CN105444476A - Heat exchange system - Google Patents
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- CN105444476A CN105444476A CN201511030770.1A CN201511030770A CN105444476A CN 105444476 A CN105444476 A CN 105444476A CN 201511030770 A CN201511030770 A CN 201511030770A CN 105444476 A CN105444476 A CN 105444476A
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- 230000001502 supplementing effect Effects 0.000 claims abstract description 14
- 238000004891 communication Methods 0.000 claims abstract description 4
- 238000001704 evaporation Methods 0.000 claims description 64
- 230000008020 evaporation Effects 0.000 claims description 61
- 206010008469 Chest discomfort Diseases 0.000 claims description 16
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 4
- 239000012530 fluid Substances 0.000 claims description 3
- 230000004087 circulation Effects 0.000 abstract description 10
- 239000003507 refrigerant Substances 0.000 description 39
- 239000007788 liquid Substances 0.000 description 17
- 238000007906 compression Methods 0.000 description 15
- 230000006835 compression Effects 0.000 description 14
- 238000012546 transfer Methods 0.000 description 14
- 238000010438 heat treatment Methods 0.000 description 13
- 239000012071 phase Substances 0.000 description 8
- 238000010586 diagram Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 7
- 230000001105 regulatory effect Effects 0.000 description 6
- 230000009467 reduction Effects 0.000 description 5
- 230000009897 systematic effect Effects 0.000 description 5
- 230000004907 flux Effects 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 238000004781 supercooling Methods 0.000 description 4
- 239000012808 vapor phase Substances 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 239000007791 liquid phase Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 239000011555 saturated liquid Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 230000001839 systemic circulation Effects 0.000 description 2
- 238000010793 Steam injection (oil industry) Methods 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000006200 vaporizer Substances 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
Classifications
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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
- F25B41/006—Fluid-circulation arrangements optical fluid control arrangements
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides a heat exchange system, comprising: the main circulation flow path is sequentially provided with a main compressor, a first heat exchanger, a first throttling device, a first flash tank, a second throttling device, a second flash tank and a second heat exchanger, wherein the main compressor is a double-cylinder double-stage compressor, or two single-cylinder compressors arranged in series, or a scroll compressor with an air supplementing port; the first air replenishing branch is used for replenishing air to the main compressor by the first flash tank; and the second air supplementing branch is used for supplementing air to the main circulation flow path from the second flash tank, and the communication point of the second air supplementing branch and the main circulation flow path is positioned between the main compressor and the first heat exchanger or between the main compressor and the second heat exchanger. The problem of heat pump system performance poor under still having the ultra-low temperature operating mode environment among the prior art is solved in this application.
Description
Technical field
The present invention relates to technical field of heat exchange, in particular to a kind of heat-exchange system.
Background technology
For heat pump, existing heat pump mainly adopts the mode of single stage compress, runs functional when outdoor environment temperature is relatively high, but in the lower situation of outdoor environment temperature, the operation that heat pump can not be efficient, reliable, stable.
This is because when outdoor environment temperature is lower, the evaporating pressure of heat pump reduces more, the pressure ratio of compressor increases, even exceed the critical value that ordinary single-stage compressibility normally runs, and the increase of compression ratio causes excessive discharge temperature, cause high frequent start and stop, compressor time serious, can be caused to burn.Therefore, single stage compress heat pump cannot meet the Production requirements such as heating, supplying hot water or high temperature drying at low temperature season.
To this, in existing product, carry out improved design.For a kind of super low temperature heat pump air conditioner system, adopt the jet screw compressor of enhancement mode and steam injection system, when worst cold case heating operation, utilize the agent of flash vessel ejector refrigeration, realize accurate Two-stage Compression second vapor injection and increase enthalpy, relative single stage compress system, be equivalent to add condensator outlet cold-producing medium degree of supercooling, the reduction of evaporator specific enthalpy and evaporator inlet-outlet are increased than enthalpy difference, heating capacity and COP can be improved to a certain extent, flash gas directly enters compressor gas supplementing opening, makes delivery temperature also decrease to some degree.But, under ultra-low temperature surroundings operating mode, when namely work condition environment temperature is lower than subzero ten degree, the evaporating temperature of heat pump is lower, and the amplitude that the saturation temperature reduction caused falls in the side pressure of evaporimeter inner refrigerant is much bigger compared with normal temperature operating mode, makes evaporimeter mean temperature difference very little, evaporimeter changes poor-performing, make existing employing twin-stage or accurate two-stage compression second vapor injection increase enthalpy technology, only can promote low-temperature heating capacity and COP to a certain extent, the reduction of compressor exhaust temperature is also very limited.
