CN104165458A - Carbon dioxide heat pump water heater - Google Patents
Carbon dioxide heat pump water heater Download PDFInfo
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- CN104165458A CN104165458A CN201310370079.2A CN201310370079A CN104165458A CN 104165458 A CN104165458 A CN 104165458A CN 201310370079 A CN201310370079 A CN 201310370079A CN 104165458 A CN104165458 A CN 104165458A
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- stream
- fork
- carbon dioxide
- evaporimeter
- water supply
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Classifications
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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
-
- 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)
- Thermal Sciences (AREA)
- Mechanical Engineering (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 invention provides a carbon dioxide heat pump water heater which can maximize the performance according to the heating capability. The carbon dioxide heat pump water heater is characterized in that the evaporation device can perform heat exchange between the air and the cooling agent through the fin assembly which is passed through in a right angle and is used as a heat guiding surface for the air and the cooling agent flow path (4) of the plurality of evaporation devices which are arranged in the direction which is orthogonal with the air flow; the inner diameter of the cooling agent flow path (4) is 4.3-4.9mm and the following equation P<=64/33*Q is satisfied when the heating capability of the carbon dioxide heat pump water heater is set as Q, and the branch quantity of the evaporation device cooling agent flow path (4) is set as P.
Description
Technical field
The present invention relates to carbon dioxide heat-pump formula hot water supply apparatus.
Background technology
Carbon dioxide is possessed and utilizes the heat of air to become the evaporimeter of gas refrigerant in the liquid refrigerant evaporates of refrigerant pipe internal flow for the carbon dioxide heat-pump formula hot water supply apparatus of duty cryogen.In the past, carried out various research taking the high performance of evaporimeter as object.For example, proposition has with lower device: roughly run through in the evaporimeter that the intersects fin tube type fins set of the thermal conductive surface of air side, so-called at the refrigerant pipe of arranging in the orthogonal mode of its length direction and air stream at right angles, the external diameter of refrigerant pipe is arranged on to 4.6mm～6.0mm, all heat exchangers are lined up to three row (with reference to patent documentation 1).According to the carbon dioxide heat-pump formula hot water supply apparatus that possesses such evaporimeter, can in solving number of parts and increase the problem of this manufacturing etc., realize high performance.
Prior art document
Patent documentation
Patent documentation 1: 2006-No. 194476 communiques of JP.
Summary of the invention
Invent problem to be solved
But, (for example possessing evaporimeter in the past, with reference to patent documentation 1) carbon dioxide heat-pump formula hot water supply apparatus in, although specified the suitable cold-producing medium caliber that makes this performance of evaporator the best, not about the record of the fork number of refrigerant flow path.At this, when than the original value that should have too small while having set the stream fork number of evaporimeter, the refrigerant side pressure loss between evaporimeter gateway increases.On the other hand, when having served as the earth and having set stream fork number, the type of flow in refrigerant pipe is no longer the annular flow that thermal conductivity is high, and becomes the laminar flow that thermal conductivity is low.That is to say, have following problem: in any too small or excessive situation of stream fork number, all can not obtain sufficient performance.In addition, in the time packing the heating efficiency enhancing of heat pump cycle of evaporimeter into, the stream fork number that the type of flow in refrigerant pipe becomes the limit of laminar flow changes, and therefore, also needs to select the stream fork number corresponding with heating efficiency.
Therefore, problem of the present invention is, a kind of carbon dioxide heat-pump formula hot water supply apparatus is provided, and described carbon dioxide heat-pump formula hot water supply apparatus possesses the evaporimeter that can make according to heating efficiency maximizing performance.
The present invention who solves described problem relates to a kind of carbon dioxide heat-pump formula hot water supply apparatus, by at least connecting in the form of a ring compressor, water refrigerant heat exchanger, each key element such as expansion valve and evaporimeter also enters carbon dioxide coolant and forms at stream inner sealing, described carbon dioxide heat-pump formula hot water supply apparatus is characterised in that, described evaporimeter be by using approximate right angle the fins set of the fixing thermal conductive surface as air side of the mode that runs through, with by with the orthogonal direction of air stream on the evaporator refrigerant stream group that forms of multiple evaporator refrigerant streams of arranging, between air and cold-producing medium, carry out the evaporimeter that intersects fin tube type of heat exchange, the internal diameter of described evaporator refrigerant stream is 4.3mm～4.9mm, when the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus is made as to Q, the stream fork number of described evaporator refrigerant stream is made as in the situation of P, meet following relational expression (1): P≤64/33 × Q...(1).
In addition, preferably in such carbon dioxide heat-pump formula hot water supply apparatus, there is following formation: when the described stream fork number of described evaporator refrigerant stream is made as in the situation of P, 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).
In addition, in preferred such carbon dioxide heat-pump formula hot water supply apparatus, there is following formation: the described stream fork number P of described evaporator refrigerant stream is the natural maximum that meets described (2) formula.
In addition, in preferred such carbon dioxide heat-pump formula hot water supply apparatus, there is following structure: in the refrigerant outlet portion of described evaporimeter, configure multiple described evaporator refrigerant streams in the mode approaching.
In addition, in preferred such carbon dioxide heat-pump formula hot water supply apparatus, there is following formation: meet following formula (3):
L
ed/D
ed 0.28＜0.169Q
0.36...（3）
(L
edthe length of stream the fork of the bifurcation point from expansion valve to distributor, D
edbe the internal diameter of the front stream of fork in the downstream of described expansion valve, Q is the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus).
Effect of the present invention is as follows.
