CN104457036B

CN104457036B - Case wing formula low-temperature heat accumulating heat exchanger and the source pump operation method containing this heat exchanger

Info

Publication number: CN104457036B
Application number: CN201410746832.8A
Authority: CN
Inventors: 倪龙; 姚杨; 曲德虎
Original assignee: Harbin Institute of Technology
Current assignee: Harbin Institute of Technology
Priority date: 2014-12-08
Filing date: 2014-12-08
Publication date: 2016-09-28
Anticipated expiration: 2034-12-08
Also published as: CN104457036A

Abstract

Case wing formula low-temperature heat accumulating heat exchanger and the source pump operation method containing this heat exchanger, it relates to a kind of heat exchanger and the source pump operation method containing this heat exchanger.The present invention is to solve that existing energy-storage type heat pump integrated system accumulator volume present in system, equipment, the method is big, the more difficult raising of heat exchange efficiency, by the constraint of energy-accumulation material character, cold heat amount two-way utilize unbalanced, there is contradiction in solar thermal utilization, operation reserve has problem to be optimized.Device: heat exchange body both sides are respectively mounted end socket, is provided with a homogenizing plate in end socket, heat exchange body includes organizing heat-exchanging component more, and many group heat-exchanging components are installed successively.Method: the source pump operation method of the present invention has following six kinds of operation methods according to different conditions: air source heat pump refrigeration mode, solar heat-preservation pattern, thermophore heat supply mode, solar energy auxiliary regenerator device heat supply mode, air source heat pump heating mode and thermophore defrosting mode.The present invention is energy-conservation for air conditioner heat pump system.

Description

Case wing formula low-temperature heat accumulating heat exchanger and the source pump operation method containing this heat exchanger

Technical field

The present invention relates to a kind of source pump and operation method thereof, be specifically related to a kind of case wing formula low-temperature heat accumulating heat exchanger and containing being somebody's turn to do The source pump operation method of heat exchanger, belongs to heat pump air conditioner field of energy-saving technology.

Background technology

At present, air source heat pump is in the extensively application of each area, but there is low the asking of heating efficiency in northern cold climate district Topic, in the problem that the area that outside relative humidity is bigger there is also heat pump cycle outdoor heat exchanger frosting.Although occurring in that a large amount of In conjunction with the air resource heat pump integrated system of different field technology, most integrated systems are still in the imagination stage, only by different Technology machinery superposition, fails to maximize favourable factors and minimize unfavourable ones, and rationality combines.The Multisource heat pump skill of integrated solar, air energy and casing pipes energy accumulating Art fully utilizes various conservation measures, it is achieved that the annual multi-mode operation of a machine.But its shortcoming is also apparent from: 1) thimble tube accumulator metal consumption is big, it is big to take up room；2) thimble tube structure is deeply by the shadow of energy-accumulation material thermophysical property Ring, such as heat conductivility, thermal expansivity etc.；3) cold, the two-way utilization of heat lack of uniformity (accumulator volume by store Cold and accumulation of heat requires that design difference is big)；4) solar energy directly/collecting apparatus that utilizes of indirect thermal and area discrepancy big；5) The more difficult raising of efficiency of the independent heat supply of thimble tube accumulator；6) technology of thimble tube accumulator associating air source heat pump heat supply is still Immaturity, heating efficiency instability etc..It addition, being phased out with conventional refrigerants, select efficient novel environment friendly system Cryogen is also the problem needing to consider.The purpose of the present invention solves the problems referred to above just.

Summary of the invention

Present invention aim to address that existing bushing type accumulating type Multisource heat pump integrated system exists in system, equipment, method Accumulator volume is big, the more difficult raising of heat exchange efficiency, by the constraint of energy-accumulation material character, cold heat amount two-way utilize unbalanced, There is contradiction in solar thermal utilization, operation reserve has problem to be optimized.And then a kind of case wing formula low-temperature heat accumulating heat exchanger is provided And the source pump operation method containing this heat exchanger.

The technical scheme is that

The case wing formula low-temperature heat accumulating heat exchanger of the present invention includes heat exchange body, refrigerant outlet pipe, refrigerant inlet pipe, the sun Energy hot water outlet pipe, solar water inlet tube, multiple homogenizing plate and multiple end socket, the both sides, top of heat exchange body and bottom Both sides are separately installed with an end socket, are provided with the top of a homogenizing plate, refrigerant outlet pipe and heat exchange body in each end socket The end socket of side connects, and refrigerant inlet pipe is connected with the end socket of heat exchange body lower part opposite side, solar heat water outlet pipe and The end socket of the top opposite side of heat exchange body connects, and solar water inlet tube is connected with the end socket of heat exchange body lower part side, Described heat exchange body includes organizing heat-exchanging component more, and many group heat-exchanging components are installed successively, often group heat-exchanging component all include heat exchanger channels, Two strip of paper used for sealings, two heat storage tanks and two groups of deflectors, two heat storage tanks are separately mounted to the two ends up and down of heat exchanger channels, two Strip of paper used for sealing is separately mounted to the two ends, left and right of heat exchanger channels, and two groups of deflectors are separately mounted to two ends before and after heat exchanger channels, described Each heat storage tank in two heat storage tanks all includes two heat-conducting plates, four sealing plates and multiple intersection fin, two heat-conducting plates Setting up and down, multiple the most equidistant fixed arrangement of intersection fin are between two heat-conducting plates, and four sealing plates enclose and are located at two The surrounding of heat-conducting plate, the space between two heat-conducting plates in heat storage tank, four sealing plates and multiple intersection fin is phase transformation material Material packing space, the 90%-96% that height is sealing plate height of described intersection fin, heat exchanger channels is square wave heat exchanger channels Or staggered square wave heat exchanger channels.

It is tightly connected between described end socket and heat exchange body.

Described heat exchanger channels is in use, it is possible to as refrigerant heat exchanger passage or solar water heat exchanger channels, respectively with lead Stream plate is tightly connected, and described strip of paper used for sealing is tightly connected with heat exchanger channels and heat storage tank.

Heat exchanger channels arrangement in described heat exchange body is: outside layout solar heat aquaporin, disposed inboard coolant channel, Cold section of overall channel number relatively hot arc overall channel number few 1.

Heat-storing material in described heat storage tank is organic fixed phase change accumulation of heat powder, and this is a kind of using inorganic material as supporting shape Becoming micropore the setting accumulation of heat powder of Adsorption Paraffin, the advantage of this material is that phase transition process is without change in volume, without mode of appearance change Change, stable performance, heat conductivility preferably, thermal storage density higher.

The structure of described heat exchanger channels is channels interleaved, and the square wave waveband width of heat exchanger channels is equal with height.

Described solar water is consistent with cold-producing medium flow direction.

In the present invention, the source pump operation method containing this heat exchanger is divided into following six kinds of methods to realize running:

(1) operation method under air source heat pump refrigeration mode is realized by following steps:

Step one: open the 4th electromagnetic valve, close the first electromagnetic valve and the 3rd electromagnetic valve:

Step 2: the circulation of system refrigerant:

Cold-producing medium is R32, and the first of the aerofluxus entrance electric four passes reversal valve of compressor is led to, then through electric four passes reversal valve Second logical enter in the fin tube type air heat exchanger of outside, sequentially pass through the 4th electromagnetic valve, capillary by forward check valve Pipe and indoor fin tube type air heat exchanger, then sequentially pass through the threeway of electric four passes reversal valve, four-way, finally depend on Secondary through forward check valve and gas-liquid separator, return to compressor；System by indoor fin tube type air heat exchanger to Family cooling, so far, unit completes the operation under air source heat pump refrigeration mode；

Step 3: the refrigeration when outdoor high temperature causes compressor exhaust temperature too high:

Opening the second electromagnetic valve and the 5th electromagnetic valve, now part of refrigerant is bypassed before the 4th electromagnetic valve, cold-producing medium warp Cross the second electromagnetic valve to sequentially enter capillary tube, flash evaporation and the 5th electromagnetic valve and spray into compressor through steam nozzle；System is passed through Indoor fin tube type air heat exchanger is to user's cooling, and so far, unit completes the operation under air source heat pump refrigeration mode.

