CN106352600A - Efficient refrigeration or heat pump device and refrigerant flow adjusting method thereof - Google Patents
Efficient refrigeration or heat pump device and refrigerant flow adjusting method thereof Download PDFInfo
- Publication number
- CN106352600A CN106352600A CN201610811750.6A CN201610811750A CN106352600A CN 106352600 A CN106352600 A CN 106352600A CN 201610811750 A CN201610811750 A CN 201610811750A CN 106352600 A CN106352600 A CN 106352600A
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- CN
- China
- Prior art keywords
- heat pump
- transfer device
- pressure refrigerant
- throttling arrangement
- heat transfer
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
- 239000003507 refrigerant Substances 0.000 title claims abstract description 39
- 238000005057 refrigeration Methods 0.000 title claims abstract description 27
- 238000000034 method Methods 0.000 title claims abstract description 11
- 239000007788 liquid Substances 0.000 claims abstract description 32
- 239000002826 coolant Substances 0.000 claims description 54
- 239000006200 vaporizer Substances 0.000 claims description 36
- 238000010438 heat treatment Methods 0.000 claims description 15
- 230000004907 flux Effects 0.000 claims description 7
- 239000000523 sample Substances 0.000 claims description 5
- 230000000694 effects Effects 0.000 abstract description 4
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 9
- 229910052802 copper Inorganic materials 0.000 description 9
- 239000010949 copper Substances 0.000 description 9
- 239000012071 phase Substances 0.000 description 9
- 238000001704 evaporation Methods 0.000 description 7
- 230000008676 import Effects 0.000 description 5
- 238000004781 supercooling Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 238000005728 strengthening Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000018044 dehydration Effects 0.000 description 1
- 238000006297 dehydration reaction Methods 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 239000012047 saturated solution Substances 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/37—Capillary tubes
-
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
-
- 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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2513—Expansion valves
-
- 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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2103—Temperatures near a heat exchanger
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The invention discloses an efficient refrigeration or heat pump device and a refrigerant flow adjusting method thereof. The efficient refrigeration or heat pump device in the first technical scheme comprises a throttling device and an evaporator, an inlet of the throttling device is communicated with a high-pressure refrigerant pipe, and an outlet of the evaporator is communicated with a low-pressure refrigerant pipe. The efficient refrigeration or heat pump device is characterized in that a middle heat exchange device is arranged, one channel of the middle heat exchange device is connected into the high-pressure refrigerant pipe in series, and the other channel of the middle heat exchange device is connected into the low-pressure refrigerant pipe in series; the resistance of the throttling device is adjustable, and therefore the liquid feeding amount of the throttling device can be adjusted; a temperature sensing device associated with adjusting of the resistance of the throttling device is arranged on or in a pipe of the low-pressure refrigerant outlet of the middle heat exchange device. The efficient refrigeration or heat pump device is easy to achieve; as the superheat degree of a refrigerant at the low-pressure refrigerant outlet of the middle heat exchanger, the heat exchange effect of the evaporator can be improved, and then the efficiency of the device can be improved.
Description
Technical field
The present invention relates to refrigeration or art of heat pumps, in particular to highly effective refrigeration or heat pump assembly and its cold medium flux
Control method.
Background technology
The state of gas phase refrigerant is weighed with the degree of superheat, and the degree of superheat of saturation gas phase refrigerant is 0k, gas-liquid two-phase coolant
State is weighed with mass dryness fraction, and the mass dryness fraction of gas-liquid two-phase coolant is more than 0 and is less than 1, and the mass dryness fraction of saturation gas phase refrigerant is 1, saturated solution
The mass dryness fraction of phase coolant is 0, and the state of liquid phase coolant is weighed with degree of supercooling, and the degree of supercooling of saturation liquid phase coolant is 0k.
Using in the refrigeration of dry evaporator or heat pump, generally require the degree of superheat of evaporator outlet coolant is carried out
Control, but typically all can have the degree of superheat of 3-10k, so can lead to exist superheat section, the exchange capability of heat of vaporizer in vaporizer
It is not fully used.Especially in vaporizer, the evaporating temperature of coolant is less with the inlet temperature Temperature Difference Ratio of vaporizer
(the above-mentioned temperature difference about 5-8k, with the degree of superheat very close to and temperature difference requirement is so little for the air-cooler of application scenario, such as freezer
Reason is the dehydration drying loss in order to reduce food in freezer), the superheat section accounting in vaporizer is higher, can reach in practical application
10～30%, particularly system use heating power expansion valve and related commissioning personnel unprofessional if, superheat section in vaporizer
Accounting is possibly even beyond 50%.So significantly waste the exchange capability of heat of vaporizer, reduce system effectiveness.
