CN203518332U - Heat recovery system and heat recovery unit with same - Google Patents
Heat recovery system and heat recovery unit with same Download PDFInfo
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- CN203518332U CN203518332U CN201320624433.5U CN201320624433U CN203518332U CN 203518332 U CN203518332 U CN 203518332U CN 201320624433 U CN201320624433 U CN 201320624433U CN 203518332 U CN203518332 U CN 203518332U
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- valve
- cross valve
- heat exchanger
- capillary
- pipe
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Abstract
The utility model discloses a heat recovery system and a heat recovery unit with the heat recovery system. A capillary tube s of a first four-way valve is communicated with an air suction pipeline between a first solenoid valve and a compressor, a capillary tube s of a second four-way valve is communicated with an air suction pipeline between a second solenoid valve and the compressor, in this way, in the period of mode switching of the heat recovery system, even if the first solenoid valve or the second solenoid valve is closed, the capillary tube s of the first four-way valve or the second four-way valve is always communicated with the lower-pressure side of the heat recovery system, stable difference between high pressure and low pressure in the first four-way valve or the second four-way value is ensured, leakage of the first four-way valve or the second four-way valve is avoided, and reliability and stability of the heat recovery system are improved.
Description
Technical field
The utility model relates to air-conditioning technical field, in particular to a kind of heat recovery system.
Background technology
Common pump type heat unit, under powering-off state, on the pilot slide valve of cross valve, the capillary that connects D pipe is exhaust outlet, the condenser conducting of d and compressor, all the time in high-pressure side; The capillary s that connects S pipe is air entry, the finned heat exchanger conducting with compressor, all the time in low-pressure side.Cross valve internal piston both sides form stable height pressure reduction like this, thereby realize the circulation of freezing and heating.
For recovery type heat unit, generally there are five kinds of patterns: freeze, heat, freeze+hot water, water heating, heat+water heating.For completing smoothly freely changing of five kinds of patterns, generally need to realize by the commutation of two cross valves.The pattern transition period, idle heat exchanger unavoidably can accumulate refrigerant.Meanwhile, for guaranteeing the antifreeze of idle heat exchanger, avoid idle heat exchanger directly and low-pressure side conducting, often between the import department of gas-liquid separator and the S pipe of cross valve, increase magnetic valve.Therefore in the situation of closed electromagnetic valve, idle heat exchanger for example, along with outer work condition rising (environment temperature or water temperature raise), cause the gaseous coolant evaporation capacity of idle heat exchanger to increase, pressure raises gradually, make cross valve internal piston both sides cannot form stable height pressure reduction, piston and main slide valve may occur that skew causes cross valve internal leakage, and main refrigerant circuit leaks to idle heat exchanger, causes that the high pressure of system is too high.
For example: as shown in Figure 1, under refrigeration mode, two cross valves are in off-position for the fundamental diagram of recovery type heat unit, and the D of two cross valves, C manage conducting, and S, E manage conducting, and the first magnetic valve 81 unlatchings, the second magnetic valve 82 cuts out.The E pipe of the first cross valve 71, S pipe respectively with air-condition heat exchanger 40 conductings, because the second magnetic valve 82 cuts out, under refrigeration mode, hot water heat exchanger 30 is idle heat exchanger, after switching, idle hot water heat exchanger 30 is subject to ectocine water temperature higher, causes the refrigerant pressure accumulating in hot water heat exchanger 30 to raise.Because the capillary s on common cross valve pilot slide valve is welded on S pipe, the E pipe, S pipe that therefore makes the second cross valve 72 respectively with hot water heat exchanger conducting, all there is higher pressure, make cannot guarantee to form stable height pressure reduction in the second cross valve 72.After continuing for some time, the piston of the second cross valve 72 inside is passed by counter-force, D, E manage conducting, S, C manage conducting, it is cross valve internal leakage, make gases at high pressure in system discharged to idle hot water heat exchanger 30, thereby cause the refrigerant circulation quantity not sufficient of main loop, cannot guarantee the reliability and stability of complete machine.
