condensation heat exchange tube and condensation header inner chamber wall with the first baffle of condenser side detached, set up the first baffle of next-door neighbour on the condensation header and be located the branch liquid export of first baffle top, divide the liquid export and draw with first sprayer and penetrate the entry linkage.
It should be noted that, in the liquid separation condensation process, a gas-phase working medium can be condensed out of a condensed saturated liquid-phase working medium after entering a condenser, accumulation of the liquid-phase working medium can prevent the gas-phase working medium from carrying out heat exchange, the heat transfer coefficient is reduced, liquid separation condensation separates a certain amount of condensed saturated liquid-phase working medium which is condensed, the dryness of the working medium is increased, the heat transfer coefficient is improved, the heat exchange capacity is improved accordingly, in addition, the components of the residual working medium in the condenser are changed, and the purpose of component regulation and control is achieved.
Furthermore, a plurality of first liquid separation holes penetrating through the first partition plate are formed in the first partition plate.
When the first partition plate is arranged, the surface of one side close to the liquid separation outlet can be provided with a certain gradient, so that condensate can be conveniently discharged into the liquid separation outlet; meanwhile, the working medium components and the flow of the condensed liquid separation outlet can be regulated and controlled by reasonably regulating the size and the number of the liquid separation holes on the first partition plate and the caliber of the liquid separation outlet, so that the components of the residual working medium in the liquid separation condenser are changed, the thermophysical property parameters of the residual working medium are changed, and the temperature slippage of the residual working medium is regulated and controlled.
Further, first evaporimeter is the phase separation evaporimeter, the phase separation evaporimeter includes the evaporation header, locate the evaporation heat exchange tube in the evaporation header inner chamber, the setting is used for being close to evaporation entry one end with the detached second baffle of evaporation tube side, and set up and be close to evaporation export one end and be used for the detached third baffle of evaporation tube side, set up the liquid phase export that is close to the second baffle and is located the second baffle top on the evaporation header, still set up the gaseous phase export that is close to the third baffle and is located the third baffle below on the evaporation header, the liquid phase export is connected with being drawn of second sprayer and is penetrated working medium entry, gaseous phase export is connected with being drawn of first sprayer and is penetrated working medium entry.
When the second partition plate is arranged, the surface of one side close to the liquid separation outlet can be provided with a certain gradient, so that the liquid-phase working medium which is not completely evaporated can be conveniently discharged from the liquid-phase outlet; meanwhile, in the split-phase evaporation process, a gas-liquid two-phase working medium enters the evaporator, the dryness of the working medium is gradually increased along with the evaporation process, the heat transfer coefficient of the working medium is increased and then decreased, the split-phase evaporation is carried out at the evaporation starting end, a certain amount of incompletely evaporated liquid-phase working medium is separated, the dryness of the working medium is increased, the heat transfer coefficient can be improved, a certain amount of gas-phase working medium is separated at the evaporation tail end, the dryness of the working medium is decreased, the working medium is evaporated under a higher heat transfer coefficient, the heat transfer efficiency is improved, the components of the residual working medium in the evaporator are changed, and the purpose of component regulation is also achieved.
Furthermore, a plurality of second liquid separation holes penetrating through the second partition plate are formed in the second partition plate.
It should be noted that, by reasonably designing the size and number of the liquid separating holes on the second partition plate, the caliber of the liquid phase outlet and the caliber of the gas phase outlet, the working medium components and flow rates of the evaporation liquid phase outlet and the evaporation gas phase outlet can be adjusted, so that the components of the residual working medium in the first evaporator are changed, the thermophysical property parameters of the residual working medium are changed, and the temperature slippage of the residual working medium is regulated.
Therefore, by simultaneously utilizing liquid separation condensation and split-phase evaporation, the regulation and control of the dryness of the working medium in the thermodynamic cycle system are realized, so that the heat transfer coefficient of the working medium is improved, and the heat exchange capacity of the condenser and the first evaporator is enhanced.
Furthermore, a first regulating valve is connected between the condenser and an injection inlet of the first injector, a second regulating valve is connected between the first evaporator and an injected working medium inlet of the first injector, and a third regulating valve is connected between the first evaporator and an injected working medium inlet of the second injector.
