CN206361931U - A kind of low-temperature heat pump water heater - Google Patents
A kind of low-temperature heat pump water heater Download PDFInfo
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- CN206361931U CN206361931U CN201621335089.8U CN201621335089U CN206361931U CN 206361931 U CN206361931 U CN 206361931U CN 201621335089 U CN201621335089 U CN 201621335089U CN 206361931 U CN206361931 U CN 206361931U
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- temperature heat
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Abstract
The utility model is related to a kind of low-temperature heat pump water heater, including major loop and air injection enthalpy-increasing loop, the major loop includes compressor, four-way valve, condenser, supercooling tube and evaporator, the supercooling tube includes the inside and outside supervisor being arranged and looped pipeline, and the major loop is connected to form air injection enthalpy-increasing loop with the gas supplementing opening of looped pipeline and compressor successively by refrigerant pipe.Low-temperature heat pump water heater provided by the utility model, as economizer, instead of plate type heat exchanger commonly used in the prior art using supercooling tube so that source pump has low cost, the advantage such as occupy little space, and is adapted to promote the use of.
Description
Technical field
The utility model is related to field of water heaters, specifically, is related to a kind of low-temperature heat pump water heater.
Background technology
Existing conventional heat pump hot water machine, when running into low-temperature condition, the evaporating temperature reduction of system, i.e. low pressure drops
It is low, cause the compression ratio of compressor to exceed confidence band, it is easy to cause the damage of the important components such as compressor, to ensure unit
Reliability, can typically select not start, or only by cool water heating to lower temperature (i.e. compressor range of operation side
At edge), then replace it to run by electric auxiliary heat.
Compared to conventional heat pump water heater, low form heat pump can then lift heating capacity and heating efficiency under low temperature, and
The reliability of system can be ensured, the compressor that common low form heat pump is used there are two major classes：Air injection enthalpy-increasing form, spray
Liquid methods for cooling, and the heat pump Energy Efficiency Ratio that air injection enthalpy-increasing compressor is constituted be better than by Liquid injection cooling compressor set into heat
Pumping system, therefore air injection enthalpy-increasing heat pump promotes degree and is higher than liquid injection cooling type.
In air injection enthalpy-increasing system, the liquid after condensation can be evaporated to gas by economizer heat absorption, then by this portion
Divide gas to spray into the middle pressure chamber of compressor, improve the enthalpy of this part refrigerant, increase return-air amount, reduce compression ratio, improve system
Reliability, heating capacity and Energy Efficiency Ratio of the increase system under low ambient temperature state.Wherein, economizer is used as refrigerant and refrigerant
The heat exchanger of heat exchange, common selection type is plate type heat exchanger or flash vessel.
Although plate type heat exchanger heat transfer effect is good, its is on the high side (for 15kW heating machines, its plate used
Formula heat exchanger price can typically reach more than 300 yuan), product cost is not dominant, and volume is larger, takes up space more, no
It is easy to placement；Flash vessel is then due to the bad control of its jet/spouting liquid.
In view of this, it is special to propose the utility model.
Utility model content
The utility model aims to provide a kind of low-temperature heat pump water heater, using supercooling tubular construction as economizer, instead of
Traditional plate type heat exchanger or flash vessel, with the purpose for reaching reduction water heater cost and reducing water heater unit floor space.
To achieve the above object, specifically adopt the following technical scheme that：
A kind of low-temperature heat pump water heater, including major loop and air injection enthalpy-increasing loop, the major loop include compressor 5, four
Port valve 1, condenser 2, supercooling tube 3 and evaporator 4, the supercooling tube 3 include the inside and outside supervisor 31 being arranged and looped pipeline 32, the master
Gas supplementing opening 51 of the loop by refrigerant pipe successively with looped pipeline 32 and compressor 5 is connected to form air injection enthalpy-increasing loop.
Further scheme of the present utility model is：The supervisor 31 is connected to form first passage with major loop；The supervisor
31 and it is sheathed between the looped pipeline 32 in the outside of supervisor 31 and forms the second channel being isolated with first passage.
Further scheme of the present utility model is：The two ends of the supervisor 31 are main import 301 and primary outlet 302 respectively；
The looped pipeline 32 is respectively equipped with secondary import 303 and sub-outlet 304 close to the two ends of radial direction.
The supervisor 31 of supercooling tube 3 is connected to form first passage with major loop, and its main import 301 is condensed out with condenser 2
Mouth 21 is connected, and primary outlet 302 is connected with evaporator 4, and the space between looped pipeline 32 and supervisor 31, i.e. second channel is then jet
The part in increasing enthalpy loop.
