CN201069286Y - Integral water source heat pump device - Google Patents
Integral water source heat pump device Download PDFInfo
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- CN201069286Y CN201069286Y CNU2007201554768U CN200720155476U CN201069286Y CN 201069286 Y CN201069286 Y CN 201069286Y CN U2007201554768 U CNU2007201554768 U CN U2007201554768U CN 200720155476 U CN200720155476 U CN 200720155476U CN 201069286 Y CN201069286 Y CN 201069286Y
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 100
- 239000007788 liquid Substances 0.000 claims abstract description 6
- 239000012530 fluid Substances 0.000 claims description 36
- 238000001816 cooling Methods 0.000 claims description 15
- 238000001035 drying Methods 0.000 claims description 6
- 238000001914 filtration Methods 0.000 claims description 6
- 238000005057 refrigeration Methods 0.000 abstract description 21
- 238000001704 evaporation Methods 0.000 description 18
- 230000002528 anti-freeze Effects 0.000 description 15
- 238000000034 method Methods 0.000 description 10
- 238000004378 air conditioning Methods 0.000 description 7
- 238000006243 chemical reaction Methods 0.000 description 7
- GNFTZDOKVXKIBK-UHFFFAOYSA-N 3-(2-methoxyethoxy)benzohydrazide Chemical compound COCCOC1=CC=CC(C(=O)NN)=C1 GNFTZDOKVXKIBK-UHFFFAOYSA-N 0.000 description 6
- 238000010438 heat treatment Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 239000003507 refrigerant Substances 0.000 description 4
- FGUUSXIOTUKUDN-IBGZPJMESA-N C1(=CC=CC=C1)N1C2=C(NC([C@H](C1)NC=1OC(=NN=1)C1=CC=CC=C1)=O)C=CC=C2 Chemical compound C1(=CC=CC=C1)N1C2=C(NC([C@H](C1)NC=1OC(=NN=1)C1=CC=CC=C1)=O)C=CC=C2 FGUUSXIOTUKUDN-IBGZPJMESA-N 0.000 description 3
- YTAHJIFKAKIKAV-XNMGPUDCSA-N [(1R)-3-morpholin-4-yl-1-phenylpropyl] N-[(3S)-2-oxo-5-phenyl-1,3-dihydro-1,4-benzodiazepin-3-yl]carbamate Chemical compound O=C1[C@H](N=C(C2=C(N1)C=CC=C2)C1=CC=CC=C1)NC(O[C@H](CCN1CCOCC1)C1=CC=CC=C1)=O YTAHJIFKAKIKAV-XNMGPUDCSA-N 0.000 description 3
- 238000007710 freezing Methods 0.000 description 3
- 230000008014 freezing Effects 0.000 description 3
- 238000004321 preservation Methods 0.000 description 3
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- UXVMQQNJUSDDNG-UHFFFAOYSA-L Calcium chloride Chemical compound [Cl-].[Cl-].[Ca+2] UXVMQQNJUSDDNG-UHFFFAOYSA-L 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000009172 bursting Effects 0.000 description 1
- 229910001628 calcium chloride Inorganic materials 0.000 description 1
- 239000001110 calcium chloride Substances 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 239000003054 catalyst Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000010977 unit operation Methods 0.000 description 1
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Abstract
The utility model discloses an integral water source heat pump device. The integrated water source heat pump device comprises a refrigeration cycle system, wherein the refrigeration cycle system comprises a refrigeration cycle system (10), the refrigeration cycle system (10) comprises a compressor (11), a condenser (12), a liquid storage tank (13), a throttling element (15) and an evaporator (17) which are sequentially connected, and the integrated water source heat pump device further comprises a waterway system with a plurality of groups of waterway switching systems (20), wherein each waterway switching system (20) is connected to the condenser (12) and the evaporator (17). Therefore, the throttling element can be reduced by adopting the water path switching system, so that the operation reliability of the refrigeration system is improved.
Description
Technical field
The utility model relates to a kind of integral headwaters heat pump.
Background technology
The air-conditioning equipment desire realizes that changes in temperature switch, and mainly contain dual mode at present.
A kind of mode is to adopt four-way change-over valve on the refrigeration system, realizes the conversion of freezing, heating by four-way change-over valve switching refrigerant flow direction.But, the evaporimeter of this heat pump and the heat exchange area of condenser are suitable substantially, and refrigeration mode down and heating mode throttle structure down differ bigger, therefore need corresponding two cover restricting elements, the four-way change-over valve leakage and the reliability that commutates also often cause the system failure.So this heat pump type air conditioning system complex structure, the manufacturing cost height, the refrigeration pipe tie point is many, leak easily, but system automation degree height does not generally need the special messenger to safeguard, is common in air source heat pump.
