CN102607218B - Expansion valve device - Google Patents
Expansion valve device Download PDFInfo
- Publication number
- CN102607218B CN102607218B CN201210019364.5A CN201210019364A CN102607218B CN 102607218 B CN102607218 B CN 102607218B CN 201210019364 A CN201210019364 A CN 201210019364A CN 102607218 B CN102607218 B CN 102607218B
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- mode
- cold
- producing medium
- valve
- pressure
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- 239000003507 refrigerant Substances 0.000 claims abstract description 48
- 238000005057 refrigeration Methods 0.000 claims description 45
- 239000002826 coolant Substances 0.000 claims description 35
- 238000011144 upstream manufacturing Methods 0.000 claims description 14
- 230000008859 change Effects 0.000 claims description 11
- 230000006837 decompression Effects 0.000 claims description 7
- 238000004378 air conditioning Methods 0.000 description 28
- 230000004308 accommodation Effects 0.000 description 24
- 238000010438 heat treatment Methods 0.000 description 17
- 238000007791 dehumidification Methods 0.000 description 15
- 230000001276 controlling effect Effects 0.000 description 13
- 238000007599 discharging Methods 0.000 description 13
- 238000001816 cooling Methods 0.000 description 6
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical compound C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 description 6
- 239000003638 chemical reducing agent Substances 0.000 description 5
- 230000006870 function Effects 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 3
- 239000003795 chemical substances by application Substances 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000007769 metal material Substances 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- CNQCVBJFEGMYDW-UHFFFAOYSA-N lawrencium atom Chemical compound [Lr] CNQCVBJFEGMYDW-UHFFFAOYSA-N 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000004913 activation Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000001815 facial effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
- F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Control Of Stepping Motors (AREA)
Abstract
Disclosed is an expansion valve device includes an electric driver (55) having a stepping motor so as to control an opening degree of a refrigerant passage (51a) by displacing a valve member (53) in accordance with a rotation angle of the stepping motor. A controller (111, 112, 113) drives the stepping motor in a micro step when a flow rate of refrigerant flowing through the refrigerant passage is equal to or less than a predetermined value, and drives the stepping motor in a full step when the flow rate of the refrigerant is larger than the predetermined value.
Description
Technical field
The present invention relates to a kind of expansion valve device.
Background technology
JP-B2-2898906 has described a kind of for controlling the electric flow control valve (electric expansion valve) of flow of the cold-producing medium of kind of refrigeration cycle.Electric flow control valve has the valve member that uses stepping motor to open or close the valve port of fluid passage.Valve member has major diameter part and small diameter portion.In low discharge interval, by only controlling small diameter portion, control flow.In large flow interval, by controlling major diameter, partly control flow.Therefore, in low discharge interval, control the precision increase of flow.
Yet the structure in this two-stage valve member with major diameter part and small diameter portion is complicated.
Summary of the invention
In view of above-mentioned and other problem, the object of this invention is to provide a kind of expansion valve device with simple valve member, described valve member can improve the precision of controlling the flow in low discharge interval.
According to an example of the present invention, the expansion valve device that is arranged in the cold-producing medium circulating in kind of refrigeration cycle with decompression and expansion in kind of refrigeration cycle comprises housing, valve member, electric drive and controller.Housing limits the coolant channel that refrigerant circulation passes through.Valve member is arranged in housing to change the opening degree of coolant channel.Electric drive has stepping motor, and by movement of valve member, controls the opening degree of coolant channel according to the anglec of rotation of stepping motor.Controller drives and control step motor.While changing in flow that opening degree is flowing through the cold-producing medium of coolant channel is equal to or less than the first flow interval of predetermined value, controller drives stepping motor in micro-stepping mode.While changing in flow that opening degree is flowing through the cold-producing medium of coolant channel is greater than the second flow interval of described predetermined value, controller drives stepping motor in step mode entirely.
Therefore, can improve the precision of controlling the flow in low discharge interval.
Accompanying drawing explanation
Above-mentioned and other objects, features and advantages of the present invention will become clearer from the following detailed description with reference to the accompanying drawings.In the accompanying drawings:
Fig. 1 shows according to the explanatory view of the expansion valve device of an embodiment;
Fig. 2 is the explanatory view that shows the automotive air conditioner with expansion valve device;
Fig. 3 shows the figure line that is supplied to the A phase coil of motor of expansion valve device and the pattern of the electric current of B phase coil;
Fig. 4 shows rotor-position in motor and the figure line of the relation between torque curve;
Fig. 5 is the part enlarged drawing of Fig. 4;
Fig. 6 is the figure line of the relation between the actual rotor stop position and instruction rotor stop position showing in motor;
Fig. 7 A shows the torque curve of motor and the figure line of the relation between load when the battery of automotive air conditioner has 12V voltage;
Fig. 7 B shows the torque curve of motor and the figure line of the relation between load when the battery of automotive air conditioner has 8V voltage;
Fig. 8 A shows the torque curve of motor and the figure line of the relation between load when constant current is applied to motor;
Fig. 8 B is the torque curve of motor and the figure line of the relation between load when constant current is changed by Fig. 8 A according to load; And
Fig. 9 is presented to be applied to the torque curve of motor and the figure line of the comparative example between load in the constant current of motor and the irrelevant indeclinable situation of load.
The specific embodiment
Referring to accompanying drawing explanation embodiments of the invention.In an embodiment, corresponding to the part of the item described in previous embodiment, can give identical Reference numeral, and can omit the unnecessary explanation to this part.When only in one embodiment during description architecture a part of, another can be applied to the other parts of this structure at front embodiment.Can be in conjunction with even without clearly stating parts, but parts can be in conjunction with.Can be in conjunction with even without clearly stating embodiment, but partly combination of embodiment, as long as not infringement in described combination.
According to the expansion valve device of an embodiment, be used to the adjustable throttling 50 shown in Fig. 1.Air conditioning control device 10 control valves 50.Fig. 2 has shown for using the apparatus of air conditioning of the vehicle of valve 50.
As shown in Figure 2, the apparatus of air conditioning has the air-conditioning unit 1 of the passenger accommodation of vehicle being carried out to air conditioning.The actuator of controlling in described unit 1 by the control device 10 such as ECU.Described unit 1 has kind of refrigeration cycle 3, and described kind of refrigeration cycle is formed by conduit 2, cfentrifugal blower, evaporimeter 27 and gas cooler 22 structures.Conduit 2 limits the air after regulating is incorporated into the air duct in passenger accommodation.Air blast produces the air-flow towards passenger accommodation in conduit 2.Evaporimeter 27 cooled flow are by the air of conduit 2.Gas cooler 22 heats by the air of evaporimeter 27 again.
Conduit 2 is arranged in the front side of passenger accommodation.Inner air entrance 11 and extraneous air entrance 12 are limited to the upstream of conduit 2 along air-flow direction, inner air entrance 11 sucks the air (being designated hereinafter simply as inner air) of passenger accommodation inside.Extraneous air entrance 12 sucks the air (being designated hereinafter simply as extraneous air) of passenger accommodation outside.Switching door 4 can be rotatably set in the inner side of entrance 11,12.Described door 4 is driven by the actuator 13 such as servomotor, and externally air is introduced and between pattern (FRS) and inner air circulation pattern (REC), changed air and enter pattern.
A plurality of air outlet slit (not shown) are limited to the downstream of conduit 2 along air-flow direction.Described outlet at least comprises defroster vent (DEF), face outlet (FACE) and foot's outlet (FOOT).Defroster vent mainly blows to hot-air the inner surface of the windshield of vehicle, and face outlet mainly blows to cold air passenger's the upper part of the body such as head or chest.Foot's outlet mainly blows to hot-air passenger's the lower part of the body such as pin.Pattern changes door and is driven by the actuator 14 such as servomotor, therefore among facial model (FACE), double-deck pattern (B/L), foot's pattern (FOOT), foot's frost removal pattern (F/D) and frost removal pattern (DEF), switches Bas Discharged pattern (MODE).
Cfentrifugal blower has the blower motor 16 of centrifugal fan 5 and rotary fan 5.Fan 5 is rotatably contained in spiral case, and described spiral case is integrally formed in the upstream side of conduit 2 along air-flow direction.The terminal voltage of the blower motor 16 of the rotating speed of motor 16 based on applying by air blast drive circuit (not shown) changes, and makes it possible to control the amount that sends to the air in passenger accommodation.
Kind of refrigeration cycle 3 has compressor 21, gas cooler 22, the first pressure reducer, outdoor heat converter 24, inner heat exchanger, the second pressure reducer, evaporimeter 27, holder 28 and is connected circlewise the refrigerant pipe of compressor 21, gas cooler 22, the first pressure reducer, outdoor heat converter 24, inner heat exchanger, the second pressure reducer, evaporimeter 27, holder 28.
Compressor 21 rotates by internal drive motor (not shown).Compressor 21 is electronic coolant compressors, and the cold-producing medium that described electronic coolant compressor compression sucks from evaporimeter 27 to be to have high temperature and to be for example equal to or higher than the high pressure of critical pressure, and by described cold-producing medium discharge.When supply electric power, compressor 21 is opened, and compressor 21 stops when stopping supply of electric power.The rotating speed of controlling compressor 21 by transverter 20, makes compressor 21 have the rotating speed of target calculating by ECU 10.
Gas cooler 22 is arranged in the downstream of evaporimeter 27 in conduit 2 along air-flow direction.Gas cooler 22 be for by with from compressor 21 effluent air cold-producing mediums, carry out the heat exchanger that the air passing through is heated in heat exchange.
Air mixes (A/M) door 6,7 rotatably to be supported by the air entering part of gas cooler 22 and Bas Discharged part.Door 6,7 passes through the amount of air of gas cooler 22 by control and the amount of the air of bypass (walking around) gas cooler 22 is controlled the temperature that is blown into the air in passenger accommodation.Door 6,7 is driven by the actuator 15 such as servomotor.
The first pressure reducer is formed by adjustable throttling 50 structures, and wherein gas refrigerant flow to described adjustable throttling 50 from gas cooler 22.Adjustable throttling 50 is first decompressors that the cold-producing medium flowing out from gas cooler 22 reduced pressure according to valve opening, and can be corresponding to the electric expansion valve for heating (EVH).Valve opening is by ECU 10 electrical controls.In addition, valve 50 can be configured to have full opening mode by ECU10, and the valve opening of choke valve 50 can be fully opened.
Outdoor heat converter 24 in the outer setting of conduit 2 in the position that is easy to receive the wind of advancing when vehicle is advanced, for example, the front portion of the enging cabin of vehicle.Between the extraneous air that flows through the cold-producing medium of heat exchanger 24 inside and sent by electric fan (not shown), carry out heat exchange.Outdoor heat converter 24 conduct under heating mode or dehumidification mode absorbs the heat dump of heat and operates from extraneous air, and conduct operates dissipation of heat to the radiator of extraneous air under refrigerating mode or dehumidification mode.
Inner heat exchanger is the cold-producing medium-refrigerant heat exchanger of the cold-producing medium in the overheated entry port that will be inhaled into compressor 21.Between the low-temperature refrigerant of the high temperature refrigerant flowing out in outlet from outdoor heat converter 24 and outlet outflow from holder 28, carry out heat exchange.Inner heat exchanger has double-deck heat exchange structure, and wherein the surperficial close contact of the surface of low-temperature side heat exchanger 29 and high temperature side heat exchanger 25 is can carry out heat exchange.
The second compressor has adjustable throttling 26 and bypass pipe 33.Cold-producing medium flow into choke valve 26 from the high temperature side heat exchanger 25 of inner heat exchanger.Due to pipe 33, the cold-producing medium flowing out from the high temperature side heat exchanger 25 of inner heat exchanger is transported to holder 28 by bypass throttle valve 26 and evaporimeter 27.
Adjustable throttling 26 is second decompressors that the cold-producing medium of high temperature side heat exchanger 25 outflows from inner heat exchanger reduced pressure according to valve opening.Adjustable throttling 26 is for carrying out cooling electric expansion valve (EVC), and passes through the electrically opening of control valve of ECU 10.Electromagnetism close/open valve 34 (VH) is arranged in pipe 33.When supply electric power, valve 34 is opened, and valve 34 cuts out when stopping supply of electric power.
Evaporimeter 27 is air-refrigerant heat exchanger (heat dumps).The cold-producing medium being reduced pressure by choke valve 26 carries out heat exchange by the air with being sent by fan 5 and is evaporated.The heat of air is absorbed by evaporimeter 27.Evaporimeter 27 is supplied to gas refrigerant by holder 28 low-temperature side heat exchanger 29 and the compressor 21 of inner heat exchanger.Holder 28 is to have the gas-liquid separation device that stores the apotheca of the cold-producing medium flowing out from evaporimeter 27 for interim.
The closed circuit switching part of kind of refrigeration cycle 3 switches the operator scheme of kind of refrigeration cycle 3, that is, the closed circuit for refrigerating mode (cool cycles), for the closed circuit (heat cycles) of heating mode and for closed circuit (dehumidifying circulation) the switching cold-producing medium of dehumidification mode or dehumidifying heating mode the circulation route in kind of refrigeration cycle 3.
In the present embodiment, adjustable throttling 50 and magnetic valve 34 can be corresponding to closed circuit switching parts.
Particularly, when the adjustable throttling 50 for heating has full opening mode, and when the magnetic valve 34 for heating cuts out, the operator scheme of kind of refrigeration cycle 3 is set in cool cycles.
In addition, when valve 50 has that wherein cold-producing medium is depressurized and expands to have the pressure reducing mode of low discharge, and when valve 34 is opened, the operator scheme of kind of refrigeration cycle 3 is set in heat cycles.
In addition, when valve 50 has pressure reducing mode, and when valve 34 cuts out, the operator scheme of kind of refrigeration cycle 3 is set in dehumidifying circulation.
Here, the kind of refrigeration cycle 3 of the present embodiment is used main component by the carbon dioxide (CO with low critical-temperature
2) cold-producing medium made.Kind of refrigeration cycle 3 is supercritical steam compression-type heat pump cycles.The cold-producing medium of discharging from the discharge port of compressor 21 has the high pressure of the critical pressure of being equal to or higher than.
In supercritical steam compression-type heat pump cycle, the refrigerant temperature of the entering part of gas cooler 22 is lifted to about 120 ℃ by increasing on high-tension side refrigerant pressure.Refrigerant temperature represents the temperature that enters of cold-producing medium.That is the temperature of the cold-producing medium of, discharging from the discharge port of compressor 21 is lifted to about 120 ℃.
In addition, though cold-producing medium by dissipation of heat in gas cooler 22, the cold-producing medium flowing in gas cooler 22 can not condense yet, this be because by compressor 21 by pressurizes refrigerant to the pressure with the critical pressure of being equal to or higher than.
ECU 10 comprises known microcomputer, and described microcomputer for example has CPU (CPU), memory (ROM, RAM), I/O port and timer function.When the ignition switch of vehicle is connected (IG-ON), electric power is supplied to ECU 10.ECU 10 is according to each actuator (servomotor 13-15, blower motor 16, adjustable throttling 26,50, magnetic valve 34 and transverter 20) of the control program electric control air-conditioning unit 1 of storing the control signal from the input of air conditioning control panel (not shown), the sensor signal of inputting from various sensors and memory.
Air conditioning control panel has temperature setting switch, air conditioning (A/C) switch, air and enters configuration switch (FRS/REC switch), Bas Discharged configuration switch (MODE switch), frost removal (DEF switch, air capacity switch, (AUTO) switch, closing switch (OFF) etc. automatically.
Air conditioning (A/C) switch be instruction passenger accommodation cooling/dehumidifying cooling/dehumidifying switch.Air conditioning (A/C) switch be refrigerating mode in the operator scheme of instruction kind of refrigeration cycle 3 or dehumidification mode cooling/dehumidifying setting section.The compressor 21 of kind of refrigeration cycle 3 can be forced to start by opening A/C switch, and is forced to stop by closing A/C switch.
DEF switch is that instruction is fixed to Bas Discharged pattern the DEF pattern floatless switch of DEF pattern.DEF switch is the antifog switch of removing or prevent that windshield from hazing.
Further, DEF switch is that the dehumidification mode that instruction is fixed to dehumidification mode by the operator scheme of kind of refrigeration cycle 3 is selected part.Dehumidification mode selection portion sets up separately to be had made to order as dehumidifying mode of priority or blow out the dehumidification mode of in temperature prioritised pattern.
Alternatively, except DEF switch, it can be to detect the antifog sensor hazing of windshield that dehumidification mode is selected part.It can be the dehumidifying switch of the dehumidifying in instruction passenger accommodation only in Bas Discharged pattern not being fixed to DEF pattern in the situation that when switch opens that dehumidification mode is selected part.Dehumidification mode select part can be when switch opens in Bas Discharged pattern not being fixed to DEF pattern in the situation that only instruction prevent the antifog switch that windshield hazes.
AUTO switch is at least according to target, to blow out temperature (TAO) operator scheme of kind of refrigeration cycle 3 is automatically set to the switch in refrigerating mode, heating mode or dehumidification mode.AUTO switch is the automatic control switch that each actuator of air-conditioning unit 1 is controlled in instruction automatically.For example, when MODE changes switch or the operation of air capacity configuration switch, cancel for switching Bas Discharged pattern or controlling for controlling the automatic air adjusting of blower motor.
Discharge pressure sensor 40 detects the discharge pressure (SP) of the cold-producing medium of discharging from the discharge port of compressor 21.Discharge temperature sensor 41 detects the discharge temperature (TD) of the cold-producing medium of discharging from the discharge port of compressor 21.The first refrigerant temperature sensors 42 detects the refrigerant temperature (TCO) of discharging from the exit portion of gas cooler 22.Second refrigerant temperature sensor 43 detects the refrigerant temperature (THO) flowing out from the exit portion of outdoor heat converter 24.
From the sensor signal of sensor 40,41,42 and 43 outputs, at input (A/D conversion) circuit (not shown Fig. 2, with reference to the input processor 102 in Fig. 1), locate to be changed by A/D, and the signal after conversion is input in microcomputer.
Discharge pressure sensor 40 is the high-voltage detector that detect the high pressure of kind of refrigeration cycle 3.Discharge temperature sensor 41 is also the cold-producing medium detector that enters temperature that detects the cold-producing medium in the entering part that flow into gas cooler 22.
The external air temperature (TAM) that external air temperature sensor 44 detects as the air themperature of passenger accommodation outside.Temperature sensor 45 detects the air themperature (TE) in evaporimeter 27 tight downstreams, and can be corresponding to dehumidifying effect detector.The Inside Air Temperature (TR) that Inside Air Temperature sensor 46 detects as the air themperature of passenger accommodation inside.Solar energy sensor 47 detects the solar radiation quantity (TS) that enters into passenger accommodation.Temperature sensor 48 detects the air themperature (TGC) in the tight downstream of gas cooler 22, and can be corresponding to heating efficiency detector.From the sensor signal of sensor 44,45,46,47 and 48 outputs, at A/D change-over circuit, by A/D, changed, and the signal after conversion is imported in microcomputer.
The operation of the apparatus of air conditioning is below described.
For example, when ignition switch starts and when by supply of electric power during to ECU 10, the control signal that ECU10 sends according to each the switch (not shown) from air conditioning control panel, the sensor signal sending from various sensors and be stored in the operator scheme that control program memory is selected kind of refrigeration cycle 3.Therefore, can electric control air-conditioning unit 1 each actuator (servomotor 13-15, blower motor 16, adjustable throttling 26,50, magnetic valve 34 and transverter 20).
For example, when AUTO switch opens regulates while controlling to carry out automatic air, ECU10 receives from the sensor signal of various sensors with from the control signal of air conditioning control panel.Need described signal to control each the air conditioning member (actuator) in air-conditioning unit 1.
Next, the target that is blown into the adjusting air in passenger accommodation according to pre-stored computing formula calculating in memory blows out temperature (TAO).
Next, for example, according to air conditioning (A/C) switch, carry out compressor operation and judge, for determining whether compressor 21 is activated or closes.When the result of judging when compressor operation represents that the target based on previous calculating blows out temperature (TAO) compressor 21 and starts, implement either operational mode is judged, for determining the operator scheme of kind of refrigeration cycle 3.
In operator scheme is judged, comparison object blows out temperature (TAO) and the first setting α (for example, 45 ℃) and the second setting β (for example, 15 ℃).The in the situation that of TAO >=α, select heat cycles (heating mode) as the operator scheme of kind of refrigeration cycle 3.The in the situation that of TAO≤β, select cool cycles (refrigerating mode) as the operator scheme of kind of refrigeration cycle 3.The in the situation that of β < TAO < α, select dehumidifying circulation (dehumidification mode) as the operator scheme of kind of refrigeration cycle 3.
After selecting the operator scheme of kind of refrigeration cycle 3, determine be applied to the terminal voltage of blower motor 16, between inner air pattern and exterior air patterns, change the opening degree that air enters the door 4 of pattern, the pattern that changes Bas Discharged pattern is switched the opening degree of door and the opening degree of A/M door 6,7, and is controlled actuator with blower and door.
Set the operator scheme of kind of refrigeration cycle 3.The opening degree of the mode of operation of compressor 21 (rotating speed etc.), adjustable throttling 50,26 and the opening/closing state of magnetic valve 34 are set and control, and the cycle efficieny of kind of refrigeration cycle 3 is maximized in each operator scheme.
When selecting refrigerating mode as the operator scheme of kind of refrigeration cycle 3, adjustable throttling 50 has full opening mode, and magnetic valve 34 cuts out.The cold-producing medium of discharging from the outlet of compressor 21 cycles through successively gas cooler 22, clear way valve 50, outdoor heat converter 24, h 25, valve 26, evaporimeter 27, holder 28, low-temperature side heat exchanger 29 and compressor 21 as shown in the blank arrow of Fig. 2.
Now, the opening degree of controlling A/M door 6,7 is to have full-shut position (MAX-COOL).The high-temperature high-pressure refrigerant of discharging from compressor 21 can distribute heat in by gas cooler 22.Therefore, in evaporimeter 27, cooled air flows through conduit 2, thereby walks around gas cooler 22.For example, air is blown into passenger accommodation from FACE outlet, makes passenger accommodation be cooled to have predefined temperature.
In inner heat exchanger, from outdoor heat converter 24, flowing through the high-temperature high-pressure refrigerant of h 25 and from holder 28, flowing through heat-shift between the low-temperature low-pressure refrigerant of low-temperature side heat exchanger 29.Therefore the high-temperature high-pressure refrigerant, flowing in evaporimeter 27 is cooled.Therefore, evaporimeter heat content increases, and makes to improve by saving power or electric power the cycle efficieny of kind of refrigeration cycle 3.
When selecting heating mode as the operator scheme of kind of refrigeration cycle 3, adjustable throttling 50 has pressure reducing mode, and magnetic valve 34 is opened.The cold-producing medium of discharging from the outlet of compressor 21 cycles through successively gas cooler 22, valve 50, outdoor heat converter 24, h 25, valve 34, holder 28, low-temperature side heat exchanger 29 and compressor 21 as shown in the black arrow of Fig. 2.Now, valve 26 can cut out completely.
Now, the opening degree of controlling A/M door 6,7 is to have full-gear (MAX-HOT).The high-temperature high-pressure refrigerant of discharging from compressor 21 by gas cooler 22 by dissipation of heat to the air conduit 2.Air is blown into passenger accommodation from FOOT outlet, makes passenger accommodation be heated to have the temperature of presetting.In inner heat exchanger, do not carry out heat exchange, this is because low-temperature low-pressure refrigerant passes through each in heat exchanger 25,29.
When selecting dehumidification mode as the operator scheme of kind of refrigeration cycle 3, adjustable throttling 50 has pressure reducing mode, and magnetic valve 34 cuts out.The cold-producing medium of discharging from the outlet of compressor 21 cycles through successively gas cooler 22, valve 50, outdoor heat converter 24, h 25, valve 26, evaporimeter 27, holder 28, low-temperature side heat exchanger 29 and compressor 21 as shown in the picture hatched arrows of Fig. 2.
Now, air is cooled and dehumidifies in evaporimeter 27, and air heats in gas cooler 22 again.For example, air is blown into passenger accommodation from DEF outlet or FOOT outlet.Passenger accommodation has the mode of the temperature of presetting with passenger accommodation and removes the mist of windshield or prevent the dehumidified and heating of mode that windshield hazes.
The discharge pressure of cold-producing medium and the refrigerant pressure of outdoor heat converter 24 of from compressor 21, discharging can change by the throttling degree of adjustable throttling 50,26.Therefore, throttling degree is controlled, and makes the heating efficiency of gas cooler 22 or the dehumidifying effect of evaporimeter 27 have desired value.The heating efficiency of gas cooler 22 can be represented by the temperature flowing out from gas cooler or flow into the air passenger accommodation.The dehumidifying effect of evaporimeter 27 can be represented by the temperature of the air flowing out from evaporimeter.
Particularly, if throttling degree is controlled such that the discharge pressure of cold-producing medium and the refrigerant pressure step-down of outdoor heat converter 24 of discharging from compressor 21, outdoor heat converter 24, as heat sink operation, increases the heat being distributed by gas cooler 22.Now, for example, the opening degree of valve 50 is set to little, and the opening degree of valve 26 is set to greatly.Therefore the temperature that blows out that, is blown into the adjusting air in passenger accommodation has relatively high temperature.
On the contrary, if throttling degree is controlled such that the discharge pressure of cold-producing medium and the refrigerant pressure of outdoor heat converter 24 of discharging from compressor 21, uprise, outdoor heat converter 24, as radiator operation, reduces the heat being distributed by gas cooler 22.Now, for example, the opening degree of valve 50 is set to greatly, and that the opening degree of valve 26 is set to is little.Therefore the temperature that blows out that, is blown into the adjusting air in passenger accommodation has relatively low temperature.
Next, illustrate for the adjustable throttling 50 that heats and the air conditioning control device 10 of control valve 50.
As shown in Figure 1, adjustable throttling 50 is formed by housing 51, base component 52, valve 53, spring 54, motor 55, plate-shaped member 56, annular element 57 and O shape ring 58 structures.
Housing 51 is for example made by metal material, and has the approximate L shaped coolant channel 51a passing through for refrigerant circulation.In housing 51, the cylindrical base parts 52 of being made by metal material are arranged on the bend office of coolant channel 51a, make a part of the inner space restriction coolant channel 51a of base component 52.Base component 52 has top surface, and the inner rim of top surface limits pedestal 52a.
Valve 53 is for example made by metal material, and is arranged in the coolant channel 51a of housing 51.The critical piece of valve 53 has approximate truncated cone shape, and the neighboring of the rear surface of valve 53 limits base part, and described base part is positioned at the pedestal 52a place of base component 52 or spaced apart with described pedestal 52a.Valve 53 has in Fig. 2 from the upwardly extending axle 53a of major part.Axle 53a is arranged in the throughhole portions of housing 51, and wherein said throughhole portions is extended on the axis direction of axle 53a, and the upper end of axle 53a is oriented to from housing 51 outstanding.
Motor 55 is formed by stepping motor structure, and is arranged in the upside of housing 51.Motor 55 has shell 553, and described shell has by the hemisphere portion of the upper end of cylindrical shape part and closed circle tubular part constructs the approximate domeshape shape forming.Annular stator 551 is arranged into the outer circumferential side of the cylindrical shape part of shell 553, and rotor 552 is arranged in the inner side of cylindrical shape part.
The lower end of the cylindrical shape part of shell 553 has radially outward extending flange portion.O shape ring 58 corresponding to containment member is placed between this flange portion and housing 51.Metal plate-like parts 56 are screwed onto on housing 51, and by being arranged in the annular element 57 of the flange portion top of shell 553, flange portion are pressed on housing 51.Therefore, can between housing 51 and the shell 553 of motor 55, on whole circumference, obtain sealing.
Stator 551 is arranged in the upside of plate-shaped member 56, and has the two phase structure being formed by A phase coil 551A and B phase coil 551B structure.Motor 55 is so-called two-phase stepper motors.
The rotor 552 being arranged in shell 553 is made by magnetic material.Rotor 552 has approximate cylindricality major part 552a and cylindrical magnet 552b.A part of major part 552a is removed with annular recess shape from upper surface and lower surface.Cylindrical magnet 552b is made by permanent magnet, and is arranged on the external peripheral surface of major part 552a.Cylindrical magnet 552b is magnetized with proportional spacing in the direction of rotation of rotor 552.
Recessed portion is limited on the major part 552a of rotor 552, and from the core of lower surface to being recessed on.The upper end of the axle 53a of valve 53 is fixed to the top surface part of recessed portion.
Negative thread is formed on the inner circumferential surface of recessed portion of major part 552a of rotor 552.On the other hand, cylindrical male threaded portion 51b is fixed on housing 51, and projects upwards.Pin thread is formed on the external peripheral surface of male screw portion 51b.The pin thread of the negative thread of the major part 552a of rotor 552 and male screw portion 51b is intermeshing.When rotor 552 rotation, rotor 552 is mobile along axis direction (above-below direction in Fig. 1).
When rotor 552 rotates and moves on axis direction, the valve 53 that is fixed to the major part 552a of rotor 552 also moves, thereby changes the opening degree between valve 53 and pedestal 52a.
By motor 55 and be threadedly engaged to structure that the male screw portion 51b of rotor 552 limits can be corresponding to thering is stepping motor and by control the electric drive of the opening degree of coolant channel according to the anglec of rotation movement of valve member of stepping motor.
As shown in Fig. 1 clearly, the axle 53a of valve 53 has step-like portion.Spring 54 is placed between the top surface of major part 552a of step-like portion and rotor 552.Therefore, if rotor 552 moves down after valve 53 is positioned on pedestal 52a, spring 54 is compressed, thereby restriction excessive load is applied to the base part being limited between valve 53 and pedestal 52a.
In addition,, because be in contact with one another from the outstanding pin parts 51c of housing 51 with from the outstanding pin parts 552c of rotor 552, therefore can restrict rotor 552 there is excessive anglec of rotation displacement.
As shown in Figure 1, ECU 10 has air conditioning controller with function 101, input processor 102 and driver element 103.Input processor 102 is processed from the signal of each switch or sensor input, and the signal of processing is sent to air conditioning controller with function 101.The numerical information that driver element 103 output is determined by controller 101 as the signal of telecommunication to control each actuator (servomotor 13-15, blower motor 16, choke valve 26, magnetic valve 34 or transverter 20).
ECU 10 also has stepper drive control device 111, driver element 113 and input processor 112.Stepper drive control device 111 receives the instruction of the valve opening degree of the valve 50 about being determined by air conditioning controller with function 101, and according to described instruction, is identified for the current value of motor 50.Particularly, for example by stepper drive control device 111, set the step number of the driving direction (direction of rotation) of motor 55 of valve 50 and the driving of the motor 55 of valve 50.
Driver element 113 is controlled A phase coil 551A and the B phase coil 551B of excitation stator 551 by PWM according to the activation bit by the definite valve 50 of stepper drive control device 111.The current value of A phase coil 551A and B phase coil 551B is imported in input processor 112, and input processor 112 is carried out FEEDBACK CONTROL with respect to stepper drive control device 111.
Stepper drive control device 111, input processor 112 and driver element 113 can limit and drive the also controller of control step motor.
When selecting refrigerating mode as the operator scheme of kind of refrigeration cycle 3, air conditioning control device 101 outputs to stepper drive control device 111 by valve open order.Valve open order order adjustable throttling 50 is fully opened.
When selecting heating mode or dehumidification mode (dehumidifying heating mode) as the operator scheme of kind of refrigeration cycle 3, air conditioning control device 101 is exported to stepper drive control device 111 by valve open order.50 decompression the swell refrigeration agent of valve open order order adjustable throttling, make the operating efficiency air conditioning of carry out desired better of kind of refrigeration cycle 3.
When stepper drive control device 111 is during from air conditioning control device 101 receiving valve open order, stepper drive control device 111 calculates the drive condition for the position (valve opening degree) of the pressure reducing mode control valve 53 in adjustable throttling 50 decompressions swell refrigeration agent.Further, stepper drive control device 111 calculates for carrying out the drive condition of the patterns of change between pressure reducing mode and full opening mode.
When the position of stepper drive control device 111 control valve 53 in pressure reducing mode, (, when valve 53 moves in the low discharge interval of execution decompression and expansion), stepper drive control device 111 calculates the condition for drive motor 55 in micro-stepping mode.That is, calculate the direction of rotation (driving direction) of rotor 552 and the quantity of micro-stepping, for valve 53 being moved to the valve aperture position of indication.The quantitaes of micro-stepping is for the quantity of the micro-stepping pulse of stepping motor 50.
When the maximum stream flow of stepper drive control device 111 in pressure reducing mode and full opening mode is when between the time, execution pattern changes, stepper drive control device 111 calculates the condition for drive motor 55 in step mode entirely.That is, calculate the direction of rotation of rotor 552 and the quantity of full step (quantity of full pace pulse), for valve 53 being moved to the valve aperture position of instruction.
In the present embodiment, the refrigerant flow interval of adjustable throttling 50 decompressions and swell refrigeration agent can be interval corresponding to first flow.In the present embodiment, flow be greater than the refrigerant flow interval of the flow in first flow interval can be interval corresponding to the second flow.When selecting full opening mode, valve 53 makes the opening degree of coolant channel 51a have maximum open, makes refrigerant flow have maximum in the second flow interval.
When entirely walking mode drive motor 55, the gear teeth of rotor 552 (for example, the magnetic pole of cylindrical magnet 552b) be actuated to from primary importance single step move to the second place.Primary importance is the position relative with first gear teeth (such as by the magnetized magnetic pole of each phase coil) of stator 551.The second place is the position relative with second gear teeth adjacent with the first gear teeth stator 551 stator 551.
When with micro-stepping mode drive motor 55, the gear teeth of rotor 552 is driven, thereby from primary importance, moves to the second place in multistep mode.That is,, in micro-stepping, the driving angle of the single step during full step drives is divided into multistep, and motor 55 is driven gradually by multistep.Therefore, the gear teeth of rotor 552 can be stopped to the place, centre position between primary importance and the second place.
Stepper drive control device 111 is exported to driver element 113 by current instruction value, makes motor 55 driven by constant current corresponding to the number of pulses of the driving direction calculating and calculating.Driver element 113 according to current instruction value by supply of electric power to A phase coil 551A and B phase coil 551B.
As shown in Figure 1, refrigerant pressure sensor 40A in high-pressure side is arranged to for detection of the pressure in the coolant channel 51a of valve 53 upstreams.Sensor 40A detects in kind of refrigeration cycle by the pressure of the cold-producing medium before choke valve 50 decompressions.In the explanation of kind of refrigeration cycle that utilizes Fig. 2, omitted sensor 40A.
Stepper drive control device 111 changes the value of the constant current of drive motor 55 according to the refrigerant pressure being detected by sensor 40A.Particularly, when the refrigerant pressure detecting uprises, the value of constant current increases.
Sensor 40A is not limited to the upstream that is directly placed on choke valve 50 in refrigerant pipe.For example, sensor 40A can be arranged in housing 51 with the upstream face at valve 53 coolant channel 51.High side pressure detector can be corresponding to the combination of sensor 40A or sensor 40A and discharge pressure sensor 40.
Although omitted detailed description, can there is the structure identical with choke valve 50 for heating for cooling choke valve 26.Therefore, for cooling adjustable throttling 26 with can be formed shared for the adjustable throttling 50 heating.
According to the present embodiment, stepper drive control device 111 is according to optionally switching pressure reducing mode and full opening mode from the valve open order of A/C control device 101 outputs.When needing 50 pairs of cold-producing mediums that circulate in coolant channel 51a of choke valve to reduce pressure, select pressure reducing mode, make cold-producing medium in low discharge interval, be depressurized and expand.When not needing 50 pairs of cold-producing mediums that circulate in coolant channel 51a of choke valve reduce pressure and expand, select full opening mode, make valve 53 be positioned at maximum open position to there is maximum refrigerant flow amount.
In pressure reducing mode, valve 53 is by drive the motor 55 corresponding to stepping motor to move in micro-stepping mode, and cold-producing medium is carried out to flow-control.
When execution pattern between pressure reducing mode and full opening mode changes, valve 53 is by moving entirely to walk mode drive motor 55.
Therefore, when pressure reducing mode, can improve for controlling the precision of refrigerant flow.Further, can execution pattern variation fast between pressure reducing mode and full opening mode.
In addition,, when stepper drive control device 111 passes through driver element 113 drive motor 55, stepper drive control device 111 calculates driving direction and number of pulses, and motor 55 is driven by constant current according to driving pulse.Therefore, can stably drive the motor 55 being formed by stepping motor structure.
When execution pattern between pressure reducing mode and full opening mode changes, be similar to pressure reducing mode, motor 55 is driven by constant current.At least, when changing valve opening in low discharge interval in pressure reducing mode, it is desirable to by using constant current with micro-stepping mode drive motor 55.Therefore, even change when the voltage from power supply supply, because constant current also can be with micro-stepping mode drive motor 55 stably.
With reference to Fig. 3-7B, the reason of above-mentioned advantage is below described.Fig. 3 has shown the figure line of inputting when motor the electric current input of A phase coil and electric current of B phase coil when having that 16 separately the micro-stepping modes of step are driven has been shown.Fig. 4 has shown the figure line that expression torque curve of the relation between rotor angle (position of rotation) and moment of torsion when using the current pattern of Fig. 3 is shown.Fig. 5 has shown the amplifier section of the torque curve of Fig. 4.
As shown in Figure 3, the angle of the single step in driving with respect to full step, is supplied to the electric current of A phase coil to increase gradually in 16 independent steps, and is supplied to the electric current of B phase coil to reduce gradually in 16 independent steps.Between phase, attract the power of rotor 552 to change gradually a step by a step.Rotor 552 can stop at the some place when attraction is balanced, makes to be divided into by the angle during step is entirely driven 16 steps and carries out micro-stepping and drive.
Yet, as shown in Figure 4, torque curve trend towards the larger mountain-shaped part of the absolute value of moment of torsion divide or paddy shape part in change.Further because the gradient of torque curve diminishes, so mountain-shaped part divide with paddy shape part in variable quantity also diminish.
Therefore, as shown in Figure 5, compare with low loading condition, because mountain-shaped part divides or paddy shape partly meets high load condition, so the resolution ratio of rotor stop position reduces under the higher high load condition of the load of motor 55.High load condition and low loading condition just show the example of high-low relation, and it doesn't matter with the load level of choke valve 50.
Fig. 6 has shown when increasing the driving load with the level shown in Fig. 5 reality (truly) stop position with respect to the instruction stop position rotor of rotor.Compare with the situation of low load, the in the situation that of high capacity, actual stop position and ideal value are different greatly, and this is because used the mountain-shaped part of torque curve to divide.
Replacing constant current by apply voltage drive motor 55 in the situation that, if voltage drop, motor torque also declines.Therefore, under high load condition, resolution ratio is further reduced.The apparatus of air conditioning of the present embodiment is for vehicle.If be arranged on battery electric quantity on vehicle, reduce, in resolution ratio by apply voltage and carry out drive motor in the situation that, significantly reduce.
For example, Fig. 7 A has shown that battery wherein has the situation of 12V voltage, and Fig. 7 B has shown battery wherein, has the situation of 8V voltage.In Fig. 7 A, load level is divided (peak portion) away from the mountain-shaped part of torque curve.Yet, if the voltage drop of battery to 8V, as shown in Figure 7 B, the load level mountain-shaped part that approaches torque curve that becomes divides, and makes extremely variation of resolution ratio.
According to the present embodiment, motor 55 is driven by constant current.Therefore, the moment of torsion being produced by the motor approximately constant that becomes, and with the independent from voltage of power supply.For example, even if the voltage of battery drops to 8V from 12V, also can keep the state shown in Fig. 7 A.
Be different from Fig. 4-6, for the ease of understanding, Fig. 7 A and 7B have shown when motor is to have the micro-stepping of four steps schematic torque curve when driven.Identical details is applied to Fig. 8 A-9 illustrating for subsequently.
According to the present embodiment, when the refrigerant pressure being detected by high-pressure side refrigerant pressure sensor 40A becomes large, stepper drive control device 111 increases constant current.If the refrigerant pressure of valve 53 upstream sides increases in coolant channel 51a, the poor increase of refrigerant pressure between valve 53 upstream sides and downstream in coolant channel 51a, makes to drive the level of load to improve.
Therefore, when using constant current with micro-stepping mode drive motor 55, if current value increases according to the increase of the refrigerant pressure of valve 53 upstreams in coolant channel 51a, the moment of torsion being produced by stepping motor can increase corresponding to the driving load increasing.Therefore, even if drive load to become large, also can be with micro-stepping mode drive motor 55 stably.
In other words, by estimating load level according to the refrigerant pressure value of valve 53 upstreams, and by changing constant current value according to the load level of estimation, it is higher that resolution ratio can keep.
Fig. 9 has shown the comparative example with respect to the present embodiment, and in described comparative example, load level is increased to B level from A level.If constant current value does not change, moment of torsion can not change from maximum X.In this case, the ratio of load level and peak torque X reduces greatly.That is, it is large that the difference between the value of A/X and the value of B/X becomes, and resolution ratio is reduced greatly.
On the contrary, according to the present embodiment, the current value of constant current driven increases according to the increase of the refrigerant pressure of valve 53 upstreams in coolant channel 51a.Therefore,, as shown in Fig. 8 A and 8B, if load level is increased to the B level of Fig. 8 B from the A level of Fig. 8 A, the value of constant current increases, so moment of torsion can " X1 " from Fig. 8 A be increased to " X2 " in Fig. 8 B.Therefore, can limit the reducing of ratio of load level and peak torque.That is, the difference between A/X1 and B/X2 can be less, thereby can greatly reduce by resolution limiting, although can produce slightly, reduces.
The present invention is not limited to above-described embodiment.
The quantity of micro-stepping is not limited to 16, but can be set arbitrarily.
Replace the increase of the refrigerant pressure of valve 53 upstreams in coolant channel 51a, stepper drive control device 111 can increase according to the increase of the pressure differential between the upstream side of valve 53 and downstream the current value of constant current driven.Alternatively, can control constant current value according to the sensor information sending from three or more sensors.
Except two-phase stepper motor, motor 55 can be heterogeneous stepping motor.For example, motor 55 can be five phase stepping motors.
Motor 55 is not limited to by constant current driven.If predetermined resolution can guarantee, motor 55 can be driven by applying voltage.
In the present embodiment, when execution pattern between pressure reducing mode and full opening mode changes, motor 55 is driven in micro-stepping mode in first flow interval under pressure reducing mode, and driven entirely to walk mode in the second flow interval.
In other words, controller can optionally switch pressure reducing mode and full opening mode.In the time need to reducing pressure to the cold-producing medium circulating in coolant channel 51a, cold-producing medium is depressurized and expands under pressure reducing mode in first flow interval.When not needing cold-producing medium to reduce pressure, valve 53 makes the opening degree of coolant channel 51a have maximum open, makes cold-producing medium in the second flow interval, have maximum stream flow under full opening mode.
When valve opening changes in first flow interval, motor 55 is driven in micro-stepping mode.When switching operation modes between pressure reducing mode and full opening mode, motor 55 is driven entirely to walk mode.That is,, in the second flow interval, only at maximum stream flow place, carry out flow-control.
Yet the present invention is not limited to above-mentioned control.For example, can in whole the second flow interval, carry out flow-control.That is,, when the flow of the cold-producing medium that controller circulates in coolant channel 51a is equal to or less than in the first flow interval of predetermined value control valve opening, motor 55 can be driven in micro-stepping mode.Further, when the flow of the cold-producing medium that controller circulates in coolant channel 51a higher than the second flow interval of predetermined value in during control valve opening, motor 55 can be driven entirely to walk mode.
Except supercritical steam compressing hot pump circulation, kind of refrigeration cycle 3 can be that wherein high side pressure is equal to or less than the vapor compression heat pump circulation of critical pressure.
Except the kind of refrigeration cycle for automotive air conditioner, the present invention can be applied to fixed kind of refrigeration cycle.
This variation and modification will be understood to be in the protection domain being defined by the claims of the present invention.
Claims (2)
1. be arranged in the expansion valve device in kind of refrigeration cycle, described expansion valve device decompression and the cold-producing medium that expands and circulate in described kind of refrigeration cycle, described expansion valve device comprises:
Housing (51), described housing limits the coolant channel (51a) that described refrigerant circulation passes through;
Valve member (53), described valve member is arranged in described housing to change the opening degree of described coolant channel;
(55,51b), described electric drive has stepping motor to control the opening degree of described coolant channel by mobile described valve member according to the anglec of rotation of described stepping motor to electric drive; With
Controller (111,112,113), described controller drives and controls described stepping motor, wherein:
While changing in flow that described opening degree is flowing through the cold-producing medium of described coolant channel is equal to or less than the first flow interval of predetermined value, described controller drives described stepping motor in micro-stepping mode;
While changing in flow that described opening degree is flowing through the cold-producing medium of described coolant channel is greater than the second flow interval of described predetermined value, described controller drives described stepping motor in step mode entirely;
When described opening degree changes in described first flow interval, described controller drives described stepping motor by supply constant current in micro-stepping mode; And,
Described controller increases described constant current according to the increase of the pressure differential between the pressure of the cold-producing medium in the pressure of the cold-producing medium of described valve member upstream and described valve member downstream, or described controller increases described constant current according to the increase of the pressure of the cold-producing medium of described valve member upstream.
2. expansion valve device according to claim 1, wherein:
Described controller optionally switches the operator scheme of described kind of refrigeration cycle between pressure reducing mode and full opening mode;
In described pressure reducing mode, in the time need to reducing pressure to the cold-producing medium by described coolant channel, described cold-producing medium is depressurized and expands in described first flow interval;
In described full opening mode, when not needing the cold-producing medium by described coolant channel to reduce pressure, described valve member makes the opening degree of described coolant channel change to maximum, and the flow that makes to flow through the cold-producing medium of described coolant channel becomes maximum in described the second flow interval; And
When described controller is switched to another by one in described pressure reducing mode and described full opening mode, described controller drives described stepping motor in step mode entirely.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011012077A JP5601217B2 (en) | 2011-01-24 | 2011-01-24 | Expansion valve device |
| JP2011-012077 | 2011-01-24 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102607218A CN102607218A (en) | 2012-07-25 |
| CN102607218B true CN102607218B (en) | 2014-07-30 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210019364.5A Expired - Fee Related CN102607218B (en) | 2011-01-24 | 2012-01-20 | Expansion valve device |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20120187202A1 (en) |
| JP (1) | JP5601217B2 (en) |
| CN (1) | CN102607218B (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2012237498A (en) * | 2011-05-11 | 2012-12-06 | Denso Corp | Expansion valve device |
| JP5445548B2 (en) | 2011-09-24 | 2014-03-19 | 株式会社デンソー | Expansion valve device |
| CN102645065B (en) * | 2012-05-17 | 2014-02-26 | 青岛海信日立空调系统有限公司 | Drive control device and method of electronic expansion valve |
| JP6557921B2 (en) * | 2015-04-27 | 2019-08-14 | 株式会社テージーケー | Electric valve device and electric valve control device |
| JP6478958B2 (en) * | 2016-09-02 | 2019-03-06 | 株式会社不二工機 | Control valve |
| CN106382405B (en) * | 2016-09-07 | 2018-11-30 | 珠海格力电器股份有限公司 | A kind of drive system of electric expansion valve, driving method and air conditioner |
| JP2019128110A (en) * | 2018-01-25 | 2019-08-01 | 株式会社デンソー | Motor control device, integrated valve device, and heat exchanger |
| JP7073925B2 (en) * | 2018-06-07 | 2022-05-24 | 株式会社デンソー | Valve device |
| JP6651586B1 (en) * | 2018-08-31 | 2020-02-19 | サーパス工業株式会社 | Flow control device and control method of flow control device |
| KR102170493B1 (en) * | 2018-11-15 | 2020-10-29 | 우리산업 주식회사 | Electronic expansion valve |
| CN112944007B (en) | 2019-12-11 | 2023-09-01 | 浙江三花智能控制股份有限公司 | Control method, control system and electric valve |
| JP2023012951A (en) * | 2021-07-14 | 2023-01-26 | 株式会社不二工機 | Motor-operated valve |
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Also Published As
| Publication number | Publication date |
|---|---|
| JP2012154371A (en) | 2012-08-16 |
| CN102607218A (en) | 2012-07-25 |
| US20120187202A1 (en) | 2012-07-26 |
| JP5601217B2 (en) | 2014-10-08 |
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