CN101672551A - A combined heat and power generation system - Google Patents
A combined heat and power generation system Download PDFInfo
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- CN101672551A CN101672551A CN200910140410A CN200910140410A CN101672551A CN 101672551 A CN101672551 A CN 101672551A CN 200910140410 A CN200910140410 A CN 200910140410A CN 200910140410 A CN200910140410 A CN 200910140410A CN 101672551 A CN101672551 A CN 101672551A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
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Abstract
The invention discloses a combined heat and power generation system, which comprises more than one heat-distributing medium flow path that makes heat-distributing medium passes through after driven bya reclamation electric generator, more than one refrigerant flow path for the refrigerant flow, and a heat interchanger that makes air perform heat exchange with the heat-distributing medium flow path after performing heat exchange with the refrigerant flow path when carrying out refrigeration, and makes air perform heat exchange with the refrigerant flow path after performing heat exchange withthe heat-distributing medium flow path when carrying out heating operation. Therefore, when carrying heating operation, outdoor air performs heat exchange with the refrigerant flow path after performing heat exchange with the heat-distributing medium flow path, thereby heating capability can be strengthened when carrying out heating operation, and frost injury can be prevented.
Description
Technical field
The present invention relates to a kind ofly when utilizing a heat exchanger to make the thermal medium heat release, make the co-generation unit of condensation of refrigerant/evaporation.Be particularly related to a kind of when refrigeration air of being included in and carry out carrying out heat exchange with above-mentioned thermal medium stream again after the heat exchange, and carry out the co-generation unit of the heat exchanger of heat exchange after air and above-mentioned thermal medium stream carry out heat exchange when system warms up again with above-mentioned refrigerant flow path with above-mentioned refrigerant flow path.
Background technology
Usually, co-generation unit is supplied to the electricity of being produced power consumption portions such as illumination after being meant and utilizing fossil fuel etc. to produce electric power, and the produced simultaneously heat utilization that will produce electric power is in the equipment of heat loss portion.
And in present co-generation unit, the off-premises station and the co-generator of air conditioner become one.Thus, will be supplied to air conditioner by the electric power that the cogeneration of heat and power generating is produced.In addition,, and make the entire system miniaturization, reduce that area being set, and make that operation is set is easy by off-premises station and the co-generator that forms air conditioner.
Yet, in the co-generation unit according to conventional art, be respectively arranged with the heat exchanger that the engine waste heat that is used for that thermal medium is absorbed discharges and the outdoor heat exchanger of above-mentioned air conditioner, therefore there is the many and baroque problem of number of components.And then, when the warm running of system, because the temperature of the outdoor air of air conditioner is low, frost takes place on outdoor heat exchanger, produce the not evaporable problem of cold-producing medium that is flowing in the outdoor heat exchanger thus.
Summary of the invention
In order to address the above problem, the objective of the invention is to, provide a kind of off-premises station of co-generator and air conditioner that makes integrated, reduce the area that is provided with of co-generation unit integral body thus, improve the co-generation unit that convenience is set.
Another object of the present invention is, provide a kind of when utilizing a heat exchanger to carry out the condensation/vaporization of the heat release of thermal medium and cold-producing medium, the thermal medium pipe is arranged on the forward and backward of a refrigerant flow path, can changes the co-generation unit that thermal medium flows thus according to the condensation/vaporization of cold-producing medium.
In order to solve above-mentioned problem, co-generation unit of the present invention comprises: make and reclaim the more than one thermal medium stream that the thermal medium behind the heat of generator drive source passes through; Make the more than one refrigerant flow path of flow of refrigerant; Heat exchanger, this heat exchanger when refrigeration air carry out heat exchange with above-mentioned thermal medium stream again after carrying out heat exchange with above-mentioned refrigerant flow path, and carry out heat exchange with above-mentioned refrigerant flow path again after air and above-mentioned thermal medium stream carry out heat exchange when system warms up.
At this, above-mentioned heat exchanger comprises: a thermal medium stream; With the air-flow direction is that benchmark is positioned at above-mentioned thermal medium stream first refrigerant flow path before; With the air-flow direction is that benchmark is positioned at above-mentioned thermal medium stream second refrigerant flow path afterwards.And, can also comprise refrigerant regulator, this refrigerant regulator makes cold-producing medium flow to above-mentioned first refrigerant flow path when refrigerating operaton, and when the warm operation of system cold-producing medium is flowed to second refrigerant flow path.
In addition, above-mentioned refrigerant regulator can also comprise: first check-valves, and it prevents that cold-producing medium from flowing in above-mentioned first refrigerant flow path when the warm operation of system; Second check-valves, it prevents that cold-producing medium from flowing in second refrigerant flow path when refrigerating operaton.
In addition, above-mentioned heat exchanger comprises: the first discrepancy portion, and it flows into cold-producing medium when refrigerating operaton, and flows out cold-producing medium when the warm operation of system; The second discrepancy portion, it flows into cold-producing medium when the warm operation of system, then flow out cold-producing medium when refrigerating operaton.Above-mentioned first refrigerant flow path comprises the first outflow portion that flows into the first inflow portion of cold-producing medium and be used to flow out cold-producing medium of being used to.Above-mentioned second refrigerant flow path comprises the second outflow portion that flows into the second inflow portion of cold-producing medium and be used to flow out cold-producing medium of being used to.And above-mentioned first check-valves can be arranged between the above-mentioned first outflow portion and the second discrepancy portion, and above-mentioned second check-valves can be arranged between the above-mentioned second outflow portion and the first discrepancy portion.
In addition, above-mentioned refrigerant regulator can comprise: first valve, and it is used to open and close above-mentioned first refrigerant flow path; Second valve, it is used to open and close above-mentioned second refrigerant flow path.
Above-mentioned heat exchanger comprises: the thermal medium stream, wherein by the thermal medium behind the heat of recovery generator drive source; First refrigerant flow path, it is that benchmark is positioned at before the above-mentioned thermal medium stream with the air-flow direction; Second refrigerant flow path, it is that benchmark is positioned at after the above-mentioned thermal medium stream with the air-flow direction.In addition, can also comprise refrigerant regulator, this refrigerant regulator makes cold-producing medium flow to above-mentioned first refrigerant flow path when refrigerating operaton, and when the warm operation of system cold-producing medium is flowed successively to above-mentioned second refrigerant flow path and above-mentioned first refrigerant flow path.
At this, above-mentioned refrigerant regulator can also comprise: first check-valves, and it can not make cold-producing medium flow into earlier in above-mentioned first refrigerant flow path when the warm operation of system; Second check-valves, it can not make by the cold-producing medium behind first refrigerant flow path when refrigerating operaton and flow in second refrigerant flow path.