Another mode is to realize the conversion of freezing, heating by switching refrigerating medium and catalyst carrier flowing on evaporimeter, condenser, is common in the big-and-middle-sized refrigeration plant such as water resource heat pump.By the combination of the valve switch on the switched system of water route, realize chilled water and the switching of cooling water on evaporimeter, condenser, and refrigerant flow direction is constant.This refrigerant system configurations is simple, but complexity is installed, and generally needs the special messenger to safeguard.
In addition, for the refrigeration unit that makes water and cold-producing medium heat exchange in the evaporimeter, often because the too small grade of discharge causes that evaporating temperature is crossed low or evaporimeter stops up, thereby cause the heat exchanger inner icing, when serious even the bursting by freezing heat exchanger, cause cold-producing medium to leak, the refrigeration system water inlet, destroy refrigeration part, influence economic benefit, damage brand image.
The utility model content
First technical problem to be solved in the utility model is: a kind of integral headwaters heat pump that improves antifreezing effect that has is provided.
Second technical problem to be solved in the utility model is: a kind of restricting element that reduces is provided, reduces the integral headwaters heat pump of refrigeration system leakage point, raising refrigeration system operational reliability.
According to first aspect of the present utility model, comprise cooling cycle system, cooling cycle system comprises compressor, condenser, fluid reservoir, restricting element and the evaporimeter that connects successively, wherein, also comprise the water circuit system with many groups water route switched system, each water route switched system is connected to condenser and evaporimeter.
In above-mentioned integral headwaters heat pump, optimal way is, the water route switched system is two groups, wherein one group of water route switched system comprises first valve, second valve, the 7th valve and the 8th valve, another group water route switched system comprises the 3rd valve, the 4th valve, the 5th valve and the 6th valve, first valve and the 8th valve are connected in turn between water route second end of water route first end of condenser and evaporimeter, second valve and the 7th valve are connected in turn between water route second end of water route first end of condenser and evaporimeter, and be arranged in juxtaposition with first valve and the 8th valve, the 3rd valve and the 6th valve are connected in turn between water route first end of water route second end of condenser and evaporimeter, the 4th valve and the 5th valve are connected in turn between water route first end of water route second end of condenser and evaporimeter, and be arranged in juxtaposition with the 3rd valve and the 6th valve, be provided with first fluid first interface between first valve and the 8th valve, be provided with second fluid, first interface between second valve and the 7th valve, be provided with first fluid second interface between the 3rd valve and the 6th valve, be provided with second fluid, second interface between the 4th valve and the 5th valve.
In addition, in above-mentioned integral headwaters heat pump, water route first end of condenser is corresponding to the cold-producing medium input of condenser, water route second end of condenser is corresponding to the cold-producing medium output of condenser, water route first end of evaporimeter is corresponding to the cold-producing medium input of evaporimeter, and water route second end of evaporimeter is corresponding to the cold-producing medium output of evaporimeter.
Optimal way is that in above-mentioned integral headwaters heat pump, first valve, second valve, the 3rd valve, the 4th valve, the 5th valve, the 6th valve, the 7th valve and the 8th valve are two position two-way valve.Wherein, four bi-bit bi-pass valves are connected to each other in the valve sets of composition, and one of them bi-bit bi-pass valve that any bi-bit bi-pass valve can be adjacent is integrally formed as a two-position three way valve.
In addition, in above-mentioned integral headwaters heat pump, first fluid is outdoor water, and second fluid is for making water; Also can be first fluid for making water, second fluid is outdoor water.
In integral headwaters heat pump of the present utility model, owing to adopt the monoblock type combining structure, the conversion valve of traditional air-conditioning water route switched system is integrated in the unit, by controlling the unlatching combination of different valves, can realize the conversion of the various operational modes of unit, thereby can omit four-way change-over valve, reduce restricting element, and reduced the refrigeration system leakage point, improved the refrigeration system operational reliability.And, by central air-conditioning water route switched system being incorporated among the refrigeration unit, also shortened the project installation cycle, improved the automatic controlling level of whole unit.
