CN104165458B - Carbon dioxide heat-pump formula hot water supply apparatus - Google Patents
Carbon dioxide heat-pump formula hot water supply apparatus Download PDFInfo
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- CN104165458B CN104165458B CN201310370079.2A CN201310370079A CN104165458B CN 104165458 B CN104165458 B CN 104165458B CN 201310370079 A CN201310370079 A CN 201310370079A CN 104165458 B CN104165458 B CN 104165458B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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- 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]
- Y02B30/12—Hot water central heating systems using heat pumps
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S122/00—Liquid heaters and vaporizers
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Filling Or Discharging Of Gas Storage Vessels (AREA)
Abstract
The present invention provides the carbon dioxide heat-pump formula hot water supply apparatus of a kind of vaporizer possessing and can making maximizing performance according to heating efficiency.The carbon dioxide heat-pump formula hot water supply apparatus of the present invention is characterised by, vaporizer (103) be by using approximate right angle run through by the way of the fins set (3) of the fixing thermal conductive surface as air side, with the evaporator refrigerant stream group being made up of multiple evaporator refrigerant streams (4) of arrangement on the direction orthogonal with air stream, the vaporizer of the cross-fin tubular type of heat exchange is carried out between air and cold-producing medium, the internal diameter of the described evaporator refrigerant stream (4) of described vaporizer (103) is 4.3mm～4.9mm, when the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus is set to Q, in the case of the number that diverged by the stream of described evaporator refrigerant stream (4) is set to P, meet relationship below (1): P≤64/33 × Q...(1).
Description
Technical field
The present invention relates to carbon dioxide heat-pump formula hot water supply apparatus.
Background technology
The carbon dioxide heat-pump formula hot water supply apparatus that carbon dioxide is used for duty cryogen possesses the heat utilizing air
Liquid refrigerant in refrigerant pipe internal flow is flashed to the vaporizer of gas refrigerant.In the past, with the high property of vaporizer
Purpose can be turned to and carried out various research.Such as, propose there is following device: in the way of its length direction is orthogonal with air stream
The refrigerant pipe of arrangement the most at right angles to runs through the fins set of the thermal conductive surface as air side, so-called cross-fin tubular type
In vaporizer, the external diameter of refrigerant pipe is arranged on 4.6mm～6.0mm, entirety heat exchanger is lined up three row (with reference to patent literary composition
Offer 1).According to the carbon dioxide heat-pump formula hot water supply apparatus possessing such vaporizer, it is possible to increase solving number of parts
High performance is realized while the problem of this manufacturing etc..
Prior art literature
Patent documentation
Patent documentation 1: 2006 No. 194476 publications of JP.
Summary of the invention
Invent problem to be solved
But, fill in the carbon dioxide heat-pump formula hot water supply possessing conventional vaporizer (for example, referring to patent documentation 1)
In putting, although specify the suitable cold-producing medium caliber optimal so that this performance of evaporator, but not about refrigerant flow path
Fork number record.Here, when too small compared to the value originally should having the stream setting vaporizer diverges number,
The refrigerant side pressure loss between vaporizer gateway increases.On the other hand, when too greatly setting stream fork number, system
The type of flow in refrigerant tube is no longer the annular flow that thermal conductivity is high, and becomes the laminar flow that thermal conductivity is low.It is to say, exist
Following problem: be unable to obtain sufficient performance in the case of stream fork too small or excessive any one of number.Additionally, work as
When the heating efficiency of the heat pump cycle loading vaporizer strengthens, the type of flow in refrigerant pipe becomes the stream of the limit of laminar flow
Road fork number changes, therefore, it is also desirable to select the stream fork number corresponding with heating efficiency.
Therefore, the problem of the present invention is, it is provided that a kind of carbon dioxide heat-pump formula hot water supply apparatus, described carbon dioxide
Heat pump type hot water supply apparatus possesses the vaporizer that can make maximizing performance according to heating efficiency.
The present invention solving described problem relates to a kind of carbon dioxide heat-pump formula hot water supply apparatus, by the most extremely
Connect each key elements such as compressor, water refrigerant heat exchanger, expansion valve and vaporizer less and enter dioxy at stream inner sealing
Change carbon cold-producing medium and constitute, described carbon dioxide heat-pump formula hot water supply apparatus is characterised by, described vaporizer be by with
The mode run through to approximate right angle fixes the fins set of the thermal conductive surface as air side and by the direction orthogonal with air stream
The evaporator refrigerant stream group that multiple evaporator refrigerant streams of arrangement are constituted, carries out heat between air and cold-producing medium
The vaporizer of the cross-fin tubular type of exchange, the internal diameter of described evaporator refrigerant stream is 4.3mm～4.9mm, when by dioxy
The heating efficiency for water changing carbon heat pump type hot water supply apparatus is set to Q, is divided by the stream of described evaporator refrigerant stream
Trouble is in the case of number is set to P, meets relationship below (1): P≤64/33 × Q...(1).
Additionally, it is preferred that such carbon dioxide heat-pump formula hot water supply apparatus has following composition: when by described evaporation
The described stream fork of device refrigerant flow path is in the case of number is set to P, meets following formula (2):
P≤4/3 × Q...(2) (in described (2) formula, Q be carbon dioxide heat-pump formula hot water supply apparatus for water
Heating efficiency).
Additionally, it is preferred that such carbon dioxide heat-pump formula hot water supply apparatus has following composition: described vaporizer system
The described stream fork number P of refrigerant line is the natural maximum meeting described (2) formula.
Additionally, it is preferred that such carbon dioxide heat-pump formula hot water supply apparatus has a structure that at described vaporizer
Refrigerant outlet portion, in the way of close, configure multiple described evaporator refrigerant stream.
Additionally, it is preferred that such carbon dioxide heat-pump formula hot water supply apparatus has following composition: meet following formula (3):
Led/Ded 0.28＜ 0.169Q0.36... (3)
(LedIt is the length of stream, D before the fork of bifurcation point from expansion valve to allotteredIt it is the downstream of described expansion valve
The internal diameter of stream before the fork of side, Q is the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus).