Therefore, the opening of the regulating valve is changed, the regulating valve realizes the regulation and control of the change of the working medium components in the thermodynamic cycle system by regulating the flow of the working medium of the pipeline, the thermophysical property parameters of the working medium can be changed, the temperature slippage of the working medium is regulated, the average heat exchange temperature difference between the heat exchange unit and a cold and heat source is reduced, and the irreversibility of the system in the heat exchange process is reduced; meanwhile, the component regulation and control can change the temperature slippage degree, can better adapt to the heat exchange process under different working conditions, and further reduces the system
Loss and improved heat exchange capacity.
Further, the throttling element is a throttle valve. It should be noted that the throttling element plays a role in reducing pressure and converting the liquid-phase working medium into a gas-liquid two-phase working medium, and is one of the important parts of the cycle.
Furthermore, the working medium pressure of the liquid outlet of the condenser is greater than the working medium pressure of the gas outlet of the first evaporator. Therefore, the working medium at the gas phase outlet of the first evaporator is injected by the working medium at the liquid separating outlet of the condenser.
Furthermore, the working medium pressure of the heating outlet of the heat exchanger is greater than the working medium pressure of the liquid phase outlet of the first evaporator. Therefore, the working medium at the liquid phase outlet of the first evaporator is injected by the working medium at the heating outlet of the heat exchanger.
Compared with the prior art, the utility model has the beneficial effects that:
the utility model adopts the first ejector and the second ejector to form two-stage ejection, can recover the expansion work of the throttle valve to a greater extent and save the consumed work in the compression process, further reduces the consumed work of the system compared with the one-stage ejection, and improves the operation efficiency of the system so as to reduce the energy consumption of a circulating system and improve the efficiency of a heat pump system.
Drawings
FIG. 1 is a schematic diagram of a system connection structure according to the present embodiment;
FIG. 2 is a schematic flow diagram of the working medium of the liquid separation condenser in this embodiment;
FIG. 3 is a schematic structural diagram of a liquid separating outlet of the liquid separating condenser in this embodiment;
FIG. 4 is a schematic flow diagram of the working medium of the split-phase evaporator in the present embodiment;
FIG. 5 is a schematic view of the liquid phase outlet of the phase separation evaporator in this embodiment;
FIG. 6 is a schematic view of the gas phase outlet of the phase separation evaporator in this embodiment.
The graphic symbols are illustrated as follows:
101-a first compressor, 102-a second compressor, 103-a condenser, 1031-a condensing heat exchange tube, 1032 a condensing header, 1034-a first partition, 1035-a first liquid separation hole, 104-a heat exchanger, 105-a throttling element, 106-a first evaporator, 1061-an evaporating heat exchange tube, 1062-a steam header, 1064-a second partition, 1065-a second liquid separation hole, 1067-a third partition, 107-a first regulating valve, 108-a first injector, 109-a second injector, 110-a second evaporator, 111-a second regulating valve, 112-a third regulating valve;
1-evaporation gas phase working medium, 2-superheated steam, 4-high temperature and high pressure superheated working medium, 5-condensation saturated liquid phase working medium, 8-condensation liquid phase working medium, 10-gas-liquid two phase working medium under the second-stage pressure, 11-gas phase working medium, 13-gas-liquid two phase working medium under the first-stage pressure, 14-saturated gas, 15-saturated gas phase working medium, and 16-incompletely evaporated liquid phase working medium.
Detailed Description
The present invention will be further described with reference to the following embodiments. Wherein the showings are for the purpose of illustration only and are shown by way of illustration only and not in actual form, and are not to be construed as limiting the present patent; to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
The same or similar reference numerals in the drawings of the embodiments of the present invention correspond to the same or similar components; in the description of the present invention, it should be understood that if there is an orientation or positional relationship indicated by the terms "upper", "lower", "left", "right", etc. based on the orientation or positional relationship shown in the drawings, it is only for convenience of describing the present invention and simplifying the description, but it is not intended to indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and therefore, the terms describing the positional relationship in the drawings are only used for illustrative purposes and are not to be construed as limiting the present patent, and the specific meaning of the terms may be understood by those skilled in the art according to specific circumstances.
