CN105299798A - Heat pump air conditioner - Google Patents
Heat pump air conditioner Download PDFInfo
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- CN105299798A CN105299798A CN201510436555.5A CN201510436555A CN105299798A CN 105299798 A CN105299798 A CN 105299798A CN 201510436555 A CN201510436555 A CN 201510436555A CN 105299798 A CN105299798 A CN 105299798A
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- heat pump
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- compressor
- air conditioner
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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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
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/30—Arrangement or mounting of heat-exchangers
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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
- F25B39/00—Evaporators; Condensers
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/02—System or Device comprising a heat pump as a subsystem, e.g. combined with humidification/dehumidification, heating, natural energy or with hybrid system
- F24F2203/021—Compression 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
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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
- F25B2400/06—Several compression cycles arranged in parallel
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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
- F25B2500/00—Problems to be solved
- F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
- F25B2500/00—Problems to be solved
- F25B2500/27—Problems to be solved characterised by the stop of the refrigeration cycle
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Air Conditioning Control Device (AREA)
- Central Air Conditioning (AREA)
- Geometry (AREA)
Abstract
A heat pump air conditioner includes an intake side heat exchanger including heat transfer pipes passing a refrigerant and being arranged in a direction along an air inlet face, intake heat exchanger configured to cool or warm air and supply the air to a space. A plurality of heat pumps include a plurality of compressors and configured to compress the refrigerant and supply the compressed refrigerant to the heat transfer pipes and a plurality of heat side exchangers and connected to the respective compressors, the heat pumps sharing the air intake side heat exchanger, and a controller configured to switch a state of the compressors and between an operating state and an operation stopped state. The controller controls the compressors and to switch an operation of each of the compressors and between starting and stopping in accordance with a magnitude of an air-conditioning load.
Description
Technical field
The present invention relates to air conditioner of heat pump type.
Background technology
Existing air conditioner of heat pump type possesses the compressor of a formation heat pump, air feed side heat exchanger and heat source side heat exchanger as Patent Document 1 respectively, and makes to be connected by pipe arrangement between them with the form making cold-producing medium circulate in them.
Prior art document:
Patent document:
Patent document 1: the flat 9-264614 publication of Japanese Unexamined Patent Publication.
Summary of the invention
The problem that invention will solve:
Air conditioner of heat pump type used in the whole year, and in following record, the period in 1 year except temperature higher summer and temperature lower winter is called intergrade;
In existing air conditioner of heat pump type, the cooling and warming ability of needs is larger, and the minimum critical power of compressor is larger.Therefore, in the period that the load putting on air-conditioning of intergrade etc. is less, there is the situation that cooling and warming ability is excessive.Consequently, stop cooling and warming running, but but cannot play cooling or heating effect next time.Therefore, cooling and warming excessively plays, or cannot play, and the useless energy ezpenditure of compressor can increase.Consequently, there is the infringement comfortableness of cooling and warming and the problem of energy saving;
The object of this invention is to provide the air conditioner of heat pump type that can improve comfortableness and energy saving.
The means of dealing with problems:
Air conditioner of heat pump type of the present invention is in order to solve the problem, and possess: there is internal circulation cold-producing medium and multiple heat-transfer pipes of direction arrangement along air intake face, and for after the air be supplied to is become cold wind or warm air to the air feed side heat exchanger supplied by conditioned space; Multiple compressor at least with the backward described heat-transfer pipe supply of compressed refrigerant and the heat source side heat exchanger be connected with each compressor, and share multiple first heat pump and second heat pump of a described air feed side heat exchanger; And carry out the operation of described compressor and run the control device of the switching between stopping, described control device switches compressor described in the starting of described each compressor and the form control of stopping with the size according to air conditioner load.
According to the present invention, multiple heat pump is shared and is born cooling and warming ability required in air conditioner of heat pump type.Therefore, such as, only start a compressor when air conditioner load is less, just can carry out cooling and warming by means of only a heat pump.By means of this, the useless energy resource consumption of compressor can be suppressed when air conditioner load is less, comfortableness and the energy saving of cooling and warming can be improved.
