CN205261964U - Critical heat pump device strides - Google Patents
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- CN205261964U CN205261964U CN201521083937.6U CN201521083937U CN205261964U CN 205261964 U CN205261964 U CN 205261964U CN 201521083937 U CN201521083937 U CN 201521083937U CN 205261964 U CN205261964 U CN 205261964U
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Abstract
The utility model provides a critical heat pump device strides, including compression system, condenser (2), main throttling arrangement (401) and evaporimeter (3), wherein lieing in main throttling arrangement (401) and still be provided with flash vessel (5) on the refrigerant line between evaporimeter (3), the exhaust end of flash vessel (5) is connected to via flash vessel by -pass line compression system's low -pressure end, middling pressure end or high -pressure side, just compression system is the doublestage compression system including two series connection compressors or two compressors in compression chamber of establishing ties. Through the utility model discloses can effectively realize striding critical doublestage compression cycle, furthest has improved the caloric receptivity of the unit mass refrigerant that should circulate, and then realizes that the heat supply temperature is high, can provide 120~130 DEG C heat supply temperature, has widened high temperature heat pump's range of application, has improved the cycle efficiency, and can also reduce high -low pressure pressure ratio and the cost reduction of system, bulk reduction effectively.
Description
Technical field
The utility model belongs to technical field of air-conditioning heat pumps, is specifically related to a kind of across critical heat pump installation.
Background technology
High temperature heat pump is a kind of part electric energy that consumes, by thermodynamic cycle, heat energy is transferred to the energy utility system of high temperature heat source by low-temperature heat source, therefore the industrial exhaust heat of the more difficult utilization of some other methods of industrial circle can by high temperature heat pump by this part transfer of heat in high temperature heat source, and waste heat thermal source is discharged in environment with lower temperature, thereby reduce the thermal pollution to environment, and the high temperature heat source producing not only can be used for heating, can also be used for as industrial circles such as food/drying of wood, desalinization, rectifying chemical industry. Because high temperature heat pump has obvious economic benefit and social benefit, market potential is huge, becomes a basic orientation of international heat pump research in recent years. But common subcritical cycle high temperature heat pump system is subject to heat supply temperature that the restriction of high-pressure provides generally 70～80 DEG C of left and right, has limited its range of application in hot industry field. The heat supply temperature of 120-130 DEG C can be provided across critical cycle high temperature heat pump, and far above the heat supply temperature of ordinary hot pumping system, therefore application prospect is more wide. But because its high-low pressure pressure ratio is far above common heat pump, cycle efficieny is relatively low. In prior art, there is the scheme of a kind of multi-stage compression, cascade raising temperature, as shown in Figure 11, system is made up of two relatively independent circulations, the thermal source of low temperature level condenser output continues by the heating of high temperature level condenser, heat source temperature is further improved, and low temperature level subcooler is the evaporimeter of high temperature level. This system has increased one or more bypass circulations that comprise compressor and condenser, and system cost is higher, and has increased the volume of system and controlled complexity.
Owing to existing subcritical cycle high temperature heat pump to limit range of application because heat supply temperature is low in prior art; Although across critical cycle high temperature heat pump heat supply temperature height, still its high-low pressure is larger, cycle efficieny is lower; Although cascade raising temperature heat pump heat supply temperature is high, but the lower cost of high-low pressure pressure ratio is higher and system bulk is large, the complicated technical problem of degree of control, therefore the utility model research and design goes out a kind of across critical heat pump installation.
Utility model content
Therefore, the technical problems to be solved in the utility model is to overcome heat pump existence of the prior art cannot realize the defect that heat supply temperature is high, high-low pressure pressure ratio is low and cost is low, system bulk is less simultaneously, thereby provides a kind of across critical heat pump installation.
It is a kind of across critical heat pump installation that the utility model provides, comprise compressibility, condenser, main throttling arrangement and evaporimeter, wherein on the refrigerant line between described main throttling arrangement and described evaporimeter, be also provided with flash vessel, the exhaust end of described flash vessel is connected to low-pressure end, intermediate voltage terminal or the high-pressure side of described compressibility via flash vessel bypass line, and described compressibility is the Two-stage Compression system that comprises the compressor of two compressors in series or two series connection compression chambers.
