CN203323365U - Heat-pump water heater - Google Patents
Heat-pump water heater Download PDFInfo
- Publication number
- CN203323365U CN203323365U CN2013202864945U CN201320286494U CN203323365U CN 203323365 U CN203323365 U CN 203323365U CN 2013202864945 U CN2013202864945 U CN 2013202864945U CN 201320286494 U CN201320286494 U CN 201320286494U CN 203323365 U CN203323365 U CN 203323365U
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- heat exchanger
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Abstract
The utility model relates to a heat-pump water heater. The heat-pump water heater is characterized by comprising a first gas-liquid separator, a first compressor, a first four-way valve, a second gas-liquid separator, a second compressor, a first one-way valve, a second one-way valve, a second four-way valve, a first heat exchanger, a first electronic expansion valve, a heat exchanger, a capillary tube, a second electronic expansion valve, a solenoid valve and a second heat exchanger. The heat-pump water heater has the advantages that the structure is simple and reliable, double-level series operation and one-level parallel operation of double compressors can be freely changed over, and the flow adjustment range is greatly enlarged.
Description
Technical field
The utility model relates to a kind of Teat pump boiler.
Background technology
Teat pump boiler is because range of operation is wider, and when summer, the refrigeration system pressure ratio is lower, adopts single-stage compressor to meet the demands; And the refrigeration system pressure ratio is higher during winter, single-stage refrigerating system has occurred that efficiency is low, the high problem of easily burning compressor of delivery temperature, and adopting double-stage compressor is the basic method addressed the above problem; Announce at present some two-stage compression heat pump systems both at home and abroad, but had following problems: or can only move by twin-stage; Can be single the twin-stage switching, but only move a compressor (another compressor is shut down) during the single-stage operation, caused the idle waste of equipment; Though being 201010600155.0 related systems, application number can realize single twin-stage switching, but also double-compressor parallel running simultaneously during the single-stage operation, but two cross valves, two choke valves have been adopted, four check valves, eight stop valves (manual or electronic), make system configuration very complicated, affected reliability, increased the control difficulty.
When refrigeration system Two-stage Compression (series operation) and single stage compress parallel running, the refrigerant circulation flow differs large (can reach more than 6 times), is difficult to match the throttle mechanism (adjustable range of general electric expansion valve is below 4 times) that the outflow adjustable range meets the demands.The solution that this problem is not yet arranged in current single two-stage refrigeration (heat pump) system.
Summary of the invention
The purpose of this utility model is to overcome the deficiencies in the prior art and a kind of Teat pump boiler simple and reliable for structure is provided, and can realize freely switching of the operation of double-compressor double stage tandem and single-stage parallel running, and flow adjustment range can significantly be widened.
In order to achieve the above object, the utility model is to realize like this, it is a kind of Teat pump boiler, it is characterized in that comprising the first vapour liquid separator, the first compressor, the first cross valve, the second vapour liquid separator, the second compressor, the first check valve, the second check valve, the second cross valve, First Heat Exchanger, the first electric expansion valve, heat exchanger, capillary, the second electric expansion valve, magnetic valve and the second heat exchanger; Wherein:
The outlet of described the first vapour liquid separator is communicated with the entrance of the first compressor, and the arrival end of the first vapour liquid separator is communicated with the S end of the first cross valve and the S end of the second cross valve respectively, and the outlet of the first compressor is communicated with the D end of the first cross valve;
The E end of described the first cross valve is communicated with the entrance of the second check valve, and the C end of the first cross valve is communicated with the arrival end of the second vapour liquid separator and the second outlet d of heat exchanger respectively;
The outlet of described the second vapour liquid separator is communicated with the entrance of the second compressor, and the outlet of the second compressor is communicated with the entrance of the first check valve;
The outlet of described the first check valve and the second check valve all is communicated with the D end of the second cross valve;
The E end of described the second cross valve is communicated with the outlet of the second heat exchanger, and the C end of the second cross valve is communicated with the entrance of First Heat Exchanger;
The outlet of described First Heat Exchanger is communicated with the entrance of the first electric expansion valve and the first entrance a of heat exchanger respectively;
The outlet of described the first electric expansion valve is communicated with the second entrance c of heat exchanger;
The first outlet b of described heat exchanger is communicated with the entrance of entrance capillaceous and the second electric expansion valve respectively;
Described outlet capillaceous is communicated with the entrance of magnetic valve;
The outlet of described the second electric expansion valve is communicated with the entrance of the second heat exchanger respectively and the outlet of magnetic valve is communicated with;
The entrance of described magnetic valve is communicated with outlet capillaceous.
