CN203744601U - Double-mode combined heat pump set - Google Patents
Double-mode combined heat pump set Download PDFInfo
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- CN203744601U CN203744601U CN201420120750.8U CN201420120750U CN203744601U CN 203744601 U CN203744601 U CN 203744601U CN 201420120750 U CN201420120750 U CN 201420120750U CN 203744601 U CN203744601 U CN 203744601U
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- heat exchanger
- communicated
- port
- cross valve
- throttling arrangement
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- 239000003507 refrigerant Substances 0.000 claims abstract description 84
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 65
- 238000001816 cooling Methods 0.000 claims abstract description 28
- 238000010438 heat treatment Methods 0.000 claims abstract description 17
- 239000007788 liquid Substances 0.000 claims description 58
- 150000001875 compounds Chemical class 0.000 claims description 23
- 239000002826 coolant Substances 0.000 claims description 18
- 239000007921 spray Substances 0.000 claims description 16
- 239000000110 cooling liquid Substances 0.000 abstract description 4
- 238000007599 discharging Methods 0.000 description 17
- 239000012809 cooling fluid Substances 0.000 description 12
- 230000000694 effects Effects 0.000 description 9
- 238000002309 gasification Methods 0.000 description 8
- 238000000034 method Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000001077 hypotensive effect Effects 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 238000010521 absorption reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000005507 spraying Methods 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000002689 soil Substances 0.000 description 1
- 231100000331 toxic Toxicity 0.000 description 1
- 230000002588 toxic effect Effects 0.000 description 1
Abstract
The utility model discloses a double-mode combined heat pump set. An exhaust opening of a compressor is communicated with a D port of a four-way valve. A C port of the four-way valve is communicated with one end of an outdoor heat exchanger, the other end of the outdoor heat exchanger is communicated with one end of a throttling device, the other end of the throttling device is communicated with one end of an indoor heat exchanger, the other end of the indoor heat exchanger is communicated with an E port of the four-way valve, an S port of the four-way valve is communicated with an air suction port of the compressor, the indoor heat exchanger comprises a refrigerant loop and an air-conditioner water loop, the outdoor heat exchanger at least comprises a first heat exchanger and a second heat exchanger, the first heat exchanger is communicated with the second heat exchanger, and a cooling liquid system is arranged outside the second heat exchanger, wherein the cooling liquid system is used in cooperation with the second heat exchanger for heat exchanging and is selectively started and stopped. The double-mode combined heat pump set has the advantages that cooling and heating are conducted through the same heat exchangers, the number of four-way valves, the number of throttling devices, the number of one-way valves and the number of branch pipes are reduced, the system structure is simplified, cost is reduced, and switching is simple.
Description
Technical field
The utility model relates to a kind of air-conditioning technical field, relates in particular to a kind of double mode compound source pump.
Background technology
Heat pump is that one can be from natural air, in water or soil, obtain low-grade heat, through electric power effect, the equipment of the high-grade heat energy of output energy use, because heat pump has the saving energy, reduce the feature of toxic emission, heat pump techniques is subject to the support of energy policy and Environment Protection Policy more and more, heat pump uses also more and more wider in industry and life, but due to the heat exchanger feature of transpiration-cooled source pump, refrigeration heat exchanger of outside when heating requires different, system need to arrange multiple different heat exchangers conventionally, and by the multiple cross valves of configuration, multiple throttling arrangements and multiple check valve complete the switching of cooling condition and heating condition, make system architecture complexity, cost is high, and handoff procedure is loaded down with trivial details.Based on above-mentioned present situation, we be necessary to provide a kind of simple in structure, cost is low, switch double mode compound source pump efficiently.
Utility model content
An object of the present utility model is: the source pump of a kind of refrigeration with heating condition common heat exchanger is provided, realizes simplied system structure, the object reducing costs.
