CN2884061Y - Warmmer air source heat-pump device of parallel compressor able to achieve tow-stage compression - Google Patents
Warmmer air source heat-pump device of parallel compressor able to achieve tow-stage compression Download PDFInfo
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- CN2884061Y CN2884061Y CN 200520136550 CN200520136550U CN2884061Y CN 2884061 Y CN2884061 Y CN 2884061Y CN 200520136550 CN200520136550 CN 200520136550 CN 200520136550 U CN200520136550 U CN 200520136550U CN 2884061 Y CN2884061 Y CN 2884061Y
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Abstract
The utility model provides a low-temperature air source heat pump apparatus for compressor in parallel operation which enables double-level compression, the utility model is characterized in that an intermediate cooling circuit is arranged in the refrigerant loop of the ordinary heat pump device; a pathway with a second electromagnetic valve is arranged between the outlet of the low pressure level compressor and the inlet of the high pressure level compressor; a fifth check valve is arranged on the exhaust pipeline of the low pressure level compressor between the junction of the loop and the exhaust pipeline of the low pressure level compressor and the junction of exhaust pipelines of both the low and the high pressure level compressor; a sixth check valve is arranged on the suction pipeline of the high pressure level compressor between the junction of the suction pipelines of the low and the high pressure level compressor and the junction of the high pressure level compressor and the intermediate cooling circuit. Under the conditions of refrigeration in summer and single-level heating in winter, both the low and the high pressure level compressor are operating in parallel. When outdoor temperature becomes lower, heat supply for cold areas in winter is satisfied by transforming single-level compression heat pump cycle into double-level compression heat pump cycle through changing process without supplementary heat source.
Description
Technical field
The utility model belongs to the low-temperature air source heat pump device in refrigeration and air-conditioning technical field, particularly relates to a kind of compressor low-temperature air source heat pump device in parallel of the twin-stage the realized compression that the energy high efficient and reliable heats under cold district outdoor cold environmental conditions in winter.
Background technology
Since nineteen nineties, air source heat pump has obtained using widely at traditional non-heating zones such as China middle and lower reach of Yangtze River, south China and southwest, and it has satisfied the requirement of this area's winter heating well with lower energy consumption.But in areas such as China Huanghe valley, North China is with fire coal, fuel oil and the electric heater main means as winter heating always.Because region temperatures such as the Huanghe valley and North China are lower, adopt the normal air source heat pump system, its heating capacity and the coefficient of performance reduce greatly, and the compressor exhaust temperature overtemperature, and system's frequent start-stop can't operate as normal.Therefore the normal air source heat pump system can't satisfy the cold district heating demand in winter.
For solving air source heat pump, except the method for present employing auxiliary thermal source, air source heat pump many technological improvements have been carried out both at home and abroad at the cold district application problem.Japan scholar Horiuchi N proposes to adopt when outdoor low temperature Kerosene heater heating auxiliary evaporator to improve heat pump heating capacity and heating performance coefficient; Japan scholar Masaji Yamagami proposes to adopt frequency-changeable compressor, when environment temperature reduces, increases system's heating capacity by improving compressor rotary speed, and hydrojet reduces compressor exhaust temperature in the compressor operating chamber simultaneously; Malaysian far waits the people to propose to have the accurate secondary compressibility of screw compressor of economizer, has improved the heating capacity and the heating performance coefficient of system; Horse is the best waits the people to propose twin-stage coupling heat pump system, utilizes air source heat pump draw heat from outdoor air, and the water of producing 10～20 ℃ is produced higher temperatures hot water to heat to building as the low level heat energy of water resource heat pump again; Canadian S.M.Sami and PJ.Tulej propose to use non-azeotropic refrigerant to improve the heating performance of heat pump under low temperature environment.Above method has improved air source heat pump to some extent and has been used for the adaptability of cold district from different aspects, but does not all address this problem well.
