CN106247659A - Heat-exchange device and heat pump assembly - Google Patents
Heat-exchange device and heat pump assembly Download PDFInfo
- Publication number
- CN106247659A CN106247659A CN201610162015.7A CN201610162015A CN106247659A CN 106247659 A CN106247659 A CN 106247659A CN 201610162015 A CN201610162015 A CN 201610162015A CN 106247659 A CN106247659 A CN 106247659A
- Authority
- CN
- China
- Prior art keywords
- pump
- heat
- liquid
- refrigerant
- extractor
- 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.)
- Pending
Links
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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
-
- 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/06—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure
- F25B1/08—Compression machines, plants or systems with non-reversible cycle with compressor of jet type, e.g. using liquid under pressure using vapour under pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
-
- 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
- F25B45/00—Arrangements for charging or discharging refrigerant
-
- 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
-
- 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
- F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
- F25B2341/001—Ejectors not being used as compression device
- F25B2341/0014—Ejectors with a high pressure hot primary flow from a compressor discharge
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/16—Receivers
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Jet Pumps And Other Pumps (AREA)
Abstract
The disclosure provides a kind of heat-exchange device and heat pump assembly.The heat-exchange device of the disclosure possesses refrigerant vapour supply source, ejector, extractor, the 1st pump, the 2nd pump, radiator and liquid path.1st pump is velocity profile pump, the liquid path being arranged between extractor and radiator.2nd pump is volume type pump, be arranged at liquid path from the outlet of the 1st pump interval to the entrance of the refrigerant liquid of ejector.
Description
Technical field
It relates to heat-exchange device and heat pump assembly.
Background technology
In the past, heat-exchange device was used at conditioner, freezing-cooling storeroom, water heater etc.
The refrigerating circulatory device of application in equipment.Patent Document 1 discloses one to use water as over the ground
The refrigerating circulatory device bearing minimum cold-producing medium in ball border.Figure 6 illustrates patent documentation 1 institute
Disclosed refrigerating circulatory device.
As shown in Figure 6, refrigerating circulatory device 100 possesses vaporizer 110, condenser 120, links and join
Pipe 130 and link pipe arrangement 150.The top of vaporizer 110 is connected to cold by linking pipe arrangement 130
The top of condenser 120.It is provided with compressor 140 linking pipe arrangement 130.The bottom of vaporizer 110
The bottom of condenser 120 it is connected to by linking pipe arrangement 150.Vaporizer 110 connects vaporizer side
Liquid path 160.Vaporizer side liquid path 160 is provided with load 180 and water supply pump 220.Cold
Condenser 120 connects condenser side liquid path 170.It is provided with at condenser side liquid path 170
Cooling tower 210 and cooling water pump 230.
Prior art literature
Patent documentation
Patent documentation 1: No. 4454456 publications of Japanese Patent Publication No.
Summary of the invention
That is, the disclosure provides a kind of heat-exchange device, possesses:
Refrigerant vapour supply source, its supply system refrigerant vapor；
Radiator, the refrigerant liquid of input is cooled down, and exports described refrigerant liquid by it；
Ejector, its accept from described refrigerant vapour supply source supply described refrigerant vapour and from
The described refrigerant liquid of described radiator output, generates described refrigerant vapour and described refrigerant liquid
Cold-producing medium mixed flow；
Extractor, it accepts the described cold-producing medium mixed flow exported from described ejector, from described refrigeration
Agent mixed flow is isolated described refrigerant liquid and stores, and by defeated for the described refrigerant liquid that stored
Go out；
Liquid path, consists of ring-type, described extractor, described radiator and described ejector
Being set in turn in this liquid path, described refrigerant liquid circulates in this liquid path；
1st pump, it is velocity profile pump, is arranged at the outlet of described extractor and entering of described radiator
Described liquid path between Kou, by described refrigerant liquid from described extractor to described radiator force feed；
And
2nd pump, it is volume type pump, is arranged at the discharge from described 1st pump of described liquid path
Mouth is to the interval of the entrance of the described refrigerant liquid of described ejector.
According to above-mentioned technology, it is possible to reduce the height from the 1st pump (velocity profile pump) to extractor, institute
So that heat-exchange device miniaturization can be made.Therefore, it is possible to maximization same of suppression heat-exchange device
Time, improve the performance of heat-exchange device.
Accompanying drawing explanation
Fig. 1 is the structure chart of the heat-exchange device in embodiment 1.
Fig. 2 is the profile of ejector.
Fig. 3 is the structure chart of the heat-exchange device in embodiment 2.
Fig. 4 is the structure chart of the heat pump assembly in embodiment 3.
Fig. 5 is the structure chart of the heat pump assembly in embodiment 4.
Fig. 6 is the structure chart of conventional refrigerating circulatory device.
Label declaration
11: refrigerant vapour supply source
12: ejector
13: extractor
14: the 1 pumps
15: the 2 pumps
16: radiator
17: the 1 liquid paths
18: the 3 pumps
19: vaporizer
31: compressor (refrigerant vapour supply source)
32: go back to fluid path footpath
200,300: heat-exchange device
400,500: heat pump assembly
Detailed description of the invention
Owing to the environmental consciousness such as global warming are improved, so seeking to improve heat friendship further
Changing device or the performance of heat pump assembly.But, for improving the performance of heat-exchange device or heat pump assembly
Technology often cause the maximization of device.
(as the basic opinion of the disclosure)
In order to improve the performance of heat-exchange device or heat pump assembly, it is desirable to have improve refrigeration for efficiently
The technology of the pressure of agent.Then, as being used for improving efficiently the technology of the pressure of cold-producing medium, this Shen
Inventor please have studied the technology that condenser replaces to condensation injector and extractor.Extractor is carried on a shoulder pole
The negative work only extracting refrigerant liquid from the cold-producing medium stream of the biphase state of autocondensation ejector discharge
With.It is made to condense by being boosted efficiently by the cold-producing medium discharged from compressor with condensation injector,
The acting of compressor can be reduced, thus improve COP (the Coefficient Of of system
Performance: the coefficient of performance).