Preferably, described Two-stage Compression system comprises the first compressor and the second compressor that are connected in series.
Preferably, described Two-stage Compression system is to comprise the twin-tub two-spool compressor that low pressure compression chamber and high pressure compressed chamber are connected in series.
Preferably, described flash vessel bypass line is connected to the low-pressure end of described compressibility, and is provided with pressure equaliser on described flash vessel bypass line.
Preferably, described flash vessel bypass line is connected to the intermediate voltage terminal of described compressibility, and is provided with the 3rd compressor on described flash vessel bypass line.
Preferably, described flash vessel bypass line is connected to the high-pressure side of described compressibility, and is provided with the 3rd compressor on described flash vessel bypass line.
Preferably, described Two-stage Compression system and the 3rd compressor be low pressure compression chamber and high pressure compressed chamber connect and be provided with in the middle of the twin-tub two-spool compressor structure in parallel with rotor compressor of gas supplementing opening, or three compressors compressor unit in a housing.
Preferably, described Two-stage Compression system and the 3rd compressor be the series connection of low pressure compression chamber and high pressure compressed chamber and do not establish in the middle of the twin-tub two-spool compressor structure in parallel with rotor compressor of gas supplementing opening, or three compressors compressor unit in a housing.
Preferably, on the pipeline between described flash vessel and evaporimeter, be also provided with auxiliary throttling arrangement.
Preferably, also comprise the Intermediate Heat Exchanger being arranged on refrigerant line, described Intermediate Heat Exchanger hot junction is arranged on the pipeline between condensator outlet and main throttling arrangement, and cold junction is arranged on the pipeline between evaporator outlet and described compressibility low-pressure end.
Preferably, described flash vessel is unidirectional flash vessel or two-way flash vessel.
Preferably, in the time having auxiliary throttling arrangement, described main throttling arrangement and auxiliary throttling arrangement are any one in capillary, restriction sleeve, heating power expansion valve, electric expansion valve, restricting orifice.
Preferably, pressure equaliser shown in is the adjustable valve element of actual internal area.
What the utility model provided has following beneficial effect across critical heat pump installation:
By of the present utility model arrange flash vessel and flash distillation bypass line across critical heat pump installation, can effectively realize across critical Two-stage Compression circulation, farthest improve the caloric receptivity of this circulating unit quality cold-producing medium, and then it is high to realize heat supply temperature, the heat supply temperature of 120～130 DEG C can be provided, the range of application of having widened high temperature heat pump, has improved cycle efficieny;
And be set to comprise the Two-stage Compression system of the compressor of two compressors in series or two series connection compression chambers by compressibility, can effectively reduce that high-low pressure pressure ratio and system cost reduce, volume reduces;
2. the gas compression that the 3rd compressor of increase small displacement separates flash evaporation is to intermediate pressure or high-pressure, reduce the wasted work of main road compressor, and main road compressor adopts twin-tub series connection compression chamber the mode in parallel with bypass compressor compresses chamber, reduce compressor volume, reduced the complexity of system cost and control;
3. by increasing Intermediate Heat Exchanger, can also increase the saturated liquid refrigerant flow that flash evaporation separates, the heat exchange amount of evaporimeter can further improve, and therefore system heating capacity and efficiency are also further promoted.
