WO2011040552A1 - 液体流量制御バルブ - Google Patents
液体流量制御バルブ Download PDFInfo
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- WO2011040552A1 WO2011040552A1 PCT/JP2010/067124 JP2010067124W WO2011040552A1 WO 2011040552 A1 WO2011040552 A1 WO 2011040552A1 JP 2010067124 W JP2010067124 W JP 2010067124W WO 2011040552 A1 WO2011040552 A1 WO 2011040552A1
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- distributor
- rotor
- control valve
- sleeve
- opening
- Prior art date
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
- B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N7/00—Starting apparatus having fluid-driven auxiliary engines or apparatus
- F02N7/08—Starting apparatus having fluid-driven auxiliary engines or apparatus the engines being of rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/22—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution
- F16K3/24—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members
- F16K3/26—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member
- F16K3/262—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with sealing faces shaped as surfaces of solids of revolution with cylindrical valve members with fluid passages in the valve member with a transverse bore in the valve member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/34—Arrangements for modifying the way in which the rate of flow varies during the actuation of the valve
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
- F16K5/04—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary with plugs having cylindrical surfaces; Packings therefor
- F16K5/0414—Plug channel at 90 degrees to the inlet
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/08—Prime-movers comprising combustion engines and mechanical or fluid energy storing means
- B60K6/12—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator
- B60K2006/126—Prime-movers comprising combustion engines and mechanical or fluid energy storing means by means of a chargeable fluidic accumulator the hydraulic accumulator starts the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0406—Valve members; Fluid interconnections therefor for rotary valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
- F15B13/0444—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with rotary electric motor
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- 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
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/2931—Diverse fluid containing pressure systems
- Y10T137/3115—Gas pressure storage over or displacement of liquid
- Y10T137/3127—With gas maintenance or application
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86509—Sequentially progressive opening or closing of plural ports
- Y10T137/86517—With subsequent closing of first port
- Y10T137/86533—Rotary
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/86702—With internal flow passage
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/8671—With annular passage [e.g., spool]
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86718—Dividing into parallel flow paths with recombining
- Y10T137/86734—With metering feature
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86718—Dividing into parallel flow paths with recombining
- Y10T137/86743—Rotary
- Y10T137/86751—Plug
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- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/87917—Flow path with serial valves and/or closures
- Y10T137/88022—One valve head provides seat for other head
Definitions
- a cylindrical distributor and a cylindrical rotor are coaxially arranged on an axis inside a cylindrical sleeve fixed to a valve housing, and the distributor is predetermined with respect to the sleeve by a first driving source.
- the area of the overlapping portion where the first opening formed in the sleeve and the second opening formed in the distributor overlap is changed, and the sleeve and the distributor with respect to the second drive source are changed.
- the present invention relates to a liquid flow rate control valve that generates a pressure.
- a liquid flow rate control valve for PWM control of the liquid flow rate is known from Patent Document 1 below.
- This liquid flow rate control valve has a cylindrical shape having left and right edges formed in a wave shape inside an outer cylinder 10 having one input port 11 and two first and second output ports 12 and 13.
- the valve plate 40 is rotatably arranged by a drive source, and the control plate 50 has a plurality of first and second opening groups 41 and 42 between the outer peripheral surface of the valve plate 40 and the inner peripheral surface of the outer cylinder 10.
- the liquid supplied from the input port 11 of the outer cylinder 10 is used to move the first and second opening groups 41 and 42 of the control plate 50 and the wavy left and right of the valve plate 40.
- the distributor and the rotor are coaxially arranged inside the cylindrical sleeve, and the distributor is rotated by the first drive source and the rotor is rotated by the second drive source, so that a large axial thrust force is obtained. It is conceivable to perform PWM control of the flow rate of the liquid without generating any. In such a case, if the first drive source is disposed at one axial end of the flow control valve and the second drive source is disposed at the other axial end of the flow control valve, the axial dimension of the flow control valve increases. There's a problem.
- the present invention has been made in view of the above circumstances, and is intended to reduce the size in the axial direction of a liquid flow rate control valve capable of PWM control of a liquid flow rate at an arbitrary duty ratio and an arbitrary duty frequency. Objective.
- a cylindrical distributor and a cylindrical rotor are coaxially arranged on the axis inside a cylindrical sleeve fixed to the valve housing, and the first drive source
- the distributor By rotating the distributor relative to the sleeve by a predetermined angle, the area of the overlapping portion where the first opening formed in the sleeve and the second opening formed in the distributor overlap is changed and the second driving is performed.
- the first opening and the second opening are opened when the third opening formed in the rotor passes through the overlapping portion.
- a liquid flow rate control valve for generating fluid pressure with a predetermined duty ratio by communicating with the distributor and the front
- One end in the axial direction of the rotor arranged radially inside is connected coaxially to one of the first and second drive sources and arranged radially outside of the distributor and the rotor.
- a liquid flow rate control valve is proposed in which one end in the axial direction is connected to the other of the first and second drive sources via a gear train.
- the first and second outlet openings 37a and 37b of the embodiment correspond to the first opening of the present invention
- the first and second communication hole groups 38c and 38d of the embodiment correspond to the second opening of the present invention
- the first and second first inlet openings 42c and 42d of the embodiment correspond to the third opening of the present invention
- the first electric motor 46 of the embodiment corresponds to the first drive source of the present invention
- the second electric motor 47 of the embodiment corresponds to the second drive source of the present invention.