(2) operation method under solar heat-preservation pattern is realized by following steps:

Step one: compressor stops, closes the first electromagnetic valve, the second electromagnetic valve, the 3rd electromagnetic valve, the 4th electromagnetic valve and the Five electromagnetic valves；

Step 2: solar water pump operating cycle, the circulation of system solar water is:

Solar heat water-circulating pump drives solar water to enter the solar water deflector in close-coupled low-temperature heat accumulating device, warp Cross solar water heat exchanger channels, part low level solar thermal energy is passed to the organic phase-change accumulation of heat powder in heat storage tank, then warp Solar water deflector enters in plate solar collector after drawing and is heated again, afterwards in plate solar collector Hot water be again introduced into solar heat water-circulating pump, complete the circulation of solar water；

Step 3: the Lowlevel thermal energy of solar water is stored in the heat storage tank in close-coupled low-temperature heat accumulating device standby, unit So far the operation under solar heat-preservation pattern is completed.

(3) operation method under thermophore heat supply mode is realized by following steps:

Step one: open the 3rd electromagnetic valve, close the first electromagnetic valve and the 4th electromagnetic valve；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium by the air vent of compressor sequentially pass through electric four passes reversal valve first logical and the 3rd Logical, indoor fin tube type air heat exchanger, forward check valve, the 3rd electromagnetic valve, electric expansion valve and restricting orifice, enter Enter the cold-producing medium deflector of close-coupled low-temperature heat accumulating device, by refrigerant heat exchanger passage, the low level heat that will be stored in heat storage tank Can take out, then flow out close-coupled low-temperature heat accumulating device through cold-producing medium deflector, sequentially pass through forward check valve and gas-liquid separation afterwards Device, returns to compressor；System is by indoor fin tube type air heat exchanger to user's heat supply, and so far, unit completes accumulation of heat Operation under device heat supply mode；

Step 3: when system inner refrigerant circular flow is too low, opens the second electromagnetic valve and the 5th electromagnetic valve, now one Divide cold-producing medium bypassed before the 3rd electromagnetic valve: cold-producing medium flows successively through the second electromagnetic valve, capillary tube, flash evaporation and the 5th electricity Magnet valve, sprays into compressor through steam nozzle；System by indoor fin tube type air heat exchanger to user's heat supply, so far, Unit completes the operation under thermophore heat supply mode.

(4) operation method under solar energy auxiliary regenerator device heat supply mode is realized by following steps:

Step one: open the 3rd electromagnetic valve, close the first electromagnetic valve, the second electromagnetic valve, the 4th electromagnetic valve and the 5th electromagnetic valve；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, and cold-producing medium enters the first logical and threeway of electric four passes reversal valve by compressor, sequentially passes through Indoor fin tube type air heat exchanger, forward check valve, the 3rd electromagnetic valve, electric expansion valve and restricting orifice enter compact The cold-producing medium deflector of formula low-temperature heat accumulating device, by refrigerant heat exchanger passage, takes out the Lowlevel thermal energy being stored in heat storage tank, Flow out close-coupled low-temperature heat accumulating device through cold-producing medium deflector again, finally sequentially pass through forward check valve and gas-liquid separator returns to pressure Contracting machine；System to user's heat supply, so far completes a refrigerant cycle by indoor fin tube type air heat exchanger；

Step 3: solar heat water cycle process is:

Solar water pump operating cycle, solar water is entered close-coupled low-temperature heat accumulating device too by solar heat water-circulating pump Sun energy hot water deflector, through solar water heat exchanger channels, passes to the organic phase-change in heat storage tank by low level solar thermal energy Accumulation of heat powder, then draw through solar water deflector, return to plate solar collector and be heated again, afterwards solar energy Hot water in flat plate collector is again introduced into solar heat water-circulating pump, completes a solar water circulation；System passes through room Inner side fin tube type air heat exchanger, to user's heat supply, stores low level heat simultaneously in the heat storage tank in close-coupled low-temperature heat accumulating device Can be standby, so far, unit completes the operation under solar energy auxiliary regenerator device heat supply mode.

(5) operation method under air source heat pump heating mode is realized by following steps:

Step one: open the first electromagnetic valve, closes the 3rd electromagnetic valve and the 4th electromagnetic valve；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium through compressor air vent enter electric four passes reversal valve first lead to, afterwards by electronic The threeway of four-way change-over valve sequentially passes through indoor fin tube type air heat exchanger, forward check valve, the first electromagnetic valve, hair Tubule and outside fin tube type air heat exchanger, after through the second logical and four-way of electric four passes reversal valve, flow successively through Forward check valve and gas-liquid separator return to compressor；System by indoor fin tube type air heat exchanger to user's heat supply, So far, the operation under unit completes air source heat pump heating mode；

Step 3: when system inner refrigerant circular flow is too low, opens the second electromagnetic valve and the 5th electromagnetic valve, now one Divide cold-producing medium bypassed before electromagnetic valve: cold-producing medium sequentially passes through the second electromagnetic valve, capillary tube, flash evaporation and the 5th electromagnetic valve Compressor is sprayed into through steam nozzle；System is by indoor fin tube type air heat exchanger to user's heat supply, and so far, unit is complete The operation under air source heat pump heating mode when one-tenth system inner refrigerant circular flow is too low.

(6) operation method under thermophore defrosting mode is realized by following steps:

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, and cold-producing medium sequentially passes through the first of electric four passes reversal valve through compressor and leads to logical, afterwards with second Pass sequentially through outside fin tube type air heat exchanger, forward check valve, the 3rd electromagnetic valve, electric expansion valve and restricting orifice Enter the cold-producing medium deflector of close-coupled low-temperature heat accumulating device, by refrigerant heat exchanger passage, the low level in heat storage tank will be stored in Heat energy takes out, then flows out close-coupled low-temperature heat accumulating device through cold-producing medium deflector, finally sequentially passes through forward check valve and gas-liquid is divided Compressor is returned to from device；System utilizes the Lowlevel thermal energy defrosting being stored in close-coupled low-temperature heat accumulating device, and so far, unit completes Operation under thermophore defrosting mode.

The present invention compared with prior art has the effect that

1, the more reasonable structure of energy storage heat exchanger.In existing energy-storage type heat pump, energy storage heat exchanger is sleeve type structure, its Shortcoming is that metal consumptive material is big, take up room big, the more difficult lifting of heat exchange efficiency.The low-temperature heat accumulating device of the present invention uses compact plate Wing formula structure, farthest saves metal consumption and takes up room；Staggered arrangement passage in thermophore, punching deflector, The heat exchange efficiency that the detailed design such as uniform flow orifice, netted intersection fin are effectively increased in thermophore；Cold-producing medium and solar heat The design of water co-flow both ensure that higher heat exchange efficiency, also ensure that the stability of heat transfer；Solar heat aquaporin in Outside is arranged, coolant channel farthest reduces thermophore in disposed inboard, the Equalization Design of cold and hot section of total number of channels Interior stress mean square deviation.