Brief description of the drawings
Fig. 1 is the structural representation of the embodiment one across critical heat pump installation of the present utility model;
Fig. 2 is the structural representation of the embodiment two across critical heat pump installation of the present utility model;
Fig. 3 is the structural representation of the embodiment three across critical heat pump installation of the present utility model;
Fig. 4 is the structural representation of the embodiment four across critical heat pump installation of the present utility model;
Fig. 5 is the structural representation of the embodiment five across critical heat pump installation of the present utility model;
Fig. 6 is the structural representation of the embodiment six across critical heat pump installation of the present utility model;
Fig. 7 is the structural representation of the embodiment seven across critical heat pump installation of the present utility model;
Fig. 8 is the structural representation of the embodiment eight across critical heat pump installation of the present utility model;
Fig. 9 is the structural representation of the embodiment nine across critical heat pump installation of the present utility model;
Figure 10 is the structural representation of the compressor unit across critical heat pump installation of the present utility model;
Wherein (a) represents the schematic diagram of compressor unit the first structure; (b) schematic diagram of expression compressor unit the first structure; (c) schematic diagram of expression compressor unit the first structure;
Figure 11 is the structural representation of the heat pump assembly of the cascade raising temperature technical scheme of prior art.
In figure, Reference numeral is expressed as:
The 101-the first compressor, the 102-the second compressor, the 103-the three compressor, 2-condenser (air cooler), 3-evaporimeter; 401-main throttling arrangement, 402-auxiliary throttling arrangement, 5-flash vessel (flash evaporation); 6-pressure equaliser; 7-Intermediate Heat Exchanger (economizer).
Detailed description of the invention
As Figure 1-10 shows, it is a kind of across critical heat pump installation that the utility model provides, comprise compressibility, condenser 2, main throttling arrangement 401 and evaporimeter 3, wherein on the refrigerant line between described main throttling arrangement 401 and described evaporimeter 3, be also provided with flash vessel 5 (also can be called flash evaporation), the exhaust end of described flash vessel 5 is connected to low-pressure end, intermediate voltage terminal or the high-pressure side of described compressibility via flash vessel bypass line, and described compressibility is the Two-stage Compression system that comprises the compressor of two compressors in series or two series connection compression chambers.
By above-mentioned flash vessel being set and corresponding syndeton can separate the two phase refrigerant after main throttling arrangement throttling via flash evaporation, the cold-producing medium that makes to enter evaporimeter reaches or is approximately saturated liquid, farthest improve the caloric receptivity of this circulating unit quality cold-producing medium, and because evaporator cold-producing medium is that the low-down two-phase state of saturated liquid state or mass dryness fraction is conducive to evaporimeter and shunts inhomogeneity improvement, (pressure drop in cold-producing medium evaporation process is along with the mass dryness fraction of cold-producing medium increases and increases to effectively reduce the pressure drop of evaporator refrigerant side, so the mass dryness fraction of evaporator is reduced to the pressure drop that can reduce evaporimeter inner refrigerant), increase evaporimeter heat transfer temperature difference, thereby can effectively realize across critical Two-stage Compression circulation, farthest improved the caloric receptivity of this circulating unit quality cold-producing medium, and then it is high to realize heat supply temperature, and the heat supply temperature of 120～130 DEG C can be provided, the range of application of having widened high temperature heat pump, has improved cycle efficieny. (especially for the high temperature heat pump system that adopts CO2 cold-producing medium, (CO2 evaporation heat transfer coefficient increases along with the reduction of cold-producing medium mass dryness fraction, so the mass dryness fraction of evaporator is reduced and can promote refrigerant side evaporation heat transfer coefficient also to have promoted refrigerant side evaporation heat transfer coefficient. other the cold-producing medium evaporation heat transfer coefficient such as R410A, R32, R22, R134a is all to reduce with the reduction of cold-producing medium mass dryness fraction. so, here list especially the high temperature heat pump system of CO2 cold-producing medium, this programme more produces effect to relative other cold-producing medium of the lifting of this systematic function), evaporimeter heat exchange property is significantly promoted, under the constant condition of heating capacity, evaporating temperature raises, (evaporimeter heat exchange property is good to have reduced circulation compression ratio merit, mean that evaporimeter heat exchange amount can become large, under the constant condition of heating capacity, evaporimeter heat exchange amount Q=U.A. Δ T also will remain unchanged, so Δ T can reduce (because overall heat-transfer coefficient U is substantially constant, A is also constant for constant its heat exchange area of heat exchanger), evaporimeter heat transfer temperature difference Δ T diminishes, also just mean evaporating temperature (the Δ T ≈ Ta-Te that can raise, air themperature Ta is exactly the operating mode of setting, constant, so only have evaporating temperature Te to raise), compressor air suction temperature also raises, pressure ratio reduces, so compressor pressure ratios merit also reduces), systematic function is promoted),
And compressibility of the prior art is set to the Two-stage Compression system of the compressor that comprises two compressors in series or two series connection compression chambers, the pressure ratio of single compressor is significantly reduced, compressor efficiency significantly promotes, and therefore systemic circulation COP also can get a promotion; Compare than (seeing Fig. 1) in scheme and need two compressors to be separately positioned in main road circulation and bypass circulation, the utility model can reduce by a bypass compressor, thereby has reduced the complexity of system cost, volume and control;
Thereby realized the beneficial effect that heat pump assembly heat supply temperature is high, high-low pressure pressure ratio is low and cost is low, system bulk is less simultaneously.
