CN104006534A - Water heater - Google Patents
Water heater Download PDFInfo
- Publication number
- CN104006534A CN104006534A CN201410064728.0A CN201410064728A CN104006534A CN 104006534 A CN104006534 A CN 104006534A CN 201410064728 A CN201410064728 A CN 201410064728A CN 104006534 A CN104006534 A CN 104006534A
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- China
- Prior art keywords
- hot water
- thermal medium
- water
- cold
- storgae
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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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
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
- F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
Abstract
A water heater including: a refrigerant circuit 3 configured by annularly connecting, to one another through refrigerant pipes, a compressor 11, a first radiator 12, an expansion device 13, and an evaporator 14; a hot water tank 21; and a heat medium circuit 4 configured by annularly connecting, to one another through heat medium pipes, the first radiator 12, a second radiator 22, and a circulation device 23, wherein the refrigerant circulating through the refrigerant circuit 3 is carbon dioxide, and in the second radiator 22, the heat medium pipe is wound around an outer surface of the hot water tank 21, and the heat medium releases heat to water in the hot water tank 21. Therefore, it is possible to efficiently produce high temperature water while suppressing precipitation of scale.
Description
Technical field
The present invention relates to a kind of hot-water supply that utilizes source heat pump heat to generate high-temperature water.
Background technology
In prior art, this hot-water supply is heating water in the source heat pump heat that uses carbon dioxide coolant, compares with using the source heat pump heat of freon class cold-producing medium, generates the more hot water of high temperature.The high-temperature water generating is stored in hot water storgae, for supplying hot water (for example,, with reference to patent documentation 1).
Fig. 8 represents the hot-water supply described in patent documentation 1.As shown in Figure 8, this hot-water supply comprises: the heat pump unit 52 with gas cooler (supplying hot water heat exchanger) 51; The storage hot water unit 54 of the storage hot water storgae 53 of hot hot-water storage will be burnt with having in gas cooler 51.
Heat pump unit 52 comprises: with refrigerant piping, compressor 55, gas cooler 51, expansion valve (decompressor) 56, evaporimeter 57 are connected into the refrigerant loop of ring-type, as the carbon dioxide (CO of cold-producing medium
2) circulation therein.In addition, storage hot water unit 54 comprises: make hot water circuit circulating pump 58, storage hot water storgae 53, the feed pipe 60 supplying water to storage hot water storgae 53 from running water pipe, utilize the high-temperature water that is stored in hot water storgae 53 to carry out the heat supply water pipe 59 of supplying hot water.Water pipe arrangement connects into ring-type by circulating pump 58, storage hot water storgae 53, gas cooler 51, forms thus water loop.
By circulating pump 58, be stored in the water of hot water storgae 53 bottoms, be transported to gas cooler 51, in gas cooler 51, the water being transferred carries out heat exchange with the gas refrigerant of HTHP by after compressor 55 compression, generates high-temperature water (for example 85 ℃).The high-temperature water generating is transferred by water loop and is stored in hot water storgae 53, flows out for supplying hot water as required from heat supply water pipe 59.Like this, carbon dioxide, as cold-producing medium, is compared with using the situation of freon class cold-producing medium, can be generated the more water of high temperature.
In addition, existing other hot-water supplies, the heat-transfer pipe of reeling in the outside wall surface of storage hot water storgae, as the kind of refrigeration cycle of thermal source use steam compression type.The cold-producing medium of the HTHP of discharging from compressor is flow in the heat-transfer pipe that is wound in storage hot water storgae and water (for example,, with reference to patent documentation 2) in heating storage hot water storgae.
Fig. 9 represents the hot-water supply described in patent documentation 2.As shown in Figure 9, hot-water supply 100 comprises: the refrigerant loop 90 that makes refrigerant circulation; With the storage hot water storgae 110 of storing hot water.
Refrigerant loop 90 forms by compressor 101, storage hot water side heat exchanger 116, expansion gear 104 and air side heat exchanger 106 being connected into ring-type with refrigerant piping.
In storage hot water storgae 110, as storage hot water side heat exchanger 116, the mode contacting with the outside wall surface with storage hot water storgae 110 configures heat-transfer pipe.In addition, by feed pipe 119, to storage hot water storgae 110, supply water.
When the storage hot water running that generates high-temperature water, cold-producing medium flows in refrigerant loop 90 towards the direction of the solid arrow of Fig. 9.The cold-producing medium of the HTHP of the gas phase state of discharging from compressor 101 flow into storage hot water side heat exchanger 116, across the partition wall of storage hot water storgae 110 to inner water-cooled condensation.Consequently, cold-producing medium is phase-changed into cooled liquid state from gas-liquid two-phase state.That is, storage hot water side heat exchanger 116 plays a role as the condenser of cold-producing medium, in the inside of storage hot water storgae 110, generates high-temperature water.