Therefore, solve recovery type heat system in the pattern transition period, owing to accumulating refrigerant in idle case tube heat exchanger, make cannot form stable height pressure reduction in cross valve, causing the inner easily leakage of cross valve, is those skilled in the art's technical problems urgently to be resolved hurrily thereby cause the reliability of heat recovery system and the problem of stability reduction.
Utility model content
Based on this, be necessary the irrationality existing for prior art, a kind of heat recovery system is provided, by the capillary s on the pilot slide valve of cross valve is connected with the suction line between low-pressure side magnetic valve and compressor, capillary s is communicated with low-pressure side all the time, guarantee to there is stable height pressure reduction in cross valve, improve reliability and the stability of heat recovery system.
The technical scheme of a kind of heat recovery system that the utility model provides is as follows:
A heat recovery system, comprising: compressor 10; The first cross valve 71 and the second cross valve 72, the D pipe of the first cross valve 71 is connected with the exhaust end of compressor 10, the D pipe of the second cross valve 72 is connected with the C pipe of the first cross valve 71, and the S pipe of the first cross valve 71 and the S pipe of the second cross valve 72 are all connected with the suction end of compressor 10; Finned heat exchanger 20, the second end of finned heat exchanger 20 is connected with the C pipe of the second cross valve 72; Air-condition heat exchanger 40, the first end of air-condition heat exchanger 40 is connected with the E pipe of the first cross valve 71, and the second end of air-condition heat exchanger 40 is connected with the first end of finned heat exchanger 20; Hot water heat exchanger 30, the first end of hot water heat exchanger 30 is connected with the E pipe of the second cross valve 72, and the second end of hot water heat exchanger 30 is connected with the first end of finned heat exchanger 20; One end of the first magnetic valve 81, the first magnetic valves 81 is connected with the S pipe of the first cross valve 71, and the other end is connected with the suction end of compressor 10; One end of the second magnetic valve 82, the second magnetic valves 82 is connected with the S pipe of the second cross valve 72, and the other end is connected with the suction end of compressor 10; Especially, on the pilot slide valve of the pilot slide valve of the first cross valve 71 and the second cross valve 72, include capillary s, the capillary s of the first cross valve 71 is connected with the suction line between the first magnetic valve 81 and compressor 10; The capillary s of the second cross valve 72 is connected with the suction line between the second magnetic valve 82 and compressor 10.
Preferably, the capillary d on the pilot slide valve of the second cross valve 72 is connected with the D pipe of the first cross valve 71.
Preferably, also comprise gas-liquid separator 60, the outlet of gas-liquid separator 60 is connected with the suction end of compressor 10, and the import of gas-liquid separator 60 is all connected with the other end of the first magnetic valve 81 and the other end of the second magnetic valve 82.
Preferably, the capillary s of the capillary s of the first cross valve 71 and the second cross valve 72 is all connected with the import of gas-liquid separator.
Preferably, also comprise reservoir 50, the first end of the second end of air-condition heat exchanger 40 and the second end of hot water heat exchanger 30 and finned heat exchanger 20 is all connected with reservoir 50.
Preferably, the first check valve 91 and the first electric expansion valve 101 between reservoir 50 and air-condition heat exchanger 40, have been arranged in parallel.
Preferably, the 3rd check valve 93 and the second electric expansion valve 102 between reservoir 50 and finned heat exchanger 20, have been arranged in parallel.
Preferably, between reservoir 50 and hot water heat exchanger 30, be arranged in parallel the second check valve 92 and defrost capillary 110, on defrost capillary 110 branch roads, be also provided with magnetic valve 83.
Preferably, the second check valve 92 and defrost electric expansion valve between reservoir 50 and hot water heat exchanger 30, have been arranged in parallel
The technical scheme of the another kind of recuperation of heat unit that the utility model provides is as follows:
A recuperation of heat unit, especially, comprises heat recovery system as above.