- the distributor when the distributor is rotated by a predetermined angle relative to the sleeve by the first driving source, the total area of the overlapping portion between the first opening of the sleeve and the second opening of the distributor changes. Therefore, when the rotor is rotated by the second drive source, the duty waveform is turned on when the third opening of the rotor passes through the overlapping portion, and the duty waveform is turned on when the third opening of the rotor does not pass through the overlapping portion. By turning OFF, the liquid flow rate can be PWM-controlled.
- the duty ratio can be arbitrarily controlled by adjusting the rotational position of the distributor with the first drive source, and the duty frequency can be arbitrarily controlled by adjusting the rotational speed of the rotor with the second drive source. be able to.
- the distributor and the rotor can be easily supported, and the cost and weight can be reduced.
- One end of the distributor and the rotor arranged on the radially inner side is coaxially connected to one of the first and second drive sources, and one end of the one arranged on the radially outer side is connected to one end of the axial direction.
- the first and second driving sources are concentrated on one end side in the axial direction of the liquid flow rate control valve to reduce the size of the liquid source.
- the viewer and the rotor can be individually driven to rotate.
- FIG. 1 is a diagram showing a driving force transmission system of a hydraulic hybrid vehicle to which a flow control valve of the present invention is applied.
- FIG. 2 is a longitudinal sectional view of the flow control valve.
- First embodiment 3 is a cross-sectional view taken along line 3-3 of FIG.
- First embodiment 4 is a cross-sectional view taken along line 4-4 of FIG.
- First embodiment 5 is a cross-sectional view taken along line 5-5 of FIG.
- First embodiment 6 is a cross-sectional view taken along line 6-6 of FIG.
- FIG. 7 is a view taken along line 7-7 in FIG.
- FIG. 8 is an exploded perspective view of the sleeve, distributor, and rotor.
- FIG. 9 is a diagram showing an equivalent circuit of a pump / motor drive circuit.
- FIG. 10 is a diagram showing a pump / motor drive circuit.
- Valve housing 37 Sleeve 37a First outlet opening (first opening) 37b Second outlet opening (first opening) 38 Distributor 38c 1st communication hole group (2nd opening) 38d Second communication hole group (second opening) 42 rotor 42c first inlet opening (third opening) 42d Second inlet opening (third opening) 46 1st electric motor (1st drive source) 47 Second electric motor (first drive source) 68 Driven Gear (Gear Train) 70 Drive gear (gear train) 73 Idle Gear (Gear Train) L axis
- the hydraulic hybrid vehicle includes a pump / motor M, an engine E, and a transmission T connected in series.
- a first shaft 12 and a first clutch 13 are provided on a connecting shaft 11 that connects a pump / motor M and an engine E configured by a gear motor
- a first shaft 12 is provided on an output shaft 14 that connects a transmission T and driving wheels W.
- a two-clutch 15 and a second gear 16 are provided.
- the bypass shaft 17 that bypasses the engine E and the transmission T is provided with a third clutch 18, a third gear 19 that meshes with the first gear 12, and a fourth gear 20 that meshes with the second gear 16. .
- a pump / motor M, a tank 21, an accumulator 22, and a flow control valve 23 are connected via a switching control valve 24, and the pump / motor M operates as a motor with the hydraulic pressure accumulated in the accumulator 22.
- the state of operating as a pump that accumulates accumulator 22 by being driven from the outside is switched.
- a radiator 25 for cooling the liquid is provided between the tank 21 and the switching control valve 24.
- the radiator 25 may be provided between the accumulator 22 and the switching control valve 24.
- the pump / motor M is operated as a motor with the hydraulic pressure accumulated in the accumulator 22, and the engine E is operated.
- the engine E can be started, the pump motor M can be operated as a pump by driving the engine E, and the accumulator 22 can be accumulated.
- the pump / motor M If the regenerative braking of the pump / motor M is performed in this state, the pump / motor M is operated as a pump by the driving force reversely transmitted from the driving wheel W side, and the accumulator 22 is accumulated to thereby convert the kinetic energy of the vehicle into the hydraulic energy. Can be recovered.
- the driving force of the engine E is transmitted to the drive wheels W via the second clutch 15 and the output shaft 14, and the vehicle Can be started or run by the driving force of the engine E.
- the pump / motor M can be operated as a motor to assist the driving force of the engine E with the driving force of the pump / motor M.
- accumulator 22 can be accumulated.
- the flow control valve 23 controls the flow rate of the liquid supplied from the accumulator 22 to the pump motor M when the pump motor M operates as a motor, and the pump motor when the pump motor M operates as a pump.
- the flow rate of the liquid supplied from M to the accumulator 22 is controlled.
- the flow control valve 23 includes a valve housing 36 including a main body housing 61 and an end housing 64 coupled to the main body housing 61 with bolts 63.
- a large-diameter hole 61a having a circular cross section and a small-diameter hole 61b having a circular cross section are coaxially formed on the axis L of the main body housing 61, and an arc-shaped input liquid chamber 61c is formed so as to surround a part of the small diameter hole 61b.
- an arc-shaped output liquid chamber 61d is formed so as to surround a part of the large-diameter hole 61a.
- An input port 61e communicating with the input liquid chamber 61c is opened at one end surface of the main body housing 61, and an output port 61f communicating with the output liquid chamber 61d is opened at the outer peripheral surface of the main body housing 61.