In the present invention, can also be, using the multiple heat-transfer pipes be connected with the first heat pump as the first heat-transfer pipe, using multiple heat-transfer pipes of being connected with the second heat pump as the second heat-transfer pipe time, multiple first heat-transfer pipe and multiple second heat-transfer pipe along a direction every the alternately configuration of one or two ground;
If the place in air intake face is partial in the configuration of multiple first heat-transfer pipe or the second heat-transfer pipe, then cause when carrying out cooling and warming by means of only a heat pump, only relatively a part for the heat exchanger of air feed side carries out cooling and warming.So, by the air cooled or heating partly of air feed side heat exchanger, heating or the inhomogeneous cooling of air is therefore produced.Therefore, by multiple first heat-transfer pipe and multiple second heat-transfer pipe alternately being configured along a direction every one or two ground, the air of air feed side heat exchanger 3 can be heated or be cooled through equably with this.
In the present invention, can also be, described control device at least alternately runs a pair compressor;
Owing to alternately running a pair compressor, therefore can prevent from only exceedingly running side heat pump.By means of this, extend the life-span of air conditioner of heat pump type, can life cycle cost be reduced;
Again, by control device or utilize software exchange operational mode namely alternately to run a pair compressor, the alternate run of being correlated with therefore easily can be implemented.Therefore, do not need the unnecessary equipment of timer etc., can also reduce costs.
In the present invention, can also be that the running time of each compressor hereto or number of run, before alternately running a pair compressor, add up to by described control device, and this running time or the less compressor of number of run are preferentially run;
By means of this, the operation of the compressor of relatively can be prevented, running time or the number of run homogenization of all compressors can be made.And even the life-span of air conditioner of heat pump type can be extended, can life cycle cost be reduced.
In the present invention, can also be that described control device does not perform the operation of a pair compressor and the switching action of stopping when the defrosting action of heating operation, and perform time beyond defrosting action.By means of this, a pair compressor can not be made when the defrosting action of heating operation simultaneously all to stop, and alternately defrost, therefore heating operation can not interrupt.Again, without the need to arranging the heater etc. for the action that defrosts in addition.
In the present invention, preferably, the operation of described second heat pump that first runs with following form control of described control device:
Making the first starting operation of described second heat pump, afterwards when starting the operation of described first heat pump, from the output of described second heat pump first run, only deducting described first hot priming of pump output quantity;
By means of this, the increase and decrease of the output of multiple heat pump offsets and eliminates overshoot, reduces the uneven of cooling and warming, can carry out stable air conditioning.
In the present invention, preferably, described control device is with the operation of the second heat pump described in following form control:
Make described first heat pump with output along with the form operation of time decline is rear, make described second heat pump to export in the shut-down operation along with the form operation of time decline, the output slippage before the vicinity making the output of described second heat pump only increase described first heat pump when the operation stopping of described first heat pump runs stopping;
By means of this, the increase and decrease of the output of multiple heat pump offsets and eliminates downward, reduces the uneven of cooling and warming, can carry out stable air conditioning.
In the present invention, preferably, the minimum critical power of multiple heat pump is different.Such as, when the minimum critical power of the first heat pump and the second heat pump is 6:4, only makes the lower side of minimum critical power when air conditioner load is lower, namely only make the second operation of heat pump.Relative to this, when the minimum critical power of all heat pumps is all identical, such as when the minimum critical power of the first heat pump and the second heat pump is 5:5, compared to the situation that the minimum critical power of each heat pump is not identical, cannot tackle air conditioner load lower time situation.Therefore, by making the minimum critical power of each heat pump not identical, can tackle with this situation that air conditioner load changes significantly.And even, comfortableness and the energy saving of cooling and warming can be improved.
In the present invention, can also be, evaporation type humidifier is configured with in the air flow circuit downstream of described air feed side heat exchanger, steam-type humidifier is also configured with in the air flow circuit downstream of this evaporation type humidifier, this evaporation type humidifier is all connected with described control device with steam-type humidifier, described control device is first by air that described evaporation humidifier humidification is supplied to, when not enough by described evaporation type humidifier humidifies, make the work of described steam-type humidifier and the air that is supplied to of humidification further;
Air conditioner carries out humidification when carrying out humidification mainly through the evaporation type humidifier that operating cost compared with steam-type humidifier is less.Therefore, first by evaporation type humidifier humidifies air, and by the part of steam-type humidifier only humidification deficiency, humidification cost can be suppressed with this.
In the present invention, preferably, the cross section of described heat-transfer pipe is formed as oval.Therefore, the flowing resistance of heat-transfer pipe is less, thus the pressure loss of the air passed through reduces.Again, the air of heat-transfer pipe and the contact area of heat transfer pipe contacts can be increased through, thus the heat exchanger effectiveness between heat-transfer pipe and the air passed through improves, comfortableness and the energy saving of cooling and warming can be improved.