Examples
As shown in fig. 1 to 6, a multi-stage injection heat pump system includes a second compressor 102, a condenser 103 having an inlet connected to an outlet of the second compressor 102, an outlet of the condenser 103 being divided into two paths, a first path being connected to an injection inlet of a first injector 108, and a second path being connected to a cooling inlet of a heat exchanger 104; one end of the throttling element 105 is connected with a cooling outlet of the heat exchanger 104, the inlet of the first evaporator 106 at the other end of the throttling element 105 is connected, the outlet of the first evaporator 106 is divided into three paths, the first path is connected with an injected working medium inlet of the first ejector 108, the second path is connected with an injected working medium inlet of the second ejector 109, the third path is connected with an inlet of the first compressor 101, and the outlet of the first compressor 101 is connected with an inlet of the second compressor 102; the mixing outlet of the first ejector 108 is connected with the heating inlet of the heat exchanger 104, the heating outlet of the heat exchanger 104 is connected with the injection inlet of the second ejector 109, the mixing outlet of the second ejector 109 is connected with the inlet of a second evaporator 110, and the outlet of the second evaporator 110 is also connected with the inlet of the second compressor 102; the system also comprises a working medium filled in the system.
In this way, by adopting the first ejector 108 and the second ejector 109 to form two-stage ejection, the expansion work of the throttling element can be recovered to a greater extent, and the consumed work in the compression process can be saved, so that the energy consumption of the circulating system is reduced, and the efficiency of the heat pump system is improved; meanwhile, two-stage injection is utilized to realize two-stage compression intercooling, and the problem that the heating capacity of the air source heat pump system is reduced at a lower ambient temperature is effectively solved.
In this embodiment, the working medium is a non-azeotropic mixture working medium.
Therefore, by adopting the non-azeotropic mixed working medium, as the components of the non-azeotropic working medium are fixed, the non-azeotropic mixed working medium has the characteristic of temperature slippage, compared with a single working medium, the heat exchange temperature difference can be reduced, the irreversibility in the heat exchange process is reduced, the operation efficiency is improved, the non-reversibility of the system can be reduced when the non-azeotropic mixed working medium is applied to a heat pump system, the temperature slippage characteristic of the non-azeotropic mixed working medium is reasonably utilized, and the components of the non-azeotropic mixed working medium can be regulated and controlled by combining different heat exchange units to adjust the heat transfer coefficient of the non-azeotropic mixed working medium.
As shown in fig. 2 and fig. 3, the condenser 103 is a liquid separating condenser, the liquid separating condenser includes a condensation header 1032, a condensation heat exchange pipe 1031 disposed in an inner cavity of the condensation header 1032, and a first partition 1034 connecting the condensation heat exchange pipe 1031 and an inner cavity wall of the condensation header 1032 and used for separating a tube pass of the condensation header, a liquid separating outlet adjacent to the first partition 1034 and located above the first partition 1034 is opened on the condensation header 1032, and the liquid separating outlet is connected with an injection inlet of the first injector 108.
It should be noted that, in the liquid separation condensation process, a gas-phase working medium can be condensed out of a condensed saturated liquid-phase working medium after entering the condenser 103, accumulation of the liquid-phase working medium can hinder the gas-phase working medium from carrying out heat exchange, the heat transfer coefficient is reduced, liquid separation condensation separates a certain amount of condensed saturated liquid-phase working medium which is condensed, the dryness of the working medium is increased, the heat transfer coefficient is improved, the heat exchange capacity is improved accordingly, in addition, the components of the residual working medium in the condenser 103 are changed, and the purpose of component regulation and control is achieved.
In this embodiment, the first partition 1034 has a plurality of first liquid dividing holes 1035 penetrating through the first partition; a certain gradient is arranged on the surface of one side, close to the liquid separation outlet, of the first partition plate 1034, so that condensate can be conveniently discharged into the liquid separation outlet;
meanwhile, the size and quantity of the liquid separating holes 1035 on the first partition plate 1034 and the caliber of the liquid separating outlet can be reasonably adjusted to regulate and control the working medium components and the flow of the condensed liquid separating outlet, so that the components of the residual working medium in the liquid separating condenser are changed, the thermophysical property parameters of the residual working medium are changed, and the temperature slippage of the residual working medium is regulated and controlled.