Preferably, the capillary s of the first cross valve 71 is fixed in the suction line between the first magnetic valve 81 and compressor 10 by fixture, and/or the capillary s of the second cross valve 72 is fixed in the suction line between the second magnetic valve 82 and compressor 10 by fixture.
Preferably, fixture is geometrical clamp.
The beneficial effects of the utility model are:
Application the technical solution of the utility model, by being connected the capillary s of the first cross valve with the suction line between the first magnetic valve and described compressor; The capillary s of the second cross valve is connected with the suction line between the second magnetic valve and described compressor, in the pattern transition period of heat recovery system, even the first magnetic valve or the second closed electromagnetic valve, the capillary s of the first cross valve or the second cross valve is connected with the low-pressure side of heat recovery system all the time, the inside that guarantees the first cross valve or the second cross valve has stable height pressure reduction, avoid the leakage of the first cross valve or the second cross valve, improve reliability and the stability of heat recovery system.
Accompanying drawing explanation
The Figure of description that forms the application's a part is used to provide further understanding of the present utility model, and schematic description and description of the present utility model is used for explaining the utility model, does not form improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is heat recovery system schematic diagram of the prior art;
Fig. 2 is cross valve off-position schematic diagram of the prior art;
Fig. 3 is cross valve "on" position schematic diagram of the prior art;
Fig. 4 is the cross valve "on" position schematic diagram in the present embodiment;
Fig. 5 is the heat recovery system schematic diagram in the present embodiment.
In above accompanying drawing, there is following Reference numeral:
1, pilot slide valve; 2, solenoid; 3, main valve; 4, piston; 5, main slide valve; 6, left piston chamber; 7, right plunger shaft; 10, compressor; 20, finned heat exchanger; 30, hot water heat exchanger; 40, air-condition heat exchanger; 50, reservoir; 60, gas-liquid separator; 71, the first cross valve; 72, the second cross valve; 81, the first magnetic valve; 82, the second magnetic valve; 83, the 3rd magnetic valve; 91, the first check valve; 92, the second check valve; 93, the 3rd check valve; 101, the first electric expansion valve; 102, the second electric expansion valve; 110, defrost capillary.
The specific embodiment
It should be noted that, in the situation that not conflicting, embodiment and the feature in embodiment in the application can combine mutually.Describe below with reference to the accompanying drawings and in conjunction with the embodiments the utility model in detail.
The operation principle of common cross valve is as follows:
Referring to Fig. 2, Fig. 3, cross valve must could normally be worked under certain pressure, and cross valve is comprised of three parts: pilot slide valve 1, and main valve 3 and solenoid 2, solenoid 2 can be dismantled, and pilot slide valve 1 is integrally welded with main valve 3.On pilot slide valve 1, include capillary d, capillary e, capillary s, capillary c, main valve 3 is provided with left piston chamber 6, right plunger shaft 7, and D manages, E manages, S manages, C pipe, capillary d is connected with D pipe, capillary e is connected with left piston chamber 6, and capillary c is connected with right plunger shaft 7, and capillary s is connected with S pipe, in air-conditioning system, D pipe is connected with the exhaust end of compressor.
When solenoid 2 is in off-position, as Fig. 2, pilot slide valve 1 moves to left under right side Compress Spring drives, and gases at high pressure enter right plunger shaft 7 after entering capillary d, on the other hand, the gas in left piston chamber 6 is discharged, because piston two ends exist pressure reduction, the main slide valve 5 in piston 4 and main valve 3 moves to left, and makes S pipe and condenser take over (E pipe) and communicates, another two adapters communicate, and form kind of refrigeration cycle.
When solenoid 2 is in "on" position, as Fig. 3, under the magneticaction that pilot slide valve 1 produces at solenoid, overcome the tension force of Compress Spring and move to right, gases at high pressure enter left piston chamber 6 after entering capillary d, on the other hand, the gas of right plunger shaft 7 is discharged, because piston two ends exist pressure reduction, piston 4 and main slide valve 5 move to right, and make S pipe and finned heat exchanger take over (C pipe) and communicate, another two adapters communicate, and form and heat circulation.