For this reason, the present inventor once proposed the structure of the double stage compresses hot pump in low temp device (Chinese utility model patent ZL02200545.5) that a kind of suitable cold district uses and is: by compressor, cross valve, outdoor air cooling heat exchanger, heating power expansion valve, check valve, the high pressure reservoir, device for drying and filtering, indoor heat exchanger, gas-liquid separator, set up one by the hiigh pressure stage compressor in the refrigerant loop of the ordinary hot pump installation that water pump and connecting pipe and cold-producing medium and water route tube connector constitute, the hiigh pressure stage cross valve, middle throttling heating power expansion valve, magnetic valve, the hiigh pressure stage unit that intercooler and cold-producing medium tube connector constitute.This hiigh pressure stage compressor exhaust temperature is lower than 120 ℃, and heating capacity can satisfy customer requirements, and system's stable and reliable operation can be satisfied cold district heat supply in winter needs without auxiliary thermal source in the outdoor low temperature environment more than-18 ℃.But this double stage compresses hot pump in low temp device is under cooling condition and single-stage heating condition, and the hiigh pressure stage compressor does not put into operation; Have only that the hiigh pressure stage compressor just starts when outdoor environment temperature is low, this just makes the hiigh pressure stage compressor most of the time be in idle state, causes very big waste.
Summary of the invention
The purpose of this utility model is to provide a kind of compressor low-temperature air source heat pump device in parallel of realizing the twin-stage compression, can solve above-mentioned double stage compresses hot pump in low temp device under cooling condition and single-stage heating condition, the hiigh pressure stage compressor does not put into operation and causes the most of the time to be in the defective of idle state.
The technical solution of the utility model is as follows:
The compressor low-temperature air source heat pump device in parallel of the twin-stage the realized compression that the utility model provides comprises:
The ordinary hot pump installation of the compressor parallel that constitutes by low-pressure stage compressor 1, hiigh pressure stage compressor 13, cross valve 3, outdoor air cooling heat exchanger 4, first check valve 6, second check valve 10, the 3rd check valve 18, the 4th check valve 19, high pressure reservoir 7, throttling arrangement 9, indoor heat exchanger 11, gas-liquid separator 12 and connecting pipe and be installed in the refrigerant loop of ordinary hot pump installation of described compressor parallel in the middle of the cooling branch road; The cooling branch road comprises first magnetic valve 17, middle throttling arrangement 16 and the intercooler 21 by series connection successively in the middle of described; It is characterized in that, also comprise:
On the connecting line between low-pressure stage compressor outlet and hiigh pressure stage compressor 13 inlets, the path that comprises second magnetic valve 15 is set;
On the gas exhaust piping of low-pressure stage compressor, the low-pressure stage compressor and comprise the tie point of second magnetic valve, 15 paths and the tie point of the gas exhaust piping of low-pressure stage compressor and hiigh pressure stage compressor 13 between, the 5th check valve 2 is set;
On the suction line of hiigh pressure stage compressor 13, between the tie point of the suction line of hiigh pressure stage compressor 13 and low-pressure stage compressor and hiigh pressure stage compressor 13 and middle cooling branch road institute tie point, the 6th check valve 14 is set.
Described low-pressure stage compressor and hiigh pressure stage compressor 13 are the compressor of identical or different model.Described low-pressure stage compressor and hiigh pressure stage compressor are constant volume compressor or variable conpacitance compressor.Described low-pressure stage compressor is 1: 1 with the quantity ratio of hiigh pressure stage compressor; 2: 1; 3: 1 or 5: 2.
Described indoor heat exchanger 11 is air cooling heat exchanger or water cooling heat exchanger.Described throttling arrangement 9 and middle throttling arrangement 16 are heating power expansion valve, electric expansion valve or capillary.
The utility model is to constitute by changing system flow and setting up middle cooling branch road on the basis, ordinary hot pump installation loop of compressor parallel.The characteristic feature of this heat pump assembly is that low-pressure stage compressor and the operation of hiigh pressure stage compressor parallel by normal air source heat pump device process flow operation, have the performance and the effectiveness of normal air source heat pump device under summer cooling condition and winter single-stage heating condition; When the outdoor environment temperature reduction, when causing systematic function to descend, heat pump assembly is changed by valve, the single stage compress heat pump cycle is converted into the circulation of twin-stage compressing hot pump, increase the degree of supercooling of high pressure liquid refrigerant, improve system's heating capacity, reduce the hiigh pressure stage compressor exhaust temperature.Result of implementation shows that this heat pump assembly is under 50 ℃ of condensation temperatures and evaporating temperature-25 ℃ operating mode, and system's heating performance coefficient is higher than 2.0, and the hiigh pressure stage compressor exhaust temperature is lower than 120 ℃, and heating capacity can satisfy customer requirements; System's stable and reliable operation can be satisfied cold district heat supply in winter needs without auxiliary thermal source in the outdoor low temperature environment more than-18 ℃.