But, present inventor finds in the system that have employed above-mentioned technology, this system with
Past system is compared, and needs the pump discharge head of more than 10 times.That is, in order to improve the COP of system,
The boosting efficiency making pump and ejector is needed to exceed the boosting efficiency of compressor.But, in order to maintain
Pump discharge head is increased, needed for the cavitation erosion (cavitation) of suppression pump under the state of the high efficiency of pump
Pressure head (required inlet head: NPSHr (Net Positive Suction Head required)) meeting
It is significantly increased.If required pump discharge head becomes 10 times, then must also can become about by inlet head
10 times.This NPSHr needs the height (water by liquid level internal from pump intake to extractor
Position pressure head) guarantee.Such as, in the conventional refrigerating circulatory device described in patent documentation 1,
Ensure that the water level pressure head of 1m.Will in the conventional refrigerating circulatory device described in patent documentation 1
In the case of condenser 120 has replaced to ejector and extractor, need the water level pressure head of more than 10m.
This can cause the maximization of system.
As it has been described above, inventors herein have recognized that following new problem: condenser is being replaced
Condensation injector and extractor is become to realize being configured to the system of refrigerant vapour supply source by pump power
Refrigerant vapor boost efficiently and condense heat-exchange device time, it is difficult to accomplish both to maintain the high efficiency of pump
The maximization of the most anti-locking system.Present inventor contemplates following with this new problem as clue
The invention of illustrated each technical scheme.
The heat-exchange device of the 1st technical scheme of the disclosure, possesses:
Refrigerant vapour supply source, its supply system refrigerant vapor；
Radiator, the refrigerant liquid of input is cooled down, and exports described refrigerant liquid by it；
Ejector, its accept from described refrigerant vapour supply source supply described refrigerant vapour and from
The described refrigerant liquid of described radiator output, generates described refrigerant vapour and described refrigerant liquid
Cold-producing medium mixed flow；
Extractor, it accepts the described cold-producing medium mixed flow exported from described ejector, from described refrigeration
Agent mixed flow is isolated described refrigerant liquid and stores, and by defeated for the described refrigerant liquid that stored
Go out；
Liquid path, consists of ring-type, described extractor, described radiator and described ejector
Being set in turn in this liquid path, described refrigerant liquid circulates in this liquid path；
1st pump, it is velocity profile pump, is arranged at the outlet of described extractor and entering of described radiator
Described liquid path between Kou, by described refrigerant liquid from described extractor to described radiator force feed；
And
2nd pump, it is volume type pump, is arranged at the discharge from described 1st pump of described liquid path
Mouth is to the interval of the entrance of the described refrigerant liquid of described ejector.
According to the 1st technical scheme, the boosting amplitude of the 1st pump can be set to and the NPSHr of the 2nd pump
Suitable boosting amplitude.Due to the NPSHr of the 2nd pump compared with the required pressure of ejector sufficiently small,
So the boosting amplitude requiring the 1st pump is the least, the NPSHr of the 1st pump is the least.Therefore, pass through
Operating speed type pump is as the 1st pump, it is possible to boost efficiently with little NPSHr.It addition,
Owing to the 2nd pumping enters the refrigerant liquid after boosting with the boosting amplitude suitable for NPSHr with the 2nd pump,
So cause the risk of hydraulic performance decline also to reduce in the 2nd pump because of cavitation erosion.Therefore, by using height
The volume type pump of effect is as the 2nd pump, it is possible to refrigerant liquid boosts to ejector must press efficiently
Power.Therefore, according to present embodiment, it is possible to by reducing to come from the height of the 1st pump to extractor
While seeking the miniaturization of heat-exchange device, efficiently refrigerant liquid is boosted to the required of ejector
Pressure.
In the 2nd technical scheme of the disclosure, such as, the heat-exchange device of the 1st technical scheme also has
Standby 3rd pump, the 3rd pump is velocity profile pump, be arranged at described liquid path from described 1st pump
Outlet is to the interval of described 2nd pump intake.According to the 2nd technical scheme, owing to one can be entered
Step reduces the boosting amplitude of the 1st pump, it is possible to make the NPSHr of the 1st pump become less, it is possible to
Make the further miniaturization of heat-exchange device.
In the 3rd technical scheme of the disclosure, such as, the 1st technical scheme or the 2nd technical scheme
Described 2nd pump of heat-exchange device is arranged at outlet the entering to described radiator from described 1st pump
Described liquid path between Kou.
In the 4th technical scheme of the disclosure, such as, in the 1st technical scheme～the 3rd technical scheme
Described 1st pump of the heat-exchange device of arbitrary technical scheme be in described liquid path in vertical side
Minimum position.
In the 5th technical scheme of the disclosure, such as, in the 1st technical scheme～the 4th technical scheme
Described 1st pump of the heat-exchange device of arbitrary technical scheme and the 2nd pump are positioned at same in vertical
Highly.
In the 6th technical scheme of the disclosure, such as, in the 1st technical scheme～the 5th technical scheme
The required inlet head of described 1st pump of the heat-exchange device of arbitrary technical scheme is than described 2nd pump
Required inlet head is little, and the required inlet head of the 2nd pump described in the boosting Amplitude Ratio of described 1st pump
Greatly.
In the 7th technical scheme of the disclosure, such as, the 1st technical scheme～the 6th technical scheme
The efficiency of pump of described 2nd pump of heat-exchange device is higher than the efficiency of pump of described 1st pump.Additionally, the " the 2nd
The efficiency of pump of pump is higher than the efficiency of pump of described 1st pump " refer to that the maximal efficiency of the 2nd pump is than the 1st pump
Maximal efficiency is high.