The present embodiment discloses a kind of heat recovery system, by optimizing the internal structure of cross valve, make cross valve in heat recovery system, there is stable height pressure reduction, avoid internal leakage, improve stability and the reliability of heat recovery system, referring to Fig. 4 and Fig. 5, specifically comprise:
In heat recovery system, arrange the first cross valve 71 and the second cross valve 72 make its freezing, heat, freeze+hot water, can mutually switch between water heating, five kinds of patterns of heat+water heating, belong to prior art, do not repeat them here.
In the present embodiment by increase by the first magnetic valve 81 between the first cross valve 71 and compressor 10, between the second cross valve 72 and compressor 10, increase by the second magnetic valve 82 simultaneously, idle heat exchanger when the break-make by the first magnetic valve 81 and the second magnetic valve 82 guarantees water heating or heats is in medium voltage side, cut-out is connected with suction side, solved the antifreeze problem of idle heat exchanger, belong to prior art, do not repeat them here.
By the capillary s of the first cross valve 71 is connected with the suction line between the first magnetic valve 81 and compressor 10, the capillary s of the second cross valve is connected with the suction line between the second magnetic valve and described compressor, in the pattern transition period of heat recovery system, even the first magnetic valve or the second closed electromagnetic valve, the capillary s of the first cross valve or the second cross valve is connected with the low-pressure side of heat recovery system all the time, the inside that guarantees the first cross valve or the second cross valve has stable height pressure reduction, avoid the leakage of the first cross valve or the second cross valve, make the interior major loop of heat recovery system there will not be the situation of coolant quantity deficiency, improve reliability and the stability of heat recovery system.
Wherein, air-condition heat exchanger 40 and hot water heat exchanger 30 are shell and tube exchanger.
Preferably, capillary d on the pilot slide valve of the second cross valve 72 is connected with the D pipe of the first cross valve 71, due under heating mode, the first cross valve 71 is in power-up state, its D, E pipe communicates, S, C pipe communicates, the second cross valve 72 is in off-position simultaneously, its D, C pipe communicates, E, S pipe communicates, now, the D pipe of the first cross valve 71 is connected with the exhaust side (high-pressure side) of compressor, the D pipe of the second cross valve 72 is connected with the suction side (low-pressure side) of compressor, and for cross valve, capillary d on its pilot valve need to be communicated with high-pressure side the normal work of guarantee cross valve, therefore, capillary d on the pilot slide valve of the second cross valve 72 is connected with the D pipe of the first cross valve 71 and can guarantees that the capillary d of the second cross valve 72 is connected with the exhaust side of compressor all the time, make the second cross valve 72 reliability service under stable height pressure reduction.
Referring to Fig. 5, heat recovery system also comprises gas-liquid separator 60, and the outlet of gas-liquid separator 60 is connected with the suction end of compressor 10, and the import of gas-liquid separator 60 is all connected with the other end of the first magnetic valve 81 and the other end of the second magnetic valve 82.The cold-producing medium that assurance enters in compressor is gaseous state, avoids compressor generation liquid hit phenomenon.
Preferably, the capillary s of the capillary s of the first cross valve 71 and the second cross valve 72 can also be connected with the import of gas-liquid separator.
Referring to Fig. 5, heat recovery system also comprises reservoir 50, the second end of air-condition heat exchanger 40 and the second end of hot water heat exchanger 30 and, the first end of finned heat exchanger 20 is all connected with reservoir 50, wherein, reservoir 50 is three pipe reservoirs.
Referring to Fig. 5, between reservoir 50 and air-condition heat exchanger 40, be arranged in parallel the first check valve 91 and the first electric expansion valve 101, between reservoir 50 and finned heat exchanger 20, be arranged in parallel the 3rd check valve 93 and the second electric expansion valve 102.Wherein, the first electric expansion valve 101 and the second electric expansion valve 102 have the effect of throttling.The first check valve 91 and the 3rd check valve 93 can avoid liquid refrigerant in fluid reservoir 50 respectively reverse flow return air-condition heat exchanger 40 and finned heat exchanger 20, affect heat transfer effect.
