CN202432754U - Single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy - Google Patents
Single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy Download PDFInfo
- Publication number
- CN202432754U CN202432754U CN2012200028126U CN201220002812U CN202432754U CN 202432754 U CN202432754 U CN 202432754U CN 2012200028126 U CN2012200028126 U CN 2012200028126U CN 201220002812 U CN201220002812 U CN 201220002812U CN 202432754 U CN202432754 U CN 202432754U
- Authority
- CN
- China
- Prior art keywords
- stage
- heat pump
- pump
- refrigerant fluid
- way change
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The utility model discloses a single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy. The single-stage and multistage complemented multi-split heat-pump air conditioner using wind energy is characterized by consisting of a primary ultralow temperature pump and a secondary ultralow temperature pump. Independent operation of the primary ultralow temperature pump or simultaneous operation of the primary ultralow temperature pump and the secondary ultralow temperature pump are achieved through a primary coupling heat exchanger, a secondary coupling heat exchanger and a single-stage and two-stage complementary switching device. The single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy can operate in single-stage refrigeration at the summer temperature larger than 35 DEG C, operate in single-stage heating at the winter temperature larger than -5 DEG C, operate in two-stage efficient refrigeration at the high summer temperature larger than 35 DEG C, and operate in two-stage heating at the low winter temperature smaller than -5 DGG C. The single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy is simple, energy-saving, environment-friendly, and reliable and safe in operation.
Description
Technical field
The utility model relates to and adapts to all efficient multimachine split-type air conditioners of operation of ultra-low temperature surroundings and the extremely hot environment of high temperature, relates to the windy ability of the complementary holder of a kind of single twin-stage heat pump air conditioner specifically.
Background technology
Wind energy splitting heat pump air conditioner, particularly VRV multimachine split frequency conversion type wind energy heat pump air-conditioning, to have an installation simple because of it, and maintenance is few, Load Regulation rate advantages of higher, the application in family expenses and small commercial air-conditioning system is more and more widely.But there is a common shortcoming in this type air-conditioning; Its heating operation efficient declining to a great extent when temperature is lower than below 5 ℃ along with temperature with being lowered into direct ratio; Cause can't be the in the winter time normal heating of this type air-conditioning, the outstanding Japan of this type of world production air-conditioning does not solve this difficult problem yet.In order to overcome this problem, heating wire has been installed by domestic part manufacturer in heat pump air conditioner, with the resistance heating system compensation deficiency that winter, heat pump air conditioner heated.Well-known electrothermal efficiency is minimum, adopts heating wire to heat the requirement that does not meet the life of energy-saving and emission-reduction low-carbon (LC), has also lost the energy-saving significance of using heat pump air-conditioning.
The utility model content
The purpose of the utility model is to the problems referred to above, provides a kind of and adapts to that single twin-stage complementary of highly effective refrigeration and heating operation holds in the palm windy ability heat pump air conditioner under 55 ℃ to-35 ℃ extremely wide temperature of outside air temperature.
The purpose of the utility model is to realize through following technical scheme:
The windy ability of the complementary holder of a kind of single twin-stage heat pump air conditioner; Be made up of prime super low temperature heat pump and back level superhigh temperature heat pump two-stage heat pump, described two-stage heat pump realizes that by the grade coupled heat exchanger in front and back and single twin-stage complementary transitions device prime super low temperature heat pump single-stage independent operating or prime super low temperature heat pump move with back level superhigh temperature heat pump twin-stage simultaneously.
Further; Described single twin-stage complementary transitions device constitutes single-stage and twin-stage complementary transitions device by compressor check-valves 8 and refrigerant fluid pump check-valves 12, four-way change-over valve 9, liquid storage gas-liquid separator 10 and refrigerant fluid pump 11; One end of described single its compressor check-valves 8 of twin-stage complementary transitions device is connected with the exhaust end of the refrigeration compressor 7 of back level superhigh temperature heat pump; After the other end of compressor check-valves 8 is connecting an end of refrigerant fluid pump check-valves 12; Be connected with the j end of four-way change-over valve 9 again; The other end of refrigerant fluid pump check-valves 12 is connecting the drain side of refrigerant fluid pump 11; The liquid feeding end of refrigerant fluid pump 11 is connected with the feed flow port o of liquid storage gas-liquid separator 10, and the gas port m of liquid storage gas-liquid separator 10 is connected with the l of four-way change-over valve 9 end, and another gas port n of liquid storage gas-liquid separator 10 is connected with the suction end of refrigeration compressor 7.