In the 8th technical scheme of the disclosure, such as, the 1st technical scheme～the 7th technical scheme
The described cold-producing medium of heat-exchange device saturated vapor pressure ratio atmospheric pressure at 20 DEG C ± 15 DEG C is low.
The heat pump assembly of the 9th technical scheme of the disclosure possesses the 1st technical scheme～the 8th technical scheme
In the heat-exchange device of arbitrary technical scheme, described refrigerant vapour supply source is the cold-producing medium to input
The compressor that steam is compressed and exports to described ejector.According to the 3rd technical scheme, it is possible to
To the effect identical with the 1st technical scheme.
In the 10th technical scheme of the disclosure, such as, the heat pump assembly of the 9th technical scheme is also equipped with:
Vaporizer, it generates the described refrigerant vapour that supply to described compressor；With return fluid path footpath,
Described extractor is connected by it with described vaporizer, is used for making quality export and warp with from described vaporizer
The quality of the described refrigerant vapour of described extractor it is fed into by described compressor and described ejector
Equal described refrigerant liquid returns described vaporizer from described extractor.If obtaining by going back to fluid path footpath
The amount of the refrigerant liquid of vaporizer and the balance of the amount of the refrigerant liquid of extractor, then can make heat pump fill
Put and stably operate.
Hereinafter, embodiment of this disclosure illustrates referring to the drawings.The disclosure is not limited to following
Embodiment.
(embodiment 1)
As it is shown in figure 1, the heat-exchange device 200 of present embodiment possess refrigerant vapour supply source 11,
Ejector 12, extractor the 13, the 1st pump the 14, the 2nd pump 15, radiator the 16 and the 1st liquid road
Footpath 17.1st liquid path 17 is configured to ring-type, including pipe arrangement 17a～17e.1st liquid path
17 pass through by pipe arrangement 17a～17e successively by ejector 12, extractor the 13, the 1st pump the 14, the 2nd pump
15 and radiator 16 connect into ring-type and constitute.
As long as refrigerant vapour supply source 11 can be by refrigerant vapour (cold-producing medium of gas phase) to injection
Device 12 supplies, and there is no particular limitation.Refrigerant vapour supply source 11 is for example as heat pump
The compressor of the element of device.Refrigerant vapour supply source 11 can also be to utilize factory's heat extraction to make
Cold-producing medium (such as water) vaporization the vaporizer as refrigerant vapour output.
As in figure 2 it is shown, ejector 12 has the 1st nozzle the 23, the 2nd nozzle 25, mixing unit 27
And diffusion part 28.1st nozzle 23 is connected to radiator 16 by pipe arrangement 17e.From radiator 16
The refrigerant liquid (cold-producing medium of liquid phase) flowed out is fed into the by pipe arrangement 17e as driving stream
1 nozzle 23.2nd nozzle 25 is connected to refrigerant vapour by pipe arrangement 26b (steam path) and supplies
Source 11.Reduced by radiator 16 from the temperature of the liquid refrigerant of the 1st nozzle 23 injection.From
1st nozzle 23 accelerate the refrigerant liquid that ejects and from the 2nd nozzle 25 while expand and
Accelerate while the refrigerant vapour ejected mixes in mixing unit 27.Then, the 1st condensation and the is produced
2 condensations, the condensation of the temperature difference that the 1st condensation is due between refrigerant liquid and refrigerant vapour,
2nd condensation is due to conveying based on the energy between refrigerant liquid and refrigerant vapour and cold-producing medium
The condensation of the boosting effect of the conveying of the momentum between liquid and refrigerant vapour.Supply from refrigerant vapour
The refrigerant vapour of source 11 supply is inhaled into the 2nd nozzle 25 continuously by pipe arrangement 26b.It addition,
The cold-producing medium mixed flow that aridity (mass dryness fraction) is little is generated through the condensation process in 2 stages.Diffusion
Portion 28 makes static pressure recover by making cold-producing medium mixed flow slow down.Ejector 12 at such structure
In, the temperature and pressure of cold-producing medium rises.
It addition, ejector 12 possesses needle valve 29 and servo actuator 30.Needle valve 29 and servo
Actuator 30 is the flow regulator for adjusting the flow as the refrigerant liquid driving stream.Pass through pin
Type valve 29, it is possible to the sectional area in the aperture (orifice) on the top of change the 1st nozzle 23.By watching
Take actuator 30, it is possible to the position of regulation needle valve 29.Thereby, it is possible to adjust at the 1st nozzle 23
The flow of the refrigerant liquid of flowing.
Extractor 13 accepts cold-producing medium mixed flow from ejector 12, extracts from cold-producing medium mixed flow
Refrigerant liquid, and store.It is to say, extractor 13 is undertaken, refrigerant liquid and cold-producing medium are steamed
Edema caused by disorder of QI from effect.Refrigerant liquid is the most only taken out from extractor 13.Extractor 13 is such as by having
The pressure vessel having thermal insulation is formed.But, as long as refrigerant liquid can be extracted, extractor 13
Structure there is no particular limitation.
1st liquid path 17 is to make from the refrigerant liquid of extractor 13 output via radiator 16 and spray
Emitter 12 and return to the path of extractor 13.1st path 17 is configured to ring-type.Extractor 13,
Radiator 16 and ejector 12 are set in turn in the 1st path 17.Refrigerant liquid is in the 1st path 17
Middle circulation.
1st pump 14 is arranged between extractor 13 and radiator 16 (specifically, extractor 13
Outlet and the entrance of radiator 16 between) the 1st liquid path 17.1st pump 14 will be from extraction
The refrigerant liquid of device 13 output is to radiator 16 force feed.