In addition, above-mentioned heat exchanger comprises: the first discrepancy portion, and it flows into cold-producing medium when refrigerating operaton, and flows out cold-producing medium when the warm operation of system; The second discrepancy portion, it flows into cold-producing medium when the warm operation of system, and flows out cold-producing medium when refrigerating operaton; Tube connector, it is used to connect above-mentioned first refrigerant pipe and above-mentioned second refrigerant pipe.Above-mentioned first refrigerant flow path comprises the first outflow portion that flows into the first inflow portion of cold-producing medium and be used to flow out cold-producing medium of being used to.Above-mentioned second refrigerant flow path comprises the second outflow portion that flows into the second inflow portion of cold-producing medium and be used to flow out cold-producing medium of being used to.And above-mentioned first check-valves can be arranged between the above-mentioned first outflow portion and the second discrepancy portion, and above-mentioned second check-valves can be arranged on the above-mentioned tube connector.
In addition, above-mentioned heat exchanger can comprise: be used for the refrigerant flow path by cold-producing medium; With the air-flow direction is that benchmark is positioned at the above-mentioned refrigerant flow path first thermal medium stream before; With the air-flow direction is that benchmark is positioned at the above-mentioned refrigerant flow path second thermal medium stream afterwards.And, can also comprise the thermal medium adjuster, this thermal medium adjuster makes thermal medium flow to the first thermal medium stream when the warm operation of system, and thermal medium is flowed to the second thermal medium stream.
At this, above-mentioned thermal medium adjuster is made of triple valve, and this triple valve makes thermal medium any one flow path in above-mentioned first thermal medium stream and the above-mentioned second thermal medium stream.And above-mentioned thermal medium adjuster comprises: first valve, and it is used to open and close the above-mentioned first thermal medium stream; Second valve, it is used to open and close the above-mentioned second thermal medium stream.
Co-generation unit according to the present invention with above-mentioned formation has following effect.
The first, integrated by the off-premises station that makes co-generator and air conditioner, can reduce the area that is provided with of co-generator, improve convenience is set.And, can reduce the unit price of co-generation unit.
Second, utilize the engine waste heat that thermal medium was absorbed when system is warm to be moved to come the preheating chamber outer air, and make the cold-producing medium in the refrigerant flow path carry out heat exchange with the outdoor air that passes through preheating, and can make the evaporation of cold-producing medium smooth and easy thus, improve the warm ability of system of air conditioner.
The 3rd, utilize the engine waste heat that thermal medium was absorbed when system is warm to be moved to come the preheating chamber outer air, have the effect that prevents outdoor heat exchanger frost thus.
Characteristics of the present invention and advantage will be easier to understand and become by the detailed description of embodiments of the invention described later with reference to following accompanying drawing.
Description of drawings
Fig. 1 is the pie graph that flow of expression according to the co-generator of first embodiment of the invention cold-producing medium and thermal medium when the refrigeration.
Fig. 2 is the pie graph that flows of the co-generator of expression first embodiment cold-producing medium and thermal medium when system is warm.
Fig. 3 is the pie graph that flow of expression according to the co-generator of second embodiment of the invention cold-producing medium and thermal medium when the refrigeration.
Fig. 4 is the pie graph that flow of expression according to the co-generator of second embodiment of the invention cold-producing medium and thermal medium when system is warm.
Fig. 5 is the pie graph that flow of expression according to the co-generation unit of third embodiment of the invention thermal medium and cold-producing medium when the refrigeration.
Fig. 6 is the pie graph that flow of expression according to the co-generation unit of third embodiment of the invention thermal medium and cold-producing medium when system is warm.
Fig. 7 is the pie graph that flow of expression according to the co-generation unit of fourth embodiment of the invention thermal medium and cold-producing medium when the refrigeration.
Fig. 8 is co-generator when freezing cold-producing medium and the thermal medium mobile pie graph of expression according to fifth embodiment of the invention.
Fig. 9 is the pie graph that flows of the co-generator of expression fifth embodiment of the invention cold-producing medium and thermal medium when system is warm.
Figure 10 is the pie graph that flow of expression according to the co-generator of sixth embodiment of the invention thermal medium and cold-producing medium when the refrigeration.
Figure 11 is the pie graph that flow of expression according to the co-generator of sixth embodiment of the invention thermal medium and cold-producing medium when system is warm.
The specific embodiment
Below, with reference to description of drawings can specific implementation the object of the invention the preferred embodiments of the present invention.In the explanation of present embodiment, same formation is used same title and same Reference numeral, and omit the supplemental instruction that causes thus.
First embodiment
Fig. 1 is the pie graph that flow of expression according to the co-generation unit of first embodiment of the invention cold-producing medium and thermal medium when the refrigeration, and Fig. 2 is the pie graph that flows of the co-generation unit of expression first embodiment cold-producing medium and thermal medium when system is warm.
With reference to Fig. 1 and Fig. 2, the integral body formation according to the co-generation unit of first embodiment is described.
In the co-generation unit of present embodiment, be provided with the off-premises station of co-generator and air conditioner integratedly, wherein, this co-generator is used to produce electric power and the heat that produced when producing electric power carries out heat release.And, the part of the electric power produced in the co-generator can be supplied to the off-premises station of air conditioner.
The co-generator of present embodiment comprises: generator 4, engine 8, endothermic section 20 and heat exchanger 30.And generator 4, engine 8, cooling end 20 and heat exchanger 30 are arranged in the casing 2 integratedly.
Said machine casing 2 is provided with the compressor 40 that constitutes air conditioner outdoor unit, and the heat exchanger 30 of co-generator plays the effect of the outdoor heat exchanger of air conditioner.And the heat exchanger 90 that is equivalent to the air conditioner indoor heat exchanger (in order to distinguish with above-mentioned heat exchanger 30, is called below that " indoor heat exchanger 90 ") is arranged on the outside of casing 2.
As a result, the co-generation unit of present embodiment is provided with co-generator and air conditioner outdoor unit integratedly in the inside of a casing 2.And then in co-generator, the heat exchanger 30 that is used to emit the thermal medium heat plays the effect of the outdoor heat exchanger of air conditioner.Therefore, the area that is provided with of co-generation unit integral body significantly reduces, and operation is set becomes easy.And, owing to when can utilize a heat exchanger to make condensation of refrigerant/evaporation, make the thermal medium heat release, so can reduce the quantity of parts, help the utilization and the cost aspect in space.
On the other hand, on each electric wire 5,6, be respectively arranged with electric switch 5a, 6a, thereby can open and close each electric wire 5,6 as required.