And in flooded evaporator, its import coolant is all liquid, the mass dryness fraction of its outlet coolant is typically smaller than 1, therefore full
Solution type evaporator has good heat transfer effect, using the system of full-liquid type evaporation, compares and above-mentioned using dry evaporator is
System, efficiency even can exceed 10%.
Content of the invention
It is an object of the invention to solving the above problems.
The first highly effective refrigeration that the present invention provides or the technical scheme of heat pump assembly are as follows:
A kind of highly effective refrigeration or heat pump assembly, comprise throttling arrangement and vaporizer, and described throttling arrangement entrance connects high pressure
Refrigerant pipe, described evaporator outlet connection low pressure refrigerant pipeline it is characterised in that: be provided with intermediate heat transfer device, described in
Between a passage of heat-exchanger rig be serially connected in described high pressure refrigerant pipeline, another passage concatenation of described intermediate heat transfer device
In described low pressure refrigerant pipeline；The resistance-adjustable of described throttling arrangement is such that it is able to adjust its liquid supply rate；Be provided with described
The temperature sensing device of throttling arrangement resistance regulation association, described temperature sensing device is arranged on described intermediate heat transfer device low pressure refrigerant outlet
Pipeline on or pipeline in.
Preferential, described intermediate heat transfer device is two pipelines being close to.
Preferential, described intermediate heat transfer device is double-tube heat exchanger, plate type heat exchanger, case tube heat exchanger or band-tube type heat exchange
Device.
Preferential, described intermediate heat transfer device is double heat exchange of heat pipe.
Preferential, described throttling arrangement is electric expansion valve.
Preferential, described throttling arrangement is the combination unit of capillary tube and valve member.
Preferential, described throttling arrangement is heating power expansion valve, and its temperature-sensitive bag is arranged on described intermediate heat transfer device low pressure cold
On the pipeline of matchmaker's outlet or in pipeline.
Based on the cold medium flux control method of the highly effective refrigeration described in any of the above-described or heat pump assembly it is: according to from described
The liquid supply rate to adjust described throttling arrangement for the degree of superheat of the low-pressure gaseous coolant of intermediate heat transfer device output.
The second highly effective refrigeration that the present invention provides or the technical scheme of heat pump assembly are as follows:
A kind of highly effective refrigeration or heat pump assembly, comprise throttling arrangement and vaporizer, and described throttling arrangement entrance connects high pressure
Refrigerant pipe, described evaporator outlet connection low pressure refrigerant pipeline it is characterised in that: be provided with intermediate heat transfer device, described in
Between a passage of heat-exchanger rig be serially connected in described high pressure refrigerant pipeline, another passage concatenation of described intermediate heat transfer device
In described low pressure refrigerant pipeline；Described throttling arrangement is electric expansion valve, is provided with least one and associates with its aperture regulation
Temperature-sensing probe；At least one described temperature-sensing probe is arranged on the pipeline of described intermediate heat transfer device low pressure refrigerant outlet or pipe
In road, or at least one described temperature-sensing probe is arranged on the compressor in described highly effective refrigeration or heat pump assembly Nei or compressor
On housing or on the discharge duct of compressor or in discharge duct.
Based on the cold medium flux control method of above-mentioned second highly effective refrigeration or heat pump assembly it is: according at least to described compression
The delivery temperature of machine or case temperature or discharge superheat are adjusting the liquid supply rate of described throttling arrangement.
Based on technique scheme, even if the heat that high-pressure liquid coolant provides is excessive, there is no harm to system, only yet
It is that the Intermediate Heat Exchanger set up is bigger, but comparatively, the requirement to the Intermediate Heat Exchanger set up is little, simplest method,
Only the high-pressure liquid tube before throttling need to be close to heat exchange with the pipeline of evaporator outlet.Because control is that Intermediate Heat Exchanger is low
The degree of superheat (can also be by controlling the method indirect control degrees of superheat herein such as discharge superheat) of pressure refrigerant exit coolant, institute
Bigger with the exchange capability of heat of Intermediate Heat Exchanger, the heat that high-pressure liquid coolant is provided by Intermediate Heat Exchanger is more, vaporizer
The coolant cold that throttling arrangement before provides is more, during the cold providing throttling arrangement is set up by evaporator outlet more
Between heat exchanger transmission give high-pressure liquid coolant, finally for vaporizer provide cold be not reduced, on the contrary due to vaporizer
The increasing of middle liquid refrigerants composition, the heat transfer effect of vaporizer is improved, and so that evaporating pressure (temperature) is increased so that coolant
Increased flow capacity, so that the cold of vaporizer output increases, unit efficiency also gets a promotion.