The cold-producing medium of condensed cooled liquid state of liquefying in storage hot water side heat exchanger 116 is depressurized the gas-liquid two-phase state that becomes low pressure in expansion gear 104, and flow into air side heat exchanger 106(evaporimeter).Cold-producing medium is at air side heat exchanger 106(evaporimeter) thus in heat absorption evaporation from the extraneous air being attracted by outdoor fan 105, from gas-liquid two-phase state, be phase-changed into overheated gas state.Then, cold-producing medium flow in compressor 101 and is again compressed, and becomes the gas phase state of HTHP.
By carrying out this refrigerant circulation, the hot water of heating storage hot water storgae 110 inside, thus can store high-temperature water.
Look-ahead technique document
Patent documentation
Patent documentation 1: TOHKEMY 2011-69572 communique
Patent documentation 2: Japanese kokai publication sho 62-59337 communique
Summary of the invention
The problem that invention will solve
In patent documentation 1, by feed pipe 60, be supplied to the water of storage hot water storgae 53, in gas cooler 51, be heated with carbon dioxide coolant heat exchange.Therefore,, particularly in the situation that the many water of the contained hardness components of heating, in the gas cooler 51 and water pipe arrangement of flowing through at high-temperature water, hardness components is separated out as incrustation scale, thereby exist this composition of scale to pile up, causes water pipe arrangement to stop up such problem.
In order to suppress the accumulation of this composition of scale, in the structure of patent documentation 2, also there is the method for using carbon dioxide coolant to generate high-temperature water.But, in the situation that using carbon dioxide coolant, in order to bear with freon class cold-producing medium, compare the pressure of about 2～3 times, must increase the withstand voltage design of pipe arrangement caliber.Therefore, there is the machining period of pipe arrangement and the problem of processing cost increase that itself and the periphery of storage hot water storgae 110 are close to.
The present invention is exactly that its object is, provides a kind of and can suppress separating out of incrustation scale, and can generate efficiently the hot-water supply of high-temperature water in order to solve above-mentioned existing problem.
For solving the method for problem
In order to solve above-mentioned problem, hot-water supply of the present invention, it is characterized in that, comprise: refrigerant loop, its with refrigerant piping, by the compressor of compressed refrigerant, between above-mentioned cold-producing medium and thermal medium, carry out heat exchange the 1st radiator, make the expansion gear that above-mentioned cold-producing medium expands and make the evaporimeter of above-mentioned cold-producing medium evaporation connect into ring-type, above-mentioned cold-producing medium is in inner loop; The storage hot water storgae of storage of water; With thermal medium loop, it connects into ring-type with thermal medium pipe arrangement by above-mentioned the 1st radiator, the 2nd radiator and the EGR that carry out heat exchange between above-mentioned thermal medium and above-mentioned water, above-mentioned thermal medium is in inner loop, the above-mentioned cold-producing medium wherein circulating in above-mentioned refrigerant loop is carbon dioxide, in above-mentioned the 2nd radiator, above-mentioned thermal medium pipe arrangement is wound on the outer surface of above-mentioned storage hot water storgae, and the heat of above-mentioned thermal medium is to the above-mentioned water-cooled in above-mentioned storage hot water storgae.
The water that hardness components is many is heated to high temperature, and this high-temperature water waits in the pipe arrangement that caliber is little and flows near the thermal medium outlet of gas cooler, so especially easily there is separating out of incrustation scale.So, according to structure of the present invention, because of thermal medium loop and supplying hot water loop separated, so can effectively suppress separating out of incrustation scale.
In addition, use carbon dioxide coolant, thus, the high side pressure of refrigerant loop becomes supercritical range.Thus, can make the thermal medium that is equipped on the entrance side of storing the 2nd radiator in hot water storgae become high temperature, thermal medium mobile in the thermal medium pipe arrangement of the 2nd radiator increases with the temperature difference of storing the water in hot water storgae.Therefore, the internal circulating load of the thermal medium in the time of can reducing the water in heating storage hot water storgae, and guarantee to add heat.
Invention effect
According to the present invention, can provide a kind of and can suppress separating out of incrustation scale, and can effectively generate the hot-water supply of high-temperature water.
Accompanying drawing explanation
Fig. 1 is the summary construction diagram of the hot-water supply of an embodiment of the invention.
Fig. 2 is the structure chart of the storage hot water storgae of this hot-water supply.
Fig. 3 is the Mollier line chart that the kind of refrigeration cycle of the refrigerant loop of this hot-water supply of explanation changes.
Fig. 4 means the concept map that the water temperature in the storage hot water storgae of this hot-water supply changes.