In the present embodiment, the 1st pump 14 is velocity profile pump.Velocity profile pump is the fluid (system to input
Cryogen liquid) give speed, the speed given is carried out static pressure recovery thus improves pressure, and should
The pump that fluid is sent.The example of velocity profile pump includes centrifugal pump, diagonal pumps, axial-flow pump etc..1st pump
14 are configured at from the suction inlet of the 1st pump 14 height to the liquid level of the refrigerant liquid of the inside of extractor 13
The position that degree H than the 1st pump 14 is big for NPSHr.
2nd pump 15 is arranged at the outlet from the 1st pump 14 of the 1st liquid path 17 to ejector
The interval of the liquid entrance (entrance of refrigerant liquid, the entrance of driving stream) of 12.In the present embodiment,
2nd pump 15 is arranged at the 1st liquid road between outlet and the entrance of radiator 16 of the 1st pump 14
Footpath 17.In the case of the 2nd pump 15 is configured at such position, it is possible to be reduced as far as from the 1st
The outlet of pump 14 is to the pressure loss in the interval of the suction inlet of the 2nd pump 15.Its result, the 2nd
Pump 15 causes the probability of cavitation erosion (cavitation) to reduce further.It addition, waited when starting
The probability crossing the cold-producing medium that phase the 2nd pump 15 sucks gas phase also reduces.But, the 2nd pump 15 also may be used
With the 1st liquid path 17 being arranged between the outlet of radiator 16 and the liquid entrance of ejector 12.
It is to say, the 2nd pump 15 can also be positioned at the downstream of radiator 16.
In the present embodiment, the 2nd pump 15 is volume type pump.Volume type pump is the fluid for input
(refrigerant liquid) makes volume change improve pressure, thus sends the pump of this fluid.Volume type pump
Example includes piston pump, plunger displacement pump, gear pump, lobe pump, vane pump, drum pump etc..
In the present embodiment, the 1st pump 14 be positioned in the 1st liquid path 17 in vertical
Minimum position.The position relationship of the 1st pump the 14 and the 2nd pump 15 in vertical is the most particularly
Limit.It is preferred, however, that the 2nd pump 15 is in the height identical with the 1st pump 14 in vertical
Degree.
According to present embodiment, refrigerant liquid is boosted up to the 2nd pump 15 in the 1st pump 14 and will not draw
Play the pressure of cavitation erosion.The most important performance requiring the 1st pump 14 is to be not easy the NPSHr with little
Cause cavitation erosion.It is to say, as the 1st pump 14, velocity profile pump specific volume type pump is more suitable for.Speed
The paramount pressure although type pump is difficult to boost refrigerant liquid, but be not easy to cause with little NPSHr
Cavitation erosion.On the other hand, the most important performance required the 2nd pump 15 is efficiently and can be by cold-producing medium
The pressure that liquid boosting is paramount.It is to say, as the 2nd pump 15, volume type pump specific rate type pump is suitableeer
Close.The NPSHr of the 1st pump 14 is less than the NPSHr of the 2nd pump 15.(NPSHr of the 1st pump 14)
The value e.g. about 0.1 of/(NPSHr of the 2nd pump 15).
Radiator 16 is handed over by the known heat such as fin tube type heat exchanger, shell-and-tube exchanger, cooling tower
Parallel operation is formed.
Then, the work to heat-exchange device 200 illustrates.
First, ejector 12 accept from refrigerant vapour supply source 11 discharge refrigerant vapour and from
The refrigerant liquid of radiator 16 output, generates cold-producing medium mixed flow.The refrigeration generated by ejector 12
Agent mixed flow is imported into extractor 13.In extractor 13, extract refrigerant liquid and store.Storage
The refrigerant liquid being stored in extractor 13 is supplied via the 1st pump the 14, the 2nd pump 15 and radiator 16
It is given to ejector 12.In order to suppress the loss of the effective head caused by the crushing of pipe arrangement, the 1st pump 14
The 1st liquid path 17 being configured between the outlet of extractor 13 and the entrance of radiator 16.Store
First refrigerant liquid in extractor 13 is inhaled into the 1st pump 14, boosted in the 1st pump 14.By
Refrigerant liquid after 1st pump 14 boosting passes through the liquid entrance of the outlet at the 1st pump 14 and ejector 12
Between the 1st liquid path 17 configuration the 2nd pump 15 and the most boosted.2nd pump 15 also may be used
With the 1st liquid path 17 being configured between the outlet of radiator 16 and the liquid entrance of ejector 12.
In the present embodiment, extractor 13 refrigerant liquid extracted is being boosted by the 1st pump 14
After, boosted by the 2nd pump 15 further.The boosting amplitude of the 1st pump 14 can be set to and the 2nd pump
The boosting amplitude suitable for NPSHr of 15.Due to the 2nd pump 15 NPSHr and ejector 12 must
Pressure is needed to compare sufficiently small, so the boosting amplitude requiring the 1st pump 14 is the least, the 1st pump 14
NPSHr is the least.Therefore, by operating speed type pump as the 1st pump 14, it is possible to little NPSHr
Boost efficiently.Further, since the 2nd pump 15 sucks with the NPSHr phase with the 2nd pump 15
When boosting amplitude boosting after refrigerant liquid, so causing under performance because of cavitation erosion in the 2nd pump 15
The risk of fall also reduces.Therefore, by using high efficiency volume type pump as the 2nd pump 15, it is possible to
Efficiently refrigerant liquid is boosted to the required pressure of ejector 12.Therefore, according to present embodiment,
Heat-exchange device 200 can sought from the height of the 1st pump 14 to extractor 13 by reduction
While miniaturization, efficiently refrigerant liquid is boosted to the required pressure of ejector 12.