As shown in fig. 4 to 6, the first evaporator 106 is a phase separation evaporator, and the phase separation evaporator includes an evaporation header 1062, an evaporation heat exchange tube 1061 disposed in an inner cavity of the evaporation header 1062, a second partition 1064 disposed at an end close to an evaporation inlet for separating the evaporation tube, and a third partition 1067 disposed at an end close to an evaporation outlet for separating the evaporation tube, a liquid phase outlet disposed adjacent to the second partition 1064 and above the second partition 1064 is opened on the evaporation header 1062, a gas phase outlet disposed adjacent to the third partition 1067 and below the third partition 1067 is further opened on the evaporation header 1062, the liquid phase outlet is connected to an injected working medium inlet of the second injector 109, and the gas phase outlet is connected to an injected working medium inlet of the first injector 108.
It should be noted that, for the split-phase evaporation process, the gas-liquid two-phase working medium enters the evaporator, the dryness of the working medium gradually increases along with the proceeding of the evaporation process, the heat transfer coefficient of the working medium increases first and then decreases, the split-phase evaporation is at the evaporation starting end, the dryness of the working medium increases by separating a certain amount of liquid-phase working medium which is not completely evaporated, the heat transfer coefficient can be improved, and at the evaporation end, a certain amount of gas-phase working medium is separated, the dryness of the working medium is decreased, the working medium is evaporated under the condition of maintaining a higher heat transfer coefficient, the heat transfer efficiency is improved, besides, the components of the residual working medium in the evaporator are changed, and the purpose of component regulation and control is also realized.
In this embodiment, the second partition 1064 is provided with a plurality of second liquid dividing holes 1065 penetrating through the second partition 1064; the surface of one side of the second partition 1064 close to the liquid phase outlet may be provided with a certain slope, so that the liquid phase working medium which is not completely evaporated can be conveniently discharged from the liquid phase outlet.
It should be noted that, by reasonably designing the size and number of the liquid separating holes 1065 on the second 1064 partition plate, the aperture of the liquid phase outlet and the aperture of the gas phase outlet, the working medium components and flow rates of the evaporated liquid phase outlet and the evaporated gas phase outlet can be adjusted, so that the components of the remaining working medium in the first evaporator 106 are changed, the thermophysical property parameters of the working medium are changed, and the temperature slippage of the working medium is regulated.
Therefore, by simultaneously utilizing liquid separation condensation and split-phase evaporation, the regulation and control of the dryness of the working medium in the thermodynamic cycle system are realized, so that the heat transfer coefficient of the working medium is improved, and the heat exchange capacity of the condenser and the first evaporator is enhanced.
As shown in fig. 1, a first regulating valve 107 is further connected between the condenser 103 and the injection inlet of the first injector 108, a second regulating valve 111 is further connected between the first evaporator 106 and the injected working medium inlet of the first injector 108, and a third regulating valve 112 is further connected between the first evaporator 108 and the injected working medium inlet of the second injector 109.
Therefore, the opening of the regulating valve is changed, the regulating valve realizes the regulation and control of the change of the working medium components in the thermodynamic cycle system by regulating the flow of the working medium of the pipeline, the thermophysical property parameters of the working medium can be changed, the temperature slippage of the working medium is regulated, the average heat exchange temperature difference between the heat exchange unit and a cold and heat source is reduced, and the irreversibility of the system in the heat exchange process is reduced; meanwhile, the component regulation and control can change the temperature slippage degree, can better adapt to the heat exchange process under different working conditions, and further reduces the system
Loss and improved heat exchange capacity.
In this embodiment, the throttling element 105 is a throttle valve. Therefore, the throttle valve can reduce the pressure at the cooling outlet end of the heat exchanger and convert the liquid-phase working medium into a gas-liquid two-phase working medium, and is one of the important parts of the circulation process of the embodiment.
In this embodiment, the working medium pressure at the liquid outlet of the condenser 103 is greater than the working medium pressure at the gas outlet of the first evaporator 106. Therefore, the working medium at the gas phase outlet of the first evaporator is injected by the working medium at the liquid separating outlet of the condenser.
In this embodiment, the pressure of the working medium at the heating outlet of the heat exchanger 104 is greater than the pressure of the working medium at the liquid phase outlet of the first evaporator 106. Therefore, the working medium at the liquid phase outlet of the first evaporator is injected by the working medium at the heating outlet of the heat exchanger.