The compressor low-temperature air source heat pump device in parallel of the twin-stage realized that the utility model provides compression has been expanded air source heat pump and has been used at the heat supply in winter of cold district, and a kind of new way of energy-conservation and environmental protection is provided for the cold district heat supply in winter.Compare with Chinese utility model patent ZL02200545.5, the hiigh pressure stage compressor still can use under cooling condition and single-stage heating condition, has avoided idle state of hiigh pressure stage compressor most of the time, has improved the device overall utilization rate.
Description of drawings
The structural representation of accompanying drawing 1 the utility model (embodiment 1);
The structural representation of accompanying drawing 2 the utility model (embodiment 2).
The specific embodiment
Embodiment 1 is by a low-pressure stage compressor and the twin-stage compression low-temperature air source heat pump device that the hiigh pressure stage compressor is formed:
Fig. 1 is the low-temperature air source heat pump apparatus structure schematic diagram that can realize the twin-stage compression, also is its refrigerant line catenation principle figure.Present embodiment is on two compressors in parallel (low-pressure stage compressor 1 and hiigh pressure stage compressor 13) basis, ordinary hot pump installation loop, on the connecting line between device for drying and filtering 8 outlets and hiigh pressure stage compressor 13 inlets, increased the middle cooling branch road that comprises first magnetic valve 17, middle throttling arrangement 16 and intercooler 21 compositions of contacting successively;
On the connecting line between 1 outlet of low-pressure stage compressor and hiigh pressure stage compressor 13 inlets, increased the path that comprises magnetic valve 15; On low-pressure stage compressor 1 gas exhaust piping, at low-pressure stage compressor 1 and described first tie point that comprises the path of magnetic valve 15; On low-pressure stage compressor 1 gas exhaust piping, at second tie point of hiigh pressure stage compressor 13 with hiigh pressure stage compressor 13 gas exhaust pipings; The 5th check valve 2 is set between first tie point and second tie point;
On the suction line of hiigh pressure stage compressor 13, between the tie point of the tie point of the suction line of hiigh pressure stage compressor 13 and low-pressure stage compressor 1 and hiigh pressure stage compressor 13 and middle cooling branch road, check valve 14 is set; Under summer condition and winter single-stage heating condition,, can select to open separately a compressor or two compressor parallel runnings according to cold or heat demand; Under the low situation of outdoor temperature, this system can pass through the valve switching flow, changes twin-stage compressing hot pump system in the winter time.
First magnetic valve 15 and second magnetic valve 17 are all closed during cooling condition, and its operation principle is: (1) if refrigeration requirement is little, opens low-pressure stage compressor or hiigh pressure stage compressor according to the refrigeration requirement situation under the summer cooling condition.If open low-pressure stage compressor 1, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by low-pressure stage compressor 1, flow in the outdoor air cooling heat exchanger 4 through the 5th check valve 2, cross valve 3, through outdoor air cooling and condensation becomes highly pressurised liquid, enter in the high pressure receiver 7 by first check valve 6 again; The flow through highly pressurised liquid passage of device for drying and filtering 8 and intercooler 21 of the high pressure liquid refrigerant that flows out by high pressure receiver 7, through throttling arrangement 9 (can be heating power expansion valve, it can be electric expansion valve, also can be capillary) the throttling step-down becomes the gas-liquid two-phase cold-producing medium of low-temp low-pressure, and enter indoor heat exchanger 11 through check valve 10, absorb the gaseous refrigerant that heat of vaporization becomes low-temp low-pressure at this liquid refrigerant, realize the refrigeration purpose; The gaseous refrigerant of low-temp low-pressure returns low-pressure stage compressor 1 through cross valve 3, gas-liquid separator 12, finishes kind of refrigeration cycle.(2) if open hiigh pressure stage compressor 13, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by high-pressure unit compressor 13, arrive gas-liquid separator 12 through the route identical then through cross valve 3 with opening low-pressure stage compressor 1, return high-pressure unit compressor 13 through the 6th check valve 14 again, finish kind of refrigeration cycle.(3) when refrigeration requirement is big, need open two compressors (being low-pressure stage compressor 1 and high-pressure unit compressor 13) simultaneously, low-pressure stage and hiigh pressure stage compressor parallel operation this moment; The gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP respectively by low-pressure stage compressor 1 and high-pressure unit compressor 13, before cross valve 3, converge through the 5th check valve 2 with by the high temperature and high pressure gaseous refrigerant of hiigh pressure stage compressor 13 compressions by the high temperature and high pressure gaseous refrigerant of low-pressure stage compressor 1 compression, arrive gas-liquid separator 12 through route identical when only opening low-pressure stage compressor 1 then, this moment, the gaseous refrigerant of low-temp low-pressure was divided into two-way, one the tunnel directly returns low-pressure stage compressor 1, another Lu Jingdi six check valves 14 return high-pressure unit compressor 13, finish kind of refrigeration cycle.