(embodiment 2)
As it is shown on figure 3, the heat-exchange device 300 of present embodiment is except possessing with reference to Fig. 1 explanation
Outside the structure of heat-exchange device 200, it is also equipped with the 3rd pump 18.In the present embodiment, the 1st liquid
Body path 17 is configured to ring-type, including pipe arrangement 17a～17f.1st liquid path 17 is by by pipe arrangement
17a～17f is successively by ejector 12, extractor the 13, the 1st pump the 14, the 3rd pump 18, radiator 16
And the 2nd pump 15 connect into ring-type and constitute.
3rd pump 18 is arranged at the 1st liquid path 17 between the 1st pump the 14 and the 2nd pump 15.In detail
For Xi, the 3rd pump 18 is arranged at the outlet from the 1st pump 14 of the 1st liquid path 17 to the 2nd
The interval of the suction inlet of pump 15.More specifically, the 3rd pump 18 is arranged at the discharge from the 1st pump 14
Mouth is to the interval of the 1st liquid path 17 of the entrance of radiator 16.3rd pump 18 is velocity profile pump.
Alternatively, it is also possible to the 1st liquid path 17 between the 1st pump the 14 and the 2nd pump 15 is additionally provided with 1
Individual or multiple pumps.It is to say, at the 1st liquid path 17 from the outlet of the 1st pump 14 to
The interval of the suction inlet of 2 pumps 15, it is also possible to along refrigerant liquid flow direction be configured with bag successively
Include multiple pumps of the 3rd pump 18～N the pump integer of more than 4 (N be).These pumps can be speed
Type pump.
In heat-exchange device 300, the 2nd pump 15 is configured at outlet and the ejector 12 of radiator 16
Liquid entrance between.But, the 2nd pump 15 can also be configured at the outlet of above-mentioned N pump with scattered
Between the entrance of hot device 16.That is, the 3rd pump 18 and the pump that adds can with the position of radiator 16 without
It is configured at closing between outlet and the suction inlet of the 2nd pump 15 of the 1st pump 14.
According to present embodiment, it is configured with multiple velocity profile pump at the 1st liquid path 17.If the speed of making
Type pump multipolarity, then can provide speed from each pump to the fluid (refrigerant liquid) passed through.Therefore,
Compared with the situation being provided only with 1 velocity profile pump, it is possible to the velocity profile pump that multipolarity is greatly improved is whole
The efficiency of body.The total NPSHr of multiple velocity profile pumps is less than the NPSHr of the 2nd pump 15.(multiple
Total NPSHr of velocity profile pump)/the value e.g. less than 0.1 of (NPSHr of the 2nd pump 15).
According to present embodiment, owing to the boosting amplitude of the 1st pump 14 can be reduced further, so energy
The NPSHr enough making the 1st pump 14 becomes less, it is possible to make the further miniaturization of heat-exchange device 300.
(variation)
In the heat-exchange device 300 shown in the heat-exchange device 200 and Fig. 3 shown in Fig. 1, it is possible to
To be filled with the saturated vapour pressure under room temperature (Japanese Industrial Standards: 20 DEG C ± 15 DEG C/JIS Z8703)
Cold-producing medium for negative pressure (pressure that absolute pressure is forced down than air).As such cold-producing medium, can lift
Go out to comprise water, alcohol or the ether cold-producing medium as main component.When heat-exchange device 200,300 operates,
Pressure ratio air within heat-exchange device 200,300 forces down.Going out of refrigerant vapour supply source 11
Mouthful pressure for instance in 5～15kPaA scope.As cold-producing medium, it is also possible to freeze for preventing
Use etc. reason and comprise water as main component and be mixed with 10～40% when being converted into quality %
The cold-producing medium of ethylene glycol, Na イ Block ラ イ Application (Japan registration trade mark), inorganic salts etc.." mainly become
Point " refer to comprise most compositions under mass ratio.Heat-exchange device 200,300 is filled just like
In the case of upper described cold-producing medium, it is the cold-producing medium of malleation with the saturated vapour pressure being filled with under room temperature
Situation compare, system has the tendency of maximization.Therefore, technology disclosed in this specification for
The system employing the cold-producing medium that the saturated vapour pressure under room temperature is negative pressure can bring more significant effect.
(embodiment 3)
Fig. 4 is the structure chart of the heat pump assembly in embodiment 3.The heat pump assembly 400 of present embodiment
(refrigerating circulatory device) possesses the 1st heat exchange unit the 40, the 2nd heat exchange unit 42, compressor
31 and steam path 26.1st heat exchange unit the 40 and the 2nd heat exchange unit 42 is formed respectively and dissipates
Hot side loop and heat absorbing side loop.The refrigerant vapour generated by the 2nd heat exchange unit 42 is via compression
Machine 31 and steam path 26 are fed into the 1st heat exchange unit 40.
Compressor 31, the downstream part 26b of steam path 26 and the 1st heat exchange unit 40 and ginseng
The heat-exchange device 200 illustrated according to Fig. 1 is corresponding.It is to say, heat pump assembly 400 possesses heat exchange
Device 200.Compressor 31 is corresponding with refrigerant vapour supply source 11, the refrigerant vapour to input
It is compressed and exports to ejector 12.Therefore, also can obtain in heat pump assembly 400 before
The effect that in embodiment 1, the effect of explanation is identical.
For the 1st heat exchange unit 40, can quote relevant with the heat-exchange device 200 of embodiment 1
Explanation.
