CN100462649C - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN100462649C CN100462649C CNB2005100704528A CN200510070452A CN100462649C CN 100462649 C CN100462649 C CN 100462649C CN B2005100704528 A CNB2005100704528 A CN B2005100704528A CN 200510070452 A CN200510070452 A CN 200510070452A CN 100462649 C CN100462649 C CN 100462649C
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/004—Outdoor unit with water as a heat sink or heat source
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
- F25B2313/0213—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during heating
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0252—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses
- F25B2313/02521—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units with bypasses during cooling
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
- F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
- F25B2313/02543—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements during heating
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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
- F25B2327/00—Refrigeration system using an engine for driving a compressor
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
To control the temperature of cooling water without using a wax three-way valve. A refrigerant circuit includes an auxiliary evaporator 15, and a cooling water circuit includes a main cooling passage for circulating the cooling water passed through an engine 31 to a cooling water pump 39 via an outdoor heat exchanger 19, a sub-cooling passage for circulating the cooling water passed through the engine 31 to the cooling water pump 39 via the auxiliary evaporator 15, and an electric three-way valve 37 sorting the cooling water to the main cooling passage and to the sub-cooling passage. When the temperature of the cooling water is lower than a target temperature, the cooling water is sorted to both the main cooling passage and the sub-cooling passage, based on the temperature difference between the temperature of the cooling water and the target temperature, or the whole quantity of the cooling water is sorted to the sub-cooling passage, and the number of revolutions of the cooling water pump 39 is reduced.
Description
Technical field
The present invention relates to conditioner by the gas heat pump type of gas engine drive compression machine; Especially, relate to the technology that is used to keep cool off the cooling water temperature of gas engine.
Background technology
Now, having connection as everyone knows is the refrigerant loop of gas-engine-driven compressor, cross valve, outdoor heat converter and chamber heat exchanger by internal combustion engine, and has by cooling water pump and send into cooling water and cool off the gas heat pump type conditioner of the chilled(cooling) water return (CWR) of gas engine to above-mentioned engine.(for example, with reference to patent documentation 1).
In addition, also know, in above-mentioned conditioner, in order to control cooling water temperature, and at the outlet side of engine lining wax triple valve (Automatic temp. adjusting valve) is set, be used for when cooling water temperature be set point of temperature when following, should make the cooling water temperature rising, the engine export side of short circuit cooling water and the suction side of cooling water pump do not make cooling water flow through outdoor heat converter.
[patent documentation 1]
The spy opens the 2003-232582 communique.
But, in existing technology, exist because carry out cooling water temperature control, the problem that cost improves with lining wax triple valve; In addition, also have in lining wax triple valve control cooling water temperature, existence can not be controlled the problem of cooling water temperature fully.
Summary of the invention
The present invention is mirror with the problems referred to above, and purpose provides the conditioner that does not use lining wax triple valve and can control cooling water temperature.
In order to achieve the above object, the present invention is a kind of conditioner, it has: connect the refrigerant loop by engine-driven compressor, cross valve, outdoor heat converter and indoor heat converter, send into cooling water and the chilled(cooling) water return (CWR) of cooling off above-mentioned engine by cooling water pump to engine.In this aircondition, in above-mentioned refrigerant loop, be provided with the auxiliary evaporator of the cooling water circulation of the above-mentioned engine of cooling; And, in above-mentioned chilled(cooling) water return (CWR), be provided with, the cooling water of above-mentioned engine of flowing through passes back into the main cooling path of above-mentioned cooling water pump via above-mentioned outdoor heat converter, the cooling water of above-mentioned engine of flowing through passes back into the secondary cooling path of above-mentioned cooling water pump via above-mentioned auxiliary evaporator, above-mentioned cooling water is distributed to the electric T-shaped valve of above-mentioned main cooling path and above-mentioned secondary cooling path, when above-mentioned cooling water temperature is lower than target temperature, based on the temperature of above-mentioned cooling water and the temperature difference of target temperature, control above-mentioned electric T-shaped valve, thus, both sides at above-mentioned main cooling path and above-mentioned secondary cooling path distribute above-mentioned cooling water, perhaps, above-mentioned cooling water whole are distributed to above-mentioned secondary cooling path, and, reduce the rotating speed of above-mentioned cooling water pump.