For reaching this object, the utility model by the following technical solutions:
A kind of double mode compound source pump, comprise compressor, cross valve, outdoor heat exchanger, throttling arrangement and indoor heat exchanger, the exhaust outlet of described compressor is communicated with the D port of described cross valve, the C port of described cross valve is communicated with one end of described outdoor heat exchanger, the other end of described outdoor heat exchanger is communicated with one end of described throttling arrangement, the other end of described throttling arrangement is communicated with one end of described indoor heat exchanger, the other end of described indoor heat exchanger is communicated with the E port of described cross valve, the S port of described cross valve is communicated with the air entry of described compressor, described indoor heat exchanger comprises refrigerant loop and air conditioner water loop, described outdoor heat exchanger at least comprises the First Heat Exchanger and the second heat exchanger that are interconnected, described First Heat Exchanger comprises many branch roads side by side, described the second heat exchanger comprises the branch road side by side identical with described First Heat Exchanger quantity, the branch road of described First Heat Exchanger is connected one by one with the branch road of described the second heat exchanger, the outer setting of described the second heat exchanger has and the heat exchange of described the second heat exchanger coolant system of selective start and stop using that matches.
Under cooling condition, the D port of described cross valve is communicated with C port, described coolant system startup work, the gaseous refrigerant of the HTHP that described compressor is discharged enter described First Heat Exchanger form to air heat release liquefaction in the liquid refrigerant of warm high pressure, then in, the liquid refrigerant of warm high pressure enters described the second heat exchanger to utilize cooling fluid to carry out cooling, become the liquid refrigerant of cryogenic high pressure, the liquid refrigerant of described cryogenic high pressure becomes the liquid refrigerant of low-temp low-pressure by the hypotensive effect of throttling arrangement, the liquid refrigerant of last described low-temp low-pressure enters described indoor heat exchanger from air conditioner water endothermic gasification and returns to compressor, make air conditioner water reach cooling effect.
Under heating condition, the D port of described cross valve is communicated with E port, described coolant system quits work, the high temperature and high pressure gaseous refrigerant that described compressor is discharged enter described indoor heat exchanger form to air conditioner water heat release liquefaction in the liquid refrigerant of warm high pressure, make air conditioner water reach the effect of intensification, then the liquid refrigerant of described middle temperature high pressure becomes the liquid refrigerant of low-temp low-pressure by the hypotensive effect of throttling arrangement, and the liquid refrigerant of last described low-temp low-pressure enters described the second heat exchanger and First Heat Exchanger from air endothermic gasification and returns to compressor.
As the preferred technical scheme of one, described coolant system comprises the spray equipment that is arranged on described the second heat exchanger top, and with the condense water disk of described the second heat exchanger bottom of being arranged on of being used in combination of described spray equipment, described condense water disk below is provided with the water tank being connected with described condense water disk, described waterbox design is enough large, can make cooling fluid fully cooling, between described spray equipment and described water tank, water pump is installed.
Particularly, under cooling condition, described coolant system starts, the driving of described spray equipment by described water pump is to described the second heat exchanger spraying cooling liquid, make the cold-producing medium cooling through described the second heat exchanger, described cooling fluid is naturally dropped in condense water disk after described the second heat exchanger, the cooling fluid of collecting by described condense water disk flows into the described water tank that is arranged on described condense water disk below automatically, and cooling fluid is again sent to described spray equipment by the driving of described water pump after collecting by described water tank and realizes spray.
As the preferred technical scheme of one, the homonymy of described First Heat Exchanger and described the second heat exchanger is provided with at least one fan assembly, particularly, and under refrigeration or cooling condition, described fan assembly is all opened, and strengthens the heat exchange effect of described First Heat Exchanger and described the second heat exchanger.
Especially, the homonymy of described First Heat Exchanger and described the second heat exchanger is provided with a fan assembly.
As the preferred technical scheme of one, described First Heat Exchanger is provided with gas collection assembly away from a side of described the second heat exchanger, particularly, under cooling condition, cold-producing medium branches to from being communicated with the single line of described cross valve C port each branch road of described First Heat Exchanger by described gas collection assembly; Under heating condition, cold-producing medium collaborates to being communicated with the single line of described cross valve C port from each branch road of described First Heat Exchanger by described gas collection assembly.