- the cylindrical sleeve 37 fitted into the large-diameter hole 61a of the main body housing 61 and prevented from rotating by the pin 65 has first and second outlet openings 37a each having a central angle of 90 ° about the axis L. 37b is formed to face the output liquid chamber 61d.
- the first and second outlet openings 37a and 37b are rectangular in a state where the sleeve 37 is developed, and the phases thereof are shifted from each other by 180 ° and are disposed at positions overlapping in the direction of the axis L.
- a first and second communication hole group 38c and 38d that can overlap the first and second outlet openings 37a and 37b of the sleeve 37 are provided on the distributor 38 that is fitted to the inner periphery of the sleeve 37 so as to be relatively rotatable. It is formed.
- the first and second communication hole groups 38c and 38d are composed of a large number of circular communication holes 38e arranged in a staggered manner, each having a central angle of 90 ° centered on the axis L and a phase. Are arranged at positions that are 180 ° apart from each other and overlap in the direction of the axis L.
- the outlines of the first and second communication hole groups 38c and 38d have the same shape as the first and second outlet openings 37a and 37b, and can exactly overlap the first and second outlet openings 37a and 37b.
- the rotor 42 includes a cylindrical portion 42a and a shaft portion 42b.
- the cylindrical portion 42a whose opening end is closed by the plug 43 is fitted to the inner periphery of the distributor 38 so as to be relatively rotatable, and the shaft portion 42b is a partition plate. 62 extends through the end housing 64.
- the tip of the cylindrical portion 42 a of the rotor 42 is rotatably supported on the inner periphery of the small diameter hole 61 b of the main body housing 61 via a bearing metal 66.
- the cylindrical portion 42a of the rotor 42 is formed with a pair of first inlet openings 42c, 42c capable of communicating with the first and second communication hole groups 38c, 38d of the distributor 38 with a phase difference of 180 °.
- a pair of second inlet openings 42d and 42d whose phases are shifted by 90 ° with respect to the pair of first inlet openings 42c and 42c are formed with a phase difference of 180 °.
- a total of four first and second inlet openings 42c, 42c; 42d, 42d aligned in the axis L direction are formed in a slit shape, and the width in the axis L direction is the first, second outlet openings 37a, 37b and the widths of the first and second communication hole groups 38c and 38d in the direction of the axis L.
- the inner space 42e of the rotor 42 communicating with the first and second inlet openings 42c, 42c; 42d, 42d communicates with the input liquid chamber 61c of the main body housing 61 via the liquid holes 42f.
- the number of teeth of the drive gear 70 is smaller than the number of teeth of the driven gear 68. Therefore, the rotation of the first electric motor 46 is decelerated and transmitted to the distributor 38, and the distributor 38 is rotated within an angle range of 90 °.
- the rotating shaft 47a of the second electric motor 47 fixed to the end housing 64 with bolts 74 is coaxially coupled to the shaft portion 42a of the rotor 42 via the joint 75. Therefore, the rotor 42 can be rotated at an arbitrary speed by the second electric motor 47.
- the right end of the distributor 38 in the drawing communicates with the atmosphere via a pressure balance passage 76 that penetrates the main body housing 61 and the sleeve 37, and the pressure at the left end of the distributor 38, which is atmospheric pressure, By balancing, it is possible to prevent the eccentric load in the axis L direction from being applied to the distributor 38.
- the right end of the rotor 42 in the drawing communicates with the atmosphere via a pressure balancing passage 77 penetrating the main body housing 61, and balances with the pressure at the left end of the rotor 42 in the drawing, which is atmospheric pressure. 42 is prevented from being subjected to an offset load in the direction of the axis L.
- FIG. 7 (A) to 7 (C) are developed views taken along line 7-7 in FIG. 4, and a sleeve 37 fixed to the valve housing 36 and a first electric motor 46 with respect to the sleeve 37 at 0 ° to
- the distributor 38 that rotates relative to the range of 90 ° and the rotor 42 that rotates relative to the sleeve 37 and the distributor 38 at a variable speed by the second electric motor 47 are developed in the circumferential direction over 360 °. Indicates the state.
- FIG. 7A corresponds to a state where the duty ratio is 100%, and the first and second outlet openings 37a and 37b of the sleeve 37 are 0 ° to 90 ° of the central angle 360 ° of the sleeve 37.
- the first and second communication hole groups 38c and 38d of the distributor 38 have first and second outlet openings 37a and 37b in the entire region. Therefore, the substantial opening ranges of the first and second outlet openings 37a and 37b of the sleeve 37 are 0 ° to 90 ° and 180 ° to 270 °.
- FIG. 7A shows a state where the two first inlet openings 42c and 42c overlap the substantial opening range, and the two second inlet openings 42d and 42d do not overlap the substantial opening range.
- the input port 61e of the main body housing 61 is connected to the accumulator 22, and the output port 61f of the main body housing 61 is connected to the tank 21. Therefore, the high-pressure liquid in the accumulator 22 is supplied to the internal space 42 e of the rotor 42 through the path of the input port 61 e of the main body housing 61 ⁇ the input liquid chamber 61 c of the main body housing 61 ⁇ the liquid hole 42 f of the rotor 42.
- the first and second inlet openings 42c and 42c; 42d and 42d facing the inner space 42e of the rotor 42 are the first and second communication hole groups 38c and 38d of the distributor 38 and the first and second outlets of the sleeve 37.