2nd heat exchange unit 42 has vaporizer 19, pump 20 (vaporizer side pump) and heat exchange
Device 21.Vaporizer 19 stores refrigerant liquid, by making refrigerant liquid evaporation generate and be compressed
The refrigerant vapour of machine 31 compression.Vaporizer 19, pump 20 and heat exchanger 21 pass through pipe arrangement
22a～22c and connect into ring-type.Vaporizer 19 is such as formed by the pressure vessel with thermal insulation.Join
Pipe 22a～22c is formed and makes the refrigerant liquid being stored in vaporizer 19 circulate via heat exchanger 21
2nd liquid path 22.Pump 20 is arranged at the liquid outlet of vaporizer 19 and the entrance of heat exchanger 21
Between the 2nd liquid path 22.By pump 20, the refrigerant liquid being stored in vaporizer 19 is boosted,
And heat exchanger 21 force feed.The discharge pressure ratio air of pump 20 forces down.Pump 20 is configured at from this pump
The suction inlet of 20 to the height He of the liquid level of the refrigerant liquid in vaporizer 19 than required inlet head
(NPSHr) big position.
Heat exchanger 21 is by the known heat exchanger shape such as finned type heat exchanger, shell-and-tube exchanger
Become.
In the present embodiment, vaporizer 19 is to make by following in the 2nd liquid path 22 in inside
Ring and heated after the heat exchanger of refrigerant liquid direct evaporation.It is stored in the cold-producing medium of vaporizer 19
Liquid directly contacts with the refrigerant liquid of circulation in the 2nd liquid path 22.It is to say, vaporizer
Part of refrigerant liquid in 19 is heated by heat exchanger 21, is used as the cold-producing medium to saturation
Liquid carries out the thermal source heated.The upstream extremity of pipe arrangement 22a is preferably attached to the bottom of vaporizer 19.Pipe arrangement
The dirty end of 22c is preferably attached to the pars intermedia of vaporizer 19.Additionally, the 2nd heat exchange unit 42
The refrigerant liquid that can also be configured to be stored in vaporizer 19 will not follow with in the 2nd liquid path 22
Other refrigerant liquids mixing of ring.Such as, at vaporizer 19, there is heat as shell-and-tube exchanger
In the case of exchange structure, it is possible to by the thermal medium of circulation in the 2nd liquid path 22 to being stored in steaming
Send out the refrigerant liquid heating of device 19 and make it evaporate.In heat exchanger 21, flowing is used for adding thermmal storage
Thermal medium in the refrigerant liquid of vaporizer 19.
Steam path 26 has upstream portion 26a and downstream part 26b.Configure at steam path 26
There is compressor 31.The top of vaporizer 19 is connected to by upstream portion 26a of steam path 26
The suction inlet of compressor 31.The outlet of the compressor 31 downstream part 26b by steam path 26
And it is connected to the 2nd nozzle 25 of ejector 12.Compressor 31 is centrifugal compressor or positive displacement pressure
Contracting machine.Multiple compressor can also be provided with at steam path 26.Compressor 31 passes through upstream portion
26a and suck refrigerant vapour from the vaporizer 19 of the 2nd heat exchange unit 42, and compress it.
Refrigerant vapour after compression is fed into ejector 12 by downstream part 26b.
According to present embodiment, ejector 12 improves the temperature and pressure of cold-producing medium.Due to can
Reduce the acting that compressor 31 should undertake, it is possible to the compression in significantly cutting down compressor 31
While Bi, reach the efficiency of as in the past or above heat pump assembly 400.It addition,
It also is able to make heat pump assembly 400 miniaturization.
Heat pump assembly 400 is also equipped with for making cold-producing medium return the 2nd heat friendship from the 1st heat exchange unit 40
That changes unit 42 goes back to fluid path footpath 32 (liquid back pipe).In the present embodiment, extractor 13 and evaporation
Device 19 connects, so that the cold-producing medium of extractor 13 can will be stored in steaming by going back to fluid path footpath 32
Send out device 19 to carry.Typically, the bottom of extractor 13 and the bottom of vaporizer 19 are by going back to fluid path footpath
32 and connect.Refrigerant liquid by return fluid path footpath 32 and from extractor 13 Returning evaporimeter 19.Returning
Fluid path footpath 32 can also be provided with the expansion mechanism such as capillary tube, expansion valve.
Return fluid path footpath 32 be configured to be connected extractor 13 with vaporizer 19, and make quality with by pressing
The refrigerant vapour amount (mass flow) that contracting machine 31 transports to extractor 13 from vaporizer 19 is equal
Refrigerant liquid returns from extractor 13 Returning evaporimeter 19.If obtaining vaporizer by going back to fluid path footpath 32
The amount of the refrigerant liquid of 19 and the balance of the amount of the refrigerant liquid of extractor 13, then can make heat pump fill
Put 400 stably to operate.But, it is being stored in the refrigerant liquid of vaporizer 19 and extractor 13
Measure situation sufficiently large compared with the operating by heat pump assembly 400 and the refrigerant vapour amount transported
Under, it is also possible to omit go back to fluid path footpath 32.
Can be from the optional position branch of the 1st heat exchange unit 40 additionally, go back to fluid path footpath 32.Such as,
Going back to fluid path footpath 32 can be from the pipe arrangement 17a branch connecting ejector 12 and extractor 13, it is also possible to from
The top branch of extractor 13.It is unnecessary that 1st heat exchange unit 40 is configured to suitably to discharge
Cold-producing medium, the 2nd heat exchange unit 42 is configured to can suitably supplement cold-producing medium.
In heat pump assembly 400, as heat-exchange device 200, the saturated steaming under room temperature can be used
Air pressure is the cold-producing medium of negative pressure.
(embodiment 4)
Fig. 5 is the structure chart of the heat pump assembly in embodiment 4.The heat pump assembly 500 of present embodiment
(refrigerating circulatory device) possesses the 1st heat exchange unit the 41, the 2nd heat exchange unit 42, compressor
31 and steam path 26.1st heat exchange unit the 41 and the 2nd heat exchange unit 42 is formed respectively and dissipates
Hot side loop and heat absorbing side loop.The refrigerant vapour generated by the 2nd heat exchange unit 42 is via compression
Machine 31 and steam path 26 are fed into the 1st heat exchange unit 41.