According to the present invention, can provide a kind of carbon dioxide heat-pump formula hot water supply apparatus that can make according to heating efficiency the evaporimeter of maximizing performance that possesses.
Brief description of the drawings
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 stereogram of the evaporimeter of the carbon dioxide heat-pump formula hot water supply apparatus of embodiments of the present invention.
Fig. 3 is the mobile schematic diagram that represents the downstream of the expansion valve of the carbon dioxide heat-pump formula hot water supply apparatus of embodiments of the present invention.
Fig. 4 is spray flow, the gas-liquid mixed region of bubble flow and the chart of the measurement result of the transition point in the gas-liquid separation region of the annular flow of formation carbon dioxide coolant that represents to form carbon dioxide coolant.
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 mass velocity (kg/m
2s).
Fig. 6 is the relation of the fork number of stream and the internal diameter of evaporator refrigerant stream before the fork representing based on being determined by distributor and utilize simulated test to calculate a part in evaporator refrigerant stream to become the chart of the result of calculation of the threshold value of annular flow, transverse axis is the internal diameter (mm) of evaporator refrigerant stream, and the longitudinal axis is the fork number being determined by distributor of stream before fork.
Fig. 7 is the internal diameter (mm) that represents evaporator refrigerant stream and the APF(Annual Performance Factor of carbon dioxide heat-pump formula hot water supply apparatus: annual energy efficiency) the chart of relation, transverse axis is the internal diameter (mm) of evaporator refrigerant stream, and the longitudinal axis is APF.
Fig. 8 is the chart that schematically represents that the refrigerant temperature of the carbon dioxide coolant from the entrance of evaporator refrigerant stream to outlet distributes, and transverse axis is the length (mm) of evaporator refrigerant stream, the longitudinal axis be refrigerant temperature (DEG C).
Fig. 9 (a) be with the Wen degree of the carbon dioxide coolant shown in Fig. 8 Shang Sheng that ⊿ T is illustrated in after the fork of the 3rd shown in Fig. 2 after stream and the 4th fork in stream accordingly, the schematic diagram of the variations in temperature of the carbon dioxide coolant of carbon dioxide coolant while flowing to refrigerant outlet portion in the refrigerant inlet portion from evaporimeter.Fig. 9 (b) be with the Wen degree of the carbon dioxide coolant shown in Fig. 8 Shang Sheng that ⊿ T is illustrated in after the 3rd fork as a comparative example after stream and the 4th fork in stream accordingly, the schematic diagram of the variations in temperature of the carbon dioxide coolant of carbon dioxide coolant while flowing to refrigerant outlet portion in the refrigerant inlet portion from evaporimeter.
Figure 10 be the heating efficiency Q that represents carbon dioxide heat-pump formula hot water supply apparatus with the fork being determined by distributor before the chart of relation of the best fork number (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 stereogram of the evaporimeter of the carbon dioxide heat-pump formula hot water supply apparatus of other embodiments.
In figure:
1-distributor, 2-interflow portion, 3-fins set, 4-evaporator refrigerant stream, stream before 5-fork, stream after the 6-the first fork, stream after the 7-the second fork, stream after the 8-the three fork, stream after the 9-the four fork, stream after the 10-the five fork, stream after the 11-the six fork, 100-compressor, 101-water refrigerant heat exchanger, 102-expansion valve, 103-evaporimeter, 104-storage hot-water cylinder, 105-circulating pump.
Detailed description of the invention
The carbon dioxide heat-pump formula hot water supply apparatus (CO of embodiments of the present invention
2heat pump type hot water supply apparatus) principal character be, when the internal diameter of evaporator refrigerant stream being made as to 4.3mm～4.9mm, the heating efficiency for water of heat pump type hot water supply apparatus being made as to Q, when the stream fork number of described evaporator refrigerant stream is made as to P, meeting following relational expression (1):
P≤64/33×Q...（1）
Below, explain the embodiment of carbon dioxide heat-pump formula hot water supply apparatus of the present invention with reference to suitable accompanying drawing.In addition, below the front and back above-below direction in explanation is taking the fore-and-aft direction up and down shown in Fig. 2 as benchmark, that is, and and taking vertical direction top as upside, taking the upstream side of air that flows into evaporimeter as front side.In addition, the left and right directions in the following description is taking the left and right directions shown in Fig. 2 as benchmark, that is, taking observe from the upstream side of air stream evaporimeter towards right-hand 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 hot water supply apparatus (following, to be sometimes called for short and to make " heat pump hot-water supply device ") of present embodiment has heat pump cycle and the circulation of water side.
As shown in Figure 1, heat pump cycle is following structure: be encapsulated into carbon dioxide coolant (CO being in the circular stream that connects each key elements such as compressor 100, water refrigerant heat exchanger 101, expansion valve 102 and evaporimeter 103 (ring-type)
2cold-producing medium).
In addition, water side circulation is following structure: be full of water being in the circular stream that connects each key elements such as storage hot-water cylinder 104, circulating pump 105 and water refrigerant heat exchanger 101 (ring-type).
Evaporimeter 103 multiple for stream is divided into (being six streams in Fig. 1) carries out heat exchange, and expansion valve 102 between dispose distributor 1, and compressor 100 between dispose interflow portion 2.
Fig. 2 is the stereogram of evaporimeter 103, also shows particularly the structure from expansion valve 102 to interflow portion 2 in Fig. 1.