- the liquid in the inner space 42e of the distributor 38 passes through the first and second inlet openings 42c and 42c of the rotor 42; 42d and 42d ⁇ the first and second communication of the distributor 38.
- the hole group 38c, 38d, the first and second outlet openings 37a, 37b of the sleeve 37, the output liquid chamber 61d of the main body housing 61, and the output port 61f of the main body housing 61 are returned to the tank 21, and the pump motor M Operates as a motor.
- the range of 0 ° to 90 ° and the range of 180 ° to 270 ° of the sleeve 37 becomes two substantial opening ranges, and the two first inlet openings 42c and 42c of the rotor 42
- the generated duty waveform is turned on in the range of 0 ° to 90 ° and in the range of 180 ° to 270 ° of the 360 ° rotation angle of the rotor 42.
- the phase of the two second inlet openings 42d, 42d of the rotor 42 is shifted by 90 ° with respect to the phase of the two first inlet openings 42c, 42c.
- the duty waveforms generated by 42d and 42d are turned ON in the range of 90 ° to 180 ° and the range of 270 ° to 360 ° of the 360 ° rotation angle of the rotor 42.
- FIG. 7B is a diagram corresponding to the state where the duty ratio is 50%, and the range of 0 ° to 45 ° and the range of 180 ° to 225 ° of the sleeve 42 are two substantial opening ranges, and thus the rotor
- the duty waveform generated by the two first communication holes 42c, 42c of 42 is ON in the range of 0 ° to 45 ° and the range of 180 ° to 225 ° of the 360 ° rotation angle of the rotor 42.
- the phase of the two second inlet openings 42d, 42d of the rotor 42 is shifted by 90 ° with respect to the phase of the two first inlet openings 42c, 42c.
- the duty waveforms generated by 42d and 42d are turned ON in the range of 90 ° to 135 ° and the range of 270 ° to 315 ° of the 360 ° rotation angle of the rotor 42.
- the rotor 42 is in a state where the first and second communication hole groups 38c and 38d and the first and second outlet openings 37a and 37b do not overlap at all, that is, there is no substantial opening range. Regardless of the phase of the first and second inlet openings 42c and 42c; 42d and 42d, the first and second communication hole groups 38c and 38d and the first and second outlet openings 37a and 37b communicate with each other.
- the duty ratio becomes 0%.
- the flow rate control valve 23 outputs a duty waveform four times for each rotation of the rotor 42. Therefore, if the rotation speed of the rotor 42 by the second electric motor 47 is N, the frequency of the duty waveform output by the flow control valve 23 is 4N, and a high duty frequency can be obtained while keeping the rotation speed of the second electric motor 47 low. Can do.
- the first and second communication hole groups 38c and 38d of the distributor 38 are arranged at the same position in the direction of the axis L and are arranged symmetrically at intervals of 180 °. Even if a load is applied to the distributor 38 from the liquid passing through the hole groups 38c and 38d, the load does not bend and deform the distributor 38 and does not tilt the distributor 38. Therefore, the occurrence of galling between the distributor 38, the sleeve 37 and the rotor 42 is prevented, and the driving force of the first and second electric motors 46 and 47 can be minimized.
- the flow rate of the liquid supplied from the accumulator 22 to the pump motor M is duty-controlled by the flow rate control valve 23, compared to the case where the flow rate of the liquid is controlled by the throttle valve, High efficiency can be obtained by reducing heat loss due to pressure loss. At that time, higher efficiency can be obtained by adjusting the rotation speed of the rotor 42 and selecting an optimum duty frequency.
- the hydraulic pressures in the input liquid chamber 61c and the output liquid chamber 61d do not cause the distributor 38 and the rotor 42 to generate a thrust load in the direction of the axis L, so that it is not necessary to support the distributor 38 and the rotor 42 so as to withstand the thrust load.
- the structure can be simplified and the weight and cost can be reduced. *
- FIG. 9 shows an equivalent circuit of the hydraulic pressure control circuit
- the switching control valve 24 includes four ports Pa, Pb, Pc, Pd, a shut-off valve 24a, and a switching valve 24b.
- the port Pa is connected to the accumulator 22, the port Pb is connected to the tank 21, the port Pc is connected to the pump motor M, and the port Pd is connected to the downstream side of the check valve 48.
- the shutoff valve 24a is disposed between the port Pa and the port Pd, and the port Pc is selectively connected to the port Pa, Pd or the port Pb via the switching valve 24b.
- the upstream side of the check valve 48 is connected to the pump / motor M and is connected to the port Pb and the tank 21 via the flow rate control valve 23.
- FIG. 10 is a hydraulic circuit that embodies the switching control valve 24 of the equivalent circuit of FIG. 9.
- the switching control valve 24 is slidably fitted to a valve housing 49, and drives the spool 50. And two return springs 53 and 54 for urging the spool 50 to the neutral position.
- the duty period during which the flow control valve 23 is open is in a load state in which the pump motor M generates driving force, and the flow rate During the duty OFF period in which the control valve 23 is closed, the pump motor M is in an unloaded state where no driving force is generated.
- both the solenoid 51 and the solenoid 52 are demagnetized, so that the spool 50 is in a neutral position.
- the shut-off valve 24a is closed and the switching valve 24b is switched to the drive / neutral side.