2, specify that the selection principle of energy-accumulation material.Organic fixed phase change accumulation of heat powder that the present invention selects, is a kind of with nothing Machine material forms micropore the setting accumulation of heat powder of Adsorption Paraffin as supporting, and its advantage is that phase transition process is without change in volume, nothing Mode of appearance change, stable performance, heat conductivility preferably, thermal storage density higher.Solve inorganic energy-accumulation material corrosivity, Easily layering, the problem such as unstable, also solve that organic solid-liquid phase-change material phase transformation rate of volumetric change is big, the problem of difficult sealing.

3, novel high-efficiency environment friendly cold-producing medium has been selected.The cold-producing medium that the present invention selects is R32, in addition to environmental protection characteristic, and its heat Work performance is better than R410A, and efficiency is the highest by 5.3%, cold the biggest 12.7%；The efficiency not control of R32 under identical cold Cold or heating condition is above R410A, and refrigeration rated load is high by 10%, and sub-load is high by 7%, heats rated load high 7%, sub-load is high by 5%.Additionally, the market availability of R32 is good, domestic existing a large amount of productions, much fluorination work enterprises Industry all has product, without risk of infringement, also has superiority in price: the price of R32 is only the 30% of R410A.

4, refrigerant flow circuit is optimized.The own characteristic of consideration R32 cold-producing medium and unit are under high/low temperature or frosting environment Running and need, be additionally arranged steam by-pass on the basis of traditional energy-storage type heat pump system flow, this design can be in high-temperature refrigeration work Delivery temperature (loss of refrigeration capacity≤8% simultaneously) is effectively reduced, it is possible under heating condition, effectively promote the cold-producing medium of system under condition Circular flow, thus promote heating capacity (rate of heating can promote 6%).Additionally, electric expansion valve and joint before low-temperature heat accumulating device The design used in parallel of discharge orifice plate ensure that the refrigerant feed liquid amount of low-temperature heat accumulating device, enhances the heat flow density in thermophore.

The operational mode of 5, selected unit and strategy.Existing casing pipes energy accumulating type integrated heat pump technology possesses multiple operation mould Formula, but a lot of pattern still immaturity, actual motion efficiency is unstable.The present invention eliminates thermophore associating air source heat supply Operational mode, adds thermophore defrosting mode, more meets and heat needs；Eliminate the cold-storage of accumulator, cooling mode, The consumption of heat-storing material is down to minimum, makes heat-storing material be fully used, it is to avoid the inequality of the two-way utilization of cold heat amount Weighing apparatus；Abandon the imagination of the direct heat utilization of solar energy, utilize coupling flat plate collector based on indirect thermal, economical and practical, simple Folk prescription just, save space, also improve the utilization ratio of solar energy；Indoor heat exchanger selects fin tube type air heat exchanger, Eliminate secondary heat exchange loss, simple and reliable.

6, the source pump based on compact molding box wing formula low-temperature heat accumulating heat exchanger of the present invention can realize 6 kinds of operational modes, It is specifically described as follows:

1) the air source heat pump refrigeration mode of the present invention is consistent with conventional heat pump air-conditioning, only need to will enter the system of low-temperature heat accumulating device Cryogen closed electromagnetic valve.

2) the solar heat-preservation pattern of the present invention utilizes solar energy production low-temperature water heating (25～35 DEG C) sufficient in the daytime, passes through Solar heat water-circulating pump enters in low-temperature heat accumulating device, and the setting accumulation of heat powder in heat storage tank accepts and stores solar water Portion of energy, in case heat supply is used.

3) the thermophore heat supply mode of the present invention utilizes the Lowlevel thermal energy being stored in heat storage tank, promotes heat energy product through compressor Matter rear line heat supply.

4) the solar energy auxiliary regenerator device heat supply mode of present invention thermal-arrest heat supply on one side on one side when solar energy abundance in the daytime, by force Change the heat transfer efficiency in low-temperature heat accumulating device, improved and heat efficiency.

5) after the thermophore defrosting mode of the present invention utilizes solar heat-preservation pattern or solar energy auxiliary regenerator device heat supply mode Lowlevel thermal energy defrost, now fin tube type air heat exchanger in outside is as the condenser of system, but outdoor fan exists Defrosting whole process is closed.

Accompanying drawing explanation

Fig. 1 is the front view of the present invention compact molding box wing formula low-temperature heat accumulating heat exchanger；Fig. 2 is the side view of Fig. 1；Fig. 3 It it is the top view of Fig. 1；Fig. 4 is the structural representation of accumulation of heat body in compact molding box wing formula low-temperature heat accumulating heat exchanger；Fig. 5 For the structural representation of heat storage tank in compact molding box wing formula low-temperature heat accumulating heat exchanger；Fig. 6 is that compact molding box wing formula low-temperature heat accumulating changes The expanded view of heat storage tank in hot device；Fig. 7 is the side view of heat storage tank；Fig. 8 is to intersect the front view of fin in heat storage tank；Figure 9 is the side view of Fig. 8；Figure 10 is the top view of Fig. 8；Figure 11 is heat exchange in compact molding box wing formula low-temperature heat accumulating heat exchanger The structural representation of passage；Figure 12 is the front view of Figure 11；Figure 13 is the side view of Figure 11；Figure 14 is bowing of Figure 11 View；Figure 15 is heat exchanger channels and the plane graph of deflector in compact molding box wing formula low-temperature heat accumulating heat exchanger；Figure 16 is compact The front view of deflector in molding box wing formula low-temperature heat accumulating heat exchanger；Figure 17 is the side view of Figure 16；Figure 18 is bowing of Figure 16 View；Figure 19 is the front view of end socket in compact molding box wing formula low-temperature heat accumulating heat exchanger；Figure 20 is the side view of Figure 19； The top view of Figure 19 of Figure 21；Figure 22 is the front view of homogenizing plate in end socket；Figure 23 is the side view of Figure 22；Figure 24 Top view for Figure 22；Figure 25 is the outside schematic diagram of overall structure of the present invention；Figure 26 is that source pump of the present invention is run The schematic diagram of method.

Detailed description of the invention

Detailed description of the invention one: combine Fig. 1 to Figure 25 and present embodiment is described, the case wing formula low-temperature heat accumulating of present embodiment Heat exchanger includes heat exchange body 5, refrigerant outlet pipe 2, refrigerant inlet pipe 6, solar heat water outlet pipe 3, solar energy Hot water inlet's pipe 7, multiple homogenizing plate 4 and multiple end socket 1, both sides, top and the both sides, bottom of heat exchange body 5 are separately installed with One end socket 1, is provided with a homogenizing plate 4 in each end socket 1, the side, top of refrigerant outlet pipe 2 and heat exchange body 5 End socket 1 connects, and refrigerant inlet pipe 6 is connected with the end socket 1 of heat exchange body 5 bottom opposite side, solar heat water outlet pipe 3 It is connected with the end socket 1 of the top opposite side of heat exchange body 5, solar water inlet tube 7 and side, heat exchange body 5 bottom End socket 1 connects, and described heat exchange body 5 includes organizing heat-exchanging component more, and many group heat-exchanging components are installed successively, often organize heat-exchanging component All include that heat exchanger channels 5-1, two strip of paper used for sealing 5-2, two heat storage tank 5-3 and two groups of deflector 5-4, two heat storage tank 5-3 divide Not being arranged on the two ends up and down of heat exchanger channels 5-1, two strip of paper used for sealing 5-2 are separately mounted to the two ends, left and right of heat exchanger channels 5-1, and two Group deflector 5-4 is separately mounted to two ends before and after heat exchanger channels 5-1, each heat storage tank 5-3 in said two heat storage tank 5-3 All including two heat-conducting plate 5-3-1, four sealing plate 5-3-2 and multiple intersection fin 5-3-3, two heat-conducting plate 5-3-1 are upper and lower Arrange, multiple intersection the most equidistant fixed arrangement of fin 5-3-3 between two heat-conducting plate 5-3-1, four sealing plate 5-3-2 Enclose the surrounding being located at two heat-conducting plate 5-3-1, two heat-conducting plate 5-3-1 in heat storage tank 5-3, four sealing plate 5-3-2 and many Space between individual intersection fin 5-3-3 is phase-change material packing space.