In addition, the present invention in foregoing invention, when above-mentioned cooling water temperature is higher than target temperature, based on the temperature difference of cooling water temperature and target temperature, improves the rotating speed of above-mentioned cooling water pump.
In addition, the present invention in one of foregoing invention item, is provided with bypass path in above-mentioned secondary cooling path, and it is used for shunting cooling water and the above-mentioned auxiliary evaporator of bypass that flows at this pair cooling path.
In addition, the present invention, in one of foregoing invention item, above-mentioned refrigerant loop has the expansion valve of change via the flow of the refrigerant of above-mentioned outdoor heat converter, the above-mentioned auxiliary evaporator of inflow, when above-mentioned cooling water temperature is lower than target temperature, reduce the aperture of above-mentioned expansion valve, the flow of the refrigerant that flows into above-mentioned auxiliary evaporator is reduced.
According to the present invention, do not use lining wax triple valve, can control the temperature of cooling water.
Description of drawings
Fig. 1 is the schematic diagram of structure that expression relates to the conditioner of embodiments of the present invention;
Fig. 2 is used to illustrate the chart that keeps coolant water temperature control;
Fig. 3 is used to illustrate the chart that keeps coolant water temperature control.
The specific embodiment
Below, with reference to accompanying drawing, describe one embodiment of the present invention in detail.
Fig. 1 is the structural representation of gas heat pump type air conditioner 100.In the figure, represent the refrigerant loop, represent the chilled(cooling) water return (CWR) with heavy line with thick chain-dotted line.Air conditioner 100 has indoor unit 1 and outdoor unit 3; The indoor heat converter 7 of current divider 5 and fan 9 etc. have been set up indoor unit 1 setting.In addition, in outdoor unit 3 sides,, compressor 11, electromagnetic type cross valve 13, auxiliary evaporator 15 (secondary evaporimeter), the outdoor heat converter 19 of having set up current divider 17, fan 21, expansion valve 72 etc. are set as the critical piece in refrigerant loop; As the critical piece of chilled(cooling) water return (CWR), it is cooling water pump 39, radiator (air heat exchanger) 20 etc. that engine 31, exhaust heat exchanger 33, electric T-shaped valve 37, electrodynamic type AC pump are set.Among the figure, the 43rd, be connected the blast pipe of exhaust heat exchanger 33, the 45th, be used to control the frequency converter of the rotating speed of cooling water pump 39, the 47th, the fan electromotor of drive fan 21, the 49th, connect the flexible connection of engine 31 and compressor 11.Above-mentioned expansion valve 72 is regulated from the flow of indoor heat converter 7 to the refrigerant of outdoor heat converter 19 backflows, and in addition, radiator 20 carries out the cooling water heat radiation.In order to suppress the heat affecting to outdoor heat converter 19, outdoor heat converter 19 relatively is configured in this radiator 20 leeward of fan 21.
In the inside of outdoor unit 3 control module 61 is set, it drives control cross valve 13, electric T-shaped valve 37, frequency converter 45, fan electromotor 47 etc.Control module 61 at first is made of CPU, and constitute by input/output interface and ROM, RAM, timer etc., on this input interface, connecting, be arranged on temperature detector 63 on the cooling water pipe 87 of outlet side of engine 31, be installed in heat exchange temperature detector 65 on the outdoor heat converter 19, be arranged on delivery temperature detector 67 on the blast pipe 43, be installed in outside air temperature detector 69 on the outside wall surface etc.In addition, control module 61 is connected with the illustrated control module that do not have of indoor unit 1 side, carries out signal mutually and receives, sends.