Further scheme of the present utility model is：The second channel with before first passage or with being connected after first passage.
Further scheme of the present utility model is：The secondary import 303 of the supercooling tube 3 and the primary outlet 302 of supercooling tube 3 or
It is connected with the refrigerant exit 21 of condenser 2, and is connected through sub-outlet 304 with the gas supplementing opening 51 of compressor 5.
Further scheme of the present utility model is：Between the primary outlet 302 and secondary import 303 or refrigerant exit 21 with it is secondary
The first magnetic valve 10 and first throttle device 7 are sequentially provided between import 303, the first throttle device 7 is heating power expansion valve
Or electric expansion valve.
In such scheme, the refrigerant of major loop has two kinds of modes for entering air injection enthalpy-increasing loop, and a kind of is from condenser 2
Refrigerant exit 21 branches to the secondary import 303 of looped pipeline 31, in the condition that condenser 2 is sufficiently large and refrigerant fully exchanges heat with water tank
Under, the refrigerant for being diverted into looped pipeline 31 is liquid, can be controlled by the first magnetic valve 10 and first throttle device 7；It is another
Kind it is the secondary import 303 that looped pipeline 31 is branched to from the primary outlet 302 of supervisor 31, it is less than normal and exchange heat and do not fill in the type selecting of condenser 2
In the case of point, condense insufficient so that the refrigerant of outflow condenser 2 is gas-liquid mixture, causes the tune of first throttle device 7
Difficulty increase is saved, jet amount is unstable to cause tonifying Qi not enough, influences the work of compressor, therefore the shunting of main refrigerant circuit is put
After the supervisor 31 of supercooling tube 3.
Further scheme of the present utility model is：The 3rd throttling arrangement 9 is provided between the primary outlet 302 and evaporator 4,
3rd throttling arrangement 9 is heating power expansion valve or electric expansion valve.
Further scheme of the present utility model is：The second electromagnetism is sequentially provided between the primary outlet 302 and gas supplementing opening 51
Valve 11 and second throttling device 8.
Further scheme of the present utility model is：The second throttling device 8 is that capillary, heating power expansion valve or electronics are swollen
One kind in swollen valve.
Further scheme of the present utility model is：The radial section product and the radial section of looped pipeline 32 of the supervisor 31 accumulates it
Than for 3:4, the refrigerant flux of unit interval interior supervisor 31 is more than the refrigerant flux of looped pipeline 32, and its flux ratio is not less than 3:1.
Further scheme of the present utility model is：The tube wall of the supervisor 31 is equidistantly provided with annular projection vertically, also may be used
Using thread protrusion structure or twisted shape structure, the heat exchange area between increase supervisor 31 and looped pipeline 32.
Further scheme of the present utility model is：Between the evaporator 4 and compressor 5 be provided with gas-liquid separator 6, prevent by
Insufficient cause operative liquid refrigerant return to compressor 5 in evaporating.
The beneficial effects of the utility model are：
1. use supercooling tubular construction as low-temperature heat pump water heater economizer, traditional plate type heat exchanger and flash distillation instead of
Device, saves cost；
2. using supercooling tubular construction as the economizer of low-temperature heat pump water heater, its space-consuming is board-like much smaller than traditional
Heat exchanger, reduces the space hold of low-temperature heat pump water heater unit；
Brief description of the drawings
Fig. 1 is the structural representation of supercooling tube used in the utility model.
The annexation schematic diagram for the low-temperature heat pump water heater that Fig. 2 is provided by the utility model embodiment 1.
The annexation schematic diagram for the low-temperature heat pump water heater that Fig. 3 is provided by the utility model embodiment 2.
Critical piece is as follows in figure：
1-four-way valve, 2-condenser, 21-refrigerant exit, 3-supercooling tube, 31-supervisor, 32-looped pipeline, 301-main
Import, 302-primary outlet, the import of 303-pair, 304-sub-outlet, 4-evaporator, 5-compressor, 51-gas supplementing opening, 6-gas
Liquid/gas separator, 7-first throttle device, 8-second throttling device, the 9-the three throttling arrangement, the 10-the first magnetic valve, 11-
Second magnetic valve.
Embodiment
To make the utility model technical problem solved, the technical scheme used and the technique effect reached clearer,
Embodiment of the present utility model is described in further detail below in conjunction with accompanying drawing.