Further, described prime super low temperature heat pump is made up of the grade coupled heat exchanger of refrigeration compressor 1, four-way change-over valve 2, front and back 3, expansion valve 4, off-premises station air heat exchanger 5, gas-liquid separator 6; Back level superhigh temperature heat pump is made up of refrigeration compressor 7, compressor check-valves 8, four-way change-over valve 9, liquid storage gas-liquid separator 10, refrigerant fluid pump 11, refrigerant fluid pump check-valves 12, indoor set air heat exchanger 13,14,15 and expansion valve 16,17,18; The port e of the grade coupled heat exchanger 3 in said front and back is connected with the port b of four-way change-over valve 2; Another port f connects the port d of expansion valve 4, off-premises station air heat exchanger 5 and four-way change-over valve 2 successively; The port c of said four-way change-over valve 2 is connected with gas-liquid separator 6; Said gas-liquid separator 6 is connected with the inlet end of refrigeration compressor 1; The outlet side of said refrigeration compressor 1 is connected with the port a of four-way change-over valve 2; The port h of the grade coupled heat exchanger 3 in front and back is connected with the port i of four-way change-over valve 9; The port k of said four-way change-over valve 9 connects indoor set air heat exchanger 13,14,15 successively, expansion valve 16,17,18 backs are connected with port g; The port l of four-way change-over valve 9 is connected with the port m of liquid storage gas-liquid separator 10, and the port n of said liquid storage gas-liquid separator 10 connects refrigeration compressor 7 successively, compressor check-valves 8 backs are connected with the port j of four-way change-over valve 9, and the port o of liquid storage gas-liquid separator 10 connects the port j of refrigerant fluid pump 11, refrigerant fluid pump check-valves 12 and four-way change-over valve 9 successively.
Further, described prime super low temperature heat pump is made up of the grade coupled heat exchanger of refrigeration compressor 1, four-way change-over valve 2, front and back 3, expansion valve 4, off-premises station air heat exchanger 5, gas-liquid separator 6; Back level superhigh temperature heat pump is made up of refrigeration compressor 7, compressor check-valves 8, four-way change-over valve 9, gas-liquid separator 19, refrigerant fluid pump 11, refrigerant fluid pump check-valves 12, indoor set air heat exchanger 13,14,15 and expansion valve 16,17,18; The port e of the grade coupled heat exchanger 3 in said front and back is connected with the port b of four-way change-over valve 2; Another port f connects the port d of expansion valve 4, off-premises station air heat exchanger 5 and four-way change-over valve 2 successively; The port c of said four-way change-over valve 2 is connected with gas-liquid separator 6; Said gas-liquid separator 6 is connected with the inlet end of refrigeration compressor 1; The outlet side of said refrigeration compressor 1 is connected with the port a of four-way change-over valve 2; The port h of the grade coupled heat exchanger 3 in front and back is connected with the port i of four-way change-over valve 9; The port k of said four-way change-over valve 9 connects indoor set air heat exchanger 13,14,15 successively, expansion valve 16,17,18 backs are connected with port g, and the port l of four-way change-over valve 9 is connected with the liquid feeding end of refrigerant fluid pump 11, and port l also is connected with the port of gas-liquid separator 19; The port of said gas-liquid separator 19 connects refrigerant fluid pump 11 successively, refrigerant fluid pump check-valves 12 backs are connected with the port j of four-way change-over valve 9, and the another port of gas-liquid separator 19 connects refrigeration compressor 7 successively, compressor check-valves 8 backs are connected with the port j of four-way change-over valve 9.
