CN1181484A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN1181484A CN1181484A CN97116922A CN97116922A CN1181484A CN 1181484 A CN1181484 A CN 1181484A CN 97116922 A CN97116922 A CN 97116922A CN 97116922 A CN97116922 A CN 97116922A CN 1181484 A CN1181484 A CN 1181484A
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- heat exchanger
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- air conditioner
- compressor
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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
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
- F24F11/79—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling the direction of the supplied air
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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
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
- F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
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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
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the 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
- 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
- F25B2400/18—Refrigerant conversion
Abstract
In an air conditioner, a refrigerant circulation cycle is constituted by sequentially connecting a compressor, an indoor heat exchanger having an indoor fan, a PMV and an outdoor heat exchanger having an outdoor fan. An alternative refrigerant having a saturated pressure higher than that of HCFC22(R22) at the same temperature is used as a refrigerant. The blowout angle of air blown out from the indoor fan is vertically regulated by lateral louvers. An indoor controller, a louver motor and a louver drive circuit are adapted to control, at the start of heating operation, the lateral louvers so as to direct the air flow upward toward a ceiling side in the room and, when the indoor heat exchanger reaches a state capable of executing heat exchange operation, adapted to control the lateral louvers so as to direct the air flow downward toward a floor side in the room.
Description
The present invention relates to adopt the air conditioner of alternative refrigerant, this alternative refrigerant substitutes HCFC (two hydrogen fluorocarbon) 22 (hereinafter referred to as R22), with the same temperature of this R22 but promptly more move under the high pressure under than the high saturation pressure of this R22.
The air conditioner of indoor air conditioner etc. makes cold-producing medium circulation in kind of refrigeration cycle, by the condensation and the evaporation of this cold-producing medium, room air is turned cold or (with) warm, become one of necessity of current family, office building etc.
Used cold-producing medium in the above-mentioned air conditioner is adopt nontoxic, non-ignitibility, thermally-stabilised and chemically stable R22 at present.
But, in the existing air conditioner of R22 as cold-producing medium, shown in the heating run chart of Figure 15, when this air conditioner of running begins heating, be under the state of when being set at the louver sheet of blowing in stopping up towards common heating position (blowing out the position of wind) towards flooring direction (below), the drive compression machine.At this moment, the temperature T of indoor side heat exchanger rises, and (T 〉=(judged result of step S2 is NO) T0) before in order cold wind not to be sent into the interior space, stops the running (step S1) of indoor fan to surpass heat exchange (condensation) possibility temperature T 0 in this temperature T.
After the running beginning soon, the indoor side heat exchanger temperature T rises, when this temperature T surpasses heat exchange may temperature T 0 and when reaching the state that hot blast blows out (T 〉=T0, the judged result of step S2 is YES), the running of beginning indoor fan, (step S3) runs well.
In air conditioner, during heating, paying airborne frost (frosting) sometimes as the outside of the outdoor heat exchanger of evaporimeter, this frosting is to hinder one of reason of outdoor heat exchanger evaporation.Therefore, in air conditioner, during heating, remove the frosting of outdoor heat exchanger, carry out so-called defrosting running.
The defrosting of air conditioner running for example, when heating is turned round, is inverted to OFF to the cross valve of ON, and the loop direction that makes cold-producing medium is opposite during with heating.And, be flow control valve (electronic control valve, PMV) that the aperture of exapnsion valve remains predetermined aperture, the running of indoor and outdoor fan is stopped.
That is, the high temperature and high pressure gas shape cold-producing medium from compressor is discharged is imported in the outdoor heat exchanger, heat release and being liquefied in this outdoor heat exchanger.At this moment, by the heat release of cold-producing medium, paying frost and be heated and remove in outdoor heat exchanger outside.In addition, at the outdoor heat exchanger condensation liquefaction aqueous cold-producing medium, flow in the indoor side heat exchanger evaporation and gasification in this indoor side heat exchanger by the exapnsion valve.The cold-producing medium (gas shape cold-producing medium) that has gasified returns compressor again, below, carry out above-mentioned actuation cycle repeatedly.
In the air conditioner of R22 as cold-producing medium, discharge pressure when defrosting running (arriving exapnsion valve pressure before from the compressor discharge and by indoor side heat exchanger (condenser)) Pd and suction pressure (being inhaled into compressor pressure before by outdoor heat exchanger (evaporimeter) from the exapnsion valve) Ps's is poor, as illustrated in fig. 16, be about 20kg/cm
2Therefore,, change noise, the vibration that on the pipe arrangement of cross valve etc., produces, be almost the degree around not influencing by this pressure even cross valve when counter-rotating produces rapid pressure and change.
The R22 that uses as cold-producing medium in existing air conditioner has destruction to ozone layer, the use that is under an embargo in the future, so, develop the air conditioner that adopts the cold-producing medium that substitutes R22.
The cold-producing medium of R22 is as an alternative considered to adopt under same temperature the air conditioner than the alternative refrigerant high with this R22 saturation pressure (condensing pressure) (for example 50 ℃ time saturation pressure be more than the 2500kPa).
But, in the existing air conditioner, when adopting under same temperature than the high alternative refrigerant of this R22 saturation pressure, owing to the high-pressure side (from compressor by the system of condenser (being indoor side heat exchanger during heating) to the exapnsion valve; In addition, be called low-pressure side by evaporimeter (being outdoor heat exchanger during heating) to the system of compressor from the exapnsion valve) pressure sharply rise (in other words, discharge pressure rises), so, when above-mentioned heating running begins, when the running before above-mentioned indoor fan entry into service stopped, on high-tension side pressure anomaly raise.
Its result has a negative impact to the reliability of compressor, and may damage heat exchanger or pipe arrangement etc.In addition, when the compressor lubricant oil (refrigerator oil) that adopts was oily that compatibility such as ester oil is good, dielectric constant is high, along with the rapid rising of high side pressure, cold-producing medium dissolved in the lubricating oil of compressor, and the pasta of lubricating oil is risen.This pasta rises, and the motor winding portion in the compressor is dipped in the lubricating oil, increases leakage current.
For example, Figure 17 is illustrated in the air conditioner of employing alternative refrigerant higher than existing R22 saturation pressure under same temperature, beginning heating running back (when the indoor fan running stops), elapsed time t when the curve map of one of variation of high side pressure P, fuel head H, leakage current I example, transverse axis representative begin from this heating running.From Figure 17 as seen, after heating running beginning, the rapid immediately and abnormal ascending of high side pressure P, along with it rises, the amount of the height H of pasta and leakage current I increases.
Above-mentioned high-pressure side abnormal pressure rises, and also has problems when the defrosting running.That is, as at the same temperature alternative refrigerant higher, for example, adopt when 50 ℃ saturation pressure is cold-producing medium more than the 2500kpa than R22 saturation pressure, with the relation of discharge pressure Pd ' corresponding among Figure 16 and suction pressure Ps ' as shown in figure 18.As can be seen from Fig. 18, the discharge pressure Pd ' abnormal ascending during the defrosting running makes this Pd ' and the difference of Ps ' reach about 30kg/cm
2Therefore, abrupt pressure when reversing along with cross valve changes and increases from noise, vibration that the pipe arrangement of cross valve etc. produces, to producing harmful effect on every side.
The present invention makes in view of the above problems, and its purpose is to provide the air conditioner of a kind of employing alternative refrigerant higher than R22 saturation pressure under same temperature.In this air conditioner, rise, keep the performance and the reliability of compressor, prevent the damage of heat exchanger etc., simultaneously, provide comfortable heating space by suppressing on high-tension side rapid and unusual pressure.
Another object of the present invention is, it is being the air conditioner of the alternative refrigerant more than the 2500kpa than R22 saturation pressure saturation pressures high, during for example at 50 ℃ under the same temperature that a kind of employing is provided, in this air conditioner, by suppressing the unusual rising of discharge pressure, reduce the poor of this discharge pressure and suction pressure, when making the cross valve counter-rotating of defrosting running, from the noise of generation such as pipe arrangement, vibrate and reduce.
For achieving the above object, the present invention takes following technical scheme:
A kind of air conditioner, the outdoor heat exchanger that in turn connects compressor, the indoor side heat exchanger of being with indoor fan, exapnsion mechanism, band outdoor fan, constitute the cold-producing medium circulation, above-mentioned cold-producing medium is to adopt the alternative refrigerant that saturation pressure is higher than HCFC22 under same temperature to it is characterized in that having:
Blow out angle adjusting mechanism and blow out angle control mechanism; Blow out angle adjusting mechanism be used to regulate the wind that blows out from indoor fan in the interior space to the angle that blows out above the ceiling side and below the ground side; Blowing out angle control blows out mechanism and is used to control angle adjusting mechanism, when heating is turned round, with blowing out angle initialization is to blow out the position of wind towards ceiling side top, and, when described indoor side heat exchanger reaches the possible state of heat exchange, be to blow out the position of wind towards the ground side below with blowing out angle initialization.
Described air conditioner is characterized in that, has temperature testing organization, and this temperature testing organization is used to detect the temperature of indoor side heat exchanger and this indoor side heat exchanger and blows out at least one side of temperature among the two; The above-mentioned angle control mechanism that blows out, according to the detected signal of this temperature testing organization, control blows out angle adjusting mechanism.
Described air conditioner is characterized in that, the above-mentioned angle position of when heating begins, setting that blows out, and the position of setting during with refrigeration is slightly identical.
Described air conditioner, it is characterized in that, indoor fan and indoor side heat exchanger are provided in the indoor unit, this indoor unit is arranged on the indoor, this indoor unit have the suction grid that sucks room air and deliver to indoor side heat exchanger, by the indoor side heat exchanger temperature adjustment air be blown out to the grid that blows out of the interior space by indoor fan; The above-mentioned angle adjusting mechanism that blows out is arranged on and blows out near the grid, regulates from blowing out the described wind angle that blows out that grid blows out; The above-mentioned angle position of when heating begins, setting that blows out, above the position of when refrigeration, setting, and be positioned at make described from blowing out the position that is inhaled into above-mentioned suction grid that grid blows out with blowing out the wind short circuit.
Described air conditioner is characterized in that, the above-mentioned angle control mechanism that blows out, and in the elapsed time when beginning corresponding to heating, control blows out angle adjusting mechanism, is to blow out the position of wind towards the ground side below with blowing out angle initialization.
Described air conditioner is characterized in that, has temperature sensor and room temperature correction mechanism; Temperature sensor is provided near the indoor side heat exchanger, is used to detect indoor temperature; Be set to when blowing out wind towards the position of ceiling side top when blowing out angle, the room temperature correction mechanism is used to revise the detected temperatures of temperature sensor.
Described air conditioner, it is characterized in that, have near the temperature sensor that is provided in the indoor side heat exchanger, is used to detect indoor temperature, be set to when blowing out wind, think that the detected temperatures of temperature sensor is invalid towards the position of ceiling side top when blowing out angle.
A kind of air conditioner, have that outdoor heat exchanger with the indoor side heat exchanger of compressor, cross valve, band indoor fan, exapnsion mechanism, band outdoor fan connects successively and the cold-producing medium circulation that constitutes, above-mentioned cold-producing medium is to adopt the saturation pressure alternative refrigerant higher than HCFC22 under same temperature, be connected with indoor side heat exchanger by the discharge side of cross valve compressor, the suction side of this compressor is connected with outdoor heat exchanger, carries out the heating running; It is characterized in that having:
Counter-rotating controlling organization, defrosting running controlling organization and differential pressure control mechanism; When the defrosting running of counter-rotating controlling organization in the heating running begins,, the discharge side of compressor is connected with outdoor heat exchanger, the suction side of this compressor is connected with indoor side heat exchanger the cross valve counter-rotating; Defrosting running controlling organization is when the counter-rotating control of cross valve, the operating frequency of compressor is set at predetermined defrosting operating frequency, simultaneously, when the counter-rotating control of this cross valve, stop the rotation of indoor fan and outdoor fan, and the aperture of exapnsion mechanism is set at predetermined defrosting aperture; Differential pressure control mechanism reduces the poor of discharge lateral pressure in the cold-producing medium circulation and suction side pressure when above-mentioned switching mechanism counter-rotating control.
Described air conditioner is characterized in that, above-mentioned differential pressure control mechanism has stop control mechanism, and this stop control mechanism is certain hour before above-mentioned counter-rotating control beginning, and compressor and running are stopped.
Described air conditioner is characterized in that, above-mentioned differential pressure control mechanism has FREQUENCY CONTROL mechanism, and the compressor operation frequency setting when this FREQUENCY CONTROL mechanism controls above-mentioned counter-rotating is for being lower than the defrosting operating frequency.
Described air conditioner, it is characterized in that, above-mentioned differential pressure control mechanism has FREQUENCY CONTROL mechanism, this FREQUENCY CONTROL mechanism is before the certain hour of above-mentioned counter-rotating control beginning, the operating frequency of compressor is set at the defrosting operating frequency, before counter-rotating control beginning, keep this defrosting operating frequency.
Described air conditioner is characterized in that, above-mentioned differential pressure control mechanism has opening controlling mechanism, and this opening controlling mechanism was controlled to be the big scheduled volume of aperture when turning round than heating to the aperture of above-mentioned exapnsion mechanism with certain hour before above-mentioned counter-rotating control beginning.
Described air conditioner is characterized in that, above-mentioned differential pressure control mechanism has opening controlling mechanism, and this opening controlling mechanism was controlled to be the little scheduled volume of aperture when turning round than heating to the aperture of above-mentioned exapnsion mechanism with certain hour before above-mentioned counter-rotating control beginning.
Described air conditioner, it is characterized in that, above-mentioned differential pressure control mechanism has the rotation number controlling organization, and this rotation number controlling organization was controlled to be the high predetermined number of rotation number when turning round than heating to the rotation number of indoor fan with the scheduled time before above-mentioned counter-rotating control beginning.
Described air conditioner, it is characterized in that, above-mentioned differential pressure control mechanism has the rotation number controlling organization, and this rotation number controlling organization hanged down predetermined number to the rotation number that the rotation number of outdoor fan is controlled to be when turn round than heating with the scheduled time before above-mentioned counter-rotating control beginning.
Described air conditioner, it is characterized in that, above-mentioned alternative refrigerant is the cold-producing medium of synthetic ingredients constitute more than 80% of HFC32 and HFC125, or the cold-producing medium of synthetic ingredients constitute more than 80% of HFC143a and HFC125, or the cold-producing medium of ingredients constitute more than 45% of HFC32.
Employing is when being alternative refrigerant more than the 2500kpa than R22 saturation pressure saturation pressures high, during for example at 50 ℃ under the same temperature, from one of rapid reason that rises of heating running beginning high side pressure be, the running of indoor fan stops, and indoor side heat exchanger does not carry out heat exchange action.But, when making the indoor fan running usually, the cold wind of being crossed after the indoor side heat exchanger heat exchange of the possible state of heat exchange flows to indoor, so, in the 1st invention, set the angle that blows out of in the interior space ceiling side top and ground side below like this, promptly, when heating running beginning, with blowing out angle initialization is to blow out the position of wind towards ceiling side top, for example the temperature when indoor side heat exchanger rises, and when reaching heat exchange possibility state, is to blow out the position of wind towards the ground side below with blowing out angle initialization.By such setting, can avoid on high-tension side pressure sharply to rise, do not influence the beginning heating running of indoor comfort ground.
In addition, in the 2nd invention, because the mechanism that the difference of discharge pressure and suction pressure reduces when being provided with the cross valve counter-rotating when making defrosting running beginning is (for example before the cross valve counter-rotating, during with the mechanism of running OFF scheduled time of compressor, from scheduled time of cross valve counter-rotating, the aperture of exapnsion mechanism strengthened predetermined aperture or reduce the mechanism etc. of predetermined aperture), so the abrupt pressure in the time of can suppressing this cross valve counter-rotating changes.Therefore, the noise, the vibration that produce from cross valve pipe arrangement etc. in the time of can reducing to defrost the running beginning.
Promptly, for achieving the above object, in the air conditioner of the 1st invention, the outdoor heat exchanger that in turn connects compressor, the indoor side heat exchanger of being with indoor fan, exapnsion mechanism, band outdoor fan, constitute the cold-producing medium circulation, above-mentioned cold-producing medium is the alternative refrigerant higher than HCFC22 of saturation pressure under same temperature that adopts; It is characterized in that, have and blow out angle adjusting mechanism and blow out angle control mechanism; Blow out angle adjusting mechanism be used to regulate the wind that blows out from indoor fan in the interior space towards the angle that blows out above the card side and below the ground side; Blow out angle control mechanism and be used to control angle adjusting mechanism, when heating is turned round, with blowing out angle initialization is to blow out the position of wind towards ceiling side top, and, when indoor side heat exchanger reaches the possible state of heat exchange, be to blow out the position of wind towards the ground side below with blowing out angle initialization.
As better embodiment of the present invention, have temperature testing organization, this temperature testing organization is used to detect the temperature of indoor side heat exchanger and this indoor side heat exchanger and blows out at least one side of temperature among the two; The above-mentioned angle control mechanism that blows out, according to the detected signal of this temperature testing organization, control blows out angle adjusting mechanism.
As better embodiment of the present invention, indoor fan and indoor side heat exchanger are provided in the indoor unit, this indoor unit is arranged on the indoor, this indoor unit have the suction grid that sucks room air and deliver to indoor side heat exchanger, by the indoor side heat exchanger temperature adjustment air be blown out to the grid that blows out of the interior space by indoor fan; The above-mentioned angle adjusting mechanism that blows out is arranged on and blows out near the grid, regulates from what blow out that grid blows out and blows out the wind angle; The above-mentioned angle position of setting when heating begins that blows out above the position of setting when refrigeration, and is positioned at and makes from blowing out the position that is inhaled into above-mentioned suction grid that grid blows out with blowing out the wind short circuit.
In order to achieve the above object, in the air conditioner of the 2nd invention, have that outdoor heat exchanger with the indoor side heat exchanger of compressor, cross valve, band indoor fan, exapnsion mechanism, band outdoor fan connects successively and the cold-producing medium circulation that constitutes, above-mentioned cold-producing medium is to adopt the saturation pressure alternative refrigerant higher than HCFC22 under same temperature, be connected with indoor side heat exchanger by the discharge side of cross valve compressor, the suction side of this compressor is connected with outdoor heat exchanger, carries out the heating running; It is characterized in that, have counter-rotating controlling organization, defrosting running controlling organization and differential pressure control mechanism; When the defrosting running of counter-rotating controlling organization in the heating running begins,, the discharge side of compressor is connected with outdoor heat exchanger, the suction side of this compressor is connected with indoor side heat exchanger the cross valve counter-rotating; Defrosting running controlling organization is when the counter-rotating control of cross valve, the operating frequency of compressor is set at predetermined defrosting operating frequency, simultaneously, when the counter-rotating control of this cross valve, stop the rotation of indoor fan and outdoor fan, and the aperture of exapnsion mechanism is set at predetermined defrosting aperture; Differential pressure control mechanism reduces the poor of discharge lateral pressure in the cold-producing medium circulation and suction side pressure when above-mentioned switching mechanism counter-rotating control.
As better embodiment of the present invention, above-mentioned differential pressure control mechanism has stop control mechanism, and this stop control mechanism makes the running of compressor stop the scheduled time before above-mentioned counter-rotating control beginning.
As better embodiment of the present invention, above-mentioned differential pressure control mechanism has FREQUENCY CONTROL mechanism, and the compressor operation frequency setting when this FREQUENCY CONTROL mechanism controls above-mentioned counter-rotating is for being lower than the defrosting operating frequency.
As better embodiment of the present invention, above-mentioned differential pressure control mechanism has FREQUENCY CONTROL mechanism, and this FREQUENCY CONTROL mechanism is set at the defrosting operating frequency with the operating frequency of compressor before the scheduled time of above-mentioned counter-rotating control beginning, before counter-rotating control beginning, keep this defrosting operating frequency.
As better embodiment of the present invention, above-mentioned differential pressure control mechanism has opening controlling mechanism, and this opening controlling mechanism was controlled to be the big scheduled volume of aperture when turning round than heating to the aperture of above-mentioned exapnsion mechanism with the scheduled time before above-mentioned counter-rotating control beginning.
As better embodiment of the present invention, above-mentioned differential pressure control mechanism has opening controlling mechanism, and this opening controlling mechanism was controlled to be the little scheduled volume of aperture when turning round than heating to the aperture of above-mentioned exapnsion mechanism with the scheduled time before above-mentioned counter-rotating control beginning.
As better embodiment of the present invention, above-mentioned differential pressure control mechanism has the rotation number controlling organization, this rotation number controlling organization was controlled to be the high predetermined number of rotation number when turning round than heating to the rotation number of indoor fan with the scheduled time before above-mentioned counter-rotating control beginning.
As better embodiment of the present invention, above-mentioned differential pressure control mechanism has the rotation number controlling organization, this rotation number controlling organization hanged down predetermined number to the rotation number that the rotation number of outdoor fan is controlled to be when turn round than heating with the scheduled time before above-mentioned counter-rotating control beginning.
Good effect of the present invention:
As mentioned above, in the air conditioner of the 1st invention, the angle that blows out below interior space ceiling side top and ground side, be set in heating when beginning running and blow out (position during towards refrigeration, the position of wind above the ceiling side, or up from being inhaled into the position that sucks grid etc.) with blowing out air short circuit that grid blows out, for example when the rising of indoor side heat exchanger temperature, when reaching heat exchange possibility state, this is blown out angle initialization is to blow out the position of wind towards the ground side below.Because such setting can avoid on high-tension side pressure sharply to rise, do not influence indoor comfort ground beginning heating running.That is, on high-tension side pressure rises slowly, can keep the Performance And Reliability of compressor, prevents the damage of heat exchanger etc.
In the air conditioner of the 2nd invention, when the cross valve when defrosting running beginning reverses, reduce the poor of discharge pressure and suction pressure, so the rapid pressure in the time of can suppressing the cross valve counter-rotating changes.Therefore, during the defrosting running, during the cross valve counter-rotating, can reduce from noise, the vibration of generations such as its pipe arrangement.The air conditioner that makes is provided.
Following with reference to accompanying drawing, describe embodiments of the invention in detail:
Fig. 1 is the figure of the kind of refrigeration cycle of expression the present invention the 1st embodiment air conditioner.
Fig. 2 is the skiagraph of indoor unit general structure shown in the presentation graphs 1.
Fig. 3 is the control system figure that comprises the whole air conditioner of indoor unit and outdoor unit.
Fig. 4 is a flow chart, represents beginning to one of the action of normal heating running example from heating running among the 1st embodiment.
Fig. 5 is illustrated in the air conditioner of employing alternative refrigerant higher than R22 saturation pressure under same temperature of present embodiment, elapsed time t during from heating running beginning, the curve map of one of variation of high side pressure PA, fuel head HA, leakage current IA example, transverse axis is represented time t.
Fig. 6 is a flow chart, one of action example when representing in the heating running of the 2nd embodiment the defrosting running.
Fig. 7 be with transverse axis as time shaft t, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and the sequential chart of PMV.
Fig. 8 is in the 1st variation, with transverse axis as time shaft, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and the sequential chart of PMV.
Fig. 9 is in the 2nd variation, with transverse axis as time shaft, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and PMV sequential chart.
Figure 10 is in the 3rd variation, with transverse axis as time shaft, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and the sequential chart of PMV.
Figure 11 is in the 4th variation, with transverse axis as time shaft, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and the sequential chart of PMV.
Figure 12 is in the 5th variation, with transverse axis as time shaft, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and the sequential chart of PMV.
Figure 13 is in the 6th variation, with transverse axis as time shaft, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and the sequential chart of PMV.
Figure 14 is in other example, with transverse axis as time shaft, the compressor when expression heating running and defrosting running, cross valve, indoor fan, outdoor fan, and the sequential chart of PMV.
Figure 15 is a flow chart, represents existingly to begin to one of the action of normal heating running example from heating running.
Figure 16 is in the air conditioner of R22 as cold-producing medium, when defrosting running, and elapsed time t when beginning as turning round, the curve map of the difference of expression discharge pressure Pd and suction pressure Ps from defrosting with transverse axis.
Figure 17 in the air conditioner of high alternative refrigerant, as from heating running beginning elapsed time t, represents one of high side pressure P, fuel head H, leakage current I variation routine curve map with transverse axis than R22 saturation pressure in employing under same temperature.
Figure 18 is that the saturation pressure when adopting 50 ℃ is in the air conditioner of the alternative refrigerant more than the 2500kpa, when defrosting running, with transverse axis as from when beginning defrosting running elapsed time t, the curve map of expression discharge pressure Pd ' and the difference of suction pressure Ps '.
Below, with reference to the description of drawings embodiments of the invention.
(the 1st embodiment)
Fig. 1 is the figure of the kind of refrigeration cycle of expression present embodiment air conditioner.In the kind of refrigeration cycle of this aircondition, adopting is being alternative refrigerant more than the 2500kpa than R22 saturation pressure saturation pressures high, during for example at 50 ℃ under the same temperature.As this alternative refrigerant, the cold-producing medium that does not particularly damage the ozone layer has R32 (CH
2F
2) and R125 (CHF
2CF
3) cold-producing medium, the R143a (CH of synthetic ingredients constitute more than 80%
3CF
3) and R125 (CHF
2CF
3) cold-producing medium and the R32 (CH of synthetic ingredients constitute more than 80%
2F
2) the cold-producing medium of ingredients constitute more than 45% etc.
As shown in Figure 1, in the air conditioner 1, by pipe arrangement 7 successively with compressor 2, have the cross valve 3 that switches the refrigerant flow path function, band indoor fan 4a indoor side heat exchanger 4, connect into annular as the electronic control valve (PMV) 5 of exapnsion valve, the outdoor heat exchanger 6 of band outdoor fan 6a, form the kind of refrigeration cycle that cold-producing medium is reversibly circulated.
From this kind of refrigeration cycle as seen, in the air conditioner 1, switching controls by the cross valve 3 when indoor fan 4a and the outdoor fan 6a running (cross valve 3 → OFF), make cold-producing medium along solid arrow direction circulation among the figure (heat exchanger (sweat cooling effect) 4 → cross valve, the 3 → compressor 2 of compressor 2 → cross valve 3 → outdoor heat exchanger (condensation) 6 → PMV5 → indoor → ...) carry out cooling operation; In addition, switching controls by cross valve 3 (cross valve 3 → ON), make cold-producing medium along the circulation of direction shown in the dotted line among the figure (compressor 2 → cross valve 3 → indoor side heat exchanger (condensation heating effect) 4 → exapnsion valve, 5 → outdoor heat exchanger (evaporation) 6 → cross valve 3 → compressor 2 → ...) carry out heating running.In addition, when heating is turned round, indoor fan 4a and outdoor fan 6a are stopped, while switching controls cross valve 3, the direction that the loop direction when making cold-producing medium with heating is opposite (solid line direction among the figure) circulation can be carried out the defrosting running.
Compressor 2, cross valve 3, PMV5, outdoor heat exchanger 6 and outdoor fan 6a are located in the outdoor unit, and this outdoor unit is arranged on outdoor.This outdoor unit has evaporating temperature sensor 9 and outer temperature degree sensor 10.Evaporating temperature sensor 9 is located on the outdoor heat exchanger 6, is used to detect the cold-producing medium evaporating temperature of this outdoor heat exchanger 6.Outer temperature degree sensor 10 establish on outdoor heat exchanger 6 bodies or this outdoor heat exchanger 6 near, be used to detect outer temperature degree.According to the detection signal of this evaporating temperature sensor 9 and outer temperature degree sensor 10, control comprises that the outside of compressor 2 grades is all.
Indoor side heat exchanger 4 and indoor fan 4a are located in the indoor unit, and this indoor unit is located at indoor.Indoor unit has indoor temperature transmitter 11 and the heat-exchanger temperature sensor 12 that detects indoor temperature, and this heat-exchanger temperature sensor 12 is located on the indoor side heat exchanger 4, is used to detect the condensation of refrigerant temperature of this indoor side heat exchanger 4.According to each detection signal of indoor temperature transmitter 11 and heat-exchanger temperature sensor 12, control comprises that the indoor of indoor side heat exchanger 4 and indoor fan 4a is all.Indoor temperature transmitter 11 is located near the indoor side heat exchanger 4 (for example weather side) in the indoor unit.
The general structure of indoor unit shown in Fig. 2 presentation graphs 1.As shown in Figure 2, have the indoor unit 15 of indoor side heat exchanger 4 and indoor fan 4a, form slightly rectangle, for example be arranged on the indoor wall, its length direction corresponding with the rotating shaft direction of indoor fan 4a is along the indoor horizontal direction.
On this ventilation road 21, setting the indoor side heat exchanger 4 and the indoor fan 4a that for example bend to inverted v-shaped, this indoor fan 4a is provided in the air supply direction downstream side, for example is made of cross flow fan.Carry out heat exchange from sucking the room airs that grid 18 is drawn in the body case 16 by indoor side heat exchanger 4, the temperature adjustment degree air of cold wind or heating is delivered to indoorly by indoor fan 4a from blowing out grid 19 again, makes room temperature lowering or intensification.
Indoor fan 4a and fan case 20 and nozzle 25 constitute air blast jointly, and nozzle 25 is fixed on the rear sidewall of drainpipe 26, and drainpipe 26 is used to accept the draining of indoor side heat exchanger 4.
Blow out the interior side of grid 19, setting wind direction adjusting louver 27 and left and right sides wind direction adjusting louver 28 up and down.Wind direction is regulated louver 27 and is regulated from blowing out wind (blowing out wind) W that grid 19 blows out towards the foreign side angle that blows out towards interior space ceiling side top and floor side below (hereinafter referred to as above-below direction) up and down, and left and right sides wind direction is regulated louver 28 and regulated the angle that blows out towards the horizontal direction (left and right directions) along fan rotation axis.
Wind direction is regulated a pair of lateral louvers 27a, the 27b up and down that louver 27 for example has coiled sheet up and down, this lateral louvers 27a, 27b be along the length direction that blows out grid 19 that slightly is parallel to fan rotation axis, along its total length abreast and above-below direction with predetermined space be arranged side by side.Each lateral louvers 27a, 27b are schemed not show that swing mechanism is center above-below direction swing with the axle (swinging axle) along its length direction, the above-below direction angle of oscillation of these lateral louvers 27a, 27b is regulated by the aftermentioned louver motor of swing mechanism, and the above-below direction that control blows out wind W blows out angle.
Fig. 3 represents to comprise the The whole control system of the air conditioner 1 of indoor unit 15 and outdoor unit 30.
As shown in Figure 3, indoor unit 15 has for example indoor control part 31 of micro computer is installed, should should be indoor the whole indoor unit 15 of control part 31 controls, on this indoor control part 31, connecting the remote controller R that usefulness is controlled in AC power S that supply power uses and straighforward operation.
Below, the action of indoor unit when beginning is turned round in the action of present embodiment, particularly heating is described.
During the 1 beginning heating of running aircondition, indoor control part 31 is by the 35 control RM34 rotations of louver drive circuit, lateral louvers 27a, the angle position of 27b is set at and blows out the position (horizontal level (or than this horizontal level horizontal level towards ceiling top) that for example slightly be parallel to ceiling or ground of wind W towards interior space ceiling direction (going up direction), perhaps, make the position (than the location of short circuit of above-mentioned horizontal level) that is inhaled into suction grid 18 (see lateral louvers 27a ' shown in dotted lines in Figure 2 towards ceiling side top with blowing out wind W short circuit, blow out wind W1 (louver horizontal level) shown in the position of 27b ' and the dotted arrow, blow out wind W2 (louver location of short circuit)).Under this state, outdoor control part 40 is the cross valve switching controls ON, by phase inverter 43 the CM42 rotation is driven, and makes compressor 2 startings, simultaneously, by fan drive circuit 45 the FM32 rotation is driven, and outdoor fan 44 is driven.
At this moment, indoor control part 31 is always with reference to the detection signal of heat-exchanger temperature sensor 12, rises based on the temperature T of the indoor side heat exchanger 4 of this detection signal, and judging whether this temperature T has surpassed heat exchange may temperature T 0 (T 〉=T0) (step S11).
That is, (during T＜T0), indoor control part 31 is NO in the judgement of step S11, repeatedly the judgment processing of step S11 when the temperature T of heat-exchanger temperature sensor 12 detected indoor side heat exchangers 4 surpasses heat exchange may temperature T 0 time.At this moment, because T＜T0, so, under indoor fan 4a running, be cold wind from blowing out inferior air-out that grid 19 blows out, owing to the angle position of lateral louvers 27a, 27b is set to horizontal level or location of short circuit, so, this is cold blows out wind as blowing out wind W1 and blowing out shown in the wind W2, blows out towards interior space ceiling side top, perhaps is inhaled into suction grid 18 ground towards short circuit ground and blows out.Like this, to whole interior space refrigeration, this interior space does not keep the few state of variations in temperature.
When the temperature T of indoor side heat exchanger 4 has surpassed heat exchange possibility temperature T 0 (T 〉=T0), judged result at step S11 is YES, indoor control part 31 is by the 35 control RM34 rotations of louver drive circuit, and the position blows out the position (see in Fig. 2 lateral louvers 27a solid line shown in, the position of 27b) of wind towards flooring direction (following direction) when being set at the angle position of lateral louvers 27a, 27b towards common heating.Carry out common heating running.That is, from blowing out the wind that blows out that grid 19 blows out, because T 〉=T, so be warm braw, this is warm to blow out wind shown in solid line arrow W under the running of indoor fan 4a, blow out towards flooring direction (following direction), so, the interior space warm (step S12).
Fig. 5 is illustrated in the above-mentioned heating running starting action, and transverse axis be elapsed time t when the heating running begins, one of variation of high side pressure PA, fuel head HA, leakage current IA example.
Promptly, in this structure, adopt in the air conditioner of alternative refrigerant higher under the same temperature than R22 saturation pressure, make indoor fan 4a running immediately after the heating running beginning, after this heating running beginning, carry out heat exchange by indoor side heat exchanger 4 immediately, so as shown in Figure 5, high side pressure PA gently rises.Its result, the maximal pressure of high side pressure PA (peak value) is than low in the prior art, can avoid the influence to the reliability of compressor 2 and indoor side heat exchanger 4 etc., life-span etc. of the rapid rising of high side pressure PA and peak value.
As shown in Figure 5, owing to high side pressure PA slowly rises, so cold-producing medium can not dissolve in the lubricating oil excessively, pasta rising compared with prior art very little (seeing fuel head HA).Therefore, compared with prior art, the peak value of the leakage current IA that rise to cause because of pasta is very low.
In this structure, if the set positions of lateral louvers 27a ', 27b ' is become location of short circuit, then the inlet temperature owing to indoor side heat exchanger 4 rises, so, to the time shortening of the common heating running of beginning (louver turns round downwards).
In this structure, it is the angle position of controlling lateral louvers 27a, 27b by the temperature T of heat-exchanger temperature sensor 12 detected indoor side heat exchangers 4, but the present invention is not limited thereto, also can be corresponding to variations in temperature, change according to indoor temperature transmitter 11 detected room temperatures, the temperature T of discerning indoor side heat exchanger 4 has surpassed heat exchange possibility temperature T 0, carries out the angle position control of lateral louvers 27a, 27b.In addition, also can use the angle position control of carrying out lateral louvers 27a, 27b from the elapsed time of heating running beginning to the time t0 of heat exchange (condensation) the possibility state of indoor side heat exchanger 4 according to beginning from the heating running.In addition, can also according to the high side pressure value of obtaining by the temperature T of indoor side heat exchanger 4, carry out the angle position control of lateral louvers 27a, 27b with reference to the high side pressure P0 in heat exchange (condensation) the possibility state of indoor side heat exchanger 4.
In addition, lateral louvers 27a, 27b blow out wind direction ceiling side top and blow out during horizontal level or the location of short circuit, are inhaled into and suck grid 18, so indoor temperature transmitter 11 detected room temperatures may surpass actual room temperature.Therefore, lateral louvers 27a, 27b are during towards horizontal level or location of short circuit, will be on indoor temperature transmitter 11 detected room temperatures, add the temperature rising part that blows out in the part that blows out above the wind direction ceiling side, revise, according to this revised house temperature, make indoor control part 31 carry out control action.Perhaps, during horizontal level or the location of short circuit, think that indoor temperature transmitter 11 detected room temperatures are invalid, make indoor control part 31 carry out control action at lateral louvers 27a, 27b.When constituting like this,, can avoid the action of indoor control part 31 to control the misoperation that is produced, improve reliability according to the detected value different of indoor temperature transmitter 11 with actual room temperature.
(the 2nd embodiment)
The structure of present embodiment air conditioner omits together to structure shown in Figure 3 with Fig. 1, and its explanation is omitted.That is, the air conditioner 1 of present embodiment, the control action when it is characterized in that defrosting, so, with reference to Fig. 6 whole actions in when control defrosting are described, do not explain for other action.In addition, with the 1st embodiment similarly, the cold-producing medium of use is not R22, and adopts the saturation pressure alternative refrigerant higher than this R22 under same temperature, for example, saturation pressure is the alternative refrigerant more than the 2500kpa in the time of 50 ℃.
Suppose that now air conditioner 1 carries out the heating running, compressor 2 drives with predetermined operating frequency (rotation number), and cross valve 3 is switched to ON.This operating frequency (rotation number) is called the heating operating frequency hereinafter.
Indoor fan 4a is with predetermined rotation number running (ON), and outdoor fan 6a is also with predetermined rotation number running (ON).PMV5 is controlled as certain aperture, the aperture of the control when this aperture is based on the heating running (overheated (SH) control).
That is, in heating when running,, the high-temperature high-pressure refrigerant (alternative refrigerant) by compressor 2 compresses shown in solid line, is guided indoor side heat exchanger 4 through cross valve 3, corresponding to the rotation of indoor fan 4a and heat release makes indoor warming.Because of making the indoor chilled cold-producing medium that warms, be subjected to the exapnsion effect at PMV5 and reduce pressure and be guided outdoor heat exchanger 6.In the rotation number of this outdoor heat exchanger 6 corresponding to outdoor fan 6a, from outer gas, absorb heat and vaporized cold-producing medium, delivered to compressor 2 once more by cross valve 3, be guided indoor side heat exchanger 4 by cross valve 3 once more as high-temperature high-pressure refrigerant.Like this, carry out the heating circulation repeatedly, carry out heating running (Fig. 6 is with reference to step S20).
In the above-mentioned heating running, at step S21, judge always that by outdoor control part 40 the cold-producing medium evaporating temperature Te of the detected evaporation in outdoor heat converter 6 of evaporating temperature sensor 9 are lower than the state (Te＜Ts) whether continued the scheduled time (for example 30 minutes) of predetermined temperature Ts (for example-2 ℃), if certain time (judged result of step S21 is NO) not, then be judged as the running that needn't defrost, the action of step S20 is the heating running repeatedly.
When the judged result at step S21 was YES, promptly (Te＜Ts) had continued the scheduled time when above, and indoor control part 31 and outdoor control part 40 are carried out defrosting running control.
At this moment, outdoor control part 40 stops the driving of CM42 earlier by phase inverter 43, stop the spinning movement (compressor 2OFF, step S22) of compressor 2.Stop through after the scheduled time from compressor 2, outdoor control part 40 is reversed to OFF to the cross valve 3 of ON, and the loop direction that makes cold-producing medium is opposite during with heating, will keep the aperture of PMV5 to remain certain aperture (defrosting aperture) simultaneously.When reversing,, stop the running of outdoor fan 6a by fan drive circuit 45 control FM44 with cross valve 3.Indoor control part 31 (stops simultaneously with the running of outdoor fan 6a) when reversing with cross valve 3, by speed control circuit 33 control FM32, stops the running (step S23) of indoor fan 4a.
Like this, defrosting running beginning.That is, the gas shape cold-producing medium of the HTHP of discharging from compressor 2 is guided in the outdoor heat exchanger 6 through the cross valve 3 of OFF state, heat release in outdoor heat exchanger 6 and liquefying.At this moment, because the heat release of cold-producing medium, paying frost and be heated and remove in outdoor heat exchanger 6 outsides.At outdoor heat exchanger 6 condensation liquefactions aqueous cold-producing medium be sent to by PMV5 in the indoor side heat exchanger 4, in indoor side heat exchanger 4, gasify by free convection heat absorption, evaporation.The cold-producing medium (gas shape cold-producing medium) that has gasified returns compressor 2 again, below, carry out above-mentioned actuation cycle (step S24) repeatedly.
The sequential chart of the air conditioner 1 (compressor 2, cross valve 3, indoor fan 4a, outdoor fan 6a and PMV5) in running of heating shown in Fig. 7 presentation graphs 6 flow charts and the defrosting running.As shown in Figure 7, in this structure, before the defrosting beginning, with compressor 2OFF, be under zero the state, to make cross valve 3 counter-rotatings in the discharge pressure of compressor 2 and suction pressure, begin the defrosting running, so the difference of discharge pressure and suction pressure diminishes, the pressure during cross valve 3 counter-rotatings changes also slow.Therefore, during cross valve 3 counter-rotating, noise, the vibration that produces on the pipe arrangement of this cross valve 3 etc. can ease down to the degree around the influence hardly.
Finish, return under the situation of the processing of step S20, heating running repeatedly being judged as defrosting, outdoor control part 40 also can be controlled phase inverter 43 and CM42, compressor 2 is remained in operation on one side, on one side the operating frequency of this compressor 2 is brought up to above-mentioned heating operating frequency from the defrosting frequency.In addition, outdoor control part 40 also can be controlled phase inverter 43 and CM42, the running of compressor 2 is temporarily stopped,, the operating frequency of this compressor 2 is brought up to above-mentioned heating operating frequency (seeing the sequential of the frequency of compressor operation shown in the dotted line among Fig. 7) through after the scheduled time.
In addition, in this structure, be before the defrosting running, with compressor 2OFF, reduce the poor of discharge pressure and suction pressure, but the present invention is not limited thereto, can make various variation.
For example, as the 1st variation, shown in the sequential chart of Fig. 8, outdoor control part 40 is in the processing of the step S22 of Fig. 6, the operating frequency of compressor 2 is lowered gradually, be lower than moment (operating frequency Hmin at this moment) of defrosting frequency at this operating frequency, make cross valve 3 counter-rotating etc., begin the defrosting running.Similarly, in the defrosting zero hour, with heating operating frequency and defrosting operating frequency compare during also with above-mentioned compressor 2 → OFF by the operating frequency of compressor 2 for this structure, because it is very low, so discharge pressure is very low, the difference of this discharge pressure and suction pressure is very little.Therefore, during cross valve 3 counter-rotating, noise, the vibration that produces on the pipe arrangement of this cross valve 3 etc. can be decreased to the degree around the influence hardly.In addition, in the structure of this variation, the operating frequency of compressor 2 is controlled to be gradually lowers, because OFF not, so the discharge pressure of (during cross valve 3 counter-rotatings) and suction pressure is poor during the defrosting beginning, little during than " compressor 2 → OFF control ".On the other hand, before beginning the defrosting running, compressor 2 is always driving, so, can proceed the heating running of this period, like this, can not influence the comfortableness of the preceding heating of defrosting running beginning.In addition, also operating frequency Hmin can be made as " OHz ".
Fig. 9 represents the sequential chart of the 2nd variation.As shown in the figure, outside control part 40 is in the processing of the step 22 of Fig. 6, the operating frequency of compressor 2 is lowered gradually, omit under the consistent state at this operating frequency and defrosting frequency, this operating frequency is kept certain hour, at the state of this maintenance, make cross valve counter-rotating etc., begin the defrosting running.In such formation, in defrosting zero hour, the state that the operating frequency of compressor 2 is more much lower than heating operating frequency keeps certain defrosting frequency constant, suction pressure is risen and the reduction discharge pressure.The difference of this discharge pressure and suction pressure is reduced.Therefore, during cross valve 3 counter-rotating, the degree around noise, the vibration that produces on the pipe arrangement of this cross valve 3 etc. can be reduced to and not influence.
This distortion also with the 1st variation similarly, before beginning defrosting running, compressor 2 is always driving, so, can proceed heating running during this period, not influencing the heating comfortableness before the defrosting beginning.
Figure 10 represents the sequential chart of the 3rd variation.As shown in figure 10, outdoor control part 40 lowers the operating frequency of compressor 2 in the processing of the step 22 of Fig. 6 gradually, simultaneously the aperture of PMV5 is further opened predetermined aperture (aperture up) from the aperture of controlling based on SH.When operating frequency reaches defrosting during frequency, outdoor control part 40 is reversed to OFF with cross valve 3, and the loop direction that makes cold-producing medium is opposite during with heating, further opens the aperture of PMV5 again, remains the defrosting aperture.In addition, when reversing, make the running OFF of outdoor fan 6a, and under the control of indoor control part 31, make the running OFF of indoor fan 4a, begin the defrosting running with cross valve 3.
Structure according to this variation, because before the defrosting beginning, the aperture of PNV5 is further opened predetermined aperture again from the aperture of controlling based on SH, so, after opening PMV5,, be sent to by PMV5 and outdoor heat converter 6 (evaporimeter) in the refrigerant gas of compressor 2 and contain liquefied refrigerant (liquid returns state) to the time between the defrosting beginning.This contains the refrigerant gas of liquefied refrigerant, and the accumulator liquefied refrigerant that does not show by figure is removed, and has only refrigerant gas to be inhaled into compressor 2.
That is, in this variation, before the defrosting running, the aperture of PMV5 is opened predetermined aperture, make the heating running and form liquid and return state, by accumulator handle liquefaction component separation, lower the refrigerant gas amount of doing the heating circulation, so, discharge pressure can temporarily be reduced (before defrosting running beginning).Therefore, with the various embodiments described above and each variation similarly, the difference of discharge pressure and suction pressure reduces, the pressure during cross valve 3 counter-rotatings changes also slow.Its result, during cross valve 3 counter-rotating, noise, the vibration that produces on the pipe arrangement of this cross valve 3 etc. can be reduced to the degree around the influence hardly.
Figure 11 represents the sequential chart of the 4th variation.As shown in figure 11, outdoor control part 40 makes the operating frequency of compressor 2 begin to lower gradually in the processing of the step 22 of Fig. 6, simultaneously the aperture of PMV5 is further closed predetermined aperture (aperture down) from the aperture of controlling based on SH.When operating frequency reaches defrosting during frequency, outdoor control part 40 is reversed to OFF with cross valve 3, and the loop direction that makes cold-producing medium is opposite during with heating, simultaneously, the aperture increasing of PMV5 is remained on the defrosting aperture.And, when reversing, make the running OFF of outdoor fan 6a with cross valve 3, under the control of indoor control part 31, make the running OFF of indoor fan 4a, begin the defrosting running.
According to this variation, owing to before the defrosting beginning, the aperture of PMV5 is closed certain aperture from the aperture of controlling based on SH, so, after closing PMV5,, reduce the refrigerant gas amount that heating circulates of doing between the defrosting beginning.Therefore, before defrosting running beginning, discharge pressure is lowered.Its result, with above-mentioned the 2nd embodiment and each variation similarly, the difference of discharge pressure and suction pressure reduces, the pressure during cross valve 3 counter-rotatings changes also slow, can obtain the inhibition noise same with the 2nd embodiment and each variation, the effect of vibration.
Figure 12 represents the sequential chart of the 5th variation, and as shown in figure 12, outdoor control part 40 makes the operating frequency of compressor 2 begin to lower gradually in the processing of the step 22 of Fig. 6.When the operating frequency of this outdoor control part 40 reduced the control beginning, indoor control part 31 made the rotation number of indoor fan 4a improve predetermined number (up) by speed control circuit 33 and FM32.When operating frequency reaches defrosting during frequency, outdoor control part 40 is reversed to OFF with cross valve 3, and the loop direction that makes cold-producing medium is opposite during with heating, simultaneously, opens the aperture of PMV5, remains the defrosting aperture.In addition, when reversing, make the running OFF of outdoor fan 6a with cross valve, indoor control part 31 with cross valve 3 counter-rotating in when running OFF (outdoor fan 6a), by speed control circuit 33 and FM32, make running (rotation) OFF of indoor fan 4a, begin the defrosting running.
According to this variation, before defrosting beginning, with the rotation number rising predetermined number of indoor fan 4a, so, the rotation number of indoor fan 4a rise the back before the defrosting beginning between, the condensation number (thermal discharge) of indoor side heat exchanger 4 (condenser) increases.Therefore, before defrosting running beginning, can reduce discharge pressure.Its result, with above-mentioned the 2nd embodiment and each variation similarly the difference of discharge pressure and suction pressure reduce, the pressure during cross valve 3 counter-rotatings changes also slow, can obtain the inhibition noise same with the 2nd embodiment and each variation, the effect of vibration.
Figure 13 represents the sequential chart of the 6th variation, as shown in figure 13, outdoor control part 40 makes the operating frequency of compressor 2 begin to lower gradually in the processing of the step 22 of Fig. 6, simultaneously, make the rotation number decline predetermined number (down) of outdoor fan 6a by fan drive circuit 45 and FM44.When operating frequency reaches defrosting during frequency, outdoor control part 40 is reversed to OFF with cross valve 3, and the loop direction that makes cold-producing medium is opposite during with heating, simultaneously, opens the aperture of PMV5, remains the defrosting aperture.In addition, outdoor control part 40, with cross valve 3 counter-rotating in, make running (rotation) OFF of outdoor fan 6a by fan drive circuit 45 and FM44, under the control of indoor control part 31, make the running OFF of indoor fan 4a simultaneously, begin defrosting and turn round.
According to this variation, before defrosting beginning, with the rotation number of the outdoor fan 6a fixed number that descends, so, the rotation number of outdoor fan 6a descend the back before the defrosting beginning between, evaporation capacity (caloric receptivity) reduction of outdoor heat exchanger 6 (evaporimeter).Therefore, before defrosting running beginning,, can reduce the circulating mass of refrigerant in the heating circulation though reduced suction pressure.The minimizing of this circulating mass of refrigerant, make discharge pressure reduce, its reduction amount is greater than the reduction amount of suction pressure, so, with above-mentioned the 2nd embodiment and each variation similarly, the difference of discharge pressure and suction pressure reduces, and the pressure during cross valve 3 counter-rotating changes also slow, can obtain the inhibition noise same with the 2nd embodiment and each variation, the effect of vibration.
In the present embodiment, in the sequential chart of the flow chart of Fig. 6 and Fig. 7～Figure 13, the various controls of the difference of discharge pressure and suction pressure have been represented to reduce.But also Fig. 7～each control combination ground shown in Figure 13 can be carried out.That is, can among the FREQUENCY CONTROL of Fig. 7～compressor 2 shown in Figure 9 any, the rotation number control of Guaranteed any of the aperture of Figure 10～PMV5 shown in Figure 11, indoor fan 4a shown in Figure 12, and the rotation number control of the outdoor fan 6a shown in Figure 13 execution that combines respectively.For example, Figure 14 represents compressor 2OFF control (Fig. 7), PMV5 aperture are strengthened the sequential chart that control (Figure 10), indoor fan 4a rotation number raising (Figure 12) and outdoor fan 6a rotation number decline (Figure 13) combine respectively and carries out.
Like this, carry out each action control in combination, can obtain better effect, have bigger inhibition noise, the effect of vibration.
In addition, in the present embodiment, cold-producing medium as an alternative, be that saturation pressure is the above cold-producing medium of 2500kpa when adopting 50 ℃, but the present invention is not limited thereto, so long as under same temperature than high cold-producing medium of R22 saturation pressure and the cold-producing medium that does not damage the ozone layer, can adopt.
Claims (16)
1. air conditioner, the outdoor heat exchanger that in turn connects compressor, the indoor side heat exchanger of being with indoor fan, exapnsion mechanism, band outdoor fan, constitute the cold-producing medium circulation, above-mentioned cold-producing medium is to adopt the alternative refrigerant that saturation pressure is higher than HCFC22 under same temperature to it is characterized in that having:
Blow out angle adjusting mechanism and blow out angle control mechanism; Blow out angle adjusting mechanism be used to regulate the wind that blows out from indoor fan in the interior space to the angle that blows out above the ceiling side and below the ground side; Blowing out angle control blows out mechanism and is used to control angle adjusting mechanism, when heating is turned round, with blowing out angle initialization is to blow out the position of wind towards ceiling side top, and, when described indoor side heat exchanger reaches the possible state of heat exchange, be to blow out the position of wind towards the ground side below with blowing out angle initialization.
2. air conditioner as claimed in claim 1 is characterized in that, has temperature testing organization, and this temperature testing organization is used to detect the temperature of indoor side heat exchanger and this indoor side heat exchanger and blows out at least one side of temperature among the two; The above-mentioned angle control mechanism that blows out, according to the detected signal of this temperature testing organization, control blows out angle adjusting mechanism.
3. air conditioner as claimed in claim 1 or 2 is characterized in that, the above-mentioned angle position of when heating begins, setting that blows out, and the position of setting during with refrigeration is slightly identical.
4. air conditioner as claimed in claim 1, it is characterized in that, indoor fan and indoor side heat exchanger are provided in the indoor unit, this indoor unit is arranged on the indoor, this indoor unit have the suction grid that sucks room air and deliver to indoor side heat exchanger, by the indoor side heat exchanger temperature adjustment air be blown out to the grid that blows out of the interior space by indoor fan; The above-mentioned angle adjusting mechanism that blows out is arranged on and blows out near the grid, regulates from blowing out the described wind angle that blows out that grid blows out; The above-mentioned angle position of when heating begins, setting that blows out, above the position of when refrigeration, setting, and be positioned at make described from blowing out the position that is inhaled into above-mentioned suction grid that grid blows out with blowing out the wind short circuit.
5. air conditioner as claimed in claim 1 is characterized in that, the above-mentioned angle control mechanism that blows out, and in the elapsed time when beginning corresponding to heating, control blows out angle adjusting mechanism, is to blow out the position of wind towards the ground side below with blowing out angle initialization.
6. air conditioner as claimed in claim 1 is characterized in that, has temperature sensor and room temperature correction mechanism; Temperature sensor is provided near the indoor side heat exchanger, is used to detect indoor temperature; Be set to when blowing out wind towards the position of ceiling side top when blowing out angle, the room temperature correction mechanism is used to revise the detected temperatures of temperature sensor.
7. air conditioner as claimed in claim 1, it is characterized in that, have near the temperature sensor that is provided in the indoor side heat exchanger, is used to detect indoor temperature, be set to when blowing out wind, think that the detected temperatures of temperature sensor is invalid towards the position of ceiling side top when blowing out angle.
8. air conditioner, have that outdoor heat exchanger with the indoor side heat exchanger of compressor, cross valve, band indoor fan, exapnsion mechanism, band outdoor fan connects successively and the cold-producing medium circulation that constitutes, above-mentioned cold-producing medium is to adopt the saturation pressure alternative refrigerant higher than HCFC22 under same temperature, be connected with indoor side heat exchanger by the discharge side of cross valve compressor, the suction side of this compressor is connected with outdoor heat exchanger, carries out the heating running; It is characterized in that having:
Counter-rotating controlling organization, defrosting running controlling organization and differential pressure control mechanism; When the defrosting running of counter-rotating controlling organization in the heating running begins,, the discharge side of compressor is connected with outdoor heat exchanger, the suction side of this compressor is connected with indoor side heat exchanger the cross valve counter-rotating; Defrosting running controlling organization is when the counter-rotating control of cross valve, the operating frequency of compressor is set at predetermined defrosting operating frequency, simultaneously, when the counter-rotating control of this cross valve, stop the rotation of indoor fan and outdoor fan, and the aperture of exapnsion mechanism is set at predetermined defrosting aperture; Differential pressure control mechanism reduces the poor of discharge lateral pressure in the cold-producing medium circulation and suction side pressure when above-mentioned switching mechanism counter-rotating control.
9. air conditioner as claimed in claim 8 is characterized in that above-mentioned differential pressure control mechanism has stop control mechanism, and this stop control mechanism is certain hour before above-mentioned counter-rotating control beginning, and compressor and running are stopped.
10. air conditioner as claimed in claim 8 is characterized in that above-mentioned differential pressure control mechanism has FREQUENCY CONTROL mechanism, and the compressor operation frequency setting when this FREQUENCY CONTROL mechanism controls above-mentioned counter-rotating is for being lower than the defrosting operating frequency.
11. air conditioner as claimed in claim 8, it is characterized in that, above-mentioned differential pressure control mechanism has FREQUENCY CONTROL mechanism, this FREQUENCY CONTROL mechanism is before the certain hour of above-mentioned counter-rotating control beginning, the operating frequency of compressor is set at the defrosting operating frequency, before counter-rotating control beginning, keep this defrosting operating frequency.
12. air conditioner as claimed in claim 8, it is characterized in that, above-mentioned differential pressure control mechanism has opening controlling mechanism, and this opening controlling mechanism was controlled to be the big scheduled volume of aperture when turning round than heating to the aperture of above-mentioned exapnsion mechanism with certain hour before above-mentioned counter-rotating control beginning.
13. air conditioner as claimed in claim 8, it is characterized in that, above-mentioned differential pressure control mechanism has opening controlling mechanism, and this opening controlling mechanism was controlled to be the little scheduled volume of aperture when turning round than heating to the aperture of above-mentioned exapnsion mechanism with certain hour before above-mentioned counter-rotating control beginning.
14. air conditioner as claimed in claim 8, it is characterized in that, above-mentioned differential pressure control mechanism has the rotation number controlling organization, this rotation number controlling organization was controlled to be the high predetermined number of rotation number when turning round than heating to the rotation number of indoor fan with the scheduled time before above-mentioned counter-rotating control beginning.
15. air conditioner as claimed in claim 8, it is characterized in that, above-mentioned differential pressure control mechanism has the rotation number controlling organization, and this rotation number controlling organization hanged down predetermined number to the rotation number that the rotation number of outdoor fan is controlled to be when turn round than heating with the scheduled time before above-mentioned counter-rotating control beginning.
16. as claim 1 or 8 described air conditioners, it is characterized in that, above-mentioned alternative refrigerant is the cold-producing medium of synthetic ingredients constitute more than 80% of HFC32 and HFC125, or the cold-producing medium of synthetic ingredients constitute more than 80% of HFC143a and HFC125, or the cold-producing medium of ingredients constitute more than 45% of HFC32.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP290883/1996 | 1996-10-31 | ||
| JP290883/96 | 1996-10-31 | ||
| JP29088396A JP3495858B2 (en) | 1996-10-31 | 1996-10-31 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1181484A true CN1181484A (en) | 1998-05-13 |
| CN1108491C CN1108491C (en) | 2003-05-14 |
Family
ID=17761751
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN97116922A Expired - Fee Related CN1108491C (en) | 1996-10-31 | 1997-09-23 | Air conditioner |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0840071B1 (en) |
| JP (1) | JP3495858B2 (en) |
| KR (1) | KR100263664B1 (en) |
| CN (1) | CN1108491C (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103968494A (en) * | 2013-01-25 | 2014-08-06 | 珠海格力电器股份有限公司 | Control method of air-conditioning system and air-conditioning system |
| CN104879977A (en) * | 2014-02-28 | 2015-09-02 | 株式会社电装 | Apparatus for adjusting temperature and storing |
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| JPS57184847A (en) * | 1981-05-07 | 1982-11-13 | Matsushita Electric Ind Co Ltd | Air conditioner |
| JPS5866744A (en) * | 1981-10-19 | 1983-04-21 | Hitachi Ltd | Air outlet of air conditioner |
| KR900005979B1 (en) * | 1985-08-22 | 1990-08-18 | 미쓰비시 덴끼 가부시기가이샤 | Air conditioning apparatus |
| JPH06249485A (en) * | 1993-02-26 | 1994-09-06 | Toshiba Corp | Air conditioning ventilation system |
| JPH08166172A (en) * | 1994-12-14 | 1996-06-25 | Sanyo Electric Co Ltd | Refrigerating equipment |
| JPH09138026A (en) * | 1995-11-14 | 1997-05-27 | Sanyo Electric Co Ltd | Refrigerating cycle and air conditioner provided with the refrigerant cycle |
| JPH09145174A (en) * | 1995-11-17 | 1997-06-06 | Sanyo Electric Co Ltd | Air conditioner and its operation controlling method |
| JPH09145169A (en) * | 1995-11-17 | 1997-06-06 | Sanyo Electric Co Ltd | Air conditioner |
-
1996
- 1996-10-31 JP JP29088396A patent/JP3495858B2/en not_active Expired - Fee Related
-
1997
- 1997-09-23 CN CN97116922A patent/CN1108491C/en not_active Expired - Fee Related
- 1997-10-29 KR KR1019970057581A patent/KR100263664B1/en not_active IP Right Cessation
- 1997-10-31 EP EP97308769A patent/EP0840071B1/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103968494A (en) * | 2013-01-25 | 2014-08-06 | 珠海格力电器股份有限公司 | Control method of air-conditioning system and air-conditioning system |
| CN103968494B (en) * | 2013-01-25 | 2016-08-03 | 珠海格力电器股份有限公司 | The control method of air conditioning system and air conditioning system |
| CN104879977A (en) * | 2014-02-28 | 2015-09-02 | 株式会社电装 | Apparatus for adjusting temperature and storing |
| CN107614984A (en) * | 2015-03-26 | 2018-01-19 | 三菱重工制冷空调系统株式会社 | The control device of air-conditioning system, air-conditioning system, the control method of the control program of air-conditioning system and air-conditioning system |
| CN107923643A (en) * | 2015-08-18 | 2018-04-17 | 大金工业株式会社 | Air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1108491C (en) | 2003-05-14 |
| JPH10132358A (en) | 1998-05-22 |
| KR100263664B1 (en) | 2000-08-01 |
| EP0840071A2 (en) | 1998-05-06 |
| EP0840071B1 (en) | 2002-12-11 |
| KR19980033401A (en) | 1998-07-25 |
| EP0840071A3 (en) | 1998-09-16 |
| JP3495858B2 (en) | 2004-02-09 |
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