As the preferred technical scheme of one, described the second heat exchanger is provided with capillary module away from a side of described First Heat Exchanger, particularly, under cooling condition, the cold-producing medium of discharging from described the second heat exchanger collaborates to being communicated with the single line of described throttling arrangement by described capillary module; Under heating condition, branch to each branch road of described the second heat exchanger by described capillary module from the cold-producing medium of the single line process that is communicated with described throttling arrangement.In addition, described capillary module has strengthened the effect of step-down.
As the preferred technical scheme of one, between described indoor heat exchanger and described throttling arrangement, be provided with reservoir, on the pipeline that described reservoir is communicated with described throttling arrangement, be provided with and make described cold-producing medium can pass through successively the first check valve of described indoor heat exchanger, described reservoir and described throttling arrangement; On the pipeline that described throttling arrangement and described indoor heat exchanger are communicated with, be provided with a branch road, one end of described branch road is arranged between described throttling arrangement and described the first check valve, the other end of described branch road is arranged between described reservoir and described indoor heat exchanger, is provided with the second check valve that makes described cold-producing medium can pass through successively described throttling arrangement and described indoor heat exchanger on described branch road.Particularly, described the first check valve is contrary with the conducting direction of described the second check valve, under cooling condition, cold-producing medium from the branch road at described the second check valve place by realizing conducting; Under heating condition, cold-producing medium from the branch road described in described the first check valve and described reservoir by realizing conducting.
As the preferred technical scheme of one, between the S port of the air entry of described compressor and described cross valve, be provided with gas-liquid separator, prevent that liquid refrigerant from entering described compressor.
As the preferred technical scheme of one, described First Heat Exchanger adopts fin type air heat exchanger.
A control method for described double mode compound source pump, double mode compound source pump realizes air conditioner water cooling condition or air conditioner water heating condition described in described control method control, and described air conditioner water cooling condition comprises the following steps:
S10, described compressor become refrigerant compression the gas of HTHP, and discharge from the exhaust outlet of described compressor, described cross valve obtains electric, the D port of described cross valve is communicated with C port, E port is communicated with S port, and the gaseous refrigerant of the HTHP of discharging from exhaust outlet enters described cross valve and discharges described cross valve from C port from D port;
The gaseous refrigerant of S20, the HTHP of discharging from described cross valve C port enters described First Heat Exchanger, the gaseous refrigerant of HTHP is to air heat release during by described First Heat Exchanger, and the gaseous refrigerant temperature of HTHP reduces and the liquid refrigerant of warm high pressure in forming;
The liquid refrigerant of S30, middle temperature high pressure enters described the second heat exchanger from described First Heat Exchanger, described coolant system startup work, the liquid refrigerant of middle temperature high pressure is to cooling fluid heat release during by described the second heat exchanger, and the liquid refrigerant temperature of middle temperature high pressure reduces and forms the liquid refrigerant of cryogenic high pressure;
S40, the liquid refrigerant of cryogenic high pressure of discharging from described the second heat exchanger become the liquid refrigerant of low-temp low-pressure by described throttling arrangement step-down;
The liquid refrigerant of S50, low-temp low-pressure after described throttling arrangement step-down enters described indoor heat exchanger, and by described indoor heat exchanger from the heat absorption of described air conditioner water loop, make air conditioner water cooling, simultaneously the liquid refrigerant endothermic gasification of low-temp low-pressure;
S60, the gaseous refrigerant of discharging from described indoor heat exchanger enter described cross valve and discharge described cross valve from the S port of described cross valve from the E port of described cross valve, finally enter described compressor from the air entry of described compressor;
Described air conditioner water heating condition comprises the following steps:
S100, described compressor become refrigerant compression the gas of HTHP, and discharge from the exhaust outlet of described compressor, described cross valve obtains electric, the D port of described cross valve is communicated with E port, C port is communicated with S port, and the gaseous refrigerant of the HTHP of discharging from exhaust outlet enters described cross valve and discharges described cross valve from E port from D port;
The gaseous refrigerant of S200, the HTHP of discharging from described cross valve E port enters described indoor heat exchanger, and by described indoor heat exchanger to the loop heat release of described air conditioner water, air conditioner water is heated up, the simultaneously gaseous refrigerant heat release of HTHP and the liquid refrigerant of warm high pressure in forming;
S300, discharge from described indoor heat exchange the liquid refrigerant of warm high pressure become the liquid refrigerant of low-temp low-pressure after by described throttling arrangement step-down;
The liquid refrigerant of S400, low-temp low-pressure after described throttling arrangement step-down enters described the second heat exchanger, described coolant system quits work, and the liquid refrigerant of low-temp low-pressure is successively by described the second heat exchanger and described First Heat Exchanger and from air endothermic gasification;
S500, the gaseous refrigerant of discharging from described First Heat Exchanger enter described cross valve and leave described cross valve from the S port of described cross valve from the C port of described cross valve, finally enter described compressor from the air entry of described compressor.