The effect by the heat of the mobile absorption engine 8 of thermal medium and engine exhaust port 11 is played in endothermic section 20.Thermal medium flows into endothermic section 20 by endothermic section inlet 20a, and is expelled to the outside of endothermic section 20 by endothermic section outlet 20b.
In addition, a plurality of exhaust outlets endothermic section 23 can be set on the exhaust outlet 11, but in the present embodiment, utilize two exhaust outlet endothermic sections 23 to reclaim heat.Specifically, the thermal medium that flows into by endothermic section inlet 20a is flowing in two exhaust outlet endothermic sections 23 successively, reclaims heat thus.In addition, in 21 process of flowing of engine endothermic section, behind the further recovery heat, be expelled to the outside of endothermic section 20 by endothermic section outlet 20b.In addition, on the inlet 20a of endothermic section, pump 25 from cyclic force to thermal medium that give can be set.And, pump 25 from cyclic force to thermal medium that give also can be set between exhaust outlet endothermic section 23 and engine endothermic section 21.
More than one refrigerant flow path and more than one thermal medium stream can dispose with multiple quantity and multiple mode, but in the present embodiment, heat exchanger 30 comprises first refrigerant flow path 32, second refrigerant flow path 33 and thermal medium stream 31.Flow into cold-producing medium when in addition, also comprising refrigerating operaton, make first 30a of discrepancy portion of outflow cold-producing medium when warming up operation and second 30b of discrepancy portion that system warms up outflow cold-producing medium when flowing into cold-producing medium, refrigerating operaton when moving.Below, the heat exchange of the thermal medium in the heat exchanger 30 is described, the heat exchange of cold-producing medium is narrated in the back.
In by the process of endothermic section 20, absorb the thermal medium of heat by being positioned at the thermal medium stream 31 on the heat exchanger 30.Then, after carrying out heat exchange and emit heat, flow to endothermic section 20 again with the outdoor air of sending by air blast 37.Specifically, thermal medium flows into to the thermal medium stream inflow 31a of portion and carry out heat exchange in by the process of thermal medium stream 31 after, the 31b of portion is discharged from by the outflow of thermal medium stream.
In addition, in the present embodiment, endothermic section inlet 20a is communicated with the thermal medium stream inflow 31a of portion, and the thermal medium stream outflow 31b of portion is communicated with endothermic section outlet 20b.As a result, thermal medium circulates in thermal medium stream 31 and the endothermic section 20 and flows.
The gas phase thermal medium that 40 pairs of expansion drums evaporate in the process by endothermic section 20 is accommodated, and reduces the pressure of thermal medium stream integral body thus.Therefore, it is connected between endothermic section outlet 20b and the thermal medium stream inflow 31a of portion, so that the gas phase thermal medium in the thermal medium that comes out by endothermic section outlet 20b can not flow among the thermal medium stream inflow 31a of portion, and flow into expansion drum 40.
The effect of supplemental heat medium when in addition, expansion drum 40 also plays thermal medium quantity not sufficient when circulation.Therefore, it is connected between the inlet 20a of the thermal medium stream outflow 31b of portion and endothermic section, so that when the thermal medium deficiency, thermal medium can flow into endothermic section 20 by the endothermic section 20a that enters the mouth.
Below, the cyclic process of thermal medium is described.
As mentioned above, see on the whole that thermal medium absorbs heat in the process by endothermic section 20, and in process, emit the heat that in endothermic section 20, absorbs by the thermal medium stream 31 in the heat exchanger 30.Specifically, the thermal medium that is circulated by pump 25 flows into by endothermic section inlet 20a, and at the heat that passes through successively to reclaim in the process of two exhaust outlet endothermic sections 23 in the emission gases.Then, at heat by absorption engine 8 in the process of engine endothermic section 21.After the thermal medium of absorption heat flowed out by endothermic section outlet 20b, the 31a of portion flow in the thermal medium stream 31 by the inflow of thermal medium stream.The thermal medium that is flowed into is discharged the heat that is absorbed by the outdoor air of being sent by air blast 37 in by the process of thermal medium stream 31.Thermal medium after the heat release is expelled to the outside of heat exchanger 30 by the thermal medium stream outflow 31b of portion.Then, flow among the inlet 20a of endothermic section.That is, thermal medium carries out above-mentioned circulation through heat absorption and exothermic process.
Below, the kind of refrigeration cycle of the air conditioner that constitutes the co-generation unit part in the present embodiment is illustrated.
The kind of refrigeration cycle of present embodiment comprises compressor 70, expansion mechanism 80, heat exchanger 30, indoor heat exchanger 90 and cross valve 100.And compressor 70, heat exchanger 30, cross valve 100 are positioned at the inside of casing 3, and indoor heat exchanger 90 is positioned at the outside of casing 2.In addition, expansion mechanism 80 is provided with two, and one of them is arranged on the inside of casing 2, and another then is arranged on the outside of casing 2.That is, casing 2 is equivalent to common air conditioner outdoor unit, comprises that 94 of the housings of second heat exchanger 90 are equivalent to common indoor machine of air conditioner.
Expansion mechanism 80 expands to cold-producing medium before the time evaporation by heat exchanger at cold-producing medium, and is made of electric expansion valves such as LEV.Expansion mechanism 80 can constitute and respectively cold-producing medium expanded when the refrigerating operaton and during the warm operation of system by a kind of mechanism.But in the present embodiment, comprising: first expansion valve 81, it expands to the cold-producing medium that flows into heat exchanger 30 when the warm operation of system; Indoor check-valves 82, itself and first expansion valve 81 are connected in parallel, and make when being provided in refrigerating operaton the cold-producing medium that flows out from heat exchanger 30 not carry out bypass by first expansion valve 81; Second expansion valve 83, it expands to the cold-producing medium that flows into indoor heat exchanger 90 when refrigerating operaton; Outdoor check-valves 84, itself and above-mentioned second expansion valve 83 are connected in parallel, and make the cold-producing medium of discharging from second heat exchanger 90 not carry out bypass by second expansion valve 83 when the warm operation of system.That is, first expansion valve 81 and indoor check-valves 82 are positioned at the inside of casing 2, and second expansion valve 83 and outdoor check-valves 84 are positioned at housing 94 inside that are arranged on casing 2 outsides.
In addition, kind of refrigeration cycle of the present invention also is included in the cross valve 100 that connects between heat exchanger 30, indoor heat exchanger 90, compressor 70 and the expansion valve 80, to allow to according to refrigeration, warm the mobile of cold-producing medium that change of system.