Below, flowing of refrigerant is described.When warming operation, liquid coolant flows into outdoor unit 3 sides from refrigerant pipe 71, via expansion valve 72, current divider 17, outdoor heat converter 19, coolant piping 75, cross valve 13, coolant piping 77, flow into auxiliary evaporator 15, between by two heat-exchanger 19,15, be heated.In addition, at auxiliary evaporator 15, adopt cooling water by the two bushing types around the coolant piping; At outdoor heat converter 19, adopt the board-like heat radiation type structure (with reference to outdoor heat converter 19 and the radiator 20 of Fig. 1) that connects coolant piping and cooling water pipe by board-like fin.At two heat-exchanger 19,15 heated gas coolants, flow into compressor 11 via coolant piping 78, by being further heated in this compression.High-temperature gas refrigerant from compressor 11 discharges, via coolant piping 79, cross valve 13, coolant piping 81, flow into the indoor heat converter 7 of indoor unit 1 side, emit heat to the air that enters the chamber by fan 9, become liquid coolant after heating, flow into outdoor unit 3 sides again from coolant piping 71.
Like this, inside at outdoor unit 3, be provided for when warming operation, utilizing the auxiliary evaporator 15 and being used for of heat of the cooling water of engine 31 when warming operation, to utilize the exhaust heat exchanger 33 of the heat of exhaust of engine 31, therefore, when warming operation, even outside air temperature also can heat when low fully.
In addition, when refrigeration is turned round, switch cross valve 6.That is, the gas coolant of the high temperature of discharging from compressor 11 is via coolant piping 79, cross valve 13, coolant piping 75, and inflow outdoor heat exchanger 19 is at this, by temperature low extraneous air cooling, liquefaction.The refrigerant of this liquefaction is via coolant piping 71, flow into the indoor heat converter 7 of indoor unit 1 side, absorb heat and evaporate from room air, flow into outdoor unit 3 sides again via coolant piping 81, via cross valve 13, coolant piping 77, auxiliary evaporator 15, coolant piping 78, flow into compressor 78 again.Here, when refrigeration is turned round, during except that warm-operation and coolant water temperature when low, stop to carry out the cooling water circulation to auxiliary evaporator 15, do not carry out the refrigerant heating at this auxiliary evaporator 15.
Below, illustrate in greater detail the structure of chilled(cooling) water return (CWR).
As illustrated in fig. 1, remove the chilled(cooling) water return (CWR) has, the cooling water of discharging from cooling water pump 39 is successively via exhaust heat exchanger 33, engine 31, electric T-shaped valve 37, radiator 20, pass back into outside the main cooling path of cooling water pump 39, also have, the cooling water of discharging from engine 31 passes back into the secondary cooling water path of cooling water pump 39 via electric T-shaped valve 37, auxiliary evaporator 15.
The present cooling-water flow during the explanation warming operation, the cooling water of discharging from cooling water pump 39 via cooling water pipe 85, flow into exhaust heat exchanger 33, by inflow engine 31 after the exhaust heating.Engine 31 is cooled off, become the cooling water of high temperature, this high-temperature cooling water is via cooling water pipe 87, electric T-shaped valve 37, cooling water pipe 89, and inflow radiator 20 is emitted heat energy.And the cooling water of emitting heat energy at radiator 20 passes back into cooling water pump 39 again via cooling water pipe 91.
Here, when warming operation, high-temperature cooling water is not only via radiator 20, and, also via auxiliary evaporator 15, heat refrigerant as described later auxiliaryly.In addition, when refrigeration was turned round, the cooling water of high temperature at this, was emitted heat energy only via radiator 20.
In addition, the structure of assembling radiator 20 on outdoor heat converter 19 also can be regarded this heat exchanger as the structure of single outdoor heat converter of the radiator of the condenser of double as refrigerant and cooling water with being integral.
On the other hand, at secondary cooling path, the cooling water from cooling water pump 39 is discharged flows into exhaust heat exchanger 33 via cooling water pipe 85, inflow engine 31 after being heated by exhaust.Engine 31 is cooled off and become the cooling water of high temperature, and this high-temperature cooling water via cooling water pipe 87, electric T-shaped valve 37, cooling water pipe 95, flows into auxiliary evaporator 15 when warming operation, by to refrigerant heating emit heat energy.And, emit the cooling water of heat energy at auxiliary evaporator 15, via cooling water pipe 97,91, at cooling water pipe 91 interflow,, pass back into cooling water pump 39 via this cooling water pipe 91.