Brief description
Fig. 1 is a kind of system schematic of refrigerating plant of prior art.
The structural representation of one embodiment of Intermediate Heat Exchanger that Fig. 2 adopts for the present invention.
Fig. 3 is the system schematic of refrigerating plant first embodiment of the present invention.
Fig. 4 is to run contrast between prior art refrigerating plant and the first situation of refrigerating plant first embodiment of the present invention
Theoretical pressure-enthalpy chart.
Fig. 5 is to run contrast between prior art refrigerating plant and refrigerating plant first embodiment second situation of the present invention
Theoretical pressure-enthalpy chart.
Fig. 6 is to run contrast between prior art refrigerating plant and the third situation of refrigerating plant first embodiment of the present invention
Theoretical pressure-enthalpy chart.
Fig. 7 is to run contrast between prior art refrigerating plant and the 4th kind of situation of first embodiment of the invention refrigerating plant
Theoretical pressure-enthalpy chart.
Specific embodiment
Below in conjunction with drawings and Examples, technical scheme is described in further detail.
As shown in figure 1, being a kind of system schematic of refrigerating plant of prior art.Wherein, 1 is outer balanced type thermal expansion
Valve, 2 is vaporizer, and 11 is the temperature-sensitive bag of heating power expansion valve 1, and 12 is the pressure-equalizing pipe of heating power expansion valve 1.The direction of arrow is cold
The flow direction of matchmaker, is liquid refrigerants at filled arrows, is gaseous coolant at hollow arrow.Wherein, high-pressure liquid coolant (a point) enters
Heating power expansion valve 1 throttles, and enters vaporizer 2 from the coolant (b point) of heating power expansion valve 1 output, by the control of heating power expansion valve 1
System, the coolant (c point) of vaporizer 2 outlet is superheated steam, the degree of superheat about 5k to 8k.
As shown in Fig. 2 the structural representation of one embodiment of Intermediate Heat Exchanger adopting for the present invention.This heat exchanger is two
Weight heat exchange of heat pipe, a piece interior copper pipe 32 of outer copper pipe 31 inner sleeve, thus define two passages: be first inside interior copper pipe 32
Passage, forms second passage between the outer wall of interior copper pipe 32 and the inwall of outer copper pipe 31.Filled arrows are in first passage
The flow direction of fluid, hollow arrow is the flow direction of second inner fluid passage.Two kinds of fluids, by the heat exchange of interior copper pipe 32, change for strengthening
Heat energy power, interior copper pipe 32 preferentially adopts inner screw thread copper pipe, and the outer wall of interior copper pipe 32 is preferably formed with strengthening screw thread or the wing of heat exchange
Piece.
As shown in figure 3, the system schematic of refrigerating plant first embodiment of the present invention.Wherein, 1 is that outer balanced type heating power is swollen
Swollen valve, 2 is vaporizer, and 3 is Intermediate Heat Exchanger (than double heat exchange of heat pipe as shown in Figure 2), and 11 is the temperature-sensitive of heating power expansion valve 1
Bag, 12 is the pressure-equalizing pipe of heating power expansion valve 1.The direction of arrow is the flow direction of coolant, is liquid refrigerants at filled arrows, hollow
It is gaseous coolant at arrow.
In the present embodiment, high-pressure liquid coolant (a point) initially enters first passage of Intermediate Heat Exchanger 3, wherein by
Low temperature refrigerant cools down, and enters back into heating power expansion valve 1 from the high-pressure liquid coolant (a point) of Intermediate Heat Exchanger 3 output, through thermal expansion
Become the coolant (b point) of low-temp low-pressure after valve 1 throttling, enter back into heat absorption evaporation in vaporizer 2, gas componant gets more and more, from
The coolant (c point) of vaporizer 2 output, through second passage of Intermediate Heat Exchanger 3, is heated by high-pressure liquid coolant wherein, from
Coolant (d point) superheated steam of Intermediate Heat Exchanger 3 output, the typically degree of superheat about 5-8k herein, because the temperature-sensitive of heating power expansion valve 1
Bag 11 is arranged on herein.