It can thus be appreciated that still there is the problem of heat exchange property difference under ultralow-temperature operation conditions environment in heat pump of the prior art.
Summary of the invention
Main purpose of the present invention is to provide a kind of heat-exchange system, to solve the problem that heat pump in prior art still exists systematic function difference under ultralow-temperature operation conditions environment.
To achieve these goals, the invention provides a kind of heat-exchange system, comprise: major cycle stream, major cycle stream is disposed with main compressor, First Heat Exchanger, first throttle device, the first flash evaporation, the second throttling arrangement, the second flash evaporation, the second heat exchanger, wherein, main compressor is twin-tub double-stage compressor or two single cylinder compressors be arranged in series or the screw compressor with gas supplementing opening; First tonifying Qi branch road, the first tonifying Qi is propped up route first flash evaporation and is carried out tonifying Qi to main compressor; Second tonifying Qi branch road, the second tonifying Qi is propped up route second flash evaporation and is carried out tonifying Qi to major cycle stream, and the connectivity points of the second tonifying Qi branch road and major cycle stream is between main compressor and First Heat Exchanger, or connectivity points is between main compressor and the second heat exchanger.
Further, connectivity points, between main compressor and the second heat exchanger, the second tonifying Qi branch road is provided with pressure equaliser.
Further, connectivity points, between main compressor and the second heat exchanger, major cycle stream is also provided with the 3rd throttling arrangement.
Further, connectivity points, between main compressor and First Heat Exchanger, the second tonifying Qi branch road is also provided with auxiliary compressor.
Further, major cycle stream is also provided with the 3rd throttling arrangement.
Further, major cycle stream is also provided with Intermediate Heat Exchanger, Intermediate Heat Exchanger makes first-class section on major cycle stream to carry out heat exchange with second section, and first-class section is between First Heat Exchanger and first throttle device, and second section is between the second heat exchanger and main compressor.
Further, when main compressor be two be arranged in series single cylinder compressor time, one end away from the first flash evaporation of the first tonifying Qi branch road and the fluid communication between two single cylinder compressors of major cycle stream; Or when main compressor is twin-tub double-stage compressor, the high pressure chest of twin-tub double-stage compressor is communicated with the connectivity part of low pressure chamber one end away from the first flash evaporation with the first tonifying Qi branch road; Or when main compressor is screw compressor, being communicated with the gas supplementing opening of screw compressor away from one end of the first flash evaporation of the first tonifying Qi branch road.
Further, auxiliary compressor and main compressor are all positioned at same compressor housing.
Further, pressure equaliser is capillary or control valve.
Further, pressure equaliser is balance pipeline section, and the caliber scope of balance pipeline section is between 3 millimeters to 4 millimeters.
Further, heat-exchange system is heat pump type air conditioner or heat pump type water heater.
Apply technical scheme of the present invention, major cycle stream is disposed with main compressor, First Heat Exchanger, first throttle device, first flash evaporation, second throttling arrangement, second flash evaporation, second heat exchanger, wherein, main compressor is twin-tub double-stage compressor, or two single cylinder compressors be arranged in series, or with the screw compressor of gas supplementing opening, first tonifying Qi is propped up route first flash evaporation and is carried out tonifying Qi to main compressor, second tonifying Qi is propped up route second flash evaporation and is carried out tonifying Qi to major cycle stream, the connectivity points of the second tonifying Qi branch road and major cycle stream is between main compressor and First Heat Exchanger, or connectivity points is between main compressor and the second heat exchanger.By increasing by the second flash evaporation at the entrance of the second heat exchanger, can obviously improve the second heat exchanger, particularly ultralow-temperature operation conditions time heat transfer property, improve heat exchange pressure, reduce the wasted work of main compressor, and then improve systematic function.From systemic circulation angle, by setting up the second tonifying Qi branch road, compared with prior art, add the degree of supercooling of the outlet of First Heat Exchanger, therefore, be conducive to the lifting of circularly cooling amount or heating capacity, and the present invention obviously can also improve the heat transfer property of the second heat exchanger, further promotes the cycle efficieny of this heat-exchange system.Meanwhile, for single stage compress circulation, the heat-exchange system in the present invention can significantly improve low-temperature heating ability and efficiency, also obviously can reduce the delivery temperature of main compressor.