First magnetic valve 15 and second magnetic valve 17 are all closed during the single-stage heating condition, and its operation principle is: (1) under the single-stage heating condition, if heat demand is little, only needs to open low-pressure stage compressor 1 or hiigh pressure stage compressor 13 in the winter time.As open low-pressure stage compressor 1, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by low-pressure stage compressor 1, through the 5th check valve 2, cross valve 3, enter indoor heat exchanger 11, gaseous refrigerant release heat cooling at this HTHP becomes highly pressurised liquid, realizes heating purpose; High pressure refrigerant liquid enters in the high pressure receiver 7 through the 3rd check valve 18; By the high pressure liquid refrigerant drying filter 8 of high pressure receiver 7 outflows and the highly pressurised liquid passage of intercooler 21, enter the gas-liquid two-phase cold-producing medium of throttling arrangement 9 throttling step-downs becoming low-temp low-pressure, again in the 4th check valve 19 inlet chamber external heat exchangers 4, liquid refrigerant evaporation absorption chamber outer air heat becomes the gaseous refrigerant of low-temp low-pressure, flow through again cross valve 3, gas-liquid separator 12 returns compressor 1, finishes heating circulation.(2) if open hiigh pressure stage compressor 13, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by hiigh pressure stage compressor 13, identical route arrives gas-liquid separator 12 when cross valve 3 passes through with unlatching low-pressure stage compressor then, return compressor 13 through the 6th check valve 14 again, finish heating circulation.(3) when heat demand bigger, then open two low-pressure stages simultaneously, low-pressure stage and hiigh pressure stage compressor parallel operation this moment.The gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP respectively by low-pressure stage compressor 1 and hiigh pressure stage compressor 13, before cross valve 3, converge through the 5th check valve 2 with by the gaseous refrigerant of the HTHP of hiigh pressure stage compressor 13 compressions by the high temperature and high pressure gaseous refrigerant of low-pressure stage compressor 1 compression, arrive gas-liquid separator 12 through route identical when only opening low-pressure stage compressor 1 then, this moment, the gaseous refrigerant of low-temp low-pressure was divided into two-way, one the tunnel directly returns low-pressure stage compressor 1, another Lu Jingdi six check valves 14 return hiigh pressure stage compressor 13, finish heating circulation.