Because control is the degree of superheat of second channel outlet coolant (d point) of Intermediate Heat Exchanger 3, intermediate heat transfer
The exchange capability of heat of device 3 is bigger, and the heat that high-pressure liquid coolant is provided by Intermediate Heat Exchanger 3 is more, the section before vaporizer 2
Stream device 1 provide coolant (b point) cold more, throttling arrangement more than 1 offer cold (enthalpy difference between b point and b point with cold
The product of matchmaker's flow) Intermediate Heat Exchanger 3 transmission set up by vaporizer 2 outlet gives high-pressure liquid coolant, and final is evaporation
The cold product of cold medium flux (enthalpy difference between b point and c point with) that device 2 provides is not reduced, on the contrary due in vaporizer 2
The increasing of liquid refrigerants composition, the heat transfer effect of vaporizer 2 is improved, and so that evaporating pressure (temperature) is increased so that coolant stream
Amount increases, so that the cold of vaporizer 2 output increases, system effectiveness also gets a promotion.
Certainly, even if the heat exchange area between 3 two passages of Intermediate Heat Exchanger is infinity, the heat exchange of Intermediate Heat Exchanger 3
Ability is also to have higher limit, and limiting case is the temperature of high-pressure liquid coolant and the evaporating temperature phase entering heating power expansion valve 1
With, at this moment, coolant all low-pressure liquids coolant of heating power expansion valve 1 output in theory, degree of supercooling is 0k.
It is illustrated in figure 4 fortune between prior art refrigerating plant and the first situation of refrigerating plant first embodiment of the present invention
The theoretical pressure-enthalpy chart of row contrast.
It is illustrated in figure 5 fortune between prior art refrigerating plant and refrigerating plant first embodiment second situation of the present invention
The theoretical pressure-enthalpy chart of row contrast.
It is illustrated in figure 6 fortune between prior art refrigerating plant and the third situation of refrigerating plant first embodiment of the present invention
The theoretical pressure-enthalpy chart of row contrast.
It is illustrated in figure 7 fortune between prior art refrigerating plant and 4th kind of situation of refrigerating plant first embodiment of the present invention
The theoretical pressure-enthalpy chart of row contrast.
It should be noted that in Fig. 4 to Fig. 7, the path a-b-c of solid line is that the coolant of above-mentioned prior art refrigerating plant follows
Endless path, the path a-a-b-c-d of dotted line is the refrigerant circulation path of refrigerating plant first embodiment of the present invention.
Also, it should be noted from the first situation of refrigerating plant first embodiment of the present invention to the 4th kind of situation, in
Between heat exchanger 3 exchange capability of heat increasing, the 4th kind of situation is limiting case, at this moment, the heat exchange of Intermediate Heat Exchanger 3 in theory
Area is infinity.In addition, in theory, between enthalpy difference between enthalpy difference between a point and a point, b point and b point, c point and d point
Enthalpy difference, three is equal.
In Fig. 4, b point coolant (coolant of vaporizer 2 import) has larger mass dryness fraction, and (it is cold that vaporizer 2 exports c point coolant
Matchmaker) there is the less degree of superheat, about 1k to 3k.
In Fig. 5, the mass dryness fraction of b point coolant (coolant of vaporizer 2 import) has reduced, and (it is cold that vaporizer 2 exports c point coolant
Matchmaker) it is saturated vapor, its degree of superheat is 0k or mass dryness fraction is 1.
In Fig. 6, the mass dryness fraction of b point coolant (coolant of vaporizer 2 import) reduces further, and c point coolant be (vaporizer 2 outlet
Coolant) it is gas-liquid two-phase coolant, liquid content is less.
In Fig. 7, b point coolant (coolant of vaporizer 2 import) is saturation liquid refrigerants, and its mass dryness fraction is 0 or degree of supercooling is
0k, c point coolant (coolant of vaporizer 2 outlet) is gas-liquid two-phase coolant, and liquid content increased.
Finally it should be noted that: above example is merely to illustrate technical scheme and is not intended to limit, institute
Belong to technical field it is to be appreciated by one skilled in the art that still the specific embodiment of the present invention can be modified or to portion
Technical characteristic is divided to carry out equivalence replacement.So, without departing from the spirit of technical solution of the present invention, all should cover in the present invention
In the middle of the technical scheme scope being claimed.