The close-coupled low-temperature heat accumulating device of present embodiment is made up of duralumin, external application heat-preservation cotton, the heat exchange in described heat exchange body 5 Passage 5-1 arrangement is: solar heat aquaporin is arranged in outside, and disposed inboard coolant channel, cold and hot section of passage is alternately arranged； Heat-storing material in described heat storage tank 5-3 is organic fixed phase change accumulation of heat powder, this material phase transition process without change in volume, Without mode of appearance change, stable performance, heat conductivility is preferable, thermal storage density is higher；2 pieces of heat conduction in same heat storage tank 5 Plate 5-3-1 should align layout, and intersection fin 5-3-3 inwardly equidistant cross arrangement；The structure of described heat exchanger channels 5-1 is for handing over Wrong square wave passage, the square wave waveband width of heat exchanger channels 5-1 is equal with height.

The present embodiment, the use of low-temperature phase-change material reduces the leaving water temperature of solar thermal collector and requires (solar heat water temperature Degree can be at 25～35 DEG C), even if solar heat coolant-temperature gage is the highest, phase-change material also can discharge considerable latent heat of phase change.By too Sun can hot water temperature be 25 DEG C of designs, and the transition temperature range of phase-change material is preferably at 10～15 DEG C.

Illustrating in conjunction with Fig. 1 to Fig. 3, the working method of compact molding box wing formula low-temperature heat accumulating heat exchanger is: 1) solar heat-preservation Pattern: compressor stops；Solar water pump operating cycle；The heat energy of solar water is stored in close-coupled low-temperature heat accumulating In device standby.2) thermophore heat supply mode: described compact molding box wing formula low-temperature heat accumulating heat exchanger is as the evaporation in heat pump Device, the Lowlevel thermal energy being stored in heat storage tank 5 supplies user after being promoted by compressor.3) solar energy auxiliary regenerator device is for hot-die Formula: described compact molding box wing formula low-temperature heat accumulating heat exchanger is as the vaporizer in heat pump, and be stored in heat storage tank 5 is low Position heat energy supplies user after being promoted by compressor；Solar water pump operating cycle simultaneously, system while user's heat supply It is standby that close-coupled low-temperature heat accumulating device 5 stores Lowlevel thermal energy, and heat storage tank now is as changing between cold-producing medium and solar water Hot relief area.4) thermophore defrosting mode: described compact molding box wing formula low-temperature heat accumulating heat exchanger 5 is as the steaming in heat pump Send out device, utilize the Lowlevel thermal energy defrosting being stored in close-coupled low-temperature heat accumulating device 5.

The present embodiment, heat-storing material should be using inorganic material as supporting formation micropore and adsorbing the setting storage of organic phase change material Hot powder, its phase transition process should without change in volume, without mode of appearance change, stable performance, heat conductivility is preferable, accumulation of heat is close Spend higher；The German RUBITHERM using Rule, Hangzhou Energy Science Co., Ltd to sell is recommended to originate in PX series of high efficiency Phase-changing energy storage material, transition temperature range is preferably 10～15 DEG C；This series material form stable, is also powder under room temperature, Can directly fill.

Detailed description of the invention two: combine Fig. 5, Fig. 6, Fig. 7, Fig. 8, Fig. 9 and Figure 10 and present embodiment, this reality are described The height of the intersection fin 5-3-3 executing mode is the 90%-96% of sealing plate 5-3-2 height.It is arranged such, when heat conduction version 5-3-1 On do not set intersection fin time, the comprehensive heat conductivity of heat storage tank 5-3 is only equivalent to 20% now～30%；When intersecting fin When the height of 5-3-3 is the 50% of sealing plate 5-3-2 height, the comprehensive heat conductivity of heat storage tank 5-3 is equivalent to now 40%～60%；And along with intersecting fin 5-3-3 increase highly, the comprehensive heat conductivity of heat storage tank 5-3 presents rising Trend, when intersection fin 5-3-3 is highly sealing plate 5-3-2 more than 96% highly, the comprehensive heat conduction of heat storage tank 5-3 The effect that coefficient highly increases with intersection fin 5-3-3 is the most obvious.Other composition and annexation and detailed description of the invention one Identical.

Detailed description of the invention three: combine Figure 19, Figure 20, Figure 21, Figure 22, Figure 23 and Figure 24 and present embodiment is described, The height of the homogenizing plate 4 of present embodiment is the half of end socket 1 height.It is arranged such, and compared with homogenizing plate end socket, thing Stream distribution nonuniformity coefficient is dropped to about 0.20 by about the 1.21 of original end socket.Other composition and annexation are with concrete Embodiment one or two is identical.

Detailed description of the invention four: combine Figure 11, Figure 12, Figure 13, Figure 14 and Figure 15 and present embodiment, this enforcement are described The heat exchanger channels 5-1 of mode is square wave heat exchanger channels or staggered square wave heat exchanger channels 5-1-1.It is arranged such, at heat exchanger channels In 5-1, cold-producing medium is two-phase flow, owing to vertical and horizontal flow distribution is uneven, in traditional straight through flow passage The uneven situation of flow distribution is the most serious: overheated " being evaporated " having, the full liquid stream having goes out；On the one hand, at flow process In, staggered square wave channel design allows logistics to equalize at any time, it is ensured that heat exchange is uniform, it is to avoid liquid phase surge in passage； On the other hand, the most staggered of fin is constantly destroyed boundary region, and the trailing vortex that two phase flow produces in upstream is to downstream fin Heat transfer has played incentive action, and heat flow density can increase by more than 50%.Other composition and annexation and detailed description of the invention one, Two, three is identical.

Detailed description of the invention five: combine Fig. 8 and present embodiment is described, multiple intersection fin 5-3-3 of present embodiment include Netted rib 5-3-3-1 and rib base 5-3-3-2, netted rib 5-3-3-1 are fixedly mounted on the upper end of rib base 5-3-3-2, rib base 5-3-3-2 Height account for intersect fin 5-3-3 height 1/8～1/10.Being arranged such, the structure of netted rib is before saving finned surface space Put and add effective heat transfer area to greatest extent, according to thermal conduction study and topological principles, under above-mentioned rib base ratio, with The straight rib of tradition is compared, and heat transfer area is effectively increased more than 60%, strengthens the heat transfer between heat-storing material and heat-conducting plate 5-3-1 Hot-fluid.Other composition and annexation and detailed description of the invention one, two, three or four are identical.