- a closed unload circuit of pump / motor M ⁇ check valve 48 ⁇ port Pd ⁇ switching valve 24b ⁇ port Pc ⁇ pump motor M is configured, and the pump motor M rotates with no load.
- the duty ratio of the flow control valve 23 is 100%, the liquid that has passed through the pump motor M can pass through the flow control valve 23 with no load, so the liquid in the tank 21 is port Pb ⁇ switching valve 24b ⁇ port Pc ⁇ pump. Circulate through the unload circuit closed by the route of motor M ⁇ flow rate control valve 23 ⁇ port Pb. At this time, since the liquid flowing through the unload circuit is the low-pressure liquid in the tank 21 (low-pressure unload), the leakage of the liquid can be prevented and the operating resistance of the pump / motor M and the flow control valve 23 can be reduced.
- the pump motor M When the duty ratio of the flow control valve 23 is larger than 0% and smaller than 100%, the pump motor M is in a load state in which the hydraulic pressure is generated during the duty OFF period when the flow control valve 23 is closed. During the duty ON period when the control valve 23 is open, the pump motor M is in an unload state in which no hydraulic pressure is generated.
- the pump / motor M since the pump / motor M is used as a drive source for the hydraulic hybrid vehicle, when the pump / motor M operates as a motor (during driving), it also operates as a pump (during regenerative braking). Although the rotation direction is the same, the switching control valve 24 reverses the connection relationship between the tank 21 and the accumulator 22, so that a mechanism for reversing the rotation direction of the pump motor M is not required. Driving and regenerative braking can be performed without any trouble.
- the pump / motor M can be driven, regenerated, or neutrally switched by a single switching control valve 24. When the pump / motor M is driven, a high-pressure unload circuit is automatically configured to provide a pump / motor. During regenerative braking of M, the low pressure unload circuit can be automatically configured.
- the flow rate control valve 23 of each embodiment can normally exhibit the function of PWM control of the liquid flow rate at an arbitrary duty ratio and an arbitrary duty frequency even when the direction of the liquid flow is reversed. it can. That is, in each embodiment, liquid flows in from the input port 61e side and liquid flows out from the output port 61f side. However, liquid flows in from the output port 61f side and liquid flows from the input port 61e side. The function of the port may be exchanged so that it flows out. Therefore, in the embodiment, the input port and the inlet opening include those having a function of flowing out the liquid, and the output port and the outlet opening include those having a function of flowing in the liquid.
- the flow control valve 23 of the present invention is applied to a hydraulic hybrid vehicle, but the use of the flow control valve 23 of the present invention is arbitrary.
- the following can be considered as uses for automobiles and the like. (1) Applying a flow control valve to the variable flow oil pump (2) Applying a flow control valve to the variable flow water pump (3) Applying a flow control valve to the engine injector (4) Applying a flow control valve to the refrigerant pump of an air conditioner (5) Applying a flow control valve to the engine throttle valve (6) Applying the flow rate control valve to the turbo boost pressure control
- the first and second electric motors 46 and 47 can be replaced with any drive source other than the electric motor.
- the sleeve 37, the distributor 38, and the rotor 42 are sequentially arranged from the radially outer side to the inner side of the flow control valve 23.
- the positional relationship between the distributor 38 and the rotor 42 is changed, and the flow control valve is changed.
- the sleeve 37, the rotor 42, and the distributor 38 may be sequentially arranged from the radially outer side to the inner side.
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- Chemical & Material Sciences (AREA)
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- Transportation (AREA)
- Multiple-Way Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
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Abstract
Description
37 スリーブ
37a 第1出口開口(第1開口)
37b 第2出口開口(第1開口)
38 デストリビュータ
38c 第1連通孔群(第2開口)
38d 第2連通孔群(第2開口)
42 ロータ
42c 第1入口開口(第3開口)
42d 第2入口開口(第3開口)
46 第1電動モータ(第1駆動源)
47 第2電動モータ(第1駆動源)
68 ドリブンギヤ(ギヤトレイン)
70 ドライブギヤ(ギヤトレイン)
73 アイドルギヤ(ギヤトレイン)
L 軸線
(1) 可変流量オイルポンプに流量制御バルブを適用すること
(2) 可変流量ウォータポンプに流量制御バルブを適用すること
(3) エンジンのインジェクタに流量制御バルブを適用すること
(4) エアコンの冷媒ポンプに流量制御バルブを適用すること
(5) エンジンのスロットルバルブに流量制御バルブを適用すること
(6) ターボ過給圧制御に流量制御バルブを適用すること
また第1、第2電動モータ46,47は、電動モータ以外の任意の駆動源に置き換えることが可能である。
Claims (1)
- バルブハウジング(36)に固定した円筒状のスリーブ(37)の内部に円筒状のデストリビュータ(38)および円筒状のロータ(42)を軸線(L)上に同軸に配置し、
第1駆動源(46)で前記スリーブ(37)に対して前記デストリビュータ(38)を所定角度だけ相対回転させることで、前記スリーブ(37)に形成した第1開口(37a,37b)および前記デストリビュータ(38)に形成した第2開口(38c,38d)が重なる重なり部分の面積を変化させるとともに、
第2駆動源(47)で前記スリーブ(37)および前記デストリビュータ(38)に対して前記ロータ(42)を所定速度で相対回転させることで、前記ロータ(42)に形成した第3開口(42c,42d)が前記重なり部分を通過するときに前記第1開口(37a,37b)および前記第2開口(38c,38d)を連通させて所定のデューティ比の液圧を発生させる液体流量制御バルブであって、
前記デストリビュータ(38)および前記ロータ(42)のうちの径方向内側に配置されたものの軸線(L)方向の一端を、前記第1、第2駆動源(46,47)の一方に同軸に接続するとともに、前記デストリビュータ(38)および前記ロータ(42)のうちの径方向外側に配置されたものの軸線(L)方向の一端を、前記第1、第2駆動源(46,47)の他方にギヤトレイン(68,70,73)を介して接続したことを特徴とする液体流量制御バルブ。
Priority Applications (2)
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US13/498,399 US8820354B2 (en) | 2009-10-01 | 2010-09-30 | Liquid flow rate control valve |
JP2011504669A JP5497737B2 (ja) | 2009-10-01 | 2010-09-30 | 液体流量制御バルブ |
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JP2009-229630 | 2009-10-01 | ||
JP2009229630 | 2009-10-01 |
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WO2011040552A1 true WO2011040552A1 (ja) | 2011-04-07 |
Family
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PCT/JP2010/067123 WO2011040551A1 (ja) | 2009-10-01 | 2010-09-30 | 液体流量制御バルブ |
PCT/JP2010/067125 WO2011040553A1 (ja) | 2009-10-01 | 2010-09-30 | 液圧回路 |
PCT/JP2010/067124 WO2011040552A1 (ja) | 2009-10-01 | 2010-09-30 | 液体流量制御バルブ |
PCT/JP2010/067122 WO2011040550A1 (ja) | 2009-10-01 | 2010-09-30 | 液体流量制御バルブ |
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PCT/JP2010/067123 WO2011040551A1 (ja) | 2009-10-01 | 2010-09-30 | 液体流量制御バルブ |
PCT/JP2010/067125 WO2011040553A1 (ja) | 2009-10-01 | 2010-09-30 | 液圧回路 |
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PCT/JP2010/067122 WO2011040550A1 (ja) | 2009-10-01 | 2010-09-30 | 液体流量制御バルブ |
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US (3) | US8820354B2 (ja) |
JP (5) | JP5502688B2 (ja) |
DE (1) | DE112010003898T5 (ja) |
WO (4) | WO2011040551A1 (ja) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA2873538A1 (en) * | 2012-03-05 | 2013-09-12 | Lightning Hybrids, Inc. | Hydraulic regeneration apparatus |
JP5940844B2 (ja) * | 2012-03-14 | 2016-06-29 | 本田技研工業株式会社 | 油圧ハイブリッド車両 |
JP5825682B2 (ja) * | 2012-07-03 | 2015-12-02 | キャタピラー エス エー アール エル | アキュムレータを備えた作業機械の油圧回路 |
DE102012106906A1 (de) * | 2012-07-30 | 2014-01-30 | Linde Hydraulics Gmbh & Co. Kg | Hydrostatische Verdrängermaschine |
JP6091345B2 (ja) * | 2013-06-10 | 2017-03-08 | ダイハツ工業株式会社 | 車両 |
JP2015129625A (ja) * | 2013-12-02 | 2015-07-16 | 三星電子株式会社Samsung Electronics Co.,Ltd. | 冷却装置 |
FR3021593B1 (fr) * | 2014-06-03 | 2018-02-02 | Peugeot Citroen Automobiles Sa | Module motopropulseur hybride comprenant trois accouplements debrayables et procede de pilotage du module |
US9435446B1 (en) * | 2014-07-24 | 2016-09-06 | Google Inc. | Rotary valve with brake mode |
EP3088782B1 (de) * | 2015-04-29 | 2019-09-18 | HAWE Hydraulik SE | Hydraulisches steuerventil in schieberbauweise und mobilhydraulik mit entsprechendem steuerventil |
US9902251B2 (en) * | 2016-01-26 | 2018-02-27 | Deere & Company | Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith |
GB2550595B (en) * | 2016-05-24 | 2021-08-25 | Changan Uk R&D Centre Ltd | A fluid control assembly |
JP6447606B2 (ja) * | 2016-10-05 | 2019-01-09 | マツダ株式会社 | 車両用駆動装置 |
JP6372537B2 (ja) * | 2016-10-05 | 2018-08-15 | マツダ株式会社 | 車両用駆動装置 |
DE102016226039B3 (de) * | 2016-12-22 | 2018-02-08 | Danfoss Power Solutions Gmbh & Co. Ohg | Verdrängungssteueranordnung für eine axialkolbenpumpe |