The operation principle of twin-stage heating condition: when outdoor environment temperature is low, change this device into double stage compresses hot pump in low temp system, this moment, first magnetic valve 15 and second magnetic valve 17 were all open-minded.On the one hand, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of medium temperature and medium pressure by low-pressure stage compressor 1, flows to the suction line of hiigh pressure stage compressor 1 through second magnetic valve 15; On the other hand, flow out and high pressure liquid refrigerant by device for drying and filtering 8 is divided into two-way by high pressure receiver 7, sub-fraction throttling arrangement 16 in the middle of first magnetic valve 17 enters (can be a heating power expansion valve, it can be electric expansion valve, also can be capillary), become the medium temperature and medium pressure coolant channel that enters intercooler 21 behind the gas-liquid two-phase cold-producing medium of medium temperature and medium pressure in this throttling, absorption flow through liquid refrigerant in the liquid coolant channel of intercooler 21 HTHPs heat and evaporate, make the liquid cold-producing medium of HTHP obtain cold excessively fully simultaneously; Medium temperature and medium pressure refrigerant vapour that comes out from middle cooler and the temperature that flows out by second magnetic valve 15 higher the compacting refrigerant vapor enter hiigh pressure stage compressor 13 after mixing, be compressed into high temperature and high pressure gaseous refrigerant through hiigh pressure stage compressor 13, flow into indoor heat exchanger 11 through cross valve 3 again, the condensation heat release reaches and heats purpose; The refrigerant vapour of HTHP becomes high temperature high pressure liquid in condensation, enters in the high pressure receiver 7 by the 3rd check valve 18 again; The high pressure liquid refrigerant that is flowed out by high pressure receiver 7 at first passes through device for drying and filtering 8, sub-fraction enters the medium temperature and medium pressure coolant channel of intercooler 21 through first magnetic valve 17, middle throttling arrangement 16 then, most of high pressure liquid refrigerant intercooler 21 high-temperature high-pressure refrigerant passages of flowing through absorb the evaporation latent heat of medium temperature and medium pressure coolant channel inner refrigerant and realize significantly cold excessively; Obtain cold fully excessively high pressure liquid refrigerant, gas-liquid two-phase cold-producing medium through throttling arrangement 9 throttling step-downs becoming low-temp low-pressure, by inlet chamber external heat exchanger 4 again behind the 4th check valve 19, become the gaseous refrigerant of low-temp low-pressure in the heat of vaporization of this liquid refrigerant absorption chamber outer air, the compressor 1 of arbitrarily downgrading that cross valve 3, gas-liquid separator 12 return of flowing through again finishes heating circulation.Adopt twin-stage compression reduction hiigh pressure stage compressor exhaust temperature like this, increased considerably the degree of supercooling of liquid refrigerant, make the unit mass cold-producing medium can from air, obtain more heat, and the cold-producing medium of intercooler branch road has also increased the refrigerant flow of indoor heat exchanger, thereby has improved the coefficient of performance and the heating capacity of the operation of air source heat pump worst cold case.
Oil balancing device: the pasta that keeps hiigh pressure stage compressor and low-pressure stage compressor and is communicated with the bottom of two compressors on same horizontal plane, with equal solenoid 20 gauge taps.Under cooling condition and single-stage heating condition situation, all solenoid 20 is held open.Under the twin-stage heating condition, equal solenoid 20 is closed when unit is opened; When source pump is shut down, open equal solenoid number minute, and then close equal solenoid.
Embodiment 2 is by two low-pressure stage compressors and the twin-stage compression low-temperature air source heat pump device that the hiigh pressure stage compressor is formed:
For Fig. 1, present embodiment has increased a low-pressure stage compressor again in low-pressure stage, thereby makes system become the twin-stage the realized compression low-temperature air source heat pump device of three parallel connections, can adapt to the cooling and heating load requirement of bigger excursion.The operation principle of heat pump is as follows under different operating modes:
