CN104344589A - Air source heat pump system and control method thereof - Google Patents
Air source heat pump system and control method thereof Download PDFInfo
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- CN104344589A CN104344589A CN201310311613.2A CN201310311613A CN104344589A CN 104344589 A CN104344589 A CN 104344589A CN 201310311613 A CN201310311613 A CN 201310311613A CN 104344589 A CN104344589 A CN 104344589A
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- stage compressor
- pressure stage
- oil
- high pressure
- heat pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
The invention discloses an air source heat pump system and a control method thereof. The air source heat pump system comprises a four-way valve device, a high pressure compressor and a low pressure compressor. A four-way valve exhaust port of the four-way valve device is connected with a first exhaust port of the high pressure compressor and a second exhaust port of the low pressure compressor, a four-way valve air suction port of the four-way valve device is connected with a first air suction port of the high pressure compressor and a second air suction portion of the low pressure air compressor, the second air exhaust port of the low pressure air compressor is further connected with the first air suction port of the high pressure air compressor, and an exhaust stop valve is arranged between the second air exhaust port and the first air suction port. By means of the air source heat pump system, switching of three operation modes of single machine operation, double machine operation and two-stage series connection operation can be achieved, and the operation mode of the system can be adjusted according to the actual working condition. The system and the method are especially applicable to the low temperature heating working condition in the Northern area, and the system has higher operation efficiency.
Description
Technical field
The present invention relates to air source heat pump system technical field, particularly relate to a kind of air source heat pump system and control method thereof.
Background technology
At present, be in the unit helical-lobe compressor air source heat pump system of heating mode when environment temperature is lower, helical-lobe compressor inspiratory volume is little, inspiratory flow is little, motor cooling is not enough, delivery temperature and lubricating oil temperature high, rotor of helical lobe compressor internal leakage increases, add that helical-lobe compressor operates in severe overvoltage contracting under High Pressure Difference operating mode and runs the operational efficiency caused and worsen, make unit helical-lobe compressor air source heat pump system when practical application, be difficult to be readily applied to winter environment temperature lower than the area of-10 DEG C.
Although adopt the economizer air compensation that the unit helical-lobe compressor air source heat pump system of band second vapor injection can provide low ring temperature to a certain degree to heat, improve the capacity of helical-lobe compressor, and then improve heating capacity and the heating efficiency of whole system, but under low ambient temperature and high supply water temperature operating mode, under helical-lobe compressor remains and operates in overcompression condition, rotor internal leakage is large, inspiratory flow and motor cooling still deficiency, heating efficiency is poor, and also has adverse influence to the service life of helical-lobe compressor.
Therefore, need a kind of air source heat pump system and control method thereof, to solve problems of the prior art at least in part.
Summary of the invention
In order to overcome above-mentioned the deficiencies in the prior art, the invention provides a kind of air source heat pump system, comprise four-way valve device, high pressure stage compressor and low-pressure stage compressor, wherein, the cross valve exhaust outlet of described four-way valve device is connected with the second exhaust port of the first row gas port of described high pressure stage compressor and described low-pressure stage compressor, the cross valve air entry of described four-way valve device is connected with the second air entry of the first air entry of described high pressure stage compressor and described low-pressure stage compressor, and between described cross valve air entry and described first air entry, be provided with breather cheek valve, the second exhaust port of described low-pressure stage compressor is also connected with the first air entry of described high pressure stage compressor, and is provided with discharge line valve between described second exhaust port and described first air entry.
Preferably, this air source heat pump system also comprises oil eliminator, wherein, the first row gas port of described high pressure stage compressor is connected with the entrance of described oil eliminator, and the first exhaust check valve is provided with between described first row gas port and described entrance, the oil-out of described oil eliminator is connected with the first oil-in of described high pressure stage compressor; The second exhaust port of described low-pressure stage compressor is connected with the described entrance of described oil eliminator, and the second exhaust check valve is provided with between described second exhaust port and described entrance, the described oil-out of described oil eliminator is connected with the second oil-in of described low-pressure stage compressor; The cross valve exhaust outlet of described four-way valve device is connected with the refrigerant outlet of described oil eliminator, to receive the refrigerant gas that described oil eliminator is discharged.
Preferably, at the described oil-out of described oil eliminator and be provided with oil cooler between described first oil-in and described second oil-in.
Preferably, described oil cooler is plate-type oil cooler, between the oil transportation mouth and described second oil-in of described oil cooler, be provided with bypass solenoid valve and differential pressure control valve, described bypass solenoid valve and described differential pressure control valve are arranged in parallel, for controlling the oil pressure of described low-pressure stage compressor.
Preferably, between described oil-out and described oil cooler, be also arranged in parallel oil pump and oil pump check valve, time not enough for the pressure reduction between described oil eliminator and described first oil-in and described second oil-in, force fuel feeding.
Preferably, this air source heat pump system also comprised cold mould economizer, and described the first blowing mouth crossing cold mould economizer is connected with the first air entry of described high pressure stage compressor.
Preferably, this air source heat pump system also comprised cold mould economizer, described the first blowing mouth crossing cold mould economizer is connected with the first gas supplementing opening of described high pressure stage compressor and the second gas supplementing opening of described low-pressure stage compressor, or described the first blowing mouth crossing cold mould economizer is connected with the first air entry of described high pressure stage compressor.