Yet, general, in the gas heat pump type conditioner,,,, therefore, there is the time-consuming such problem of warming operation so carry out heat exchange with refrigerant hardly at auxiliary evaporator because coolant water temperature is low when when stopping the back starting for a long time.During severe winter etc., the start-up time during warming operation is long especially.
Therefore, in the present embodiment, when cooling water temperature is low, make cooling water, therefore, cooling water temperature is risen rapidly only in above-mentioned secondary cooling path circulation.
More specifically, when after stopping for a long time, beginning to pilot engine 31 the time, when engine 31 outlet coolant water temperatures are lower than target temperature (is 70 ℃ in present embodiment), control module 61 is closed radiator 20 sides of electric T-shaped valve 37 and is opened auxiliary evaporator 15 sides, and the whole of cooling water are circulated in secondary cooling water path.That is, auxiliary evaporator 15 is littler than radiator 20 heat dissipation capacities that are arranged on main cooling path, and therefore, cooling water is at secondary cooling path circulation time, and water temperature descends and suppressed, and is littler than descending in main cooling path circulation time temperature, forms cooling water temperature and rises.
At this, use the auxiliary evaporator 15 littler than radiator 20 heat dissipation capacities, can either reduce the heat dissipation capacity of cooling water at secondary cooling path circulation time, can promote cooling water temperature rise De Genggao again.But, when auxiliary evaporator 15 uses the too small evaporimeter of heat dissipation capacities, because the kind difference of outdoor heat converter 19, might increase the crushing consumption of refrigerant, cause refrigerant loop ability drop.
Therefore, in present embodiment, form, the structure of bypass pipe 99 is set at above-mentioned secondary cooling path as illustrated in fig. 1, is used for making a part of cooling water flow through the bypass (making a circulation) of this auxiliary evaporator 15 at the front of auxiliary evaporator 15 shunting cooling water, therefore, the crushing consumption of refrigerant is increased, and more the lowland suppresses the heat dissipation capacity of the cooling water in the secondary cooling path, and cooling water temperature is promptly risen.In addition, in the structure that bypass pipe 99 is set in this wise,, change the ratio that cooling water flows into each amount of auxiliary evaporator 15 and bypass pipe 99, can regulate the heat dissipation capacity in the secondary cooling path simply by suitably changing the bore of this bypass pipe 99.
In this wise, when coolant water temperature is lower than target temperature, make cooling water all control electric T-shaped valve 37 circularly, therefore, coolant water temperature is risen, promptly reach target temperature at the secondary cooling path littler than main cooling path heat dissipation capacity.
And then, in present embodiment, when coolant water temperature is lower than target temperature, except that the switching controls of above-mentioned cooling path, the lowest speed rotating speed of revolution speed that also will be when being lower than common running drives cooling water pump 39, reduces the cooling water flow in the chilled(cooling) water return (CWR), thus, prolong cooling water in the holdup time of engine 31, impel cooling water temperature to rise.Like this, just can make cooling water temperature reach target temperature quickly.
And after coolant water temperature reached target temperature, control module 61 was opened radiator 20 sides of electric T-shaped valve 37 gradually, and thus, the higher cooling water of temperature will inflow radiator 20.Like this,, after moving from the outset, can promptly make cooling water temperature rise to target temperature, therefore, can promptly finish warm-operation in present embodiment.In addition,, in the cooling water of warm-operation heats up, also can carry out Waste Heat Recovery by enough auxiliary evaporators, therefore, can improve the starting characteristic of warming operation even during temperature very low severe winter.
In addition, in present embodiment, be after warming-up is finished after coolant water temperature reaches target temperature, for institute's water content in the exhaust that prevents engine 31 in exhaust pathway and the cap (from the position of engine 31 discharging waste gas) of engine 31 condense, mix the generation precipitation with engine oil, also will be based on the rotating speed of atmospheric temperature and cooling water temperature control cooling water pump 39, thus, regulate cooling water flow, keep coolant water temperature at target temperature.
