CN203744599U - Low-temperature heat pump system for multiple working conditions - Google Patents
Low-temperature heat pump system for multiple working conditions Download PDFInfo
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- CN203744599U CN203744599U CN201420107783.9U CN201420107783U CN203744599U CN 203744599 U CN203744599 U CN 203744599U CN 201420107783 U CN201420107783 U CN 201420107783U CN 203744599 U CN203744599 U CN 203744599U
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Abstract
The utility model discloses a low-temperature heat pump system for multiple working conditions. An enhanced vapor injection compressor is adopted, a middle vapor injection loop is added to a circulation loop during refrigeration and heating, a gaseous refrigerant is supplementarily sprayed to the enhanced vapor injection compressor, and an overcooling refrigerant is added. When the environment temperature is as low as subzero 25 DEG C or as high as 55 DEG C, the heat pump system can still be normally started and operate; and at the same time, through matching use of a four-way valve, a throttling part, a one-way valve and the like, the flowing direction of working media can be changed, so that various modes of operation such as independent heating, independent refrigeration and the like can be realized simultaneously, the use simplicity of a heat-pump water heater is sufficiently improved, and the application range is enlarged.
Description
Technical field
The utility model relates to heat pump field, relates in particular to a kind of multi-state hot pump in low temp system.
Background technology
Along with the environment each seasonal temperature variation gap that warms is excessive, fixed air-cooled changes in temperature unit is frequently difficult to bear the decay such as energy that summer high-temperature cryogenic refrigeration, winter heat at present, and range of operation is subject to extremely restriction, causes the large increase of energy consumption.The enhancing of overall national strength, China's power industry has very large development, low by the end of 1999, and China's capacity of installed generator and annual electricity generating capacity reach respectively 2.988 hundred million kW and 12,231 hundred million kW, Jun Ju second place of the world.But the growth of electric power still can not meet the needs of fast development and the people's lives electricity consumption sharp increase of national economy, national short of electricity situation does not obtain basic change yet.1), load rate of grid is low at present power supply shortage performance is as follows:, system peak-valley difference is large, and peak power wretched insufficiency causes electrical network often to connect lock and rations the power supply; 2), urban electric power Growth of Consumption is rapid, and urban distribution network can not adapt to, and causes the situation of electricity under can't get into, join not.But current wind-cooling type heat pump is applied to high-temperature heat accumulation and low-temperature air conditioner cold-storage in the course of the work, in low-temperature cold accumulation or high-temperature heat accumulation, because both reach by heat exchange the object that floor space is little, high-energy stores.Thereby,-15 ~ 10 DEG C of low-temperature cold accumulations or 45 ~ 60 DEG C of accumulation of heats process in the time of work, current be mainly manifested in following two aspects: one, heating capacity progressively decay along with the decline (otherwise refrigerating capacity) of environment temperature, the size of inspiratory capacity is corresponding one by one with its air-breathing saturation temperature, air-breathing saturation temperature is higher, air-breathing larger, vice versa, and along with environment temperature progressively declines, heat pump evaporating temperature reduces, and compressor air suction specific volume increases, and gas transmission coefficient reduces, cause heating capacity to reduce, the corresponding decline of heat pump Energy Efficiency Ratio (COP); Two, parts operational reliability problem, especially compressor, under low temperature environment, when evaporating temperature is too low, the compression ratio of compressor increases and causes excessive discharge temperature, causes heat pump easily to occur back liquid, causes compressor damage when serious.Therefore, existing heat pump structure remains to be further improved, and propose will be by promoting energy accumulating technique simultaneously, part peak load is transferred to low ebb and in conjunction with dwindling floor space.
The in the situation that of power supply shortage for this reason, the feature of enforcement, multi-state hot pump in low temp and the energy accumulating technique self of time-of-use tariffs policy, for the application of energy accumulating technique provides vast potential for future development.
Summary of the invention
The purpose of this utility model is to overcome the deficiencies in the prior art, a kind of multi-state hot pump in low temp system is provided, it is combined high temperature cryogenic refrigeration, low-temperature heating with accumulation of heat, cold-storage, collection winter hot water preparing, summer high temperature are got the low peak valley low-temperature cold accumulation energy of system, make that its structure is compacter, utilization rate of equipment and installations is high, energy-saving effect is more outstanding.