Preferably, this air source heat pump system also comprises Flash Type economizer, and the second blowing mouth of described Flash Type economizer is connected with the first air entry of described high pressure stage compressor; Described the first blowing mouth crossing cold mould economizer is connected with the first gas supplementing opening of described high pressure stage compressor and the second gas supplementing opening of described low-pressure stage compressor.
Preferably, this air source heat pump system also comprises two and crosses cold mould economizer, the first blowing mouth crossing cold mould economizer described in one of them is connected with the first gas supplementing opening of described high pressure stage compressor and the second gas supplementing opening of described low-pressure stage compressor, and the first blowing mouth crossing cold mould economizer described in another is connected with the first air entry of described high pressure stage compressor.
Preferably, this air source heat pump system also comprises air side heat exchanger and device for drying and filtering, and described device for drying and filtering is arranged between described air side heat exchanger and described mistake cold mould economizer.
Preferably, this air source heat pump system also comprises oil return injector and water-side heat, the injection air inlet of described oil return injector is connected with the top vent of described oil eliminator, the injection oil-in of described oil return injector is connected with the bottom oil drain out of described water-side heat, and the injection oil drain out of described oil return injector is connected with described cross valve air entry.
Preferably, described four-way valve device comprises the first cross valve and the second cross valve, and described first cross valve and described second four-way valve connection in parallel are arranged.
Preferably, high pressure stage compressor and described low-pressure stage compressor are screw compressor.
Preferably, described high pressure stage compressor and described low-pressure stage compressor are scroll compressor.
Present invention also offers a kind of control method of air source heat pump system, for above-mentioned air source heat pump system, comprise the following steps: start described high pressure stage compressor or described low-pressure stage compressor, carry out unit running, or start described high pressure stage compressor and described low-pressure stage compressor carries out double parallel running simultaneously; Control air source heat pump system according to actual condition and change described high pressure stage compressor and the running of described low-pressure stage compressor double parallel into by described unit running, or change described high pressure stage compressor and the running of described low-pressure stage compressor double stage tandem into, or control described air source heat pump system according to actual condition to be operated by described double parallel and change described unit into and operate or change described double stage tandem into and operate, or control described air source heat pump system according to actual condition and to be operated by described double stage tandem and change described unit into and operate or change described double parallel into and operate.
Preferably, first start high pressure stage compressor, carry out described unit running.
Preferably, when being converted to described high pressure stage compressor by described high pressure stage compressor unit and described low-pressure stage compressor double parallel operates, keeping discharge line valve to close, starting low-pressure stage compressor, opening bypass solenoid valve and shut off differential pressure control valve.
Preferably, when being converted to described high pressure stage compressor by described high pressure stage compressor unit and described low-pressure stage compressor double stage tandem operates, opening discharge line valve, starting low-pressure stage compressor, close bypass solenoid valve and starting differential pressure control valve.
According to air source heat pump system of the present invention, the running of compressor unit, the running of compressor double parallel and compressor double stage tandem can be realized to operate the switching of three kinds of methods of operation, thus be able to the method for operation of the Operating condition adjustment system according to reality, be particularly useful for the operating mode of northern low-temperature heating, the system of guarantee has higher operational efficiency.
In summary of the invention part, introduce the concept of a series of reduced form, this will further describe in detailed description of the invention part.Content part of the present invention does not also mean that the key feature and essential features that will attempt to limit technical scheme required for protection, does not more mean that the protection domain attempting to determine technical scheme required for protection.
Below in conjunction with accompanying drawing, describe advantages and features of the invention in detail.
Accompanying drawing explanation
Following accompanying drawing of the present invention in this as a part of the present invention for understanding the present invention.Shown in the drawings of embodiments of the present invention and description thereof, be used for explaining principle of the present invention.In the accompanying drawings,
Fig. 1 is the system composition schematic diagram according to the air source heat pump system of one embodiment of the present invention;
Fig. 2 is the system composition schematic diagram according to the air source heat pump system of another embodiment of the present invention;
Fig. 3 is the system composition schematic diagram according to the air source heat pump system of another embodiment of the present invention;
Fig. 4 is the system composition schematic diagram according to the air source heat pump system of the present invention's the 4th kind of embodiment;
Fig. 5 is the system composition schematic diagram according to the air source heat pump system of the present invention's the 5th kind of embodiment;
Fig. 6 is the system composition schematic diagram according to the air source heat pump system of the present invention's the 6th kind of embodiment;
Fig. 7 is the system composition schematic diagram according to the air source heat pump system of the present invention's the 7th kind of embodiment;
Fig. 8 is the system composition schematic diagram according to the air source heat pump system of the present invention's the 8th kind of embodiment;
Fig. 9 is converted to by high pressure stage compressor unit the flow chart that high pressure stage compressor and low-pressure stage compressor double parallel operate according to one embodiment of the present invention;
Figure 10 is converted to by high pressure stage compressor unit the flow chart that high pressure stage compressor and low-pressure stage compressor double stage tandem operate according to one embodiment of the present invention.
Detailed description of the invention
In the following description, a large amount of concrete details is given to provide more thorough understanding of the invention.But, it will be apparent to one skilled in the art that the present invention can be implemented without the need to these details one or more.In other example, in order to avoid obscuring with the present invention, technical characteristics more well known in the art are not described.
In order to thoroughly understand the present invention, by following description, detailed structure is proposed.Obviously, execution of the present invention is not limited to the specific details that those skilled in the art has the knack of.Preferred embodiment of the present invention is described in detail as follows, but except these are described in detail, the present invention can also have other embodiments.