Specifically be, as illustrated in fig. 2, in the present embodiment, set the judgement temperature A～E of 5 regulation cooling water temperature scopes, judge that according to present coolant water temperature which among A～E be temperature be, the rotating speed of control cooling water pump 39.About judging temperature A～E, be described in detail as follows: with present coolant water temperature is the target temperature degree, promptly do not need temperature when control of coolant water temperature to judge that temperature is C, judge when being lower than set point of temperature than target temperature that temperature is B with present coolant water temperature, judge that when more being lower than set point of temperature temperature is A, and than target, judge that temperature is D with present coolant water temperature during the only high set point of temperature of temperature, judge that when exceeding set point of temperature temperature is E.
In addition, when refrigeration is turned round and during warming operation, whether cooling water is used for the desired water temperature condition difference of cooling water of refrigerant heating etc., therefore, for judging temperature A～E, the different temperature range of setting during with warming operation when refrigeration turn round.And then, even when warming operation, also set different temperature ranges according to outside air temperature.Specifically be, temperature is higher than 5 ℃ occasion during when refrigeration is turned round or at warming operation, judge when being target temperature that temperature is C with coolant water temperature, judge that with coolant water temperature temperature is B, judges that temperature is A low 10 ℃ the time during than low 2 ℃ of target temperature, and, judge that with coolant water temperature temperature is D, judges that temperature is E high 20 ℃ the time during than high 10 ℃ of target temperature.In addition, temperature is lower than 5 ℃ occasion when warming operation, judge that temperature is C with coolant water temperature for low 2 ℃ than target temperature, judge that with coolant water temperature temperature is B, judges that temperature is A low 10 ℃ the time during than low 5 ℃ of target temperature, and, judge when being target temperature that temperature is D, judges that temperature is E high 10 ℃ the time with coolant water temperature.
As described above,, therefore, seek to make this coolant water temperature to rise, reduce the rotating speed of cooling water pump 39 gradually when coolant water temperature is that the expression coolant water temperature is lower than target temperature when judging that temperature is B, A.For example, judging temperature when present coolant water temperature is between B～C the time, whenever reduces 100rpm through the rotating speed that made cooling water pump 39 in 200 seconds, till coolant water temperature is being judged more than the temperature C.In addition, judging temperature when coolant water temperature is between A～B the time, makes the rotating speed of cooling water pump 39 reduce 100rpm again, in addition, and when cooling water temperature is when judging that temperature A is following, to make the rotating speed of cooling water pump 39 reduce 200rpm again.As a result, cooling water temperature is lower than target temperature more makes cooling water pump 39 rotating speeds reduce more, and can realize quickly that coolant water temperature rises, and therefore, can make coolant water temperature reach target temperature rapidly.
On the other hand,, represent coolant water temperature, therefore, rise, improve the rotating speed of cooling water pump 39 gradually in order to suppress this cooling water temperature than target temperature height when coolant water temperature is when judging temperature D, E.For example, judging temperature when present coolant water temperature is between D～E the time, whenever increases 100rpm through the rotating speed that just made cooling water pump 39 in 200 seconds, up to coolant water temperature for till judging below the temperature E.In addition, when coolant water temperature be when judging that temperature E is above, to make the rotating speed of cooling water pump 39 increase 100rpm again.As a result, cooling water temperature is higher than target temperature more, and the rotating speed of cooling water pump 39 is increased, and rises and suppress coolant water temperature, therefore, can make coolant water temperature promptly drop to target temperature.
In addition, the recruitment (reduction) of the setting of judgement temperature A～E shown in Figure 2 and cooling water pump 39 shown in Figure 3 is illustrations, can suitably change according to the performance of conditioner 100 and the kind of cooling water pump 39 etc.In addition, when refrigeration is turned round, make cooling water,, preferentially carry out the rotating speed control of cooling water pump 39, thus, carry out the control that keeps coolant water temperature not in secondary cooling path circulation only in radiator 20 circulations of main cooling path; Have only when the rotating speed control coolant water temperature by cooling water pump 39 does not rise yet, just cooling water is shunted to secondary cooling path, seek the coolant water temperature that raises.
