CN100470165C - Engine heat pump - Google Patents
Engine heat pump Download PDFInfo
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- CN100470165C CN100470165C CNB200580016138XA CN200580016138A CN100470165C CN 100470165 C CN100470165 C CN 100470165C CN B200580016138X A CNB200580016138X A CN B200580016138XA CN 200580016138 A CN200580016138 A CN 200580016138A CN 100470165 C CN100470165 C CN 100470165C
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- Prior art keywords
- supercooling
- liquid refrigerant
- compressor
- heat exchanger
- engine
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- 239000003507 refrigerant Substances 0.000 claims abstract description 194
- 238000004781 supercooling Methods 0.000 claims abstract description 193
- 239000007788 liquid Substances 0.000 claims abstract description 149
- 238000001704 evaporation Methods 0.000 claims description 26
- 239000002918 waste heat Substances 0.000 claims description 22
- 230000008020 evaporation Effects 0.000 claims description 17
- 238000007599 discharging Methods 0.000 claims description 3
- 230000006835 compression Effects 0.000 abstract description 59
- 238000007906 compression Methods 0.000 abstract description 59
- 238000010438 heat treatment Methods 0.000 description 28
- 230000009183 running Effects 0.000 description 28
- 238000001816 cooling Methods 0.000 description 26
- 239000007789 gas Substances 0.000 description 13
- 238000010521 absorption reaction Methods 0.000 description 11
- 238000010586 diagram Methods 0.000 description 8
- 230000000694 effects Effects 0.000 description 7
- 238000005057 refrigeration Methods 0.000 description 7
- 230000029058 respiratory gaseous exchange Effects 0.000 description 7
- 238000009833 condensation Methods 0.000 description 4
- 230000005494 condensation Effects 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000003292 diminished effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B27/00—Machines, plants or systems, using particular sources of energy
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
- F25B2400/0751—Details of compressors or related parts with parallel compressors the compressors having different capacities
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
An object of the invention is to provide an engine heat pump whose compression work is reduced without increase of consumed electric power, thereby improving its driving efficiency (energy efficiency). An engine heat pump comprises: an engine (4); a main compressor (2) driven by the engine (4); a sub compressor (3); an indoor heat exchanger (8); an outdoor heat exchanger (5); an expansion valve (23) for the indoor heat exchanger; an expansion valve (21) for the outdoor heat exchanger; and a supercooling heat exchanger (15) disposed on a liquid refrigerant passage (main passage 26) of a connection passage between the indoor heat exchanger (8) and the outdoor heat exchanger (5). In the supercooling heat exchanger (15), a supercooling liquid refrigerant branched into a branching passage (27(27a, 27b)) supercools a liquid refrigerant before being branched. The sub compressor (3) is driven by the engine (4) so as to compress the supercooling liquid refrigerant. A ratio (R) of a capacity of the sub compressor (3) to a total capacity of the main compressor (2) and the sub compressor (3) ranges between 20% and 29%.
Description
Technical field
The present invention relates to the apparatus structure of engine heat pump, tax relates to the technology that does not increase new electric power consumption and reduce the total compression merit in more detail.
Background technology
About the engine heat pump of the structure of utilizing the motor driven compressor, patent documentation 1 described structure is known.In patent documentation 1, disclosed an invention, described invention is divided into work done during compression that is produced by main compressor and two systems of work done during compression that produced by auxiliary compressor with the work done during compression of engine heat pump, remain on the high pressure of evaporating pressure by evaporating pressure than opposite side (main compressor side) with a side (auxiliary compressor side), reduce the work done during compression of a described side, by this, be reduced in total compression merit in the engine heat pump.
In aforementioned patent document 1, disclosed a kind of structure, this structure utilizes the compressor (motor compressor) of driven type that the side (auxiliary compressor side) that evaporating pressure becomes high pressure is done work done during compression, but, in this structure, in engine heat pump, append the equipment (aforementioned motor compressor) that needs new electric power that has been equipped with.In this case,, increased the consumption of electric power, caused fully to produce the results such as advantage that the engine heat pump of so-called " reduction electric power consumption " should have although reduced work done during compression.
Patent documentation 1: the spy opens the 2004-20153 communique
The content of invention
Problem of the present invention is, in engine heat pump, do not increase electric power consumption and reduces work done during compression, improves running efficiency (energy efficiency).
Engine heat pump of the present invention, comprise: by engine-driven main compressor and auxiliary compressor, indoor heat converter, outdoor heat converter, the indoor heat converter expansion valve, the outdoor heat converter expansion valve, and supercooling heat exchanger, described supercooling heat exchanger is arranged on liquid refrigerant among the access path of described indoor heat converter and described outdoor heat converter by in the path, to be branched off into liquid refrigerant in the individual path as the supercooling liquid refrigerant, the liquid refrigerant that utilizes this supercooling with liquid refrigerant branch to be supported the front carries out supercooling, described engine heat pump converges cold-producing medium of being discharged by aforementioned auxiliary compressor and the cold-producing medium of discharging from aforementioned main compressor, it is characterized in that, utilize described auxiliary compressor to compress aforementioned supercooling liquid refrigerant, simultaneously, the capacity of described auxiliary compressor is 20% to 29% with respect to the Capacity Ratio of the total capacity of described main compressor and described auxiliary compressor, be provided with the expansion valve that described supercooling heat exchanger is used, simultaneously, the expansion of remaining liquid refrigerant is suppressed more after the branch that the described supercooling that caused with expansion valve by described supercooling heat exchanger causes with expansion valve by described indoor heat converter with the expansion ratio of liquid refrigerant by making, make described supercooling with the evaporation of liquid refrigerant press with described branch after the evaporation of remaining liquid refrigerant press to compare and uprise, with outdoor heat converter the engine waste heat recover is set side by side, evaporates described supercooling liquid refrigerant by described engine waste heat recover.
In addition, in engine heat pump of the present invention, the engine waste heat recover is set side by side, utilizes aforementioned engine waste heat recover to make aforementioned supercooling liquid refrigerant evaporates, simultaneously, utilize auxiliary compressor to compress with outdoor heat converter.
In engine heat pump of the present invention, by utilizing by engine-driven auxiliary compressor evaporating pressure (cold-producing medium suction pressure) than compressing with cold-producing medium by the high supercooling of main compressor refrigerant compressed, needn't increase the electric power consumption that is equivalent to the auxiliary compressor of driven by power formula in the prior art newly, and reduced total work done during compression in cold-producing medium circulation, simultaneously, the supercooling effect that utilizes the supercooling heat exchanger to produce keeps or the raising refrigerating capacity.
In addition, the capacity by making auxiliary compressor reaches the number range of regulation with respect to the Capacity Ratio of the total capacity of main compressor and auxiliary compressor, when refrigeration, keep or the raising refrigerating capacity, simultaneously, when heating, can guarantee the performance of supercooling heat exchanger.That is, in the structure of the present invention of utilizing common motor driven main compressor and auxiliary compressor, when when refrigeration and heating, can carry out the good running of running efficiency (energy efficiency).