Preferably, described Two-stage Compression system comprises the first compressor 101 and the second compressor 102 that are connected in series. This is a kind of structure and embodiment of preferred Two-stage Compression system, can be referring to (a) in Figure 10.
Preferably, described Two-stage Compression system is to comprise the twin-tub two-spool compressor that low pressure compression chamber and high pressure compressed chamber are connected in series, and this is also a kind of structure and embodiment of preferred Two-stage Compression system, sees shown in (a) in Figure 10. Gas supplementing opening in the middle of further preferably not establishing between this low pressure compression chamber and high pressure compressed chamber, reaches object simple in structure.
As Fig. 1, Fig. 4, shown in Fig. 7, preferably, described flash vessel bypass line is connected to the low-pressure end of described compressibility, and is provided with pressure equaliser 6 on described flash vessel bypass line. To via the isolated gaseous refrigerant step-down of shwoot by-pass collar, to prevent that liquid refrigerant from entering low-pressure stage compressor 102 air entries by the Main Function of pressure equaliser is set.
As Fig. 2, Fig. 5, shown in Fig. 8, preferably, described flash vessel bypass line is connected to the intermediate voltage terminal of described compressibility, and is provided with the 3rd compressor 103 on described flash vessel bypass line. The saturated gas that flash evaporation is separated is by compression refrigerant in the high temperature of the 3rd compressor 103 boil down to intermediate pressures, and the refrigerant mixed of pressing in the high temperature of discharging with the second compressor 102 enters the cold-producing medium of the 3rd compressor 103 boil down to HTHPs. By being set, the 3rd compressor the saturated refrigerant gas of low pressure of flash evaporation separation can be compressed to intermediate pressure by the 3rd compressor 101, compared with adopting pressure equaliser can reduce certain restriction loss, thereby can reduce the work done during compression of main road compressor.
As Fig. 3, Fig. 6, shown in Fig. 9, preferably, described flash vessel bypass line is connected to the high-pressure side of described compressibility, and is provided with the 3rd compressor 103 on described flash vessel bypass line. The saturated gas that flash evaporation is separated, by the cold-producing medium of the 3rd compressor 103 boil down to HTHPs, enters air cooler after the high-temperature high-pressure refrigerant compressing mixes cooling with the first compressor 101. Replace pressure equaliser 6 by arranging compared with the 3rd compressor 103 of small displacement, the saturated refrigerant gas of low pressure that flash evaporation can be separated is compressed to pressure at expulsion by the 3rd compressor 101, compared with adopting pressure equaliser can reduce certain restriction loss, thereby can reduce the work done during compression of main road compressor.
By being set on described flash vessel bypass line, the 3rd compressor 103 (being preferably compared with small displacement) replace pressure equaliser 6 the saturated refrigerant gas of low pressure of flash evaporation separation can be compressed to intermediate pressure or pressure at expulsion by the 3rd compressor 101, reduce the restriction loss that pressure equaliser 6 causes, thereby reduced the work done during compression of main road compressor.