In addition, the co-generation unit of present embodiment comprises: first 30a of discrepancy portion, and it flows into cold-producing medium when refrigerating operaton, and flows out cold-producing medium when the warm operation of system; The second discrepancy portion, it flows into cold-producing medium when the warm operation of system, and flows out cold-producing medium when refrigerating operaton; Refrigerant regulator, it makes cold-producing medium flow to above-mentioned first refrigerant flow path when refrigerating operaton, and when the warm operation of system cold-producing medium is flowed to second refrigerant flow path.
In the heat exchanger 30, carry out carrying out condensation/vaporization in the process of heat exchange with the outdoor air of sending here by air blast 37 in the time of flow of refrigerant.That is, heat exchanger 30 is equivalent to the outdoor heat exchanger of common air conditioner.And then, in the present embodiment, carry out the effect that absorbs the thermal medium heat in the thermal medium stream 31 that is flowing in above-mentioned explanation simultaneously.As a result, can carry out the effect of the heat absorption heat exchanger of the outdoor heat exchanger of common air conditioner and co-generator simultaneously.Therefore, the effect that has the number of components that reduces co-generation unit integral body.
On the other hand, first refrigerant flow path 32 is that benchmark is positioned at before the thermal medium stream 31 with the outdoor air flows direction that flows into by air blast 37.And, have first 32a of inflow portion from cold-producing medium to first refrigerant flow path 32 and first 32b of outflow portion that flow into.That is, first 32a of inflow portion is connected with first 30a of discrepancy portion, and first 32b of outflow portion is connected with second 30b of discrepancy portion.Thus, the cold-producing medium that flows into by first 30a of discrepancy portion during refrigerating operaton flow in first refrigerant flow path 32 by first 32a of inflow portion, and by after first 32b of the outflow portion discharge, is expelled to the outside of heat exchanger 30 by second 30b of discrepancy portion.
On the other hand, second refrigerant flow path 33 is that benchmark is positioned at after the thermal medium stream 31 with the flow direction of the outdoor air that flows into by air blast 37.And, have second 33a of inflow portion from cold-producing medium to second refrigerant flow path 33 and second 33b of outflow portion that flow into.That is, second 33a of inflow portion is connected with second 30b of discrepancy portion, and second 33b of outflow portion is connected with first 30a of discrepancy portion.Thus, when refrigerating operaton, the cold-producing medium that flows into by second 30b of discrepancy portion flow in second refrigerant flow path 33 by second 33a of inflow portion, and after being discharged from by second 33b of outflow portion, is expelled to the outside of heat exchanger 30 by first 30a of discrepancy portion.
As a result, along the flow direction of outdoor air, be disposed with first refrigerant flow path 32, thermal medium stream 31 and second refrigerant flow path 33.
Refrigerant regulator makes cold-producing medium flow to above-mentioned first refrigerant flow path 32 when refrigerating operaton, and cold-producing medium is flowed to second refrigerant flow path 33.
In the present embodiment, refrigerant regulator is made of a plurality of check-valves.Have first check-valves 34 between first 32a of outflow portion and second 30b of discrepancy portion, can not flow in above-mentioned first refrigerant flow path 32 so that when the warm operation of system, flow into the cold-producing medium of second 30b of discrepancy portion.Thus, the cold-producing medium that flow into the second discrepancy portion 30 when the warm operation of system can not flow in first refrigerant flow path 32, but flow in second refrigerant flow path 33 by second 33a of inflow portion.
And, between second 33a of outflow portion and first 30a of discrepancy portion, having second check-valves 35, can not flow among above-mentioned first 30a of discrepancy portion so that when refrigerating operaton, flow into the cold-producing medium of first 30a of discrepancy portion.Thus, the cold-producing medium that flow into first 30a of discrepancy portion when refrigerating operaton can not flow in second refrigerant flow path 32, but flow in first refrigerant flow path 32 by first 32a of inflow portion.
Thus, when the warm operation of system flow of refrigerant in second refrigerant flow path 33.And when being benchmark with the outdoor air flows direction, thermal medium stream 31 is positioned at before second refrigerant flow path 33.Therefore, outdoor air carries out the heat exchange second time with the cold-producing medium that is flowing in second refrigerant flow path 33 after carrying out the heat exchange first time with thermal medium by thermal medium stream 31.
On the other hand, outdoor environment temperature is below the freezing point temperature when the warm operation of system, and when having a certain amount of moisture, frosts take place the heat exchanger 30 that is exposed in the outdoor environment when outdoor.As a result, in order to prevent that because of frost causes the phenomenon that the evaporation of cold-producing medium in the heat exchanger 30 has some setbacks the common practice is to make air conditioner at regular intervals to eliminate the defrosting mode operation of frost.
But the used heat that utilizes in the present embodiment, co-generation unit to heat by the outdoor air before second refrigerant flow path 33 when making warm operation.That is, carrying out heat exchange by the outdoor air before second refrigerant flow path 33 with the thermal medium that is flowing in thermal medium stream 31 is heated.Thus, prevent or produces on heat exchanger 30 because of the outdoor air below the freezing point temperature during the warm operation of delay base the phenomenon of frost, the system in the time of can strengthening the warm operation of system warms up ability.
Indoor heat exchanger 90 constitutes the part of kind of refrigeration cycle.That is, when system is warm, play the effect of condenser, then play the effect of evaporimeter during refrigeration.Be provided with indoor refrigerant flow path 91 in the inside of indoor heat exchanger 90, warm up, the cold-producing medium that is flowing in the indoor refrigerant flow path 91 is carried out condensation or evaporation according to refrigeration, system.In addition, indoor heat exchanger 90 is positioned at the outside of casing 2.And, also can be positioned at the inside of other housing 94.In addition, indoor heat exchanger 90 can be provided with more than one, in the present embodiment, is provided with three indoor heat exchangers 90.Above-mentioned housing 94 can be positioned at the warm place of need freezing/make, and is usually located at the indoor of building etc. and room air freezed/make warms up.That is, in the present embodiment, above-mentioned housing 94 plays the effect of the indoor set in the common divergence type air conditioner.And, be provided with second expansion valve 83 and the outdoor check-valves 84 of above-mentioned explanation in the inside of housing 94.And, also being provided with blower fan 93, it is used to suck room air and discharges.Therefore, the cold-producing medium that is flowing in the indoor refrigerant flow path 91 carries out heat exchange with the room air that is flowed into by blower fan 93.
Below, the flowing of cold-producing medium of the kind of refrigeration cycle of present embodiment is described.