Accompanying drawing explanation
Fig. 1 illustrates the integrally-built front view according to air conditioner of heat pump type of the present invention;
Fig. 2 is the stereogram of the internal structure that air feed side heat exchanger is shown;
Fig. 3 is the top view of the air feed side heat exchanger of Fig. 2;
Fig. 4 (A) in Fig. 4, Fig. 4 (B) are the figure that the first heat-transfer pipe of air feed side heat exchanger and the configuration example of the second heat-transfer pipe are shown, observe Fig. 2 from front;
Fig. 5 (A) in Fig. 5 is the figure of the rate-determining steps of operation halted state to exporting and reaching the upper limit illustrated from heat pump, and the Fig. 5 (B) in Fig. 5 is the figure of the rate-determining steps of running status to becoming halted state illustrated from heat pump;
1 housing;
2a first compressor;
2b second compressor;
3 air feed side heat exchangers;
4a, 4b heat source side heat exchanger;
5a first heat pump;
5b second heat pump;
6 evaporation type humidifiers;
7 steam-type humidifiers;
8 control device;
9a, 9b mechanism of decompressor;
10a, 10b switching mechanism;
12a, 12b heat-transfer pipe;
13 air intake faces;
200 air conditioner of heat pump type.
Detailed description of the invention
Hereinafter, with reference to the accompanying drawings of the air conditioner of heat pump type of embodiment according to the present invention.In addition, below, in all of the figs identical reference symbol be marked with for same or equivalent key element and omit repeat specification;
Fig. 1 illustrates the front view of the schematic configuration of the air conditioner of heat pump type 200 according to this embodiment.Air conditioner of heat pump type 200 possesses: the housing 1 forming air intake 18 and outlet 19; Air feed pressure fan 14; An air feed side heat exchanger 3 in air intake face 13 is set; First refrigerant compression carrying compressor 2a and second refrigerant compression carrying compressor 2b; And multiple heat source side heat exchanger 4a, 4b.Air conditioner of heat pump type 200 also possesses: share described air inlet side heat exchanger 3 and possess the first heat pump 5a and the second heat pump 5b of refrigerating function and heat-production functions; Be configured in the evaporation type humidifier 6 in the downstream of air inlet side heat exchanger 3; Be configured in the steam-type humidifier 7 in the downstream of this evaporation humidifier 6; With the control device 8 of their action of control.First heat pump 5a and its lowest power that can bring into operation of the second heat pump 5b, namely minimum critical power is not identical.Specifically, the minimum critical power of the first heat pump 5a is 6:4 with the ratio of the minimum critical power of the second heat pump 5b.Certainly, this ratio is not limited to;
The entrance 18 of housing 1 is offered towards air intake face 13, flows into air feed side heat exchanger 3 from this entrance 18 leaked-in air from air intake face 13, heat exchange in this air feed side heat exchanger 3 and become cold wind or warm air.Afterwards, this cold wind or warm air are supplied to by conditioned space (such as room) from the outlet 19 of housing 1.Idle call air flows along flow direction F.
First heat pump 5a successively repeats compression condensation to the cold-producing medium circulated therein and to expand the operation of evaporation, absorbs heat respectively, dispel the heat in condensation procedure to the air carrying out heat exchange with this cold-producing medium in evaporization process;
This first heat pump 5a possesses: in evaporization process and condensation procedure, performs the heat source side heat exchanger 4a being different from the operation of air feed side heat exchanger 3; Perform the first compressor 2a of compression section; Perform the mechanism of decompressor 9a of the expansion valve of expansion stroke etc.; And the switching mechanism 10a of the valve carrying out the switching between evaporization process and condensation procedure etc.First compressor 2a, switching mechanism 10a, heat source side heat exchanger 4a are connected by pipe arrangement mutually with mechanism of decompressor 9a, thus cold-producing medium is in inner loop.
Second heat pump 5b also repeats four operations of compression condensation expansion evaporation therein successively to the cold-producing medium circulated;
This second heat pump 5b possesses: in evaporization process and condensation procedure, performs the heat source side heat exchanger 4b being different from the operation of air feed side heat exchanger 3; Perform the second compressor 2b of compression section; Perform the mechanism of decompressor 9b of the expansion valve of expansion stroke etc.; And the switching mechanism 10b of the valve carrying out the switching between evaporization process and condensation procedure etc.Second compressor 2b, switching mechanism 10b, heat source side heat exchanger 4b are connected by pipe arrangement mutually with mechanism of decompressor 9b, thus cold-producing medium is in inner loop.