Accompanying drawing explanation
The Figure of description forming a application's part is used to provide a further understanding of the present invention, and schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 shows the schematic diagram of the heat-exchange system according to first embodiment of the present invention;
Fig. 2 shows the schematic diagram of the heat-exchange system according to second embodiment of the present invention;
Fig. 3 shows the schematic diagram of the heat-exchange system according to the 3rd embodiment of the present invention;
Fig. 4 shows the schematic diagram of the heat-exchange system according to the 4th embodiment of the present invention;
Fig. 5 shows the schematic diagram of the heat-exchange system according to the 5th embodiment of the present invention; And
Fig. 6 shows the schematic diagram of the heat-exchange system according to the 6th embodiment of the present invention.
Wherein, above-mentioned accompanying drawing comprises the following drawings mark:
10, major cycle stream; 11, main compressor; 111, high pressure chest; 112, low pressure chamber; 12, First Heat Exchanger; 13, first throttle device; 14, the first flash evaporation; 15, the second throttling arrangement; 16, the second flash evaporation; 17, the second heat exchanger; 18, the 3rd throttling arrangement; 19, Intermediate Heat Exchanger; 20, the first tonifying Qi branch road; 21, connectivity points; 22, auxiliary compressor; 30, the second tonifying Qi branch road; 31, pressure equaliser.
Detailed description of the invention
It should be noted that, when not conflicting, the embodiment in the application and the feature in embodiment can combine mutually.Below with reference to the accompanying drawings and describe the present invention in detail in conjunction with the embodiments.
It is noted that following detailed description is all exemplary, be intended to provide further instruction to the application.Unless otherwise, all technology used herein and scientific terminology have the identical meanings usually understood with the application person of an ordinary skill in the technical field.
Still there is the problem of systematic function difference under ultralow-temperature operation conditions environment in order to solve heat-exchange system in prior art, the invention provides a kind of heat-exchange system.
As shown in Figures 1 to 6, heat-exchange system comprises major cycle stream 10, first tonifying Qi branch road 20 and the second tonifying Qi branch road 30, major cycle stream 10 is disposed with main compressor 11, First Heat Exchanger 12, first throttle device 13, first flash evaporation 14, second throttling arrangement 15, second flash evaporation 16, second heat exchanger 17, wherein, main compressor 11 is twin-tub double-stage compressor or two single cylinder compressors be arranged in series or the screw compressor with gas supplementing opening; First tonifying Qi branch road 20 carries out tonifying Qi by the first flash evaporation 14 to main compressor 11; Second tonifying Qi branch road 30 carries out tonifying Qi by the second flash evaporation 16 to major cycle stream 10, the connectivity points 21 of the second tonifying Qi branch road 30 and major cycle stream 10 is between main compressor 11 and First Heat Exchanger 12, or connectivity points 21 is between main compressor 11 and the second heat exchanger 17.
By increasing by the second flash evaporation 16 at the entrance of the second heat exchanger 17, can obviously improve the second flash evaporation 16, particularly ultralow-temperature operation conditions time heat transfer property, improve heat exchange pressure, reduce the wasted work of main compressor 11, and then improve systematic function.From systemic circulation angle, by setting up the second tonifying Qi branch road 30, compared with prior art, add the degree of supercooling of the outlet of First Heat Exchanger 12, therefore, be conducive to the lifting of circularly cooling amount or heating capacity, and the present invention obviously can also improve the heat transfer property of the second heat exchanger 17, further promotes the cycle efficieny of this heat-exchange system.Meanwhile, for single stage compress circulation, the heat-exchange system in the present invention can significantly improve low-temperature heating ability and efficiency, also obviously can reduce the delivery temperature of main compressor 11.
In detailed description of the invention shown in Fig. 1 to Fig. 6, the second heat exchanger 17 is evaporimeter, and First Heat Exchanger 12 is condenser.And embodiment is all the circulation of various two-stage compression refrigeration, these circulations may be used in the actual refrigeration such as single cold air-conditioning, air conditioner, super low temperature heat pump air-conditioning and Teat pump boiler or heating, can improve the list refrigeration of these systems, singly heat or the combination property of cooling and warming.