As mentioned above,, form following structure: in the refrigerant loop, the auxiliary evaporator 15 of the cooling water circulation of engine 31 is set according to present embodiment; And, in the chilled(cooling) water return (CWR), be provided with, the cooling water of engine 31 of flowing through passes back into the main cooling path of cooling water pump 39 and the engine 31 of flowing through via radiator 20 cooling water passes back into the secondary cooling path of cooling water pump 39 via auxiliary evaporator 15 and cooling water is distributed to the electric T-shaped valve 37 of main cooling path and secondary cooling path; When cooling water temperature is lower than target temperature, based on the temperature difference of cooling water temperature and target temperature, control electric T-shaped valve 37.Thus, the both sides at main cooling path and secondary cooling path distribute cooling water, perhaps cooling water are all distributed to secondary cooling path, meanwhile, reduce the rotating speed of cooling water pump 39.Therefore, obtain following effect.
That is, also distribute cooling water at the secondary cooling path littler than main cooling path heat dissipation capacity, and then, reduce cooling water flow by the rotating speed that reduces cooling water pump 39, thus, be suppressed at the heat dissipation capacity of radiator 20, and, prolongation is in the holdup time of engine 31, and increase recuperation of heat amount from this engine 31, therefore, realize cooling water heat dissipation capacity minimizing and add the increase of heat, as a result, coolant water temperature is risen rapidly.
Especially, when warm-operation, cooling water all being distributed to secondary cooling path, is minimum and make the heat radiation of cooling water, thus, can make coolant water temperature reach the target temperature of regulation rapidly, therefore, can shorten the time of finishing warm-operation.
In addition, after warm-operation is finished,,, also can impel coolant water temperature to rise owing to reduce the rotating speed of cooling water pump 39 even when degradation and cooling water temperature descend under the rotating speed of engine 31.At this moment, when warming operation, based on the temperature difference of coolant water temperature and target temperature, distribute cooling water at main cooling path and secondary cooling path both sides, perhaps cooling water is all distributed to secondary cooling path, like this, regulate the heat dissipation capacity of this cooling water, just can correctly control cooling water temperature.
On the other hand, when refrigeration is turned round, in order not hinder refrigeration output, when cooling water temperature is low, make whole radiators 20 of cooling water continue circulation at main cooling path, reduce the rotating speed of cooling water pump 39, to impel coolant water temperature to rise, when coolant water temperature can not rise, cooling water is also distributed to secondary cooling path, and the heat dissipation capacity of inhibition cooling water impels coolant water temperature to rise.
Like this,,, can control cooling water temperature, not need as now, to use lining wax triple valve, therefore, can reduce cost by carrying out the distribution of cooling water and the rotating speed of control cooling water pump 39 to main cooling path and secondary cooling path according to present embodiment.
In addition,, when cooling water temperature is higher than target temperature, improve the rotating speed of cooling water pump 39, therefore, outside cooling water temperature rises, can also suppress this temperature and rise based on the temperature difference of cooling water temperature and target temperature according to present embodiment.Thus, can remain on target temperature to coolant water temperature.
In addition, according to present embodiment, form the structure that bypass pipe 99 is set at secondary cooling path, it is used to shunt the cooling water that flows through at this pair cooling path, bypass auxiliary evaporator 15.Therefore, do not increase the crushing consumption of refrigerant, more the lowland suppresses the heat dissipation capacity of the cooling water in the secondary cooling path, and cooling water temperature can promptly raise.
Above-mentioned embodiment is just represented an example of the present invention after all, can at random be out of shape in scope of the present invention.For example,, be formed on the structure of establishing bypass pipe 99 in the secondary cooling path, thus, reduce the heat dissipation capacity of the cooling water in the auxiliary evaporator 15 at above-mentioned embodiment.Yet, also be not limited to this, also can when being lower than target temperature, cooling water temperature reduce the aperture of expansion valve 72, to reduce the flow of the refrigerant that flows into auxiliary evaporator 15,, suppress the heat dissipation capacity of the cooling water in this auxiliary evaporator 15 with such structure.In addition, also can be formed on and establish bypass pipe 99 in the secondary cooling path, simultaneously, also control the structure of the aperture of expansion valve 72.
In addition,, the AC pump is used for cooling water pump 39, forms structure by the amount of spin of frequency converter 45 these cooling water pumps 39 of control at above-mentioned embodiment.Yet, also be not limited to this, also can form the structure that the DC pump is used for cooling water pump 39, form and do not use frequency converter 45 can control the structure of rotating speed.