In engine heat pump of the present invention, reach the structure of the number range of regulation with respect to the Capacity Ratio of the total capacity of main compressor and auxiliary compressor by the capacity that makes auxiliary compressor, total compression merit when reducing refrigeration, simultaneously, when heating, electric power consumption can be do not increased newly yet, the total compression merit can be reduced.
In addition, owing to,, can improve the heat absorption capacity of the cold-producing medium of per unit mass flow by the supercooling effect from outside atmosphere by carrying out the supercooling of liquid refrigerant in when heating, so, can reduce the total amount of the cold-producing medium that flows through the cold-producing medium circulation.As a result, the total compression merit can be reduced, running efficiency (energy efficiency) can be improved.
Description of drawings
Fig. 1 is the refrigerant loop figure according to engine heat pump of the present invention.
Fig. 2 is the block diagram of its control appliance class.
Fig. 3 is according to the Mollier of its refrigerant loop structure (Mollier) figure (heat-entropy diagram).
Fig. 4 is the curve map of the relation of expression auxiliary compressor Capacity Ratio and COP.
Fig. 5 is the curve map of the relation of expression auxiliary compressor Capacity Ratio and supercooling heat exchanger refrigerant temperature.
Symbol description
2 main compressors
3 auxiliary compressors
4 engines
5 outdoor heat converters
6 engine waste heat recovers
8 indoor heat converters
15 supercooling heat exchangers
21 outdoor heat converter expansion valves
22 supercooling heat exchanger expansion valves
23 indoor heat converter expansion valves
26 main paths
The 27a individual path
The 27b individual path
The specific embodiment
At first, utilize Fig. 1 to illustrate that refrigerant loop structure and cold-producing medium according to engine heat pump of the present invention circulate.
According to engine heat pump of the present invention, comprise: by the main compressor 2 and the auxiliary compressor 3 of engine 4 drivings, indoor heat converter 8, outdoor heat converter 5, indoor heat converter expansion valve 23, outdoor heat converter expansion valve 21, and supercooling heat exchanger 15, described supercooling heat exchanger 15 be arranged among the access path of indoor heat converter 8 and outdoor heat converter 5 as liquid refrigerant by in the main path 26 in path, utilization is branched off into individual path 27 (27a, the liquid refrigerant that supercooling 27b) is supported the front to branch with liquid refrigerant carries out supercooling, and described engine heat pump is the heat pump that utilizes the cold-producing medium circulation that is made of above-mentioned part.In addition, supercooling heat exchanger 15 comprise with tie point 15a, the 15b of main path 26 and with tie point 15c, the 15d of individual path 27.In addition, in this structure, a plurality of indoor heat converters 8 can be set also.
Main compressor 2 is driven by engine 4, utilizes the gas refrigerant that not shown accumulator attracts, pressurized liquid refrigerant is separated, and discharges the gas refrigerant of HTHP.From the gas refrigerant of main compressor 2 discharges, by the direction of cross valve 24 guiding regulations.In addition, also guided by cross valve 24 in order to make the gas refrigerant that is attracted by main compressor 2, the path 32 that the refrigerant inlet of main compressor 2 and cross valve 24 are configured the suction line of main compressor 2 is communicated with.
In addition, the individual path 27a that the individual path 27 that is provided with in main path 26 constitutes between indoor heat converter 8 and the supercooling heat exchanger 15, simultaneously, constitute the individual path 27b between outdoor heat converter 5 and the supercooling heat exchanger 15, between each individual path 27a, 27b and supercooling heat exchanger are with expansion valve 22, open and close valve 28a, 28b are set respectively.The liquid refrigerant of supporting the front with the branch of main path 26 in cool cycles that described each open and close valve 28a, 28b will describe in the back or the heat cycles is switched its switching by overcooled mode.
And, the cold-producing medium of being discharged by auxiliary compressor 3 is converged being located at from the point 65 of each compressor 2,3 in the path of cross valve 24 and the cold-producing medium of being discharged by main compressor 2.Here, the cold-producing medium that converges is changed flow direction by cross valve 24, carries out cool cycles or the heat cycles described later.In addition, between aforementioned point 65 and cross valve 24, the oil eliminator (not shown) is set, the refrigerator oil that is included in the gas refrigerant of HTHP is separated, make it to be back to the suction side of main compressor 2 and auxiliary compressor 3, so that carry out the lubricated of two compressors 2,3 well.
Utilize the cold-producing medium circulation of as above structure,, carry out cool cycles or heat cycles by the switching of the flow of refrigerant direction of being undertaken by cross valve 24.
In cool cycles, converged at point 65 places by main compressor 2 and auxiliary compressor 3 refrigerant compressed, via cross valve 24, be sent to outdoor heat converter 5, after this outdoor heat converter 5 places heat release condensation, be sent to supercooling heat exchanger 15, flow into, flow out by tie point 15a by tie point 15b.Expanded with expansion valve 23 places at indoor heat converter by supercooling heat exchanger 15 overcooled liquid refrigerants, after the heat absorption evaporation of indoor heat converter 8 places, attracted in the main compressor 2 via cross valve 24.Then, this cold-producing medium that is attracted is discharged from after being compressed by main compressor 2 once more.
In addition, send and the part of liquid refrigerant by main path 26 is divided to the individual path 27a with liquid refrigerant as supercooling from outdoor heat converter 5, reduce with the expansion of expansion valve 22 places, temperature at the supercooling heat exchanger, become the cold-producing medium of low temperature and moisture, by tie point 15c to supercooling heat exchanger 15 flow into, in the process that tie point 15d flows out, the liquid refrigerant of the main path 26 of flowing through is carried out supercooling.At this moment, open and close valve 28a becomes the state of opening, open and close valve 28b becomes closing state, liquid refrigerant by main path 26 is not shunted to individual path 27b side, by the supercooling liquid refrigerant that is branched off into individual path 27a, the liquid refrigerant of whole amounts that branch is supported the front carries out supercooling.
Like this, the supercooling of the liquid refrigerant by passing through main path 26 improves the efficient of kind of refrigeration cycle.And aforementioned supercooling is attracted by auxiliary compressor 3 with liquid refrigerant, is discharged once more by these auxiliary compressor 3 compression backs.
On the other hand, in heat cycles, converged at point 65 places by main compressor 2 and auxiliary compressor 3 refrigerant compressed, be sent to indoor heat converter 8 via cross valve 24, after this indoor heat converter 8 places heat release condensation, be sent to supercooling heat exchanger 15, flow into, flow out by tie point 15b by tie point 15a.Expanded with expansion valve 21 places at outdoor heat converter by supercooling heat exchanger 15 overcooled liquid refrigerants, after the heat absorption evaporation of outdoor heat converter 5 places, attracted by main compressor 2 via cross valve 24.Then, this cold-producing medium that is attracted is discharged after being compressed by main compressor 2 once more.
In addition, sent, passed through the part of the liquid refrigerant of main path 26 from indoor heat converter 8, as the supercooling liquid refrigerant, be divided to individual path 27b, reduce with the expansion of expansion valve 22 places, temperature at the supercooling heat exchanger, become the cold-producing medium of low temperature and moisture, by tie point 15c to supercooling heat exchanger 15 flow into, in the process that tie point 15d flows out, the liquid refrigerant that flows through main path 26 is carried out supercooling.At this moment, open and close valve 28a becomes closed condition, and open and close valve 28b becomes open mode, does not shunt to individual path 27a side by the liquid refrigerant of main path 26, by the supercooling liquid refrigerant that is branched off into individual path 27b, the liquid refrigerant of whole amounts that branch is supported the front carries out supercooling.