Because vapor phase refrigerant flow pressure drop is much larger than liquid phase refrigerant, therefore the vapor phase refrigerant in the entrance cold-producing medium of the second heat exchanger 17 being isolated deenergizes significantly improves the pressure drop of the second heat exchanger 17, and owing to being separated a part to the vapor phase refrigerant of heat transfer without profit, make flow in the second heat exchanger 17 have the reduction of certain amplitude, also make pressure drop reduce further.The gas that second flash evaporation 16 is separated is low-pressure gas, if directly mixed with high pressure gas, then high pressure gas can directly flow back in the second flash evaporation 16, therefore or this portion gas directly mixes with main road low-pressure gas, otherwise by an increasing apparatus be raised to high pressure again with main road high pressure mixing.
It should be noted that, set up cross valve in this heat-exchange system after, the heat pump in the application can be heat pump type air conditioner or heat pump type water heater.
In application, when main compressor 11 be two be arranged in series single cylinder compressor time, the first tonifying Qi branch road 20 away from one end of the first flash evaporation 14 and the fluid communication between two single cylinder compressors of major cycle stream 10.
Or when main compressor 11 is twin-tub double-stage compressors, the high pressure chest 111 of twin-tub double-stage compressor is communicated with one end away from the first flash evaporation 14 of the first tonifying Qi branch road 20 with the connectivity part of low pressure chamber 112.
Or when main compressor 11 is screw compressors, one end away from the first flash evaporation 14 of the first tonifying Qi branch road 20 is communicated with the gas supplementing opening of screw compressor.Screw compressor is not similar to the high pressure chest of twin-tub double-stage compressor and dividing of low pressure chamber, and compression process being undertaken by rotating by certain track of orbiter.Do not have dividing of single twin-tub, gas supplementing opening is turned off, namely single stage compress, opens multiple gas supplementing opening and just can form accurate multi-stage compression.
In the detailed description of the invention shown in Fig. 1, connectivity points 21, between main compressor 11 and the second heat exchanger 17, the second tonifying Qi branch road 30 is provided with pressure equaliser 31.When heat-exchange system runs, the refrigerant gas of HTHP from high pressure chest 111 discharge enter First Heat Exchanger 12 after become the subcooled liquid of cryogenic high pressure, the cold-producing medium two-phase mixture becoming medium temperature and medium pressure after entering first throttle device 13 throttling enters in the first flash evaporation 14 and carries out gas-liquid separation, the cold-producing medium two-phase mixture that the liquid refrigerant be separated becomes low-temp low-pressure after the second throttling arrangement 15 throttling enters in the second flash evaporation 16 and carries out gas-liquid separation, the liquid refrigerant of the low-temp low-pressure be separated directly enters the overheated gas cold-producing medium that the second heat exchanger 17 is evaporated to low-temp low-pressure, the low temperature low pressure gas refrigerant mixed through pressure equaliser 31 pressure regulation be separated with the second flash evaporation 16 enters the air entry of low pressure chamber 112, the refrigerant gas of medium temperature and medium pressure is become after the compression boosting of low pressure chamber 112, the air entry of high pressure chest 111 is mixed into the medium temperature and medium pressure gas refrigerant be separated in the first flash evaporation 14, through high pressure chest 111 boil down to high-temperature high-pressure refrigerant gas, complete a circulation.
This embodiment is by the gas liquid separating function of the second flash evaporation 16 in heat-exchange system, the gas phase portion of the gas-liquid two-phase cold-producing medium entering the second heat exchanger 17 is separated to the air entry of low pressure chamber 112, and the cold-producing medium being approximately saturated liquid enters in the second heat exchanger 17 and evaporates, farthest improve the caloric receptivity of the unit mass cold-producing medium of this circulation, and second the inlet refrigerant of heat exchanger 17 be the low-down two-phase state of saturated liquid state or mass dryness fraction, improve the shunting uniformity of the second heat exchanger 17, reduce refrigerant side pressure drops, add the mean temperature difference of the second heat exchanger 17, second heat exchanger 17 is significantly promoted as heat exchange property during evaporimeter, evaporating temperature raises, reduce circulation compression ratio merit, systematic function significantly promotes.And, the low temperature low pressure gas cold-producing medium be separated by the gas liquid separating function of the second flash evaporation 16 is directly sucked by low pressure chamber 112, reduce suction temperature, therefore the delivery temperature of low pressure chamber 112 also can reduce, and then the delivery temperature of high pressure chest 111 also can reduce further.