As the preferred technical scheme of one, between described S200 and described S300, there is step S210: discharging from described indoor heat exchanger, the liquid refrigerant of warm high pressure enters described reservoir and discharges described reservoir from the other end of described reservoir from one end of described reservoir, then after described the first check valve, just enters described throttling arrangement.
The beneficial effects of the utility model are:
By a kind of double mode compound source pump is provided, realize the object of refrigeration and heating condition common heat exchanger, reduce the quantity of cross valve, throttling arrangement, check valve and pipeline branch road, thereby reach simplied system structure, reduce costs and switch simple effect.
Brief description of the drawings
According to drawings and embodiments the utility model is described in further detail below.
Fig. 1 is the system diagram of the double mode compound source pump described in embodiment;
Fig. 2 is the refrigerating circuit figure of the double mode compound source pump described in embodiment;
Fig. 3 is the loop diagram that heats of double mode compound source pump described in embodiment;
Fig. 4 is the cooling condition control block diagram of the double mode compound source pump described in embodiment;
Fig. 5 is the heating condition control block diagram of the double mode compound source pump described in embodiment.
In Fig. 1:
1, compressor; 2, cross valve; 3, outdoor heat exchanger; 31, First Heat Exchanger; 32, the second heat exchanger; 4, coolant system; 41, spray equipment; 42, condense water disk; 43, water tank; 44, water pump; 5, throttling arrangement; 6, indoor heat exchanger; 7, gas collection assembly; 8, fan assembly; 9, capillary module; 10, reservoir; 11, the first check valve; 12, the second check valve; 13, gas-liquid separator.
Detailed description of the invention
Further illustrate the technical solution of the utility model below in conjunction with accompanying drawing and by detailed description of the invention.
As shown in Fig. 1～5, in the present embodiment, a kind of double mode compound source pump, comprise compressor 1, cross valve 2, outdoor heat exchanger 3, throttling arrangement 5 and indoor heat exchanger 6, the exhaust outlet of compressor 1 is communicated with the D port of cross valve 2, the C port of cross valve 2 is communicated with one end of outdoor heat exchanger 3, the other end of outdoor heat exchanger 3 is communicated with one end of throttling arrangement 5, the other end of throttling arrangement 5 is communicated with one end of indoor heat exchanger 6, the other end of indoor heat exchanger 6 is communicated with the E port of cross valve 2, the S port of cross valve 2 is communicated with the air entry of compressor 1.
Indoor heat exchanger 6 comprises refrigerant loop and air conditioner water loop.Outdoor heat exchanger 3 comprises the First Heat Exchanger 31 and the second heat exchanger 32 that are interconnected, First Heat Exchanger 31 comprises many branch roads side by side, the second heat exchanger 32 comprises the branch road side by side identical with First Heat Exchanger 31 quantity, the branch road of First Heat Exchanger 31 is connected one by one with the branch road of the second heat exchanger 32, and First Heat Exchanger 31 adopts fin type air heat exchanger.