Preferably, described Two-stage Compression system and the 3rd compressor 103 are twin-tub two-spool compressor structures in parallel with rotor compressor that middle gas supplementing opening was connected and was provided with in low pressure compression chamber and high pressure compressed chamber, or three compressors compressor unit in a housing, as shown in (b) in Figure 10. Can effectively reduce the volume of compressibility by this kind of structure, thereby reduce cost.
Preferably, described Two-stage Compression system and the 3rd compressor 103 are twin-tub two-spool compressor structures in parallel with rotor compressor that middle gas supplementing opening was connected and do not established in low pressure compression chamber and high pressure compressed chamber, or three compressors compressor unit in a housing, see shown in (c) in Figure 10. Can effectively reduce the volume of compressibility by this kind of structure, thereby reduce cost.
As Figure 4-Figure 6, preferably, on the pipeline between described flash vessel 5 (or claiming flash evaporation) and evaporimeter 3, be also provided with auxiliary throttling arrangement 402, this auxiliary flow device 402 can be used to regulate evaporator cold-producing medium mass dryness fraction, especially for cold-producing mediums such as R32, R134a, R1234yf, evaporation heat transfer coefficient and refrigerant side pressure drop all increase along with the increase of cold-producing medium mass dryness fraction, by regulating the auxiliary throttling arrangement 9 can balancing evaporator tube internal heat exchange coefficient and pressure drop, ensure that performance of evaporator performs to the best.
As Figure 7-9, be respectively in the scheme of Fig. 1～3, introduce Intermediate Heat Exchanger double-stage compressor one-level throttling shwoot bypass across critical cycle high temperature heat pump system schematic diagram. Preferably, also comprise the Intermediate Heat Exchanger being arranged on refrigerant line, described Intermediate Heat Exchanger hot junction is arranged on the pipeline between condenser 2 (air cooler) outlet and main throttling arrangement 401, and cold junction is arranged on the pipeline between evaporimeter 3 outlets and described compressibility low-pressure end. For the high high temperature heat pump system of gas cooler exit temperature, Intermediate Heat Exchanger 7 can significantly reduce air cooler 2 outlet temperatures, and then reduce specific enthalpy and the mass dryness fraction after 401 throttlings of first throttle device, increase the saturated liquid refrigerant flow that flash evaporation separates, the heat exchange amount of evaporimeter can further improve, and therefore system heating capacity and efficiency are also further promoted.
Preferably, described flash vessel 5 (flash evaporation) is unidirectional flash vessel or two-way flash vessel. This is a kind of preferred kind and the structure of flash vessel.
Preferably, pressure equaliser 6 is the adjustable valve elements of actual internal area, and this is the preferred kind of one and the structure of pressure equaliser. Further preferably pressure equaliser 6 can also be pipeline as less in internal diameter capillaceous.
Preferably, described main throttling arrangement 401 and auxiliary throttling arrangement 402 are any one in capillary, restriction sleeve, heating power expansion valve, electric expansion valve, restricting orifice. This is also preferred kind and the structure of throttling arrangement.