First magnetic valve 15 and second magnetic valve 17 are all closed during cooling condition, its operation principle is: (1) is under the summer cooling condition, if refrigerating capacity is not very big, when only needing to open a compressor, can between three compressors, select the proper compression machine according to actual chilling requirement size.If open low-pressure stage compressor 1 or 22, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by low-pressure stage compressor 1 or 22, enter cross valve 3 through the 5th check valve 2, arrive gas-liquid separator 12 through opening the identical route of low-pressure stage compressor then with embodiment 1 cooling condition, return low-pressure stage compressor 1 or 22, finish kind of refrigeration cycle.(2) if open hiigh pressure stage compressor 13, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by hiigh pressure stage compressor 13, through the cross valve 3 route arrival gas-liquid separator 12 that process is identical with unlatching low-pressure stage compressor 1 or 22 o'clock then, return compressor 13 through the 6th check valve 14 again, finish kind of refrigeration cycle.(3) if chilling requirement is bigger, in the time of need opening two compressors simultaneously, have three kinds of modes to select this moment: open compressor 1,22 or 1,13 or 13,22.To open compressor 1 and 13 is example, the gaseous refrigerant of low-temp low-pressure is divided into two-way and enters low-pressure stage compressor 1 and hiigh pressure stage compressor 13 respectively, before cross valve 3, converge through the 5th check valve 2 and gaseous refrigerant by the gaseous refrigerant of the HTHP of low-pressure stage compressor 1 compression by the HTHP of hiigh pressure stage compressor 13 compressions, then through arriving gas-liquid separator 12 with unlatching low-pressure stage compressor 1 or 22 o'clock identical routes, this moment, the gaseous refrigerant of low-temp low-pressure was divided into two-way, one the tunnel directly returns compressor 1, another Lu Jingdi six check valves 14 return hiigh pressure stage compressor 13, finish kind of refrigeration cycle.(4) if chilling requirement is very big, need open three compressors simultaneously, this moment, the gaseous refrigerant of low-temp low-pressure was divided into three the tunnel, enter low-pressure stage compressor 1 respectively, low-pressure stage compressor 22 and hiigh pressure stage compressor 13, gaseous refrigerant by low-pressure stage compressor 1 and 22 HTHPs that compress converges before the 5th check valve 2, converge before cross valve 3 through the gaseous refrigerant of the 5th check valve 2 with the HTHP of compressor 13 compressions, then through arriving gas-liquid separator 12 with unlatching low-pressure stage compressor 1 or 22 o'clock identical routes, this moment, the gaseous refrigerant of low-temp low-pressure was divided into three the tunnel, one the tunnel returns low-pressure stage compressor 1, one the tunnel returns low-pressure stage compressor 22, also have one the tunnel to return hiigh pressure stage compressor 13, finish kind of refrigeration cycle through the 6th check valve 14.
First magnetic valve 15 and second magnetic valve 17 are all closed during the single-stage heating condition, and its operation principle is: (1) is under the single-stage heating condition, if calorific requirement is not very big, when only needing to open a compressor, can select compressor operation.To open low-pressure stage compressor 1 or 22 is example, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by compressor 1 or 22, enter cross valve 3 through the 5th check valve 2, arrive gas-liquid separator 12 through opening the identical route of low-pressure stage compressor then with embodiment 1 single-stage heating condition, return compressor 1 or 22, finish heating circulation.(2) if what open is hiigh pressure stage compressor 13, the gaseous refrigerant of low-temp low-pressure is collapsed into the gaseous refrigerant of HTHP by compressor 13, through the cross valve 3 route arrival gas-liquid separator 12 that process is identical with unlatching low-pressure stage compressor 1 or 22 o'clock then, return compressor 13 through the 6th check valve 14 again, finish heating circulation.(3) if heating capacity is bigger, in the time of need opening two compressors simultaneously, have three kinds of modes to select this moment: open compressor 1,22 or 1,13 or 13,22.To open compressor 1 and 13 is example, the gaseous refrigerant of low-temp low-pressure is divided into two-way, enter compressor 1 and compressor 13 respectively, before cross valve 3, converge through the 5th check valve 2 and gaseous refrigerant by the gaseous refrigerant of the HTHP of compressor 1 compression by the HTHP of compressor 13 compressions, then through arriving gas-liquid separator 12 with unlatching low-pressure stage compressor 1 or 22 o'clock identical routes, this moment, the gaseous refrigerant of low-temp low-pressure was divided into two-way, one the tunnel directly returns compressor 1, another Lu Jingdi six check valves 14 return compressor 13, finish heating circulation.(4) if required heating capacity is very big, in the time of need opening three compressors simultaneously, the gaseous refrigerant of low-temp low-pressure was divided into three the tunnel and entered compressor 1 respectively this moment, compressor 22 and compressor 13, gaseous refrigerant by compressor 1 and 22 HTHPs that compress converges before the 5th check valve 2, converge before cross valve 3 through the gaseous refrigerant of the 5th check valve 2 with the HTHP of compressor 13 compressions, then through arriving gas-liquid separator 12 with unlatching low-pressure stage compressor 1 or 22 o'clock identical routes, this moment, the gaseous refrigerant of low-temp low-pressure was divided into three the tunnel, one the tunnel returns compressor 1, one the tunnel returns compressor 13, also have one the tunnel to return compressor 13, finish heating circulation through the 6th check valve 14.