In addition, integral headwaters heat pump according to second aspect of the present utility model, be in above-mentioned arbitrary integral headwaters heat pump, also to comprise also comprising defroster, defroster has bypath valve, bypath valve is connected between the cold-producing medium input of the cold-producing medium output of condenser and evaporimeter, and is arranged in juxtaposition with restricting element.
In above-mentioned integral headwaters heat pump, the input of bypath valve is connected to the input of restricting element, and the output of bypath valve is connected to the output of restricting element.
In addition, in above-mentioned integral headwaters heat pump, also comprise device for drying and filtering, be arranged on after the fluid reservoir, before the junction of the input of restricting element and the input of bypath valve.
Optimal way is, above-mentioned integral headwaters heat pump also comprises gas-liquid separator, is arranged between the input of the cold-producing medium output of evaporimeter and compressor.
In above-mentioned integral headwaters heat pump, owing to be provided with bypath valve, thus prevented the evaporating temperature of evaporimeter inside because former thereby too reductions such as inner obstruction or discharge deficiency have strengthened antifreezing effect.
Description of drawings
Fig. 1 is the structural principle schematic diagram according to integral headwaters heat pump of the present utility model.
Fig. 2 is the flow chart according to the antifreeze control method of the integral headwaters heat pump of the utility model one embodiment.
The specific embodiment
Below in conjunction with accompanying drawing and embodiment integral headwaters heat pump of the present utility model and antifreeze control method thereof are described in detail.
Fig. 1 is the structural principle schematic diagram according to integral headwaters heat pump of the present utility model, as shown in the figure, integral headwaters heat pump comprises cooling cycle system 10, has water circuit system and the defrosters of organizing water route switched systems 20 (being two groups in the present embodiment) more.Cooling cycle system 10 comprises compressor 11, condenser 12, high pressure fluid reservoir 13, device for drying and filtering 14, restricting element 15, evaporimeter 17 and gas-liquid separator 18.Then the connected mode to cooling cycle system 10 is illustrated, compressor 11 1 ends in the cooling cycle system 10 are connected with condenser 12, condenser 12 is connected with device for drying and filtering 14 by high pressure fluid reservoir 13, utilize restricting element 15 in parallel and bypath valve 30 that device for drying and filtering 14 and evaporimeter 17 are linked together, and, an other end of compressor 11 is connected with evaporimeter 17 by gas-liquid separator 18, so constitutes cooling cycle system 10.In this integral headwaters heat pump, the bypath valve 30 and the tube connector that are connected in parallel on the restricting element 15 of cooling cycle system 10 constitute defroster of the present utility model.
As shown in Figure 1, each water route switched system 20 all is connected on condenser 12 and the described evaporimeter 17.Wherein one group of water route switched system 20 comprises the first valve V1, the second valve V2, the 7th valve V7 and the 8th valve V8, and another group water route switched system 20 comprises the 3rd valve V3, the 4th valve V4, the 5th valve V5 and the 6th valve V6.And, the first valve V1 and the 8th valve V8 are connected in turn between water route second end of water route first end of condenser 12 and evaporimeter 17, the second valve V2 and the 7th valve V7 are connected in turn between water route second end of water route first end of condenser 12 and evaporimeter 17, and be arranged in juxtaposition with the first valve V1 and the 8th valve V8, the 3rd valve V3 and the 6th valve V6 are connected in turn between water route first end of water route second end of condenser 12 and evaporimeter 17, the 4th valve V4 and the 5th valve V5 are connected in turn between water route first end of water route second end of condenser 12 and evaporimeter 17, and are arranged in juxtaposition with the 3rd valve V3 and the 6th valve V6.In addition, between the first valve V1 and the 8th valve V8, be provided with first fluid first interface 28, between the second valve V2 and the 7th valve V7, be provided with second fluid, first interface 22, between the 3rd valve V3 and the 6th valve V6, be provided with first fluid second interface 24, between the 4th valve V4 and the 5th valve V5, be provided with second fluid, second interface 26.
In integral headwaters heat pump of the present utility model, water route first end of condenser 12 is corresponding to the cold-producing medium input of condenser 12, water route second end of condenser 12 is corresponding to the cold-producing medium output of condenser 12, water route first end of evaporimeter 17 is corresponding to the cold-producing medium input of evaporimeter 17, and water route second end of evaporimeter 17 is corresponding to the cold-producing medium output of evaporimeter 17.
In Fig. 1, the first valve V1, the second valve V2, the 3rd valve V3, the 4th valve V4, the 5th valve V5, the 6th valve V6, the 7th valve V7 and the 8th valve V8 are two position two-way valve.But four bi-bit bi-pass valves are connected to each other in the valve sets of composition, and one of them the bi-bit bi-pass valve that also can take any bi-bit bi-pass valve to be adjacent is integrally formed as a two-position three way valve.