Introduce preferred embodiment of the present utility model below
Embodiment one
The utility model provides a kind of adopt double-stage compressor one-level throttling shwoot bypass across critical cycle high temperature heat pump system schematic diagram as shown in Figure 1, the refrigerant gas of HTHP becomes the high pressure supercriticality gas of relatively lower temp from the first compressor 101 discharges enter air cooler 2, entering the cold-producing medium two-phase mixture that becomes low-temp low-pressure after electric expansion valve 401 throttlings enters in flash evaporation 5, isolate saturated liquid and saturated gas through the gas liquid separating function of flash evaporation, saturated liquid enters the refrigerant gas that becomes low-temp low-pressure after the rear evaporation of evaporimeter 3, saturated gas is mixed into the cold-producing medium of pressing in the second compressor 102 boil down to high temperature with evaporimeter 3 low-temperature low-pressure refrigerant gas out after pressure equaliser 6, enter again the cold-producing medium of the first compressor 101 boil down to HTHPs, complete a circulation. this embodiment changes single stage compress of the prior art into double-stage compressor, and the pressure ratio of single compressor is significantly reduced, and compressor efficiency significantly promotes, and therefore systemic circulation COP also can get a promotion. in addition, this embodiment separates the two phase refrigerant after throttling by flash evaporation, the cold-producing medium that makes to enter evaporimeter reaches or is approximately saturated liquid, farthest improve the caloric receptivity of this circulating unit quality cold-producing medium, and because evaporator cold-producing medium is that the low-down two-phase state of saturated liquid state or mass dryness fraction is conducive to evaporimeter and shunts inhomogeneity improvement, effectively reduce the pressure drop of evaporator refrigerant side, increase evaporimeter heat transfer temperature difference, for the high temperature heat pump system that adopts CO2 cold-producing medium, also promote refrigerant side evaporation heat transfer coefficient, evaporimeter heat exchange property is significantly promoted, under the constant condition of heating capacity, evaporating temperature raises, reduce circulation compression ratio merit, systematic function promotes. the first compressor 101 adopting in the present embodiment and the second compressor 102 can be the twin-tub two-spool compressors that comprises low pressure compression chamber and high pressure compressed chamber, see shown in (a) in Figure 10, low pressure compression chamber and high pressure compressed chamber are connected in series, it is the compression that compressor operating time-division two-stage is carried out cold-producing medium simultaneously, comparing than (seeing Figure 11) in scheme needs two compressors to be separately positioned in main road circulation and bypass circulation, the utility model can reduce by a bypass compressor, thereby has reduced the complexity of system cost, volume and control.
Embodiment two and embodiment three
Fig. 2 and Fig. 3 are more excellent scheme of the present utility model, replace pressure equaliser 6 by the 3rd compressor 103 compared with small displacement, Fig. 2 be saturated gas that flash evaporation is separated by compression refrigerant in the high temperature of the 3rd compressor 103 boil down to intermediate pressures, the refrigerant mixed of pressing in the high temperature of discharging with the second compressor 102 enters the cold-producing medium of the 3rd compressor 103 boil down to HTHPs; Fig. 3 is that the saturated gas that flash evaporation is separated passes through the cold-producing medium of the 3rd compressor 103 boil down to HTHPs, enters air cooler cooling with the first compressor 101 after the high-temperature high-pressure refrigerant compressing mixes. The saturated refrigerant gas of low pressure that embodiment two separates flash evaporation with embodiment three is compressed to intermediate pressure (Fig. 2) or pressure at expulsion (Fig. 3) by the 3rd compressor 101, reduce the restriction loss that in Fig. 1, pressure equaliser 6 causes, reduced the work done during compression of main road compressor.
Embodiment four, embodiment five and embodiment six
Fig. 4～Fig. 6 arranges auxiliary throttling arrangement 402 on the pipeline between flash evaporation 5 and the evaporimeter 3 of Fig. 1～3, this auxiliary flow device 402 can be used to regulate evaporator cold-producing medium mass dryness fraction, for cold-producing mediums such as R32, R134a, R1234yf, evaporation heat transfer coefficient and refrigerant side pressure drop all increase along with the increase of cold-producing medium mass dryness fraction, by regulating the auxiliary throttling arrangement 9 can balancing evaporator tube internal heat exchange coefficient and pressure drop, ensure that performance of evaporator performs to the best.
Embodiment seven, embodiment eight and embodiment nine
Fig. 7～Fig. 9 be respectively in the scheme of Fig. 1～3, introduce Intermediate Heat Exchanger double-stage compressor one-level throttling shwoot bypass across critical cycle high temperature heat pump system schematic diagram. Intermediate Heat Exchanger hot junction is arranged on the pipeline between air cooler outlet and first throttle device 401, and cold junction is arranged on evaporimeter 3 export pipelines. For the high high temperature heat pump system of gas cooler exit temperature, Intermediate Heat Exchanger 7 can significantly reduce air cooler 2 outlet temperatures, and then reduce specific enthalpy and the mass dryness fraction after 401 throttlings of first throttle device, increase the saturated liquid refrigerant flow that flash evaporation separates, the heat exchange amount of evaporimeter can further improve, and therefore system heating capacity and efficiency are also further promoted.