Then,,, attracted, discharged once more by these auxiliary compressor 3 compression backs by auxiliary compressor 3 in the heat absorption evaporation of engine waste heat recover 6 places by the supercooling liquid refrigerant of supercooling heat exchanger 15.
Secondly, utilize Fig. 2 that the relevant apparatus structure of controlling according to the running of engine heat pump of the present invention is described.
In addition, this controller 25 is connected with open and close valve 28a, 28b on being separately positioned on aforementioned branches path 27a, 27b, controls their switching.Here, specifically, each open and close valve 28a, 28b are controlled in the manner as described below.That is, be opened during the supercooling of the liquid refrigerant of open and close valve 28a in carrying out aforementioned cool cycles, in addition, be closed.In addition, be opened during the supercooling of the liquid refrigerant of open and close valve 28b in carrying out aforementioned heat cycles, in addition, be closed.Like this, by controlling each open and close valve 28a, 28b, in cool cycles and heat cycles, liquid refrigerant is branched in the downstream of supercooling heat exchanger 15 respectively, and the liquid refrigerant of the whole amounts before being branched off into individual path 27 is by 15 supercooling of supercooling heat exchanger.
And then controller 25 and engine 4 (control circuit) are connected, and start to stop (sending out and stop) control, the running of control main compressor 2 and auxiliary compressor 3 by what carry out engine 4.
In above structure, controller 25 control supercooling heat exchangers make by the supercooling heat exchanger and use the cold-producing medium of the humidity of expansion valve 22 expansions to increase the degree of superheat in 33 (that is the suction lines of auxiliary compressor 3) in the path with the aperture of expansion valve 22.And, as hereinafter described, by selected (formation) auxiliary compressor 3, the cold-producing medium suction pressure of auxiliary compressor 3 becomes than the cold-producing medium suction pressure height of main compressor 2, shown in the mollier diagram of Fig. 3, compare with the work done during compression Δ Wm that is done by main compressor 2, can make the work done during compression Δ Ws that is done by auxiliary compressor 3 littler.Like this, compare, can reduce the total compression merit with the situation of the cold-producing medium that utilizes single work done during compression Δ Wm compression all to measure.
Below, follow flowing of cold-producing medium in the refrigerant loop structure, the mollier diagram (Fig. 3) of the kind of refrigeration cycle in above-mentioned refrigerant loop structure is described.In addition, in this mollier diagram, the state variation of the cold-producing medium of expression per unit mass flow, transverse axis is represented the specific enthalpy (kJ/kg) as the energy that cold-producing medium had of every 1kg quality, the longitudinal axis is represented (definitely) pressure (Mpaabs).
About the kind of refrigeration cycle on this mollier diagram, describe for the situation of cool cycles.
Some Am in this mollier diagram represents the state that cold-producing medium flows in the path 32 of the suction line that constitutes main compressor 2, the specific enthalpy and the force value that are located at this state are respectively h2 (kJ/kg), p2 (MPa abs).And the flow of establishing the cold-producing medium in the refrigerant loop here is Gm.In addition, some As represents the state that cold-producing medium flows in the path 33 of the suction line that constitutes auxiliary compressor 3, and specific enthalpy and the force value of order under this state is respectively h1 (kJ/kg), p1 (MPa abs).And the flow that is located at the cold-producing medium in the refrigerant loop here is Gs.
The cold-producing medium of these states is inhaled into each compressor 2,3 from suction line separately, does work done during compression in each compressor 2,3.At this moment, in main compressor 2, be work done during compression Δ Wm (AmB between the compressional zone), in auxiliary compressor 3, be work done during compression Δ Ws (AsB between the compressional zone) for the cold-producing medium of per unit mass flow for the cold-producing medium of per unit mass flow.
The cold-producing medium (gas refrigerant) that is become high pressure by each compressor 2,3 compressions converges at point 65 places.The flow of the cold-producing medium that in refrigerant loop, converges here, as total amount Go (=Gm+Gs).This cold-producing medium that converges is sent to outdoor heat converter 5.In room temperature heat exchanger 5, carry out the heat release that the condensation because of the cold-producing medium that becomes gases at high pressure produces, be cooled into and be liquid refrigerant (BC between condensing zone).That is, the STA representation cold-producing medium of some B is in from point 65 to outdoor heat converter the state 5 the path, is h0 (kJ/kg) in the value of the specific enthalpy of this state.
Cold-producing medium from outdoor heat converter 5 is sent as liquid refrigerant at supercooling heat exchanger 15 places, is branched off into the supercooling liquid refrigerant supercooling (the interval CD of supercooling) among the individual path 27a in the downstream of supercooling heat exchanger 15.Here, T1 among the figure, T2 and T3 represent respectively each temperature t 1 (℃), t2 (℃) and t3 (℃) thermoisopleth (t1〉t2〉t3), the liquid refrigerant that main path 26 is flow through in expression at supercooling heat exchanger 15 places by from t1 (℃) supercooling to t2 (℃).Force value under the state of the some D of the liquid refrigerant after this supercooling is p0 (MPa abs).
Then,, after its part is branched in main path 26, utilize indoor heat converter to expand, become liquid refrigerant (DEm between the breathing space) than the room air low temperature that cools off, low pressure with expansion valve 23 by the liquid refrigerant after the supercooling.Force value under the state that becomes at the some Em place of the liquid refrigerant of low temperature, low pressure is p2 (MPa abs).The liquid refrigerant that becomes the state of an Em is sent to indoor heat converter 8, carries out the evaporation (evaporation region EmAm) by the liquid refrigerant that causes from the room air heat absorption in indoor heat converter 8.Then, the cold-producing medium that becomes gas refrigerant flows through the path 32 of the suction line that constitutes main compressor 2, is sucked to main compressor 2 once more.That is, here, the refrigerant pressure in evaporation region EmAm (value p2) becomes with the cold-producing medium suction pressure Pm of the cold-producing medium of aforementioned main compressor 2 and equates that in refrigerant loop, the flow that is inhaled into the cold-producing medium of main compressor 2 becomes Gm.
On the other hand, be branched off into the supercooling liquid refrigerant among the individual path 27a, expanded with expansion valve 22, compare pressure, temperature reduction (DEs between the breathing space) with the state liquid refrigerant down of a C by the supercooling heat exchanger.At this moment, supercooling with liquid refrigerant from by the supercooling heat exchanger with expansion valve 22 carried out the liquid refrigerant after the aforementioned supercooling temperature t 2 (℃) be reduced to t3 (℃).Like this, among by supercooling heat exchanger 15 overcooled liquid refrigerants, the liquid refrigerant that is branched off in the individual path 27a becomes the supercooling liquid refrigerant.And the flow of liquid refrigerant in refrigerant loop that is branched off into individual path 27a becomes Gs.