To this, a kind of multi-state hot pump in low temp system of the present utility model, comprise the compressor that connects into working medium circulation loop by working medium tube, cross valve, heat exchanger components, throttle part and gas-liquid are from device, wherein, described compressor is air injection enthalpy-increasing compressor, between air injection enthalpy-increasing compressor and heat exchanger components, be provided with unidirectional valve member, liquid reservoir, overheated air jet system, described heat exchanger components comprises First Heat Exchanger, the second heat exchanger, described throttle part comprises first throttle device, bidirectional throttle assembly, the exhaust outlet of described air injection enthalpy-increasing compressor is connected with a interface of cross valve, the d interface of cross valve be connected with the gas returning port of air injection enthalpy-increasing compressor by gas-liquid separator, the b interface of cross valve is connected with the arrival end of the second heat exchanger, the c interface of cross valve is connected with the arrival end of First Heat Exchanger, the port of export of described First Heat Exchanger, the port of export of the second heat exchanger is connected with the arrival end of liquid reservoir by unidirectional valve member respectively, the port of export of described liquid reservoir respectively with the arrival end of first throttle device, the first end interface of overheated air jet system connects, the port of export of first throttle device is connected with the second end interface of overheated air jet system, the gaseous state outlet of described overheated air jet system and liquid outlet respectively with the gas supplementing opening of air injection enthalpy-increasing compressor, the arrival end of bidirectional throttle assembly connects, the port of export of bidirectional throttle assembly is connected with liquid reservoir by unidirectional valve member.
Be optimized according to above-mentioned, described multi-state hot pump in low temp system also comprises supervising device, and supervising device is connected and controls their operations sequentially from device with compressor, cross valve, First Heat Exchanger, the second heat exchanger, first throttle device, bidirectional throttle assembly, liquid reservoir, overheated air jet system and gas-liquid respectively.
Be optimized according to above-mentioned, described unidirectional valve member comprises the first check valve, the second check valve, the 3rd check valve, the 4th check valve, the arrival end of the first check valve, the port of export respectively with the port of export of First Heat Exchanger, the arrival end of liquid reservoir connects, the arrival end of the second check valve, the port of export respectively with the port of export of bidirectional throttle assembly, the arrival end of the first check valve connects, the arrival end of the 3rd check valve, the port of export respectively with the port of export of bidirectional throttle assembly, the arrival end of the 4th check valve connects, the 4th port of export of check valve and the arrival end of liquid reservoir are connected.
Be optimized according to above-mentioned, described bidirectional throttle assembly comprises the second throttling arrangement, the 3rd throttling arrangement and magnetic valve, and described magnetic valve and the 3rd throttling arrangement are connected in series, and the second throttling arrangement is connected in parallel with magnetic valve, the 3rd throttling arrangement of going into series connection.
Be optimized according to above-mentioned, the arrival end of described the second throttling arrangement, the arrival end of magnetic valve are connected with the liquid state outlet of overheated air jet system respectively, and the port of export of the second throttling arrangement is connected with the arrival end of the second check valve, the arrival end of the 3rd check valve respectively with the port of export of the 3rd throttling arrangement.
Be optimized according to above-mentioned, described first throttle device, the second throttling arrangement, the 3rd throttling arrangement are respectively electric expansion valve.
Be optimized according to above-mentioned, described First Heat Exchanger is shell and tube exchanger, or is plate type heat exchanger or for double pipe heat exchanger.
Be optimized according to above-mentioned, described overheated air jet system is plate type heat exchanger.
Be optimized according to above-mentioned, described the second heat exchanger is provided with the blower fan that is provided with of supervising device connection.
The beneficial effects of the utility model are: it adopts air injection enthalpy-increasing compressor, when freezing, heating closed circuit increase in the middle of jet loop, give the air injection enthalpy-increasing compressor gaseous refrigerant that fills spray, and increased cold matchmaker.Heat pump is low to moderate-25 DEG C during in environment temperature, high still can normally start operation during to 55 DEG C, do not need to rely on auxiliary equipment just can obtain good refrigeration, heating effect, or be to improve 10%～30% at low temperature or hot environment heat energy ability, and system is made-15 DEG C～60 DEG C bed temperature.Be used in conjunction with by combinations such as cross valve, throttle part and unidirectional valve members simultaneously, change the flow direction of working medium, thereby realize the various mode operations such as while independent heating, independent cooling, fully improved simplicity and range of application that Teat pump boiler uses.Therefore, it is multi-functional in one that this invention is specially adapted to various energy accumulating technique systems etc., has many advantages such as utilization rate of equipment and installations is high, energy-saving effect is remarkable, is a kind of building energy composite energy system of novel environmental type, is applicable to the vast urban and rural buildings of China.
Brief description of the drawings
Fig. 1 is the fundamental diagram of the utility model preferred embodiment.
Fig. 2 is the control principle drawing of the utility model preferred embodiment.