The operation principle of twin-stage heating condition: under the low situation of outdoor temperature, change this device into double stage compresses hot pump in low temp system in the winter time, this moment, first magnetic valve 15 and second magnetic valve 17 were all open-minded.The gaseous refrigerant of low-temp low-pressure is divided into two-way, is collapsed into the gaseous refrigerant of medium temperature and medium pressure respectively by compressor 1 and 22, converges after second magnetic valve 15 flows to the hiigh pressure stage compressor suction duct, and other are with the route of twin-stage heating condition among the embodiment 1.
Oil balancing device: the pasta that keeps three compressors and is communicated with the bottom of three compressors on same horizontal plane, and equal solenoid 20 gauge taps are set on the oil equalizing pipe of compressor 13 and compressor 22.Under cooling condition and single-stage heating condition situation, all solenoid 20 is held open.Under the twin-stage heating condition: equal solenoid 20 is closed when unit is opened, and when source pump is shut down, opens equal solenoid number minute, and then closes equal solenoid.
Claims (6)
1, a kind of compressor low-temperature air source heat pump device in parallel of realizing the twin-stage compression comprises:
The ordinary hot pump installation of the compressor parallel that constitutes by low-pressure stage compressor (1), hiigh pressure stage compressor (13), cross valve (3), outdoor air cooling heat exchanger (4), first check valve (6), second check valve (10), the 3rd check valve (18), the 4th check valve (19), high pressure reservoir (7), throttling arrangement (9), indoor heat exchanger (11), gas-liquid separator (12) and connecting pipe and be installed in the refrigerant loop of ordinary hot pump installation of described compressor parallel in the middle of the cooling branch road; The cooling branch road comprises first magnetic valve (17), middle throttling arrangement (16) and the intercooler (21) by series connection successively in the middle of described; It is characterized in that, also comprise:
Between low-pressure stage compressor (1) outlet and hiigh pressure stage compressor (13) inlet, the path that comprises second magnetic valve (15) is set;
On the gas exhaust piping of low-pressure stage compressor (1), low-pressure stage compressor (1) and comprise the tie point of path of second magnetic valve (15) and the tie point of the gas exhaust piping of low-pressure stage compressor (1) and hiigh pressure stage compressor (13) between, the 5th check valve (2) is set;
On the suction line of hiigh pressure stage compressor (13), between the tie point of the suction line of hiigh pressure stage compressor (13) and low-pressure stage compressor (1) and hiigh pressure stage compressor (13) and middle cooling branch road institute tie point, the 6th check valve (14) is set.
2, by the described compressor low-temperature air source heat pump device in parallel of realizing the twin-stage compression of claim 1, it is characterized in that described low-pressure stage compressor and hiigh pressure stage compressor are the compressor of identical or different model.
3, by the described compressor low-temperature air source heat pump device in parallel of realizing the twin-stage compression of claim 1, it is characterized in that described low-pressure stage compressor is 1: 1 with the quantity ratio of hiigh pressure stage compressor; 2: 1; 3: 1 or 5: 2.
4, by the described compressor low-temperature air source heat pump device in parallel of realizing the twin-stage compression of claim 1, it is characterized in that described low-pressure stage compressor and hiigh pressure stage compressor are constant volume compressor or variable conpacitance compressor.
5, by the described compressor low-temperature air source heat pump device in parallel of realizing the twin-stage compression of claim 1, it is characterized in that described indoor heat exchanger (11) is air cooling heat exchanger or water cooling heat exchanger.
6, by the described compressor low-temperature air source heat pump device in parallel of realizing the twin-stage compression of claim 1, it is characterized in that described throttling arrangement (9) and middle throttling arrangement (16) are heating power expansion valve, electric expansion valve or capillary.
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| CN 200520136550 CN2884061Y (en) | 2005-12-23 | 2005-12-23 | Warmmer air source heat-pump device of parallel compressor able to achieve tow-stage compression |
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