Here, the expansion (DEs between the breathing space) of the liquid refrigerant of the branch that causes with expansion valve 22 by the supercooling heat exchanger,, be why because following reason less than the expansion (DEm between the breathing space) of the liquid refrigerant that causes with expansion valve 23 by indoor heat converter.Promptly, this be because, flow through the liquid refrigerant of main path 26 with the liquid refrigerant supercooling in order to use the supercooling that is branched off among the individual path 27a, as long as supercooling is lower than the temperature of sending into supercooling heat exchanger 15 liquid refrigerant (state of some C) before with liquid refrigerant, even use the expansion of liquid refrigerant with the supercooling at expansion valve 22 places at the supercooling heat exchanger, when the force value p0 of the cold-producing medium under the state of a D drops to force value p1, stop, still can carry out supercooling.
In addition, become the supercooling liquid refrigerant of the state of an Es,, the liquid refrigerant that flows through main path 26 is carried out supercooling (evaporation region EsAs) by in supercooling heat exchanger 15, from the liquid refrigerant that flows through main path 26, absorbing heat.Finish this overcooled cold-producing medium, flow through the path 33 of the suction line that constitutes auxiliary compressor 3, sucked auxiliary compressor 3 once more.
Here, in refrigerant loop, the flow through liquid refrigerant of main path 26, a part (flow Gs) is branched off into individual path 27a, the flow Gm that is admitted to the liquid refrigerant of indoor heat converter 8 compares minimizing with total amount Go, but, since the liquid refrigerant of supporting the front by branch in supercooling heat exchanger 15 by supercooling, the heat absorption capacity of the liquid refrigerant of per unit mass flow (cooling capacity) (kJ/kg) improves, so, can keep or improve the cooling capacity in indoor heat converter 8.
Like this, be branched off into the expansion that the supercooling of the flow Gs of individual path 27a is caused with expansion valve 22 by the supercooling heat exchanger with liquid refrigerant, be lower than the expansion that the liquid refrigerant of the flow Gm after the branch is caused with expansion valve 23 by indoor heat converter, terminate in force value p1 by supercooling is descended with the pressure of liquid refrigerant from force value p0, the evaporating pressure among the evaporation region EsAs can be become high pressure.Promptly, owing to compare with the evaporating pressure of the cold-producing medium of remaining flow Gm after the branch, can improve the evaporating pressure of the supercooling of the flow Gs that is branched with cold-producing medium, so, compare with necessary work done during compression Δ Wm among the AmB between the compressional zone, can be reduced between the compressional zone necessary work done during compression Δ Ws among the AsB significantly.Thereby, compare with the work done during compression in main compressor 2, can be reduced in the work done during compression in the auxiliary compressor 3 significantly, can reduce the total compression merit in the engine heat pump.
As the reduction of concrete work done during compression, as follows.In addition, the comparison other here is the total compression merit when utilizing the cold-producing medium of single work done during compression Δ Wm compression total amount Go.In other words, be not possess auxiliary compressor, only having in the refrigerant loop of single compressor, the total compression merit during with the cold-producing medium of work done during compression Δ Wm compression total amount Go.This equates with the total compression merit that pressure liquid refrigerant, between the breathing space among the DEs reduces when force value p0 becomes force value p2 with the supercooling of flow Gs in being branched off into individual path 27a.
At first, with the single work done during compression Δ Wm compression total compression merit the during cold-producing medium of the total amount Go of object as a comparison here, with Go * Δ Wm=Go * (h0-h2) (Go:Gm+Gs) ... (1) expression.
On the other hand, work done during compression as the integral body of the engine heat pump among the present invention, as previously described, the supercooling that is branched off into the flow Gs among the individual path 27a descends with the pressure of liquid refrigerant and terminates in p1 from p0, so, total compression function following formula represents, (Gm * Δ Wm)+(Gs * Δ Ws)=Gm * (h0-h2) }+Gs * (h0-h1) } ... (2).
Promptly, the supercooling that is branched off into the flow Gs among the individual path 27a descends with the pressure of liquid refrigerant and terminates in p1 from p0, reduction amount by the caused work done during compression of evaporating pressure of the cold-producing medium that improves this flow Gs, poor for aforementioned formula (1) and formula (2), that is, reduce and to be equivalent to Gs * (Δ Wm-Δ Ws)=(work done during compression of Gs * (h1-h2).
Like this, by utilizing the auxiliary compressor 3 that drives by engine 4 to compress and being compared the high supercooling cold-producing medium of evaporating pressure (aforementioned cold-producing medium suction pressure) by main compressor 2 refrigerant compressed, can not increase the electric power consumption that is equivalent in the prior art as the auxiliary compressor of driven type newly, in the total compression merit in reducing the cold-producing medium circulation, by the supercooling effect that produces by supercooling heat exchanger 15, keep or the raising cooling capacity.
Secondly, describe for the Capacity Ratio of the main compressor in the engine heat pump according to the present invention 2 with auxiliary compressor 3.
Here said main compressor 2 is ratios of the discharge capacity of each compressor 2,3 with the Capacity Ratio of auxiliary compressor 3, and the discharge capacity of each compressor 2,3 is drawn by their volume capacity and rotating speeds separately.So-called volume capacity is meant the suction volume (cc/ circulation) of the cold-producing medium of each circulation of rotary body (turning around) that each compressor 2,3 is equipped with.In addition, as previously described, because main compressor 2 and auxiliary compressor 3 are driven by common engine 4, so the rotating speed of each compressor 2,3 is determined than (gear ratio) by each belt wheel with respect to the engine belt wheel of engine 4 of main compressor 2 and auxiliary compressor 3 respectively.
Therefore, the discharge capacity of each compressor 2,3 is obtained by the product of volume capacity and belt wheel ratio, when volume capacity, the belt wheel ratio of main compressor 2 is respectively Vm, Um, the volume capacity of auxiliary compressor 3, when the belt wheel ratio is respectively Vs, Us, the discharge capacity of main compressor 2 becomes Vm * Um.The discharge capacity of auxiliary compressor 3 becomes Vs * Us.That is, the Capacity Ratio of the total capacity with respect to main compressor 2 and auxiliary compressor 3 of auxiliary compressor 3 (always discharging capacity) (below be called " auxiliary compressor Capacity Ratio R (%) ") is expressed from the next, R=(Vs * Us)/(Vm * Um)+(Vs * Us) }.Therefore, auxiliary compressor Capacity Ratio R, under the situation that volume capacity Vm, the Vs of each compressor 2,3 equate, determine than Um, Us with respect to the belt wheel of engine 4 separately by them, when each compressor 2,3 is more equal than Um, Us with respect to the belt wheel of engine 4, determine by volume capacity Vm, Vs respectively.In addition, in the present invention, the discharge capacity of auxiliary compressor 3 is less than the discharge capacity of main compressor 2.
And in engine heat pump according to the present invention, this auxiliary compressor Capacity Ratio R (%) is 20% to 29%.Below, describe for the structure of auxiliary compressor Capacity Ratio R in aforementioned number range.