Embodiment 1
As shown in Fig. 2 a kind of low-temperature heat pump water heater, including major loop and air injection enthalpy-increasing loop, in the major loop
Refrigerant sequentially passes through compressor 5 and exports, returns to compressor 5 after four-way valve 1, condenser 2, supercooling tube 3, evaporator 4, four-way valve 1
Import.
As depicted in figs. 1 and 2, supercooling tube 3 described in the present embodiment includes the supervisor 31 being connected with major loop and sealing
The looped pipeline 32 in the outside of supervisor 31 is sheathed on, the two ends of the supervisor 31 are main import 301 and primary outlet 302, the looped pipeline respectively
32 are respectively equipped with secondary import 303 and sub-outlet 304 close to the two ends of radial direction；The supervisor 31 of supercooling tube is connected with major loop, and it is led
Import 301 is connected with the condensate outlet 21 of condenser 2, and primary outlet 302 is connected with evaporator 4, and looped pipeline 32 is then jet increasing
The part in enthalpy loop.
As shown in Fig. 2 the secondary import 303 of supercooling tube 3 described in the present embodiment is connected with the primary outlet 302 of supercooling tube 3,
And the gas supplementing opening 51 through sub-outlet 304 and compressor 5 is connected to form air injection enthalpy-increasing loop；It is less than normal and change in the type selecting of condenser 2
In the case that heat is insufficient, condense insufficient so that the refrigerant of outflow condenser 2 is gas-liquid mixture, causes first throttle to fill
Put 7 the increase of regulation difficulty, jet amount is unstable to cause tonifying Qi not enough, influences the work of compressor, therefore by main refrigerant circuit
Shunting be placed on after the supervisor 31 of supercooling tube 3.
In the present embodiment, the first magnetic valve 10 and first throttle are sequentially provided between the primary outlet 302 and secondary import 303
Device 7, the first throttle device 7 is preferably electric expansion valve, can be by the regulating guarantee refrigerant gas of refrigerant flow
Body has certain degree of superheat, naturally it is also possible to select heating power expansion valve to replace.
In the present embodiment, the 3rd throttling arrangement 9, the 3rd throttling dress are provided between the primary outlet 302 and evaporator 4
It is preferably electric expansion valve to put 9, can have certain degree of superheat by the regulating guarantee refrigerant gas of refrigerant flow, when
Can also so heating power expansion valve be selected to replace.
In the present embodiment, the second magnetic valve 11 and the second throttling are sequentially provided between the primary outlet 302 and gas supplementing opening 51
Device 8, it is considered to Cost Problems, the second throttling device 8 is preferably capillary, naturally it is also possible to select heating power expansion valve or electricity
Sub- expansion valve, can equally reach the throttling action that capillary is played.
In the present embodiment, the ratio between the radial section product of the supervisor 31 and the radial section product of looped pipeline 32 are preferably 4, unit
The refrigerant flux of supervisor 31 is more than the refrigerant flux of looped pipeline 32 in time, and its flux ratio is not less than 3:1.
In the present embodiment, the tube wall of the supervisor 31 is equidistantly provided with annular projection vertically, certainly also can be convex using screw thread
Structure or twisted shape structure are played, to increase the heat exchange area between supervisor 31 and looped pipeline 32.
In the present embodiment, gas-liquid separator 6 is provided preferably between the evaporator 4 and compressor 5, is prevented due to evaporation not
Fully cause operative liquid refrigerant return to compressor 5.
The operation principle of the present embodiment is：During normal operation, refrigerant is subcooled via compressor 5- four-way valve 1- condensers 2-
The major loop flowing that the throttling arrangement 9- evaporator 4- four-way valve 1- compressors 5 of pipe 3- the 3rd are constituted；When the temperature of the surroundings is low,
First magnetic valve 10 is opened, and refrigerant is divided into two-way flowing, respectively above-mentioned major loop and compressor 5- four-way valve 1- condensers
2- supercooling tubes 3- the first magnetic valve 10- first throttle device 7- supercooling tube 3- compressors 5, wherein behind a loop be jet
Increasing enthalpy loop, refrigerant returns the pair of supercooling tube 3 after the supervisor 31 by supercooling tube 3 by the throttling of first throttle device 7
Pipe 32 carries out heat absorption evaporation, spurts into the middle pressure chamber of compressor 5 by gas supplementing opening 51 afterwards, improves the capacity of compressor 5, increases
The input power of big compressor 5, reduces compression ratio, improves the operational reliability of system at low ambient temperatures, while supercooling tube 3
Using the Energy Efficiency Ratio of system can be greatly improved.