The effect of the present invention is as follows.
In accordance with the invention it is possible to provide the two of a kind of vaporizer possessing and can making maximizing performance according to heating efficiency
Carbonoxide heat pump type hot water supply apparatus.
Accompanying drawing explanation
Fig. 1 is the system diagram of the carbon dioxide heat-pump formula hot water supply apparatus of embodiments of the present invention.
Fig. 2 is the axonometric chart of the vaporizer of the carbon dioxide heat-pump formula hot water supply apparatus of embodiments of the present invention.
Fig. 3 is the downstream of the expansion valve of the carbon dioxide heat-pump formula hot water supply apparatus representing embodiments of the present invention
The schematic diagram of flowing.
Fig. 4 is gas-liquid mixed region and the formation titanium dioxide representing and forming the spray flow of carbon dioxide coolant, bubble stream
The chart of the measurement result of the transition point in the gas-liquid separation region of the annular flow of carbon cold-producing medium.
Fig. 5 is the type of flow line chart for carbon dioxide coolant, and transverse axis is cold-producing medium aridity, and the longitudinal axis is quality speed
Degree (kg/m2S).
Fig. 6 is to represent internal diameter based on the fork number of stream before the fork determined by allotter with evaporator refrigerant stream
Relation and utilize simulation test calculate the part in evaporator refrigerant stream become annular flow threshold value calculating knot
Fruit chart, transverse axis is the internal diameter (mm) of evaporator refrigerant stream, the longitudinal axis be fork before stream by allotter determine point
Trouble number.
Fig. 7 is the APF of internal diameter (mm) and the carbon dioxide heat-pump formula hot water supply apparatus representing evaporator refrigerant stream
The chart of the relation of (Annual Performance Factor: annual energy efficiency), transverse axis is evaporator refrigerant stream
Internal diameter (mm), the longitudinal axis is APF.
Fig. 8 is to show schematically the cold-producing medium from the entrance of evaporator refrigerant stream to the carbon dioxide coolant of outlet
The chart of Temperature Distribution, transverse axis is the length (mm) of evaporator refrigerant stream, and the longitudinal axis is refrigerant temperature (DEG C).
Fig. 9 (a) is that the temperature rising T-phase with the carbon dioxide coolant shown in Fig. 8 represents accordingly shown in Fig. 2
After 3rd fork after stream and the 4th fork in stream, carbon dioxide coolant flowing to system from the refrigerant inlet portion of vaporizer
The schematic diagram of the variations in temperature of carbon dioxide coolant during cryogen export department.Fig. 9 (b) is and the carbon dioxide system shown in Fig. 8
The temperature of cryogen rise T-phase represent accordingly after as the 3rd fork of comparative example after stream and the 4th fork in stream,
The temperature of the carbon dioxide coolant carbon dioxide coolant when flowing to refrigerant outlet portion from the refrigerant inlet portion of vaporizer
The schematic diagram of degree change.
Figure 10 be heating efficiency Q representing carbon dioxide heat-pump formula hot water supply apparatus with the fork determined by allotter before
The chart of the relation of the number that most preferably diverges (stream fork number P) of stream, transverse axis is heating efficiency Q(kw), the longitudinal axis is stream fork
Number P.
Figure 11 is the axonometric chart of the vaporizer of the carbon dioxide heat-pump formula hot water supply apparatus of other embodiments.
In figure:
1 allotter, 2 merging part, 3 fins set, 4 evaporator refrigerant streams, streams before 5 forks, 6 the
Stream after one fork, stream after 7 second forks, stream after 8 the 3rd forks, stream after 9 the 4th forks, 10 the 5th points
Stream after trouble, stream after 11 the 6th forks, 100 compressors, 101 water refrigerant heat exchanger, 102 expansion valves,
103 vaporizers, 104 storage hot-water cylinders, 105 circulating pumps.
Detailed description of the invention
The carbon dioxide heat-pump formula hot water supply apparatus (CO of embodiments of the present invention2Heat pump type hot water supply apparatus)
It is characterized mainly in that, when the internal diameter of evaporator refrigerant stream being set to 4.3mm～4.9mm, by heat pump type hot water supply apparatus
The heating efficiency for water be set to Q, the number that the stream of described evaporator refrigerant stream diverged is when being set to P, meet with ShiShimonoseki
It is formula (1):
P≤64/33 × Q...(1)
Hereinafter, the enforcement of the carbon dioxide heat-pump formula hot water supply apparatus of the present invention is explained with reference to suitable accompanying drawing
Mode.Additionally, above-below direction is on the basis of the fore-and-aft direction up and down shown in Fig. 2 before and after in following description, i.e. with vertical direction
It is arranged above upside, with the upstream side of the air that flows into vaporizer as front side.It addition, the left and right directions in the following description is with Fig. 2
On the basis of shown left and right directions, i.e. with from the upstream side of air stream observe vaporizer towards under right as right side.
Fig. 1 is the system diagram of the heat pump type hot water supply apparatus of embodiments of the present invention.The heat-pump-type of present embodiment
Hot water supply apparatus (following, to be sometimes referred to as " heat pump hot-water supply device ") has heat pump cycle and the circulation of water side.
As it is shown in figure 1, heat pump cycle is following structure: connecting compressor 100, water cold-producing medium in circular (ring-type)
It is encapsulated into carbon dioxide coolant (CO in the stream of each key elements such as heat exchanger 101, expansion valve 102 and vaporizer 1032System
Cryogen).
It addition, the circulation of water side is for following structure: connect in circular (ring-type) storage hot-water cylinder 104, circulating pump 105 with
And in the stream of each key element such as water refrigerant heat exchanger 101, it is full of water.
Vaporizer 103 carries out heat exchange in order to stream is divided into multiple (being six streams in FIG), with expansion
It is configured with allotter 1 between valve 102, between compressor 100, is configured with merging part 2.
Fig. 2 is the axonometric chart of vaporizer 103, also particularly illustrates the knot from expansion valve 102 to merging part 2 in Fig. 1
Structure.