In addition, also can use heat-exchangers of the plate type as secondary unit 15.
Claims (4)
1. conditioner, it has: connect the refrigerant loop by engine-driven compressor, cross valve, outdoor heat converter and indoor heat converter, the chilled(cooling) water return (CWR) of cooling off above-mentioned engine to engine input cooling water by cooling water pump, it is characterized in that: in above-mentioned refrigerant loop, be provided with the auxiliary evaporator of the cooling water circulation of the above-mentioned engine of cooling; And in above-mentioned chilled(cooling) water return (CWR), be provided with, the cooling water of above-mentioned engine of flowing through passes back into the main cooling path of above-mentioned cooling water pump via above-mentioned outdoor heat converter, the cooling water of above-mentioned engine of flowing through passes back into the secondary cooling path of above-mentioned cooling water pump and the electric T-shaped valve of above-mentioned cooling water being distributed to above-mentioned main cooling path and above-mentioned secondary cooling path via above-mentioned auxiliary evaporator, when above-mentioned cooling water temperature is lower than target temperature, based on the temperature of above-mentioned cooling water and the temperature difference of target temperature, control above-mentioned electric T-shaped valve, thus, above-mentioned cooling water is distributed to the both sides of above-mentioned main cooling path and above-mentioned secondary cooling path, perhaps, above-mentioned cooling water whole are distributed to above-mentioned secondary cooling path, and, reduce the rotating speed of above-mentioned cooling water pump.
2. conditioner as claimed in claim 1 is characterized in that, when above-mentioned cooling water temperature is higher than target temperature, based on the temperature difference of cooling water temperature and target temperature, improves the rotating speed of above-mentioned cooling water pump.
3. conditioner as claimed in claim 1 or 2 is characterized in that, in above-mentioned secondary cooling path bypass path is set, cooling water and the above-mentioned auxiliary evaporator of bypass that its shunting is flowed in this pair cooling path.
4. as one of in claim 1 or 2 described conditioners, it is characterized in that, above-mentioned refrigerant loop have change via above-mentioned outdoor heat converter, flow into the expansion valve of flow of the refrigerant of above-mentioned auxiliary evaporator; When above-mentioned cooling water temperature is lower than target temperature, reduce the aperture of above-mentioned expansion valve, the flow of the refrigerant that flows into above-mentioned auxiliary evaporator is reduced.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP226676/04 | 2004-08-03 | ||
| JP2004226676A JP4565923B2 (en) | 2004-08-03 | 2004-08-03 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1734214A CN1734214A (en) | 2006-02-15 |
| CN100462649C true CN100462649C (en) | 2009-02-18 |
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|---|---|---|---|
| CNB2005100704528A Active CN100462649C (en) | 2004-08-03 | 2005-05-09 | Air conditioner |
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| EP (1) | EP1624260B1 (en) |
| JP (1) | JP4565923B2 (en) |
| KR (1) | KR100597145B1 (en) |
| CN (1) | CN100462649C (en) |
| DE (1) | DE602005010159D1 (en) |
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| JP5057710B2 (en) * | 2006-06-30 | 2012-10-24 | 関西電力株式会社 | Heat pump heat recovery device |
| KR101270616B1 (en) * | 2006-07-27 | 2013-06-07 | 엘지전자 주식회사 | Co-generation |