Alternatively, pressure equaliser 31 is capillary or control valve.Control valve is the adjustable valve mechanism of actual internal area, and its Main Function is to via the isolated gaseous refrigerant step-down of the second flash evaporation 16 and regulate the gaseous refrigerant mass flow be separated.
Alternatively, pressure equaliser 31 is balance pipeline section, and the caliber scope of balance pipeline section is between 3 millimeters to 4 millimeters.
" pressure equaliser 31 " effect is to via the isolated gaseous refrigerant step-down of the second flash evaporation 16, enter to prevent liquid refrigerant, and the pressure drop balanced in the second tonifying Qi branch road 30 in gaseous refrigerant and major cycle stream 10 in evaporimeter and pipeline, make system run all right.In addition, " pressure equaliser 31 " gaseous refrigerant agent flux in the second tonifying Qi branch road 30 can should be regulated.
In the detailed description of the invention shown in Fig. 3, on the basis of Fig. 1 embodiment, connectivity points 21, between main compressor 11 and the second heat exchanger 17, major cycle stream 10 is also provided with the 3rd throttling arrangement 18.Like this, suitably can regulate the inlet refrigerant mass dryness fraction of the second heat exchanger 17 (being evaporimeter in figure), for cold-producing mediums such as R410A, R32, R134a, R1224yf, evaporation heat transfer coefficient and refrigerant side pressure drops all increase along with the increase of cold-producing medium mass dryness fraction, by regulating the 3rd throttling arrangement 18 can balancing evaporator tube internal heat exchange coefficient and pressure drop, ensure that performance of evaporator performs to the best.
In the detailed description of the invention shown in Fig. 2, connectivity points 21, between main compressor 11 and First Heat Exchanger 12, the second tonifying Qi branch road 30 is also provided with auxiliary compressor 22.The pressure equaliser 31 in Fig. 1 is namely substituted for auxiliary compressor 22.Auxiliary compressor 22 mainly by the gas lift of shwoot in the second flash evaporation 16 to pressure at expulsion, the wasted work of main compressor 11 can be reduced.Now, auxiliary compressor 22 is small displacement compressors.The low temperature low pressure gas that second flash evaporation 16 is separated directly can be boosted to high pressure gas by auxiliary compressor 22, save in Fig. 1 due to restriction loss that pressure equaliser 31 causes, and because the amount of cold-producing medium in global cycle is higher than the summation of the circularly cooling agent flux of high pressure chest 111 and low pressure chamber 112, the compression horsepower of heat-exchange system is reduced.
In the detailed description of the invention shown in Fig. 4, on the basis of Fig. 2 embodiment, major cycle stream 10 is also provided with the 3rd throttling arrangement 18.Like this, suitably can regulate the inlet refrigerant mass dryness fraction of the second heat exchanger 17 (being evaporimeter in figure), for cold-producing mediums such as R410A, R32, R134a, R1224yf, evaporation heat transfer coefficient and refrigerant side pressure drops all increase along with the increase of cold-producing medium mass dryness fraction, by regulating the 3rd throttling arrangement 18 can balancing evaporator tube internal heat exchange coefficient and pressure drop, ensure that performance of evaporator performs to the best.
Alternatively, first throttle device 13, second throttling arrangement 15 and the 3rd throttling arrangement 18 can be one or more in capillary, restriction sleeve, heating power expansion valve, electronic expansion, restricting orifice.
In the detailed description of the invention shown in Fig. 5, on the basis of Fig. 1 embodiment, major cycle stream 10 is also provided with Intermediate Heat Exchanger 19, Intermediate Heat Exchanger 19 makes first-class section on major cycle stream 10 to carry out heat exchange with second section, first-class section is between First Heat Exchanger 12 and first throttle device 13, and second section is between the second heat exchanger 17 and main compressor 11.The hot junction channel setting of this Intermediate Heat Exchanger 19 is on the pipeline between the outlet and first throttle device 13 of First Heat Exchanger 12, cold junction channel setting is on the pipeline between the outlet and the air-breathing of low pressure chamber 112 of the second heat exchanger 17, this Intermediate Heat Exchanger 19 significantly can reduce the outlet temperature of First Heat Exchanger 12, and then the specific enthalpy reduced after first throttle device 13 throttling and mass dryness fraction, increase the liquid refrigerant mass flux entered in the second heat exchanger 17, the heat exchange amount of the second heat exchanger 17 is improved further, therefore system heating capacity and efficiency are also promoted further.