As in figure 2 it is shown, vaporizer 103 is the vaporizer of cross-fin tubular type, possesses the wing of the thermal conductive surface as air side
Sheet group 3 and multiple evaporator refrigerant stream 4(evaporator refrigerant stream group).Specifically, multiple by tabular of fins set 3
Fin is constituted, be configured to the plate face of fin by be separated by predetermined gap ground relative in the way of overlap each other.Further, air is in fins set
Flow between the plate face of the fin of 3.
Although not shown, but evaporator refrigerant stream 4 generally perpendicularly runs through each fin of fins set 3, thus is fixed on
Each fin.Specifically, evaporator refrigerant stream 4 after each fin generally perpendicularly having run through fins set 3, turn back and
The most generally perpendicularly run through each fin of fins set 3.It is to say, run through multiple evaporator refrigerant streams 4 of fins set 3
(evaporator refrigerant stream group) arranges on the direction orthogonal with air stream with the length direction of evaporator refrigerant stream 4
Mode configures.The internal diameter of the conduit constituting the evaporator refrigerant stream 4 of present embodiment is set as 4.6mm, and its external diameter sets
For 5.0mm.
Such vaporizer 103 is amounted to two row by the entrance side (side, prostatitis) of air and outlet side (rank rear side) etc. and constitutes.
It follows that explanation from expansion valve 102 via the structure of the stream of vaporizer 103 to merging part 2.
Before the formation fork of the bifurcation point of expansion valve 102 to allotter 1, the internal diameter of the conduit of stream 5 is set as 4mm, shape
Become length L of the conduit of the front stream 5 of forkedIt is set as 60mm.
Stream the 7, the 3rd fork after stream 6, second diverges after stream 5 is bifurcated into the first fork by allotter 1 before fork
After after rear stream 8, the 4th fork, after stream 9, the 5th fork, stream 10 and the 6th diverges, stream 11 etc. amount to six articles of streams.
After each fork diverged in stream 6～11, stream 8 and the 5th after stream the 6, the 3rd fork after the first fork
After fork, stream 10 is connected on the left of the rank rear of vaporizer 103, generally perpendicularly runs through each fin of fins set 3 and towards evaporation
On the right side of the rank rear of device 103.Incidentally, stream 8 and the 5th after stream the 6, the 3rd diverges after running through the first fork of fins set 3
After fork, stream 10 forms described evaporator refrigerant stream 4.
Although not shown, but towards stream 8 after stream the 6, the 3rd fork after the first fork on the right side of the rank rear of vaporizer 103 with
And the 5th fork after stream 10 turn back to the left in the way extended upward and again run through fins set 3 thus again towards steaming
Send out on the left of the rank rear of device 103.It addition, after the first fork after stream the 6, the 3rd fork after stream 8 and the 5th fork stream 10 exist
The top of vaporizer 103 carries out once running through fins set 3 toward ground return and more again towards on the left of the rank rear of vaporizer 103,
Then, forward side extends and is connected with on the left of the prostatitis of vaporizer.
After the l fork being connected with on the left of the prostatitis of vaporizer 103, after stream the 6, the 3rd fork, stream 8 and the 5th diverges
Rear stream 10 generally perpendicularly runs through each fin of fins set 3 and towards on the right side of the prostatitis of vaporizer 1.Further, although not shown, face
After the first fork on the right side of prostatitis, after stream the 6, the 3rd fork, stream 10 extends downwards after stream 8 and the 5th fork
Turn back to the left in Tu and again run through fins set 3 thus again towards on the left of the prostatitis of vaporizer.It addition, flow after the first fork
After the fork of road the 6, the 3rd, after stream 8 and the 5th fork, stream 10 is carried out once toward ground return in the lower section of vaporizer 103 the most again
Running through fins set 3 and again towards on the left of the prostatitis of vaporizer 103, the merging part 2 of forward side is stretched out.
On the other hand, after each fork diverged in stream 6～11, after the second fork, stream 7 diverges described first
The lower section of rear stream 6 is connected with on the left of the rank rear of vaporizer 103 the most adjacently.After 4th fork, stream 9 is at described 3rd point
After trouble, the lower section of stream 8 is connected with on the left of the rank rear of vaporizer 103 the most adjacently.After 6th fork, stream 11 is the described 5th
After fork, the lower section of stream 10 is connected with on the left of the rank rear of vaporizer 103 the most adjacently.
After the second fork being connected with on the left of the rank rear of vaporizer after stream the 7, the 4th fork after stream 9 and the 6th fork
Stream 11 generally perpendicularly runs through each fin of fins set 3 and towards on the right side of the rank rear of vaporizer 103.Incidentally, wing is run through
After second fork of sheet group 3, after stream the 7, the 4th fork, after stream 9 and the 6th fork, stream 11 forms described evaporator refrigeration
Agent stream 4.
Although not shown, but towards stream 9 after stream the 7, the 4th fork after the second fork on the right side of the rank rear of vaporizer 103 with
And the 6th turn back to the left in the way that extends downwards of stream 11 after fork and run through fins set 3 thus again towards vaporizer
On the left of the rank rear of 103.It addition, after the second fork after stream the 7, the 4th fork after stream 9 and the 6th fork stream 11 in evaporation
The lower section of device 103 carries out once running through fins set 3 toward ground return and more again towards on the left of the rank rear of vaporizer 103, then,
Forward side extends and is connected on the left of the prostatitis of vaporizer 103.
Stream 9 and the 6th point after stream the 7, the 4th fork after the second fork being connected with on the left of the prostatitis of vaporizer 103
After trouble, stream 11 generally perpendicularly runs through each fin of fins set 3 and towards on the right side of the prostatitis of vaporizer 103.Further, though not scheming
Show, but towards stream 11 after stream 9 after stream the 7, the 4th fork after the second fork on the right side of prostatitis and the 6th fork upwards
Turn back to the left in the way of Fang Yanshen and again run through fins set 3 thus again towards on the left of the prostatitis of vaporizer 103.It addition,
After second fork, after stream the 7, the 4th fork, after stream 9 and the 6th fork, stream 11 enters above vaporizer 103 the most again
Row once runs through fins set 3 and again towards on the left of the prostatitis of vaporizer 103, the merging part 2 of forward side is stretched out toward ground return.