In addition, consider the heat exchange mode of water route switched system 20 and cooling cycle system 10 following currents, adverse current, each is organized water route switched system 20 and is not limited to above-mentioned connected mode with being connected of evaporimeter 17, condenser 12, as long as water route switched system 20 and meeting the following conditions evaporimeter 17, being connected of condenser 12: one in connector of water route switched system 20 and evaporimeter 17 or the condenser 12 is connected, and then the diagonal angle connector of this connector must be connected with the another one in evaporimeter 17 or the condenser 12.The remaining interface of valve sets with outdoor water system, make the connection principle of water system identical with this principle.Promptly can connect the combination that situation is opened or closed valve V1～V8 after two principles satisfy, realize the conversion of multi-mode operation according to reality.
Integral headwaters heat pump of the present utility model has refrigeration, heats and directly cools off three kinds of operational modes, below in conjunction with Fig. 1 and table 1 running status to each pattern of table 4 explanation.For convenience of description, below the outdoor water of definition is first fluid in the explanation, and making water is second fluid.Also can define outdoor water in the practical application is second fluid, and making water is first fluid, but corresponding flow process also needs to change accordingly.
1, refrigerating operaton pattern: the on off state of valve V1～V8, outdoor water (being first fluid) and the flow process that makes water (i.e. second fluid) are referring to table 1.
Table 1
2, heating operation pattern: the on off state of valve V1～V8, outdoor water (being first fluid) and the flow process that makes water (i.e. second fluid) are referring to table 2.
Table 2
3, direct cooling mode of operation: when outdoor water with water can be used with, and the temperature of outdoor water is enough low when being equivalent to chilled water, can directly feed the indoor fan coil and freeze, and the compressor 11 of cooling cycle system 10 does not need to move.The on off state of valve V1～V8 and outdoor water (first fluid) flow process are referring to table 3 or table 4.
Table 3
Table 4
In addition, the water that integral headwaters heat pump of the present utility model uses is not limited to the light water known to the public, comprises that also refrigerating and air conditioning industry is known such as glycol water, calcium chloride water etc.; In addition, for the outdoor water in the listed form of various operational modes or the flow direction that makes water with → " expression, but also can change " ← " into by " → ".
Adopt the monoblock type combining structure, the conversion valve of at present traditional air-conditioning water route switched system is integrated in the unit, valve switch by control water route switched system, three kinds of operational modes that can realize unit are promptly freezed, are heated and the directly conversion of cooling, thereby omitted four-way change-over valve, reduce restricting element, reduced the refrigeration system leakage point simultaneously, improved the refrigeration system operational reliability.In addition,, also shortened the project installation cycle, can improve the automatic controlling level of whole unit by central air-conditioning water route switching mechanism being incorporated among the refrigeration unit.
Then, describe the antifreeze control method of integral headwaters heat pump of the present utility model in detail, specifically be meant the antifreeze control method of the evaporimeter 17 of integral headwaters heat pump.
With reference to shown in Figure 2 this method is described.
At first, in step a), the evaporating temperature T in the evaporimeter 17 is detected;
Then, in step b), with a detected evaporating temperature T and a default antifreeze setting value T
LCompare, if detected evaporating temperature T is higher than antifreeze setting value T
L, then return described step a), if detected evaporating temperature T is not higher than antifreeze setting value T
L, then enter next step c);
In step c), start bypath valve 30, start the unit warning system simultaneously, the evaporating temperature T of prompting evaporimeter 17 inside is low excessively, writes down time of fire alarming simultaneously;
Then enter step d), detect the discharge V of evaporimeter 17;
Then in step e) with a detected discharge V and a default protection flow V
LCompare, if detected discharge V is higher than described protection flow V
L, enter step f); If detected discharge V is not higher than described protection flow V
L, enter step f1);
In step f), judge whether this time warning is that this compressor start is reported to the police the later first time, and report to the police the later first time if this warning is this compressor start, enters step g); If this is reported to the police is not that this compressor start is reported to the police the later first time, enter step j);
In step g), the evaporating temperature T of evaporimeter 17 is detected;
And then at step h) in a detected evaporating temperature T and the default antifreeze setting value of a releasing T
HCompare, remove antifreeze setting value T if detected evaporating temperature T is lower than
H, then return step g), if detected evaporating temperature T is not less than antifreeze setting value T
H, then enter next step i);
Step I) in, closes bypath valve 30, close warning system, and return step a).