Detailed description of the invention
Below in conjunction with accompanying drawing, the utility model will be further described, Fig. 1 and Fig. 2 illustrate the preferred embodiment of the utility model, it comprises the compressor that connects into working medium circulation loop by working medium tube, cross valve 2, heat exchanger components, throttle part and gas-liquid are from device 3, wherein, described compressor is air injection enthalpy-increasing compressor 1, between air injection enthalpy-increasing compressor 1 and heat exchanger components, be provided with unidirectional valve member, liquid reservoir 4, overheated air jet system 5, described heat exchanger components comprises First Heat Exchanger 6, the second heat exchanger 7, described throttle part comprises first throttle device 8, bidirectional throttle assembly, the exhaust outlet of described air injection enthalpy-increasing compressor 1 is connected with a interface of cross valve 2, the d interface of cross valve 2 be connected with the gas returning port of air injection enthalpy-increasing compressor 1 by gas-liquid separator, the b interface of cross valve 2 is connected with the arrival end of the second heat exchanger 7, the c interface of cross valve 2 is connected with the arrival end of First Heat Exchanger 6, the port of export of described First Heat Exchanger 6, the port of export of the second heat exchanger 7 is connected with the arrival end of liquid reservoir 4 by unidirectional valve member respectively, the port of export of described liquid reservoir 4 respectively with the arrival end of first throttle device 8, the first end interface of overheated air jet system 5 connects, the port of export of first throttle device 8 is connected with the second end interface of overheated air jet system 5, the gaseous state outlet of described overheated air jet system 5 and liquid outlet respectively with the gas supplementing opening of air injection enthalpy-increasing compressor 1, the arrival end of bidirectional throttle assembly connects, the port of export of bidirectional throttle assembly is connected with liquid reservoir 4 by unidirectional valve member.
And, multi-state hot pump in low temp system also comprises supervising device 9, and supervising device 9 is connected and controls their operations sequentially from device 3 with air injection enthalpy-increasing compressor 1, cross valve 2, First Heat Exchanger 6, the second heat exchanger 7, first throttle device 8, bidirectional throttle assembly, liquid reservoir 4, overheated air jet system 5 and gas-liquid respectively.And, in prioritization scheme, described unidirectional valve member comprises the first check valve 10, the second check valve 11, the 3rd check valve 12, the 4th check valve 13, the arrival end of the first check valve 10, the port of export respectively with the port of export of First Heat Exchanger 6, the arrival end of liquid reservoir 4 connects, the arrival end of the second check valve 11, the port of export respectively with the port of export of bidirectional throttle assembly, the arrival end of the first check valve 10 connects, the arrival end of the 3rd check valve 12, the port of export respectively with the port of export of bidirectional throttle assembly, the arrival end of the 4th check valve 13 connects, the port of export of the 4th check valve 13 is connected with the arrival end of liquid reservoir 4.And described bidirectional throttle assembly comprises the second throttling arrangement 14, the 3rd throttling arrangement 15 and magnetic valve 16, described magnetic valve 16 and the 3rd throttling arrangement 15 are connected in series, and the second throttling arrangement 14 is connected in parallel with magnetic valve 16, the 3rd throttling arrangement 15 of going into series connection.And, the arrival end of described the second throttling arrangement 14, the arrival end of magnetic valve 16 are connected with the liquid state outlet of overheated air jet system 5 respectively, and the port of export of the second throttling arrangement 14 is connected with the arrival end of the second check valve 11, the arrival end of the 3rd check valve 12 respectively with the port of export of the 3rd throttling arrangement 15.According to practical application, the port of export of described First Heat Exchanger 6 is connected with the arrival end of the first check valve 10 and the port of export of the second check valve 11 respectively by t-joint, the arrival end of liquid reservoir 4 by t-joint respectively with the port of export of the first check valve 10, the outlet mold end of the 4th check valve 13 connects, the port of export of liquid reservoir 4 be also by t-joint respectively with the arrival end of first throttle device 8, the first interface of overheated air jet system 5 connects, and the arrival end of the second check valve 11 equally by t-joint respectively with the port of export of bidirectional throttling device, the arrival end of the 3rd check valve 12 connects.And the second heat exchanger 7 is provided with the blower fan 17 that supervising device 9 connects, and first throttle device 8, the second throttling arrangement 14, the 3rd throttling arrangement 15 are respectively electric expansion valve, or are the sub-assembly of other throttling arrangement and stop valve.And described First Heat Exchanger 6 is shell and tube exchanger, or it is plate type heat exchanger or for double pipe heat exchanger, described overheated air jet system 5 is plate type heat exchanger, or other heat exchanger.Carrier temperature that it should be noted that this product can be at-30～90oC medium.