The invention discloses a kind of air source heat pump system, its system diagram as depicted in figs. 1 and 2, mainly comprises four-way valve device, high pressure stage compressor 30 and low-pressure stage compressor 50.Shown in Fig. 1 is have employed independent high pressure stage compressor 30 and low-pressure stage compressor 50, shown in Fig. 2 is then have employed high pressure stage compressor group and low-pressure stage compressor bank, each high pressure stage compressor group comprises multiple high pressure stage compressor 30, and each low-pressure stage compressor bank comprises multiple low-pressure stage compressor 50.
Continue to see figures.1.and.2, the cross valve exhaust outlet of four-way valve device is connected with the second exhaust port 51 of the first row gas port 31 of high pressure stage compressor 30 and low-pressure stage compressor 50, to receive the refrigerant gas doped with lubricating oil.The cross valve air entry of four-way valve device is connected with the second air entry 53 of the first air entry 33 of high pressure stage compressor 30 and low-pressure stage compressor 50, to provide refrigerant gas to high pressure stage compressor 30 and low-pressure stage compressor 50, and be provided with breather cheek valve 32 between cross valve air entry and the first air entry 33.In addition, in order to realize connecting of low-pressure stage compressor 50 and high pressure stage compressor 30, the second exhaust port 51 of low-pressure stage compressor 50 is also connected with the first air entry 33 of high pressure stage compressor 30.Particularly, as can be seen from Fig. 1 and Fig. 2, refrigerant gas is introduced into pipeline 1002 after being discharged by the second exhaust port 51 of low-pressure stage compressor 50, and subsequently, pipeline 1002 is divided into pipeline 1003 and pipeline 1004.Pipeline 1003 is connected with pipeline 1008 and converges for pipeline 1009 with pipeline 1007, and pipeline 1004 is connected to the first air entry 33 of high pressure stage compressor 30, and is also provided with discharge line valve 52 on pipeline 1004.Opening by discharge line valve 52 series connection realizing two compressors, then needing when not needing two compressor series operations discharge line valve 52 to close.
According to air source heat pump system of the present invention, the running of compressor unit, the running of compressor double parallel and compressor double stage tandem can be realized to operate the switching of three kinds of methods of operation, thus be able to the method for operation of the Operating condition adjustment system according to reality, be particularly useful for the operating mode of northern low-temperature heating, the system of guarantee has higher operational efficiency.
One of the present invention preferred embodiment in, as shown in Figures 3 to 8, further provided with oil eliminator 10.The first row gas port 31 of high pressure stage compressor 30 is connected with the entrance 11 of oil eliminator 10, to carry the refrigerant gas doped with lubricating oil to oil eliminator 10.In order to reach the object preventing refrigerant gas from flowing backwards, also on the pipeline 1007 connecting first row gas port 31 and entrance 11, be provided with the first exhaust check valve 39.And in order to make isolated lubricating oil in oil eliminator 10 return high pressure stage compressor 30, the oil-out 15 of oil eliminator 10 is connected with the first oil-in 37 of high pressure stage compressor 30.
The second exhaust port 51 of low-pressure stage compressor 50 is also connected with the entrance 11 of oil eliminator 10, the refrigerant gas doped with lubricating oil is carried equally to oil eliminator 10, and be provided with the second exhaust check valve 59 on the pipeline 1008 connecting second exhaust port 51 and entrance 11, thus prevent refrigerant gas from flowing back to low-pressure stage compressor 50.Pipeline 1008 can converge for pipeline 1009 is to oil eliminator 10 refrigerant conveying gas with aforesaid pipeline 1007.In addition, the oil-out 15 of oil eliminator 10 is also connected with the second oil-in 57 of low-pressure stage compressor 50, lubricates to be delivered in low-pressure stage compressor 50 by lubricating oil.
The cross valve exhaust outlet of four-way valve device is connected with the refrigerant outlet 13 of oil eliminator 10, to receive the refrigerant gas that oil eliminator 10 is discharged, the cross valve air entry of this four-way valve device is connected with the second air entry 53 of the first air entry 33 of high pressure stage compressor 30 and low-pressure stage compressor 50, to provide refrigerant gas to high pressure stage compressor 30 and low-pressure stage compressor 50, and be provided with breather cheek valve 32 between cross valve air entry and the first air entry 33.
Preferably, four-way valve device can adopt the first cross valve 70 shown in Fig. 3 and the second cross valve 90 to compose in parallel, and also as Suo Shi Fig. 4 to 8, only can adopt first cross valve 70.The parallel connection of two cross valves, namely be that the first cross valve exhaust outlet D1 of the first cross valve 70 is connected with the second cross valve exhaust outlet D2 of the second cross valve 90, first cross valve air entry S 1 of the first cross valve 70 is connected with the second cross valve air entry S2 of the second cross valve 90, first condenser interface C1 of the first cross valve 70 is connected with the second condenser interface C2 of the second cross valve 90, and the first evaporimeter interface E1 of the first cross valve 70 is connected with the second evaporimeter interface E2 of the second cross valve 90.This mode together used by two four-way valve connection in parallel, can be only that two cross valves in parallel are equipped with a set of matching component (such as check valve etc.), save the cost of whole system.Here it should be noted that, cross valve exhaust outlet do not refer to cross valve exhaust outlet be used to be vented, and refer to the interface of other equipment that cross valve exhaust outlet connects be used to be vented.Such as in FIG, the refrigerant outlet 13 of oil eliminator 10 that connects of the first cross valve exhaust outlet D1 is for discharging refrigerant gas.Cross valve air entry is also in like manner, repeats no more.Condenser interface and evaporimeter interface are then be respectively used to be connected condenser and evaporimeter.