Cold-producing medium flows when with reference to Fig. 1 refrigeration being described.When refrigeration, heat exchanger 30 plays the effect of cold-producing medium being carried out condenser condensing, and indoor heat exchanger 90 plays the effect of the evaporimeter that cold-producing medium is evaporated.That is, cold-producing medium carries out heat exchange with the room air of being sent here by blower fan 93 and evaporates in the indoor refrigerant flow path 91 of indoor heat exchanger 90.The cold-producing medium that is evaporated flow in the liquid reservoir 71 by cross valve 100.Liquid phase refrigerant in liquid reservoir 71 in the cold-producing medium of evaporation is stored in the liquid reservoir 71, and vapor phase refrigerant flow in the compressor 70.In compressor 70, pass through cross valve 100, flow among first 30a of discrepancy portion of heat exchanger 30 through refrigerant compressed.And, owing to second check-valves 35 can not flow in second refrigerant flow path 33, but flow in first refrigerant flow path 32 by first 32a of inflow portion.Cold-producing medium carry out heat exchange in the process of flowing and by the outdoor air that air blast 37 is sent here in first refrigerant flow path 32 after flows out among second 30b of discrepancy portion by first 32b of outflow portion, first check-valves 34.After flowing out to the outer cold-producing mediums of heat exchanger 30 and in second expansion valve 83, expand by second 30b of discrepancy portion, flow into once more in the indoor heat exchanger 90 and evaporate by indoor check-valves 82.
Cold-producing medium flows when illustrating that with reference to Fig. 2 system is warm.Condensation when carrying out heat exchange, cold-producing medium that flows in the indoor refrigerant flow path 91 of indoor heat exchanger 90 and room air takes place.And, the room air of sending here by air blast 93 absorb behind the heat to indoor make warm.Condensed refrigerant expands in first expansion valve 81 by outdoor check-valves 84 in indoor heat exchanger 90.Cold-producing medium after the expansion flow in the heat exchanger 30.
Specifically, the cold-producing medium that flows into by second 30b of discrepancy portion can not flow to first refrigerant flow path 32 because of first check-valves 34, but flows into to second refrigerant flow path 33 by second 33a of inflow portion.And, in second refrigerant flow path 33, in the process of flowing, carry out heat exchange with the outdoor air of sending here by air blast 37.At this, as mentioned above, room air be by be that thermal medium that benchmark is arranged in the thermal medium stream 31 before second refrigerant flow path 33 carries out heat exchange and by the outdoor air after the heating once with the outdoor air flows direction.In addition, by second 33b of outflow portion, second check-valves 3 and flow out from first 30a of discrepancy portion.
And, carry out heat exchange with above-mentioned heated outdoor air and the cold-producing medium that evaporates flow in the liquid reservoir 71 by cross valve 100, thus aqueous refrigerant storage in liquid reservoir 71, and vapor phase refrigerant flow into compressor 70 and be compressed.Cold-producing medium after compression flow in the indoor heat exchanger 90 and is condensed.
Second embodiment
Fig. 3 is the pie graph that flow of expression according to the co-generation unit of second embodiment of the invention thermal medium and cold-producing medium when the refrigeration, and Fig. 4 is the pie graph that flow of expression according to the co-generation unit of second embodiment of the invention thermal medium and cold-producing medium when system is warm.
According to Fig. 3 and Fig. 4, in the thermal medium adjuster according to the co-generation unit of second embodiment of the invention, comprise first valve 34 ' and second valve 35 ' replace the check- valves 34,35 of first embodiment, co-generation unit also to comprise be used to control first valve 34 ' and second valve 35 ' control part (not shown).
Specifically, in first refrigerant flow path 32, be provided with first valve 34 that is used to open and close first refrigerant flow path 32 ', in second refrigerant flow path 33, be provided with second valve 35 that is used to open and close second refrigerant flow path 33 '.
And, control part (not shown) when refrigeration open above-mentioned first valve 34 ' and close above-mentioned second valve 35 ', when system is warm, close above-mentioned first valve 34 ' and open above-mentioned second valve 35 '.Therefore, with above-mentioned first embodiment similarly, when refrigeration cold-producing medium flow to first refrigerant flow path 32, cold-producing medium flowed to second refrigerant flow path 33 when system was warm.
In addition, because other formations and effect are identical with the first embodiment of the present invention, therefore use identical Reference numeral, and omit detailed description thereof.
The 3rd embodiment
Fig. 5 is the pie graph that flow of expression according to the co-generation unit of third embodiment of the invention thermal medium and cold-producing medium when the refrigeration, and Fig. 6 is the pie graph that flow of expression according to the co-generation unit of third embodiment of the invention thermal medium and cold-producing medium when system is warm.
According to Fig. 5 and Fig. 6, in the present embodiment, flow of refrigerant is at first refrigerant flow path 32 during refrigerating operaton " in, and cold-producing medium is flowing in second refrigerant flow path 33 " and first refrigerant flow path 32 " successively when system is warm.Therefore, cold-producing medium and outdoor air carry out twice heat exchange when the warm operation of system.In the present embodiment, cold-producing medium and outdoor air carry out twice heat exchange, but when appending the outfit refrigerant pipe, can increase the heat exchange number of times.
In the present embodiment, heat exchanger 30 " comprising: first 30a of discrepancy portion, it flows into cold-producing medium and flow out cold-producing medium when the warm operation of system when refrigerating operaton; Second 30b of discrepancy portion, it flows into cold-producing medium and flows out cold-producing medium during at refrigerating operaton when the warm operation of system; Tube connector 36, it is used to connect above-mentioned first refrigerant flow path 32 " and above-mentioned second refrigerant flow path 33 ".
In addition, first refrigerant flow path 32 " comprises first 32a of inflow portion that flows into cold-producing medium " and flows out first 32b of outflow portion of cold-producing medium ", second refrigerant flow path 33 " comprises second 33a of inflow portion that flows into cold-producing medium " and flows out second 33b of outflow portion of cold-producing medium ".
And, above-mentioned first 32a of outflow portion " and being provided with first check-valves 34 between second 30b of discrepancy portion ", during this first check-valves 34 " makes the cold-producing medium that flow into second 30b of discrepancy portion can not flow into above-mentioned first 32a of outflow portion when the warm operation of system ".Therefore, the cold-producing medium that flow among second 30b of discrepancy portion can not flow into first refrigerant flow path 32 " and in the tube connector 36.
And, in tube connector 36, be provided with second check-valves 35 ", the cold-producing medium that this second check-valves 35 " prevents when refrigerating operaton by first refrigerant flow path 32 " flow in the above-mentioned tube connector 36.