Referring to Fig. 5, between reservoir 50 and hot water heat exchanger 30, be arranged in parallel the second check valve 92 and defrost capillary 110, on defrost capillary 110 branch roads, be also provided with magnetic valve 83.Wherein, the second check valve 92 can be avoided the liquid refrigerant reverse flow backheat water-to-water heat exchanger 30 in fluid reservoir 50, affects heat transfer effect, and another, the magnetic valve 83 on defrost capillary branch road is opened under defrost pattern, makes system carry out defrost.
Separately, between reservoir 50 and hot water heat exchanger 30, the second check valve 92 and defrost electric expansion valve can also be arranged in parallel.The same, the second check valve 92 can be avoided the liquid refrigerant reverse flow backheat water-to-water heat exchanger 30 in fluid reservoir 50, affects heat transfer effect, and another, defrost electric expansion valve is opened under defrost pattern, makes system carry out defrost.
The utility model also provides a kind of recuperation of heat unit, especially, comprises heat recovery system as above.
Wherein, the capillary s of the first cross valve 71 is fixed in the suction line between the first magnetic valve 81 and compressor 10 by fixture, and/or, the capillary s of the second cross valve 72 is fixed in the suction line between the second magnetic valve 82 and compressor 10 by fixture, prevents that the capillary s on cross valve from shattering in running.
Preferably, fixture is geometrical clamp.
In order better to illustrate, now describe above-mentioned heat recovery system operation principle in detail by the utility model, the water heating of wherein take circulates, heats circulation and water heating defrost circulation is example:
Water heating circulation:
Heat circulation:
Water heating defrost circulation:
The foregoing is only preferred embodiment of the present utility model, be not limited to the utility model, for a person skilled in the art, the utility model can have various modifications and variations.All within spirit of the present utility model and principle, any modification of doing, be equal to replacement, improvement etc., within all should being included in protection domain of the present utility model.
Claims (12)
1. a heat recovery system, comprising:
Compressor (10);
The first cross valve (71) and the second cross valve (72), the D pipe of described the first cross valve (71) is connected with the exhaust end of compressor (10), the D pipe of described the second cross valve (72) is connected with the C pipe of described the first cross valve (71), and the S pipe of described the first cross valve (71) and the S pipe of described the second cross valve (72) are all connected with the suction end of described compressor (10);
Finned heat exchanger (20), the first end of described finned heat exchanger (20) is connected with the C pipe of described the second cross valve (72);
Air-condition heat exchanger (40), the first end of described air-condition heat exchanger (40) is connected with the E pipe of described the first cross valve (71), and the second end of described air-condition heat exchanger (40) is connected with the second end of described finned heat exchanger (20);
Hot water heat exchanger (30), the first end of described hot water heat exchanger (30) is connected with the E pipe of described the second cross valve (72), and the second end of described hot water heat exchanger (30) is connected with the first end of described finned heat exchanger (20);
The first magnetic valve (81), one end of described the first magnetic valve (81) is connected with the S pipe of described the first cross valve (71), and the other end is connected with the suction end of described compressor (10);
The second magnetic valve (82), one end of described the second magnetic valve (82) is connected with the S pipe of described the second cross valve (72), and the other end is connected with the suction end of described compressor (10);
It is characterized in that, on the pilot slide valve of the pilot slide valve of described the first cross valve (71) and described the second cross valve (72), include capillary s, the capillary s of described the first cross valve (71) is connected with the suction line between described the first magnetic valve (81) and described compressor (10); The capillary s of described the second cross valve (72) is connected with the suction line between described the second magnetic valve (82) and described compressor (10).
2. heat recovery system according to claim 1, is characterized in that:
Capillary d on the pilot slide valve of described the second cross valve (72) is connected with the D pipe of described the first cross valve (71).
3. heat recovery system according to claim 1 and 2, is characterized in that:
Also comprise gas-liquid separator (60), the outlet of described gas-liquid separator (60) is connected with the suction end of described compressor (10), and the import of described gas-liquid separator (60) is all connected with the other end of described the first magnetic valve (81) and the other end of described the second magnetic valve (82).
