WO2012046335A1 - 巻掛け伝動装置の油圧制御装置 - Google Patents
巻掛け伝動装置の油圧制御装置 Download PDFInfo
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- WO2012046335A1 WO2012046335A1 PCT/JP2010/067717 JP2010067717W WO2012046335A1 WO 2012046335 A1 WO2012046335 A1 WO 2012046335A1 JP 2010067717 W JP2010067717 W JP 2010067717W WO 2012046335 A1 WO2012046335 A1 WO 2012046335A1
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- hydraulic
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- control valve
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- hydraulic pressure
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 88
- 238000004804 winding Methods 0.000 title claims abstract description 42
- 230000000903 blocking effect Effects 0.000 claims description 3
- 230000007423 decrease Effects 0.000 description 7
- 238000013459 approach Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 230000020169 heat generation Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66254—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
- F16H61/66259—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling using electrical or electronical sensing or control means
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
- F16H2061/1244—Keeping the current state
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures
- F16H2061/1256—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected
- F16H2061/126—Detecting malfunction or potential malfunction, e.g. fail safe; Circumventing or fixing failures characterised by the parts or units where malfunctioning was assumed or detected the failing part is the controller
- F16H2061/1268—Electric parts of the controller, e.g. a defect solenoid, wiring or microprocessor
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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
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
- F16H61/66272—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing
Definitions
- the present invention relates to a winding transmission that performs a speed change by changing a groove radius of a rotating member such as a driving pulley or a driven pulley around which a transmitting member such as a belt or a chain is wound and changing a winding radius of the transmitting member. More particularly, the present invention relates to an apparatus for controlling the hydraulic pressure supplied to the rotating members.
- This type of transmission can set a gear ratio according to the wrapping radius of a belt or chain.
- a belt-type continuously variable transmission has a belt winding around a driving pulley and a driven pulley.
- the gear ratio which is the ratio of the rotational speeds of these pulleys, is changed by changing the multiplying radius.
- each pulley has a so-called V-groove, and the belt winding radius, that is, the gear ratio is changed by changing the groove width by hydraulic pressure. Has been.
- Examples of hydraulic control devices in belt type continuously variable transmissions are described in European Patent No. 0985855 and International Publication No. 2010/021218.
- a driving pulley (hereinafter referred to as a primary pulley) in a belt-type continuously variable transmission described in the specification of European Patent No. 0985855 and International Publication No. 2010/021218 is fixed to a pulley shaft.
- the driven pulley (hereinafter referred to as “secondary pulley”) is composed of a fixed sheave attached to the pulley shaft and a movable sheave that moves back and forth in the axial direction on the pulley shaft, similarly to the primary pulley.
- a belt clamping force is generated by each sheave by the hydraulic pressure of the hydraulic chamber provided on the back side of the movable sheave, and a necessary transmission torque capacity is set.
- the hydraulic source is constituted by a hydraulic pump and an accumulator, and a supply-side control valve is provided in a so-called supply oil passage that communicates the hydraulic source and the hydraulic chamber of each pulley. Is provided with a discharge side control valve in communication therewith.
- each solenoid valve switches to a valve open state in which the input side port and the output side port communicate with each other by energizing the solenoid.
- each control valve opens the valve body away from the valve seat by energizing the solenoid, and interrupts the energization to the solenoid.
- the valve body is configured by a so-called poppet type electromagnetic valve that is closed by being pushed by a spring and in close contact with the valve seat.
- the gear ratio is set to the maximum gear ratio on the lowest vehicle speed side or a gear ratio close thereto.
- an electronic device for the continuously variable transmission is used. If the control device or the electrical system including it is abnormal, or if the vehicle is driven by towing the vehicle in a state where the control valve cannot be energized by turning off the main switch of the vehicle, etc.
- the continuously variable transmission is driven in a state where a large gear ratio, which is the ratio, is set. In this case, even if the output speed of the continuously variable transmission is low due to the low vehicle speed, the input speed becomes high due to the large gear ratio. If the forward / reverse switching mechanism is connected to the input side of the step transmission, the rotational speed of any of the rotating members constituting the forward / reverse switching mechanism may increase.
- the present invention has been made paying attention to the above technical problem, and when the winding transmission is driven in a state where the control valve cannot be controlled, the transmission ratio is reduced by driving the winding transmission. It is an object of the present invention to provide a hydraulic control device that can be used.
- the present invention provides a groove in which an annular transmission member is wound around a pair of rotating members, and the transmission member is wound around when the rotating members are supplied with hydraulic pressure.
- Each of the hydraulic chambers is connected to a hydraulic source via a supply control valve that is electrically controlled, and each of the hydraulic chambers is electrically connected.
- the hydraulic chamber is configured to be shut off from the hydraulic power source and the drain location, and includes a communication path that allows the hydraulic chambers to communicate with each other. That.