In addition, if judge this warning in step f) is not that this compressor start is reported to the police the later first time, enter step j), then at step j) in utilize the Time Calculation that writes down in the step c) this report to the police with last warning between time interval t, enter next step k then);
At step k) in, with a time interval t and a default time interval t who calculates
0Compare, if the time interval t that calculates is higher than described Preset Time t at interval
0, then enter step g); If the time interval t that calculates is not higher than described Preset Time t at interval
0, then enter step m);
Step m) in, orderly close-down bypath valve 30, compressor 11 and water circuit system 20 keep reporting to the police.
In the step e) noted earlier, if detected discharge V is not higher than described protection flow V
L, enter step f1), described step f1) be: detect the evaporating temperature T in the evaporimeter 17, enter step g 1 then);
Step g 1): with a detected evaporating temperature T and the default antifreeze setting value of a releasing T
HCompare, remove antifreeze setting value T if detected evaporating temperature T is lower than
H, then return step f1), if detected evaporating temperature T is not less than antifreeze setting value T
H, then enter next step h1);
At step h1) in, close bypath valve 30, close compressor 11 then, and pick up counting, and enter step I 1);
Step I 1) be through a preset time t
1The discharge V of evaporimeter 17 is detected in the back, enters step j1 then);
At step j1) in, with a detected discharge V and a default de-preservation flow V
HCompare, if detected discharge V is lower than described de-preservation flow V
H, enter step k1); If detected discharge V is not less than described protection flow V
H, then enter step m1);
At step k1) in, close water circuit system 20, and keep reporting to the police;
At step j1) in detected discharge V be not less than described protection flow V
HAnd enter described step m1) time, open compressor 11 again, and close warning system, return step a) then.
In addition, in steps in related T
LAnd T
H, V
LAnd V
H, t
0And t
1Can preset according to actual conditions.
In sum; antifreeze control method according to integral headwaters heat pump of the present utility model; control the refrigerant amount of inflow evaporator 17 by control bypath valve 30; can avoid evaporating device 17 inside evaporating temperature since inner stop up or discharge not enough and too reduce, thereby can and antifreezely take effective safeguard measure to unit operation.
Be preferred embodiment of the present utility model only below, be not limited to the utility model.In the above-described embodiments, the utility model can have various changes and variation.All within spirit of the present utility model and principle, any modification of being done, be equal to replacement, improvement etc., all should be included within the protection domain of the present utility model.
Symbol description
10 cooling cycle systems, 20 water route switched systems
11 compressors, 12 condensers
13 high pressure fluid reservoirs, 14 devices for drying and filtering
15 restricting elements, 30 bypath valves
17 evaporimeters, 18 gas-liquid separators
22 second fluid interfaces, one 24 first fluid interfaces two
26 second fluid interfaces, 2 28 first fluid interfaces one
V1～V8 position two-port valve door T evaporating temperature
T
LAntifreeze setting value T
HRemove antifreeze setting value
The discharge V of V evaporimeter
LThe protection flow
V
HThe de-preservation flow t time interval
t
0Preset Time is t at interval
1The default time
Claims (9)
1. integral headwaters heat pump, comprise cooling cycle system (10), described cooling cycle system (10) comprises compressor (11), condenser (12), fluid reservoir (13), restricting element (15) and the evaporimeter (17) that connects successively, it is characterized in that
Also comprise the water circuit system with many group water route switched systems (20), described each water route switched system (20) is connected to described condenser (12) and described evaporimeter (17).
2. integral headwaters heat pump according to claim 1, it is characterized in that, described water route switched system (20) is two groups, wherein one group of described water route switched system (20) comprises first valve (V1), second valve (V2), the 7th valve (V7) and the 8th valve (V8), another is organized described water route switched system (20) and comprises the 3rd valve (V3), the 4th valve (V4), the 5th valve (V5) and the 6th valve (V6)
Described first valve (V1) and described the 8th valve (V8) are connected in turn between water route second end of water route first end of described condenser (12) and described evaporimeter (17),
Described second valve (V2) and described the 7th valve (V7) are connected in turn between water route second end of water route first end of described condenser (12) and described evaporimeter (17), and are arranged in juxtaposition with described first valve (V1) and described the 8th valve (V8),
Described the 3rd valve (V3) and described the 6th valve (V6) are connected in turn between water route first end of water route second end of described condenser (12) and described evaporimeter (17),
Described the 4th valve (V4) and described the 5th valve (V5) are connected in turn between water route first end of water route second end of described condenser (12) and described evaporimeter (17), and are arranged in juxtaposition with described the 3rd valve (V3) and described the 6th valve (V6),
Be provided with first fluid first interface (28) between described first valve (V1) and described the 8th valve (V8),
Be provided with second fluid, first interface (22) between described second valve (V2) and described the 7th valve (V7),
Be provided with first fluid second interface (24) between described the 3rd valve (V3) and described the 6th valve (V6),
Be provided with second fluid, second interface (26) between described the 4th valve (V4) and described the 5th valve (V5).