In the detailed description of the invention shown in Fig. 6, on the basis of Fig. 2 embodiment, major cycle stream 10 is also provided with Intermediate Heat Exchanger 19, Intermediate Heat Exchanger 19 makes first-class section on major cycle stream 10 to carry out heat exchange with second section, first-class section is between First Heat Exchanger 12 and first throttle device 13, and second section is between the second heat exchanger 17 and main compressor 11.The hot junction channel setting of this Intermediate Heat Exchanger 19 is on the pipeline between the outlet and first throttle device 13 of First Heat Exchanger 12, cold junction channel setting is on the pipeline between the outlet and the air-breathing of low pressure chamber 112 of the second heat exchanger 17, this Intermediate Heat Exchanger 19 significantly can reduce the outlet temperature of First Heat Exchanger 12, and then the specific enthalpy reduced after first throttle device 13 throttling and mass dryness fraction, increase the liquid refrigerant mass flux entered in the second heat exchanger 17, the heat exchange amount of the second heat exchanger 17 is improved further, therefore system heating capacity and efficiency are also promoted further.
In the detailed description of the invention shown in Fig. 1, Fig. 3 and Fig. 5, main compressor 11 can be the twin-tub two-spool compressor be made up of high pressure chest 111 and low pressure chamber 112, or the compressor unit of accurate secondary screw compressor.If twin-tub two-spool compressor then high pressure chest 111 and low pressure chamber 112 is connected in series, and second vapor injection mouth between high pressure chest 111 and low pressure chamber 112, is established to be connected with the first tonifying Qi branch road 20.
As shown in Fig. 2, Fig. 4, Fig. 6, auxiliary compressor 22 and main compressor 11 are all positioned at same compressor housing.Same motor can be adopted to drive, multiple motor also can be adopted to drive.General is all that employing motor drives, the convenient unified start and stop controlling compressor.
Alternatively, auxiliary compressor 22 can be the compressor of rotor compressor or other type, in parallel with high pressure chest 111, and high pressure chest 111 and low pressure chamber 112 are connected.
Certainly, above-mentioned auxiliary compressor 22 and main compressor 11 can also be replaced with a multicylinder compressor.High pressure chest 111, low pressure chamber 112 and auxiliary compressor 22 are placed in same compressor housing, become the compressor unit comprising three compression chambers.
Alternatively, the first flash evaporation 14 and the second flash evaporation 16 can be unidirectional flash evaporation or two-way flash evaporation, also can be that other has the flash evaporation of gas liquid separating function.
It should be noted that, for cold-producing mediums such as R410A, R32, R134a, R1224yf, evaporation heat transfer coefficient and refrigerant side pressure drops all increase along with the increase of cold-producing medium mass dryness fraction, the 3rd throttling arrangement 18 between the second flash evaporation 16 and evaporimeter, make the import mass dryness fraction of evaporimeter have certain increase, now the coefficient of heat transfer can increase, and pressure drop simultaneously also can increase, by regulating the 3rd throttling arrangement 18 can balance the coefficient of heat transfer and pressure drop better, make evaporimeter combination property best; For CO
2cold-producing medium, evaporation heat transfer coefficient reduces along with the increase of mass dryness fraction, and pressure drop increases along with the increase of mass dryness fraction, now need not increase the better effects if of the 3rd throttling arrangement 18.For the 3rd throttling arrangement 18 of adjustable restriction characteristic as electric expansion valve etc., different evaporator inlet mass dryness fractions can be regulated by regulating aperture, need not arrange multiple, multiple effect that also can't allow being set and more optimizing.