Fig. 5 be this hot-water supply storage hot water when running running efficiency than with pipe range L/ pipe in the graph of a relation of sectional area S.
Fig. 6 is the pressure loss dP in storage hot water when running and the graph of a relation of the interior sectional area S of pipe range L/ pipe of this hot-water supply.
Fig. 7 means the caliber d of the thermal medium pipe arrangement of heat exchanger and the summary construction diagram of the relation of the contact length W of storage hot water storgae for storage hot water of this hot-water supply.
Fig. 8 is the summary construction diagram of existing hot-water supply.
Fig. 9 is the summary construction diagram of existing other hot-water supplies.
Reference numeral explanation
1 heat source unit
2 container units
3 refrigerant loops
4 thermal medium loops
5 supplying hot water loops
11 compressors
12 cold-producing mediums are to thermal medium heat exchanger (the 1st radiator)
13 expansion valves (expansion gear)
14 cold-producing mediums are to air heat exchanger (evaporimeter)
21 storage hot water storgaes
22 storages heat exchanger (the 2nd radiator) for hot water
23 circulating pumps (EGR)
The specific embodiment
The 1st invention is a kind of hot-water supply, it is characterized in that, comprise: refrigerant loop, its with refrigerant piping, by the compressor of compressed refrigerant, between above-mentioned cold-producing medium and thermal medium, carry out heat exchange the 1st radiator, make the expansion gear that above-mentioned cold-producing medium expands and make the evaporimeter of above-mentioned cold-producing medium evaporation connect into ring-type, above-mentioned cold-producing medium is in inner loop; The storage hot water storgae of storage of water; With thermal medium loop, it connects into ring-type with thermal medium pipe arrangement by above-mentioned the 1st radiator, the 2nd radiator and the EGR that carry out heat exchange between above-mentioned thermal medium and above-mentioned water, above-mentioned thermal medium is in inner loop, the above-mentioned cold-producing medium wherein circulating in above-mentioned refrigerant loop is carbon dioxide, in above-mentioned the 2nd radiator, above-mentioned thermal medium pipe arrangement is wound on the outer surface of above-mentioned storage hot water storgae, and the heat of above-mentioned thermal medium is to the above-mentioned water-cooled in above-mentioned storage hot water storgae.
The water that hardness components is many is heated to high temperature, and this high-temperature water waits in the pipe arrangement that caliber is little and flows near the thermal medium outlet of gas cooler, so especially easily there is separating out of incrustation scale.So according to structure of the present invention, thermal medium loop and supplying hot water loop are separated.That is, the Fluid Circulation of high temperature, the thermal medium loop easily occurring under temperature conditions that incrustation scale separates out becomes loop circuit.Thus, the fluid that hardness components the is many thermal medium loop of can not flowing through at any time, can suppress separating out of incrustation scale effectively.
In addition, use carbon dioxide coolant, thus, the high side pressure of refrigerant loop becomes supercritical range.Like this, in the 1st radiator, thermal medium is heated to high temperature, thereby can make the thermal medium of the entrance side of the 2nd radiator of reeling in the mode that contact of periphery with storage hot water storgae become high temperature, the temperature difference increase of the water in the thermal medium pipe arrangement of the 2nd radiator in mobile thermal medium and storage hot water storgae.Therefore, the internal circulating load of the thermal medium in the time of can reducing the water in heating storage hot water storgae, and guarantee to add heat.
In addition, by reducing the internal circulating load of thermal medium, thermal medium is to the water-cooled of storing in hot water storgae in the 2nd radiator, and temperature declines fully.Afterwards, from the 2nd radiator, flow out, flow into the 1st radiator.That is, the temperature that flow into the thermal medium of the 1st radiator declines, so the on high-tension side excessive pressure rise of refrigerant loop is suppressed.In addition, in thermal medium pipe arrangement, the internal circulating load of mobile thermal medium reduces, thus can suppress the increase of the pressure loss in thermal medium pipe arrangement, and can make the thermal medium pipe arrangement of the 2nd radiator increase or attenuate.
Therefore, suppress the decline of the running efficiency of compressor.In addition, by increasing the length of tube of thermal medium pipe arrangement, increase heat transfer area.In addition, the turbulent flow that promotes caliber because of thermal medium pipe arrangement to attenuate to produce is to increase hot percent of pass.Consequently, according to these synergies, can realize the high efficiency in storage hot water when running of hot-water supply.
The 2nd invention is characterized in that, particularly, in the 1st invention, the total length of establishing the above-mentioned thermal medium pipe arrangement that forms above-mentioned the 2nd radiator is L(m), in the pipe of above-mentioned thermal medium pipe arrangement, sectional area is S(mm
2) time, L/S(m/mm
2) be more than 2.8 below 5.3.