As follows according to above-mentioned operation principle:
Refrigeration mode: by supervising device 9, cross valve 2 is opened, first throttle device 8 is opened, and magnetic valve 16 leaves, the second throttling arrangement 14 is opened, and the 3rd throttling arrangement 15 is opened.When startup, working medium produces high temperature and high pressure gas by air injection enthalpy-increasing compressor 1 and flows into condensation in the second heat exchanger 7 through the ab interface of cross valve 2, then by the 4th check valve 13 and liquid reservoir 4, after completing heat exchange, flow to respectively first throttle device 8 and overheated air jet system 5, now working medium is again excessively cold, make overheated rear gas flow back to the gas supplementing opening of air injection enthalpy-increasing compressor 1, subcooled liquid is through flowing to magnetic valve 16, the second throttling arrangement 14, the 3rd throttling arrangement 15, after bidirectional throttle, flow to First Heat Exchanger 6 by the second check valve 11 again and carry out heat exchange, flow out by the cd interface of cross valve 2 immediately, finally turn back to air injection enthalpy-increasing compressor 1 gas returning port by gas-liquid separator.
Heating mode: by supervising device 9, cross valve 2 is closed, first throttle device 8 is opened, and magnetic valve 16 closes, the second throttling arrangement 14 is opened, and the 3rd throttling arrangement 15 is opened.When startup, working medium produces high temperature and high pressure gas by air injection enthalpy-increasing compressor 1 and flows into condensation in First Heat Exchanger 6 through the cd interface of cross valve 2, by the first check valve 10 and liquid reservoir 4, after completing heat exchange, flow to respectively first throttle device 8 and overheated air jet system 5, now working medium is again excessively cold, make overheated rear gas flow back to air injection enthalpy-increasing compressor 1 gas supplementing opening, subcooled liquid is through flowing to the second throttling arrangement 14, after throttling, flowing to the second heat exchanger 7 by the 3rd check valve 12 carries out after heat exchange, by the ab interface of cross valve 2 flow out thereafter, then turn back to the gas returning port of air injection enthalpy-increasing compressor 1 by gas-liquid separator.
Defrost pattern: cross valve 2 is opened by supervising device 9, first throttle device 8 closes, magnetic valve 16 leaves, the second throttling arrangement 14 is opened, the 3rd throttling arrangement 15 is opened, working medium produces high temperature and high pressure gas by air injection enthalpy-increasing compressor 1 and flows into condensation in the second heat exchanger 7 through the ab interface end of cross valve 2, after completing heat exchange by the 4th check valve 13 and liquid reservoir 4, flow to overheated air jet system 5, then through flowing to magnetic valve 16, the second throttling arrangement 14, the 3rd throttling arrangement 15, complete and flow to First Heat Exchanger 6 by the second check valve 11 after bidirectional throttle and carry out heat exchange, by the cd interface of cross valve 2 flow out thereafter, then turn back to air injection enthalpy-increasing compressor 1 gas returning port by gas-liquid separator.
Above-mentioned specific embodiment is only the good detailed description of the invention of the utility model effect, and all or multi-state hot pump in low temp system of being equal to identical with this structure, all in the application's protection domain.
Claims (9)
1. a multi-state hot pump in low temp system, comprise the compressor that connects into working medium circulation loop by working medium tube, cross valve (2), heat exchanger components, throttle part and gas-liquid are from device (3), it is characterized in that: described compressor is air injection enthalpy-increasing compressor (1), between air injection enthalpy-increasing compressor (1) and heat exchanger components, be provided with unidirectional valve member, liquid reservoir (4), overheated air jet system (5), described heat exchanger components comprises First Heat Exchanger (6), the second heat exchanger (7), described throttle part comprises first throttle device (8), bidirectional throttle assembly, the exhaust outlet of described air injection enthalpy-increasing compressor (1) is connected with a interface of cross valve (2), the d interface of cross valve (2) be connected with the gas returning port of air injection enthalpy-increasing compressor (1) by gas-liquid separator, the b interface of cross valve (2) is connected with the arrival end of the second heat exchanger (7), the c interface of cross valve (2) is connected with the arrival end of First Heat Exchanger (6), the port of export of described First Heat Exchanger (6), the port of export of the second heat exchanger (7) is connected with the arrival end of liquid reservoir (4) by unidirectional valve member respectively, the port of export of described liquid reservoir (4) respectively with the arrival end of first throttle device (8), the first end interface of overheated air jet system (5) connects, the port of export of first throttle device (8) is connected with the second end interface of overheated air jet system (5), the gaseous state outlet of described overheated air jet system (5) and liquid outlet respectively with the gas supplementing opening of air injection enthalpy-increasing compressor (1), the arrival end of bidirectional throttle assembly connects, the port of export of bidirectional throttle assembly is connected with liquid reservoir (4) by unidirectional valve member.