In embodiment shown in Fig. 1 and Fig. 4, the first compressor 101 and the second compressor 102 can be the twin-tub two-spool compressors that comprises low pressure compression chamber and high pressure compressed chamber, low pressure compression chamber and high pressure compressed chamber are connected in series, and gas supplementing opening in the middle of can not establishing between low pressure compression chamber and high pressure compressed chamber, is shown in shown in (a) in Figure 10.
In embodiment shown in Fig. 2, Fig. 5 and Fig. 8, the first compressor 101, the second compressor 102 and the 3rd compressor 103 can be that low pressure compression chamber and the twin-tub two-spool compressor series connection of high pressure compressed chamber and that be provided with middle gas supplementing opening are in parallel with rotor compressor, also can be the compressor units of three compressors in a housing, see shown in (b) in Figure 10.
In embodiment shown in Fig. 3, Fig. 6 and Fig. 9, the first compressor 101, the second compressor 102 and the 3rd compressor 103 can be that in the middle of not establishing of low pressure compression chamber and the series connection of high pressure compressed chamber, the twin-tub two-spool compressor of gas supplementing opening is in parallel with rotor compressor, also can be the compressor units of three compressors in a housing, see shown in (c) in Figure 10.
The flash evaporation 5 adopting in embodiment of the present utility model can be unidirectional flash evaporation or two-way flash evaporation, can be also other flash evaporation with gas liquid separating function. The throttling arrangement 401 and the auxiliary throttling arrangement 402 that adopt can be capillary, restriction sleeve, heating power expansion valve, electronic expansion, restricting orifice etc. or its combination. Pressure equaliser 6 can be pipeline as less in internal diameter capillaceous, also can be the adjustable valve element of actual internal area, its Main Function is to via the isolated gaseous refrigerant step-down of shwoot by-pass collar, to prevent that liquid refrigerant from entering low-pressure stage compressor 102 air entries.
Those skilled in the art will readily understand, under the prerequisite of not conflicting, above-mentioned each advantageous manner can freely combine, superpose.
The foregoing is only preferred embodiment of the present utility model; not in order to limit the utility model; all any amendments of doing within spirit of the present utility model and principle, be equal to and replace and improvement etc., within all should being included in protection domain of the present utility model. The above is only preferred embodiment of the present utility model; should be understood that; for those skilled in the art; do not departing under the prerequisite of the utility model know-why; can also make some improvement and modification, these improve and modification also should be considered as protection domain of the present utility model.
Claims (13)
1. across a critical heat pump installation, comprise compressibility, condenser (2), main throttling arrangement (401)And evaporimeter (3), it is characterized in that: be positioned at described main throttling arrangement (401) and described evaporimeter (3)Between refrigerant line on be also provided with flash vessel (5), the exhaust end of described flash vessel (5) is via sudden strain of a muscleSteaming device bypass line is connected to low-pressure end, intermediate voltage terminal or the high-pressure side of described compressibility, and described compression systemSystem is the Two-stage Compression system that comprises the compressor of two compressors in series or two series connection compression chambers.
2. according to claim 1 across critical heat pump installation, it is characterized in that: described Two-stage CompressionSystem comprises the first compressor (101) and the second compressor (102) that are connected in series.
3. according to claim 1 across critical heat pump installation, it is characterized in that: described Two-stage CompressionSystem is to comprise the twin-tub two-spool compressor that low pressure compression chamber and high pressure compressed chamber are connected in series.
According to one of claim 1-3 Suo Shu across critical heat pump installation, it is characterized in that: described sudden strain of a muscleSteaming device bypass line is connected to the low-pressure end of described compressibility, and arranges on described flash vessel bypass lineThere is pressure equaliser (6).