3. integral headwaters heat pump according to claim 2 is characterized in that:
Water route first end of described condenser (12) is corresponding to the cold-producing medium input of described condenser (12),
Water route second end of described condenser (12) is corresponding to the cold-producing medium output of described condenser (12),
Water route first end of described evaporimeter (17) is corresponding to the cold-producing medium input of described evaporimeter (17),
Water route second end of described evaporimeter (17) is corresponding to the cold-producing medium output of described evaporimeter (17).
4. integral headwaters heat pump according to claim 3, it is characterized in that described first valve (V1), second valve (V2), the 3rd valve (V3), the 4th valve (V4), the 5th valve (V5), the 6th valve (V6), the 7th valve (V7) and the 8th valve (V8) are two position two-way valve.
5. integral headwaters heat pump according to claim 4 is characterized in that:
Four described bi-bit bi-pass valves are connected to each other in the valve sets of composition, and one of them described bi-bit bi-pass valve that any described bi-bit bi-pass valve can be adjacent is integrally formed as a two-position three way valve.
6. according to each described integral headwaters heat pump in the claim 1 to 5, it is characterized in that: also comprise defroster, described defroster has bypath valve (30), described bypath valve (30) is connected between the cold-producing medium input of the cold-producing medium output of described condenser (12) and described evaporimeter (17), and is arranged in juxtaposition with described restricting element (15).
7. integral headwaters heat pump according to claim 6, it is characterized in that, the input of described bypath valve (30) is connected to the input of described restricting element (15), and the output of described bypath valve (30) is connected to the output of described restricting element (15).
8. integral headwaters heat pump according to claim 7, it is characterized in that, also comprise device for drying and filtering (14), be arranged on described fluid reservoir (13) afterwards, before the junction of the input of the input of described restricting element (15) and described bypath valve (30).
9. integral headwaters heat pump according to claim 8 is characterized in that, also comprises gas-liquid separator (18), is arranged between the input of the cold-producing medium output of described evaporimeter (17) and described compressor (11).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201554768U CN201069286Y (en) | 2007-08-17 | 2007-08-17 | Integral water source heat pump device |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201554768U CN201069286Y (en) | 2007-08-17 | 2007-08-17 | Integral water source heat pump device |
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| CN201069286Y true CN201069286Y (en) | 2008-06-04 |
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| CNU2007201554768U Expired - Lifetime CN201069286Y (en) | 2007-08-17 | 2007-08-17 | Integral water source heat pump device |
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Cited By (5)
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| CN105066542A (en) * | 2015-08-17 | 2015-11-18 | 泉港区奇妙工业设计服务中心 | Device for moving ice with photo-thermal method |
| CN105899884A (en) * | 2014-03-20 | 2016-08-24 | 三菱电机株式会社 | Heat source side unit and air conditioner |
| CN106500419A (en) * | 2016-11-21 | 2017-03-15 | 珠海格力电器股份有限公司 | Waterway control system of heat pump unit and control method thereof |
| CN108955004A (en) * | 2018-03-30 | 2018-12-07 | 河南三张节能环保工程有限公司 | A kind of heat pump unit control system Internet-based |
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2007
- 2007-08-17 CN CNU2007201554768U patent/CN201069286Y/en not_active Expired - Lifetime
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|---|---|---|---|---|
| CN105899884A (en) * | 2014-03-20 | 2016-08-24 | 三菱电机株式会社 | Heat source side unit and air conditioner |
| CN105899884B (en) * | 2014-03-20 | 2018-12-14 | 三菱电机株式会社 | Heat source side unit and air-conditioning device |
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| CN105066542A (en) * | 2015-08-17 | 2015-11-18 | 泉港区奇妙工业设计服务中心 | Device for moving ice with photo-thermal method |
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