Fig. 2 is the stereogram of the internal structure that air feed side heat exchanger 3 is shown, Fig. 3 is the top view of the air feed side heat exchanger 3 of Fig. 2.Air feed side heat exchanger 3 is to make the form passed through from flow direction F leaked-in air arrange gap and the multi-disc heat transfer plate 11 that is configured in the longitudinal direction, installs multiple first heat-transfer pipe 12a of flow of refrigerant and the second heat-transfer pipe 12b in the vertical direction in parallel to each other and forms.First heat-transfer pipe 12a is connected with the first heat pump 5a, and the second heat-transfer pipe 12b is connected with the second heat pump 5b;
As shown in Figure 3, the pipe key element 100 bending with the form be connected with multiple heat transfer plate 11 connects and is formed by each heat-transfer pipe 12a, 12b in the transverse direction.Each pipe key element 100 possesses: the Part I 110 extended to the inside with the form that the flow direction F with idle call air is orthogonal from the import and export of cold-producing medium; From the medial end of this Part I 110 along the Part II 120 that extends of the shorter ground of flow direction F; With the Part III 130 extended abreast from the end of this Part II 120 to the import and export of cold-producing medium and with Part I 110.That is, the first heat-transfer pipe 12a and the second heat-transfer pipe 12b is the adverse current type (counterflow) that the length orthogonal with the flow direction F of idle call air is longer.
When cold-producing medium flows in the first heat-transfer pipe 12a and the second heat-transfer pipe 12b, the air flowed in this cold-producing medium and the gap between heat transfer plate 11 carries out heat exchange by means of the first heat-transfer pipe 12a and the second heat-transfer pipe 12b and heat transfer plate 11.As mentioned above, the first heat-transfer pipe 12a and the second heat-transfer pipe 12b is adverse current type (counterflow), but also can be cross-flow type (crossflow).Again, the cross section of the first heat-transfer pipe 12a and the second heat-transfer pipe 12b is formed as oval (with reference to Fig. 4 (A), Fig. 4 (B)), thus reduces the flowing resistance of heat-transfer pipe 12a, 12b, and increases the contact area contacted with the air by heat-transfer pipe 12a, 12b.But the cross section of the first heat-transfer pipe 12a and the second heat-transfer pipe 12b also can be formed as circular;
Again, heat source side heat exchanger 4a, 4b also arrange with the form making air pass through identically with air feed side heat exchanger 3 and multi-disc heat transfer plate that gap is configured install multiple heat-transfer pipe and is formed.Heat source side heat exchanger 4a, 4b possess ventilation pressure fan 15a, 15b.
Fig. 4 (A), Fig. 4 (B) are the figure that the first heat-transfer pipe 12a of air feed side heat exchanger 3 and the configuration example of the second heat-transfer pipe 12b are shown, from direction G, namely observe Fig. 2 from front.In Fig. 4 (A), Fig. 4 (B), the heat-transfer pipe that white circle represents is the first heat-transfer pipe 12a, and the heat-transfer pipe of blacking is the second heat-transfer pipe 12b.Each heat-transfer pipe 12a, 12b are formed as along the flow direction F of idle call air shape concavo-convex continuously as shown in the dotted line of Fig. 4 (A), Fig. 4 (B), and specifically, Part III 130 is positioned at the position higher than Part I 110.Each heat-transfer pipe 12a, 12b are formed as shape concavo-convex continuously, thus make the length that contacts with idle call air;
In Fig. 4 (A), multiple first heat-transfer pipe 12a and multiple second heat-transfer pipe 12b is along above-below direction often alternately configuration alternately.Replace, as shown in Fig. 4 (B), also can make multiple first heat-transfer pipe 12a and multiple second heat-transfer pipe 12b along above-below direction every the alternately configuration of two ground.
If the place in air intake face 13 is partial in the configuration of multiple first heat-transfer pipe 12a or the second heat-transfer pipe 12b, then as described belowly cause when carrying out cooling and warming by means of only a heat pump, only relatively a part for the heat exchanger 3 of air feed side carries out cooling and warming.So, by the air cooled or heating partly of air feed side heat exchanger 3, heating or the inhomogeneous cooling of air is therefore produced.Therefore, by alternately being configured along a direction every one or two ground by multiple first heat-transfer pipe 12a and the second heat-transfer pipe 12b, the air of air feed side heat exchanger 3 can be heated or be cooled through equably with this;
In Fig. 4 (A), Fig. 4 (B), heat-transfer pipe 12a, 12b and heat-transfer pipe 12a, 12b neighbouring with it are arranged at equal intervals, but also can not be arranged at equal intervals.Again, also can be each heat-transfer pipe 12a, 12b flow direction F formation rectilinear form along idle call air.