The working principle of the embodiment is as follows:
the working medium is compressed by the second compressor 102 to form a high-temperature high-pressure superheated working medium 4, the high-temperature high-pressure superheated working medium 4 enters the inlet of the condenser 103 from the outlet of the second compressor 102, the high-temperature high-pressure superheated working medium 4 is partially condensed by the condenser 103, the condensed liquid-phase working medium 8 which is condensed enters the injection inlet of the first ejector 108 from the liquid separation outlet of the condenser 103 through the first regulating valve 107, the residual working medium in the condenser 103 is continuously condensed to form a condensed saturated liquid-phase working medium 5, the condensed saturated liquid-phase working medium 5 enters the cooling inlet of the heat exchanger 104, and the condensed saturated liquid-phase working medium 5 enters the first evaporator 106 after being cooled by the heat exchanger 104 and being throttled by the throttling element 105;
through the evaporation of the first evaporator 106, a part of the working medium forms a saturated gas-phase working medium 15, the saturated gas-phase working medium passes through the second regulating valve 111 from a gas-phase outlet and enters the injected inlet of the first ejector 108, a part of the liquid-phase working medium 16 which forms incomplete evaporation passes through the liquid-phase outlet and enters the injected inlet of the second ejector 109 through the second regulating valve 112, the rest of the working medium in the first evaporator 106 forms an evaporated gas-phase working medium 1, the evaporated gas-phase working medium enters the first compressor 1 for compression, and superheated steam 2 is formed at the outlet of the first compressor 1;
the condensed liquid-phase working medium 8 which is condensed is mixed with a saturated gas-phase working medium 15 from a gas-phase outlet of a first evaporator 106 in a first ejector 108, the mixture is changed into a gas-liquid two-phase working medium 10 under a second-stage pressure at an outlet of the first ejector 108, the gas-liquid two-phase working medium 10 enters a heating inlet of a heat exchanger 104, the gas-phase working medium 11 is formed after being heated by the heat exchanger 104, the gas-phase working medium 11 enters an injection inlet of a second ejector 109, the gas-phase working medium 11 is mixed with a liquid-phase working medium 16 which is not completely evaporated and is separated from a liquid outlet of the first evaporator 106 in the second ejector 109, the mixture is changed into a gas-liquid two-phase working medium 13 under a first-stage pressure at an outlet of the second ejector 109, the gas-liquid two-phase working medium 13 under the first-stage pressure enters a second evaporator 110 to be evaporated to form saturated gas 14, the saturated gas 14 is mixed with superheated steam 2 at an outlet of the first compressor 101 and then enters an inlet of the second compressor 102, the whole circulation process is completed.
In this embodiment, the high-efficiency heat pump system has four different working pressures in the cycle operation process, which are the condensing pressure, the secondary pressure, the primary pressure, and the evaporating pressure in this order. For the first ejector, the condensed liquid-phase working medium 8 which is condensed under the condensing pressure ejects the saturated gas-phase working medium 15 under the evaporating pressure of the first evaporator to form a gas-liquid two-phase working medium 10 under the secondary pressure; for the second ejector, the gas-phase working medium 11 under the secondary pressure ejects the liquid-phase working medium 16 which is not completely evaporated under the evaporation pressure of the first evaporator to form a gas-liquid two-phase working medium 13 under the primary pressure; the condensing pressure and the evaporating pressure are determined by the operation conditions of the circulating system, namely a condensing temperature and an evaporating temperature, and the heating temperature requirement and the air environment temperature condition need to be considered during actual operation.