Described First Heat Exchanger and the second heat exchanger can be fin tube type, plate-fin heat exchanger, shell-tube type, bushing type and plate type heat exchanger, and heat transferring medium can be cold-producing medium, water, aqueous organopolysiloxane, saline solution etc.
Described the first electric expansion valve and the second electric expansion valve can be capillary, heating power expansion valve and electric expansion valve, or the combination between throttle mechanism.
Described the first vapour liquid separator and the second vapour liquid separator are vapour liquid separator independently, or the vapour liquid separator carried during the supply of material of Partial shrinkage machine.
The utility model advantage compared with prior art is as follows:
1, simple in structure, system adopts two cross valves, two check valves, two electric expansion valves have just been realized the single-stage parallel connection of compressor and the switching of double stage tandem, flow adjustment range can significantly be widened, and no matter system is to have a clear superiority in aspect weld bond number or the simplification of device reliability and control;
2, adopt the method for electric expansion valve and capillary paralleling to widen flow adjustment range, make the system operation more reliable and more stable.
The accompanying drawing explanation
Fig. 1 is refrigerant flow path block diagram of the present utility model.
The specific embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present utility model is described further.It should be noted that at this,, but do not form restriction of the present utility model for helping to understand the utility model for the explanation of these embodiments.In addition, below in each embodiment of described the utility model involved technical characterictic as long as form each other conflict, just can not interosculate.
In description of the present utility model, term " first " reaches " second " only for describing purpose, and can not be interpreted as indication or hint relative importance.
As shown in Figure 1, it is a kind of Teat pump boiler, comprises the first vapour liquid separator 1, the first compressor 2, the first cross valve 3, the second vapour liquid separator 4, the second compressor 5, the first check valve 6, the second check valve 7, the second cross valve 8, First Heat Exchanger 9, the first electric expansion valve 10, heat exchanger 11, capillary 12, the second electric expansion valve 13, magnetic valve 14 and the second heat exchanger 15; Wherein:
The outlet of described the first vapour liquid separator 1 is communicated with the entrance of the first compressor 2, and the arrival end of the first vapour liquid separator 1 is communicated with the S end of the first cross valve 3 and the S end of the second cross valve 8 respectively, and the outlet of the first compressor 2 is communicated with the D end of the first cross valve 3;
The E end of described the first cross valve 3 is communicated with the entrance of the second check valve 7, and the C end of the first cross valve 3 is communicated with the arrival end of the second vapour liquid separator 4 and the second outlet d of heat exchanger 11 respectively;
The outlet of described the second vapour liquid separator 4 is communicated with the entrance of the second compressor 5, and the outlet of the second compressor 5 is communicated with the entrance of the first check valve 6;
The outlet of described the first check valve 6 and the second check valve 7 all is communicated with the D end of the second cross valve 8;
The E end of described the second cross valve 8 is communicated with the outlet of the second heat exchanger 15, and the C end of the second cross valve 8 is communicated with the entrance of First Heat Exchanger 9;
The outlet of described First Heat Exchanger 9 is communicated with the entrance of the first electric expansion valve 10 and the first entrance a of heat exchanger 11 respectively;
The outlet of described the first electric expansion valve 10 is communicated with the second entrance c of heat exchanger 11;
The first outlet b of described heat exchanger 11 is communicated with the entrance of capillary 12 and the entrance of the second electric expansion valve 13 respectively;
The outlet of described capillary 12 is communicated with the entrance of magnetic valve 14;
The outlet of described the second electric expansion valve 13 is communicated with the entrance of the second heat exchanger 15 respectively and the outlet of magnetic valve 14 is communicated with;
The entrance of described magnetic valve 14 is communicated with the outlet of capillary 12.