(action of control device)
first embodiment
Control device 8 is made up of microprocessor and various sensor, possesses memory as required.The a reference value of the air conditioner load putting on air conditioner of heat pump type 200 is stored in control device 8, the air conditioner load and a reference value that put on air conditioner of heat pump type 200 are compared, thus to the operation of the first compressor 2a and the second compressor 2b and run stopping and switching, and regulation output.Specifically, if the air conditioner load putting on air conditioner of heat pump type 200 is less than a reference value, then control device 8 stops the operation of two compressors 2a, 2b;
Control device 8, when the load putting on air conditioner of heat pump type 200 is more than a reference value and is larger, runs two compressors 2a, 2b and makes cold-producing medium flow into all heat-transfer pipe 12a, 12b.But, if the load putting on air conditioner of heat pump type 200 be more than a reference value and less time, only run compressor 2a, 2b of side and make cold-producing medium only flow into heat-transfer pipe 12a, 12b of side;
Therefore, when such as air conditioner load is more than a reference value but is less, only start a compressor, thus can cooling and warming be carried out by means of only a heat pump.By means of this, when air conditioner load is less, the useless energy ezpenditure of compressor can be suppressed, comfortableness and the energy saving of cooling and warming can be improved.
second embodiment
When the load putting on air conditioner of heat pump type 200 is more than a reference value, control device 8 also alternately can run the first compressor 2a and the second compressor 2b.By means of this, in heat-transfer pipe 12a, 12b, alternately flow into cold-producing medium.That is, when operation first compressor 2a, stop the second compressor 2b and stop the inflow of the cold-producing medium in the second heat-transfer pipe 12b, when stopping first compressor 2a, run the second compressor 2b and cold-producing medium is flowed in heat-transfer pipe 12b.For the order alternately running this first compressor 2a and the second compressor 2b, way also can be in operation conversely.In addition, control device 8 also can start stopping by making multiple heat pump 5a, 5b and the staggered multiple operational modes of the order that this starting is stopped one by one successively, switches successively when any one heat pump of stopping;
Again, when air feed side heat exchanger 3 carries out heating operation, two compressors 2a, 2b absorb heat, and when therefore the temperature of gas is lower outside, there is the situation of the upper frosting of each compressor 2a, 2b.Under the state of this frosting, the service ability of compressor 2a, 2b declines, and therefore makes compressor temporarily move to inverse circulation and remove frost.This action is called defrosting (defrost).Control device 8 does not perform the operation of these two compressors 2a, 2b and the switching action of stopping when defrosting action, performs time only beyond defrosting action.By means of this, the heating operation of air feed side heat exchanger 3 can not interrupt.Again, without the need to arranging defrosting heater etc. in addition.In addition, also carry out defrosting action is beyond inverse circular flow, above-mentioned record illustrates an example of defrosting action.
3rd embodiment
Or the running time of each compressor 2a, 2b hereto or number of run, when alternately running the first compressor 2a and the second compressor 2b, add up to by control device 8.Also this running time or less compressor 2a, the 2b of number of run can be made preferentially to run, running time or more compressor 2a, the 2b of number of run are stopped.By means of this, make the running frequency of compressor 2a, 2b or running time reach homogenization, thus extend the life-span of this compressor 2a, 2b, and the number of times of the repairing carried out because of fault can be reduced;
Control device 8 can not perform the operation of these two compressors 2a, 2b and the switching action of stopping when above-mentioned defrosting action yet, and performs time only beyond defrosting action.