| FR2937589B1 (en) * | 2008-10-29 | 2012-07-13 | Valeo Systemes Thermiques | AIR CONDITIONING THERMODYNAMIC LOOP INTEGRATED WITH A HEATING, VENTILATION AND / OR AIR CONDITIONING EQUIPMENT EQUIPPED WITH A VEHICLE, IN PARTICULAR ELECTRIC PROPULSION. |
| JP5405161B2 (en) * | 2009-03-23 | 2014-02-05 | 三洋電機株式会社 | Air conditioner and energy equipment |
| JP5571978B2 (en) * | 2010-03-10 | 2014-08-13 | 大阪瓦斯株式会社 | Heat pump system |
| CN102022804B (en) * | 2010-12-22 | 2013-06-12 | 广东美的电器股份有限公司 | Condensation prevention control method of air conditioner |
| CN103158488B (en) * | 2011-12-19 | 2016-09-28 | 杭州三花研究院有限公司 | A kind of automotive air-conditioning system |
| CN103158487B (en) * | 2011-12-19 | 2016-05-04 | 杭州三花研究院有限公司 | A kind of automotive air-conditioning system |
| CN103158489B (en) * | 2011-12-19 | 2016-06-15 | 杭州三花研究院有限公司 | A kind of automotive air-conditioning system |
| CN103158490B (en) * | 2011-12-19 | 2016-05-25 | 杭州三花研究院有限公司 | A kind of automotive air-conditioning system |
| CN103158486B (en) * | 2011-12-19 | 2016-06-15 | 杭州三花研究院有限公司 | A kind of automotive air-conditioning system |
| CN103192681B (en) * | 2012-01-05 | 2016-05-04 | 杭州三花研究院有限公司 | A kind of automotive air-conditioning system |
| EP3081881A1 (en) * | 2015-04-17 | 2016-10-19 | Daikin Europe N.V. | Compressor unit for an air conditioner and heat source unit for an air conditioner comprising the compressor unit and a heat source unit |
| DE102016104730A1 (en) * | 2016-03-15 | 2017-09-21 | Connaught Electronics Ltd. | Method for detecting an object along a road of a motor vehicle, computing device, driver assistance system and motor vehicle |
| CN106338112B (en) * | 2016-10-21 | 2018-07-17 | 珠海格力电器股份有限公司 | Air conditioner heat recovery system |
| KR20180078049A (en) * | 2016-12-29 | 2018-07-09 | 포스코에너지 주식회사 | WASTE HEAT RECOVERY device and SYSTEM AND COMBINED CYCLE POWER PLANT |
| CN108312805B (en) * | 2018-01-04 | 2019-12-24 | 英格索兰（中国）工业设备制造有限公司 | Control method and control device of air conditioning unit |
| CN110285530A (en) * | 2019-06-12 | 2019-09-27 | 特灵空调系统(中国)有限公司 | Control method, air-conditioner control system, machine readable storage medium and air-conditioning system |
| JP2020201019A (en) * | 2019-06-13 | 2020-12-17 | 三菱重工エンジン＆ターボチャージャ株式会社 | Co-generation system, control method and program |
| CN111098665B (en) * | 2020-01-19 | 2020-11-20 | 湖南汽车工程职业学院 | Internal combustion engine automobile multi-mode temperature management system |
| JP2021156441A (en) * | 2020-03-25 | 2021-10-07 | ヤンマーパワーテクノロジー株式会社 | heat pump |
| CN112013606B (en) * | 2020-08-12 | 2024-01-30 | 浙江天旭机电设备有限公司 | Novel cooling water station |
| CN112188799B (en) * | 2020-09-21 | 2024-03-15 | 珠海格力电器股份有限公司 | Cooling system, control method thereof, water chilling unit and air conditioner |
| CN113905594B (en) * | 2021-10-28 | 2023-03-14 | 珠海格力电器股份有限公司 | Heat dissipation control method and device of frequency converter power module, medium and air conditioner |
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- 2005-05-12 KR KR20050039539A patent/KR100597145B1/en not_active IP Right Cessation
- 2005-08-01 DE DE200560010159 patent/DE602005010159D1/en active Active
- 2005-08-01 EP EP20050016680 patent/EP1624260B1/en not_active Expired - Fee Related
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Also Published As
| Publication number | Publication date |
|---|---|
| EP1624260B1 (en) | 2008-10-08 |
| CN1734214A (en) | 2006-02-15 |
| EP1624260A2 (en) | 2006-02-08 |
| DE602005010159D1 (en) | 2008-11-20 |
| KR20060047781A (en) | 2006-05-18 |
| JP4565923B2 (en) | 2010-10-20 |
| KR100597145B1 (en) | 2006-07-06 |
| JP2006046755A (en) | 2006-02-16 |
| EP1624260A3 (en) | 2007-02-14 |
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