Further, described prime super low temperature heat pump is made up of the grade coupled heat exchanger of refrigeration compressor 1, four-way change-over valve 2, front and back 3, expansion valve 4, off-premises station air heat exchanger 5, gas-liquid separator 6; Back level superhigh temperature heat pump is made up of refrigeration compressor 7, compressor check-valves 8, four-way change-over valve 9, liquid storage gas-liquid separator 10, refrigerant fluid pump 11, indoor set air heat exchanger 13,14,15, expansion valve 16,17,18 and valve 20,21,22,23; The port e of the grade coupled heat exchanger 3 in said front and back is connected with the port b of four-way change-over valve 2; Another port f connects the port d of expansion valve 4, off-premises station air heat exchanger 5 and four-way change-over valve 2 successively; The port c of said four-way change-over valve 2 is connected with gas-liquid separator 6; Said gas-liquid separator 6 is connected with the inlet end of refrigeration compressor 1; The outlet side of said refrigeration compressor 1 is connected with the port a of four-way change-over valve 2; The port h of the grade coupled heat exchanger 3 in front and back is connected with the port m of liquid storage gas-liquid separator 10; The port n of liquid storage gas-liquid separator 10 is connected with the port i of four-way change-over valve 9; The port l of four-way change-over valve 9 connects refrigeration compressor 7 successively, compressor check-valves 8 backs are connected with the port j of four-way change-over valve 9, and the port k of said four-way change-over valve 9 is connected with indoor set air heat exchanger 13,14,15, and said indoor set air heat exchanger 13,14,15 connects valve 20 backs and is connected with the outlet end of refrigerant fluid pump 11; The liquid feeding end of said refrigerant fluid pump 11 is connected with the port o of liquid storage gas-liquid separator 10; Its outlet end also connects valve 21 successively, expansion valve 16,17,18 backs are connected with indoor set air heat exchanger 13,14,15, and said indoor set air heat exchanger 13,14,15 connects valve 22 backs and is connected with the port g of the grade coupled heat exchanger 3 in front and back, and said port g connects valve 23 backs and is connected with expansion valve 16,17,18.
Preferably, described refrigeration compressor 1,7 adopts VFC.
Preferably, described expansion valve the 4,16,17, the 18th, electronic expansion valve, described valve the 20,21,22, the 23rd, electromagnetic valve.
The beneficial effect of the utility model does, the single-stage more than the single-stage refrigerating operaton that complementary ultralow temperature one holder of said single, double level is windy when can air-conditioning system having realized that summer temperature is less than 35 ℃ and winter-5 ℃ during temperature heats heating operation, and summer temperature moves greater than the twin-stage highly effective refrigeration under the extremely hot environment more than 35 ℃ and winter temperature less than the twin-stage heating operation under-5 ℃ of cold environments; System is succinct; Energy-conserving and environment-protective, reliable safety, and refrigerant fluid pump has been disposed in the operation of the utility model single-stage;, single-stage force cold-producing medium in indoor set, to circulate when moving by refrigerant fluid pump; The internal circulating load of its internal circulating load after the expansion valve throttling is 4～6 times of choke valve circulation, and boiling coefficient is very high; And lubricating oil is difficult for accumulating among the indoor set; Not only strengthened the heat exchange effect, and refrigerant fluid pump can be transported to farther place with cold-producing medium, can prolong the indoor set piping length and increase indoor set quantity; The indoor set installation site is not influenced by the height of building and finishing, and any position is installed can; In addition, in order to adapt to the demand of back level high temperature heat pump needs gas-liquid separator, adopt the integrative-structure of liquid storage, gas-liquid separator; To satisfy the reliable and stable operation of back level high temperature heat pump; Its reservoir partly guarantees to the stable supply of refrigerant fluid pump liquid refrigeration, prevents that refrigerant fluid pump from inhaling emptyly, guaranteed that the liquid pump safety and stability moves reliably; Its gas-liquid separator part; What guarantee the refrigeration compressor suction is refrigerant gas fully, prevents the generation of liquid hammer accident, has guaranteed the refrigeration compressor safe operation; In addition, refrigeration compressor is the VFC compressor, has further improved energy-saving effect, and expansion valve is electric expansion valve, has realized automatic control.
Description of drawings
According to accompanying drawing and embodiment the utility model is done further explain below.
Fig. 1 is the first example structure sketch map of the windy ability of the complementary holder of a kind of single twin-stage of the utility model heat pump air conditioner;
Fig. 2 is the second example structure sketch map of the windy ability of the complementary holder of a kind of single twin-stage of the utility model heat pump air conditioner;
Fig. 3 is the 3rd an example structure sketch map of the windy ability of the complementary holder of a kind of single twin-stage of the utility model heat pump air conditioner.
Among the figure:
1,7, refrigeration compressor; 2,9, four-way change-over valve; 3, the grade coupled heat exchanger in front and back; 4,16,17,18, expansion valve; 5, off-premises station air heat exchanger; 6,19, gas-liquid separator; 8, compressor check-valves; 10, liquid storage gas-liquid separator; 11, refrigerant fluid pump; 12, refrigerant fluid pump check-valves; 13,14,15, indoor set air heat exchanger; 20,21,22,23, valve.