As shown in Figure 2, evaporimeter 103 is evaporimeters of intersection fin tube type, possesses fins set 3 and multiple evaporator refrigerant stream 4(evaporator refrigerant stream group as the thermal conductive surface of air side).Particularly, fins set 3 is made up of tabular multiple fins, and the plate face that is configured to fin overlaps each other in the relative mode in predetermined gap ground of being separated by.And air flows between the plate face of the fin of fins set 3.
Though not shown, evaporator refrigerant stream 4 roughly runs through each fin of fins set 3 orthogonally, thereby is fixed on each fin.Particularly, evaporator refrigerant stream 4, after roughly having run through orthogonally each fin of fins set 3, turns back and again roughly runs through orthogonally each fin of fins set 3.That is to say, run through multiple evaporator refrigerant stream 4(evaporator refrigerant stream groups of fins set 3) with the length direction of evaporator refrigerant stream 4 with the orthogonal direction of air stream on the mode of arranging configure.The internal diameter that forms the conduit of the evaporator refrigerant stream 4 of present embodiment is set as 4.6mm, and its external diameter is set as 5.0mm.
Such evaporimeter 103 amounts to two row by the entrance side (prostatitis side) of air with outlet side (rank rear side) etc. and forms.
Next, the structure to the stream of interflow portion 2 via evaporimeter 103 is described from expansion valve 102.
The formation fork of the bifurcation point from expansion valve 102 to distributor 1, the internal diameter of the conduit of stream 5 is set as 4mm, forms the length L of the conduit of the front stream 5 of fork
edbe set as 60mm.
Before fork, stream 5 is bifurcated into after the first fork after stream 6, the second fork after stream 7, the 3rd fork after stream 8, the 4th fork after stream 9, the 5th fork after stream 10 and the 6th fork stream 11 etc. by distributor 1 and amounts to six articles of streams.
After the each fork having diverged in stream 6～11, after the first fork, after stream 6, the rear stream 8 of the 3rd fork and the 5th fork, stream 10 is connected with the rank rear left side of evaporimeter 103, roughly runs through orthogonally each fin of fins set 3 the rank rear right side towards evaporimeter 103.Explanation in passing, run through after stream 6 after the first fork of fins set 3, the 3rd fork stream 8 and the 5th fork after stream 10 form described evaporator refrigerant stream 4.
Though be not shown, thereby in the way of extending upward, turn back to the left and again run through fins set 3 again towards the rank rear left side of evaporimeter 103 towards stream 10 after stream 8 after stream 6, the 3rd fork after first fork on the rank rear right side of evaporimeter 103 and the 5th fork.In addition, after the first fork, after stream 6, the 3rd fork, after stream 8 and the 5th fork, stream 10 carries out equally more once running through fins set 3 and again towards the rank rear left side of evaporimeter 103 toward ground return above evaporimeter 103, then, extend to front side and be connected with the left side, prostatitis of evaporimeter.
After the l fork being connected with the left side, prostatitis of evaporimeter 103, after stream 6, the rear stream 8 of the 3rd fork and the 5th fork, stream 10 roughly runs through each fin of fins set 3 right side, prostatitis towards evaporimeter 1 orthogonally.And, though not shown, thus fins set 3 again run through again on the left of the prostatitis of evaporimeter towards turning back to the left in stream 10 way of extending downwards after stream 8 after stream 6, the 3rd fork after first fork on right side, prostatitis and the 5th fork.In addition, after the first fork after stream 6, the 3rd fork after stream 8 and the 5th fork stream 10 below evaporimeter 103, carry out equally more once running through fins set 3 and again towards the left side, prostatitis of evaporimeter 103, stretching out to the interflow portion 2 of front side toward ground return.
On the other hand, after the each fork having diverged, in stream 6～11, after the second fork, stream 7 is connected with the rank rear left side of evaporimeter 103 adjacently with it below the rear stream 6 of described the first fork.After the 4th fork, stream 9 is connected with the rank rear left side of evaporimeter 103 adjacently with it below the rear stream 8 of described the 3rd fork.After the 6th fork, stream 11 is connected with the rank rear left side of evaporimeter 103 adjacently with it below the rear stream 10 of described the 5th fork.
After the second fork being connected with the rank rear left side of evaporimeter, after stream 7, the rear stream 9 of the 4th fork and the 6th fork, stream 11 roughly runs through each fin of fins set 3 the rank rear right side towards evaporimeter 103 orthogonally.In passing explanation, run through fins set 3 second fork after stream 7, the 4th fork after stream 9 and the 6th fork after stream 11 form described evaporator refrigerant stream 4.
Though be not shown, thereby in the way of extending downwards towards stream 11 after stream 9 after stream 7, the 4th fork after second fork on the rank rear right side of evaporimeter 103 and the 6th fork, turn back to the left and run through fins set 3 again on the left of the rank rear of evaporimeter 103.In addition, after the second fork, after stream 7, the 4th fork, after stream 9 and the 6th fork, stream 11 carries out equally more once running through fins set 3 and again towards the rank rear left side of evaporimeter 103 toward ground return below evaporimeter 103, then, extend to front side and be connected with the left side, prostatitis of evaporimeter 103.
After the second fork being connected with the left side, prostatitis of evaporimeter 103, after stream 7, the rear stream 9 of the 4th fork and the 6th fork, stream 11 roughly runs through each fin of fins set 3 right side, prostatitis towards evaporimeter 103 orthogonally.And, though not shown, thereby the rear stream 7, the 4th that diverges towards second of right side, prostatitis diverges, rear stream 9 and the rear stream 11 of the 6th fork turn back to the left and again run through fins set 3 again on the left of the prostatitis of evaporimeter 103 in the way of extension upward.In addition, after the second fork, after stream 7, the rear stream 9 of the 4th fork and the 6th fork, stream 11 carries out equally more once running through fins set 3 and again towards the left side, prostatitis of evaporimeter 103, stretching out to the interflow portion 2 of front side toward ground return above evaporimeter 103.
In addition after the first fork stretching out to interflow portion 2, after stream 6 and the second fork stream 7 each other, after the 3rd fork after stream 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 in the prostatitis left side of evaporimeter 103 adjacency respectively.
And after each fork, stream 6～11 starts to be connected with interflow portion 2 from evaporimeter 103, again becomes a stream.
Next, the see figures.1.and.2 action of the carbon dioxide heat-pump hot water supply apparatus to present embodiment describes.
Carbon dioxide coolant is compressed by compressor 100 and becomes high temperature, high pressure conditions.The carbon dioxide coolant of this high temperature, high pressure carries out heat exchange by water refrigerant heat exchanger 101 and the water transporting by circulating pump 105 from storage hot-water cylinder 104, and water boil is become to boiling water and loses heat.The hot amount of movement of the time per unit from carbon dioxide coolant to water now becomes heating efficiency Q.This heating efficiency Q is equivalent to " heating efficiency " described in claims, in the present embodiment, supposes to be set as 4.5kw.
Next, carbon dioxide coolant becomes the gas-liquid mixed state (gas-liquid two-phase flow) of low temperature, low-pressure state by contracted flow portion (omitting diagram) at expansion valve 102.And carbon dioxide coolant branches in the rear stream 6～11 of fork by distributor 1.And, carbon dioxide coolant flow through be divided into fork after stream 6～11 ground while running through respectively the evaporator refrigerant stream 4 of fins set 3, owing to connecing and evaporating by heat from air.Then, the cold-producing medium flowing out from evaporimeter 103 collaborates and after turning back to a stream, returns to compressor 100 in interflow portion 2, again compressed and pass out in heat pump cycle.
Next, illustrate in greater detail the action of the carbon dioxide coolant from expansion valve 102 to distributor l.Fig. 3 is the schematic diagram that represents the flow regime in the downstream of expansion valve 102.
As shown in Figure 3, the carbon dioxide coolant flowing out from expansion valve 102 is because the decline of pressure becomes the two-phase state of gas and cold-producing medium.Particularly, carbon dioxide coolant becomes the spray flow that is mixed with liquid refrigerant in the gas refrigerant as the continuous phase bubble flow (not shown) of gas refrigerant (or be mixed with in liquid refrigerant as continuous phase) near expansion valve 102, forms in the region of leaving expansion valve 102 the mobile annular flow of mode that covers the internal perisporium of stream with liquid refrigerant.
The internal diameter of stream is larger, and refrigerant flow is larger, far away apart from the refrigerant outlet portion of expansion valve 102 to the transition point of annular flow from spray flow (or bubble flow (omitting diagram)).In addition, if consider for the cold-producing medium of evaporimeter 103 and distribute, in annular flow, there is following situation: the bias current meeting of the departing from of the gas-liquid being caused by the inclination of distributor 1, carbon dioxide coolant self causes maldistribution, and result, can not obtain the performance of evaporator that should obtain.On the other hand, in spray flow, can not be subject to these stablize with affecting and distribute uniformly.
Therefore, when utilizing stream 6～11 after fork in the situation of streams formation evaporator refrigerant streams 4 of many forks, annular flow and spray flow relatively in, utilize spray flow to distribute for the decline that prevents performance particularly important.
Next Fig. 4 of institute's reference is spray flow, the gas-liquid mixed region of bubble flow and the chart of the measurement result of the transition point in the gas-liquid separation region of the annular flow of formation carbon dioxide coolant that represents to form carbon dioxide coolant, transverse axis represents heating efficiency Q(kw), the longitudinal axis represents x/D
ed 0.28(x is the flow path length (m) of the distance expansion valve 102 shown in Fig. 3, D
edthe internal diameter (m) of the front stream 5 of fork in the downstream of the expansion valve 102 shown in Fig. 2).
Explanation in passing, the transition point in the gas-liquid mixed region shown in Fig. 4 and gas-liquid separation region carries out simulated test under minimum frosting phase condition and tries to achieve by showing that in the performance of the heat pump hot-water supply device of heating efficiency 4.5kw flow in needed experimental condition, carbon dioxide coolant is realized.
As shown in Figure 4, meet x/D
ed 0.28=0.169Q
0.36the curve of this relational expression represents the transition point in gas-liquid mixed region and gas-liquid separation region, than the top side's of this curve region (x/D
ed 0.28large region) be gas-liquid separation region, form the region of annular flow, than this curve region (x/D on the lower
ed 0.28little region) be gas-liquid mixed region, form the region of spray flow or bubble flow.
Therefore, in the present embodiment, for the carbon dioxide coolant to distributor 1 distribution spray stream or bubble flow, wish to meet the following formula (3) being specifically described in the back:
L
ed/D
ed 0.28＜0.169Q
0.36...（3）
(wherein, L
edthe length (mm) of stream 5 fork of the bifurcation point from expansion valve 102 to distributor 1 shown in Fig. 2, D
edbe 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 mentioned above, by stream inner diameter D
edbe made as 4mm, heating efficiency Q is made as to 4.5kw, therefore, in order to calculate APF(Annual Performance Factor: annual energy efficiency, below unified writing APF) carbon dioxide coolant of spray flow or bubble flow is dispensed to distributor 1 under needed total Test condition, the flow path length (m) of the distance expansion valve 102 shown in Fig. 3 must be less than 61.9mm(x < 61.9mm).