When double stage tandem moves, cold-producing medium divides device 1 via the first vapour-liquid, the first compressor 2, through the D of the first cross valve 3 hold into and C bring out, enter the second compressor 5 by the second vapour liquid separator 4 again, the D that enters the second cross valve 8 by the first check valve 6 hold into and C bring out, enter First Heat Exchanger 9, after condensation of refrigerant becomes liquid, be divided into two-way, first via cold-producing medium temperature after the first electric expansion valve 10 throttlings reduces, by cooling the second road cold-producing medium of heat exchanger 11, cold-producing medium after the second tunnel is cooled by the second electric expansion valve 13(now with it in parallel magnetic valve 14 turn-off) enter the second heat exchanger 15, be subject to thermal evaporation in the second heat exchanger 15 after out, through the E of the second cross valve 8, hold and after S brings out and, flow into the first vapour liquid separator 1, First Heat Exchanger 9 out becomes gas through the cold-producing medium of the first electric expansion valve 10 after being heated in heat exchanger 11, converges into a road with the C mouth cold-producing medium out of the first cross valve 3 and enters the second vapour liquid separator 4.
When the single-stage parallel running, cold-producing medium divides two-way respectively by two compressors, and the first via is divided device 1, the first compressor 2 via the first vapour-liquid, through the D of the first cross valve 3 hold into and E bring out, flow into the D end of the second cross valves 8 through the second check valve 7; The S of second tunnel the first cross valve 3 hold into and C bring out, through the second vapour liquid separator 4, the second compressor 5, through the first check valve 6(and the first via, converge) flow into the D end of the second cross valve 8, cold-producing medium after converging goes out through the C of the second cross valve, the First Heat Exchanger 9 of flowing through, be condensed into liquid, from the first entrance a of heat exchanger 11, flow into again from the first outlet b flows out (now the first electric expansion valve 10 is closed), by the second electric expansion valve 13 and capillary 12(now two paths all open to increase flow).
In the present embodiment, described First Heat Exchanger 9 and the second heat exchanger 15 can be that the heat exchanger of cold-producing medium and the mutual heat exchange of air is as (being not limited to) fin tube type and plate-fin, cold-producing medium-other liquid as the heat exchanger of (being not limited to) water, aqueous organopolysiloxane, the mutual heat exchange of saline solution as (being not limited to) shell-tube type, bushing type, plate type heat exchanger.
In the present embodiment, described the first electric expansion valve 10 and the second electric expansion valve 13 contain general all kinds of throttle mechanisms, as capillary, heating power expansion valve, electric expansion valve etc., and the combination between throttle mechanism (as capillary+electric expansion valve).
In the present embodiment, described the first vapour liquid separator 1 and the second vapour liquid separator 4 be containing vapour liquid separator independently, and the vapour liquid separator carried during the supply of material of Partial shrinkage machine.
In the utility model implementation process, according to the purposes difference, can produce refrigeration (as air-conditioning, freezing and refrigeration) at the second heat exchanger place, also can produce at the First Heat Exchanger place heating effect (as produced hot water, hot blast).
Below by reference to the accompanying drawings embodiment of the present utility model is made to detailed invention, but the utility model is not limited to described embodiment.For the ordinary skill in the art, in the situation that do not break away from principle of the present utility model and aim and these embodiments are carried out to multiple variation, modification, replacement and distortion still fall within protection domain of the present utility model.