The specific embodiment
Fig. 1 has provided an embodiment of the utility model, forms prime super low temperature heat pump loop by the grade coupled heat exchanger of refrigeration compressor 1, four-way change-over valve 2, front and back 3, expansion valve 4, off-premises station air heat exchanger 5, gas-liquid separator 6; Form back level superhigh temperature heat pump circuit by refrigeration compressor 7, compressor check-valves 8, four-way change-over valve 9, liquid storage gas-liquid separator 10, refrigerant fluid pump 11, refrigerant fluid pump check-valves 12, indoor set air heat exchanger 13,14,15 and expansion valve 16,17,18.
When summer, if temperature was lower than 30 ℃; Move by prime super low temperature heat pump independent cooling; Its course of work is: refrigeration compressor 1 exhaust is held to d through a of four-way change-over valve 2 and is held; Through off-premises station air heat exchanger 5 condensation heat is disposed in the air, the f of grade coupled heat exchanger 3 holds to the evaporation heat absorbing end of e end condensed liquid to front and back after expansion valve 4 throttlings, and evaporation absorbs the heat by g to h release end of heat; Evaporation back gas is held the end to c through four-way change-over valve b, is sucked the continuation compression through gas-liquid separator 6 by refrigeration compressor 1 again and repeats above-mentioned refrigerating operaton; Simultaneously, refrigerant fluid pump 11 operations, refrigerant liquid is through refrigerant fluid pump 11 to refrigerant fluid pump check-valves 12; Hold end through the j of four-way change-over valve 9 again, discharge the heat in the cold-producing medium, after e to f evaporation heat absorption through the h to g of the grade coupled heat exchanger 3 in front and back to i; Cross cold refrigerant liquid by g to expansion valve 16,17,18 after throttling in the inlet chamber machine air heat exchanger 13,14,15 evaporation absorb the heat of room airs; Its overheated refrigerant liquid is held the end to l via the k of four-way change-over valve 9, and the m through liquid storage gas-liquid separator 10 gets into liquid storage gas-liquid separator 10 again, and its refrigerant liquid exports refrigerant fluid pump 11 to by the o end and continues circulation; Repeat above-mentioned liquid pump and force the operation of cold-producing medium circularly cooling; Realize the energy-conservation refrigeration air-conditioner operation of unit in summer, single-stage operation temperature is provided with a little, also can be other temperature value.
When summer temperature is higher than 30 ℃; Prime continues operation; Back level superhigh temperature heat pump starts operation; Refrigeration compressor 7 exhausts are through h to the g condensation heat release of the j to i of compressor check-valves 8 to four-way change-over valve 9 grade coupled heat exchanger 3 through front and back, and condensed refrigerant liquid absorbs the room air heats to indoor refrigeration air-conditioner to 13,14,15 evaporations of indoor set air heat exchanger through g to expansion valve 16,17,18 after throttling.Gas after the evaporation heat absorption gets into through the m of liquid storage gas-liquid separator 10 through the k to l of four-way change-over valve 9, holds the suction end that exports refrigeration compressor 7 to by n, repeats above-mentioned kind of refrigeration cycle after compression, accomplishes the high efficiency energy saving refrigeration operation of air conditioner of twin-stage sweltering hot weather.The twin-stage operation is set temperature and is not limited to 30 ℃, and can freely set selection according to energy-conservation situation by the user.
Four-way change-over valve switching-over during winter; When more than temperature >=0 ℃; By prime hot pump in low temp single-stage energy-saving run; Refrigeration compressor 1 exhaust discharges condensation heat through e to the f condensation heat release of a to b of four-way change-over valve 2 grade coupled heat exchanger 3 through front and back to h to g heat absorbing end; Condensed liquid heat, gas to off-premises station air heat exchanger 5 evaporation absorption chamber outer air after expansion valve 4 throttlings is sucked continuation compression through gas-liquid separator 6 by refrigeration compressor 1 through the d to c of four-way change-over valve 2, repeats above-mentioned single-stage heating operation; Simultaneously; After refrigerant fluid pump 11 runnings; Refrigerant liquid through the j to k of refrigerant fluid pump check-valves 12 to four-way change-over valve 9 through the heat of indoor set air heat exchanger 13,14,15 in indoor release refrigerant liquid, to indoor heating heating, through the cold-producing medium after the heat release after expansion valve 16,17,18 throttlings to front and back g to the h heat absorbing end of grade coupled heat exchanger 3; Absorb the condensation heat that e to f discharges; Its overheated refrigerant liquid gets into liquid storage gas-liquid separator 10 by the i to l of h through four-way change-over valve 9 by m, and overheated cold-producing medium is held to refrigerant fluid pump 11 by o again; Continuation forces the above-mentioned heat release circulation of cold-producing medium by refrigerant fluid pump 11, accomplishes single-stage winter saving energy heating operation.