For above-mentioned reasons, in the present embodiment, by the length L of stream 5 fork of the bifurcation point from expansion valve 102 to distributor 1
ed(with reference to Fig. 2) is set as 60mm.
Next, describe for the relation of the fork number of stream 5 and the internal diameter of evaporator refrigerant stream 4 before fork in the carbon dioxide heat-pump hot water supply apparatus of present embodiment, that determined by distributor 1.
Next Fig. 5 of institute's reference is the type of flow line chart for carbon dioxide coolant, and transverse axis is cold-producing medium aridity, and the longitudinal axis is mass velocity (kg/m
2s).
As shown in Figure 5, the region representation that surrounded by line ABCD forms the region of laminar flow, and in layered stream, gas refrigerant and liquid refrigerant depart from and be divided into two-layer flow in conduit.
In addition, between online A and line C, speed quality is greater than the region representation gas refrigerant of line D and liquid refrigerant and forms in conduit the region of described annular flow.If evaluate laminar flow and annular flow from the viewpoint of thermal conductivity, annular flow is owing to producing explosive evaporation and can obtain high thermal conductivity to flow evaporator at whole tube wall.On the other hand, in laminar flow, a part for the inner peripheral surface of conduit contacts with gas refrigerant, therefore, does not produce explosive evaporation in this part, with annular flow phase specific thermal conductivity step-down.Therefore,, in order to utilize identical heat-conducting area to obtain higher heat conductivility, need in stream, form annular flow.
And, in the present embodiment, the speed quality based on shown in Fig. 5 and the relation of aridity, utilizing simulated test to calculate a part in evaporator refrigerant stream 4 becomes the threshold value of annular flow.This result shown in Figure 6.Fig. 6 is the relation of the fork number of stream 5 and the internal diameter of evaporator refrigerant stream 4 before the fork representing based on being determined by distributor 1 and utilize a part in the evaporator refrigerant stream 4 that simulated test calculates to become the chart of the result of calculation of the threshold value of annular flow, transverse axis is the internal diameter (mm) of evaporator refrigerant stream 4, the longitudinal axis is the fork number of stream 5 before the fork being determined by distributor 1, in Fig. 6, be denoted as respectively " evaporator refrigerant stream internal diameter (mm) " and " stream fork number ".Explanation in passing, the transition point that becomes annular flow from laminar flow calculates and tries to achieve by showing that in the performance of the heat pump hot-water supply device of heating efficiency 4.5kw flow needed experimental condition, carbon dioxide coolant is realized under minimum frosting phase condition.
In Fig. 6, the line that has linked black circle "●" with straight line is the threshold value of the mutual transformation of generation laminar flow and annular flow.The region of the laminar flow that the region representation thermal conductivity larger than this linear flow road fork number is low, the region of the annular flow that the region representation thermal conductivity less than this linear flow road fork number is high.In addition, the stream fork number of the longitudinal axis in Fig. 6 is natural number scale, the internal diameter of the position of the predetermined fork of expression number that therefore, can be on the longitudinal axis evaporator refrigerant stream 4 that decision is best in the scope of the evaporator refrigerant stream internal diameter (mm) of the defined each other of two black circle "●" arranged side by side mutually.Particularly, for example, in Fig. 6, in the time that stream fork number is 6, the threshold value that becomes annular flow is that evaporator refrigerant stream internal diameter (mm) is in the scope of 4.4mm～4.7mm.
Next, describe for the specification of evaporimeter 103 and the relation of performance of the heat pump type hot water supply apparatus of present embodiment.Fig. 7 is the internal diameter (mm) that represents evaporator refrigerant stream 4 and the chart that represents the result of calculation of the relation of the APF of the performance of heat pump hot-water supply system, transverse axis is the internal diameter (evaporator refrigerant stream internal diameter mm) of evaporator refrigerant stream 4, and the longitudinal axis is APF.
In addition, the internal diameter with evaporator refrigerant stream 4 herein corresponding, the threshold value shown in fork number (the stream fork number) application drawing 6 of stream 5 before the fork that determined by distributor 1.Its object is, because the pressure loss between the stream fork larger evaporimeter of number gateway is less, so obtain best performance by taking into account high thermal conductivity and low pressure loss.In addition, the calculating of APF is carried out as the fixing mode of the fin material price of the air side thermal conductive surface of evaporimeter 103 and the summation of the refrigerant pipe price as evaporator refrigerant stream 4 making.
Known as shown in Figure 7: the internal diameter (in Fig. 7, being the evaporator refrigerant stream internal diameter (mm) of transverse axis) of evaporator refrigerant stream 4 is less, and APF is larger, thus the performance of heat pump type hot water supply apparatus improves.This be considered to because: in order to ensure a certain size the heat-conducting area of refrigerant flow path, the internal diameter of evaporator refrigerant stream 4 is thinner, and the quantity of stream more increases, and stream interval to each other more reduces simultaneously.That is to say, this be considered to because: thereby heat conduct to equably fins set 3 fin efficiencies improve.But known: to be accompanied by the performance increase rate that the internal diameter of evaporator refrigerant stream 4 reduces and to slow down as boundary taking internal diameter 4.6mm.This reason is used ensuing Fig. 8,9 to describe.