Preferably, high pressure stage compressor 30 and low-pressure stage compressor 50 can adopt screw compressor (as shown in Figures 3 to 8), particularly frequency conversion type helical-lobe compressor.Because the control of frequency conversion type helical-lobe compressor is more accurate, the operational efficiency of whole system can be improved further.
Equally preferably, high pressure stage compressor 30 and low-pressure stage compressor 50 can also adopt scroll compressor (as depicted in figs. 1 and 2).Screw compressor has the advantages such as vibration is little, reliability is high and noise is little, contributes to system stability and reliably operates.
In another preferred embodiment of the present invention, as shown in Figures 3 to 6, between the oil-out 15 of oil eliminator 10 and the second oil-in 57 of the first oil-in 37 of high pressure stage compressor 30 and low-pressure stage compressor 50, oil cooler 20 is provided with.Particularly, through entering oil cooler 20 by pipeline 1017 after lubricating oil flows out from the oil-out 15 of oil eliminator 10, meanwhile, from the pipeline 1023 being positioned at water-side heat 83 upstream, liquid refrigerant 1016 is introduced oil cooler 20 by the road, carry out heat exchange with lubricating oil.Lubricating oil is contrary with the flow direction of liquid refrigerant in oil cooler 20, to realize better heat transfer effect.Flow out from the oil transportation mouth 21 of oil cooler 20 after the lubricating oil cooling of heat exchange, shunting subsequently enters pipeline 1018 and pipeline 1019.Lubricating oil in pipeline 1018 flows into the first oil-in 37 of high pressure stage compressor 30, and the lubricating oil in pipeline 1019 then flows into the second oil-in 57 of low-pressure stage compressor 50.Lubricating oil through cooling is introduced in two compressors, being conducive to when two compressors run simultaneously (can be parallel running, also can be series operation) effectively reduce temperature of rotor and delivery temperature, ensure that two compressors reliably run.
Further preferably, oil cooler 20 can adopt plate-type oil cooler, and still as shown in Figures 3 to 6, between the oil transportation mouth 21 and the second oil-in 57 of low-pressure stage compressor 50 of oil cooler 20, namely on pipeline 1019, be provided with bypass solenoid valve 54 and differential pressure control valve 56.It can also be seen that from Fig. 3 to Fig. 6, bypass solenoid valve 54 and differential pressure control valve 56 are arranged in parallel, for controlling the oil pressure of low-pressure stage compressor 50.Particularly, open bypass solenoid valve 54 and shut off differential pressure control valve 56, for low-pressure stage compressor 50 isolated operation or with during high pressure stage compressor 30 parallel running to low-pressure stage compressor 50 fuel feeding.Close bypass solenoid valve 54 and starting differential pressure control valve 56 then for low-pressure stage compressor 50 with during high pressure stage compressor 30 series operation to low-pressure stage compressor 50 fuel feeding, to ensure that low-pressure stage compressor 50 has the charge oil pressure of the pressure at expulsion a little less than low-pressure stage compressor 50.The adjustment of differential pressure control valve 56 pairs of charge oil pressures with the pressure at expulsion of low-pressure stage compressor 50 for reference pressure, by the pressure difference of setting, be reduced to the charge oil pressure of the pressure difference of setting lower than the pressure at expulsion (reference pressure) of low-pressure stage compressor 50 by the charge oil pressure of pipeline 1019 before the valve of differential pressure control valve 56, and the impulse mouth 561 that the pressure at expulsion of low-pressure stage compressor 50 is connected on pipeline 1002 by differential pressure control valve 56 obtains.
Equally preferably, as shown in Figures 3 to 6, oil pump 89 and oil pump check valve 891 can also be set between the oil-out 15 of oil eliminator 10 and oil cooler 20, to carry out pressure fuel feeding by starting oil pump 89 to high pressure stage compressor 30 and low-pressure stage compressor 50 at oil eliminator 10 and when there is the situation of charge oil pressure deficiency between the first oil-in 37 and the second oil-in 57.
Air source heat pump system provided by the invention, when bringing into operation, such as, preferentially opens high pressure stage compressor 30.Now, discharge line valve 52, bypass solenoid valve 54, differential pressure control valve 56 and other be arranged on and be all in closed condition towards the valve on the pipeline of low-pressure stage compressor 50.
High pressure stage compressor 30 is upon actuation from pipeline 1005 air-breathing, and breather cheek valve 32 plays the effect of forward conduction.The refrigerant gas that high pressure stage compressor 30 is discharged enters oil eliminator 10 through the first exhaust check valve 39 and pipeline 1007, downstream pressure due to the second exhaust check valve 59 be connected with low-pressure stage compressor 50 is the pressure at expulsion of high pressure stage compressor 30, the upstream pressure of its second exhaust check valve 59 is the pressure of inspiration(Pi) of high pressure stage compressor 30, and pressure distribution causes the second exhaust check valve 59 oppositely check.After high pressure stage compressor 30 starts, lubricating oil flows out rear final 1018 realizations by the road to high pressure stage compressor 30 fuel feeding from the oil-out 15 of oil eliminator 10.At this moment, whole system is in the unit drive manner of only high pressure stage compressor 30 isolated operation.
When needs switch to two compressor parallel running modes, need to start low-pressure stage compressor 50.After low-pressure stage compressor 50 starts, open bypass solenoid valve 54 simultaneously, shut off differential pressure control valve 56, to realize to low-pressure stage compressor 50 fuel feeding, low-pressure stage compressor 50 is from pipeline 1001 air-breathing, and the refrigerant gas that low-pressure stage compressor 50 is discharged enters oil eliminator 10 through the second exhaust check valve 59 and pipeline 1008.Now whole system is in high pressure stage compressor 30 and low-pressure stage compressor 50 double parallel drive manner.
When needs switch to two compressor double stage tandem drive manners, need first to open discharge line valve 52.Upstream pressure due to discharge line valve 52 is the pressure of pipeline 1001, and the downstream pressure of discharge line valve 52 is the pressure of pipeline 1005, and pipeline 1001 is balance with the pressure of pipeline 1005.Therefore when discharge line valve 52 is opened time, any impact is not had on the high pressure stage compressor 30 run.Then start low-pressure stage compressor 50, low-pressure stage compressor 50, from pipeline 1001 air-breathing, is vented to pipeline 1002, and pipeline 1002 splits into pipeline 1003 and 1004 in parallel.Therefore, after low-pressure stage compressor 50 starts, the pressure of pipeline 1001 and 1006 reduces, and the pressure of pipeline 1003 and 1004 improves.The downstream pressure of the breather cheek valve 32 on pipeline 1005 is the pressure at expulsion of low-pressure stage compressor 50, and its upstream pressure is the pressure of inspiration(Pi) of low-pressure stage compressor 50, the namely pressure of pipeline 1006, and pressure distribution causes breather cheek valve 32 oppositely check.Downstream pressure due to the second exhaust check valve 59 be connected with low-pressure stage compressor 50 is the pressure at expulsion of high pressure stage compressor 30, the upstream pressure of the second check valve 59 is the pressure of inspiration(Pi) of high pressure stage compressor 30, and pressure distribution causes the second exhaust check valve 59 oppositely check.Low-pressure stage compressor 50 is due to the reverse check of the second check valve 59, cannot be vented to pipeline 1003 and 1008, can only be vented to pipeline 1004, high pressure stage compressor 30 due to the reverse check of breather cheek valve 32 cannot from pipeline 1006 air-breathing, can only from pipeline 1004 air-breathing.After low-pressure stage compressor 50 starts, starting differential pressure control valve 56 and keep closing bypass solenoid valve 54, lubricating oil flows out rear final by the road 1019 and differential pressure control valve 56 from the oil-out 15 of oil eliminator 10, realizes to low-pressure stage compressor 50 fuel feeding.Now whole system is in high pressure stage compressor 30 and low-pressure stage compressor 50 double stage tandem drive manner.
In another preferred embodiment of the present invention, do not have on the basis of oil eliminator, as illustrated in fig. 1 and 2, also for air source heat pump system was equipped with cold mould economizer 40.As can be seen from Fig. 1 and Fig. 2, the first blowing mouth 41 crossing cold mould economizer 40 is only connected with the first air entry 33 of high pressure stage compressor 30, is high pressure stage compressor 30 air feed.
The present invention another preferred embodiment in, with reference to Fig. 3 to Fig. 8, on the basis with oil eliminator 10, air source heat pump system had cold mould economizer 40.As can be seen from Fig. 3,5,6,7,8, cross the first blowing mouth 41 of cold mould economizer 40 to be connected with the second gas supplementing opening 55 of the first gas supplementing opening 35 of high pressure stage compressor 30 and low-pressure stage compressor 50, to provide tonifying Qi to high pressure stage compressor 30 and low-pressure stage compressor 50 respectively.The tonifying Qi pipeline 1011 of high pressure stage compressor 30 and the tonifying Qi pipeline 1012 of low-pressure stage compressor 50 are also provided with supporting gas supply control valve and tonifying Qi check valve, to control tonifying Qi.
Further preferably, as shown in Fig. 3,5,7,8, air source heat pump system of the present invention also has Flash Type economizer 60, and this Flash Type economizer 60 is arranged in the air source heat pump system with cold mould economizer 40.Usually, the first blowing mouth 41 now crossing cold mould economizer 40 is connected with the first gas supplementing opening 35 of high pressure stage compressor 30 and the second gas supplementing opening 51 of low-pressure stage compressor 50, provides tonifying Qi respectively to high pressure stage compressor 30 and low-pressure stage compressor 50.Flash Type economizer 60 is then connected with the first air entry 33 of high pressure stage compressor 30 by the second blowing mouth 61 of oneself, the pipeline that second blowing mouth 61 of Flash Type economizer 60 is connected with the first air entry 33 of high pressure stage compressor 30 is also provided with supporting gas supply control valve and tonifying Qi check valve, to control tonifying Qi.Under unit drive manner and double parallel drive manner, this gas supply control valve should be in closed condition all the time; Only under double stage tandem drive manner, this gas supply control valve is in open completely or specify opens aperture state.
The present invention another preferred embodiment in, as shown in Figure 6, air source heat pump system has two and crosses cold mould economizer 40, one of them is crossed the first blowing mouth 41 of cold mould economizer 40 and is connected with the second gas supplementing opening 55 of the first gas supplementing opening 35 of high pressure stage compressor 30 and low-pressure stage compressor 50, provides tonifying Qi respectively to high pressure stage compressor 30 and low-pressure stage compressor 50.First air entry 33 of another the first blowing mouth 41 and high pressure stage compressor 30 of crossing cold mould economizer 40 is connected.
Cross the confession hydraulic pressure difference that cold mould economizer 40 can ensure evaporimeter feed flow expansion valve, ensure the correct operation of valve, and realized the tonifying Qi effect of cold mould economizer 40.When system is in unit drive manner, avoid the low voltage control problem owing to causing for hydraulic pressure difference deficiency.Flash Type economizer 60 can substitute the effect of high pressure fluid reservoir and other similar fluid reservoirs so that the different effect of balanced system cold-peace heating mode refrigerant charge, under heating operation mode, the control liquid level of Flash Type economizer 60 is higher than the control liquid level under cooling operation mode, its liquid level difference is the difference of the refrigerant charge under cooling operation mode and heating operation mode, and realizes the tonifying Qi effect of Flash Type economizer 60 simultaneously.How to be connected with Flash Type economizer 60 as crossing cold mould economizer 40, and how the two is connected in total system, is all contents that those skilled in the art have known, repeats no more herein to this.
Have oil eliminator 10 above-mentioned and cross on the basis of embodiment of cold mould economizer 40, air source heat pump system is also provided with air side heat exchanger 85 and device for drying and filtering 87.Device for drying and filtering 87 is arranged on air side heat exchanger 85 and crosses between cold mould economizer 40.Device for drying and filtering 87 for carrying out drying to the refrigerant gas of discharging from air side heat exchanger 85, so that ensured in the refrigerant gas that cold mould economizer 40 obtains can not containing too much moisture.
The present invention another preferred embodiment in, as shown in Fig. 3 to Fig. 7, on the basis of embodiment with oil eliminator 10, be also provided with oil return injector 81.The injection air inlet 811 of oil return injector 81 is connected with the top vent 17 of oil eliminator 10, the injection oil-in 813 of oil return injector 81 is connected with the bottom oil drain out 831 of the water-side heat 83 of system, and the injection oil drain out 815 of oil return injector 81 is connected with cross valve air entry.Having in the embodiment of the first cross valve 70 and the second cross valve 90 shown in Fig. 3, be connected with the second cross valve air entry S2 of the first cross valve air entry S1 of the first cross valve 70 and the second cross valve 90.In the embodiment only with the first cross valve 70 (with reference to Fig. 4 to Fig. 7), be connected with the first cross valve air entry S1 of the first cross valve 70.
Orifice plate and the nozzle of taper is provided with in oil return injector 81, when the top vent 17 from oil eliminator 10 gas with certain flow velocity by the road 1014 enter after this taper orifice plate reducing pressure by regulating flow time, the negative pressuren zone also lower than the refrigerant pressure in water-side heat 83 is defined in oil return injector 81, interior lubricating oil bottom water-side heat device 83 and the mixture of cold-producing medium can 1015 be inhaled in oil return injector 81 by the road, in oil return injector 81, the lubricating oil be inhaled into and the mixture of cold-producing medium 1013 are transported in pipeline 1006 and enter the first air entry 33 of high pressure stage compressor 30 and the second air entry 53 of low-pressure stage compressor 50 by the road immediately again after the speed-raising supercharging of nozzle.Oil return injector 81 is arranged in public suction line, can be implemented in ejecting scavenge return under unit running, double parallel running and double stage tandem operation mode, realizes simple line arrangement, reliably ejecting scavenge return, automatically close under heating operation mode simultaneously.
Preferably, as shown in Fig. 3 to Fig. 7, water-side heat 83 can also be full-liquid type heat exchanger or falling-film heat exchanger.In full-liquid type heat exchanger and falling-film heat exchanger, cold-producing medium is in the outer flowing of pipe, refrigerating medium is (as water, ethylene glycol solution etc.) at Bottomhole pressure, the heat transfer efficiency of cold-producing medium outside the heat exchanger tube of shell-side is very high, and heat exchanger cost is low, and manufacturing process is simple, but need the circuit of auxiliary injector, be applicable to the refrigeration system that refrigerating capacity is large and efficiency is high.
Be preferred equally, as shown in Fig. 1,2 and 8, water-side heat 83 can also be the direct-expansion-type heat exchanger such as dry type shell and tube exchanger or plate type heat exchanger.In direct-expansion-type heat exchanger, cold-producing medium is at Bottomhole pressure, refrigerating medium is (as water, ethylene glycol solution etc.) in the outer flowing of pipe, heat transfer efficiency is lower, but compact conformation, directly adopt the mode of air-breathing oil return, eliminate the circuit of comparatively complicated auxiliary injector, be applicable to the refrigeration system that refrigerating capacity is less and efficiency requirements is low.
The invention also discloses a kind of control method of air source heat pump system.First, start high pressure stage compressor or low-pressure stage compressor, carry out unit running, or startup high pressure stage compressor and low-pressure stage compressor carry out double parallel running simultaneously.Control air source heat pump system according to actual condition subsequently and change high pressure stage compressor and the running of low-pressure stage compressor double parallel into by unit running, or change high pressure stage compressor and the running of low-pressure stage compressor double stage tandem into.Or change unit according to actual condition control air source heat pump system into by double parallel running operate or change double stage tandem running into.Or control described air source heat pump system according to actual condition to be operated by described double stage tandem and change described unit into and operate or change described double parallel into and operate.Particularly, the parameters such as testing environment temperature, supplying hot water leaving water temperature, delivery temperature, air-breathing saturation temperature and exhaust saturation temperature, compressor load percentage and compressor behavior can be passed through, any operation mode should be according to these parameters and heating capacity demand certainty annuity.
Preferably, first start high pressure stage compressor, make air source heat pump system enter unit operation mode.
When judging according to various parameter to need system to be converted to high pressure stage compressor and low-pressure stage compressor double parallel operation mode by high pressure stage compressor unit operation mode, according to the flow chart shown in Fig. 9, discharge line valve is kept to close, start low-pressure stage compressor, open bypass solenoid valve and shut off differential pressure control valve.
When judging according to various parameter to need system to be converted to high pressure stage compressor and low-pressure stage compressor double stage tandem operation mode by high pressure stage compressor unit operation mode, according to the flow chart shown in Figure 10, open discharge line valve, start low-pressure stage compressor, bypass solenoid valve is closed in starting differential pressure control valve and maintenance.
The present invention is illustrated by above-described embodiment, but should be understood that, above-described embodiment just for the object of illustrating and illustrate, and is not intended to the present invention to be limited in described scope of embodiments.In addition it will be appreciated by persons skilled in the art that the present invention is not limited to above-described embodiment, more kinds of variants and modifications can also be made according to instruction of the present invention, within these variants and modifications all drop on the present invention's scope required for protection.Protection scope of the present invention defined by the appended claims and equivalent scope thereof.
Claims (18)
1. an air source heat pump system, is characterized in that, comprises four-way valve device, high pressure stage compressor (30) and low-pressure stage compressor (50), wherein,
The cross valve exhaust outlet of described four-way valve device is connected with the second exhaust port (51) of the first row gas port (31) of described high pressure stage compressor (30) and described low-pressure stage compressor (50), the cross valve air entry of described four-way valve device is connected with second air entry (53) of first air entry (33) of described high pressure stage compressor (30) and described low-pressure stage compressor (50), and is provided with breather cheek valve (32) between described cross valve air entry and described first air entry (33);
The second exhaust port (51) of described low-pressure stage compressor (50) is also connected with first air entry (33) of described high pressure stage compressor (30), and is provided with discharge line valve (52) between described second exhaust port (51) and described first air entry (33).
2. according to air source heat pump system according to claim 1, it is characterized in that, also comprise oil eliminator (10), wherein,
The first row gas port (31) of described high pressure stage compressor (30) is connected with the entrance (11) of described oil eliminator (10), and the first exhaust check valve (39) is provided with between described first row gas port (31) and described entrance (11), the oil-out (15) of described oil eliminator (10) is connected with first oil-in (37) of described high pressure stage compressor (30);
The second exhaust port (51) of described low-pressure stage compressor (50) is connected with the described entrance (11) of described oil eliminator (10), and the second exhaust check valve (59) is provided with between described second exhaust port (51) and described entrance (11), the described oil-out (15) of described oil eliminator (10) is connected with second oil-in (57) of described low-pressure stage compressor (50);
The cross valve exhaust outlet of described four-way valve device is connected with the refrigerant outlet (13) of described oil eliminator (10), to receive the refrigerant gas that described oil eliminator (10) is discharged.
3. according to air source heat pump system according to claim 2, it is characterized in that, at the described oil-out (15) of described oil eliminator (10) and be provided with oil cooler (20) between described first oil-in (37) and described second oil-in (57).
4. according to air source heat pump system according to claim 3, it is characterized in that, described oil cooler (20) is plate-type oil cooler, bypass solenoid valve (54) and differential pressure control valve (56) is provided with between the oil transportation mouth (21) and described second oil-in (57) of described oil cooler (20), described bypass solenoid valve (54) and described differential pressure control valve (56) are arranged in parallel, for controlling the oil pressure of described low-pressure stage compressor (50).
5. according to air source heat pump system according to claim 3, it is characterized in that, between described oil-out (15) and described oil cooler (20), be also arranged in parallel oil pump (89) and oil pump check valve (891), time not enough for the pressure reduction between described oil eliminator (10) and described first oil-in (37) and described second oil-in (57), force fuel feeding.
6. according to air source heat pump system according to claim 1, it is characterized in that, also comprised cold mould economizer (40), described the first blowing mouth (41) crossing cold mould economizer (40) is connected with first air entry (33) of described high pressure stage compressor (30).
7. according to air source heat pump system according to claim 2, it is characterized in that, also comprised cold mould economizer (40), described the first blowing mouth (41) crossing cold mould economizer (40) is connected with first gas supplementing opening (35) of described high pressure stage compressor (30) and second gas supplementing opening (55) of described low-pressure stage compressor (50), or described the first blowing mouth (41) crossing cold mould economizer (40) is connected with first air entry (33) of described high pressure stage compressor (30).
8. according to air source heat pump system according to claim 7, it is characterized in that, also comprise Flash Type economizer (60), second blowing mouth (61) of described Flash Type economizer (60) is connected with first air entry (33) of described high pressure stage compressor (30); Described the first blowing mouth (41) crossing cold mould economizer (40) is connected with first gas supplementing opening (35) of described high pressure stage compressor (30) and second gas supplementing opening (55) of described low-pressure stage compressor (50).
9. according to air source heat pump system according to claim 2, it is characterized in that, also comprise two and cross cold mould economizer (40), the first blowing mouth (41) crossing cold mould economizer (40) described in one of them is connected with first gas supplementing opening (35) of described high pressure stage compressor (30) and second gas supplementing opening (55) of described low-pressure stage compressor (50), and the first blowing mouth (41) crossing cold mould economizer (40) described in another is connected with first air entry (33) of described high pressure stage compressor (30).