Compressor 31, the downstream part 26b of steam path 26 and the 1st heat exchange unit 41 and ginseng
The heat-exchange device 300 illustrated according to Fig. 3 is corresponding.It is to say, heat pump assembly 500 possesses heat exchange
Device 300.Compressor 31 is corresponding with refrigerant vapour supply source 11, the refrigerant vapour to input
It is compressed, and exports to ejector 12.Therefore, also can obtain in heat pump assembly 500 with upper
State the effect that in embodiment 2, the effect of explanation is identical.
For the 1st heat exchange unit 41, can quote relevant with the heat-exchange device 300 of embodiment 2
Explanation.It addition, the details of the 2nd heat exchange unit 42 are identical with explanation in embodiment 3.
For heat pump assembly 500, as heat-exchange device 300, the saturated steaming under room temperature can be used
Air pressure is the cold-producing medium of negative pressure.
As mentioned above, heat-exchange device disclosed in this specification and heat pump assembly possess the 1st
Pump 14 (velocity profile pump) and the 2nd pump 15 (volume type pump).The boosting amplitude of the 1st pump 14 can set
The boosting amplitude suitable for NPSHr of Cheng Yu 2 pump 15.NPSHr and spray due to the 2nd pump 15
The required pressure of emitter 12 is compared sufficiently small, so the boosting amplitude required by the 1st pump 14 is the least,
The NPSHr of the 1st pump 14 is the least.Therefore, it is possible to reduce the height from the 1st pump 14 to extractor 13
Degree.I.e. it is capable of reduce heat-exchange device or the height of heat pump assembly and make system entirety small-sized
Change.
According to technology disclosed in this specification, using the teaching of the invention it is possible to provide small-sized and high efficiency heat pump assembly.Also
That is, it also is able to use heat pump assembly 400,500 to carry out air in the building that installation space is little
Regulation.It addition, be not only air-conditioning purposes, heat pump assembly 400,500 is being used for supplying the feelings of hot water
Under condition, it is also possible to carry out hot water supply at higher temperature.
Heat-exchange device disclosed in this specification and heat pump assembly are applicable to utilize the warm water system of steam
Conditioner, the water heaters etc. such as thermal, domestic air conditioning, business air conditioner.
Claims (10)
1. a heat-exchange device, possesses:
Refrigerant vapour supply source, its supply system refrigerant vapor；
Radiator, the refrigerant liquid of input is cooled down, and exports described refrigerant liquid by it；
Ejector, its accept from described refrigerant vapour supply source supply described refrigerant vapour and from
The described refrigerant liquid of described radiator output, generates described refrigerant vapour and described refrigerant liquid
Cold-producing medium mixed flow；
Extractor, it accepts the described cold-producing medium mixed flow exported from described ejector, from described refrigeration
Agent mixed flow isolated described refrigerant liquid and stores, and exporting the described refrigerant liquid stored；
Liquid path, consists of ring-type, described extractor, described radiator and described ejector
Being set in turn in this liquid path, described refrigerant liquid circulates in this liquid path；
1st pump, it is velocity profile pump, is arranged at the outlet of described extractor and entering of described radiator
Described liquid path between Kou, by described refrigerant liquid from described extractor to described radiator force feed；
And
2nd pump, it is volume type pump, is arranged at the discharge from described 1st pump of described liquid path
Mouth is to the interval of the entrance of the described refrigerant liquid of described ejector.
Heat-exchange device the most according to claim 1,
Being also equipped with the 3rd pump, the 3rd pump is velocity profile pump, be arranged at described liquid path from described
The outlet of the 1st pump is to the interval of described 2nd pump intake.
Heat exchanger the most according to claim 1 and 2,
Described 2nd pump is arranged at from the outlet of described 1st pump to the entrance of described radiator
Described liquid path.
4. according to the heat exchanger according to any one of claims 1 to 3,
The position minimum in vertical that described 1st pump is in described liquid path.
5. according to the heat exchanger according to any one of Claims 1 to 4,
Described 1st pump and the 2nd pump are positioned at sustained height in vertical.
6. according to the heat exchanger according to any one of Claims 1 to 5,
The required inlet head of described 1st pump is less than the required inlet head of described 2nd pump and described
Described in the boosting Amplitude Ratio of the 1st pump, the required inlet head of the 2nd pump is big.
7. according to the heat exchanger according to any one of claim 1～6,
The efficiency of pump of described 2nd pump is higher than the efficiency of pump of described 1st pump.
8. according to the heat exchanger according to any one of claim 1～7,
Described cold-producing medium saturated vapor pressure ratio atmospheric pressure at 20 DEG C ± 15 DEG C is low.
9. a heat pump assembly, possesses the heat-exchange device according to any one of claim 1～8, its
In,
Described refrigerant vapour supply source is that the refrigerant vapour to input is compressed and to described injection
The compressor of device output.