Claims (10)
1. a kind of highly effective refrigeration or heat pump assembly, comprises throttling arrangement (1) and vaporizer (2), and described throttling arrangement (1) entrance is even
Logical high pressure refrigerant pipeline, described vaporizer (2) outlet low pressure refrigerant pipeline it is characterised in that:
It is provided with intermediate heat transfer device (3), a passage of described intermediate heat transfer device (3) is serially connected in described high pressure refrigerant pipeline
In, another passage of described intermediate heat transfer device (3) is serially connected in described low pressure refrigerant pipeline；
The resistance-adjustable of described throttling arrangement (1) is such that it is able to adjust its liquid supply rate；
It is provided with the temperature sensing device (11) associating with described throttling arrangement (1) resistance regulation, described temperature sensing device (11) is arranged on
On the pipeline of described intermediate heat transfer device (3) low pressure refrigerant outlet or in pipeline.
2. a kind of highly effective refrigeration according to claim 1 or heat pump assembly it is characterised in that:
Described intermediate heat transfer device is two pipelines being close to.
3. a kind of highly effective refrigeration according to claim 1 or heat pump assembly it is characterised in that:
Described intermediate heat transfer device is double-tube heat exchanger, plate type heat exchanger, case tube heat exchanger or band-tube type heat exchanger.
4. a kind of highly effective refrigeration according to claim 3 or heat pump assembly it is characterised in that:
Described intermediate heat transfer device (3) is double heat exchange of heat pipe.
5. a kind of highly effective refrigeration according to claim 1 or heat pump assembly it is characterised in that:
Described throttling arrangement is electric expansion valve.
6. a kind of highly effective refrigeration according to claim 1 or heat pump assembly it is characterised in that:
Described throttling arrangement is the combination unit of capillary tube and valve member.
7. a kind of highly effective refrigeration according to claim 1 or heat pump assembly it is characterised in that:
Described throttling arrangement (1) is heating power expansion valve, and its temperature-sensitive bag (11) is arranged on described intermediate heat transfer device (3) low pressure refrigerant
On the pipeline of outlet or in pipeline.
8. the cold medium flux regulation side of the highly effective refrigeration described in a kind of any one based on the claims 1 to 7 or heat pump assembly
Method it is characterised in that:
Described throttling arrangement (1) is adjusted according to the degree of superheat of the low-pressure gaseous coolant exporting from described intermediate heat transfer device (3)
Liquid supply rate.
9. a kind of highly effective refrigeration or heat pump assembly, comprises throttling arrangement and vaporizer, and described throttling arrangement entrance connection high pressure is cold
Matchmaker's pipeline, described evaporator outlet connection low pressure refrigerant pipeline it is characterised in that:
It is provided with intermediate heat transfer device, a passage of described intermediate heat transfer device is serially connected in described high pressure refrigerant pipeline, institute
Another passage stating intermediate heat transfer device is serially connected in described low pressure refrigerant pipeline；
Described throttling arrangement is electric expansion valve, is provided with the temperature-sensing probe that at least one is associated with its aperture regulation；
At least one described temperature-sensing probe is arranged on the compressor in described highly effective refrigeration or heat pump assembly Nei or compressor housing
Above or on the discharge duct of compressor or in discharge duct.
10. a kind of cold medium flux control method based on the highly effective refrigeration described in the claims 9 or heat pump assembly, its feature
It is:
Delivery temperature according at least to described compressor or case temperature or discharge superheat to adjust the confession of described throttling arrangement
Liquid measure.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610811750.6A CN106352600A (en) | 2016-09-08 | 2016-09-08 | Efficient refrigeration or heat pump device and refrigerant flow adjusting method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610811750.6A CN106352600A (en) | 2016-09-08 | 2016-09-08 | Efficient refrigeration or heat pump device and refrigerant flow adjusting method thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106352600A true CN106352600A (en) | 2017-01-25 |
Family
ID=57859507
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610811750.6A Pending CN106352600A (en) | 2016-09-08 | 2016-09-08 | Efficient refrigeration or heat pump device and refrigerant flow adjusting method thereof |
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| CN (1) | CN106352600A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111854201A (en) * | 2019-04-28 | 2020-10-30 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
| CN111854207A (en) * | 2019-04-28 | 2020-10-30 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
| CN111854205A (en) * | 2019-04-28 | 2020-10-30 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
-
2016
- 2016-09-08 CN CN201610811750.6A patent/CN106352600A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111854201A (en) * | 2019-04-28 | 2020-10-30 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
| CN111854207A (en) * | 2019-04-28 | 2020-10-30 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
| CN111854205A (en) * | 2019-04-28 | 2020-10-30 | 青岛海尔智能技术研发有限公司 | Refrigerator equipment, refrigerating system and control method of refrigerating system |
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Application publication date: 20170125 |