Claims (4)
1. a Teat pump boiler, is characterized in that comprising the first vapour liquid separator (1), the first compressor (2), the first cross valve (3), the second vapour liquid separator (4), the second compressor (5), the first check valve (6), the second check valve (7), the second cross valve (8), First Heat Exchanger (9), the first electric expansion valve (10), heat exchanger (11), capillary (12), the second electric expansion valve (13), magnetic valve (14) and the second heat exchanger (15); Wherein:
The outlet of described the first vapour liquid separator (1) is communicated with the entrance of the first compressor (2), the arrival end of the first vapour liquid separator (1) is communicated with the S end of the first cross valve (3) and the S end of the second cross valve (8) respectively, and the outlet of the first compressor (2) is communicated with the D end of the first cross valve (3);
The E end of described the first cross valve (3) is communicated with the entrance of the second check valve (7), and the C end of the first cross valve (3) is communicated with the arrival end of the second vapour liquid separator (4) and the second outlet d of heat exchanger (11) respectively;
The outlet of described the second vapour liquid separator (4) is communicated with the entrance of the second compressor (5), and the outlet of the second compressor (5) is communicated with the entrance of the first check valve (6);
The outlet of described the first check valve (6) and the second check valve (7) all is communicated with the D end of the second cross valve (8);
The E end of described the second cross valve (8) is communicated with the outlet of the second heat exchanger (15), and the C end of the second cross valve (8) is communicated with the entrance of First Heat Exchanger (9);
The outlet of described First Heat Exchanger (9) is communicated with the entrance of the first electric expansion valve (10) and the first entrance a of heat exchanger (11) respectively;
The outlet of described the first electric expansion valve (10) is communicated with the second entrance c of heat exchanger (11);
The first outlet b of described heat exchanger (11) is communicated with the entrance of capillary (12) and the entrance of the second electric expansion valve (13) respectively;
The outlet of described capillary (12) is communicated with the entrance of magnetic valve (14);
The outlet of described the second electric expansion valve (13) is communicated with the entrance of the second heat exchanger (15) respectively and the outlet of magnetic valve (14) is communicated with;
The entrance of described magnetic valve (14) is communicated with the outlet of capillary (12).
2. Teat pump boiler according to claim 1, it is characterized in that described First Heat Exchanger (9) and the second heat exchanger (15) can be fin tube type, plate-fin heat exchanger, shell-tube type, bushing type and plate type heat exchanger, heat transferring medium can be cold-producing medium, water, aqueous organopolysiloxane, saline solution etc.
3. Teat pump boiler according to claim 1, is characterized in that described the first electric expansion valve (10) and the second electric expansion valve (13) can be capillary, heating power expansion valve and electric expansion valve, or the combination between throttle mechanism.
4. Teat pump boiler according to claim 1, is characterized in that described the first vapour liquid separator (1) and the second vapour liquid separator (4) are for vapour liquid separator independently, or the vapour liquid separator carried during the supply of material of Partial shrinkage machine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013202864945U CN203323365U (en) | 2013-05-24 | 2013-05-24 | Heat-pump water heater |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013202864945U CN203323365U (en) | 2013-05-24 | 2013-05-24 | Heat-pump water heater |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203323365U true CN203323365U (en) | 2013-12-04 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013202864945U Expired - Fee Related CN203323365U (en) | 2013-05-24 | 2013-05-24 | Heat-pump water heater |
Country Status (1)
| Country | Link |
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| CN (1) | CN203323365U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104676940A (en) * | 2015-01-14 | 2015-06-03 | 宁波赛西电器有限公司 | Double-stage compressed air source heat pump system |
| CN105509358A (en) * | 2015-12-21 | 2016-04-20 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
-
2013
- 2013-05-24 CN CN2013202864945U patent/CN203323365U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104676940A (en) * | 2015-01-14 | 2015-06-03 | 宁波赛西电器有限公司 | Double-stage compressed air source heat pump system |
| CN104676940B (en) * | 2015-01-14 | 2017-04-05 | 宁波赛森节能设备有限公司 | A kind of Two-stage Compression air source heat pump system |
| CN105509358A (en) * | 2015-12-21 | 2016-04-20 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
| CN105509358B (en) * | 2015-12-21 | 2018-05-01 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
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Legal Events
| 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: 20131204 Termination date: 20170524 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |