CN1158973A - Heat pump system driven by engine - Google Patents
Heat pump system driven by engine Download PDFInfo
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- CN1158973A CN1158973A CN 96101436 CN96101436A CN1158973A CN 1158973 A CN1158973 A CN 1158973A CN 96101436 CN96101436 CN 96101436 CN 96101436 A CN96101436 A CN 96101436A CN 1158973 A CN1158973 A CN 1158973A
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Abstract
The heat pump system with high heating efficiency corresponding to the number of operated indoor heat exchangers includes engine-driven compressor; refrigerant circulating loop with expansion valve, indoor heat exchanger and outdoor heat exchanger; cooling-water circulating loop for engine-cooling water with exhaust heat exchanger; and a controller which makes the pressure of refrigerant at high-pressure side constant and independent of the number of operated indoor heat exchangers.
Description
The present invention relates to when the heating running, absorb the engine driving type heat pump apparatus of the used heat of engine as the evaporation heat of refrigerant.
Fig. 8 is the fundamental circuit structure chart of engine driving type heat pump apparatus when the heating running, and Fig. 9 is the Mo Liai figure (P-i line chart) that represents the refrigerant state variation respectively.
At this, the basic circulation when the heating running is described.
During by engine 1 drive compression machine 2,1. state (pressure P as shown in Figure 9
1, enthalpy i
1) gas phase refrigerant compressed by compressor 2, become state (pressure P 2. shown in Fig. 9
2, enthalpy i
2) high temperature, the refrigerant of high pressure.And this moment compressor 2 desired power (compression heat) AL with (i
2-i
1) expression.
Above-mentioned HTHP refrigerant has been imported into the indoor heat converter 7 (hereinafter referred to as indoor set) of condenser effect, emits heat of condensation Q2 and is liquefied to room air at this.3. state (pressure P among the state of the liquid phase refrigerant by indoor set 7 such as Fig. 9
2, enthalpy I
3) shown in, by emitting heat Q
2=(i
2-i
3), finished indoor heating.
Then, by the decompression of expansion valve 8, state (pressure P shown in 4. above-mentioned state liquid phase refrigerant 3. become among Fig. 9
1, enthalpy i
3) and make wherein part gasification, be imported into again in the outdoor heat converter 10 (hereinafter referred to as off-premises station) as the evaporimeter effect.
On the one hand, the cooling water by water pump 24 circulations exchanges with exhaust gas in exhaust gas heat exchanger 25, reclaims the used heat of engine 1, and these heats offer refrigerant in off-premises station 10.Thereby refrigerant receives the used heat of heat that the external world gives and engine 1 and evaporates in above-mentioned off-premises station 10, further overheatedly gets back to state (pressure P 1. shown in Figure 9
1, enthalpy I
1), repeat these operations then repeatedly.And, give the heat Q of refrigerant at indoor set 7
1=(i
1-i
3) expression.
And, owing to above-mentionedly reclaim the used heat of engine 1 and provide it to refrigerant like that,, therefore also improve heating ability (thermal discharge Q so improved the circulating temperature of refrigerant
2).
Yet because utilize the used heat of engine as described above at above-mentioned engine driving type heat pump apparatus, and when the load of engine diminished, the engine waste heat amount of generation was also little, and the heating ability will descend.For example, when making many of the heat pump assemblies running of many indoor sets, the platform number of the indoor set of running can access the refrigeration output of overgauge during more than standard when refrigeration is turned round, but in when running heating because the heat-transfer area of condenser is big, the high side pressure P of the refrigerant shown in Figure 10
2Descend, will produce the problem of the heating ability of warming oneself ability drop and can not obtain Duoing than standard.
In view of the above problems, the object of the present invention is to provide a kind of engine driving type heat pump apparatus, because it is when heating, make the on high-tension side pressure of refrigerant and the operating number of indoor set irrespectively keep certain substantially, so can access the higher heating ability corresponding with the operating number of indoor set.
In order to achieve the above object, the described invention of claim 1 is at engine driving type heat pump apparatus, design has the chilled(cooling) water return (CWR) that is made the cooling water circulation of the refrigerant circulation circuit of refrigerant cycle and circulation cooled engine by engine-driven compressor, described closed circuit design has indoor set, expansion valve and outdoor heat converter, design has the exhaust fuel gas heat exchanger it is characterized in that in the above-mentioned cooling water circulation loop: make the pressure of high cryogen pressures side and the control device that above-mentioned in-room switch operating number irrespectively remains unchanged substantially when also being arranged on heating.
The described the present invention of claim 2 is in the described invention of claim 1, also has to be characterised in that: above-mentioned control device is controlled the aperture of above-mentioned expansion valve.
In the described invention of claim 3 is in the described invention of claim 1, also has to be characterised in that: above-mentioned control device is controlled the air quantity of above-mentioned in-room switch.
In the described invention of claim 4 is in the described invention of claim 1, also has to be characterised in that: above-mentioned control device is controlled the inlet temperature of indoor set by the blow out air of a part of above-mentioned in-room switch that circulates.
In the described invention of claim 5 is in the described invention of claim 1, also has to be characterised in that: above-mentioned control device is controlled the thermal efficiency of above-mentioned engine.
If according to the present invention, because the on high-tension side pressure of refrigerant can irrespectively keep basically identical with the indoor set operating number when heating, operating number that can corresponding indoor set increases the load of compressor, the result, the load of engine also rises, increased the waste heat that this engine is emitted, can access high heating ability corresponding to the operating number of indoor heat converter.
Fig. 1 is the loop diagram of the basic structure of expression engine driving type heat pump apparatus of the present invention.
Fig. 2 is the block diagram of the control system structure of expression engine driving type heat pump apparatus of the present invention.
Fig. 3 is the performance plot of temperature-sensitive reversal valve.
Fig. 4 is the performance plot of linear triple valve.
Fig. 5 is the pattern sectional drawing of indoor set (indoor set).
Fig. 6 is to be parameter with the engine thermal efficiency, the graph of a relation of expression and the corresponding evaporation heat of compressor rotary speed and waste heat.
Fig. 7 is the graph of a relation of indoor set operating number and high cryogen pressures lateral pressure and heating ability in the engine driving type heat pump apparatus of the present invention.
Fig. 8 is the basic structure loop diagram of heat pump assembly.
Fig. 9 is Mo Liai figure.
Figure 10 is the graph of a relation of indoor set operating number and the high cryogen pressures lateral pressure and the ability of heating in the existing heat pump assembly.
Figure 11 is the graph of a relation of the valve lifting capacity of the crankangle of timing control of expression valve and inlet valve and air bleeding valve.
Embodiments of the invention are described below with reference to the accompanying drawings.
Fig. 1 is the loop diagram of expression engine driving type heat pump apparatus basic structure of the present invention.Fig. 2 is the block diagram of the control system structure of expression engine driving type heat pump apparatus of the present invention.The performance plot of Fig. 3 temperature-sensitive reversal valve.Fig. 4 is the performance plot of linear triple valve.
The basic structure of the heat pump assembly of embodiments of the invention at first, is described according to Fig. 1.
In Fig. 1, the 1st, water-cooled engine, 2 (2A 2B) is two compressors that driven by water-cooled engine 1.In this heat pump assembly, design has the compressor of comprising 2 (2A, 2B) chilled(cooling) water return (CWR) 4 of closed-loop refrigerant loop 3 that constitutes and the cooling water circulation that makes cooled engine 1.
Above-mentioned cryogen circuit 3 is loops of the refrigerant cycle in fluorine Lyons of being flowed out by compressor 2 etc., and this loop comprises, and respectively discharges the refrigerant pipeline 3a of side to oil eliminator 5 by compressor 2A, 2B; By the refrigerant pipeline 3b of oil eliminator 5 to cross valve 6; By cross valve 6 to n platform indoor sets 7 (7-1 ..., refrigerant pipeline 3c 7-n); Pass through the refrigerant pipeline 3d of 9 to two off-premises stations 10 of main reservoir through expansion valve 8 by indoor set 7; By the refrigerant pipeline 3e of off-premises station 10 to above-mentioned cross valve 6; By the refrigerant pipeline 3f of above-mentioned cross valve 6 to above-mentioned main reservoir 9; By the refrigerant pipeline 3g of main reservoir 9 to auxilliary reservoir 11; By above-mentioned auxilliary reservoir 11 to above-mentioned compressor 2A, the refrigerant pipeline 3i of each suction side of 2B.
And, to derive by oily return line 12 and by-pass line 3j from above-mentioned oil eliminator 5, oily return line 12 is connected with above-mentioned refrigerant pipeline 3g, and bypass refrigerant line 3j is connected with above-mentioned refrigerant pipeline 3f, and this by-pass line 3j is connected with bypass valve 13.And, above-mentioned main reservoir 9 is assisted the level detection sensor 14,15 that designs the liquid level of the liquid phase refrigerant that the storage of detecting is arranged in the reservoir 11 respectively, the bottom of main reservoir 9 is connected with above-mentioned refrigerant line 3g by by-pass line 3k, and by-pass line 3k goes up design bypass valve 16.
And design has the high side pressure sensor 17 that detects the high cryogen pressures lateral pressure in the refrigerant pipeline 3 of the cryogen circuit 3 of above-mentioned explanation, and design has the low-pressure lateral pressure sensor 18 that detects the refrigerant low-pressure lateral pressure on refrigerant pipeline 3i.And, near the design indoor temperature transmitter 19 above-mentioned indoor set 7, design has outdoor temperature sensor 20 near above-mentioned off-premises station 10.Therefore, above-mentioned high side pressure sensor 17 is connected with control device 21 shown in Figure 2 with indoor temperature transmitter 19.And in control device 21 shown in Figure 2, connecting refrigeration, heating switch 22 and n the switch 23 that indoor set uses.
On the other hand, above-mentioned cooling circuit 4 is the chilled(cooling) water return (CWR)s that make the cooling water circulation of cooled engine 1 by water pump 24.This loop comprises: discharge side by the cooling water pipeline 4a of exhaust fuel gas heat exchanger 25 to the cooling water inlet of engine 1 by water pump 24; By the coolant outlet of engine 1 cooling water pipeline 4b to temperature-sensitive reversal valve 26; By the cooling water pipeline 4c of above-mentioned temperature-sensitive reversal valve 26 to linear triple valve 27; The above-mentioned main reservoir 9 interior cooling water pipeline 4d that are connected with the suction side of above-mentioned water pump 24 that pass through by linear triple valve 27 derivation; Derive and be connected to cooling water pipeline 4e, the 4f of above-mentioned cooling water pipeline 4d respectively from above-mentioned temperature-sensitive reversal valve 26, linear triple valve 27, design has heat release with heat exchanger 28 on cooling water pipeline 4f.
Yet, above-mentioned temperature-sensitive reversal valve 26, by thermostat effect in this setting, as shown in Figure 3, when cooling water temperature makes cooling water pipeline 4 Close Alls in time below 60 ℃, cooling water pipeline 4e is all opened, only allowing has flow of cooling water among the cooling water pipeline 4e, when cooling water temperature surpasses 60 ℃, begins to open cooling water pipeline 4c, and begin to close cooling water pipeline 4e, make two cooling water pipeline 4c, flow of cooling water is arranged among the 4e, when cooling water temperature surpasses 75 ℃, all open cooling water pipeline 4c, Close All cooling water pipeline 4e, and only in cooling water pipeline 4c, flow of cooling water is arranged.And, in Fig. 3, I
1, I
2Be illustrated respectively in cooling water pipeline 4c, the flow of the cooling water that flows among the 4e.
And the characteristic of the above-mentioned straight line triple valve 27 of expression in Fig. 4.That is to say I in Fig. 4
3, I
4Be illustrated respectively in cooling water pipeline 4d, the flow of the cooling water that flows among the 4f is along with the flow I that is increased in the cooling water that flows among cooling water pipeline 4d, the 4f of the valve angle of linear triple valve 27
3, I
4Increase like that point-blank as shown or reduce.Thereby cooling water pipeline 4d all opened when the angle of linear triple valve 27 was 0 °, and cooling water pipeline 4f Close All flows through among the cooling water pipeline 4c total amount I of the cooling water that flows
1(=I
3) be imported into main reservoir 9, cooling water pipeline 4d Close All when the valve angle of linear triple valve 27 is 90 °, cooling water pipeline 4f all opens, and flows through the cooling water total amount I of cooling water pipeline 4c
1(=I
4) switch to and import heat release behind the main reservoir with heat exchanger 28.
Below, with reference to the effect of heat pump assembly when warming oneself of Mo Liai figure explanation present embodiment shown in Figure 9.
During by engine 1 revolution drive compression machine 2A, 2B, 1. state (pressure P as shown in Figure 9
1, enthalpy i
1) gas phase refrigerant be inhaled into compressor 2A, 2B by refrigerant pipeline 3i and be compressed, become as shown in Figure 9 2. state (pressure P
2, enthalpy i
2) high temperature, the refrigerant of high pressure.And this moment compressor 2A, the desired power of 2B (compression heat) AL with (i
2-i
1) expression.The pressure P of the gas phase refrigerant that compressor 2A, 2B suck
1Detect and input in the above-mentioned control device 21 by above-mentioned low-pressure side sensor 18.
The gas phase refrigerant of above-mentioned HTHP imports oil eliminator 5 by refrigerant pipeline 3a, removes oil content with oil eliminator 5.Therefore, the gas phase refrigerant of removing oil content enters cross valve 6 by refrigerant pipeline 3b.And isolated oil turns back to above-mentioned refrigerant pipeline 3g by above-mentioned oily return line 12 from refrigerant in oil eliminator 5.Also has the pressure P of the HTHP refrigerant that in refrigerant 3b, flows
2(disregarding the pressure loss).Detect and be input to above-mentioned control device 21 by above-mentioned high side pressure sensor 17.
When the heating running, be communicated with mouth a and mouthful c and mouthful b and mouthful d of cross valve 6 respectively, high temperature and high pressure gas refrigerant flows into refrigerant pipeline 3c by cross valve 6, is imported into the indoor set 7 with condenser function.Therefore, the HTHP gaseous refrigerant that imports indoor set is emitted condensation heat Q to room air
2And liquefy, become 3. state (pressure P as shown in Figure 9
2, enthalpy i
3) liquid phase refrigerant, emit heat Q this moment
2=(i
2-i
3), carry out indoor heating.
Then, thus in above-mentioned indoor set 7 liquefaction high pressure liquid phase refrigerant become among Fig. 9 4. by 8 decompressions of above-mentioned expansion valve shown in state (pressure P
1, enthalpy i
3), making wherein part gasification, 3d flows to off-premises station 10 by the refrigerant pipeline.
On the other hand, because the driving of water pump 24, the cooling water of circulation is discharged by water pump 24 in chilled(cooling) water return (CWR) 4, flow into cooling water pipeline 4a, in the way, reclaim in exhaust fuel gas heat exchanger 25 from engine 1 and discharge contained heat the gas and after being heated, the cooling jacket by engine 1 cools off this engine 1.Therefore, cooled off the cooling water of engine 1, flow to temperature-sensitive reversal valve 26 by cooling water pipeline 4b.
At this, the temperature of cooling water is lower when engine 1 begins to start, when its value is lower than below 60 ℃, as previously mentioned, owing to (with reference to Fig. 3) temperature-sensitive reversal valve 26 Close All cooling water pipeline 4c, all open cooling water pipeline 4e, cooling water all turns back to water pump 24 by cooling water pipeline 4e.Therefore, because the temperature of cooling water rises gradually, cause engine 1 to enter warm-up mode from cold machine state rapidly.
Therefore, when cooling water temperature surpassed 60 ℃, cooling water pipeline 4c began to open, cooling water pipeline 4e begins to close, and when cooling water temperature surpassed 75 ℃, cooling water pipeline 4c all opened, cooling water pipeline 4e Close All, cooling water all flow through cooling water pipeline 4c to linear triple valve 2.At this, the valve angle of linear triple valve is 0 o'clock when the heating running, and as shown in Figure 4, all cooling water flows in the main reservoir 9 by cooling water pipeline 4d.
Thereby, in main reservoir 9, cool off the cooling water of pipeline 4d by inflow, refrigerant that flows into refrigerant pipeline 3d and the liquid phase refrigerant of storing in main reservoir 9 are heated, give refrigerant the used heat of engine 1 (rely on absorb and from cooled engine 1 resulting heat) from exhaust fuel gas.
And, flow through the part heating of refrigerant used heat of launched machine 1 in above-mentioned main reservoir 9 of above-mentioned refrigerant pipeline 3D after, flow into off-premises station 10 as evaporator function, gasify from external world's absorption heat of evaporation at this place.And, when ambient temperature when institute's definite value is following, drive the fan 10A of off-premises station, absorb heat from the external world and evaporate at off-premises station 10 place's refrigerant as mentioned above.
Therefore, refrigerant flows to cross valve 6 from off-premises station 10 by refrigerant pipeline 3e, but as mentioned above, because when the heating running, the mouth b of cross valve 6 is communicated with a mouthful d, refrigerant flows into refrigerant pipeline 3F by cross valve 6, imports in the main reservoir 9.
Refrigerant carries out gas-liquid separation in above-mentioned main reservoir 9, and the water that flows in water pipeline 4d gives liquid phase refrigerant with the part of the used heat of engine 1, because these heats, the part of liquid phase refrigerant is evaporated and vaporized.
And, gas phase refrigerant in main reservoir 9 is admitted in the auxilliary reservoir 11 by refrigerant pipeline 3g, and be inhaled among compressor 2A, the 2B by refrigerant pipeline 3I, the state that sucks the gas phase refrigerant among compressor 2A, the 2B is got back to 1. state (pressure P as shown in Figure 9
1, enthalpy i
1), these gas phase refrigerant compress once more by compressor 2A, 2B, carry out operation same as described above repeatedly.
Thereby, be inhaled into compressor 2A, 2B by the refrigerant of expansion valve 8 decompression during, refrigerant not only absorbs the used heat of engine 1 in main reservoir 9, absorb extraneous heat, result, the heat Q that refrigerant absorbs simultaneously in off-premises station 10
1(=i
1-i
3) and evaporate.Further by overheated.
As mentioned above, in when running heating, the used heat of the engine 1 that will be reclaimed by cooling water is passed to refrigerant, makes the thermal discharge Q of indoor set 7
2Increase, improved the heating ability.
Yet, when many of heat pump assemblies are warmed oneself running, when the platform number of the indoor set 7 of running is above standard, since above-mentioned reason, the high side pressure P of refrigerant
2Descend, make the heating ability drop, can only obtain the ability of standard.
Therefore, in the present embodiment,, can access higher heating ability corresponding to indoor set 7 operating numbers owing to when heating, make the high side pressure P2 of refrigerant and the operating number of indoor set 7 irrespectively keep certain substantially.Just, the high side pressure P of refrigerant when heating
2Irrespectively keep one substantially regularly with the operating number of indoor set 7, operating number increase along with indoor set 7, the load of compressor 2 rises, the load of engine 1 also rises, thereby the waste heat of this engine 1 is increased, just can obtain and the corresponding higher heating ability of indoor set 7 operating numbers.
, as the on high-tension side pressure P that when warming oneself, makes refrigerant
2Irrespectively keep certain concrete grammar as follows substantially with the operating number of indoor set 7: the method for the aperture of control expansion valve 8; The method of the air quantity of control indoor set 7; The be blown into method of temperature of a part of indoor set 7 blow out air with the control indoor set circulates; And reduce the thermal efficiency of engine 1 and increase the method for the heat of exhaust fuel gas.
At first the method for expansion valve 8 apertures is controlled in explanation.
The following describes the method for the air quantity of control indoor set 7.
And, use switch 23 to become the indoor set 7 of OFF for indoor set, to close expansion valve 8, or all open expansion valve 8, the air quantity that can both make indoor set 7 is 0.No matter because that type, the platform number that is in the indoor set 7 of OFF increases more, and just the platform number of the indoor set 7 under the ON state reduces more, and the pressure of high cryogen pressures side just raises more, so just be necessary more to enlarge the aperture of expansion valve 8 of the indoor set 7 of ON side, or more increase its air quantity.
The following describes the method for the air that blows out of a part of indoor set of circulation with the inlet temperature of control indoor set 7.
As shown in Figure 5, formation makes the upstream side of indoor set 7 and the circulation canal 31 that the downstream is communicated with, at open and close valve 32 of the downstream of this circulation canal 31 opening part design, by the aperture of circulation canal open and close valve driver 33 these open and close valves 32 of control.
And, rotation by fan 7A, high temperature air that a part is blown out by indoor set 7 and process filter 34 is recycled by above-mentioned circulation canal 31, so the inlet temperature of indoor set 7 is enhanced, this inlet temperature is the aperture by open and close valve 32, thereby just control by the air capacity of circulation canal 31 adjustment circulations.
Just, control device 21 as shown in Figure 2, use the ON/OFF of switch 23 to detect the operating number of indoor set 7 by indoor set, to be sent to circulating open close valve actuator 33 (with reference to Fig. 2) corresponding to the control signal of this operating number and adjust open and close valve 32 apertures, control the inlet temperature of indoor set 7 as described above.Specifically,, make the internal circulating load of air increase and improve the inlet temperature of indoor set 7, to keep the pressure P of high high cryogen pressures side along with the increase of the platform number of indoor set 7 running
2
Below, the method that increases the exhaust fuel gas liberated heat by the thermal efficiency that reduces engine 1 is described.
Fig. 6 represents corresponding to concerning between the evaporation heat of compressor revolution and the waste heat as parameter with engine thermal efficiency η.In Fig. 6, solid line A represents necessary evaporation heat, and dotted line B～F represents thermal efficiency η=0.2,0.225 respectively, 0.25, the waste heat of the engine under 0.275,0.3, learn that from this figure η is more little for the thermal efficiency, just can access a large amount of waste heat more corresponding to the evaporation heat of necessity.
And, control device 21 uses the ON/OFF of switch 23 to detect the operating number of indoor set 7 by indoor set shown in Figure 2, corresponding to this operating number, control device 21 sends the control signal of the thermal efficiency of control engine 1 to engine thermal efficiency control device 35.Along with the increase of the platform number of indoor set 7 running, the thermal efficiency of engine 1 descends, thereby keeps the pressure P of high high cryogen pressures side
2And, in Fig. 2, the 36th, linear triple valve driver.
Here, as the method for the thermal efficiency that reduces engine 1, inhale, during the switching regularly of valve (valve timing), should consider to control the method etc. of the aperture of fuel control valve at ignition timing.
For example, in the control of ignition timing, control device 21 is according to the high cryogen pressures lateral pressure P that detects with high side pressure sensor 17
2, the engine that detects with not shown engine speed sensor rotating speed and with the degree in crank angle of not shown crank angle sensor detection control signal is sent in the IGNITION CONTROL loop not shown in the figures, by ignition spark plug late ignition period.
When late ignition as described above during period, reduce piston work done corresponding to burning gases, the output of engine 1 just might descend, only the exhaust fuel gas temperature of this part rises, can be recovered to more used heat in exhaust fuel gas heat exchanger 25, the result can improve the heating ability.
And, descend as the output that makes engine 1 in the method, the engine speed that output is descended because of the load of compressor 2 also descends, but by increasing the amount of the air mixture of supplying with to the cylinder of engine 1, just can replenish that engine 1 is exported and the sloping portion of rotating speed.
Also have, in valve timing control, control device 21 transmits control signal to the variable actuator of valve timing not shown in the figures, the switching that makes the inlet valve of gas engine 1 and air bleeding valve regularly corresponding to the best regularly, stagger a bit along arrow A～D shown in Figure 11, thus the thermal efficiency of reduction engine 1.And the transverse axis of Figure 11 is a crankangle, and the longitudinal axis is the valve lifting capacity, and TDC, BDC are respectively top dead-centre, bottom dead centre.
And, in indoor temperature or the low low temperature heating of outdoor temperature, because the caloric value of engine 1 is not enough, when the high side pressure of refrigerant (compressor discharge pressure) P2 descends, as ignition timing by control device 21 control gas engines 1, the switching timing (valve timing) of inlet valve and air bleeding valve etc. can reduce the thermal efficiency of engine 1, then the caloric value of engine 1 increases and the thermal cycling temperature of refrigerant is improved, the result, the rotating speed of engine 1 does not raise, thereby, do not increase the noise of engine 1 and the life-span is descended, and the heating ability can improve the low temperature heating time.