As can be seen from the above description, the above embodiments of the present invention achieve following technique effect:
1) increase by the second flash evaporation 16, be equivalent to the outlet subcooling again increasing condenser, reduce further entrance specific enthalpy and the mass dryness fraction of evaporimeter, make evaporator inlet-outlet increase further than enthalpy difference, be conducive to improving low-temperature heating capacity or COP;
2) cold-producing medium absorbs heat in evaporation process in evaporimeter, vapor phase refrigerant constantly increases, linear loss increases, the contribution of heat exchanging is also much smaller than liquid phase refrigerant, so reduce the entrance cold-producing medium mass dryness fraction of evaporimeter, can effectively reduce friction loss in evaporimeter, increase the evaporator heat transfer temperature difference, thus effectively improve the heat exchange efficiency of evaporimeter;
3) evaporimeter generally adopts the method increasing point way to reduce the refrigerant side pressure loss, but the distribution of the uniformity of two phase refrigerant is difficult to accomplish, the heat exchange area of evaporimeter is caused to utilize insufficient, reduce evaporator cold-producing medium mass dryness fraction, obviously can improve evaporator refrigerant branches uniformity, and then improve evaporator heat exchange performance, in order to better play performance of evaporator, evaporimeter generally adopts many layout type along separate routes, when each shunt inner refrigerant flow and mass dryness fraction uniformity, the heat transfer effect of each shunt is consistent, whole evaporator heat exchange performance is best, but, because evaporator inlet is gas-liquid two-phase cold-producing medium, gas is different with the gravity of liquid, each shunt inner refrigerant flow and mass dryness fraction is difficult to divide evenly, and by increasing flash evaporation, evaporator inlet is made to be pure liquid phase refrigerant substantially, therefore easily accomplish along separate routes evenly, make evaporator heat exchange performance better,
4) because the gas liquid separating function of the second flash evaporation 16 makes the cold-producing medium of lower temperature enter the air entry compression of main compressor 11 or directly be compressed to high-pressure exhaust, mixing exhaust temperature or delivery temperature can obviously be reduced;
5) for cold-producing mediums such as R410A, R32, R134a, R1224yf, evaporation heat transfer coefficient and refrigerant side pressure drops all increase along with the increase of cold-producing medium mass dryness fraction, evaporator increases by the 3rd throttling arrangement 18 can balancing evaporator tube internal heat exchange coefficient and pressure drop, ensures that performance of evaporator performs to the best; For super low temperature heat pump system, evaporimeter pressure drop is occupied an leading position, and evaporator cancels the 3rd throttling arrangement 18, can increase considerably evaporimeter mean temperature difference, improves the heat exchange property of evaporimeter;
6) gas compression that the second flash evaporation 16 is separated by the auxiliary compressor 22 increasing small displacement is to high-pressure, reduce the wasted work of main compressor 11 in major cycle stream 10, and main compressor 11 adopts twin-tub to connect compression chamber in parallel with the compression chamber of auxiliary compressor 22, reduce compressor volume, reduce the complexity of system cost and control.
7) the second flash evaporation 16 and Intermediate Heat Exchanger 19 is increased, reduce further conventional two-stage compression cycle condensator outlet degree of supercooling, add evaporimeter inner refrigerant flow, and by the second flash evaporation 16, unhelpful for heat exchanging in the low mass dryness fraction gas-liquid two-phase cold-producing medium entering evaporimeter and the gaseous refrigerant increasing on-way resistance is separated, only pure liquid refrigerant enters evaporimeter, not only improve the shunting effect of evaporator cold-producing medium, also considerably reduce vaporizer side pressure drop, maximize unit mass cold-producing medium caloric receptivity in evaporimeter, improve the heat exchange property of evaporimeter, and then improve heat pump system performance,
8) by pressure equaliser 31, the low temperature low pressure gas that second flash evaporation 16 is separated is introduced directly in the low pressure chamber 112 of main compressor 11, reduces the suction temperature of low pressure chamber 112, therefore the reduction of delivery temperature is had certain effect;
It should be noted that used term is only to describe detailed description of the invention here, and be not intended to the illustrative embodiments of restricted root according to the application.As used herein, unless the context clearly indicates otherwise, otherwise singulative is also intended to comprise plural form, in addition, it is to be further understood that, " comprise " when using term in this manual and/or " comprising " time, it indicates existing characteristics, step, work, device, assembly and/or their combination.
It should be noted that, term " first ", " second " etc. in the description of the application and claims and above-mentioned accompanying drawing are for distinguishing similar object, and need not be used for describing specific order or precedence.Should be appreciated that the data used like this can be exchanged in the appropriate case, so as the embodiment of the application described herein can with except here diagram or describe those except order implement.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any amendment done, equivalent replacement, improvement etc., all should be included within protection scope of the present invention.