Heat pump assembly the most according to claim 9, is also equipped with:
Vaporizer, it generates the described refrigerant vapour that supply to described compressor；With
Going back to fluid path footpath, described extractor is connected by it with described vaporizer, be used for making quality with from described
Vaporizer output is also supplied to the described system of described extractor via described compressor and described ejector
The described refrigerant liquid that the quality of refrigerant vapor is equal returns described vaporizer from described extractor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015-116413 | 2015-06-09 | ||
| JP2015116413 | 2015-06-09 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106247659A true CN106247659A (en) | 2016-12-21 |
Family
ID=55745676
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610162015.7A Pending CN106247659A (en) | 2015-06-09 | 2016-03-21 | Heat-exchange device and heat pump assembly |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20160363351A1 (en) |
| EP (1) | EP3106783A1 (en) |
| JP (1) | JP2017003252A (en) |
| CN (1) | CN106247659A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113418310A (en) * | 2021-06-22 | 2021-09-21 | 广东海悟科技有限公司 | Overall process anti-cavitation refrigeration system |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6237942B1 (en) * | 2017-01-30 | 2017-11-29 | 富士通株式会社 | Immersion cooling device |
| JP6781066B2 (en) * | 2017-02-21 | 2020-11-04 | 三菱重工サーマルシステムズ株式会社 | Refrigerant system with direct contact heat exchanger and how to control the refrigerant system |
| WO2020097263A1 (en) * | 2018-11-06 | 2020-05-14 | Evapco, Inc. | Direct expansion evaporator with vapor ejector capacity boost |
| US11162717B2 (en) | 2018-12-20 | 2021-11-02 | Johnson Controls Technology Company | Supplemental cooling for an HVAC system |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003176958A (en) * | 2001-10-04 | 2003-06-27 | Denso Corp | Ejector cycle |
| CN1475716A (en) * | 2002-07-08 | 2004-02-18 | 株式会社电装 | Injector circulation |
| CA2671914A1 (en) * | 2009-07-13 | 2011-01-13 | Zine Aidoun | A jet pump system for heat and cold management, apparatus, arrangement and methods of use |
| WO2014057656A1 (en) * | 2012-10-10 | 2014-04-17 | パナソニック株式会社 | Heat exchanging device and heat pump |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4716044A (en) * | 1986-01-31 | 1987-12-29 | Clemson University | Process for obtaining juices from fruits containing same |
| JP4454456B2 (en) * | 2004-09-30 | 2010-04-21 | 三建設備工業株式会社 | Refrigeration system for steam compression refrigerator |
| WO2012147366A1 (en) * | 2011-04-28 | 2012-11-01 | パナソニック株式会社 | Freezer |
| DE102012011278A1 (en) * | 2012-06-08 | 2013-12-12 | Stiebel Eltron Gmbh & Co. Kg | Ejector for refrigerant circuit of heat pump, has drive flow nozzle, which has opening in wall, where hole closer is arranged on wall, and opening is opened in position of hole closer |
-
2016
- 2016-03-21 CN CN201610162015.7A patent/CN106247659A/en active Pending
- 2016-03-22 US US15/076,649 patent/US20160363351A1/en not_active Abandoned
- 2016-03-29 JP JP2016065585A patent/JP2017003252A/en active Pending
- 2016-04-12 EP EP16164946.2A patent/EP3106783A1/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003176958A (en) * | 2001-10-04 | 2003-06-27 | Denso Corp | Ejector cycle |
| CN1475716A (en) * | 2002-07-08 | 2004-02-18 | 株式会社电装 | Injector circulation |
| CA2671914A1 (en) * | 2009-07-13 | 2011-01-13 | Zine Aidoun | A jet pump system for heat and cold management, apparatus, arrangement and methods of use |
| WO2014057656A1 (en) * | 2012-10-10 | 2014-04-17 | パナソニック株式会社 | Heat exchanging device and heat pump |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113418310A (en) * | 2021-06-22 | 2021-09-21 | 广东海悟科技有限公司 | Overall process anti-cavitation refrigeration system |
| CN113418310B (en) * | 2021-06-22 | 2022-10-28 | 广东海悟科技有限公司 | Overall process anti-cavitation refrigeration system |
Also Published As
| Publication number | Publication date |
|---|---|
| US20160363351A1 (en) | 2016-12-15 |
| EP3106783A1 (en) | 2016-12-21 |
| JP2017003252A (en) | 2017-01-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106247659A (en) | Heat-exchange device and heat pump assembly | |
| CN103069226B (en) | Ejector type refrigerating cycle and use the refrigerating plant of this circulation | |
| CN108800633A (en) | Heat pump assembly | |
| CN101464069B (en) | Thermal injection and vortex flow combined air conditioner | |
| CN101122428A (en) | Refrigerant cycle device with ejector | |
| CN105135749B (en) | Carbon dioxide cold-hot combined supply system | |
| CN104864622A (en) | Auto-cascade steam compression type refrigeration cycle system | |
| CN102853578B (en) | Mixed working medium two-stage jet type refrigerating machine | |
| KR101679782B1 (en) | Steam production system | |
| CN204830556U (en) | Solar energy sprays overlapping cooling cycle system | |
| CN105241115B (en) | Both vapor compression sprays Combined Refrigeration Cycle device and method | |
| CN205002435U (en) | Utilize solar energy steam -jet ejector formula overlapping cooling cycle system | |
| CN103206802B (en) | A kind of pulse tube expander | |
| CN207006629U (en) | A kind of heat pump | |
| CN110296543B (en) | Refrigerating or heat pump system with jet gas-liquid separation heat exchange function | |
| CN102878715B (en) | Throttling liquid feeding refrigerating system with jet pump | |
| CA3117235C (en) | System and method of mechanical compression refrigeration based on two-phase ejector | |
| CN210242068U (en) | Gas-liquid separation heat exchange refrigeration or heat pump system with injection | |
| CN108180670A (en) | Absorption type heat exchange system | |
| CN104990302B (en) | Injection compression refrigerating system with gas-liquid separator and utilization low grade heat energy | |
| CN112969895A (en) | Direct expansion evaporator with enhanced steam injector production | |
| CN202692525U (en) | Hot water unit with exterior coupled type cascade high temperature heat pumps | |
| CN102305492B (en) | Multi-evaporating-temperature combined jet refrigerating system | |
| CN109163474A (en) | One pump multistage absorption-multistage evaporation absorption heat pump processed and the method for increasing the temperature difference | |
| CN107380132A (en) | Mechanical steam recompression car washer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20161221 |
|
| WD01 | Invention patent application deemed withdrawn after publication |