KR101884769B1 (ko) * | 2017-03-02 | 2018-08-02 | 서울대학교산학협력단 | 핀틀 인젝터 |
KR101902818B1 (ko) | 2017-07-27 | 2018-10-01 | 한국항공대학교산학협력단 | 젤 연료용 회전 핀틀 인젝터 |
CN117328835A (zh) | 2018-11-09 | 2024-01-02 | 芙罗服务管理公司 | 用于在至少两个流体流之间交换压力的设备及其操作方法 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5467800A (en) * | 1993-04-20 | 1995-11-21 | Atlas Fluid Controls Inc. | Low inertia servo valve |
JP2001027340A (ja) * | 1999-05-13 | 2001-01-30 | Amada Eng Center Co Ltd | 制御バルブ |
WO2003016761A1 (fr) * | 2001-08-15 | 2003-02-27 | Amada Company, Limited | Distributeur |
JP2009068553A (ja) * | 2007-09-11 | 2009-04-02 | Hitachi Constr Mach Co Ltd | 液圧開閉弁 |
Family Cites Families (49)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2349641A (en) | 1941-12-18 | 1944-05-23 | Hydraulic Dev Corp Inc | Rotating servo-valve |
US2395979A (en) | 1941-12-18 | 1946-03-05 | Hydraulic Dev Corp Inc | Torque amplifier |
US2593316A (en) * | 1946-12-23 | 1952-04-15 | Dole Valve Co | Reciprocating pump assembly |
US3018622A (en) | 1958-07-11 | 1962-01-30 | Bendix Corp | Control apparatus |
US3069025A (en) | 1959-07-01 | 1962-12-18 | Berkley Machine Co | Rotary valve for controlling application of suction |
DE1426491B2 (de) | 1962-08-01 | 1971-12-02 | Fujitsu Ltd , Communications and Electronics, Tokio | Druckmittelbetriebener drehmomentverstaerker |
US3213881A (en) * | 1963-07-17 | 1965-10-26 | Int Harvester Co | Directional control valve |
DE2555752C2 (de) | 1975-12-11 | 1977-12-01 | Gestra-Ksb-Vertriebsgesellschaft Mbh & Co Kg, 2800 Bremen | Drosselventil |
US4037620A (en) | 1976-04-23 | 1977-07-26 | Eaton Corporation | Controller for fluid pressure operated devices |
US4387783A (en) * | 1980-09-04 | 1983-06-14 | Advanced Energy Systems Inc. | Fuel-efficient energy storage automotive drive system |
GB2104249B (en) * | 1981-08-19 | 1985-05-15 | Moog Inc | Servovalves |
JPS5875023U (ja) | 1982-06-08 | 1983-05-20 | ヤンマー農機株式会社 | 農作業車の駆動装置 |
US4793133A (en) | 1983-10-28 | 1988-12-27 | Colt Industries Inc | Manual backup for electronic fuel control |
FR2567984B1 (fr) | 1984-07-20 | 1986-08-14 | Centre Techn Ind Mecanique | Distributeur hydraulique proportionnel |
SE449718B (sv) | 1985-09-27 | 1987-05-18 | Volvo Flygmotor Ab | Forfarande och anordning for reglering av ett regenerativt hydrostatiskt drivsystem, serskilt for fordon |
US4697929A (en) * | 1986-10-28 | 1987-10-06 | Charles Ross & Son Company | Planetary mixers |
US4779512A (en) | 1987-04-13 | 1988-10-25 | Leonard Willie B | Rotary drive spool valve |
US4800924A (en) | 1987-04-24 | 1989-01-31 | Davidson Textron Inc. | Direct drive servovalve with rotary valve |
IT214557Z2 (it) | 1988-05-10 | 1990-05-09 | Fiat Auto Spa | Servovalvola rotativa a comando elettromagnetico |
DE3912743C2 (de) | 1989-04-19 | 2000-12-14 | Bw Hydraulik Gmbh | Hydraulische Steuereinrichtung |
JPH04238739A (ja) | 1991-01-09 | 1992-08-26 | Kenji Mimura | 自動車の加速装置 |
JPH0629963U (ja) | 1992-09-25 | 1994-04-19 | 日産ディーゼル工業株式会社 | 蓄圧式ハイブリッド自動車 |
US5242150A (en) | 1992-09-30 | 1993-09-07 | The United States Of America As Represented By The Secretary Of The Navy | Rotary hydraulic servo or throttle valve |
NO177874C (no) | 1993-07-14 | 1996-10-30 | Sinvent As | Anordning for blanding av komponentene i en fluidströmning, og anvendelse av anordningen i et måleapparat for masseström |
CA2107693A1 (en) * | 1993-10-05 | 1995-04-06 | Philip Sylvester Esmond Farrell | Pneumatic pressure regulation system |
JP3642808B2 (ja) | 1994-10-03 | 2005-04-27 | セイレイ工業株式会社 | クローラトラクタの防振構造 |
JPH08296607A (ja) | 1995-04-25 | 1996-11-12 | Smc Corp | 流体圧アクチュエータの駆動回路 |
US5950664A (en) | 1997-02-18 | 1999-09-14 | Amot Controls Corp | Valve with improved combination bearing support and seal |
US5954093A (en) | 1998-09-08 | 1999-09-21 | Leonard; Marcus B. | Rotary servo valve |
JP4361159B2 (ja) | 1999-03-24 | 2009-11-11 | 石川島運搬機械株式会社 | 立体駐車装置の油圧制御装置 |
DE69923005T2 (de) | 1999-04-14 | 2005-12-29 | Amada Co., Ltd., Isehara | Drehbares servoventil und eine, das drehbare servoventil verwendende, hydraulische-stanzpresse servovorrichtung |