The homonymy of First Heat Exchanger 31 and the second heat exchanger 32 is provided with a fan assembly 8, and under cooling condition or cooling condition, fan assembly 8 is all opened, and strengthens the heat exchange effect of First Heat Exchanger 31 and the second heat exchanger 32.First Heat Exchanger 31 is provided with gas collection assembly 7 away from a side of the second heat exchanger 32.The second heat exchanger 32 is provided with capillary module 9 away from a side of First Heat Exchanger 31.
The outer setting of the second heat exchanger 32 has and the heat exchange of the second heat exchanger 32 coolant system 4 of selective start and stop using that matches.Coolant system 4 comprises the spray equipment 41 that is arranged on the second heat exchanger 32 tops, and the condense water disk 42 that is arranged on the second heat exchanger 32 bottoms being used in combination with spray equipment 41, condense water disk 42 belows are provided with the water tank 43 being connected with condense water disk 42, water tank 43 can make cooling fluid fully cooling, between spray equipment 41 and water tank 43, water pump 44 is installed.Spray equipment 41 can be by the driving of water pump 44 to the second heat exchanger 32 spraying cooling liquid, make the cold-producing medium cooling through the second heat exchanger 32, cooling fluid is naturally dropped in 42 li of condense water disks after the second heat exchanger 32, the cooling fluid of collecting by condense water disk 42 flows into the water tank 43 that is arranged on condense water disk 42 belows automatically, and cooling fluid is again sent to spray equipment 41 realizations by the driving of water pump 44 after collecting by water tank 43 and repeats spray.
Between indoor heat exchanger 6 and throttling arrangement 5, be provided with reservoir 10, on the pipeline that reservoir 10 is communicated with throttling arrangement 5, be provided with the first check valve 11 that makes cold-producing medium can pass through successively indoor heat exchanger 6, reservoir 10 and throttling arrangement 5; On the pipeline that throttling arrangement 5 and indoor heat exchanger 6 are communicated with, be provided with a branch road, one end of branch road is arranged between throttling arrangement 5 and the first check valve 11, the other end of branch road is arranged between reservoir 10 and indoor heat exchanger 6, on branch road, be provided with the second check valve 12, the second check valves 12 that make cold-producing medium can pass through successively throttling arrangement 5 and indoor heat exchanger 6 contrary with the conducting direction of the first check valve 11.
Between the S port of the air entry of compressor 1 and cross valve 2, be provided with gas-liquid separator 13, prevent that liquid refrigerant from entering compressor 1.
Under cooling condition, the D port of cross valve 2 is communicated with C port, coolant system 4 startup work, refrigerating circuit as shown in Figure 2, cooling condition control step as shown in Figure 4, the gaseous refrigerant of the HTHP that compressor 1 is discharged branches to by gas collection assembly 7 on each branch road of First Heat Exchanger 31, the liquid refrigerant of warm high pressure in forming to air heat release liquefaction by First Heat Exchanger 31, then in, the liquid refrigerant of warm high pressure enters the second heat exchanger 32 and utilizes cooling fluid to carry out cooling, become the liquid refrigerant of cryogenic high pressure, the liquid refrigerant of cryogenic high pressure collaborates to throttling arrangement 5 from each branch road of the second heat exchanger 32 by capillary module 9, and become the liquid refrigerant of low-temp low-pressure by the hypotensive effect of throttling arrangement 5, the liquid refrigerant of low-temp low-pressure is after the second check valve 12, enter indoor heat exchanger 6 and from air conditioner water endothermic gasification, make air conditioner water reach cooling effect, last gaseous refrigerant returns to compressor 1 by gas-liquid separator 13.
Under heating condition, the D port of cross valve 2 is communicated with E port, coolant system 4 quits work, heat loop as shown in Figure 3, heating condition control step as shown in Figure 5, the high temperature and high pressure gaseous refrigerant that compressor 1 is discharged enter indoor heat exchanger 6 form to air conditioner water heat release liquefaction in the liquid refrigerant of warm high pressure, make air conditioner water reach the effect of intensification, then in, the liquid refrigerant of warm high pressure enters throttling arrangement 5 through reservoir 10 and the first check valve 11, and become the liquid refrigerant of low-temp low-pressure by the hypotensive effect of throttling arrangement 5, the liquid refrigerant of low-temp low-pressure branches to after each branch road of the second heat exchanger 32 and each branch road of First Heat Exchanger 31 from air endothermic gasification by capillary module 9, last gaseous refrigerant enters gas-liquid separator 13 after collaborating by gas collection assembly 7, and return to compressor 1.
A control method for the double mode compound source pump of the present embodiment, the double mode compound source pump of this control method control realizes air conditioner water cooling condition or air conditioner water heating condition, and air conditioner water cooling condition comprises the following steps:
S10, compressor 1 become refrigerant compression the gas of HTHP, and discharge from the exhaust outlet of compressor 1, cross valve 2 obtains electric, the D port of cross valve 2 is communicated with C port, E port is communicated with S port, and the gaseous refrigerant of the HTHP of discharging from exhaust outlet enters cross valve 2 and discharges cross valve 2 from C port from D port;
S20, the gaseous refrigerant of HTHP of discharging from cross valve 2C port enter First Heat Exchanger 31, the gaseous refrigerant of HTHP is to air heat release when the First Heat Exchanger 31, and the gaseous refrigerant temperature of HTHP reduces and the liquid refrigerant of warm high pressure in forming;
The liquid refrigerant of S30, middle temperature high pressure enters the second heat exchanger 32 from First Heat Exchanger 31, coolant system 4 startup work, when the liquid refrigerant of middle temperature high pressure passes through the second heat exchanger 32, to cooling fluid heat release, the liquid refrigerant temperature of middle temperature high pressure reduces and the liquid refrigerant of formation cryogenic high pressure;
The liquid refrigerant of S40, the cryogenic high pressure of discharging from the second heat exchanger 32 becomes the liquid refrigerant of low-temp low-pressure by throttling arrangement 5 step-downs;
The liquid refrigerant of S50, low-temp low-pressure after throttling arrangement 5 step-downs enters indoor heat exchanger 6, and by indoor heat exchanger 6 from the heat absorption of air conditioner water loop, make air conditioner water cooling, simultaneously the liquid refrigerant endothermic gasification of low-temp low-pressure;
S60, the gaseous refrigerant of discharging from indoor heat exchanger 6 enter cross valve 2 and leave cross valve 2 from the S port of cross valve 2 from the E port of cross valve 2, finally enter compressor 1 from the air entry of compressor 1;
Air conditioner water heating condition comprises the following steps:
S100, compressor 1 become refrigerant compression the gas of HTHP, and discharge from the exhaust outlet of compressor 1, cross valve 2 obtains electric, the D port of cross valve 2 is communicated with E port, C port is communicated with S port, and the gaseous refrigerant of the HTHP of discharging from exhaust outlet enters cross valve 2 and discharges cross valve 2 from E port from D port;
S200, the gaseous refrigerant of HTHP of discharging from cross valve 2E port enter indoor heat exchanger 6, and pass through indoor heat exchanger 6 to the heat release of air conditioner water loop, air conditioner water is heated up, the simultaneously gaseous refrigerant heat release of HTHP and the liquid refrigerant of warm high pressure in forming;
S210: discharging from indoor heat exchanger 6, the liquid refrigerant of warm high pressure enters reservoir 10 and discharges reservoir 10 from the other end of reservoir 10 from one end of reservoir 10, then enters throttling arrangement 5 after the first check valve 11.
The liquid refrigerant of S300, middle temperature high pressure after the first check valve 11 becomes the liquid refrigerant of low-temp low-pressure after by throttling arrangement 5 step-downs;
The liquid refrigerant of S400, low-temp low-pressure after throttling arrangement 5 step-downs enters the second heat exchanger 32, and coolant system 4 quits work, and the liquid refrigerant of low-temp low-pressure is successively by the second heat exchanger 32 and First Heat Exchanger 31 and from air endothermic gasification;
S500, the gaseous refrigerant of discharging from First Heat Exchanger 31 enter cross valve 2 and leave cross valve 2 from the S port of cross valve 2 from the C port of cross valve 2, finally enter compressor 1 from the air entry of compressor 1.