Thus, using carbon dioxide coolant, thereby heating in the hot-water supply of structure that water in storage hot water storgae generates high-temperature water by thermal medium, can improve to greatest extent running efficiency, and generate high-temperature water.
The 3rd invention is characterized in that, particularly, in the 1st or the 2nd invention, above-mentioned thermal medium flows downwards from the top of above-mentioned the 2nd radiator.
Thus, when the running of storage hot water, the water in storage hot water storgae is heated successively from top, the water temperature of the upper side in storage hot water storgae raises, and the water temperature of lower side maintains low temperature,, suppress the free convection of the hot water in storage hot water storgae, and in the inside formation temperature layering of storing hot water storgae.
Like this, the suitable temperature difference of water of the temperature of maintaining heat medium and storage hot water storgae inside.In addition, the temperature that can suppress to flow into the thermal medium of the 1st radiator rises, and heating water effectively.Therefore, can improve the energy saving as hot-water supply.
Below, with reference to accompanying drawing, embodiments of the present invention are described.But, and can't help present embodiment and limit the present invention.
Fig. 1 is the skeleton diagram of the hot-water supply of an embodiment of the invention.The hot-water supply of present embodiment comprises: for the heat source unit 1 of heat hot medium; Have for storing the container unit 2 of the storage hot water storgae 21 of the hot water being generated by heated thermal medium.
The hot-water supply of present embodiment comprises: heat pump unit; For example as thermal source, make the refrigerant loop 3 of refrigerant circulation; The thermal medium loop 4 of thermal medium circulation; Thereby the supplying hot water loop 5 of the hot water after being heated with the supply of supplying water in storage hot water storgae.In the present embodiment, use carbon dioxide (CO herein,
2) as the cold-producing medium of the inner loop at refrigerant loop 3, make water as the thermal medium of circulation in thermal medium loop 4.
Refrigerant loop 3 by with refrigerant piping by compressor 11, cold-producing medium to thermal medium heat exchanger 12, make expansion valve (expansion gear) 13, cold-producing medium that cold-producing medium expands connect into ring-type to air heat exchanger 14 to form.Cold-producing medium plays a role as the 1st radiator to thermal medium heat exchanger 12, carries out heat exchange between cold-producing medium and thermal medium.In addition, cold-producing medium comprises refrigerant flow path and the mobile thermal medium stream of thermal medium of flow of refrigerant to thermal medium heat exchanger 12, and cold-producing medium and thermal medium carry out heat exchange across the partition wall that forms each stream, generate thus the thermal medium of high temperature.Cold-producing medium is fin-tube heat exchangers to air heat exchanger 14, as evaporimeter, plays a role, and carries out heat exchange between cold-producing medium and air.Utilize the adjacent pressure fan setting 16, to cold-producing medium, air heat exchanger 14 is sent to air, the air of sending and cold-producing medium carry out heat exchange.
Thermal medium loop 4 utilizes thermal medium pipe arrangement that cold-producing medium is connected into ring-type and forms thermal medium heat exchanger 12, the expansion vessel 24 corresponding with the expansion of hot water, heat exchanger 22, the circulating pump (EGR) 23 for storage hot water playing a role as the 2nd radiator.
Storage hot water is spirally wound on the periphery of storage hot water storgae 21 by the mode that heat exchanger 22 contacts with the outer surface of storage hot water storgae 21 with thermal medium pipe arrangement.That is, the thermal medium of the high temperature generating in to thermal medium heat exchanger 12 at cold-producing medium, flow into storage heat exchanger 22 hot water for, carries out heat exchange and heats the water of storing in hot water storgae 21 with the water in storage hot water storgae 21.Thermal medium is carrying out after heat exchange with the water of storing in hot water storgae 21, from storage hot water, with heat exchanger 22, flows out.Now, in order reducing, to form the thermal resistance between the thermal medium pipe arrangement of heat exchanger 22 and the outer surface of storage hot water storgae 21 for storage hot water, at the outer surface of storing hot water storgae 21, to be coated with and to be applied to the bonding agent 25 that promotes close property, heat conductivity.In addition, in the present embodiment, form storage hot water and form in such a way with the thermal medium pipe arrangement of heat exchanger 22: the length of establishing thermal medium pipe arrangement is L(m), in the pipe of thermal medium pipe arrangement, sectional area is S(mm
2) time, L/S(m/mm
2) be more than 2.8 below 5.3.