Embodiment 2
As shown in figure 3, a kind of low-temperature heat pump water heater, including major loop and air injection enthalpy-increasing loop, in the major loop
Refrigerant sequentially passes through compressor 5 and exports, returns to compressor 5 after four-way valve 1, condenser 2, supercooling tube 3, evaporator 4, four-way valve 1
Import.
As shown in figures 1 and 3, supercooling tube 3 described in the present embodiment includes the supervisor 31 being connected with major loop and sealing
The looped pipeline 32 in the outside of supervisor 31 is sheathed on, the two ends of the supervisor 31 are main import 301 and primary outlet 302, the looped pipeline respectively
32 are respectively equipped with secondary import 303 and sub-outlet 304 close to the two ends of radial direction；The supervisor 31 of supercooling tube is connected with major loop, and it is led
Import 301 is connected with the condensate outlet 21 of condenser 2, and primary outlet 302 is connected with evaporator 4, and looped pipeline 32 is then jet increasing
The part in enthalpy loop.
As shown in figure 3, the refrigerant exit 21 of condenser 2 described in the present embodiment is connected with the secondary import 303 of supercooling tube 3
Connect, and the gas supplementing opening 51 through sub-outlet 304 and compressor 5 is connected to form air injection enthalpy-increasing loop；Using sufficiently large condenser 2
When, and under conditions of refrigerant and water tank fully exchange heat, flow out all liquid of refrigerant of refrigerant exit 21, the first electricity can be passed through
Magnet valve 10 and the control coolant distribution of first throttle device 7 enter looped pipeline 31, therefore the shunting of main refrigerant circuit is placed on into supercooling tube 3
Supervisor 31 before.
In the present embodiment, the first magnetic valve 10 and first segment are sequentially provided between the refrigerant exit 21 and secondary import 303
Device 7 is flowed, the first throttle device 7 is preferably heating power expansion valve, can be by the regulating guarantee refrigerant of refrigerant flow
Gas has certain degree of superheat, naturally it is also possible to select electric expansion valve to replace.
In the present embodiment, the 3rd throttling arrangement 9, the 3rd throttling dress are provided between the primary outlet 302 and evaporator 4
It is preferably electric expansion valve to put 9, can have certain degree of superheat by the regulating guarantee refrigerant gas of refrigerant flow, when
Can also so heating power expansion valve be selected to replace.
In the present embodiment, the second magnetic valve 11 and the second throttling are sequentially provided between the primary outlet 302 and gas supplementing opening 51
Device 8, it is considered to Cost Problems, the second throttling device 8 is preferably capillary, naturally it is also possible to select heating power expansion valve or electricity
Sub- expansion valve, can equally reach the throttling action that capillary is played.
In the present embodiment, the ratio between the radial section product of the supervisor 31 and the radial section product of looped pipeline 32 are preferably 4, unit
The refrigerant flux of supervisor 31 is more than the refrigerant flux of looped pipeline 32 in time, and its flux ratio is not less than 3:1.
In the present embodiment, the tube wall of the supervisor 31 is equidistantly provided with annular projection vertically, certainly also can be convex using screw thread
Structure or twisted shape structure are played, to increase the heat exchange area between supervisor 31 and looped pipeline 32.
In the present embodiment, gas-liquid separator 6 is provided preferably between the evaporator 4 and compressor 5, is prevented due to evaporation not
Fully cause operative liquid refrigerant return to compressor 5.
The operation principle of the present embodiment is：During normal operation, refrigerant is subcooled via compressor 5- four-way valve 1- condensers 2-
The major loop flowing that the throttling arrangement 9- evaporator 4- four-way valve 1- compressors 5 of pipe 3- the 3rd are constituted；When the temperature of the surroundings is low,
First magnetic valve 10 is opened, and refrigerant is divided into two-way flowing, respectively above-mentioned major loop and compressor 5- four-way valve 1- condensers
2- supercooling tubes 3- the first magnetic valve 10- first throttle device 7- supercooling tube 3- compressors 5, wherein behind a loop be jet
Increasing enthalpy loop, refrigerant returns to the pair of supercooling tube 3 by the throttling of first throttle device 7 after being flowed out from the refrigerant exit 2 of condenser 2
Pipe 32 carries out heat absorption evaporation, spurts into the middle pressure chamber of compressor 5 by gas supplementing opening 51 afterwards, improves the capacity of compressor 5, increases
The input power of big compressor 5, reduces compression ratio, improves the operational reliability of system at low ambient temperatures, while supercooling tube 3
Using the Energy Efficiency Ratio of system can be greatly improved.