4th embodiment
Fig. 5 (A) is the figure of the rate-determining steps of operation halted state to exporting and reaching the upper limit illustrated from the first heat pump 5a and the second heat pump 5b, and horizontal axis representing time, the longitudinal axis represents the output level of heat pump 5a, 5b.In the example that Fig. 5 (A) illustrates, first make the second heat pump 5b first run when time t1, start the operation of the first heat pump 5a afterwards when time t2.The output of heat pump 5b is risen pro rata with the elapsed time from starting, reaches and export S2 before contiguous time t2;
On the other hand, the output when operation of the first heat pump 5a is started when time t2 is expressed as S1.When control device 8 is when the operation of the first heat pump 5a is started, at time t2, with the operation making the output of the second heat pump 5b reach the form control second heat pump 5b deducting the value of S1 from S2.By means of this, the output sum of two heat pumps 5a, 5b when time t2 becomes S2, identical with the output before contiguous time t2.If when time t2, the second heat pump 5b exports still is S2, then the output sum of two heat pumps 5a, 5b becomes S2+S1, causes output sharply to rise, i.e. overshoot (overshoot) phenomenon.So, the uneven or exceedingly loss that causes of cooling and warming of cooling and warming is caused.Therefore, control device 8, with the operation making the output of the second heat pump 5b reach the form control second heat pump 5b deducting the value of S1 from S2 when time t2, performs the comfortable air conditioning without the uneven of cooling and warming or loss with this.
Fig. 5 (B) is the figure of the rate-determining steps of running status to becoming halted state illustrated from the first heat pump 5a and the second heat pump 5b.In the example shown in Fig. 5 (B), first by the first heat pump 5a to export the form declined pro rata with the time when time t3 run from exporting the state that is in the upper limit, the form declined pro rata with the output of the second heat pump 5b when time t4 and time is afterwards run.First heat pump 5a stops when time t5, and the output before this vicinity stops is S3.That is, when time t5, the output of the first heat pump 5a becomes zero from S3.If the output resume of the second heat pump 5b declines when time t5, then cause the output sum of two heat pumps 5a, 5b sharply to decline, namely lower (undershoot) phenomenon.So, the uneven of cooling and warming or the exceedingly loss that causes of cooling and warming is caused;
Therefore, control device 8 is as shown in Figure 5 (B) to make the output of the second heat pump 5b reach the operation of the form control second heat pump 5b of the value of the S3 that only rises when time t5.By means of this, when two heat pumps 5a, 5b become halted state from running status, carry out the comfortable air conditioning without the uneven of cooling and warming or loss.
As mentioned above, be configured with evaporation type humidifier 6 in the air flow circuit downstream of air feed side heat exchanger 3, be configured with steam-type humidifier 7 in the air flow circuit downstream of evaporation type humidifier 6.Evaporation type humidifier 6 is all connected with control device 8 with steam-type humidifier 7.Control device 8 is also connected with the humidity sensor (not shown) in housing 1, stores a reference value of humidity in control device 8;
Control device 8 first by the air that evaporation humidifier 6 humidification is supplied to, and passes through humidity sensor measuring humidity.The a reference value of the humidity of mensuration and humidity also can compare by control device 8, and when being judged as that humidification is not enough, steam-type humidifier 7 is worked and the air that is supplied to of humidification further;
Generally speaking, evaporation type humidifier operating cost compared with steam-type humidifier is few.Therefore, first by evaporation type humidifier 6 humidifying air, and only compensated the part of humidification deficiency by steam-type humidifier 7, humidification cost can be suppressed with this.
In addition, content of the present invention is not limited to the air conditioner of heat pump type of above-mentioned embodiment, without departing from the spirit and scope of the invention can design for change.Such as, air feed side heat exchanger 3 is set in housing 1 in FIG, at arranged outside two heat pumps 5a, 5b of housing 1.But, replace, also can two heat pumps 5a, 5b be set in housing 1.Again, heat source side heat exchanger 4a, 4b are set as air heat source formula, but also can be water heat source type.Again, heat pump 5a, 5b are not limited to two, also can be more than three.
Industrial applicability:
It is useful when the present invention is applied in air conditioner of heat pump type.
Claims (10)
1. an air conditioner of heat pump type, is characterized in that, possesses:
There is internal circulation cold-producing medium and multiple heat-transfer pipes of direction arrangement along air intake face, and for after the air be supplied to is become cold wind or warm air to the air feed side heat exchanger supplied by conditioned space;
Multiple compressor at least with the backward described heat-transfer pipe supply of compressed refrigerant and the heat source side heat exchanger be connected with each compressor, and share multiple first heat pump and second heat pump of a described air feed side heat exchanger; With
Carry out the operation of described compressor and run the control device of the switching between stopping,
Described control device switches compressor described in the starting of each described compressor and the form control of stopping with the size according to air conditioner load.