When winter temperature is lower than below 0 ℃; Except the prime super low temperature heat pump continues heating operation; Back level superhigh temperature heat pump starts operation; Refrigeration compressor 7 exhausts are through the j to k of compressor check-valves 8 to four-way change-over valve 9, through indoor set air heat exchanger 13,, 14,15 to indoor blowing hot-air heating, the liquid after the condensation heat release after expansion valve 16,17,18 throttlings to front and back g to the h heat absorbing end of grade coupled heat exchanger 3; Evaporation absorbs the condenser heat of e to f release end of heat; Gas gets into liquid storage gas-liquid separator 10 through the i to l of four-way change-over valve 9 through m by h, and overheated refrigerant gas repeats the efficient heating operation of above-mentioned twin-stage after compression again by the suction end of n to refrigeration compressor 7.Winter, the critical point of twin-stage operation not necessarily was selected in 0 ℃, and when 5 ℃ of temperature, the heating efficiency of single-stage heat pump just begins to have descended, and should automatically adjust control automatically according to temperature and relationship between efficiency by manual work setting or automatic control circuit in fact.
Fig. 2 has provided another embodiment of the utility model; It is compared with embodiment one; Difference is that the suction end of the refrigeration compressor 7 of back level superhigh temperature heat pump connects an end of gas-liquid separator 19, the other end of gas-liquid separator 19 be connected with the liquid feeding end of refrigerant fluid pump 11 again after the l of four-way change-over valve 9 is connected.After refrigerant fluid pump 11 runnings, refrigerant liquid is the suction end that is got into refrigerant fluid pump 11 by the l end of four-way change-over valve 9 when single-stage is moved, and other running and embodiment one are just the same, no longer repeat; When twin-stage moves, refrigeration compressor 7 air-breathing be l by four-way change-over valve 9 to gas-liquid separator 19, get into refrigeration compressor 7 compression operations through gas-liquid separator 19 refrigerant gas, no longer narrate and other running and embodiment one are just the same.
Fig. 3 has provided another embodiment of the utility model; The refrigeration of it compares with embodiment one that different is refrigerant fluid pump 11 with heat switching-over and the conversion of single twin-stage by valve 20,21,22,23 independent completion; Its running is: when summer temperature is lower than 30 ℃; By refrigerant fluid pump 11 cold-producing medium is forced through 16,17,18 throttlings of valve 21 to expansion valve after 13,14,15 evaporations of indoor set air heat exchanger absorb the heat of room air; G to the h release end of heat of liquid grade coupled heat exchanger 3 through valve 22 to front and back is by the heat absorbing end of e to f heat absorption cooling; After crossing cold cold-producing medium and getting into liquid storage gas-liquid separator 10, hold to the liquid feeding end of refrigerant fluid pump 11 through o again, repeat above-mentioned forced circulation again through refrigerant fluid pump 11 by h to m; After temperature raises above 30 ℃; Back level superhigh temperature operation of heat pump; The exhaust of refrigeration compressor 7 through the j to i of compressor check-valves 8 to four-way change-over valve 9 through the n to m of liquid storage gas-liquid separator 10 through release end of heat h to g condensation heat release; After the condensation liquid by g after 16,17,18 throttlings of valve 23 to expansion valve; To indoor set air heat exchanger 13,14,15 evaporation absorption room air heats, gas is sucked the continued compression through the k to l of four-way change-over valve 9 by refrigeration compressor 7 and repeats above-mentioned two-stage refrigeration operation.
Winter is when more than temperature＞0 ℃; The operation of prime super low temperature heat pump single-stage; Refrigerant fluid pump 11 force cold-producing medium by valve 20 to indoor set air heat exchanger 13,14,15 to the room air release heat, the cold-producing medium after the heat release absorbs the condensation heat that e to f discharges through valve 23 by g to h heat absorbing end after expansion valve 16,17,18 throttlings; After overheated liquid gets into liquid storage gas-liquid separator 10 by h to m; Hold to the liquid feeding end of refrigerant fluid pump 11 by o, continue to force cold-producing medium circulation, release heat heating operation by refrigerant fluid pump 11; When temperature is low to moderate below 0 ℃; Back level superhigh temperature operation of heat pump; The exhaust of refrigeration compressor 7 gets into indoor set air heat exchanger 13,14,15 through the j to k of compressor check-valves 8 to four-way change-over valve 9; To indoor release condensation heat heating, condensed cold-producing medium is sucked continued compression through i to l by refrigeration compressor 7 through m to n by g to h through valve 23 and constitutes the efficient heating operation of twin-stage after expansion valve 16,17,18 throttlings.
Above embodiment has just set forth the basic principle and the characteristic of the utility model; The utility model is not limited by the foregoing description; Under the prerequisite that does not break away from the utility model spirit and scope; The utility model also has various variations and change, and these variations and change all fall in the utility model scope that requires protection.The utility model requires protection domain to be defined by appending claims and equivalent thereof.
Claims (7)
1. a single twin-stage complementary holds in the palm windy ability heat pump air conditioner; It is characterized in that: be made up of prime super low temperature heat pump and back level superhigh temperature heat pump two-stage heat pump, described two-stage heat pump realizes that by the grade coupled heat exchanger in front and back and single twin-stage complementary transitions device prime super low temperature heat pump single-stage independent operating or prime super low temperature heat pump move with back level superhigh temperature heat pump twin-stage simultaneously.
2. the windy ability of the complementary holder of a kind of single twin-stage according to claim 1 heat pump air conditioner; It is characterized in that: described single twin-stage complementary transitions device constitutes single-stage and twin-stage complementary transitions device by compressor check-valves (8) and refrigerant fluid pump check-valves (12), four-way change-over valve (9), liquid storage gas-liquid separator (10) and refrigerant fluid pump (11); One end of described single its compressor check-valves (8) of twin-stage complementary transitions device is connected with the exhaust end of the refrigeration compressor (7) of back level superhigh temperature heat pump; After the other end of compressor check-valves (8) is connecting an end of refrigerant fluid pump check-valves (12); Be connected with the j end of four-way change-over valve (9) again; The other end of refrigerant fluid pump check-valves (12) is connecting the drain side of refrigerant fluid pump (11); The liquid feeding end of refrigerant fluid pump (11) is connected with the feed flow port o of liquid storage gas-liquid separator (10); The gas port m of liquid storage gas-liquid separator (10) is connected with the l of four-way change-over valve (9) end, and another gas port n of liquid storage gas-liquid separator (10) is connected with the suction end of refrigeration compressor (7).
3. the windy ability of the complementary holder of a kind of single twin-stage according to claim 1 heat pump air conditioner, it is characterized in that: described prime super low temperature heat pump is made up of refrigeration compressor (1), four-way change-over valve (2), the grade coupled heat exchangers in front and back (3), expansion valve (4), off-premises station air heat exchanger (5), gas-liquid separator (6); Back level superhigh temperature heat pump is made up of refrigeration compressor (7), compressor check-valves (8), four-way change-over valve (9), liquid storage gas-liquid separator (10), refrigerant fluid pump (11), refrigerant fluid pump check-valves (12), indoor set air heat exchanger (13,14,15) and expansion valve (16,17,18).
4. the windy ability of the complementary holder of a kind of single twin-stage according to claim 1 heat pump air conditioner, it is characterized in that: described prime super low temperature heat pump is made up of refrigeration compressor (1), four-way change-over valve (2), the grade coupled heat exchangers in front and back (3), expansion valve (4), off-premises station air heat exchanger (5), gas-liquid separator (6); Back level superhigh temperature heat pump is made up of refrigeration compressor (7), compressor check-valves (8), four-way change-over valve (9), gas-liquid separator (19), refrigerant fluid pump (11), refrigerant fluid pump check-valves (12), indoor set air heat exchanger (13,14,15) and expansion valve (16,17,18).