According to one of claim 1-3 Suo Shu across critical heat pump installation, it is characterized in that: described sudden strain of a muscleSteaming device bypass line is connected to the intermediate voltage terminal of described compressibility, and arranges on described flash vessel bypass lineThere is the 3rd compressor (103).
According to one of claim 1-3 Suo Shu across critical heat pump installation, it is characterized in that: described sudden strain of a muscleSteaming device bypass line is connected to the high-pressure side of described compressibility, and arranges on described flash vessel bypass lineThere is the 3rd compressor (103).
7. according to claim 5 across critical heat pump installation, it is characterized in that: described Two-stage CompressionSystem and the 3rd compressor (103) are connect and are provided with middle gas supplementing opening in low pressure compression chamber and high pressure compressed chamberThe twin-tub two-spool compressor structure in parallel with rotor compressor, or three compressors are at a housingInterior compressor unit.
8. according to claim 6 across critical heat pump installation, it is characterized in that: described Two-stage CompressionSystem and the 3rd compressor (103) are low pressure compression chamber and the series connection of high pressure compressed chamber and do not establish middle gas supplementing openingThe twin-tub two-spool compressor structure in parallel with rotor compressor, or three compressors are at a housingInterior compressor unit.
9. according to claim 1-3, one of 7-8 described across critical heat pump installation, it is characterized in that:On pipeline between described flash vessel (5) and evaporimeter (3), be also provided with auxiliary throttling arrangement (402).
10. according to claim 1-3, one of 7-8 described across critical heat pump installation, it is characterized in that: alsoComprise the Intermediate Heat Exchanger (7) being arranged on refrigerant line, described Intermediate Heat Exchanger hot junction is arranged on coldOn pipeline between condenser (2) outlet and main throttling arrangement (401), cold junction is arranged on evaporimeter (3)On pipeline between outlet and described compressibility low-pressure end.
11. according to claim 1-3, one of 7-8 described across critical heat pump installation, it is characterized in that: instituteStating flash vessel (5) is unidirectional flash vessel or two-way flash vessel.
12. is according to claim 9 across critical heat pump installation, it is characterized in that: when having auxiliary jointStream device is when (402), described main throttling arrangement (401) and auxiliary throttling arrangement (402) be capillary,Any one in restriction sleeve, heating power expansion valve, electric expansion valve, restricting orifice.
13. is according to claim 4 across critical heat pump installation, it is characterized in that: described pressure balanceDevice (6) is the adjustable valve element of actual internal area.
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105466059A (en) * | 2015-12-21 | 2016-04-06 | 珠海格力电器股份有限公司 | Transcritical heat pump device |
| CN107560210A (en) * | 2017-08-21 | 2018-01-09 | 珠海格力电器股份有限公司 | A kind of refrigeration system |
| CN107576085A (en) * | 2017-08-21 | 2018-01-12 | 珠海格力电器股份有限公司 | A kind of refrigeration system |
| CN107990584A (en) * | 2017-11-23 | 2018-05-04 | 西安交通大学 | A kind of CO 2 trans-critical heat pump formula refrigeration system |
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2015
- 2015-12-21 CN CN201521083937.6U patent/CN205261964U/en active Active
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105466059A (en) * | 2015-12-21 | 2016-04-06 | 珠海格力电器股份有限公司 | Transcritical heat pump device |
| CN107560210A (en) * | 2017-08-21 | 2018-01-09 | 珠海格力电器股份有限公司 | A kind of refrigeration system |
| CN107576085A (en) * | 2017-08-21 | 2018-01-12 | 珠海格力电器股份有限公司 | A kind of refrigeration system |
| CN107560210B (en) * | 2017-08-21 | 2023-11-03 | 珠海格力电器股份有限公司 | Refrigerating system |
| CN107576085B (en) * | 2017-08-21 | 2023-11-07 | 珠海格力电器股份有限公司 | Refrigerating system |
| CN107990584A (en) * | 2017-11-23 | 2018-05-04 | 西安交通大学 | A kind of CO 2 trans-critical heat pump formula refrigeration system |
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