2. air conditioner of heat pump type according to claim 1, is characterized in that,
Using the multiple heat-transfer pipes be connected with described first heat pump as the first heat-transfer pipe, using multiple heat-transfer pipes of being connected with described second heat pump as the second heat-transfer pipe time, described multiple first heat-transfer pipe and multiple second heat-transfer pipe along a described direction every the alternately configuration of one or two ground.
3. air conditioner of heat pump type according to claim 1 and 2, is characterized in that, described control device at least alternately runs a pair compressor.
4. air conditioner of heat pump type according to claim 3, is characterized in that,
The running time of each compressor hereto or number of run, before alternately running a pair compressor, add up to by described control device, and this running time or the less compressor of number of run are preferentially run.
5. air conditioner of heat pump type according to claim 3, is characterized in that,
Described control device does not perform the operation of a pair compressor and the switching action of stopping when defrosting action, and performs time beyond defrosting action.
6. air conditioner of heat pump type according to claim 1 and 2, is characterized in that,
The operation of described second heat pump that described control device first runs with following form control:
Making the first starting operation of described second heat pump, afterwards when starting the operation of described first heat pump, from the output of described second heat pump first run, only deducting described first hot priming of pump output quantity.
7. air conditioner of heat pump type according to claim 1 and 2, is characterized in that,
Described control device is with the operation of the second heat pump described in following form control:
Make described first heat pump with output along with the form operation of time decline is rear, make described second heat pump to export in the shut-down operation along with the form operation of time decline, the output slippage before the vicinity making the output of described second heat pump only increase described first heat pump when the operation stopping of described first heat pump runs stopping.
8. air conditioner of heat pump type according to claim 1 and 2, is characterized in that,
The minimum critical power of multiple heat pump is different.
9. air conditioner of heat pump type according to claim 1 and 2, is characterized in that,
Evaporation type humidifier is configured with in the air flow circuit downstream of described air feed side heat exchanger, steam-type humidifier is also configured with in the air flow circuit downstream of this evaporation type humidifier, this evaporation type humidifier is all connected with described control device with steam-type humidifier, described control device is first by air that described evaporation humidifier humidification is supplied to, when not enough by described evaporation type humidifier humidifies, make the work of described steam-type humidifier and the air that is supplied to of humidification further.
10. air conditioner of heat pump type according to claim 1 and 2, is characterized in that,
The cross section of described heat-transfer pipe is formed as oval.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014152542A JP5805833B1 (en) | 2014-07-28 | 2014-07-28 | Heat pump air conditioner |
| JP2014-152542 | 2014-07-28 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105299798A true CN105299798A (en) | 2016-02-03 |
| CN105299798B CN105299798B (en) | 2018-03-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520538249.8U Expired - Fee Related CN204943747U (en) | 2014-07-28 | 2015-07-23 | Air conditioner of heat pump type |
| CN201510436555.5A Active CN105299798B (en) | 2014-07-28 | 2015-07-23 | Air conditioner of heat pump type |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
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| CN201520538249.8U Expired - Fee Related CN204943747U (en) | 2014-07-28 | 2015-07-23 | Air conditioner of heat pump type |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20160025384A1 (en) |
| JP (1) | JP5805833B1 (en) |
| KR (1) | KR101665522B1 (en) |
| CN (2) | CN204943747U (en) |