Supplying hot water loop 5 comprises: storage hot water storgae 21; Be connected to the storage hot water storgae 21 feed pipe 5b for feedwater with the bottom of storage hot water storgae 21; With with storage hot water storgae 21 top be connected the heat supply water pipe 5a to user's supplying hot water.When the water in heating storage hot water storgae 21 generates the storage hot water running of high-temperature water, high temperature thermal medium after cold-producing medium is heated in to thermal medium heat exchanger 12 flow into storage heat exchanger 22 hot water for, the thermal medium of this high temperature and the water that is stored in hot water storgae 21 inside by storage hot water with the thermal medium pipe arrangement of heat exchanger 22 with store hot water storgae 21 and carry out heat exchange.The high-temperature water being stored in hot water storgae 21 is supplied with to user by heat supply water pipe 5a, thus, when the hot water amount in storage hot water storgae 21 reduces, from feed pipe 5b, to storage hot water storgae 21, supply feedwater.
Storage hot water storgae 21 as shown in Figure 2, consists of the dome-type upper member 21b and the lower member 21c that form central portion 21a cylindraceous, an end opening and the other end and form hemisphere.Central portion 21a, upper member 21b and lower member 21c be quilt difference solder joints in the 21d of junction surface.
Periphery at storage hot water storgae 21 is equipped with the thermal medium pipe arrangement of heat exchanger 22 for formation storage hot water.This thermal medium pipe arrangement contacts with the outer surface of storage hot water storgae 21 at inlet portion 4a, is spirally wound to the below of storage hot water storgae 21, at the 4b of export department of lower member 21c, from the periphery of storage hot water storgae 21, leaves.In addition, as shown in Figure 2, inlet portion 4a is arranged at upper member 21b, and the 4b of export department is arranged at lower member 21c.
That is, as shown in Figure 2, from the thermal medium pipe arrangement of the inlet portion 4aZhi 4b of export department, contact with the outer surface of storage hot water storgae 21, form and store heat exchanger 22 for hot water.Like this, thermal medium pipe arrangement is spirally wound to lower member 21c from upper member 21b, so can form, stores heat exchanger 22 for hot water in whole storage hot water storgae 21, so the water of storage hot water storgae 21 inside all can be heated to high temperature.
In addition, the feed pipe 5b being connected from the below connecting portion 5d with lower member 21c to storage hot water storgae 21 for feedwater, storage hot water with the high-temperature water after being heated in heat exchanger 22 from upper member 21b above the heat supply water pipe 5a that is connected of connecting portion 5c flow out and supply with user.
Like this, supplying hot water pipe arrangement or water supply piping are connected with lower member 21c with upper member 21b, install thus pipe arrangement concentratedly, can improve processability and the withstand voltage properties of storage hot water storgae 21.
Herein, as shown in Figure 2, from feed pipe 5b, to the storage hot water storgae 21 water supply Shi Congbi 4b of export department positions closer to the top, carry out.That is, connecting portion 5d in below is equipped on than export department 4b more by storing the top of the vertical of hot water storgae 21.Thus, forming storage hot water is disposed at than below connecting portion 5d more on the lower by least a portion of the thermal medium pipe arrangement of heat exchanger 22, so utilize free convection effectively to heat, be easily trapped in the water at low temperature of storage hot water storgae 21 bottoms, thus can be at the whole inner high-temperature water that generates of storage hot water storgae 21.
In addition, as shown in Figure 2, from heat supply water pipe 5a to user's supplying hot water, be to carry out from the position more closer to the top than inlet portion 4a.That is, connecting portion 5c in top is equipped on than inlet portion 4a more by storing the top of the vertical of hot water storgae 21.Thus, can be by the high-temperature water that is heated with heat exchanger 22 by storage hot water and be stored in hot water storgae 21 tops because of free convection effectively for supplying hot water.
In addition, can apply selectively respectively heat supply water pipe 5a and the annexation, feed pipe 5b of storage hot water storgae 21 and the position relationship of position relationship, the 4b of export department and the below connecting portion 5d of annexation, inlet portion 4a and the top connecting portion 5c of storage hot water storgae 21.
Use Fig. 1, Fig. 3, Fig. 4, the action of the hot-water supply to form is as mentioned above described.Fig. 3 means the P-h line chart (Mollier line chart) of the refrigerant pressure P of refrigerant loop and the relation of refrigerant enthalpy h, and Fig. 4 means the skeleton diagram that the water temperature in storage hot water storgae 21 changes.
When heating is store the water in hot water storgae 21 and is started to store the storage hot water running of hot water, CO in refrigerant loop 3
2cold-producing medium is to the direction circulation shown in the solid arrow of Fig. 1.Then, the CO of saturated or superheat state
2cold-producing medium is inhaled into compressor 11(Fig. 3 a point), by compressor 11, be compressed to supercritical pressure, become the gaseous state (Fig. 3 b point) of HTHP.Become the CO of the gaseous state of HTHP
2cold-producing medium is sent to cold-producing medium to thermal medium heat exchanger 12, carries out heat exchange with thermal medium, generates thus the thermal medium of high temperature.