In the present embodiment, the overall flow of cold-producing medium is same as the previously described embodiments, below, to the cold-producing medium of present embodiment at heat exchanger 30 " in mobile describing.
According to Fig. 5, when refrigerating operaton, flow into heat exchanger 30 by cross valve 100 by compressor 70 refrigerant compressed " first 30a of discrepancy portion in.Flow and " outflow by first 32a of inflow portion " to first refrigerant flow path 32 " then by first 32b of outflow portion.At this, at first refrigerant flow path 32 " in the cold-producing medium that flows carrying out being condensed in the process of heat exchange with the outdoor air of sending here by air blast 37.Can not flow in the tube connector 36 by first 32b of outflow portion " cold-producing medium of discharging is because of second check-valves 35 ", but the outside that " is expelled to heat exchanger 30 with second 30b of discrepancy portion " through first check-valves 34 successively.In addition, afterwards flow identical with the embodiment of above-mentioned explanation.
According to Fig. 6, the cold-producing medium that expands in first expansion valve 81 when the warm operation of system flow into heat exchanger 30 " second 30b of discrepancy portion in.Then, " be flowing in second refrigerant flow path 33 " by second 33a of inflow portion in and " flow out to tube connector 36 by second 32b of outflow portion.Therefore, cold-producing medium is by second refrigerant flow path 33 " process in carry out heat exchange with outdoor air.At this, outdoor air is by first refrigerant flow path 32 " cold-producing medium and the heat exchange of the thermal medium in the thermal medium stream 31 be in heated state.
Flow into during cold-producing medium in the tube connector 36 " flow into first 32b of outflow portion " by second check-valves 35.At this moment, can not be because of being positioned at the cold-producing medium that first 32b of outflow portion " and first check-valves 34 between second 30b of discrepancy portion " passes through tube connector to the second discrepancy portion side flow.
" cold-producing medium that flows into carries out heat exchange with outdoor air in by the process of first refrigerant pipe by first 32b of outflow portion.That is, in the present embodiment, cold-producing medium was flowing in second refrigerant flow path 33 " and first refrigerant flow path 32 " successively when system warmed up operation, thereby carried out twice heat exchange with outdoor air.But when appending the configuration refrigerant pipe, can increase the heat exchange number of times.
By first refrigerant flow path 32 " process in carry out heat exchange with outdoor air cold-producing medium, " guide by first 32a of inflow portion to first 30a of discrepancy portion.Then, be expelled to the outside of heat exchanger 30 by first 30a of discrepancy portion.In addition, afterwards flow identical with the embodiment of above-mentioned explanation.
The 4th embodiment
Fig. 7 is the pie graph that flow of expression according to the co-generation unit of fourth embodiment of the invention thermal medium and cold-producing medium when the refrigeration.
According to Fig. 7, the integral body of the co-generator in the present embodiment constitutes identical with the co-generator of the 3rd embodiment.Below, the difference of main explanation and the 3rd embodiment.
In an embodiment, possess first valve 38 and replace first check-valves 34 among the 3rd embodiment ", and possess second valve 39 replace second check-valves 35 ".And, also comprising control part, this control part is closed second valve 39 and open first valve 38 when refrigerating operaton, close first valve 38 and open second valve 39 when the warm operation of system.
Thus, utilize control part to open and close first valve 38 and second valve 39, thereby realize the flowing of cold-producing medium among above-mentioned the 3rd embodiment.Other formation and the effect with the 3rd embodiment in formation and act on identical.
The 5th embodiment
Fig. 8 is the pie graph that flow of expression according to the co-generation unit of fifth embodiment of the invention cold-producing medium and thermal medium when the refrigeration, and Fig. 9 is the pie graph that flows of the co-generation unit of expression fifth embodiment of the invention cold-producing medium and thermal medium when system is warm.
With reference to Fig. 8 and Fig. 9, the co-generation unit of the 5th embodiment and the difference of above-mentioned first embodiment～the 4th embodiment are described mainly.
As mentioned above, heat exchanger comprises: the more than one thermal medium stream that is used to make the thermal medium behind the heat that reclaims the generator drive source to pass through; Be used to make the more than one refrigerant flow path of flow of refrigerant.Therefore, in when refrigeration, after air of being sent here by air blast and above-mentioned refrigerant flow path carry out heat exchange, carry out heat exchange with above-mentioned thermal medium stream again.And when system was warm, air and above-mentioned thermal medium stream carried out carrying out heat exchange with above-mentioned refrigerant flow path again after the heat exchange.As a result, warm according to refrigeration and system, air is different with the heat exchange order that thermal medium stream and refrigerant flow path carry out, and particularly, when system warms up, carries out heat exchange by carrying out air and refrigerant flow path that heat exchange heats up with the thermal medium stream.Therefore, the advantage that has the frost phenomenon that can prevent that air conditioner from might take place when the warm operation of system.
More than one refrigerant flow path and more than one thermal medium stream can be configured with various quantity and multiple mode.Heat exchanger 130 in the present embodiment and above-mentioned first embodiment～the 4th embodiment differently comprise two thermal medium streams of a refrigerant flow path and above-mentioned refrigerant flow path front and back.Specifically, the heat exchanger 130 of present embodiment comprises: be used for the refrigerant flow path 131 by cold-producing medium; Be positioned at the first thermal medium stream 132 before the above-mentioned refrigerant flow path during for benchmark with the air-flow direction; Be positioned at the second thermal medium stream 133 after the above-mentioned refrigerant flow path during for benchmark with the air-flow direction.That is, be benchmark with the flow direction of the outdoor air that sucks by air blast 137, refrigerant flow path 131 is between the first thermal medium stream 132 and the second thermal medium stream 133.
In addition, the above-mentioned first thermal medium stream 132 and the second thermal medium stream 133 are connected in parallel, and after the thermal medium of absorption heat flows out by endothermic section outlet 20b in endothermic section 20, flow in the thermal medium stream inflow portion 135.Then, a part flows to the first thermal medium stream 132, and remaining part flows to the second thermal medium stream 133.
In addition, co-generator in an embodiment comprises that the thermal medium adjuster replaces the refrigerant regulator among above-mentioned first embodiment～the 4th embodiment.Specifically, the thermal medium adjuster is arranged between above-mentioned thermal medium stream inflow portion 135, the first thermal medium stream 132 and the second thermal medium stream 133, thus, make optionally any one flow path in the first thermal medium stream 132 and the second thermal medium stream 133 of thermal medium.That is, the thermal medium adjuster makes thermal medium flow to the first thermal medium stream 132 when the warm operation of system, and thermal medium is flowed to the second thermal medium stream 133.