Additionally, after stream 6 and the second fork, stream 7 is each other, flow after the 3rd fork after the first fork that merging part 2 is stretched out
Behind road 8 and the 4th fork stream 9 each other and after the 5th fork after stream 10 and the 6th fork stream 11 be configured to each other steaming
Send out and adjoin respectively on the left of the prostatitis of device 103.
Further, after each fork, stream 6～11 starts to be connected with merging part 2 from vaporizer 103, again becomes a stream.
It follows that see figures.1.and.2, the action of the carbon dioxide heat-pump hot water supply apparatus to present embodiment is said
Bright.
Carbon dioxide coolant is compressed by compressor 100 and becomes high temperature, high pressure conditions.This high temperature, the titanium dioxide of high pressure
Carbon cold-producing medium carries out heat friendship with from storage hot-water cylinder 104 by the water that circulating pump 105 conveying comes by water refrigerant heat exchanger 101
Change, water boil becomes boiled water lose heat.Now from carbon dioxide coolant to the hot amount of movement of the time per unit of water
Become heating efficiency Q.This heating efficiency Q is equivalent to " heating efficiency " described in claims, in the present embodiment, false
If being set as 4.5kw.
It follows that carbon dioxide coolant becomes low temperature, low pressure shape at expansion valve 102 by contracting stream portion (omitting diagram)
The gas-liquid mixture phase (gas-liquid two-phase flow) of state.Further, stream 6 after carbon dioxide coolant branches to diverge by allotter 1
～in 11.Further, carbon dioxide coolant flow through be divided into fork after stream 6～11 ground extend through the vaporizer of fins set 3
During refrigerant flow path 4, evaporate by heat owing to connecing from air.Then, the cold-producing medium flowed out from vaporizer 103 is 2-in-1 in merging part
Stream and after returning to a stream, return compressor 100, again compressed and pass out in heat pump cycle.
It follows that illustrate in greater detail the action of the carbon dioxide coolant from expansion valve 102 to allotter l.Fig. 3 is table
Show the schematic diagram of the flow regime in the downstream of expansion valve 102.
As it is shown on figure 3, the carbon dioxide coolant flowed out from expansion valve 102 becomes gas and system due to the decline of pressure
The two-phase state of cryogen.Specifically, carbon dioxide coolant becomes the gas refrigeration as continuous phase near expansion valve 102
Agent is mixed with the spray flow of liquid refrigerant (or as the liquid refrigerant of continuous phase is mixed with the gas of gas refrigerant
Bubble stream (not shown)), formed in the region leaving expansion valve 102 and flow in the way of liquid refrigerant covers the internal perisporium of stream
Annular flow.
The internal diameter of stream is the biggest, and refrigerant flow is the biggest, from spray flow (or bubble stream (omitting diagram)) to annular flow
Transition point distance expansion valve 102 refrigerant outlet portion the most remote.If it addition, in view of the cold-producing medium for vaporizer 103
, then there is situations below in distribution in annular flow: the deviation of the gas-liquid caused by the inclination of allotter 1, carbon dioxide coolant
The bias current of self can cause maldistribution as a result, the performance of evaporator that should obtain can not be obtained.On the other hand, in spraying
In stream, it is possible to do not carried out by these stable with being affected and distribute uniformly.
Therefore, the feelings of evaporator refrigerant stream 4 are formed when the stream utilizing many forks as stream 6～11 after fork
Under condition, in the annular flow comparison with spray flow, the decline utilizing spray flow to be allocated for preventing performance is particularly important.
Next Fig. 4 of institute's reference is to represent the formation spray flow of carbon dioxide coolant, the gas-liquid mixed district of bubble stream
The chart of the measurement result of the transition point in the gas-liquid separation region of the annular flow of territory and formation carbon dioxide coolant, transverse axis represents
Heating efficiency Q(kw), the longitudinal axis represents x/Ded 0.28(x is the flow path length (m) of the distance expansion valve 102 shown in Fig. 3, DedIt is Fig. 2
The internal diameter (m) of stream 5 before the fork in the downstream of shown expansion valve 102).
Incidentally, the gas-liquid mixed region shown in Fig. 4 and the transition point in gas-liquid separation region are by heating efficiency
The performance of the heat pump hot-water supply device of 4.5kw show required for experimental condition in, the flow of carbon dioxide coolant realizes
It is simulated test under the conditions of the minimum frosting phase to try to achieve.
As shown in Figure 4, x/D is meted 0.28=0.169Q0.36The curve of this relational expression represents gas-liquid mixed region and gas-liquid
The transition point of separated region, than this curve region (x/D by the toped 0.28Big region) it is gas-liquid separation region, i.e. form ring
The region of shape stream, than this curve region (x/D on the lowered 0.28Little region) be gas-liquid mixed region, i.e. formed spray flow or
The region of person's bubble stream.
Therefore, in the present embodiment, in order to allotter 1 distribution spray stream or the carbon dioxide refrigeration of bubble stream
Agent, it is desirable to the satisfied following formula (3) being specifically described later:
Led/Ded 0.28＜ 0.169Q0.36... (3)
(wherein, LedIt is the length of stream 5 before the fork of the bifurcation point from expansion valve 102 to allotter 1 shown in Fig. 2
(mm), DedBeing the internal diameter (mm) of the front stream 5 of fork in the downstream of the expansion valve 102 shown in Fig. 2, Q is heating efficiency (kw)).
In the present embodiment, as it has been described above, by stream internal diameter DedIt is set to 4mm, heating efficiency Q is set to 4.5kw, because of
This, is in order to calculate APF(Annual Performance Factor: annual energy efficiency, below unified writing APF) institute
Under the conditions of the total Test needed, the carbon dioxide coolant of spray flow or bubble stream is distributed to allotter 1, shown in Fig. 3
The flow path length (m) of distance expansion valve 102 is necessarily less than 61.9mm(x ＜ 61.9mm).