Fig. 8 is the chart that schematically represents that the refrigerant temperature from the entrance of evaporator refrigerant stream 4 to outlet distributes, and transverse axis is the length (mm) of evaporator refrigerant stream, the longitudinal axis be refrigerant temperature (DEG C).
Evaporimeter 103(is with reference to Fig. 2) liquid refrigerant evaporates is being become in the characteristic of gas refrigerant, as shown in Figure 8, near the outlet side of evaporimeter 103, evaporation finishes completely, the upper ⊿ T(DEG C that rises of Wen Du of cold-producing medium).
Next Fig. 9 (a) of institute's reference be with the Wen degree of the carbon dioxide coolant shown in Fig. 8 Shang Sheng that ⊿ T is illustrated in after the fork of the 3rd shown in Fig. 2 after stream and the 4th fork in stream accordingly, the schematic diagram of the variations in temperature of the carbon dioxide coolant of carbon dioxide coolant while flowing to refrigerant outlet portion in the refrigerant inlet portion from evaporimeter 103.Fig. 9 (b) be with the Wen degree of the carbon dioxide coolant shown in Fig. 8 Shang Sheng that ⊿ T is illustrated in after the 3rd fork as a comparative example after stream and the 4th fork in stream accordingly, the schematic diagram of the variations in temperature of the carbon dioxide coolant of carbon dioxide coolant while flowing to refrigerant outlet portion in the refrigerant inlet portion from evaporimeter.
As shown in Fig. 9 (a), after the 3rd fork of described embodiment after stream 8 and the 4th fork stream 9 as described above from distributor 1(with reference to Fig. 2) stream 8 and the rear stream 9 of the 4th fork abut one another the 3rd fork that extends position is connected with fins set 3 and forms the refrigerant inlet portion of evaporimeter 103.In addition, from evaporimeter 103 towards the 2(of interflow portion with reference to Fig. 2) the 3rd fork after stream 8 and the 4th fork stream 9 as described above in the refrigerant outlet portion of the position formation evaporimeter 103 adjoining each other.
On the other hand, after the 3rd fork of the comparative example shown in Fig. 9 (b) after stream 8 and the 4th fork after stream 9 and the 3rd shown in Fig. 9 (a) fork after stream 8 and the 4th fork stream 9 different, the refrigerant inlet portion of evaporimeter 103 and refrigerant outlet portion with via be configured on the above-below direction of fins set 3 be divided into three sections evaporator refrigerant stream 4 and mutual away from mode form.
And as shown in Fig. 9 (a) and Fig. 9 (b), the evaporator refrigerant stream 4 that runs through fins set 3 utilizes via the fin of fins set 3 mutually adjacent stream to carry out heat exchange shown in hollow arrow.Compared with the situation that does not have the heat exchange of being undertaken by fins set 3 with hypothesis, in the time carrying out above-mentioned heat exchange, generally, the hydraulic performance decline of heat pump hot-water supply device thereby the evaporator refrigerant stream 4 of high temperature side is cooled.
In addition, the interval between evaporator refrigerant stream 4 is less, conducts the hot amount of movement carrying out larger by heat.Therefore, more make evaporator refrigerant stream 4 tiny and improve stream density, the performance of heat pump hot-water supply device is more because heat conducting impact is difficult to improve.In addition, the refrigerant superheat degree of the outlet of evaporimeter 103 is higher, and the hydraulic performance decline of the heat pump hot-water supply device that the heat of the fin of fins set 3 causes is more obvious.In addition, in heat pump cycle, not possessing refrigerant amount adjusts the heat pump hot-water supply device of function and has the characteristic that the higher refrigerant superheat degree of atmospheric temperature more rises.
The carbon dioxide coolant representing with " low temperature " in the evaporator refrigerant stream 4 of the carbon dioxide coolant that in addition, the carbon dioxide coolant in the evaporator refrigerant stream 4 of " the refrigerant outlet portion of evaporimeter 103 " in the comparative example shown in Fig. 9 (b) represents with " high temperature " in Fig. 9 (b) and thereunder adjacency carries out heat exchange.Therefore,, in the comparative example shown in Fig. 9 (b), the hydraulic performance decline amount of the heat pump hot-water supply device that heat causes is large.On the other hand, in the present embodiment shown in Fig. 9 (a), the carbon dioxide coolant representing with " high temperature " in the evaporator refrigerant stream 4 of " the refrigerant outlet portion of evaporimeter 103 " with and the evaporator refrigerant stream 4 of its adjacency in the carbon dioxide coolant representing with " middle temperature " carry out heat exchange.
Therefore, in the embodiment shown in Fig. 9 (a), stream 9 after stream 8 and the 4th fork after the 3rd fork of evaporator refrigerant stream 4(Fig. 9 (a) by " the refrigerant outlet portion of evaporimeter 103 ") abut one another, can improve the performance of heat pump hot-water supply device.
As described in the explanation of above Fig. 4 to Fig. 9 being carried out, 4.6mm is suitable as the internal diameter of evaporator refrigerant stream 4, in addition, by using the flow passage structure shown in Fig. 9 (a), can alleviate the hydraulic performance decline that heat causes.And, consider the deviation of manufacture etc., also need the scope of the internal diameter that specifies the evaporator refrigerant stream 4 that can allow.
As described in the explanation that Fig. 6 carries out as utilized, stream fork number while selecting 4.6mm as the internal diameter of evaporator refrigerant stream 4 is 6, but, even in the case of stream internal diameter due to the deviation etc. of manufacturing from 4.6mm departs from, as long as the internal diameter of the evaporator refrigerant stream 4 shown in the transverse axis of Fig. 6, can corresponding (setting) best stream fork number P in the scope of 4.4mm～4.7mm.