CO
2cold-producing medium is cooled in to thermal medium heat exchanger 12 at cold-producing medium, from cold-producing medium, thermal medium heat exchanger 12 being flowed out, flow into expansion valve 13(Fig. 3 c point).Afterwards, CO
2cold-producing medium is inflated valve 13 puffings (Fig. 3 c-d point) and becomes liquid condition, flow into cold-producing medium to air heat exchanger 14.Afterwards, CO
2cold-producing medium cold-producing medium to air heat exchanger 14 in, heat absorption evaporation from the air of being sent by pressure fan 16, becomes saturated gas or overheated gas state, again flow into compressor 11(Fig. 3 a point).
On the other hand, in thermal medium loop 4, the high temperature thermal medium generating in to thermal medium heat exchanger 12 at cold-producing medium flows to the direction shown in the dotted arrow of Fig. 1.Thermal medium is by being positioned at the expansion vessel 24 of entrance side of storage hot water storgae 21, flow into storage heat exchanger 22 for hot water from the top of storage hot water storgae 21.The heat energy that high temperature thermal medium has passes through thermal medium pipe arrangement and the storage hot water storgae 21 of heat exchanger 22 for storage hot water, to the water transmission of storing in hot water storgae 21, generates high-temperature water.
According to such structure, the thermal medium loop 4 of flowing through is inner completely separated with the fluid quilt of 5 inside, supplying hot water loop of flowing through.The water many because of hardness components are heated to high temperature, and this high-temperature water flows in the little pipe arrangement of caliber, and separating out of incrustation scale especially easily occurs.According to this structure, can effectively suppress separating out of incrustation scale.
In addition, use CO
2cold-producing medium, thus, can make the on high-tension side pressure of refrigerant loop 3 be increased to supercritical range.Therefore, at cold-producing medium, generate high temperature thermal medium in to thermal medium heat exchanger 12, can make the thermal medium of high temperature flow into storage heat exchanger 22 hot water for, so can increase the storage hot water use thermal medium of heat exchanger 22 and the temperature difference of water.
Thus, even in the situation that the internal circulating load of thermal medium is few, also can guarantee the heat that adds of regulation.And, after at thermal medium, to storage, the water-cooled in hot water storgae 21 and temperature fully decline, can with heat exchanger 22, flow out from storage hot water, can to the temperature of the thermal medium of thermal medium heat exchanger 12, maintain lowlyer by flowing into cold-producing medium, so the excessive rising of the high side pressure of refrigerant loop 3 is suppressed.
If particularly adopted, high temperature thermal medium is flowed into the top of heat exchanger 22 from storage hot water, the structure flowing out from below, the water of storing in hot water storgae 21 is heated successively from top, as shown in Figure 4, the distribution of the hot water in storage hot water storgae 21 is together moved downwards from top with the carrying out of storage hot water running.Therefore,, before the temperature that is stored in the water of hot water storgae 21 bottoms raises, the temperature of the thermal medium flowing out with heat exchanger 22 from storage hot water can not raise.So, can to the temperature of the thermal medium of thermal medium heat exchanger 12, maintain lowlyer by flowing into cold-producing medium, and thermal medium can be heated to high temperature at cold-producing medium in to thermal medium heat exchanger 12, so can suppress the rising of the high side pressure of refrigerant loop 3, and can make heat pump effectively turn round.
In addition, at storage hot water, by the internal circulating load of thermal medium mobile in heat exchanger 22, reduce, thus the increase of the pressure loss can be suppressed, and can extend the pipe range of thermal medium, and the caliber of thermal medium pipe arrangement is attenuated.
As described above, the running efficiency of heat pump improves.In addition, by increasing the pipe range of thermal medium pipe arrangement, carry out enlarge active surface.In addition, the turbulent flow that promotes caliber because of thermal medium pipe arrangement to attenuate to produce is to increase hot percent of pass.Consequently, according to these synergies, can realize the high efficiency in storage hot water when running of hot-water supply.
Then, use Fig. 5～Fig. 7, storage hot water is described by the structure of heat exchanger 22.
Herein, thermal medium is flow into from top and store heat exchanger 22 for hot water, and flow out from below.Length L=25～45(m at storage hot water with the thermal medium pipe arrangement of heat exchanger 22), under condition heat-transfer pipe inner diameter d i=3～28(mm), internal volume Vt=150～300(liter of storage hot water storgae), guarantee average heating efficiency Q=2.0～2.5kW, running hot-water supply.The relation of the ratio of average running efficiency when Fig. 5 represents to change condition (hereinafter referred to as " running efficiency ratio ") and L/S.That is the heating-up temperature of water that, is illustrated in storage hot water storgae 21 is the situation of 55 ℃ of existing use freon class cold-producing medium and the situation of 85 ℃ of using carbon dioxide coolant.