5. the windy ability of the complementary holder of a kind of single twin-stage according to claim 1 heat pump air conditioner, it is characterized in that: described prime super low temperature heat pump is made up of refrigeration compressor (1), four-way change-over valve (2), the grade coupled heat exchangers in front and back (3), expansion valve (4), off-premises station air heat exchanger (5), gas-liquid separator (6); Back level superhigh temperature heat pump is made up of refrigeration compressor (7), compressor check-valves (8), four-way change-over valve (9), liquid storage gas-liquid separator (10), refrigerant fluid pump (11), indoor set air heat exchanger (13,14,15), expansion valve (16,17,18) and valve (20,21,22,23).
6. according to the windy ability of the complementary holder of each described a kind of single twin-stage of claim 2 to 5 heat pump air conditioner, it is characterized in that: described refrigeration compressor (1,7) adopts VFC.
7. according to the windy ability of the complementary holder of each described a kind of single twin-stage of claim 3 to 5 heat pump air conditioner, it is characterized in that: described expansion valve (4,16,17,18) is the electronic expansion valve, and described valve (20,21,22,23) is an electromagnetic valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012200028126U CN202432754U (en) | 2012-01-05 | 2012-01-05 | Single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012200028126U CN202432754U (en) | 2012-01-05 | 2012-01-05 | Single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202432754U true CN202432754U (en) | 2012-09-12 |
Family
ID=46782194
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012200028126U Expired - Lifetime CN202432754U (en) | 2012-01-05 | 2012-01-05 | Single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202432754U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102706034A (en) * | 2012-01-05 | 2012-10-03 | 王全龄 | Single-double-stage complementary-type one-support-multiple wind energy heat pump air conditioner |
| CN105115194A (en) * | 2015-09-08 | 2015-12-02 | 中节能先导城市节能有限公司 | Hierarchical-type self-circulation water source heat pump area energy saving conveying-and-distributing system |
-
2012
- 2012-01-05 CN CN2012200028126U patent/CN202432754U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102706034A (en) * | 2012-01-05 | 2012-10-03 | 王全龄 | Single-double-stage complementary-type one-support-multiple wind energy heat pump air conditioner |
| CN102706034B (en) * | 2012-01-05 | 2015-03-25 | 王全龄 | Single-double-stage complementary-type one-support-multiple wind energy heat pump air conditioner |
| CN105115194A (en) * | 2015-09-08 | 2015-12-02 | 中节能先导城市节能有限公司 | Hierarchical-type self-circulation water source heat pump area energy saving conveying-and-distributing system |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103090485B (en) | Air conditioning system for restaurant | |
| CN103712367B (en) | Solar air source heat pumps air conditioning system | |
| CN202757346U (en) | Central air-conditioning and hot water all-in-one machine | |
| CN103245122A (en) | Ultra-low-temperature double-circuit heat pump air-conditioning water heater | |
| CN106839518A (en) | The double cold and hot pump assemblys of integral type | |
| CN100467964C (en) | Air condition device of using diversiform natural environmental protective energy sources | |
| CN103836792B (en) | Heat pump and hot water heating combined system | |
| CN201302241Y (en) | Environment-friendly and energy-saving household central air-conditioning system | |
| CN202403450U (en) | Household integrated multifunctional air source heat pump type air conditioning unit | |
| CN203274348U (en) | Ultralow-temperature double-loop heat pump air-conditioning hot water machine | |
| CN203671820U (en) | Air source integrated central air conditioner | |
| CN202432754U (en) | Single-stage and two-stage complemented multi-split heat-pump air conditioner using wind energy | |
| CN201104049Y (en) | Full fresh air heat pump type air conditioner | |
| CN103851723A (en) | Air conditioning system for restaurant | |
| CN102706034A (en) | Single-double-stage complementary-type one-support-multiple wind energy heat pump air conditioner | |
| CN203501363U (en) | Double-effect heat pump air conditioning unit | |
| CN103225850B (en) | A kind of silent air-conditioning system | |
| CN203431984U (en) | Noiseless air condition system | |
| CN200986311Y (en) | Double system air conditioner heat pump water heater | |
| CN203629122U (en) | Air conditioning system for solar air source heat pump | |
| CN209726564U (en) | A kind of phase-change accumulation energy defrosting Multifunctional cold heating system | |
| CN203928493U (en) | Earth source heat pump | |
| CN105605818A (en) | Double-working-condition air conditioner | |
| CN102175054B (en) | Efficient heat pump full-heat recovery solution-type new fan and energy regulating method thereof | |
| CN201401995Y (en) | R290 household air-conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20120912 Effective date of abandoning: 20150325 |
|
| RGAV | Abandon patent right to avoid regrant |