Claims (11)
1. a heat-exchange system, is characterized in that, comprising:
Major cycle stream (10), described major cycle stream (10) is disposed with main compressor (11), First Heat Exchanger (12), first throttle device (13), the first flash evaporation (14), the second throttling arrangement (15), the second flash evaporation (16), the second heat exchanger (17), wherein, described main compressor (11) is twin-tub double-stage compressor or two single cylinder compressors be arranged in series or the screw compressor with gas supplementing opening;
First tonifying Qi branch road (20), described first tonifying Qi branch road (20) carries out tonifying Qi by described first flash evaporation (14) to described main compressor (11);
Second tonifying Qi branch road (30), described second tonifying Qi branch road (30) carries out tonifying Qi by described second flash evaporation (16) to described major cycle stream (10), the connectivity points (21) of described second tonifying Qi branch road (30) and described major cycle stream (10) is positioned between described main compressor (11) and described First Heat Exchanger (12), or described connectivity points (21) is positioned between described main compressor (11) and described second heat exchanger (17).
2. heat-exchange system according to claim 1, it is characterized in that, described connectivity points (21) is positioned between described main compressor (11) and described second heat exchanger (17), and described second tonifying Qi branch road (30) is provided with pressure equaliser (31).
3. heat-exchange system according to claim 1 and 2, it is characterized in that, described connectivity points (21) is positioned between described main compressor (11) and described second heat exchanger (17), described major cycle stream (10) is also provided with the 3rd throttling arrangement (18).
4. heat-exchange system according to claim 1, it is characterized in that, described connectivity points (21) is positioned between described main compressor (11) and described First Heat Exchanger (12), and described second tonifying Qi branch road (30) is also provided with auxiliary compressor (22).
5. heat-exchange system according to claim 4, is characterized in that, described major cycle stream (10) is also provided with the 3rd throttling arrangement (18).
6. the heat-exchange system according to claim 2 or 4, it is characterized in that, described major cycle stream (10) is also provided with Intermediate Heat Exchanger (19), described Intermediate Heat Exchanger (19) makes first-class section on described major cycle stream (10) to carry out heat exchange with second section, described first-class section is between described First Heat Exchanger (12) and described first throttle device (13), and described second section is between described second heat exchanger (17) and described main compressor (11).
7. heat-exchange system according to claim 1, is characterized in that,
When described main compressor (11) be two be arranged in series single cylinder compressor time, described first tonifying Qi branch road (20) away from one end of described first flash evaporation (14) and the fluid communication between two described single cylinder compressors of described major cycle stream (10); Or
When described main compressor (11) is twin-tub double-stage compressor, the high pressure chest (111) of described twin-tub double-stage compressor is communicated with the connectivity part of low pressure chamber (112) one end away from described first flash evaporation (14) with described first tonifying Qi branch road (20); Or
When described main compressor (11) is screw compressor, being communicated with the described gas supplementing opening of described screw compressor away from described one end of first flash evaporation (14) of described first tonifying Qi branch road (20).
8. heat-exchange system according to claim 4, is characterized in that, described auxiliary compressor (22) and described main compressor (11) are all positioned at same compressor housing.
9. heat-exchange system according to claim 2, is characterized in that, described pressure equaliser (31) is capillary or control valve.
10. heat-exchange system according to claim 2, is characterized in that, described pressure equaliser (31) is balance pipeline section, and the caliber scope of described balance pipeline section is between 3 millimeters to 4 millimeters.
11. heat-exchange systems according to claim 2, is characterized in that, described heat-exchange system is heat pump type air conditioner or heat pump type water heater.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511030770.1A CN105444476A (en) | 2015-12-29 | 2015-12-29 | Heat exchange system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201511030770.1A CN105444476A (en) | 2015-12-29 | 2015-12-29 | Heat exchange system |
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| CN105444476A true CN105444476A (en) | 2016-03-30 |
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| CN201511030770.1A Pending CN105444476A (en) | 2015-12-29 | 2015-12-29 | Heat exchange system |
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| CN108224774A (en) * | 2017-12-07 | 2018-06-29 | 合肥通用机械研究院 | A kind of carbon dioxide heat pump water heater with defrosting |
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| WO2021004304A1 (en) * | 2019-07-09 | 2021-01-14 | 珠海格力节能环保制冷技术研究中心有限公司 | Refrigeration/heat pump system having two-stage compression and multiple air suplementations, control method therefor and air conditioner |
| CN115200268A (en) * | 2022-06-10 | 2022-10-18 | 智己汽车科技有限公司 | Heat exchange circulation system, air conditioner and vehicle |
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Application publication date: 20160330 |