For above-mentioned reasons, in the present embodiment, will flow before the fork of the bifurcation point of expansion valve 102 to allotter 1
Length L on road 5ed(with reference to Fig. 2) is set as 60mm.
It follows that in the carbon dioxide heat-pump hot water supply apparatus of present embodiment, by dividing that allotter 1 determines
Before trouble, the fork number of stream 5 illustrates with the relation of the internal diameter of evaporator refrigerant stream 4.
Next Fig. 5 of institute's reference is the type of flow line chart for carbon dioxide coolant, and transverse axis is that cold-producing medium is dried
Degree, the longitudinal axis is mass velocity (kg/m2S).
As it is shown in figure 5, the region representation surrounded by line ABCD forms the region of laminar flow, in layered stream, gas
Cold-producing medium and liquid refrigerant occur deviation to be divided into two-layer flow in conduit.
It addition, online between A and line C the speed quality region representation gas refrigerant more than line D and liquid refrigerant exist
The region of described annular flow is formed in conduit.If evaluating laminar flow and annular flow from the viewpoint of thermal conductivity, then annular flow due to
Produce explosive evaporation at whole tube wall and flow evaporator is obtained in that high thermal conductivity.On the other hand, in laminar flow, conduit
The part of inner peripheral surface contact with gas refrigerant, therefore, do not produce explosive evaporation in this part, heat conduction compared with annular flow
Rate step-down.Therefore, in order to utilize identical heat-conducting area to obtain higher heat conductivility, need to be formed annular flow in stream.
Further, in the present embodiment, relation based on the speed quality shown in Fig. 5 Yu aridity, utilize simulation test
Calculate the part in evaporator refrigerant stream 4 and become the threshold value of annular flow.Figure 6 illustrates this result.Fig. 6 is to represent
Mould is utilized based on the relation of the internal diameter of fork number and the evaporator refrigerant stream 4 of stream 5 before the fork determined by allotter 1
A part in the evaporator refrigerant stream 4 that plan tester calculates becomes the chart of the result of calculation of the threshold value of annular flow, horizontal
Axle is the internal diameter (mm) of evaporator refrigerant stream 4, and the longitudinal axis is the fork number of the front stream 5 of the fork determined by allotter 1, at figure
In 6, it is denoted as " evaporator refrigerant stream internal diameter (mm) " and " stream fork number " respectively.Incidentally, ring is become from laminar flow
The transition point of shape stream passes through in the experimental condition required for the performance of the heat pump hot-water supply device of heating efficiency 4.5kw shows
, the flow of carbon dioxide coolant calculates under the conditions of realizing the minimum frosting phase and tries to achieve.
In figure 6, having linked the line of black circle "●" with straight line is to produce the transformation that laminar flow is mutual with annular flow
Threshold value.The region of the laminar flow that the region representation thermal conductivity bigger than this line stream fork number is low, less than this line stream fork number
The region of the annular flow that region representation thermal conductivity is high.Additionally, the stream fork number of the longitudinal axis in Fig. 6 is natural number scale, therefore,
Can the position representing predetermined fork number on the longitudinal axis defined each other of two black circle "●" that is mutually juxtaposed
The internal diameter of optimal evaporator refrigerant stream 4 is determined in the range of evaporator refrigerant stream internal diameter (mm).Specifically, example
As in figure 6, when stream fork number is 6, the threshold value becoming annular flow is that evaporator refrigerant stream internal diameter (mm) is at 4.4mm
～in the range of 4.7mm.
It follows that the pass of specification and performance of vaporizer 103 of the heat pump type hot water supply apparatus for present embodiment
System illustrates.Fig. 7 is the internal diameter (mm) representing evaporator refrigerant stream 4 and the performance representing heat pump hot-water supply system
The chart of the result of calculation of the relation of APF, transverse axis is internal diameter (the evaporator refrigerant stream internal diameter of evaporator refrigerant stream 4
Mm), the longitudinal axis is APF.
Additionally, flow before the fork corresponding, that determined by allotter 1 of the internal diameter with evaporator refrigerant stream 4 herein
The threshold value shown in fork number (stream fork number) application drawing 6 on road 5.It is intended that because the stream fork the biggest vaporizer of number
The pressure loss between gateway is the least, so obtaining optimal performance by taking into account high thermal conductivity with low pressure loss.It addition,
APF calculate so that as vaporizer 103 air side thermal conductive surface fin material price with as evaporator refrigerant stream
The mode that the summation of the refrigerant pipe price on road 4 is fixed is carried out.
Understand as shown in Figure 7: the internal diameter of evaporator refrigerant stream 4 is (in the figure 7, for the evaporator refrigerant stream of transverse axis
Road internal diameter (mm)) the least, APF is the biggest, thus the performance of heat pump type hot water supply apparatus improves.This be considered as because: in order to
Ensureing the heat-conducting area of a certain size refrigerant flow path, the internal diameter of evaporator refrigerant stream 4 is the thinnest, and the quantity of stream more increases
Adding, stream interval to each other more reduces simultaneously.It is to say, this be considered as because: heat conduct equably to fins set 3 from
And fin efficiency improves.However, one will appreciate that: along with evaporator refrigerant stream 4 internal diameter reduce performance increase rate with internal diameter
4.6mm is to slow down in boundary.This reason uses ensuing Fig. 8,9 illustrates.
Fig. 8 is to show schematically the chart from the entrance of evaporator refrigerant stream 4 to the distribution of the refrigerant temperature of outlet,
Transverse axis is the length (mm) of evaporator refrigerant stream, and the longitudinal axis is refrigerant temperature (DEG C).
Vaporizer 103(is with reference to Fig. 2) liquid refrigerant is being flashed in the characteristic of gas refrigerant, as shown in Figure 8,
Near the outlet side of vaporizer 103, evaporation is fully completed, and the temperature of cold-producing medium rises T(DEG C).