In addition, the thermal medium adjuster in the present embodiment is made of the triple valve 134 between thermal medium inflow portion 135, the first thermal medium stream 132 and the second thermal medium stream 133.
In addition, co-generation unit in the present embodiment also comprises control part (not shown), this control part is controlled above-mentioned triple valve 134 when system is warm, so that thermal medium flows to the above-mentioned first thermal medium stream 132, and control triple valve 134 when refrigeration, so that thermal medium flows to the second thermal medium stream 133.
Therefore, when air conditioner was in the warm operation of system, above-mentioned control part was controlled triple valve 134, so that mobile to the first thermal medium stream 132 through the thermal medium of subcooler outflow 20a of portion and thermal medium stream inflow portion 135 successively.
And when air conditioner was in refrigerating operaton, above-mentioned control part was controlled triple valve 134, so that mobile to the second thermal medium stream 133 through the thermal medium of subcooler outflow 20a of portion and thermal medium stream inflow portion 135 successively.
Thus, when the warm operation of the system of air conditioner, the outdoor air of being sent here by air blast 137 carries out the heat exchange first time with thermal medium and is heated in the first thermal medium stream 132.Then, the outdoor air through once heating carries out heat exchange with the cold-producing medium that is flowing in the refrigerant flow path 131.Thus, can prevent or produce during the warm operation of delay base the phenomenon of frost in heat exchanger (130), the system in the time of can strengthening the warm operation of system warms up ability.
That is, in the present embodiment, with above-mentioned first embodiment～the 4th embodiment differently, be not that refrigeration, system according to air conditioner warms up and change flowing of cold-producing medium, change flowing of thermal medium but warm up according to refrigeration, the system of air conditioner.
Below, the cyclic process of thermal medium is described.
As mentioned above, thermal medium reclaims heat in the process by endothermic section 20 on the whole, discharges the heat that reclaims in the endothermic section 20 in by the process of the first thermal medium stream 132 in the heat exchanger 130 or the second thermal medium stream 133.Identical with the embodiment of above-mentioned explanation by the process of absorption heat in the endothermic section 20.
In addition, the thermal medium after the heat absorption flow in the thermal medium stream inflow portion 135 after flowing out by endothermic section outlet 20b.Then, flow in the first thermal medium stream 132 or the second thermal medium stream 133 by triple valve 134.
Specifically, above-mentioned control part is judged warm operation of above-mentioned air conditioner system or refrigerating operaton.Then, above-mentioned control part is controlled triple valve 134 when the warm operation of system, so that flow to the first thermal medium stream 132 by the thermal medium of thermal medium stream inflow portion 135.In addition, control triple valve 134 when refrigerating operaton is so that flow to the second thermal medium stream 133 by the thermal medium of thermal medium stream inflow portion 135.
That is, when the warm operation of system, the thermal medium that flows in the first thermal medium stream 132 carries out heat exchange and release heat with the outdoor air of being sent here by air blast 137.As mentioned above, because refrigerant flow path 131 is positioned at after the first thermal medium stream 132 when being benchmark with the outdoor air flows direction, therefore, outdoor air carries out heat exchange with the cold-producing medium by refrigerant flow path 131 described later after being heated by the thermal medium by the first thermal medium stream 132 again.
In addition, when refrigerating operaton, because the second thermal medium stream 133 was positioned at after the above-mentioned refrigerant flow path 131 when being benchmark with the outdoor air flows direction, therefore, after the outdoor air that is sucked by air blast 137 carries out heat exchange with refrigerant flow path 131, carry out heat exchange with thermal medium mobile in the second thermal medium stream 133 again.
On the other hand, warm up according to refrigeration, system, after the thermal medium that flows in the first thermal medium stream 132 or the second thermal medium stream 133 flowed out from heat exchanger 130 by thermal medium stream outflow portion 136, inlet 20a was flowing in the endothermic section 20 by the endothermic section.That is, thermal medium circulates along the stream of above-mentioned explanation, and absorbs heat and heat release.
Below, the air conditioner refrigeration circulation of the part of the co-generation unit that constitutes present embodiment is described.The integral body of the air conditioner of present embodiment constitutes identical with above-mentioned first embodiment～the 4th embodiment, has only the structure difference of heat exchanger 130, below a heat exchanging device 130 describe.
As mentioned above, the first thermal medium stream 132 is that benchmark is positioned at before the refrigerant flow path 131 with the flow direction of outdoor air, and the second thermal medium stream 133 is that benchmark is positioned at after the refrigerant flow path 131 with the outdoor air flows direction.That is, be benchmark with the flow direction of cold-producing medium, the first thermal medium stream 132, the second thermal medium stream 133 and refrigerant flow path 131 are by in series and row arrangement.Therefore, when the warm operation of system, outdoor air is heated in the first thermal medium stream 132 after, flow to refrigerant flow path 131.
Below, the flow of refrigerant of the kind of refrigeration cycle of present embodiment is described.Flow of refrigerant in the present embodiment is identical with above-mentioned first embodiment～the 4th embodiment.Just in the present embodiment, warm according to refrigeration, the system of air conditioner, mobile the changing into to the first thermal medium stream 132 and the second thermal medium stream 133 of thermal medium flowed.Therefore, in the present embodiment, when freezing, making warm operation, cold-producing medium is by a refrigerant flow path 131 of heat exchanger 130.
The 6th embodiment
Figure 10 is the pie graph that flow of expression according to the co-generation unit of sixth embodiment of the invention thermal medium and cold-producing medium when the refrigeration, and Figure 11 is the pie graph that flow of expression according to the co-generation unit of sixth embodiment of the invention thermal medium and cold-producing medium when system is warm.
According to Figure 10 and Figure 11, in the thermal medium adjuster according to the co-generation unit of sixth embodiment of the invention, possesses the triple valve 134 that other valve replaces the 5th embodiment at the first thermal medium stream 132 and the second thermal medium stream, 133 inlet portions.That is, comprise second valve 138 that is used to open and close first valve 139 of the first thermal medium stream 132 and is used to open and close the second thermal medium stream 33.
And the control part that describes in detail in the 5th embodiment (not shown) in open first valve 139, is closed second valve 138 when refrigerating operaton.In addition, when the warm operation of system, close first valve 139 in open second valve 138.Thus, with above-mentioned first embodiment just as ground, when the warm operation of system, the outdoor air by refrigerant flow path 131 is heated, thereby prevents or postpone the phenomenon that frosts take place heat exchanger 130, the warm ability of system when strengthening the warm operation of system.
Identical in other formations and effect and the fifth embodiment of the invention, therefore use identical Reference numeral, and omit detailed description thereof.