In addition, Fig. 6 is illustrated under the condition identical with Fig. 5, and storage is the pressure loss dP in the thermal medium pipe arrangement of heat exchanger 22 and the relation of L/S for hot water.
In addition, Fig. 7 forms the thermal medium pipe arrangement of heat exchanger 22 and the skeleton diagram of the contact length of storage hot water storgae 21 for storage hot water for regulation.
In addition, the ratio of the running efficiency as the longitudinal axis of Fig. 5, the relative ratios that the peak value η o that represents to establish the running efficiency η when heating-up temperature of the water of storage hot water storgae 21 is set in to 55 ℃ is 100%, L/S as transverse axis, form storage hot water elongated by the length L of 1 thermal medium pipe arrangement of heat exchanger 22, or the bore di of thermal medium pipe arrangement diminishes, its numerical value increases, length L shortens or bore di becomes large, and its numerical value reduces.
In the present embodiment, establishing formation storage hot water is L(m by the length of 1 thermal medium pipe arrangement of heat exchanger 22), in the pipe of thermal medium pipe arrangement, sectional area is S(mm
2) time, with L/S(m/mm
2) be that mode more than 2.8 and below 5.3 forms storage heat exchanger 22 for hot water.According to this structure, can considering compression machine and the performance error of the component parts of other refrigerant loops, make running efficiency η maximum simultaneously.
This trend based on following: in the situation that set the water that thermal medium pipe arrangement heats storage hot water storgae 21 inside in storage hot water storgae 21, under identical heating efficiency condition, running efficiency (COP) is according to the ratio of sectional area S in the pipe of the length L of thermal medium pipe arrangement and thermal medium pipe arrangement, its peak value η o changes, in addition, the variation of its peak value η o because of the temperature of generated hot water greatly different.
Like this, running efficiency η because of L/S change when the peak value η o according to below phenomenon.
L/S increases gradually from zero, and, along with storage hot water is elongated by the length L of the thermal medium pipe arrangement of heat exchanger 22, storage hot water increases with the surface area of heat exchanger 22, so running efficiency η presents the trend increasing gradually.On the other hand, L/S increases expression, and the length L of thermal medium pipe arrangement increases, or the bore di of thermal medium pipe arrangement diminishes.
As shown in Figure 6, if L/S increases, the pressure loss dP of thermal medium pipe arrangement inside increase L/S square more than, because this pressure loss dP increases, the power consumption of circulating pump 23 also increases, running efficiency η declines gradually.In addition, if dwindle the bore di of thermal medium pipe arrangement, the heet transfer rate of the inner surface of thermal medium pipe arrangement increases, and in contrast, the heat transfer area of thermal medium pipe arrangement reduces.
In addition, as shown in Figure 7, be coated in the situation that the close property of outer surface of storage hot water storgae 21 is identical with the thickness t f of heat conductivity promoter, the caliber less (d1 > d2) of heat-transfer pipe, the length (heat transfer area) that the outer surface of heat-transfer pipe contacts with heat conductivity promoter with close property more reduces (W1 > W2), so L/S increases,, exist storage hot water less with the bore di of the thermal medium pipe arrangement of heat exchanger 22, the trend that running efficiency η is lower.
Therefore, as shown in Figure 5, running efficiency η has along with the increase of L/S increase gradually, becomes after peak value η o the characteristic reducing gradually at running efficiency η.In addition, if the heating-up temperature of water of storage hot water storgae 21 is 85 ℃, while being 55 ℃ with heating-up temperature, compare, must further improve the compression ratio of compressor 11, so compressor power increases, during with 55 ℃ of heating-up temperatures, compare, running efficiency η reduces.
Using CO herein,
2cold-producing medium Heat of Formation medium, is heated to the water of storage hot water storgae 21 inside in the situation of high temperature of 85 ℃, during with 55 ℃ of heating-up temperatures, compares, and can increase water in storage hot water storgae 21 and the temperature difference of cold-producing medium.Thus, under the identical condition of average heating efficiency, can reduce the flow of the thermal medium of circulation, so the pressure loss of the thermal medium pipe arrangement of formation storage hot water use heat exchanger 22 as shown in Figure 6, compare with 55 ℃ of heating-up temperatures, there is the characteristic of step-down.
Therefore, by the elongated heat transfer area that makes of length L of thermal medium pipe arrangement is increased, or make in the pipe of thermal medium pipe arrangement sectional area S diminish to make the flow velocity of thermal medium increase, heet transfer rate improves.Therefore, by flowing into storage hot water, with the thermal medium of heat exchanger 22, be heated to the high temperature of 85 ℃, the in the situation that of storage hot water storgae 21 interior generating hot water, as shown in Figure 5, while being 55 ℃ with heating-up temperature, compare, by increasing L/S, can make running efficiency η maximum.