In the refrigerating circuit of engine pump, the influence that is caused by the variation of auxiliary compressor Capacity Ratio R is that the flow Gs that is branched off into individual path 27a (during cool cycles) or 27b (during heat cycles) in main path 26 changes with respect to the ratio of supercooling with the total amount Go of liquid refrigerant.That is, when auxiliary compressor Capacity Ratio R became big, the flow Gs of branch increased with respect to the ratio of the total amount Go of liquid refrigerant, and when auxiliary compressor Capacity Ratio R diminished, the flow Gs of branch reduced with respect to the ratio of the total amount Go of liquid refrigerant.
According to this situation, describe for the number range 20%～29% of auxiliary compressor Capacity Ratio R in the present invention.In addition, in the following description, in main path 26, the supercooling that is branched off into individual path 27a or 27b is defined as " branch's liquid refrigerant " with liquid refrigerant (flow Gs), the liquid refrigerant (flow Gm) that flows through main path 26 after the branch is defined as " main liquid refrigerant ".
At first, about the number range 20%～29% of auxiliary compressor Capacity Ratio R, describe for higher limit being decided to be 29%.
The higher limit 29% of auxiliary compressor Capacity Ratio R is derived by the variation of (during cooling) running efficiency (energy efficiency) when the cool cycles.Promptly, when cooling, by strengthening auxiliary compressor Capacity Ratio R, flow Gs to the liquid refrigerant of individual path 27a branch, that is, it is many with the quantitative change of liquid refrigerant that the liquid refrigerant of the total amount Go that flows through main path 26 is carried out overcooled supercooling, so, supercooling effect in supercooling heat exchanger 15 is increased, and the cooling capacity of the main liquid refrigerant of per unit mass flow also improves.But the flow Gm of main liquid refrigerant has reduced the amount that the flow Gs of the liquid refrigerant that is equivalent to branch is increased, and can not obtain enough cooling capacities in indoor heat converter 8.Based on this phenomenon, determine the higher limit of auxiliary compressor Capacity Ratio R by the variation of running efficiency (energy efficiency).
And, in the present invention, be 29% situation about the higher limit of auxiliary compressor Capacity Ratio R, be illustrated in the curve map of Fig. 4 as the concrete determination data of its basis.
In curve map shown in Figure 4, transverse axis is represented auxiliary compressor Capacity Ratio R (%), and the longitudinal axis is illustrated in the coefficient of performance (Coefficient of Performance:COP) in the cold-producing medium circulation.Represent that with cooling, heating efficiency/Fuel Consumption the value of COP is big more at COP.Expression running efficiency (energy efficiency) is good more.In addition, the curve that dots represents not have auxiliary compressor, the COP in the refrigerant loop structure when being equipped with single compressor.
As from this curve as can be seen, COP during cooling is near 10% the time at auxiliary compressor Capacity Ratio R, and with the numerical value held stationary higher than the situation of single compressed machine, but auxiliary compressor Capacity Ratio R is near 15%, along with auxiliary compressor Capacity Ratio R increases, COP reduces.And R becomes for about 30% the moment from the auxiliary compressor Capacity Ratio, the COP the when COP during cooling is lower than the single compressed machine.Promptly, in the value (about 30%) of the auxiliary compressor Capacity Ratio R in this moment is to attempt total compression merit when being reduced in cooling among aforementioned the present invention so that improve the critical value (higher limit) of running efficiency (COP), if auxiliary compressor Capacity Ratio R less than 30%, the COP when then cooling off can keep the value higher than prior art.Therefore, making the higher limit of the auxiliary compressor Capacity Ratio R among the present invention is 29%.In addition, as can be from finding out the curve, the COP when heating, irrelevant with the value of auxiliary compressor Capacity Ratio R, always show the value higher than prior art.
Secondly, about the number range 20%～29% of auxiliary compressor Capacity Ratio R, describe for lower limit being decided to be 20%.
The lower limit 20% of auxiliary compressor Capacity Ratio R, according to when the heat cycles (during heating) become supercooling heat exchanger 15 main path 26 sides refrigerant inlet tie point 15a refrigerant temperature (below be called " inlet temperature " simply), derive with the relation of the refrigerant temperature of the tie point 15b of the refrigerant outlet of main path 26 sides that become supercooling heat exchanger 15 (below abbreviate " outlet temperature " as).Promptly, when heating, by dwindling auxiliary compressor Capacity Ratio R, be branched off into the flow Gs of branch's liquid refrigerant of individual path 27b, promptly the liquid refrigerant of the total amount Go that flows through main path 26 to be carried out overcooled supercooling few with the quantitative change of liquid refrigerant, so, supercooling effect in supercooling heat exchanger 15 reduces, and branch's liquid refrigerant becomes and evaporates easily.But, the flow Gm of main liquid refrigerant increases the amount that the flow Gs that is equivalent to branch's liquid refrigerant is reduced, the liquid refrigerant that becomes total amount Go can not abundant overcooled state in supercooling heat exchanger 15, in supercooling heat exchanger 15, with respect to roughly certain inlet temperature, outlet temperature rises.This outlet temperature in supercooling heat exchanger 15 can hinder the sufficient supercooling degree of acquisition in supercooling heat exchanger 15 with respect to the rising of inlet temperature when heating.Promptly, when heating, performance in order to ensure supercooling heat exchanger 15, (for example be necessary to be selected in by certain above temperature difference between the outlet temperature after the inlet temperature of overcooled liquid refrigerant and the supercooling, more than 5 ℃), that is the selected capacity (structure) that produces the auxiliary compressor 3 of supercooling degree.Determine the lower limit of auxiliary compressor Capacity Ratio R by this.
And, in the present invention, being decided to be 20% for lower limit with auxiliary compressor Capacity Ratio R, the concrete determination data that expression becomes its basis is illustrated in the curve map of Fig. 5.
In the described curve map of Fig. 5, transverse axis is represented auxiliary compressor Capacity Ratio R (%), the longitudinal axis represent the inlet temperature of supercooling heat exchanger 15 or outlet temperature (℃), the numerical value separately when being illustrated in heating.
As from finding out this curve, the value of the inlet temperature of supercooling heat exchanger 15 and auxiliary compressor Capacity Ratio R is irrelevant, is roughly certain temperature (32～33 ℃).On the other hand, the outlet temperature of supercooling heat exchanger 15 is accompanied by the minimizing of auxiliary compressor Capacity Ratio R, rises to high temperature from the temperature that is lower than inlet temperature.Promptly, become the moment of a certain value from auxiliary compressor Capacity Ratio R, outlet temperature becomes than inlet temperature height, and, in the present invention, when heating, can guarantee the inlet temperature of supercooling heat exchanger 15 performances and the relation of outlet temperature, it is low approximately more than 5 ℃ or 5 ℃ with respect to inlet temperature to be preferably outlet temperature, and the critical value (lower limit) that outlet temperature becomes than the low approximately auxiliary compressor Capacity Ratio R more than 5 ℃ or 5 ℃ of inlet temperature is 20%.Therefore, the lower limit of the auxiliary compressor Capacity Ratio R among the present invention is 20%.
As explained above, for the auxiliary compressor Capacity Ratio R in the engine heat pump according to the present invention, the lower limit of determining during according to higher limit of when cooling off, determining and heating, its number range is set in 20% to 29%, whereby, when cooling, keep or the raising cooling capacity, simultaneously, when heating, can guarantee the performance of supercooling heat exchanger 15.Promptly, utilizing common engine 4 to drive in the structure of the present invention of main compressor 2 and auxiliary compressor 3, by making auxiliary compressor Capacity Ratio R in 20% to 29% scope, can carry out the good running of running efficiency (energy efficiency) during cooling and during heating.
In addition, in refrigerant loop structure according to engine heat pump of the present invention, from the transmission of engine 4, also can adopt the structure of buncher (Continuously Variable Transmission:CVT) to the driving force of main compressor 2 and auxiliary compressor 3.
In this case, consider the critical value of the auxiliary compressor Capacity Ratio R under each situation when foregoing when cooling and heating, change the gear ratio of main compressor 2 and auxiliary compressor 3 by CVT.
Specifically, in engine heat pump according to the present invention, in when cooling, as long as the value that makes auxiliary compressor Capacity Ratio R less than aforementioned higher limit, in addition, when heating, as long as the value that makes auxiliary compressor Capacity Ratio R is greater than aforementioned lower limit.That is, control CVT changes gear ratio when when cooling and heating, makes when cooling auxiliary compressor Capacity Ratio R not enough about 30%, and when heating, auxiliary compressor Capacity Ratio R is more than 20%.
Like this, by utilizing the structure of CVT, can improve the volume capacity Vs of the auxiliary compressor of setting than Um with respect to the volume capacity Vm of main compressor 2 and belt wheel 3 and belt wheel the free degree than Us.In addition, when cool cycles, as long as determine higher limit, when heat cycles, as long as determine lower limit, so, when when cooling and heating, can set auxiliary compressor Capacity Ratio R for more suitably value respectively, so that improve each running efficiency (energy efficiency) in circulating.
In addition, in engine heat pump according to the present invention, engine waste heat recover 6 is set side by side with outdoor heat converter 5.And, utilize the waste heat recoverer 6 of this engine will be in main path 26 the supercooling liquid refrigerant evaporates of branch, simultaneously, utilize auxiliary compressor 3 with its compression.
As previously described, engine waste heat recover 6 is used in the branch's liquid refrigerant heat absorption by supercooling heat exchanger 15 of when heating, evaporates, in this engine waste heat recover 6, by carrying out the heat exchange of branch's liquid refrigerant and the engine cooling water CW higher, make branch's liquid refrigerant heat absorption, evaporation than this branch's liquid refrigerant temperature.
Secondly, about the kind of refrigeration cycle on the mollier diagram (Fig. 3), describe for the situation of heat cycles.In addition, for the part that the situation with aforementioned cool cycles repeats, omit its explanation.
At first, by the cold-producing medium (gas refrigerant) of main compressor 2 and auxiliary compressor 3 compressions becoming high pressure, 65 places converge at point.This cold-producing medium that converges is sent to indoor heat converter 8.In indoor heat converter 8, heat release is carried out in the condensation of the cold-producing medium by becoming gases at high pressure, and the indoor heat release to heating simultaneously, is cooled, and becomes liquid refrigerant (BC between condensing zone).That is, the state of some B, expression cold-producing medium are positioned at from point 65 to indoor heat converter the state in 8 path.
Cold-producing medium as liquid refrigerant is sent from indoor heat converter 8 in supercooling heat exchanger 15, is branched off into the supercooling liquid refrigerant supercooling (the interval CD of supercooling) among the individual path 27b in the downstream of supercooling heat exchanger 15.
Then,, in main path 26, after its part is branched, utilize outdoor heat converter to expand, become the liquid refrigerant (DEm between the breathing space) of low temperature, low pressure with expansion valve 21 by the liquid refrigerant after the supercooling.Become a liquid refrigerant of Em state and be sent to outdoor heat converter 5, in outdoor heat converter 5, carry out the evaporation (evaporation region EmAm) of cold-producing medium by absorbing heat from outside atmosphere.Then, the cold-producing medium that becomes gas refrigerant flows through the path 32 of the suction line that constitutes main compressor 2, is sucked to main compressor 2 once more.
On the other hand, be branched off into the supercooling liquid refrigerant of individual path 27b, be inflated with expansion valve 22 places at the supercooling heat exchanger, compare with the liquid refrigerant under the state of a C, pressure, temperature reduce (DEs between the breathing space).Like this, in by supercooling heat exchanger 15 overcooled liquid refrigerants, the liquid refrigerant that is branched off among the individual path 27b becomes the supercooling liquid refrigerant.And the flow of liquid refrigerant in refrigerant loop that is branched off among the individual path 27b becomes Gs.
Then, become the supercooling liquid refrigerant of the state of an Es,, the liquid refrigerant that flows through main path 26 is carried out supercooling by in supercooling heat exchanger 15, absorbing heat from the liquid refrigerant that flows through main path 26.Supercooling liquid refrigerant by supercooling heat exchanger 15 is fed to engine waste heat recover 6.In this engine waste heat recover 6, carry out the heat exchanger of supercooling with liquid refrigerant and engine cooling water CW, supercooling is evaporated (evaporation region EsAs) with the liquid refrigerant heat absorption.The cold-producing medium of this evaporation flows through the path 33 of the suction line that constitutes auxiliary compressor 3, is sucked auxiliary compressor 3 once more.
Like this, by when heating, carrying out supercooling, utilize effect as described below to improve running efficiency (energy efficiency).
Flow through the liquid refrigerant of the total amount Go of main path 26, as previously described, in supercooling heat exchanger 15 by supercooling.Here, by with the liquid refrigerant supercooling, the heat absorption capacity of the cold-producing medium of per unit mass flow (kJ/kg) improves.That is, ability that liquid refrigerant in the outdoor heat converter 5 after supercooling, the per unit mass flow absorbs heat from outside atmosphere improves, and the liquid refrigerant with not by supercooling the time is compared, and can absorb equal heat with a spot of liquid refrigerant.By this, when heating, the flow Gm of the main liquid refrigerant that is admitted to outdoor heat converter 5 can be reduced, the total amount Go of the cold-producing medium of circulation in the cold-producing medium circulation can be reduced.As a result, can be reduced in the total compression merit in the cold-producing medium circulation, improve running efficiency (energy efficiency).
Like this, with outdoor heat converter 5 engine waste heat recover 6 is set side by side, in branch's liquid refrigerant evaporates of utilizing engine waste heat recover 6 that supercooling is used, simultaneously, compress, by this structure with auxiliary compressor 3, total compression merit in the time of can reducing cooling in the aforementioned range by auxiliary compressor Capacity Ratio R is in, when heating, also needn't increase electric power consumption newly, can reduce the total compression merit.
And then, in when heating, owing to, improve the heat absorption capacity of the cold-producing medium of per unit mass flow from outside atmosphere by the supercooling effect by carrying out the supercooling of liquid refrigerant, so, can reduce the total amount of the cold-producing medium that in the cold-producing medium circulation, flows.As a result, the total compression merit can be reduced, running efficiency (energy efficiency) can be improved.
In addition, in Shuo Ming the engine heat pump, also can distinguish the main compressor 2 and the auxiliary compressor 3 that drive separately by engine 4 drivings in the above.By this structure, can according to the size of air conditioner load carry out main compressor 2 and auxiliary compressor 3 running, stop, can improving running efficiency (energy efficiency).
In this case, as concrete structure, as shown in Figure 1, the main compressor that the cut-out of carrying out the driving force of engine 4 respectively, connection (be connected, disconnected switching) be set between engine 4 and main compressor 2 and auxiliary compressor 3 with clutch 42 and auxiliary compressor with clutch 43.
And the path 32 that utilizes access path 34 will constitute the suction line of main compressor 2 is communicated with the path 33 of the suction line that constitutes auxiliary compressor 3, simultaneously, on this access path 34 open and close valve 35 is set.Promptly, make by open and close valve 35 is opened and closed and switch the connection of access path 34, the switching of non-connection, can toggle path 32 and being communicated with of path 33, unconnected structure, make the basic, normal, high load condition of refrigerant loop corresponding to air conditioner load, carry out running in various load conditions.
Here, as shown in Figure 2, aforementioned controller 25 is connected with clutch 43 with clutch 42 and auxiliary compressor with main compressor, and controller 25 is controlled from cut-out, the connection of engine 4 to the driving force of each clutch according to each load condition.In addition, this controller 25 is connected with open and close valve 35, the switching of control open and close valve 35.
By such structure, for example, when when cooling and heating, carry out control respectively as described below corresponding to each load condition.That is, when cooling, be under the situation of underload at air conditioner load, auxiliary compressor 3 individual operations, under the situation of moderate duty, main compressor 2 individual operations.And, when high load capacity, as previously described, make main compressor 2 and auxiliary compressor 3 both runnings, carry out supercooling with supercooling heat exchanger 15 simultaneously.On the other hand, when heating, be under the situation of underload at air conditioner load, auxiliary compressor 3 individual operations, under the situation of moderate duty, main compressor 2 individual operations carry out heat exchange with engine waste heat recover 6 simultaneously.And, under the situation of high load capacity, as previously described, utilize main compressor 2 and auxiliary compressor 3 both runnings, simultaneously, carry out supercooling and the heat exchange in engine waste heat recover 6 in supercooling heat exchanger 15.
In addition, the height of said air conditioner load here is a underload in the scope 0%～15% roughly at the air conditioner load (%) of engine heat pump, is moderate duty in 15%～60% scope, is high load capacity in 60%～100% scope.
Running during at first, for cooling describes.
At air conditioner load is under the situation of underload, is auxiliary compressor 3 individual operations.In this case, controller 25 makes main compressor be in off-state with clutch 42, opens open and close valve 35 simultaneously.That is, the driving force of engine 4 is only passed to auxiliary compressor 3, simultaneously, be communicated with path 33, utilize the cold-producing medium of auxiliary compressor 3 compression total amount Go as the suction line of auxiliary compressor 3 by making as the path 32 of the suction line of main compressor 2.In addition, in this case, by the switching of control supercooling heat exchanger with expansion valve 22, whether control carries out the supercooling by 15 generations of supercooling heat exchanger.And, when utilizing supercooling heat exchanger 15 to carry out supercooling, in order to be reduced in pressure loss that point 64 (Fig. 1) locates etc., consider pressure dependence, controller 25 control supercooling heat exchangers use expansion valve 22 and indoor heat converter with the aperture of expansion valve 23, make refrigerant pressure that comes from path 32 and the refrigerant pressure that comes from path 33 about equally.
In addition, be under the situation of moderate duty at air conditioner load, be main compressor 2 individual operations.In this case, controller 25 makes auxiliary compressor become the state of disconnection with clutch 43, makes the driving force of engine 4 only pass to main compressor 2, utilizes the cold-producing medium of main compressor 2 compression total amount Go.In addition, in this case, when utilizing supercooling heat exchanger 15 to carry out supercooling, controller 25 is opened open and close valve 35, simultaneously, control supercooling heat exchanger is with expansion valve 22 and the indoor heat converter aperture with expansion valve 23, makes the refrigerant pressure of locating to come from path 32 at point 63 (Fig. 1) and the refrigerant pressure that comes from path 33 about equally.
In addition, be under the situation of high load capacity at air conditioner load, carry out both runnings of main compressor 2 and auxiliary compressor 3, utilize supercooling heat exchanger 15 to carry out supercooling.In this case, controller 25 makes main compressor, and both all become the state of connection with clutch 43 with clutch 42 and auxiliary compressor, simultaneously, close open and close valve 35.That is, make the driving force of engine 4 pass to each compressor 2,3, simultaneously, cut-out path 32 is communicated with path 33, utilizes the cold-producing medium of main compressor 2 compression flow Gm, utilizes the supercooling cold-producing medium of auxiliary compressor 3 compression flow Gs.
Secondly, describe for adding heat run.
At air conditioner load is under the situation of underload, is auxiliary compressor 3 individual operations.That is, in this case, the situation of the underload in the running of the form of utilizing the control that controller 25 carries out during with aforementioned cooling is the same.
In addition, air conditioner load is under the situation of moderate duty, is main compressor 2 individual operations, simultaneously, utilizes engine waste heat recover 6 to carry out heat exchange.In this case, controller 25 makes auxiliary compressor be in the state of disconnection with clutch 43, simultaneously, opens open and close valve 35.That is, make the driving force of engine 4 only pass to main compressor 2, simultaneously, utilize engine waste heat recover 6 to carry out heat exchanger, utilize main compressor 2 to be compressed in the cold-producing medium of the total amount Go that converges at point 63 places.In this case, when utilizing supercooling heat exchanger 15 to carry out supercooling, controller 25 is opened open and close valve 35, simultaneously, control supercooling heat exchanger is with expansion valve 22 and the outdoor heat converter aperture with expansion valve 21, and the pressure that makes the cold-producing medium that comes from path 32 at point 63 places and the refrigerant pressure that comes from path 33 are about equally.
In addition, be under the situation of high load capacity at air conditioner load, be main compressor 2 and auxiliary compressor 3 both runnings, simultaneously, carry out in the supercooling at supercooling heat exchanger 15 places and in the heat exchange at engine waste heat recover 6 places.In this case, controller 25, both become on-state with clutch 43 with clutch 42 and auxiliary compressor to make main compressor, close open and close valve 35 simultaneously.Promptly, the driving force of engine 4 is passed to each compressor 2,3, simultaneously, cut-out path 32 is communicated with path 33, utilize the cold-producing medium compression of main compressor 2, utilize auxiliary compressor 3 to be compressed in the supercooling cold-producing medium that engine waste heat recover 6 places carry out the flow Gs of heat exchange flow Gm.
Like this, owing to can switch the structure of the running of main compressor 2 and auxiliary compressor 3 according to the height of required air conditioner load by forming, operating condition in the time of can reducing the low sub-load of the efficiency of combustion of engine 4, so, running efficiency (energy efficiency) can be improved.
The industrial possibility of utilizing
Engine heat pump of the present invention utilizes the motor driven compressor by being widely used in Engine heat pump, the consumption that can not increase electric power can reduce work done during compression, can improve Running efficiency (energy efficiency).
Claims (2)
1. engine heat pump, comprise: by engine-driven main compressor and auxiliary compressor, indoor heat converter, outdoor heat converter, the indoor heat converter expansion valve, the outdoor heat converter expansion valve, and supercooling heat exchanger, described supercooling heat exchanger is arranged on liquid refrigerant among the access path of described indoor heat converter and described outdoor heat converter by in the path, to be branched off into liquid refrigerant in the individual path as the supercooling liquid refrigerant, the liquid refrigerant that utilizes this supercooling with liquid refrigerant branch to be supported the front carries out supercooling, described engine heat pump converges cold-producing medium of being discharged by aforementioned auxiliary compressor and the cold-producing medium of discharging from aforementioned main compressor
It is characterized in that, utilize described auxiliary compressor to compress aforementioned supercooling liquid refrigerant, simultaneously, the capacity of described auxiliary compressor is 20% to 29% with respect to the Capacity Ratio of the total capacity of described main compressor and described auxiliary compressor,
Be provided with the expansion valve that described supercooling heat exchanger is used, simultaneously, the expansion of remaining liquid refrigerant is suppressed more after the branch that the described supercooling that caused with expansion valve by described supercooling heat exchanger causes with expansion valve by described indoor heat converter with the expansion ratio of liquid refrigerant by making, make described supercooling with the evaporation of liquid refrigerant press with described branch after the evaporation of remaining liquid refrigerant press to compare and uprise
With outdoor heat converter the engine waste heat recover is set side by side, evaporates described supercooling liquid refrigerant by described engine waste heat recover.
2. engine heat pump as claimed in claim 1, it is characterized in that, when air conditioner load is 0～15% underload, have only described auxiliary compressor to be driven, when air conditioner load is 15～60% middle load, have only described main compressor to be driven, when air conditioner load was 60～100% high load capacity, described main compressor and described auxiliary compressor were driven.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004150371A JP4336619B2 (en) | 2004-05-20 | 2004-05-20 | Engine heat pump |
| JP150371/2004 | 2004-05-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1957211A CN1957211A (en) | 2007-05-02 |
| CN100470165C true CN100470165C (en) | 2009-03-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200580016138XA Expired - Fee Related CN100470165C (en) | 2004-05-20 | 2005-04-18 | Engine heat pump |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20070295025A1 (en) |
| EP (1) | EP1762792A4 (en) |
| JP (1) | JP4336619B2 (en) |
| CN (1) | CN100470165C (en) |
| WO (1) | WO2005114064A1 (en) |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008145002A (en) * | 2006-12-07 | 2008-06-26 | Sanyo Electric Co Ltd | Air conditioning device |
| JP5163161B2 (en) * | 2008-02-01 | 2013-03-13 | ダイキン工業株式会社 | Auxiliary heating unit and air conditioner |
| JP5149663B2 (en) * | 2008-03-24 | 2013-02-20 | ヤンマー株式会社 | Engine driven heat pump |
| FR2956190B1 (en) * | 2010-02-08 | 2012-04-13 | Muller & Cie Soc | HEAT PUMP WITH POWER STAGES |
| KR101212681B1 (en) * | 2010-11-08 | 2012-12-17 | 엘지전자 주식회사 | air conditioner |
| JP6134477B2 (en) * | 2012-01-10 | 2017-05-24 | ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド | Refrigeration equipment and refrigerator unit |
| KR101497813B1 (en) * | 2013-06-27 | 2015-03-04 | 한국교통대학교산학협력단 | Vapor injection heat pump system |
| EP3080527B1 (en) * | 2013-12-12 | 2022-05-04 | Johnson Controls Tyco IP Holdings LLP | Steam turbine driven centrifugal heat pump |
| CN105466063A (en) * | 2015-12-16 | 2016-04-06 | 珠海格力电器股份有限公司 | Heat pump system |
| CN105588357B (en) * | 2015-12-16 | 2019-04-16 | 珠海格力电器股份有限公司 | Heat pump system |
| CN106766327A (en) * | 2016-11-29 | 2017-05-31 | 珠海格力电器股份有限公司 | Air conditioner |
| CN106801953A (en) * | 2016-11-29 | 2017-06-06 | 珠海格力电器股份有限公司 | Air conditioner |
| KR102105706B1 (en) * | 2017-12-12 | 2020-04-28 | 브이피케이 주식회사 | Heat pump system, bidiectional injection operation method of the heat pump |
| EP3781883A1 (en) * | 2018-04-16 | 2021-02-24 | Carrier Corporation | Dual compressor heat pump |
| CN110173912B (en) * | 2019-04-29 | 2020-10-02 | 同济大学 | Mixed working medium compression circulation system with mechanical heat recovery function and working method |
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| CN1205073A (en) * | 1996-08-14 | 1999-01-13 | 大金工业株式会社 | Air conditioner |
| CN1231408A (en) * | 1998-03-04 | 1999-10-13 | 株式会社日立制作所 | Refrigerating unit |
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| US2242588A (en) * | 1938-02-07 | 1941-05-20 | Honeywell Regulator Co | Heating system |
| US2273281A (en) * | 1938-07-11 | 1942-02-17 | Honeywell Regulator Co | Control system |
| JPS60226669A (en) * | 1984-04-24 | 1985-11-11 | 三洋電機株式会社 | Refrigerator |
| JPS62293066A (en) * | 1986-06-12 | 1987-12-19 | ヤンマーディーゼル株式会社 | Engine drive type heat pump type air conditioner |
| JPH0618121A (en) * | 1992-06-30 | 1994-01-25 | Nippondenso Co Ltd | Engine driven heat pump type air conditioner |
| JPH11193966A (en) * | 1997-12-28 | 1999-07-21 | Tokyo Gas Co Ltd | Gas heat pump apparatus |
| JP4214021B2 (en) * | 2003-08-20 | 2009-01-28 | ヤンマー株式会社 | Engine heat pump |
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- 2004-05-20 JP JP2004150371A patent/JP4336619B2/en not_active Expired - Fee Related
-
2005
- 2005-04-18 US US11/569,429 patent/US20070295025A1/en not_active Abandoned
- 2005-04-18 CN CNB200580016138XA patent/CN100470165C/en not_active Expired - Fee Related
- 2005-04-18 WO PCT/JP2005/007411 patent/WO2005114064A1/en active Application Filing
- 2005-04-18 EP EP05730684A patent/EP1762792A4/en not_active Withdrawn
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1205073A (en) * | 1996-08-14 | 1999-01-13 | 大金工业株式会社 | Air conditioner |
| CN1231408A (en) * | 1998-03-04 | 1999-10-13 | 株式会社日立制作所 | Refrigerating unit |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1762792A1 (en) | 2007-03-14 |
| JP4336619B2 (en) | 2009-09-30 |
| JP2005331177A (en) | 2005-12-02 |
| EP1762792A4 (en) | 2008-05-07 |
| US20070295025A1 (en) | 2007-12-27 |
| CN1957211A (en) | 2007-05-02 |
| WO2005114064A1 (en) | 2005-12-01 |
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