Detailed description of the invention six: combine Figure 15, Figure 16, Figure 17 and Figure 18 and present embodiment is described, present embodiment The 1/2～5/8 of multiple water conservancy diversion circular hole 5-4-1, water conservancy diversion circular hole 5-4-1 a diameter of deflector 5-4 height is had on deflector 5-4, The water conservancy diversion angle of deflector 5-4 is 30 °～60 °, with 45 ° for optimum.It is arranged such, generally makes in industrial design at present Water conservancy diversion angle be 90 °, logistics transverse distribution is the most uneven, when selecting the channelization angle of 45 °, enters heat exchanger channels 5-1 Interior Peak Flow Rate drops to 1.2～1.3 with the ratio of minimum flow velocity from more than 2.2；When water conservancy diversion angle is between 30 °～60 °, The obvious change of Two-Phase Flow Resistance will not be caused.On the other hand, deflector 5-4 percent opening is the highest, and distribution effects is better. Other composition and annexation and detailed description of the invention one, two, three, four or five are identical.

Detailed description of the invention seven: combine Figure 22, Figure 23 and Figure 24 and present embodiment is described, the homogenizing plate 4 of present embodiment On offer multiple equal discharge orifice 4-1.Be arranged such, it is illustrated that homogenizing plate perforate mode be that equal diameter is interlocked perforate, compare porous The density arrangement in footpath designs more versatility, and in flow distribution effect, with compared with homogenizing plate end socket, flow distribution is uneven Even coefficient reduces an order of magnitude, compared with staggered arrangement multiple aperture density arrangement type homogenizing plate end socket, and flow distribution heterogeneous system Number have dropped 50%, and the pressure loss reduces 4%.Other composition and annexation and detailed description of the invention one, two, three, Four, five or six is identical.

Detailed description of the invention eight: combine Fig. 4 and Fig. 5 and present embodiment is described, two in the heat storage tank 5-3 of present embodiment Phase-change material packing space between individual heat-conducting plate 5-3-1, four sealing plate 5-3-2 and multiple intersection fin 5-3-3 is filled with Machine fixed phase change accumulation of heat powder.It is arranged such, the existence of multiple intersection fin 5-3-3, increases setting accumulation of heat powder and lead Heat transfer area between hot plate 5-3-1, it is ensured that heat exchange is uniform；The application of setting accumulation of heat powder avoids and adds expansion vessel Trouble, also solves the problem that organic heat-storing material mixes with caulking gum；The design in box space effectively reduces bushing type The occupation of land space of energy storage heat exchanger.Other composition and annexation and detailed description of the invention one, two, three, four, five, six or Seven is identical.

Detailed description of the invention nine: combine Figure 26 and present embodiment is described, under the air source heat pump refrigeration mode of present embodiment Operation method realized by following steps:

Step one: open the 4th electromagnetic valve E4, close the first electromagnetic valve E1 and the 3rd electromagnetic valve E3:

Step 2: the circulation of system refrigerant:

Cold-producing medium is R32, and the first of the aerofluxus entrance electric four passes reversal valve 21 of compressor 20 is led to, then through electric four passes The second of reversal valve 21 is logical to be entered in outside fin tube type air heat exchanger 22, is sequentially passed through by forward check valve 23 4th electromagnetic valve E4, capillary tube 24 and indoor fin tube type air heat exchanger 25, then sequentially pass through electric four passes commutation The threeway of valve 21, four-way, finally sequentially pass through forward check valve 23 and gas-liquid separator 26, return to compressor 20； System is by indoor fin tube type air heat exchanger 25 to user's cooling, and so far, unit completes air source heat pump refrigeration mould Operation under formula；

Opening the second electromagnetic valve E2 and the 5th electromagnetic valve E5, now part of refrigerant is bypassed before the 4th electromagnetic valve E4, Cold-producing medium sequentially enters capillary tube 24, flash evaporation 27 and the 5th electromagnetic valve E5 through steam nozzle through the second electromagnetic valve E2 28 spray into compressor 20；System is by indoor fin tube type air heat exchanger 25 to user's cooling, and so far, unit completes Operation under air source heat pump refrigeration mode.

It is arranged such, it is ensured that net for air-source heat pump units is energy Effec-tive Function in the range of outdoor temperature is 20～35 DEG C, in room After outer temperature is higher than 35 DEG C, especially in the range of 40～43 DEG C, effectively can reduce by the way of spraying steam cools down Compressor exhaust temperature, it is demonstrated experimentally that under conditions of outside air temperature is 43 DEG C, compressor exhaust temperature is more than 100 DEG C Time, carrying out spraying steam cooling, spraying steam time about 30s, delivery temperature have dropped 15 DEG C, refrigerating capacity loss less than 5%. Other composition is identical with detailed description of the invention eight with annexation.

Detailed description of the invention ten: combine Figure 26 and present embodiment is described, the fortune under the solar heat-preservation pattern of present embodiment Row method is realized by following steps:

Step one: compressor 20 stops, close the first electromagnetic valve E1, the second electromagnetic valve E2, the 3rd electromagnetic valve E3, Four electromagnetic valve E4 and the 5th electromagnetic valve E5；

Step 2: solar heat water-circulating pump 29 runs, the circulation of system solar water is:

Solar heat water-circulating pump 29 drives solar water to enter the solar water water conservancy diversion in close-coupled low-temperature heat accumulating device 33 Plate 5-4, through solar water heat exchanger channels, passes to the organic phase-change accumulation of heat in heat storage tank by part low level solar thermal energy Powder, then after solar water deflector 5-4 draws, entrance plate solar collector 32 is heated again, afterwards Hot water in plate solar collector 32 is again introduced into solar heat water-circulating pump 29, completes a solar water circulation；

Step 3: the Lowlevel thermal energy of solar water is stored in the heat storage tank 5-3 in close-coupled low-temperature heat accumulating device 33 standby With, unit so far completes the operation under solar heat-preservation pattern.

It is arranged such, it is demonstrated experimentally that be 25 DEG C at solar heat coolant-temperature gage, under conditions of single channel flow is 0.009kg/s, Heat-storing material is heated to 24 DEG C by 2 DEG C and only needs 10min.Other composition is identical with detailed description of the invention eight with annexation.

Detailed description of the invention 11: combine Figure 26 and present embodiment is described, under the thermophore heat supply mode of present embodiment Operation method is realized by following steps:

Step one: open the 3rd electromagnetic valve E3, close the first electromagnetic valve E1 and the 4th electromagnetic valve E4；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium by the air vent of compressor 20 sequentially pass through electric four passes reversal valve 21 first logical and Threeway, indoor fin tube type air heat exchanger 25, forward check valve the 23, the 3rd electromagnetic valve E3, electric expansion valve 30 and restricting orifice 31, enter the cold-producing medium deflector 5-4 of close-coupled low-temperature heat accumulating device 33, by refrigerant heat exchanger passage, The Lowlevel thermal energy being stored in heat storage tank 5-3 is taken out, then flows out close-coupled low-temperature heat accumulating device 33 through cold-producing medium deflector 5-4, Sequentially pass through forward check valve 23 and gas-liquid separator 26 afterwards, return to compressor 20；System passes through indoor fin tube type Air heat exchanger 25 is to user's heat supply, and so far, unit completes the operation under thermophore heat supply mode；

Step 3: when system inner refrigerant circular flow is too low, open the second electromagnetic valve E2 and the 5th electromagnetic valve E5, this Time part of refrigerant bypassed before the 3rd electromagnetic valve E3: cold-producing medium flow successively through the second electromagnetic valve E2, capillary tube 24, Flash evaporation 27 and the 5th electromagnetic valve E5, sprays into compressor 20 through steam nozzle 28；System is empty by indoor fin tube type Gas heat exchanger 25 is to user's heat supply, and so far, unit completes the operation under thermophore heat supply mode.