Next Fig. 9 (a) of institute's reference is that the temperature with the carbon dioxide coolant shown in Fig. 8 rises T-phase accordingly
Represent after the 3rd fork shown in Fig. 2 after stream and the 4th fork in stream, carbon dioxide coolant is from vaporizer 103
The schematic diagram of the variations in temperature of carbon dioxide coolant when refrigerant inlet portion flow to refrigerant outlet portion.Fig. 9 (b) is and figure
The temperature of the carbon dioxide coolant shown in 8 rise T-phase represent accordingly after as the 3rd fork of comparative example stream and
After 4th fork in stream, carbon dioxide coolant when flowing to refrigerant outlet portion from the refrigerant inlet portion of vaporizer two
The schematic diagram of the variations in temperature of carbonoxide cold-producing medium.
As shown in Fig. 9 (a), after the 3rd fork of described embodiment, after stream 8 and the 4th fork, stream 9 is as described above
From allotter 1(with reference to Fig. 2) after stream 8 and the 4th fork, stream 9 abuts one another after the 3rd fork that extends position
It is connected with fins set 3 and constitutes the refrigerant inlet portion of vaporizer 103.It addition, from vaporizer 103 towards merging part 2(with reference to figure
2) after the 3rd fork, after stream 8 and the 4th fork, stream 9 forms vaporizer 103 in the position adjoined each other as described above
Refrigerant outlet portion.
On the other hand, stream 9 and Fig. 9 (a) after stream 8 and the 4th fork after the 3rd fork of the comparative example shown in Fig. 9 (b)
After shown 3rd fork, after stream 8 and the 4th fork, stream 9 is different, and refrigerant inlet portion and the cold-producing medium of vaporizer 103 go out
Oral area is to be located remotely from each other via the evaporator refrigerant stream 4 being divided into three sections on the above-below direction being arranged in fins set 3
Mode is formed.
Further, as shown in Fig. 9 (a) and Fig. 9 (b), the evaporator refrigerant stream 4 running through fins set 3 utilizes via fin
Group 3 fin and the most adjacent stream carries out heat exchange as shown in hollow arrow.Do not exist with hypothesis and pass through fin
The situation of the heat exchange that group 3 is carried out is compared, when carrying out above-mentioned heat exchange, generally, and the evaporator refrigeration of high temperature side
Agent stream 4 is cooled thus the hydraulic performance decline of heat pump hot-water supply device.
It addition, the interval between evaporator refrigerant stream 4 is the least, the hot amount of movement carried out by conduction of heat is the biggest.Cause
This, more make evaporator refrigerant stream 4 tiny and improve flow stream density, and the performance of heat pump hot-water supply device is got over due to conduction of heat
Affect and be difficult to improve.Additionally, the refrigerant superheat degree of the outlet of vaporizer 103 is the highest, the conduction of heat of the fin of fins set 3 is led
The hydraulic performance decline of the heat pump hot-water supply device caused is the most obvious.It addition, do not possess refrigerant amount in heat pump cycle to adjust the heat of function
Pump hot-water supply device has the characteristic that atmospheric temperature the highest refrigerant superheat degree more rises.
It addition, the evaporator refrigerant stream in " the refrigerant outlet portion of vaporizer 103 " in the comparative example shown in Fig. 9 (b)
The carbon dioxide coolant that carbon dioxide coolant in road 4 i.e. represents with " high temperature " in Fig. 9 (b) is with thereunder adjacent
The carbon dioxide coolant represented with " low temperature " in evaporator refrigerant stream 4 carries out heat exchange.Therefore, Fig. 9 (b) Suo Shi
Comparative example in, the hydraulic performance decline amount of the heat pump hot-water supply device that conduction of heat causes is big.On the other hand, in the basis shown in Fig. 9 (a)
The dioxy represented with " high temperature " in embodiment, in the evaporator refrigerant stream 4 in " the refrigerant outlet portion of vaporizer 103 "
Change carbon cold-producing medium with and its evaporator refrigerant stream 4 adjoined in the carbon dioxide coolant represented with " middle temperature " carry out heat
Exchange.
Therefore, in the embodiment shown in Fig. 9 (a), by the vaporizer system in " the refrigerant outlet portion of vaporizer 103 "
Stream 9 after stream 8 and the 4th fork after 3rd fork of refrigerant line 4(Fig. 9 (a)) abut one another, it is possible to increase heat pump
The performance of hot-water supply device.
As described in the explanation carried out Fig. 4 to Fig. 9 above, 4.6mm is suitable as the internal diameter of evaporator refrigerant stream 4,
Additionally, by using the flow passage structure shown in Fig. 9 (a), it is possible to alleviate the hydraulic performance decline that conduction of heat causes.And, it is contemplated that system
The deviation etc. made, in addition it is also necessary to the scope of the internal diameter of the evaporator refrigerant stream 4 that regulation can allow for.
Utilized as described in the explanation that Fig. 6 carries out, select 4.6mm as the stream during internal diameter of evaporator refrigerant stream 4
Road fork number is 6, but, even if stream internal diameter due to the deviation etc. that manufactures in the case of 4.6mm deviates, as long as
The internal diameter of the evaporator refrigerant stream 4 shown in the transverse axis of Fig. 6, then can correspondence (setting) in the range of 4.4mm～4.7mm
Optimal stream fork number P.
Referring again to Fig. 7, when stream fork number selecting but the upside transverse axis of 7(reference Fig. 7 due to refrigerant flow)
Time, it is allowed to the inside diameter ranges of evaporator refrigerant stream 4 at 4.4mm～4.7mm, when stream fork number is that 6(is with reference to Fig. 7
Upside transverse axis) time, it is allowed to the inside diameter ranges of evaporator refrigerant stream 4 at 4.6mm～4.9mm.Even if it is to say, considering
The internal diameter of evaporator refrigerant stream 4 caused to the deviation etc. manufactured deviates from 4.6mm, if the vaporizer system shown in Fig. 7
The internal diameter of refrigerant line 4 in the range of 4.3mm～4.9mm, then can diverge number P by corresponding (setting) optimal stream.In passing
Illustrate, with the inside diameter ranges of the stream of the upside transverse axis of Fig. 7 fork evaporator refrigerant stream 4 corresponding to (6 or 7) number as
The scope allowing laminar flow under the low volumetric refrigerant flows such as frosting phase is calculated by simulation test tries to achieve.