Scope of the present invention is not limited to the foregoing description, and in above-mentioned technical scope, those skilled in the art can be that various distortion are carried out on the basis with the present invention.
Claims (11)
1. a co-generation unit is characterized in that, comprising:
More than one thermal medium stream is wherein by the thermal medium behind the heat of recovery generator drive source;
More than one refrigerant flow path, wherein flow system cryogen;
Heat exchanger, it carries out heat exchange with above-mentioned thermal medium stream after making air and above-mentioned refrigerant flow path carry out heat exchange again when refrigeration, and carries out heat exchange with above-mentioned refrigerant flow path again after making air and above-mentioned thermal medium stream carry out heat exchange when system is warm.
2. co-generation unit according to claim 1 is characterized in that,
Above-mentioned heat exchanger comprises: the thermal medium stream that the thermal medium behind the heat of recovery generator drive source passes through; With the air-flow direction is that benchmark is positioned at above-mentioned thermal medium stream first refrigerant flow path before; With the air-flow direction is that benchmark is positioned at above-mentioned thermal medium stream second refrigerant flow path afterwards,
This co-generation unit also comprises refrigerant regulator, and this refrigerant regulator makes cold-producing medium flow to above-mentioned first refrigerant flow path when refrigerating operaton, and when the warm operation of system cold-producing medium is flowed to second refrigerant flow path.
3. co-generation unit according to claim 2 is characterized in that, above-mentioned refrigerant regulator comprises: first check-valves, and it prevents that cold-producing medium from flowing in above-mentioned first refrigerant flow path when the warm operation of system; Second check-valves, it prevents that cold-producing medium from flowing in above-mentioned second refrigerant flow path when refrigerating operaton.
4. co-generation unit according to claim 2 is characterized in that,
Above-mentioned heat exchanger comprises: the first discrepancy portion, and it flows into cold-producing medium when refrigerating operaton, and flows out cold-producing medium when the warm operation of system; The second discrepancy portion, it flows into cold-producing medium when the warm operation of system, and flows out cold-producing medium when refrigerating operaton,
Above-mentioned first refrigerant flow path comprises: the first inflow portion that is used to flow into cold-producing medium; Be used to flow out the first outflow portion of cold-producing medium,
Above-mentioned second refrigerant flow path comprises: the second inflow portion that is used to flow into cold-producing medium; Be used to flow out the second outflow portion of cold-producing medium,
Above-mentioned first check-valves is arranged between the above-mentioned first outflow portion and the second discrepancy portion,
Above-mentioned second check-valves is arranged between the above-mentioned second outflow portion and the first discrepancy portion.
5. co-generation unit according to claim 2 is characterized in that, above-mentioned refrigerant regulator comprises: first valve, and it opens and closes above-mentioned first refrigerant flow path; Second valve, it opens and closes above-mentioned second refrigerant flow path.
6. co-generation unit according to claim 1 is characterized in that,
Above-mentioned heat exchanger comprises: the thermal medium stream, wherein by the thermal medium behind the heat of recovery generator drive source; First refrigerant flow path, it is that benchmark is positioned at before the above-mentioned thermal medium stream with the air-flow direction; Second refrigerant flow path, it is that benchmark is positioned at after the above-mentioned thermal medium stream with the air-flow direction;
This co-generation unit also comprises refrigerant regulator, this refrigerant regulator makes cold-producing medium flow to above-mentioned first refrigerant flow path when refrigerating operaton, and when the warm operation of system cold-producing medium is flowed successively to above-mentioned second refrigerant flow path and above-mentioned first refrigerant flow path.
7. co-generation unit according to claim 6 is characterized in that, above-mentioned refrigerant regulator comprises: first check-valves, and it can not make cold-producing medium flow into earlier in above-mentioned first refrigerant flow path when the warm operation of system; Second check-valves, it can not make by the cold-producing medium behind first refrigerant flow path when refrigerating operaton and flow in second refrigerant flow path.
8. co-generation unit according to claim 7 is characterized in that,
Above-mentioned heat exchanger comprises: the first discrepancy portion, and it flows into cold-producing medium when refrigerating operaton, and flows out cold-producing medium when the warm operation of system; The second discrepancy portion, it flows into cold-producing medium when the warm operation of system, and flows out cold-producing medium when refrigerating operaton; Tube connector, it connects above-mentioned first refrigerant pipe and above-mentioned second refrigerant pipe,
Above-mentioned first refrigerant flow path comprises: be used to the first outflow portion that flows into the first inflow portion of cold-producing medium and be used to flow out cold-producing medium,
Above-mentioned second refrigerant flow path comprises: be used to the second outflow portion that flows into the second inflow portion of cold-producing medium and be used to flow out cold-producing medium,
Above-mentioned first check-valves is arranged between the above-mentioned first outflow portion and the second discrepancy portion,
Above-mentioned second check-valves is arranged on the above-mentioned tube connector.
9. co-generation unit according to claim 1 is characterized in that,
Above-mentioned heat exchanger comprises: the refrigerant flow path that cold-producing medium passes through; With the air-flow direction is that benchmark is positioned at the above-mentioned refrigerant flow path first thermal medium stream before; With the air-flow direction is that benchmark is positioned at the above-mentioned refrigerant flow path second thermal medium stream afterwards,
This co-generation unit also comprises the thermal medium adjuster, and this thermal medium adjuster makes thermal medium flow to the first thermal medium stream when the warm operation of system, and thermal medium is flowed to the second thermal medium stream.
10. co-generation unit according to claim 9 is characterized in that, above-mentioned thermal medium adjuster is a triple valve, and this triple valve makes thermal medium any one flow path in above-mentioned first thermal medium stream and the above-mentioned second thermal medium stream.
11. co-generation unit according to claim 9 is characterized in that, above-mentioned thermal medium adjuster comprises: first valve, and it is used to open and close the above-mentioned first thermal medium stream; Second valve, it is used to open and close the above-mentioned second thermal medium stream.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020080088901 | 2008-09-09 | ||
| KR20080088902A KR101507441B1 (en) | 2008-09-09 | 2008-09-09 | Co-generation system |
| KR1020080088901A KR20100030112A (en) | 2008-09-09 | 2008-09-09 | Co-generation system |
| KR1020080088902 | 2008-09-09 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101672551A true CN101672551A (en) | 2010-03-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910140410A Pending CN101672551A (en) | 2008-09-09 | 2009-05-08 | A combined heat and power generation system |
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| Country | Link |
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| CN (1) | CN101672551A (en) |
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- 2009-05-08 CN CN200910140410A patent/CN101672551A/en active Pending
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