Being arranged such, use thermophore heat supply, heating performance is stable and unrelated with outdoor weather condition, and experiment proves thermophore The cycle average COP of heat supply up to 2.8, compared with under the conditions of the COP of air source heat pump low-temperature heating high by 33.3%.Other Form identical with detailed description of the invention eight with annexation.

Detailed description of the invention 12: combine Figure 26 and present embodiment is described, the solar energy auxiliary regenerator device of present embodiment supplies Operation method under heat pattern is realized by following steps:

Step one: open the 3rd electromagnetic valve E3, close the first electromagnetic valve E1, the second electromagnetic valve E2, the 4th electromagnetic valve E4 With the 5th electromagnetic valve E5；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, and cold-producing medium enters the first logical and threeway of electric four passes reversal valve 21 by compressor 20, depends on Secondary through indoor fin tube type air heat exchanger 25, forward check valve the 23, the 3rd electromagnetic valve E3, electric expansion valve 30 And restricting orifice 31 enters the cold-producing medium deflector 5-4 of close-coupled low-temperature heat accumulating device 33, by refrigerant heat exchanger passage, will The Lowlevel thermal energy being stored in heat storage tank 5-3 takes out, then flows out close-coupled low-temperature heat accumulating device 33 through cold-producing medium deflector 5-4, Finally sequentially pass through forward check valve 23 and gas-liquid separator 26 returns to compressor 20；System passes through indoor fin tube type Air heat exchanger 25, to user's heat supply, so far completes a refrigerant cycle；

Step 3: solar heat water cycle process is:

Solar heat water-circulating pump 29 runs, and solar water is entered close-coupled low-temperature heat accumulating by solar heat water-circulating pump 29 The solar water deflector 5-4 of device 33, through solar water heat exchanger channels, passes to accumulation of heat by low level solar thermal energy Organic phase-change accumulation of heat powder in case 5-3, then draw through solar water deflector 5-4, return to plate solar collector 32 are heated again, and the hot water in plate solar collector 32 is again introduced into solar heat water-circulating pump 29 afterwards, completes One solar water circulation；System by indoor fin tube type air heat exchanger 25 to user's heat supply, simultaneously compact Storing Lowlevel thermal energy in heat storage tank 5-3 in formula low-temperature heat accumulating device 33 standby, so far, unit completes solar energy auxiliary regenerator Operation under device heat supply mode.

It is arranged such, it is demonstrated experimentally that be 25 DEG C at solar heat coolant-temperature gage, under conditions of single channel flow is 0.009kg/s, The COP of solar energy auxiliary regenerator device heat supply up to more than 3.9, compared with under the conditions of the COP that heats of air source heat pump high by 86%. Other composition is identical with detailed description of the invention eight with annexation.

Detailed description of the invention 13: combine Figure 26 and present embodiment is described, the air source heat pump heating mode of present embodiment Under operation method realized by following steps:

Step one: open the first electromagnetic valve E1, closes the 3rd electromagnetic valve E3 and the 4th electromagnetic valve E4；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium through compressor 20 air vent enter electric four passes reversal valve 21 first lead to, afterwards By the threeway of electric four passes reversal valve 21 sequentially pass through indoor fin tube type air heat exchanger 25, forward check valve 23, First electromagnetic valve E1, capillary tube 24 and outside fin tube type air heat exchanger 22, after through electric four passes reversal valve 21 The second logical and four-way, flow successively through forward check valve 23 and gas-liquid separator 26 return to compressor 20；System is passed through Indoor fin tube type air heat exchanger 25 is to user's heat supply, and so far, unit completes the fortune under air source heat pump heating mode OK；

Step 3: when system inner refrigerant circular flow is too low, open the second electromagnetic valve E2 and the 5th electromagnetic valve E5, this Time part of refrigerant bypassed before electromagnetic valve E1: cold-producing medium sequentially pass through the second electromagnetic valve E2, capillary tube 24, dodge Send out device 27 and the 5th electromagnetic valve E5 and spray into compressor 20 through steam nozzle 28；System is changed by indoor fin tube type air Hot device 25 is to user's heat supply, and so far, air source heat pump when unit completion system inner refrigerant circular flow is too low heats mould Operation under formula.

It is arranged such, it is demonstrated experimentally that when outside air temperature is in the range of 6～15 DEG C, and it is the highest that air source heat pump heats efficiency； After outside air temperature is less than 6 DEG C, air source heat pump heats efficiency and declines substantially with outside air temperature, when compressor evaporating pressure During less than 0.7MPa, carrying out spraying steam and increase enthalpy, spraying steam duration about 45s, the rate that heats improves 4%, heats COP and becomes Change inconspicuous.Other composition is identical with detailed description of the invention eight with annexation.

Detailed description of the invention 14: combine Figure 26 and present embodiment is described, under the thermophore defrosting mode of present embodiment Operation method is realized by following steps:

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, and cold-producing medium sequentially passes through the first of electric four passes reversal valve 21 through compressor 20 and leads to logical with second, Pass sequentially through outside fin tube type air heat exchanger 22, forward check valve the 23, the 3rd electromagnetic valve E3, electronic expansion afterwards Valve 30 and restricting orifice 31 enter the cold-producing medium deflector 5-4 of close-coupled low-temperature heat accumulating device 33, are led to by refrigerant heat exchanger Road, takes out the Lowlevel thermal energy being stored in heat storage tank 5-3, then flows out close-coupled low-temperature heat accumulating through cold-producing medium deflector 5-4 Device 33, finally sequentially passes through forward check valve 23 and gas-liquid separator 26 returns to compressor 20；System utilizes and is stored in tightly The Lowlevel thermal energy in formula low-temperature heat accumulating device 33 that gathers defrosts, and so far, unit completes the operation under thermophore defrosting mode.

It is arranged such, it is demonstrated experimentally that use thermophore defrosting to reduce 60% than the defrosting time of traditional reverse cycle defrosting, pressure Contracting machine input power reduces by 48.1%, and the rate that heats promotes 10%, heats COP and promotes 50%.Other composition and annexation Identical with detailed description of the invention eight.

In the application, the outer wall of close-coupled low-temperature heat accumulating device 33, gas-liquid separator 26 and flash evaporation 27 all pastes heat-preservation cotton, too Sun can flat plate collector 32, solar water heating pipe between solar heat water-circulating pump 29 and close-coupled low-temperature heat accumulating device 33 Pipeline outer wall patch heat-preservation cotton, close-coupled low-temperature heat accumulating device 33 and the pipeline being connected between restricting orifice 31 and electric expansion valve 30 Outer wall patch heat-preservation cotton, the pipeline outer wall between close-coupled low-temperature heat accumulating device 33 and gas-liquid separator 26 entrance, gas-liquid separator Pipeline outer walls between 26 outlets and compressor 20 air entry all paste heat-preservation cotton, capillary tube after the first electromagnetic valve E1 24 with Pipeline outer wall between outside fin tube type air heat exchanger 22, outside fin tube type air heat exchanger 22 and electronic four Pipeline outer wall between logical reversal valve 21 second is logical, electric four passes reversal valve 21 four-way and gas-liquid separator 26 entrance it Between pipeline outer wall all paste heat-preservation cotton, capillary tube after the 4th electromagnetic valve E4 24 and indoor fin tube type air heat exchanger Between pipeline outer wall, indoor fin tube type air heat exchanger 25 and electric four passes reversal valve 21 threeway between 25 Pipeline outer wall all pastes heat-preservation cotton, the pipeline outer wall between capillary tube 24 and flash evaporation 27 entrance after the second electromagnetic valve E2, Flash evaporation 27 exports the pipeline outer wall between the steam nozzle 28 of compressor 20 and all pastes heat-preservation cotton.