It follows that for heating efficiency Q(kW of heat pump hot-water supply device) with the fork determined by allotter 1 before stream 5
The relation of the number that most preferably diverges (stream fork number P) illustrate.Figure 10 is heating efficiency Q representing Teat pump hot water supply device
With the chart of the relation of the number that most preferably diverges (stream fork number P) of stream before the fork determined by allotter, transverse axis is to add heat energy
Power Q(kw), the longitudinal axis is stream fork number P.It is to say, the chart shown in Figure 10 is as described above at evaporator refrigerant stream
In the case of the internal diameter of 4 is 4.6mm, by utilizing simulation test to calculate the carbon dioxide refrigeration in evaporator refrigerant stream 4
The relation of heating efficiency Q and stream fork number P that agent becomes annular flow is tried to achieve.In Fig. 10, the bar of calculating APF it is represented by dotted lines
The result of the frosting phase condition that the refrigerant flow in part is minimum, represents the refrigerant flow in the condition calculating APF with solid line
The result of maximum summer conditions.
As shown in Figure 10, the threshold value for frosting phase condition represents with P=4/3 × Q, for the threshold value of summer conditions with P
=64/33 × Q represents.Further, stream fork number P is two in evaporator refrigerant stream 4 less than the region of respective threshold value
Carbonoxide cold-producing medium becomes the region of annular flow.
Therefore, under summer conditions benchmark, meet described formula (1) by setting:
P≤64/33 × Q...(1)
Heating efficiency Q(kw of this relational expression) and stream fork number P enable to two in evaporator refrigerant stream 4
Carbonoxide cold-producing medium becomes annular flow.
It addition, under frosting phase condition reference, if meeting formula (2):
P≤4/3 × Q...(2)
This relational expression, then can be under calculating the full terms required for APF so that in evaporator refrigerant stream 4
Carbon dioxide coolant become annular flow.In the present embodiment, in order to guarantee high-performance under full terms, in formula (2):
In P≤4/3 × Q, it is assumed that heating efficiency Q be the situation of described 4.5kw, stream fork number P be 6.
Additionally, in the present embodiment, the situation that heating efficiency Q is 4.5kw is recorded, but as long as is not hindered
The problem of the present invention, can suitably set heating efficiency Q.
According to the carbon dioxide heat-pump formula hot water supply apparatus of the present embodiment possessing above-mentioned vaporizer 103, by making
The internal diameter of evaporator refrigerant stream 4 in the range of 4.3mm to 4.9mm, make the relation of stream fork number P and heating efficiency Q
Meet described formula (1): P≤64/33 × Q, the type of flow within evaporator refrigerant stream 4 can represent carbon dioxide heat
In experimental condition required for the calculating of the APF of the performance of pump type hot water supply apparatus, refrigerant flow becomes maximum bar
Under part, become the annular flow that thermal conductivity is high, therefore, it is possible to obtain high-performance.
It addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, it is set to described formula (2) by the number P that diverged by stream:
Value in the range of P≤4/3 × Q, it is possible under the conditions of calculating the total Test required for APF so that evaporator refrigerant stream
The type of flow on road 4 becomes the annular flow that thermal conductivity is high, therefore, it is possible to obtain high-performance under full terms.
It addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, be set to meet described formula by the number P that diverged by stream
(2): natural maximum (such as, the fork of the described stream in the present embodiment number P=of the P of P≤4/3 × this relation of Q
6), thermal conductivity is not only improved, additionally it is possible to obtain the effect reducing the refrigerant side pressure loss, therefore, it is possible to obtain more preferably property
Energy.
It addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, by closely configuring multiple vaporizer system
The refrigerant outlet portion of refrigerant line 4, the situation phase kept off with the refrigerant outlet portion of multiple evaporator refrigerant streams 4
Ratio, it is possible to prevent the hydraulic performance decline that the impact of the conduction of heat via fins set 3 causes, significantly improve the performance of vaporizer 103.
It addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, vaporizer 103 will necessarily have multiple fork, because of
This, carry out the uniform distribution of carbon dioxide coolant to give full play to performance need, meets following formula (3) by selection:
Led/Ded 0.28＜ 0.169Q0.36... (3)
(Led、DedAnd Q and above-mentioned same meaning) value, the cold-producing medium stream flowed out from expansion valve 102 is able to maintain that gas-liquid
Admixture ground flows into stream branched portion, no matter stream fork number P is allocated with uniform flow and aridity.
According to above-mentioned present embodiment, it is possible to select to consider the deviation of manufacture for arbitrary heating efficiency Q
The inside diameter ranges of good evaporator refrigerant stream 4 and stream diverge number P, therefore, it is possible to be provided with can be according to heating efficiency Q
Make the carbon dioxide heat-pump formula hot water supply apparatus vaporizer of the vaporizer 103 of maximizing performance.
Above, it is illustrated for embodiments of the present invention, but the present invention is not limited to described embodiment,
But can implement with various forms.In other embodiments of following description, for the structure identical with described embodiment
One-tenth key element marks identical symbol and description is omitted.
Figure 11 of following institute reference is the vaporizer of the carbon dioxide heat-pump hot water supply apparatus of other embodiments
Axonometric chart.In fig. 11, symbol 1 represents that allotter, symbol 2 represent that merging part, symbol 3 represent fins set, and symbol 5 represents fork
Front stream, symbol 6 represents that stream after the first fork, symbol 7 represent that stream after the second fork, symbol 8 flow after representing the 3rd fork
Road, symbol 9 represents stream after the 4th fork, and symbol 10 represents stream after the 5th fork, and symbol 11 represents stream after the 6th fork,
Symbol 102 represents that expansion valve, symbol 103 represent vaporizer.
As shown in figure 11, compared with the vaporizer 103 of the described embodiment shown in Fig. 2, the dioxy of other embodiments
The vaporizer 103 changing carbon Teat pump hot water supply device becomes the columns increase string of fins set 3 and amounts to the composition of three row, therefore
Flow passage structure is different.Moreover, it is assumed that heating efficiency Q possessing the heat pump hot-water supply device of the vaporizer 103 shown in Figure 11 is
6.0kW。
Compared with the device shown in Fig. 2, the vaporizer 103 shown in Figure 11 increases and vaporizer due to the columns of fins set 3
Refrigerant flow path 4 increases.Therefore, the specification that the pressure loss between the refrigerating fluid discharging and feeding of vaporizer 103 is big is become.