| MY (1) | MY190880A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112041619A (en) * | 2018-04-11 | 2020-12-04 | 夏普株式会社 | Air conditioning system |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5805833B1 (en) * | 2014-07-28 | 2015-11-10 | 木村工機株式会社 | Heat pump air conditioner |
| JP6151409B2 (en) * | 2015-10-06 | 2017-06-21 | 木村工機株式会社 | Heat pump type heat source device |
| JP6084737B1 (en) * | 2015-10-06 | 2017-02-22 | 木村工機株式会社 | Air conditioning system |
| WO2017168669A1 (en) * | 2016-03-31 | 2017-10-05 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle apparatus |
| US10298587B2 (en) * | 2016-06-20 | 2019-05-21 | International Business Machines Corporation | Peer-to-peer augmented reality handlers |
| JP6416975B1 (en) | 2017-04-26 | 2018-10-31 | 木村工機株式会社 | Air source heat pump air conditioner |
| CN107576211A (en) * | 2017-09-11 | 2018-01-12 | 广东芬尼克兹节能设备有限公司 | A kind of cross flow heat exchanger and Multi-stage heating heat pump |
| CN112325395B (en) * | 2020-10-23 | 2021-08-10 | 重庆阿泰可科技股份有限公司 | Air duct structure for manufacturing low dew point air |
| JP7030172B1 (en) | 2020-11-16 | 2022-03-04 | 木村工機株式会社 | Heat pump type air conditioner |
| US20220397312A1 (en) * | 2021-06-09 | 2022-12-15 | LGL France S.A.S. | Counter-current flow in both ac and hp modes for part load optimization |
Family Cites Families (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4332137A (en) * | 1979-10-22 | 1982-06-01 | Carrier Corporation | Heat exchange apparatus and method having two refrigeration circuits |
| US4384462A (en) * | 1980-11-20 | 1983-05-24 | Friedrich Air Conditioning & Refrigeration Co. | Multiple compressor refrigeration system and controller thereof |
| US4787211A (en) * | 1984-07-30 | 1988-11-29 | Copeland Corporation | Refrigeration system |
| US4947655A (en) * | 1984-01-11 | 1990-08-14 | Copeland Corporation | Refrigeration system |
| JPS61191892A (en) * | 1985-02-20 | 1986-08-26 | Matsushita Refrig Co | Manufacture of fin tube type heat exchanger |
| JP3489932B2 (en) | 1996-03-29 | 2004-01-26 | 松下電器産業株式会社 | Air conditioner |
| JPH109693A (en) * | 1996-06-20 | 1998-01-16 | Kimura Kohki Co Ltd | Air conditioner |
| JP3513740B2 (en) * | 1997-12-15 | 2004-03-31 | 株式会社日立製作所 | Air conditioner |
| US6755396B1 (en) * | 2002-03-06 | 2004-06-29 | Kenneth E. Weinrich | Portable vehicle humidifier |
| US6978630B2 (en) * | 2004-01-16 | 2005-12-27 | Dometic Corporation | Dual-circuit refrigeration system |
| US7451614B2 (en) * | 2004-04-01 | 2008-11-18 | Perlick Corporation | Refrigeration system and components thereof |
| JP2007107859A (en) * | 2005-10-17 | 2007-04-26 | Mitsubishi Heavy Ind Ltd | Gas heat pump type air conditioner |
| US7980535B2 (en) * | 2007-05-21 | 2011-07-19 | Dristeem Corporation | Demand activated steam dispersion system |
| CN102037293B (en) * | 2008-05-21 | 2014-02-19 | 摩丁制造公司 | Chiller with setpoint adjustment |
| JP5624713B2 (en) * | 2008-09-22 | 2014-11-12 | パナソニックヘルスケア株式会社 | Refrigeration equipment |
| JP2010230282A (en) * | 2009-03-27 | 2010-10-14 | Tokyo Electric Power Co Inc:The | Air conditioner |
| KR101636328B1 (en) * | 2009-12-22 | 2016-07-05 | 삼성전자주식회사 | Heat Pump Apparatus and Outdoor Unit thereof |
| JP2012211709A (en) * | 2011-03-30 | 2012-11-01 | Mitsubishi Electric Corp | Air conditioner |
| US9921591B2 (en) * | 2012-03-26 | 2018-03-20 | Siemens Schweiz Ag | System and method for HVAC interlocks |
| CN203203173U (en) * | 2013-04-09 | 2013-09-18 | 林开生 | Double-circulation constant-temperature and constant-humidity air conditioner as well as control device thereof |
| JP5805833B1 (en) * | 2014-07-28 | 2015-11-10 | 木村工機株式会社 | Heat pump air conditioner |
-
2014
- 2014-07-28 JP JP2014152542A patent/JP5805833B1/en active Active
-
2015
- 2015-05-28 KR KR1020150074715A patent/KR101665522B1/en active IP Right Grant
- 2015-07-23 CN CN201520538249.8U patent/CN204943747U/en not_active Expired - Fee Related
- 2015-07-23 CN CN201510436555.5A patent/CN105299798B/en active Active
- 2015-07-24 MY MYPI2015702439A patent/MY190880A/en unknown
- 2015-07-27 US US14/810,331 patent/US20160025384A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112041619A (en) * | 2018-04-11 | 2020-12-04 | 夏普株式会社 | Air conditioning system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5805833B1 (en) | 2015-11-10 |
| CN204943747U (en) | 2016-01-06 |
| US20160025384A1 (en) | 2016-01-28 |
| KR101665522B1 (en) | 2016-10-12 |
| KR20160013800A (en) | 2016-02-05 |
| MY190880A (en) | 2022-05-13 |
| JP2016031168A (en) | 2016-03-07 |
| CN105299798B (en) | 2018-03-06 |
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