Referring again to Fig. 7, when stream fork number due to the selection of refrigerant flow but 7(with reference to the upside transverse axis of Fig. 7) time, the inside diameter ranges of the evaporator refrigerant stream 4 allowing is at 4.4mm～4.7mm, when stream fork number is the upside transverse axis of 6(with reference to Fig. 7) time, the inside diameter ranges of the evaporator refrigerant stream 4 of permission is at 4.6mm～4.9mm.That is to say, even if the internal diameter of the evaporator refrigerant stream 4 that deviation of considering manufacture etc. causes departs from from 4.6mm, as long as the internal diameter of the evaporator refrigerant stream 4 shown in Fig. 7, can corresponding (setting) best stream fork number P in the scope of 4.3mm～4.9mm.Explanation in passing, the inside diameter ranges of the evaporator refrigerant stream 4 corresponding with the stream fork number (6 or 7) of the upside transverse axis of Fig. 7 is as allowing the scope of laminar flow to be calculated and tried to achieve by simulated test under the low refrigerant flow conditions such as frosting phase.
Next, for the heating efficiency Q(kW of heat pump hot-water supply device) with the fork being determined by distributor 1 before the relation of the best fork number (stream fork number P) of stream 5 describe.Figure 10 is the chart that represents the relation of the best fork number (stream fork number P) of stream before the heating efficiency Q of Teat pump hot water supply device and the fork that determined by distributor, and transverse axis is heating efficiency Q(kw), the longitudinal axis is stream fork number P.That is to say, the chart shown in Figure 10 at the internal diameter of evaporator refrigerant stream 4 is 4.6mm as described above, try to achieve by utilizing simulated test to calculate the diverge relation of number P of heating efficiency Q that carbon dioxide coolant in evaporator refrigerant stream 4 becomes annular flow and stream.In Figure 10, be represented by dotted lines the result of the frosting phase condition of calculating the refrigerant flow minimum in the condition of APF, represent to calculate with solid line refrigerant flow maximum in the condition of APF summer condition result.
As shown in figure 10, for the frosting phase, the threshold value of condition represents with P=4/3 × Q, and for summer, the threshold value of condition represents with P=64/33 × Q.And the region that stream fork number P is less than threshold value is separately the region that the carbon dioxide coolant in evaporator refrigerant stream 4 becomes annular flow.
Therefore,, under summer condition benchmark, meet described formula (1) by setting:
P≤64/33×Q...（1）
The heating efficiency Q(kw of this relational expression) and stream fork number P can make the carbon dioxide coolant in evaporator refrigerant stream 4 become annular flow.
In addition, under frosting phase condition benchmark, if meet formula (2):
P≤4/3×Q...（2）
This relational expression, can, calculating under the needed full terms of APF, make the carbon dioxide coolant in evaporator refrigerant stream 4 become annular flow.In the present embodiment, in order to guarantee high-performance under full terms, in formula (2): in P≤4/3 × Q, suppose that heating efficiency Q is that situation, the stream fork number P of described 4.5kw is 6.
In addition, in the present embodiment, the situation that is 4.5kw to heating efficiency Q is recorded, but as long as do not hinder problem of the present invention, can suitably set heating efficiency Q.
According to the carbon dioxide heat-pump formula hot water supply apparatus of present embodiment that possesses above-mentioned evaporimeter 103, by making the internal diameter of evaporator refrigerant stream 4 in the scope 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 of evaporator refrigerant stream 4 inside can be in the needed experimental condition of calculating of APF of performance that represents carbon dioxide heat-pump formula hot water supply apparatus, refrigerant flow becomes under maximum condition, become the annular flow that thermal conductivity is high, therefore, can obtain high-performance.
In addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, be made as described formula (2) by number P that stream is diverged: the value in the scope of P≤4/3 × Q, can calculate under the needed total Test condition of APF, make the type of flow of evaporator refrigerant stream 4 become the annular flow that thermal conductivity is high, therefore, can under full terms, obtain high-performance.
In addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, be made as and meet described formula (2) by number P that stream is diverged: the natural maximum of the P of this relation of P≤4/3 × Q (for example, described stream fork number P=6 in present embodiment), not only improve thermal conductivity, can also obtain the effect that reduces the refrigerant side pressure loss, therefore can obtain better performance.
In addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, by close to each other the refrigerant outlet portion that configures multiple evaporator refrigerant streams 4, compared with situation about keeping off with the refrigerant outlet portion of multiple evaporator refrigerant streams 4, can prevent the hydraulic performance decline causing via the heat conducting impact of fins set 3, significantly improve the performance of evaporimeter 103.
In addition, according to this carbon dioxide heat-pump formula hot water supply apparatus, evaporimeter 103 will inevitably have multiple forks, therefore, carries out the uniform distribution of carbon dioxide coolant in order to give full play to performance need, meets following formula (3) by selection:
L
ed/D
ed 0.28＜0.169Q
0.36...（3）
(L
ed, D
edand Q is identical with above-mentioned meaning) value, the cold-producing medium stream flowing out from expansion valve 102 can maintain gas-liquid mixed state and flow into stream branched portion, no matter how stream fork number P distributes with uniform flow and aridity.
According to above-mentioned present embodiment, inside diameter ranges and the stream fork number P of the optimal evaporation device refrigerant flow path 4 of the deviation of manufacturing can be considered for heating efficiency Q selection arbitrarily, therefore, can provide and possess the carbon dioxide heat-pump formula hot water supply apparatus evaporimeter that can make according to heating efficiency Q the evaporimeter 103 of maximizing performance.