On the other hand, in the formula shown in Figure 10, because the project of the pressure loss does not exists, so can apply with described
The theory that embodiment is identical.
It is to say, when in formula (2): when heating efficiency Q being set to 6kw in P≤4/3 × Q, P≤8, therefore, from reducing pressure
Being suitable for from the viewpoint of power loss making stream fork number P is " 8 " as maximum.But, from the viewpoint of production, excellent
Selecting stream fork number P consistent with the body of output 6.0kw at output 4.5kw, the number that therefore diverged by stream is set to
" 6 ", select to play high performance specification for multiple heating efficiencies Q.
It addition, in said embodiment, to shown in Fig. 1, there is compressor 100, water refrigerant heat exchanger 101, swollen
The heat pump cycle of swollen valve 12 and vaporizer 103 is illustrated, but, the present invention also is able to be applicable to also comprise refrigerant amount
The heat pump cycle of guiding mechanism, inner heat exchanger etc., described inner heat exchanger makes the cold-producing medium of high-pressure side and low-pressure side enter
Row heat exchange.
Claims (5)
1. a carbon dioxide heat-pump formula hot water supply apparatus, by being annularly at least connected with compressor, water cold-producing medium heat is handed over
The each key element of parallel operation, expansion valve and vaporizer also enters carbon dioxide coolant at stream inner sealing and constitutes, described titanium dioxide
Carbon heat pump type hot water supply apparatus is characterised by,
Described vaporizer be by using approximate right angle run through by the way of the fixing thermal conductive surface as air side fins set and by
The evaporator refrigerant stream group that multiple evaporator refrigerant streams of arrangement are constituted on the direction orthogonal with air stream, comes
The vaporizer of the cross-fin tubular type of heat exchange is carried out between air and cold-producing medium,
The internal diameter of the described evaporator refrigerant stream of described vaporizer is 4.3mm～4.9mm,
When the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus being set to Q, by described evaporator refrigerant
The stream fork of stream is in the case of number is set to P, under summer conditions benchmark, meets following formula (1):
P≤64/33×Q…(1)。
Carbon dioxide heat-pump formula hot water supply apparatus the most according to claim 1, it is characterised in that
In the case of the number that diverged by the described stream of described evaporator refrigerant stream is set to P, under frosting phase condition reference,
Meet following formula (2):
P≤4/3×Q…(2)
In described (2) formula, Q is the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus.
Carbon dioxide heat-pump formula hot water supply apparatus the most according to claim 2, it is characterised in that
The described stream fork number P of described evaporator refrigerant stream is the natural maximum meeting described (2) formula.
Carbon dioxide heat-pump formula hot water supply apparatus the most according to claim 1, it is characterised in that
In the refrigerant outlet portion of described vaporizer, configure multiple described evaporator refrigerant stream in a mutually adjacent manner.
Carbon dioxide heat-pump formula hot water supply apparatus the most according to claim 1, it is characterised in that
Meet following formula (3):
Led/Ded 0.28＜ 0.169Q0.36…(3)
LedIt is the length of stream, D before the fork of bifurcation point from expansion valve to allotteredBe described expansion valve downstream point
The internal diameter of stream before trouble, Q is the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013103653A JP5943206B2 (en) | 2013-05-16 | 2013-05-16 | CO2 heat pump water heater |
| JP2013-103653 | 2013-05-16 |
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| CN104165458A CN104165458A (en) | 2014-11-26 |
| CN104165458B true CN104165458B (en) | 2016-12-28 |
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| CN201310370079.2A Expired - Fee Related CN104165458B (en) | 2013-05-16 | 2013-08-22 | Carbon dioxide heat-pump formula hot water supply apparatus |
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| JP (1) | JP5943206B2 (en) |
| KR (1) | KR101520675B1 (en) |
| CN (1) | CN104165458B (en) |
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| CN104522133A (en) * | 2014-12-16 | 2015-04-22 | 田幼华 | Meat animal dehairing system and method based on carbon dioxide air source heat pump |
| KR101624622B1 (en) * | 2015-07-07 | 2016-05-26 | 이달주 | Apparatus for supplying warm water utilizing an air source heat pump |
| JP6553981B2 (en) * | 2015-08-18 | 2019-07-31 | 日立グローバルライフソリューションズ株式会社 | Heat exchange equipment for heat pump equipment |
| JP2017044431A (en) * | 2015-08-28 | 2017-03-02 | 日立アプライアンス株式会社 | Heat pump type water heater |
| JP6590948B2 (en) * | 2015-12-17 | 2019-10-16 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle equipment |
| CN105841124A (en) * | 2016-05-27 | 2016-08-10 | 陕西盛田能源服务股份有限公司 | Small steam generation device and method based on air source carbon dioxide heat pump |
| CN113853502A (en) * | 2019-05-31 | 2021-12-28 | 三菱电机株式会社 | Refrigeration cycle device and refrigerator |
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- 2013-05-16 JP JP2013103653A patent/JP5943206B2/en active Active
- 2013-08-06 KR KR1020130092871A patent/KR101520675B1/en active IP Right Grant
- 2013-08-22 CN CN201310370079.2A patent/CN104165458B/en not_active Expired - Fee Related
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| JPH08313115A (en) * | 1995-05-15 | 1996-11-29 | Daikin Ind Ltd | Multi-path type heat exchanger |
| JP2003343942A (en) * | 2002-05-23 | 2003-12-03 | Denso Corp | Evaporator |
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Also Published As
| Publication number | Publication date |
|---|---|
| KR101520675B1 (en) | 2015-05-15 |
| CN104165458A (en) | 2014-11-26 |
| JP2014224637A (en) | 2014-12-04 |
| KR20140135586A (en) | 2014-11-26 |
| JP5943206B2 (en) | 2016-06-29 |
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