2. multi-state hot pump in low temp system according to claim 1, it is characterized in that: described multi-state hot pump in low temp system also comprises supervising device (9), supervising device (9) is connected and controls their operations sequentially from device (3) with air injection enthalpy-increasing compressor (1), cross valve (2), First Heat Exchanger (6), the second heat exchanger (7), first throttle device (8), bidirectional throttle assembly, liquid reservoir (4), overheated air jet system (5) and gas-liquid respectively.
3. multi-state hot pump in low temp system according to claim 1, it is characterized in that: described unidirectional valve member comprises the first check valve (10), the second check valve (11), the 3rd check valve (12), the 4th check valve (13), the arrival end of the first check valve (10), the port of export respectively with the port of export of First Heat Exchanger (6), the arrival end of liquid reservoir (4) connects, the arrival end of the second check valve (11), the port of export respectively with the port of export of bidirectional throttle assembly, the arrival end of the first check valve (10) connects, the arrival end of the 3rd check valve (12), the port of export respectively with the port of export of bidirectional throttle assembly, the arrival end of the 4th check valve (13) connects, the port of export of the 4th check valve (13) is connected with the arrival end of liquid reservoir (4).
4. according to multi-state hot pump in low temp system described in claims 1 to 3 any one claim, it is characterized in that: described bidirectional throttle assembly comprises the second throttling arrangement (14), the 3rd throttling arrangement (15) and magnetic valve (16), described magnetic valve (16) is connected in series with the 3rd throttling arrangement (15), and the second throttling arrangement (14) is connected in parallel with magnetic valve (16), the 3rd throttling arrangement (15) of going into series connection.
5. multi-state hot pump in low temp system according to claim 4, it is characterized in that: the arrival end of described the second throttling arrangement (14), the arrival end of magnetic valve (16) are connected with the liquid state outlet of overheated air jet system (5) respectively, and the port of export of the second throttling arrangement (14) is connected with the arrival end of the second check valve (11), the arrival end of the 3rd check valve (12) respectively with the port of export of the 3rd throttling arrangement (15).
6. multi-state hot pump in low temp system according to claim 4, is characterized in that: described first throttle device (8), the second throttling arrangement (14), the 3rd throttling arrangement (15) are respectively electric expansion valve.
7. according to multi-state hot pump in low temp system described in claims 1 to 3 any one claim, it is characterized in that: described First Heat Exchanger (6) is shell and tube exchanger, or be plate type heat exchanger or for double pipe heat exchanger.
8. multi-state hot pump in low temp system according to claim 2, is characterized in that: described overheated air jet system (5) is plate type heat exchanger.
9. multi-state hot pump in low temp system according to claim 2, is characterized in that: described the second heat exchanger (7) is provided with the blower fan (17) being connected with supervising device (9).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420107783.9U CN203744599U (en) | 2014-03-11 | 2014-03-11 | Low-temperature heat pump system for multiple working conditions |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420107783.9U CN203744599U (en) | 2014-03-11 | 2014-03-11 | Low-temperature heat pump system for multiple working conditions |
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| Publication Number | Publication Date |
|---|---|
| CN203744599U true CN203744599U (en) | 2014-07-30 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420107783.9U Expired - Fee Related CN203744599U (en) | 2014-03-11 | 2014-03-11 | Low-temperature heat pump system for multiple working conditions |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203744599U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103836836A (en) * | 2014-03-11 | 2014-06-04 | 广东长菱空调冷气机制造有限公司 | Multi-condition low-temperature heat pump system |
| CN105258392A (en) * | 2015-10-15 | 2016-01-20 | 珠海格力电器股份有限公司 | Heat pump heating system, control method and heat pump water heater |
-
2014
- 2014-03-11 CN CN201420107783.9U patent/CN203744599U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103836836A (en) * | 2014-03-11 | 2014-06-04 | 广东长菱空调冷气机制造有限公司 | Multi-condition low-temperature heat pump system |
| CN103836836B (en) * | 2014-03-11 | 2016-03-02 | 广东长菱空调冷气机制造有限公司 | A kind of multi-state hot pump in low temp system |
| CN105258392A (en) * | 2015-10-15 | 2016-01-20 | 珠海格力电器股份有限公司 | Heat pump heating system, control method and heat pump water heater |
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| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140730 Termination date: 20200311 |
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| CF01 | Termination of patent right due to non-payment of annual fee |