Above, be illustrated for embodiments of the present invention, but the present invention is not limited to described embodiment, but can implements with various forms.In other embodiments of following explanation, mark identical symbol and description is omitted for the inscape identical with described embodiment.
Next Figure 11 of institute's reference is the stereogram of the evaporimeter of the carbon dioxide heat-pump hot water supply apparatus of other embodiments.In Figure 11, symbol 1 represents distributor, and symbol 2 represents interflow portion, symbol 3 represents fins set, symbol 5 represents stream before fork, and symbol 6 represents stream after the first fork, and symbol 7 represents stream after the second fork, symbol 8 represents the rear stream of the 3rd fork, symbol 9 represent the 4th fork after stream, symbol 10 represent the 5th fork after stream, symbol 11 represent the 6th fork after stream, symbol 102 represents expansion valve, and symbol 103 represents evaporimeter.
As shown in figure 11, compared with the evaporimeter 103 of the described embodiment shown in Fig. 2, the columns that the evaporimeter 103 of the carbon dioxide heat-pump hot water supply apparatus of other embodiments becomes fins set 3 increases by row and amounts to the formations of three row, therefore flow passage structure difference.In addition the heating efficiency Q that, supposes to possess the heat pump hot-water supply device of the evaporimeter 103 shown in Figure 11 is 6.0kW.
Compared with the device shown in Fig. 2, because the columns of fins set 3 increases, evaporator refrigerant stream 4 increases the evaporimeter 103 shown in Figure 11.Therefore, become the large specification of the pressure loss between the refrigerating fluid discharging and feeding of evaporimeter 103.
On the other hand, in the formula shown in Figure 10, because the project of the pressure loss does not exist, so can apply the theory identical with described embodiment.
That is to say, when in formula (2): while heating efficiency Q being made as to 6kw in P≤4/3 × Q, P≤8, therefore, are applicable to making stream fork number P for as peaked " 8 " from reducing the viewpoint of the pressure loss.But from the viewpoint of production, preferred flow path fork number P is consistent in the body of power output 4.5kw and power output 6.0kw, the number that therefore stream diverged is made as " 6 ", and selection can be brought into play high performance specification for multiple heating efficiency Q.
In addition, in said embodiment, the heat pump cycle with compressor 100, water refrigerant heat exchanger 101, expansion valve 12 and evaporimeter 103 shown in Fig. 1 is illustrated, but, the present invention also can be applicable to also comprise the heat pump cycle of refrigerant amount guiding mechanism, inner heat exchanger etc., and described inner heat exchanger makes the cold-producing medium of high-pressure side and low-pressure side carry out heat exchange.
Claims (5)
1. a carbon dioxide heat-pump formula hot water supply apparatus, form by least connecting in the form of a ring each key elements such as compressor, water refrigerant heat exchanger, expansion valve and evaporimeter and entering carbon dioxide coolant at stream inner sealing, described carbon dioxide heat-pump formula hot water supply apparatus is characterised in that
Described evaporimeter be by using approximate right angle the fixing thermal conductive surface as air side of the mode that runs through fins set and by with the orthogonal direction of air stream on the evaporator refrigerant stream group that forms of multiple evaporator refrigerant streams of arranging, between air and cold-producing medium, carry out the evaporimeter that intersects fin tube type of heat exchange
The internal diameter of the described evaporator refrigerant stream of described evaporimeter is 4.3mm～4.9mm,
When the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus being made as to Q, the stream fork number of described evaporator refrigerant stream being made as in the situation of P, meet following formula (1):
P≤64/33×Q...（1）。
2. carbon dioxide heat-pump formula hot water supply apparatus according to claim 1, is characterized in that,
When the described stream fork number of described evaporator refrigerant stream is made as in the situation of P, 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.
3. carbon dioxide heat-pump formula hot water supply apparatus according to claim 2, is characterized in that,
The described stream fork number P of described evaporator refrigerant stream is the natural maximum that meets described (2) formula.
4. carbon dioxide heat-pump formula hot water supply apparatus according to claim 1, is characterized in that,
In the refrigerant outlet portion of described evaporimeter, configure multiple described evaporator refrigerant streams in the mode approaching.
5. carbon dioxide heat-pump formula hot water supply apparatus according to claim 1, is characterized in that,
Meet following formula (3):
L
ed/D
ed 0.28＜0.169Q
0.36...（3）
L
edthe length of stream the fork of the bifurcation point from expansion valve to distributor, D
edbe the internal diameter of the front stream of fork in the downstream of described expansion valve, Q is the heating efficiency for water of carbon dioxide heat-pump formula hot water supply apparatus.
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| JP2013103653A JP5943206B2 (en) | 2013-05-16 | 2013-05-16 | CO2 heat pump water heater |
| JP2013-103653 | 2013-05-16 |
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| JP (1) | JP5943206B2 (en) |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| 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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| 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 |
| US10760824B2 (en) * | 2015-12-17 | 2020-09-01 | Mitsubishi Electric Corporation | Heat exchanger and refrigeration cycle apparatus |
| 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 |
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Also Published As
| Publication number | Publication date |
|---|---|
| KR20140135586A (en) | 2014-11-26 |
| JP2014224637A (en) | 2014-12-04 |
| KR101520675B1 (en) | 2015-05-15 |
| CN104165458B (en) | 2016-12-28 |
| JP5943206B2 (en) | 2016-06-29 |
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