The use of material for storing heat of phase change in low temperature reduces the leaving water temperature of plate solar collector and requires (solar heat coolant-temperature gage Can be at 25～35 DEG C), even if solar heat coolant-temperature gage is the highest, phase-change material also can discharge considerable latent heat of phase change.By too Sun can hot water temperature be 25 DEG C of designs, and the transition temperature range of phase-change material is preferably at 10～15 DEG C.

Phase-change material should be using inorganic material as supporting formation micropore and adsorbing the setting accumulation of heat powder of organic phase change material, its Phase transition process should without change in volume, without mode of appearance change, stable performance, heat conductivility preferably, thermal storage density higher；Can The German RUBITHERM using Rule, Hangzhou Energy Science Co., Ltd to sell originates in PX series of high efficiency phase-change accumulation energy material Material, transition temperature range is preferably 10～15 DEG C；This series material form stable, is also powder under room temperature, can directly fill out Fill.

The low-temperature heat accumulating heat exchanger occurred in detailed description of the invention nine to the detailed description of the invention 14 of the application is in Figure 26 Reference is 33.

Although the present invention is disclosed above with preferred embodiment, but it is not limited to the present invention, those skilled in the art Other changes can also be done in spirit of the present invention, and be applied in the NM field of the present invention, certainly, these foundations The change that present invention spirit is done all should be included in scope of the present invention.

Claims

null1. a case wing formula low-temperature heat accumulating heat exchanger，It includes heat exchange body (5)、Refrigerant outlet pipe (2)、Refrigerant inlet pipe (6)、Solar heat water outlet pipe (3)、Solar water inlet tube (7)、Multiple homogenizing plates (4) and multiple end socket (1)，The both sides, top of heat exchange body (5) and both sides, bottom are separately installed with an end socket (1)，A homogenizing plate (4) it is provided with in each end socket (1)，Refrigerant outlet pipe (2) is connected with the end socket (1) of the side, top of heat exchange body (5)，Refrigerant inlet pipe (6) is connected with the end socket (1) of heat exchange body (5) bottom opposite side，Solar heat water outlet pipe (3) is connected with the end socket (1) of the top opposite side of heat exchange body (5)，Solar water inlet tube (7) is connected with the end socket (1) of heat exchange body (5) side, bottom，It is characterized in that: described heat exchange body (5) includes organizing heat-exchanging component more，Many group heat-exchanging components are installed successively，Often group heat-exchanging component all includes heat exchanger channels (5-1)、Two strip of paper used for sealings (5-2)、Two heat storage tanks (5-3) and two groups of deflectors (5-4)，Two heat storage tanks (5-3) are separately mounted to the two ends up and down of heat exchanger channels (5-1)，Two strip of paper used for sealings (5-2) are separately mounted to the two ends, left and right of heat exchanger channels (5-1)，Two groups of deflectors (5-4) are separately mounted to two ends before and after heat exchanger channels (5-1)，Each heat storage tank (5-3) in said two heat storage tank (5-3) all includes two heat-conducting plates (5-3-1)、Four sealing plates (5-3-2) and multiple intersection fin (5-3-3)，Two heat-conducting plates (5-3-1) are setting up and down，The most equidistant fixed arrangement of multiple intersection fin (5-3-3) is between two heat-conducting plates (5-3-1)，Four sealing plates (5-3-2) enclose the surrounding being located at two heat-conducting plates (5-3-1)，Two heat-conducting plates (5-3-1) in heat storage tank (5-3)、Space between four sealing plates (5-3-2) and multiple intersection fin (5-3-3) is phase-change material packing space，The height of described intersection fin (5-3-3) is the 90%-96% of sealing plate (5-3-2) height，Heat exchanger channels (5-1) is square wave heat exchanger channels or staggered square wave heat exchanger channels (5-1-1).
Case wing formula low-temperature heat accumulating heat exchanger the most according to claim 1, it is characterised in that: the height of described homogenizing plate (4) is the half of end socket (1) height.
Case wing formula low-temperature heat accumulating heat exchanger the most according to claim 2, it is characterized in that: multiple intersection fins (5-3-3) include netted rib (5-3-3-1) and rib base (5-3-3-2), netted rib (5-3-3-1) is fixedly mounted on the upper end of rib base (5-3-3-2), and the height of rib base (5-3-3-2) accounts for the 1/8～1/10 of intersection fin (5-3-3) height.
Case wing formula low-temperature heat accumulating heat exchanger the most according to claim 3, it is characterized in that: on deflector (5-4), have multiple water conservancy diversion circular hole (5-4-1), the 1/2～5/8 of water conservancy diversion circular hole (5-4-1) a diameter of deflector (5-4) height, the water conservancy diversion angle of deflector (5-4) is 30 °～60 °.
5. the source pump operation method containing the case wing formula low-temperature heat accumulating heat exchanger described in claim 4, it is characterised in that: the operation method under air source heat pump refrigeration mode is realized by following steps:

Step one: open the 4th electromagnetic valve (E4), close the first electromagnetic valve (E1) and the 3rd electromagnetic valve (E3):

Step 2: the circulation of system refrigerant:

Cold-producing medium is R32, the first of aerofluxus entrance electric four passes reversal valve (21) of compressor (20) is led to, then in the second logical entrance outside fin tube type air heat exchanger (22) of electric four passes reversal valve (21), the 4th electromagnetic valve (E4), capillary tube (24) and indoor fin tube type air heat exchanger (25) is sequentially passed through by forward check valve (23), sequentially pass through the threeway of electric four passes reversal valve (21), four-way again, finally sequentially pass through forward check valve (23) and gas-liquid separator (26), return to compressor (20)；System is by indoor fin tube type air heat exchanger (25) to user's cooling, and so far, unit completes the operation under air source heat pump refrigeration mode；

Step 3: the refrigeration when outdoor high temperature causes compressor exhaust temperature too high:

Open the second electromagnetic valve (E2) and the 5th electromagnetic valve (E5), now part of refrigerant is front bypassed at the 4th electromagnetic valve (E4), and cold-producing medium sequentially enters capillary tube (24), flash evaporation (27) and the 5th electromagnetic valve (E5) through the second electromagnetic valve (E2) and sprays into compressor (20) through steam nozzle (28)；System is by indoor fin tube type air heat exchanger (25) to user's cooling, and so far, unit completes the operation under air source heat pump refrigeration mode.
6. the source pump operation method containing the case wing formula low-temperature heat accumulating heat exchanger described in claim 4, it is characterised in that: the operation method under solar heat-preservation pattern is realized by following steps:

Step one: compressor (20) stops, and closes the first electromagnetic valve (E1), the second electromagnetic valve (E2), the 3rd electromagnetic valve (E3), the 4th electromagnetic valve (E4) and the 5th electromagnetic valve (E5)；