4. heat recovery system according to claim 3, is characterized in that:
The capillary s of the capillary s of described the first cross valve (71) and described the second cross valve (72) is all connected with the import of described gas-liquid separator.
5. heat recovery system according to claim 1 and 2, is characterized in that:
Also comprise reservoir (50), the second end of the second end of described air-condition heat exchanger (40) and described hot water heat exchanger (30) and the first end of described finned heat exchanger (20) are all connected with described reservoir (50).
6. heat recovery system according to claim 5, is characterized in that:
The first check valve (91) and the first electric expansion valve (101) between described reservoir (50) and described air-condition heat exchanger (40), have been arranged in parallel.
7. heat recovery system according to claim 5, is characterized in that:
The 3rd check valve (93) and the second electric expansion valve (102) between described reservoir (50) and described finned heat exchanger (20), have been arranged in parallel.
8. heat recovery system according to claim 5, is characterized in that:
Between described reservoir (50) and described hot water heat exchanger (30), be arranged in parallel the second check valve (92) and defrost capillary (110), on the branch road of described defrost capillary (110) place, be also provided with magnetic valve (83).
9. heat recovery system according to claim 5, is characterized in that:
Between described reservoir (50) and described hot water heat exchanger (30), the second check valve (92) and defrost electric expansion valve have been arranged in parallel.
10. a recuperation of heat unit, is characterized in that, comprises the heat recovery system as described in claim 1 to 9 any one.
11. recuperation of heat units according to claim 10, is characterized in that:
The capillary s of described the first cross valve (71) is fixed in the suction line between described the first magnetic valve (81) and described compressor (10) by fixture, and/or the capillary s of described the second cross valve (72) is fixed in the suction line between described the second magnetic valve (82) and described compressor (10) by fixture.
12. recuperation of heat units according to claim 11, is characterized in that: described fixture is geometrical clamp.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320624433.5U CN203518332U (en) | 2013-10-10 | 2013-10-10 | Heat recovery system and heat recovery unit with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320624433.5U CN203518332U (en) | 2013-10-10 | 2013-10-10 | Heat recovery system and heat recovery unit with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203518332U true CN203518332U (en) | 2014-04-02 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320624433.5U Withdrawn - After Issue CN203518332U (en) | 2013-10-10 | 2013-10-10 | Heat recovery system and heat recovery unit with same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203518332U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104567094A (en) * | 2013-10-10 | 2015-04-29 | 珠海格力电器股份有限公司 | Heat recovery system and heat recovery unit provided with same |
| CN107940796A (en) * | 2017-12-11 | 2018-04-20 | 广东美的暖通设备有限公司 | The startup control method of multi-line system and its outdoor unit |
| CN110094546A (en) * | 2018-01-27 | 2019-08-06 | 浙江盾安机械有限公司 | Four-way valve and air-conditioning system |
-
2013
- 2013-10-10 CN CN201320624433.5U patent/CN203518332U/en not_active Withdrawn - After Issue
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104567094A (en) * | 2013-10-10 | 2015-04-29 | 珠海格力电器股份有限公司 | Heat recovery system and heat recovery unit provided with same |
| CN104567094B (en) * | 2013-10-10 | 2017-12-08 | 珠海格力电器股份有限公司 | Heat recovery system and there is its recuperation of heat unit |
| CN107940796A (en) * | 2017-12-11 | 2018-04-20 | 广东美的暖通设备有限公司 | The startup control method of multi-line system and its outdoor unit |
| CN110094546A (en) * | 2018-01-27 | 2019-08-06 | 浙江盾安机械有限公司 | Four-way valve and air-conditioning system |
| CN110094546B (en) * | 2018-01-27 | 2022-06-07 | 浙江盾安机械有限公司 | Four-way valve and air conditioning system |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20140402 Effective date of abandoning: 20171208 |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20140402 Effective date of abandoning: 20171208 |