In this embodiment, the heat exchanger 104 has four inlets and outlets, which are respectively a cooling inlet, a cooling outlet, a heating inlet, and a heating outlet. Wherein the condensed saturated liquid-phase working medium 5 from the condensation outlet of the condenser 103 flows in through the cooling inlet of the heat exchanger 104, and flows out from the cooling outlet of the heat exchanger 104, the gas-liquid two-phase working medium 10 under the secondary pressure of the mixing outlet of the first ejector 108 flows in from the heating inlet of the heat exchanger 104 and flows out from the heating outlet of the heat exchanger 104, the two working media carry out heat exchange in the heat exchanger 104, the condenser 103 enters the condensed saturated liquid-phase working medium 5 in the heat exchanger 104 for supercooling, meanwhile, the gas-liquid two-phase working medium 10 at the second-stage pressure of the mixed outlet of the first ejector 108 is converted from gas-liquid two-phase to gas-phase, and the incompletely evaporated liquid-phase working medium 16 at the liquid-phase outlet of the first evaporator 106 is ejected, so that the flow of the second evaporator 110 is increased, two-stage compression intercooling is realized, the temperature of the outlet of the first compressor 101 can be effectively reduced, and the overall operation efficiency of the system is improved.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
1. The multi-stage injection type heat pump system is characterized by comprising a second compressor (102), wherein the inlet of the second compressor (102) is connected with a condenser (103) at the outlet of the second compressor (102), the outlet of the condenser (103) is divided into two paths, the first path is connected with an injection inlet of a first injector (108), and the second path is connected with a cooling inlet of a heat exchanger (104);
one end of the throttling element (105) is connected with a cooling outlet of the heat exchanger (104), the inlet of a first evaporator (106) connected with the other end of the throttling element (105) is divided into three paths, the first path is connected with an injected working medium inlet of a first ejector (108), the second path is connected with an injected working medium inlet of a second ejector (109), the third path is connected with an inlet of a first compressor (101), and an outlet of the first compressor (101) is connected with an inlet of the second compressor;
the mixing outlet of the first ejector (108) is connected with the heating inlet of the heat exchanger (104), the heating outlet of the heat exchanger (104) is connected with the injection inlet of the second ejector (109), the mixing outlet of the second ejector (109) is connected with the inlet of a second evaporator (110), and the outlet of the second evaporator (110) is also connected with the inlet of the second compressor (102);
the system also comprises a working medium filled in the system.
2. The multi-stage ejector heat pump system of claim 1, wherein the working fluid is a non-azeotropic mixture.
3. The multi-stage injection heat pump system according to claim 2, wherein the condenser (103) is a liquid separation condenser, the liquid separation condenser comprises a condensation header (1032), a condensation heat exchange pipe (1031) arranged in an inner cavity of the condensation header (1032), and a first partition plate (1034) connecting the condensation heat exchange pipe (1031) with the inner cavity wall of the condensation header (1032) and used for separating a condensation pipe pass, a liquid separation outlet which is close to the first partition plate (1034) and located above the first partition plate (1034) is opened on the condensation header (1032), and the liquid separation outlet is connected with an injection inlet of the first injector (108).
4. The multiple-injection heat pump system of claim 3, wherein the first partition (1034) has a plurality of first liquid-separating holes (1035) formed therethrough.
5. The multi-injection heat pump system of claim 3, wherein the first evaporator (106) is a phase separation evaporator, the phase separation evaporator comprises an evaporation header (1062), evaporation heat exchange tubes (1061) arranged in the inner cavity of the evaporation header (1062), a second partition plate (1064) arranged at one end close to the evaporation inlet for separating the evaporation tube passes, and a third partition plate (1067) arranged at one end close to the evaporation outlet for separating the evaporation tube passes, a liquid phase outlet arranged above the second partition plate (1064) and adjacent to the second partition plate (1064) is opened on the evaporation header (1062), a gas phase outlet arranged below the third partition plate (1067) and adjacent to the third partition plate (1067) is opened on the evaporation header (1062), and the liquid phase outlet is connected with an injected working medium inlet of the second ejector (109), the gas phase outlet is connected with an injected working medium inlet of the first injector (108).
6. The heat pump system of claim 5, wherein the second partition (1064) is provided with a plurality of second liquid dividing holes (1065) penetrating through the second partition (1064).
7. The multi-stage injection heat pump system according to claim 5, wherein a first regulating valve (107) is further connected between the condenser (103) and the injection inlet of the first injector (108), a second regulating valve (111) is further connected between the first evaporator (106) and the injected working medium inlet of the first injector (108), and a third regulating valve (112) is further connected between the first evaporator (108) and the injected working medium inlet of the second injector (109).
8. The multiple injection heat pump system of claim 1, wherein the throttling element (105) is a throttle valve.
9. The multi-stage ejector heat pump system of claim 1, wherein the pressure of the working fluid at the liquid outlet of the condenser (103) is greater than the pressure of the working fluid at the vapor outlet of the first evaporator (106).
10. The multiple-injection heat pump system of claim 1, wherein the pressure of the working fluid at the heat outlet of the heat exchanger (104) is greater than the pressure of the working fluid at the liquid outlet of the first evaporator (106).
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| CN202121891518.0U CN215765836U (en) | 2021-08-12 | 2021-08-12 | Multistage injection type heat pump system |
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| CN202121891518.0U CN215765836U (en) | 2021-08-12 | 2021-08-12 | Multistage injection type heat pump system |
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