As in order to last method, as shown in Figure 7, because the operating number of high cryogen pressures lateral pressure P2 and indoor set 7 irrespectively keeps certain substantially in heating, load corresponding to the operating number compressor of indoor set 7 rises, the result, the load of engine 1 also rises, and the waste heat of engine 1 is increased, and can access the high heating ability corresponding to the indoor set operating number.Even when particularly the operating number of indoor set 7 is more than (100%) of standard, also can obtain the high heating ability that balances each other with this operating number.
As described abovely just can understand, in the present invention, engine-driven heat pump assembly have by the cryogen circuit of engine-driven compressor cycle refrigerant and circulation cooled engine the chilled(cooling) water return (CWR) of cooling water, design has expansion valve and indoor set and outdoor heat converter in the above-mentioned cryogen circuit, design exhaust gas heat exchanger in the above-mentioned chilled(cooling) water return (CWR), make the operating number of high cryogen pressures lateral pressure and indoor set irrespectively keep certain control device substantially owing to when heating, be provided with, can access high heating ability corresponding to the operating number of in-room switch.
Claims (5)
1. engine driving type heat pump apparatus, have the cryogen circuit of engine-driven compressor cycle refrigerant and make cooled engine the chilled(cooling) water return (CWR) of cooling water circulation, design has expansion valve and indoor set and outdoor heat converter in the above-mentioned cryogen circuit, design has exhaust heat exchanger in the above-mentioned chilled(cooling) water return (CWR), it is characterized in that: also be provided with in heating and the time make the operating number of high cryogen pressures lateral pressure and indoor set irrespectively keep certain control device substantially.
2. engine driving type heat pump apparatus according to claim 1, it is characterized in that: above-mentioned control device is controlled the aperture of above-mentioned expansion valve.
3. engine driving type heat pump apparatus according to claim 1, it is characterized in that: above-mentioned control device is controlled the air quantity of above-mentioned indoor set.
4. engine driving type heat pump apparatus according to claim 1, it is characterized in that: the portion of air that above-mentioned control device blows out by the above-mentioned indoor set that circulates is controlled the inlet temperature of indoor set.
5. engine driving type heat pump apparatus according to claim 1 is characterized in that: the thermal efficiency of above-mentioned control device control engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96101436 CN1158973A (en) | 1996-02-08 | 1996-02-08 | Heat pump system driven by engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96101436 CN1158973A (en) | 1996-02-08 | 1996-02-08 | Heat pump system driven by engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1158973A true CN1158973A (en) | 1997-09-10 |
Family
ID=5117074
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 96101436 Pending CN1158973A (en) | 1996-02-08 | 1996-02-08 | Heat pump system driven by engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1158973A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103129349A (en) * | 2011-11-23 | 2013-06-05 | 杭州三花研究院有限公司 | Electric vehicle air conditioner system |
| CN103129348A (en) * | 2011-11-23 | 2013-06-05 | 杭州三花研究院有限公司 | Electric vehicle heat pump system |
| WO2020224037A1 (en) * | 2019-05-07 | 2020-11-12 | 珠海格力电器股份有限公司 | Control method and device for multi-split air conditioning system |
-
1996
- 1996-02-08 CN CN 96101436 patent/CN1158973A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103129349A (en) * | 2011-11-23 | 2013-06-05 | 杭州三花研究院有限公司 | Electric vehicle air conditioner system |
| CN103129348A (en) * | 2011-11-23 | 2013-06-05 | 杭州三花研究院有限公司 | Electric vehicle heat pump system |
| CN103129349B (en) * | 2011-11-23 | 2016-05-04 | 杭州三花研究院有限公司 | A kind of electric automobile air-conditioning system |
| CN103129348B (en) * | 2011-11-23 | 2017-07-11 | 杭州三花研究院有限公司 | A kind of electric vehicle heat pump system |
| WO2020224037A1 (en) * | 2019-05-07 | 2020-11-12 | 珠海格力电器股份有限公司 | Control method and device for multi-split air conditioning system |
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