That is, as shown in Figure 5, with freon class cold-producing medium, carry out heat hot medium, thereby utilizing thermal medium after heating to come heating water to generate in the situation of hot water of 55 ℃, at L/S(m/mm
2) be more than 1.2 and 1.8 following between, become the peak value η o of running efficiency η.
On the other hand, using CO
2cold-producing medium heat hot medium, thus utilize thermal medium after heating to come heating water to generate in the situation of high-temperature water of 85 ℃, so that L/S(m/mm
2) mode in the scope more than 2.8 and below 5.3 forms thermal medium pipe arrangement.Thus, can considering compression machine and the performance error (3%) of the component parts of other refrigerant loops, make average running efficiency maximum simultaneously.
In addition, in the present embodiment, as the thermal medium circulating, use water in thermal medium loop 4, but be not limited to this, also can use for example anti-icing fluid.
In addition, in the present embodiment, in thermal medium loop 4, be equipped with expansion vessel 24, but few in the internal circulating load of thermal medium, and in the few situation of the swell increment of thermal medium, also can not load expansion vessel.
In industry, utilize possibility
As mentioned above, hot-water supply of the present invention can suppress separating out of incrustation scale and effectively generate high-temperature water, so can be applicable to the hot-water supply that home-use and business is used etc.
Claims (3)
1. a hot-water supply, is characterized in that, comprising:
Refrigerant loop, its with refrigerant piping, by the compressor of compressed refrigerant, between described cold-producing medium and thermal medium, carry out heat exchange the 1st radiator, make the expansion gear that described cold-producing medium expands and make the evaporimeter of described cold-producing medium evaporation connect into ring-type, described cold-producing medium is in inner loop;
The storage hot water storgae of storage of water; With
Thermal medium loop, it connects into ring-type with thermal medium pipe arrangement by described the 1st radiator, the 2nd radiator and the EGR that carry out heat exchange between described thermal medium and described water, and described thermal medium is in inner loop, wherein
The described cold-producing medium circulating in described refrigerant loop is carbon dioxide,
In described the 2nd radiator, described thermal medium pipe arrangement is wound on the outer surface of described storage hot water storgae, and the heat of described thermal medium is to the described water-cooled in described storage hot water storgae.
2. hot-water supply as claimed in claim 1, is characterized in that:
If forming the total length of the described thermal medium pipe arrangement of described the 2nd radiator is L(m), in the pipe of described thermal medium pipe arrangement, sectional area is S(mm
2) time, L/S(m/mm
2) be more than 2.8 below 5.3.
3. hot-water supply as claimed in claim 1 or 2, is characterized in that:
Described thermal medium flows downwards from the top of described the 2nd radiator.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013034189A JP2014163566A (en) | 2013-02-25 | 2013-02-25 | Water heater |
| JP2013-034189 | 2013-02-25 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104006534A true CN104006534A (en) | 2014-08-27 |
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ID=50112822
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410064728.0A Pending CN104006534A (en) | 2013-02-25 | 2014-02-25 | Water heater |
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| Country | Link |
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| EP (1) | EP2770278B1 (en) |
| JP (1) | JP2014163566A (en) |
| CN (1) | CN104006534A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104864599A (en) * | 2015-04-10 | 2015-08-26 | 广东美的暖通设备有限公司 | High-efficiency heat exchange water tank |
| CN107202420A (en) * | 2016-03-17 | 2017-09-26 | 松下知识产权经营株式会社 | Teat pump boiler |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2543086B (en) * | 2015-10-08 | 2018-05-02 | Isentra Ltd | Water-cooled carbon dioxide refrigeration system |
| CN106940087A (en) * | 2016-01-04 | 2017-07-11 | 艾欧史密斯(中国)热水器有限公司 | Teat pump boiler and water tank |
| CN106196600B (en) * | 2016-08-22 | 2022-03-29 | 艾欧史密斯(中国)热水器有限公司 | Heat pump water heater and assembling method thereof |
| ES2737673A1 (en) * | 2018-07-13 | 2020-01-15 | Robert Art En Pedra S L | System for temperature control of at least one energy storage module and associated method (Machine-translation by Google Translate, not legally binding) |
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| CN101842643A (en) * | 2007-11-02 | 2010-09-22 | 松下电器产业株式会社 | Hot water supply system |
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| CN107202420A (en) * | 2016-03-17 | 2017-09-26 | 松下知识产权经营株式会社 | Teat pump boiler |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2770278B1 (en) | 2019-07-31 |
| EP2770278A1 (en) | 2014-08-27 |
| JP2014163566A (en) | 2014-09-08 |
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