Step 2: solar heat water-circulating pump (29) runs, the circulation of system solar water is:

Solar heat water-circulating pump (29) drives solar water to enter the solar water deflector (5-4) in case wing formula low-temperature heat accumulating heat exchanger (33), through solar water heat exchanger channels, part low level solar thermal energy is passed to the organic phase-change accumulation of heat powder in heat storage tank, enter in plate solar collector (32) after solar water deflector (5-4) is drawn again and be heated again, hot water in plate solar collector (32) is again introduced into solar heat water-circulating pump (29) afterwards, completes a solar water circulation；

Step 3: the Lowlevel thermal energy of solar water is stored in the heat storage tank (5-3) in case wing formula low-temperature heat accumulating heat exchanger (33) standby, and unit so far completes the operation under solar heat-preservation pattern.
7. the source pump operation method containing the case wing formula low-temperature heat accumulating heat exchanger described in claim 4, it is characterised in that: the operation method under thermophore heat supply mode is realized by following steps:

Step one: open the 3rd electromagnetic valve (E3), close the first electromagnetic valve (E1) and the 4th electromagnetic valve (E4)；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium is sequentially passed through the first logical and threeway of electric four passes reversal valve (21) by the air vent of compressor (20), indoor fin tube type air heat exchanger (25), forward check valve (23), 3rd electromagnetic valve (E3), electric expansion valve (30) and restricting orifice (31), enter the cold-producing medium deflector (5-4) of case wing formula low-temperature heat accumulating heat exchanger (33), by refrigerant heat exchanger passage, the Lowlevel thermal energy being stored in heat storage tank (5-3) takes out, case wing formula low-temperature heat accumulating heat exchanger (33) is flowed out again through cold-producing medium deflector (5-4), sequentially pass through forward check valve (23) and gas-liquid separator (26) afterwards, return to compressor (20)；System is by indoor fin tube type air heat exchanger (25) to user's heat supply, and so far, unit completes the operation under thermophore heat supply mode；

Step 3: when system inner refrigerant circular flow is too low, open the second electromagnetic valve (E2) and the 5th electromagnetic valve (E5), now part of refrigerant is front bypassed at the 3rd electromagnetic valve (E3): cold-producing medium flows successively through the second electromagnetic valve (E2), capillary tube (24), flash evaporation (27) and the 5th electromagnetic valve (E5), sprays into compressor (20) through steam nozzle (28)；System is by indoor fin tube type air heat exchanger (25) to user's heat supply, and so far, unit completes the operation under thermophore heat supply mode.
8. the source pump operation method containing the case wing formula low-temperature heat accumulating heat exchanger described in claim 4, it is characterised in that: the operation method under solar energy auxiliary regenerator device heat supply mode is realized by following steps:

Step one: open the 3rd electromagnetic valve (E3), close the first electromagnetic valve (E1), the second electromagnetic valve (E2), the 4th electromagnetic valve (E4) and the 5th electromagnetic valve (E5)；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium enters the first logical and threeway of electric four passes reversal valve (21) by compressor (20), sequentially pass through indoor fin tube type air heat exchanger (25), forward check valve (23), 3rd electromagnetic valve (E3), electric expansion valve (30) and restricting orifice (31) enter the cold-producing medium deflector (5-4) of case wing formula low-temperature heat accumulating heat exchanger (33), by refrigerant heat exchanger passage, the Lowlevel thermal energy being stored in heat storage tank (5-3) takes out, case wing formula low-temperature heat accumulating heat exchanger (33) is flowed out again through cold-producing medium deflector (5-4), finally sequentially pass through forward check valve (23) and gas-liquid separator (26) returns to compressor (20)；System to user's heat supply, so far completes a refrigerant cycle by indoor fin tube type air heat exchanger (25)；

Step 3: solar heat water cycle process is:

Solar heat water-circulating pump (29) runs, solar water is entered the solar water deflector (5-4) of case wing formula low-temperature heat accumulating heat exchanger (33) by solar heat water-circulating pump (29), through solar water heat exchanger channels, low level solar thermal energy is passed to the organic phase-change accumulation of heat powder in heat storage tank (5-3), draw through solar water deflector (5-4) again, return to plate solar collector (32) be heated again, hot water in plate solar collector (32) is again introduced into solar heat water-circulating pump (29) afterwards, complete a solar water circulation；System passes through indoor fin tube type air heat exchanger (25) to user's heat supply, store Lowlevel thermal energy in heat storage tank (5-3) in case wing formula low-temperature heat accumulating heat exchanger (33) standby simultaneously, so far, the operation under unit completes solar energy auxiliary regenerator device heat supply mode.
9. the source pump operation method containing the case wing formula low-temperature heat accumulating heat exchanger described in claim 4, it is characterised in that: the operation method under air source heat pump heating mode is realized by following steps:

Step one: open the first electromagnetic valve (E1), closes the 3rd electromagnetic valve (E3) and the 4th electromagnetic valve (E4)；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium through compressor (20) air vent enter electric four passes reversal valve (21) first lead to, indoor fin tube type air heat exchanger (25), forward check valve (23), the first electromagnetic valve (E1), capillary tube (24) and outside fin tube type air heat exchanger (22) is sequentially passed through afterwards by the threeway of electric four passes reversal valve (21), through the second logical and four-way of electric four passes reversal valve (21) after, flow successively through forward check valve (23) and gas-liquid separator (26) returns to compressor (20)；System is by indoor fin tube type air heat exchanger (25) to user's heat supply, and so far, unit completes the operation under air source heat pump heating mode；

Step 3: when system inner refrigerant circular flow is too low, opening the second electromagnetic valve (E2) and the 5th electromagnetic valve (E5), now part of refrigerant is front bypassed at electromagnetic valve (E1): cold-producing medium sequentially passes through the second electromagnetic valve (E2), capillary tube (24), flash evaporation (27) and the 5th electromagnetic valve (E5) and sprays into compressor (20) through steam nozzle (28)；System by indoor fin tube type air heat exchanger (25) to user's heat supply, so far, the operation under air source heat pump heating mode when unit completion system inner refrigerant circular flow is too low.
10. the source pump operation method containing the case wing formula low-temperature heat accumulating heat exchanger described in claim 4, it is characterised in that: the operation method under thermophore defrosting mode is realized by following steps:

Step one: open the 3rd electromagnetic valve (E3), close the first electromagnetic valve (E1), the second electromagnetic valve (E2), the 4th electromagnetic valve (E4) and the 5th electromagnetic valve (E5)；

Step 2: system refrigerant circulation is:

Cold-producing medium is R32, cold-producing medium sequentially passes through the first of electric four passes reversal valve (21) through compressor (20) and leads to logical with second, pass sequentially through outside fin tube type air heat exchanger (22) afterwards, forward check valve (23), 3rd electromagnetic valve (E3), electric expansion valve (30) and restricting orifice (31) enter the cold-producing medium deflector (5-4) of case wing formula low-temperature heat accumulating heat exchanger (33), by refrigerant heat exchanger passage, the Lowlevel thermal energy being stored in heat storage tank (5-3) takes out, case wing formula low-temperature heat accumulating heat exchanger (33) is flowed out again through cold-producing medium deflector (5-4), finally sequentially pass through forward check valve (23) and gas-liquid separator (26) returns to compressor (20)；System utilizes the Lowlevel thermal energy defrosting being stored in case wing formula low-temperature heat accumulating heat exchanger (33), and so far, unit completes the operation under thermophore defrosting mode.