US6826988B2 (en) * | 2000-09-29 | 2004-12-07 | Sd3, Llc | Miter saw with improved safety system |
US20020079003A1 (en) | 2000-10-04 | 2002-06-27 | Scampini Daniel Charles | Straight through flow cage-type valve |
DE10110764A1 (de) | 2001-03-07 | 2002-09-19 | Dambach Lagersysteme Gmbh & Co | Hydraulische Hubvorrichtung |
JP4694717B2 (ja) | 2001-05-23 | 2011-06-08 | ヤンマー株式会社 | クローラ式作業機 |
US6769451B2 (en) | 2002-04-17 | 2004-08-03 | Eaton Corporation | Power beyond steering unit with bypass |
US6739127B2 (en) * | 2002-06-07 | 2004-05-25 | Caterpillar Inc | Hydraulic system pump charging and recirculation apparatus |
US7322375B2 (en) | 2004-04-30 | 2008-01-29 | Vanderbilt University | High bandwidth rotary servo valves |
JP4337677B2 (ja) | 2004-07-26 | 2009-09-30 | 株式会社豊田中央研究所 | エンジン始動装置 |
US20060108860A1 (en) * | 2004-11-23 | 2006-05-25 | Delaware Capital Formation | Brake energy recovery system |
JP4285424B2 (ja) | 2005-03-09 | 2009-06-24 | 株式会社豊田中央研究所 | エンジン始動装置 |
JP4638362B2 (ja) * | 2006-02-21 | 2011-02-23 | 株式会社豊田中央研究所 | エンジン始動装置 |
US7574859B2 (en) * | 2006-03-10 | 2009-08-18 | Grigoriy Epshteyn | Monocylindrical hybrid two-cycle engine, compressor and pump, and method of operation |
JP4874059B2 (ja) * | 2006-11-08 | 2012-02-08 | 中国電力株式会社 | 圧力操作システム |
US7775040B2 (en) | 2006-11-08 | 2010-08-17 | Caterpillar Inc | Bidirectional hydraulic transformer |
JP2008247320A (ja) | 2007-03-30 | 2008-10-16 | Mazda Motor Corp | 気体燃料タンクとバッテリの車両搭載構造 |
JP2009126398A (ja) | 2007-11-26 | 2009-06-11 | Toyota Motor Corp | 燃料電池自動車の車体下部構造 |
JP2009255611A (ja) | 2008-04-11 | 2009-11-05 | Iem:Kk | 車両の省エネ装置及び方法 |
US8646558B2 (en) * | 2009-10-31 | 2014-02-11 | Grigoriy Epshteyn | Ultra-efficient hydraulic hybrid drivetrain and method of operation |
-
2010
- 2010-09-30 JP JP2010221177A patent/JP5502688B2/ja not_active Expired - Fee Related
- 2010-09-30 WO PCT/JP2010/067123 patent/WO2011040551A1/ja active Application Filing
- 2010-09-30 WO PCT/JP2010/067125 patent/WO2011040553A1/ja active Application Filing
- 2010-09-30 JP JP2011504668A patent/JP5513484B2/ja not_active Expired - Fee Related
- 2010-09-30 JP JP2011534323A patent/JP5554781B2/ja not_active Expired - Fee Related
- 2010-09-30 US US13/498,399 patent/US8820354B2/en not_active Expired - Fee Related
- 2010-09-30 US US13/498,434 patent/US9150091B2/en not_active Expired - Fee Related
- 2010-09-30 DE DE112010003898T patent/DE112010003898T5/de not_active Withdrawn
- 2010-09-30 JP JP2011504667A patent/JP5497736B2/ja not_active Expired - Fee Related
- 2010-09-30 US US13/497,094 patent/US8931514B2/en not_active Expired - Fee Related
- 2010-09-30 JP JP2011504669A patent/JP5497737B2/ja not_active Expired - Fee Related
- 2010-09-30 WO PCT/JP2010/067124 patent/WO2011040552A1/ja active Application Filing
- 2010-09-30 WO PCT/JP2010/067122 patent/WO2011040550A1/ja active Application Filing
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5467800A (en) * | 1993-04-20 | 1995-11-21 | Atlas Fluid Controls Inc. | Low inertia servo valve |
JP2001027340A (ja) * | 1999-05-13 | 2001-01-30 | Amada Eng Center Co Ltd | 制御バルブ |
WO2003016761A1 (fr) * | 2001-08-15 | 2003-02-27 | Amada Company, Limited | Distributeur |
JP2009068553A (ja) * | 2007-09-11 | 2009-04-02 | Hitachi Constr Mach Co Ltd | 液圧開閉弁 |
Also Published As
Publication number | Publication date |
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DE112010003898T5 (de) | 2012-11-15 |
WO2011040550A1 (ja) | 2011-04-07 |
JPWO2011040553A1 (ja) | 2013-02-28 |
JPWO2011040552A1 (ja) | 2013-02-28 |
JP2011093519A (ja) | 2011-05-12 |
US8931514B2 (en) | 2015-01-13 |
JP5554781B2 (ja) | 2014-07-23 |
US20120234400A1 (en) | 2012-09-20 |
JP5497737B2 (ja) | 2014-05-21 |
WO2011040551A1 (ja) | 2011-04-07 |
JP5502688B2 (ja) | 2014-05-28 |
WO2011040553A1 (ja) | 2011-04-07 |
US20120234417A1 (en) | 2012-09-20 |
JP5497736B2 (ja) | 2014-05-21 |
JPWO2011040550A1 (ja) | 2013-02-28 |
JPWO2011040551A1 (ja) | 2013-02-28 |
US8820354B2 (en) | 2014-09-02 |
US9150091B2 (en) | 2015-10-06 |
JP5513484B2 (ja) | 2014-06-04 |
US20120237362A1 (en) | 2012-09-20 |
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