10. according to the air source heat pump system according to any one of claim 7 to 9, it is characterized in that, also comprise air side heat exchanger (85) and device for drying and filtering (87), described device for drying and filtering (87) is arranged between described air side heat exchanger (85) and described mistake cold mould economizer (40).
11. according to air source heat pump system according to claim 2, it is characterized in that, also comprise oil return injector (81) and water-side heat (83), the injection air inlet (811) of described oil return injector (81) is connected with the top vent (17) of described oil eliminator (10), the injection oil-in (813) of described oil return injector (81) is connected with the bottom oil drain out (831) of described water-side heat (83), and the injection oil drain out (815) of described oil return injector (81) is connected with described cross valve air entry.
12. according to air source heat pump system according to claim 2, it is characterized in that, described four-way valve device comprises the first cross valve (70) and the second cross valve (90), and described first cross valve (70) and described second cross valve (90) are arranged in parallel.
13., according to air source heat pump system according to claim 1, is characterized in that, described high pressure stage compressor (30) and described low-pressure stage compressor (50) are screw compressor.
14., according to air source heat pump system according to claim 1, is characterized in that, described high pressure stage compressor (30) and described low-pressure stage compressor (50) are scroll compressor.
The control method of 15. 1 kinds of air source heat pump systems, is characterized in that, for the air source heat pump system according to any one of claim 1 to 14, comprises the following steps:
Start described high pressure stage compressor or described low-pressure stage compressor, carry out unit running, or start described high pressure stage compressor and described low-pressure stage compressor carries out double parallel running simultaneously;
Control air source heat pump system according to actual condition and change described high pressure stage compressor and the running of described low-pressure stage compressor double parallel into by described unit running, or change described high pressure stage compressor and the running of described low-pressure stage compressor double stage tandem into, or control described air source heat pump system according to actual condition to be operated by described double parallel and change described unit into and operate or change described double stage tandem into and operate, or control described air source heat pump system according to actual condition and to be operated by described double stage tandem and change described unit into and operate or change described double parallel into and operate.
16., according to control method according to claim 15, is characterized in that, first start high pressure stage compressor, carry out described unit running.
17. according to control method according to claim 16, it is characterized in that, when being converted to described high pressure stage compressor by described high pressure stage compressor unit and described low-pressure stage compressor double parallel operates, discharge line valve is kept to close, start low-pressure stage compressor, open bypass solenoid valve and shut off differential pressure control valve.
18. according to control method according to claim 16, it is characterized in that, when being converted to described high pressure stage compressor by described high pressure stage compressor unit and described low-pressure stage compressor double stage tandem operates, open discharge line valve, start low-pressure stage compressor, close bypass solenoid valve and starting differential pressure control valve.
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| CN104696197A (en) * | 2015-03-20 | 2015-06-10 | 马鞍山市博浪热能科技有限公司 | Check valve and compressor system with same |
| CN107514832A (en) * | 2017-09-21 | 2017-12-26 | 无锡职业技术学院 | A kind of low-temperature air-cooling hot screw pump system |
| CN107702369A (en) * | 2017-10-19 | 2018-02-16 | 无锡职业技术学院 | The changeable low-temperature air-cooling heat pump system of a kind of direct-connected twin-stage and double parallel |
| CN107860146A (en) * | 2017-10-19 | 2018-03-30 | 无锡职业技术学院 | A kind of control method of air source heat pump system |
| CN108518892A (en) * | 2018-05-03 | 2018-09-11 | 中国科学院理化技术研究所 | Air supply control device based on air source heat pump system and control method thereof |
| CN110470067A (en) * | 2018-05-11 | 2019-11-19 | 松下冷链（大连）有限公司 | A kind of carbon dioxide refrigerant two-stage pressurization convertible device in parallel with single-stage |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104696197A (en) * | 2015-03-20 | 2015-06-10 | 马鞍山市博浪热能科技有限公司 | Check valve and compressor system with same |
| CN104696197B (en) * | 2015-03-20 | 2017-05-17 | 马鞍山市博浪热能科技有限公司 | Compressor system with check valve |
| CN107514832A (en) * | 2017-09-21 | 2017-12-26 | 无锡职业技术学院 | A kind of low-temperature air-cooling hot screw pump system |
| CN107702369A (en) * | 2017-10-19 | 2018-02-16 | 无锡职业技术学院 | The changeable low-temperature air-cooling heat pump system of a kind of direct-connected twin-stage and double parallel |
| CN107860146A (en) * | 2017-10-19 | 2018-03-30 | 无锡职业技术学院 | A kind of control method of air source heat pump system |
| CN108518892A (en) * | 2018-05-03 | 2018-09-11 | 中国科学院理化技术研究所 | Air supply control device based on air source heat pump system and control method thereof |
| CN108518892B (en) * | 2018-05-03 | 2023-11-07 | 中国科学院理化技术研究所 | Air source heat pump system-based air supply control device and control method thereof |
| CN110470067A (en) * | 2018-05-11 | 2019-11-19 | 松下冷链（大连）有限公司 | A kind of carbon dioxide refrigerant two-stage pressurization convertible device in parallel with single-stage |
| CN113370751A (en) * | 2021-07-26 | 2021-09-10 | 上海柯诺威新能源科技有限公司 | Electric vehicle whole vehicle thermal management system and control method thereof |
| CN113370751B (en) * | 2021-07-26 | 2022-07-12 | 上海柯诺威新能源科技有限公司 | Whole vehicle thermal management system of electric vehicle and control method thereof |
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