" first " herein, " second " are only used to be distinguished on describing, and do not have special implication.
What need statement is; above-mentioned detailed description of the invention is only preferred embodiment of the present utility model and institute's application technology principle; in technical scope disclosed in the utility model; the variation that any those skilled in the art of being familiar with easily expect or replacement, all should be encompassed in protection domain of the present utility model.
Claims (8)
1. a double mode compound source pump, it is characterized in that, comprise compressor, cross valve, outdoor heat exchanger, throttling arrangement and indoor heat exchanger, the exhaust outlet of described compressor is communicated with the D port of described cross valve, the C port of described cross valve is communicated with one end of described outdoor heat exchanger, the other end of described outdoor heat exchanger is communicated with one end of described throttling arrangement, the other end of described throttling arrangement is communicated with one end of described indoor heat exchanger, the other end of described indoor heat exchanger is communicated with the E port of described cross valve, the S port of described cross valve is communicated with the air entry of described compressor, described indoor heat exchanger comprises refrigerant loop and air conditioner water loop, described outdoor heat exchanger at least comprises the First Heat Exchanger and the second heat exchanger that are interconnected, the outer setting of described the second heat exchanger has and the heat exchange of described the second heat exchanger coolant system of selective start and stop using that matches, under cooling condition, the D port of described cross valve is communicated with C port, described coolant system startup work, under heating condition, the D port of described cross valve is communicated with E port, described coolant system quits work.
2. double mode compound source pump according to claim 1, it is characterized in that, described coolant system comprises the spray equipment that is arranged on described the second heat exchanger top, and with the condense water disk of described the second heat exchanger bottom of being arranged on of being used in combination of described spray equipment, described condense water disk below is provided with the water tank being connected with described condense water disk, between described spray equipment and described water tank, water pump is installed.
3. double mode compound source pump according to claim 2, is characterized in that, the homonymy of described First Heat Exchanger and described the second heat exchanger is provided with at least one fan assembly.
4. double mode compound source pump according to claim 3, is characterized in that, described First Heat Exchanger is provided with gas collection assembly away from a side of described the second heat exchanger.
5. double mode compound source pump according to claim 4, is characterized in that, described the second heat exchanger is provided with capillary module away from a side of described First Heat Exchanger.
6. double mode compound source pump according to claim 5, it is characterized in that, between described indoor heat exchanger and described throttling arrangement, be provided with reservoir, on the pipeline that described reservoir is communicated with described throttling arrangement, be provided with and make described cold-producing medium can pass through successively the first check valve of described indoor heat exchanger, described reservoir and described throttling arrangement; On the pipeline that described throttling arrangement and described indoor heat exchanger are communicated with, be provided with a branch road, one end of described branch road is arranged between described throttling arrangement and described the first check valve, the other end of described branch road is arranged between described reservoir and described indoor heat exchanger, is provided with the second check valve that makes described cold-producing medium can pass through successively described throttling arrangement and described indoor heat exchanger on described branch road.
7. double mode compound source pump according to claim 6, is characterized in that, between the S port of described compressor air suction mouth and described cross valve, is provided with gas-liquid separator.
8. double mode compound source pump according to claim 7, is characterized in that, described First Heat Exchanger adopts fin type air heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420120750.8U CN203744601U (en) | 2014-03-17 | 2014-03-17 | Double-mode combined heat pump set |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420120750.8U CN203744601U (en) | 2014-03-17 | 2014-03-17 | Double-mode combined heat pump set |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203744601U true CN203744601U (en) | 2014-07-30 |
Family
ID=51344391
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420120750.8U Expired - Lifetime CN203744601U (en) | 2014-03-17 | 2014-03-17 | Double-mode combined heat pump set |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203744601U (en) |
-
2014
- 2014-03-17 CN CN201420120750.8U patent/CN203744601U/en not_active Expired - Lifetime
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| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
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| CX01 | Expiry of patent term |
Granted publication date: 20140730 |