It above are only preferred embodiment of the present utility model and institute's application technology principle.It will be appreciated by those skilled in the art that
The utility model is not limited to specific embodiment described here, and various obvious changes can be carried out for a person skilled in the art
Change, readjust and substitute without departing from protection domain of the present utility model.Therefore, although by above example to this reality
It is described in further detail with new, but the utility model is not limited only to above example, is not departing from this practicality
In the case of new design, other more equivalent embodiments can also be included, and scope of the present utility model is by appended right
Claimed range is determined.
Claims (10)
1. a kind of low-temperature heat pump water heater, including major loop and air injection enthalpy-increasing loop, the major loop include compressor (5), four
Port valve (1), condenser (2), supercooling tube (3) and evaporator (4), it is characterised in that what the supercooling tube (3) was arranged including inside and outside
Be responsible for (31) and looped pipeline (32), the major loop by refrigerant pipe successively with looped pipeline (32) and the gas supplementing opening of compressor (5)
(51) it is connected to form air injection enthalpy-increasing loop.
2. low-temperature heat pump water heater according to claim 1, it is characterised in that the supervisor (31) is connected shape with major loop
Into first passage；Form what is be isolated with first passage between the supervisor (31) and the looped pipeline (32) being sheathed on the outside of supervisor (31)
Second channel.
3. low-temperature heat pump water heater according to claim 1, it is characterised in that based on the two ends difference of the supervisor (31)
Import (301) and primary outlet (302)；The looped pipeline (32) is respectively equipped with secondary import (303) and sub-outlet close to the two ends of radial direction
(304)。
4. low-temperature heat pump water heater according to claim 2, it is characterised in that the second channel with before first passage or
It is connected with after first passage.
5. low-temperature heat pump water heater according to claim 3, it is characterised in that the secondary import (303) and primary outlet
(302) or with the refrigerant exit (21) of condenser (2) it is connected, and gas supplementing opening (51) phase through sub-outlet (304) with compressor (5)
Even.
6. low-temperature heat pump water heater according to claim 5, it is characterised in that the primary outlet (302) and secondary import
(303) the first magnetic valve (10) and first throttle device are sequentially provided between or between refrigerant exit (21) and secondary import (303)
(7), the first throttle device (7) is heating power expansion valve or electric expansion valve.
7. low-temperature heat pump water heater according to claim 3, it is characterised in that the primary outlet (302) and evaporator (4)
Between be provided with the 3rd throttling arrangement (9), the 3rd throttling arrangement (9) be heating power expansion valve or electric expansion valve.
8. low-temperature heat pump water heater according to claim 3, it is characterised in that the primary outlet (302) and gas supplementing opening
(51) the second magnetic valve (11) and second throttling device (8) are sequentially provided between.
9. low-temperature heat pump water heater according to claim 8, it is characterised in that the second throttling device (8) is capillary
One kind in pipe, heating power expansion valve or electric expansion valve.
10. the low-temperature heat pump water heater according to claims 1 to 3 any one, it is characterised in that the supervisor (31)
It is 3 that radial section, which accumulates the ratio between radial section product with looped pipeline (32),:4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621335089.8U CN206361931U (en) | 2016-12-07 | 2016-12-07 | A kind of low-temperature heat pump water heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201621335089.8U CN206361931U (en) | 2016-12-07 | 2016-12-07 | A kind of low-temperature heat pump water heater |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206361931U true CN206361931U (en) | 2017-07-28 |
Family
ID=59373607
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201621335089.8U Active CN206361931U (en) | 2016-12-07 | 2016-12-07 | A kind of low-temperature heat pump water heater |
Country Status (1)
| Country | Link |
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| CN (1) | CN206361931U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111023609A (en) * | 2019-11-25 | 2020-04-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioning system and control method |
| CN116263279A (en) * | 2021-12-13 | 2023-06-16 | 中国石油天然气股份有限公司 | Air source heat pump device and method for heating produced liquid in oil production well site |
-
2016
- 2016-12-07 CN CN201621335089.8U patent/CN206361931U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111023609A (en) * | 2019-11-25 | 2020-04-17 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioning system and control method |
| CN111023609B (en) * | 2019-11-25 | 2023-12-12 | 珠海格力节能环保制冷技术研究中心有限公司 | Air conditioning system and control method |
| CN116263279A (en) * | 2021-12-13 | 2023-06-16 | 中国石油天然气股份有限公司 | Air source heat pump device and method for heating produced liquid in oil production well site |
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