- the supply control valve is constituted by a normally open type valve that opens an oil passage when the current cannot be supplied, and each of the exhaust pressure control valves cannot be supplied with current.
- a first oil passage that supplies hydraulic pressure from the hydraulic power source to one of the rotating members via one of the supply control valves; and Hydraulic pressure is supplied from the hydraulic pressure source to the predetermined position on the hydraulic pressure source side from the one supply control valve of the first oil passage and to the other rotating member via the other supply control valve.
- a hydraulic control device for a winding transmission device including a second oil passage.
- This invention is the hydraulic control device for a winding transmission device according to the above invention, further comprising a hydraulic pressure limiting means for limiting the hydraulic pressure supplied from the hydraulic pressure source to the communication path.
- the hydraulic pressure limiting means includes a shut-off valve that cuts off the communication between the hydraulic power source and the communication passage when the supply control valve and the exhaust pressure control valve cannot be energized.
- This is a hydraulic control device for a winding power transmission.
- the hydraulic pressure limiting means reduces the relief pressure when the hydraulic pressure source is connected between the hydraulic pressure source and the communication path and the supply control valve and the exhaust pressure control valve cannot be energized.
- a hydraulic control device for a winding transmission device including a relief valve that is provided.
- the input-side rotating member to which torque is input from the driving force source among the pair of rotating members reverses the direction of the torque input to the input-side rotating member.
- a hydraulic control device for a winding transmission device wherein the hydraulic control device is connected to a forward / reverse switching mechanism.
- the transmission member includes a belt
- the pair of rotating members includes a driving pulley capable of changing a width of a groove around which the belt is wound, and the belt is wound.
- a hydraulic control device for a winding transmission device including a driven pulley capable of changing a width of a groove to be hung.
- the supply control valve and the exhaust pressure control valve cannot be energized
- the supply control valve is opened and the exhaust pressure control valve is closed.
- the hydraulic chambers of the rotating members or pulleys are communicated with each other through the communication passages, and the drains are blocked, so that a closed system is formed by the respective hydraulic chambers and the communication passages communicating these.
- the hydraulic pressure is confined in the closed system.
- the drive side The rotational speed of the rotating member or pulley becomes relatively high with respect to the rotational speed of the driven-side rotating member or pulley, and the internal pressure of the hydraulic chamber in the driving-side rotating member or pulley increases. Therefore, the driving side rotating member or pulley has a greater force to pinch the transmission member or belt, and the driven side rotating member or pulley has a larger force to pinch the transmission member or belt.
- the communication path can be constituted by the first oil passage and the second oil passage provided with the supply control valve, and accordingly, the supply control valve and the exhaust pressure control valve
- the winding transmission device since the influence of the hydraulic pressure of the hydraulic power source on the pressure in each hydraulic chamber can be suppressed or cut off, the winding transmission device can be used in a state where the hydraulic pressure of the hydraulic chamber in each pulley cannot be electrically controlled. It is possible to avoid or suppress an increase in hydraulic pressure during operation, and as a result, it is possible to prevent or suppress heat generation or wear in the winding transmission.
- the rotational speed of the input side that is, the rotational speed of the forward / reverse switching mechanism can be reduced.
- FIG. 1 is a partial hydraulic circuit diagram illustrating an example of a hydraulic control device according to the present invention. It is a partial hydraulic circuit diagram which shows the other example of the hydraulic control apparatus which concerns on this invention.
- FIG. 6 is a partial hydraulic circuit diagram showing still another example of the hydraulic control device according to the present invention. It is a schematic diagram which shows an example of the power transmission path
- the present invention transmits power between a pair of rotating members such as pulleys via a winding transmission member such as a belt, and changes the gear ratio of the winding transmission member with respect to the rotating member to change the gear ratio.
- a hydraulic control apparatus for a transmission configured to do this. Therefore, the transmission member in the present invention includes an annular transmission member such as a chain in addition to the belt as described above, and the rotating member is wound with a pulley, a sprocket, and the like, and the wrapping radius of the transmission member is changed to change the speed. It includes a rotating member capable of changing the ratio.
- FIG. 4 shows an example in which the internal combustion engine (engine) 1 is mounted on a vehicle having a driving force source.
- the driving force source in the present invention may be a motor or a combination of an internal combustion engine and a motor. It may be of a hybrid type.
- a torque converter 3 having a lockup clutch 2 is connected to the output side of the engine 1.
- the torque converter 3 has the same configuration as that conventionally known, and a turbine runner 6 is disposed opposite to a pump impeller 5 integrated with a front cover 4 connected to the engine 1. Is an output element.
- stator 7 that supplies oil discharged from the pump impeller 5 to the turbine runner 6 while changing the flow direction with a small speed ratio. ing.
- the stator 7 is connected to a predetermined fixed portion via a one-way clutch (not shown).
- the lockup clutch 2 is configured to rotate integrally with the turbine runner 6, and the lockup clutch 2 is an annular member disposed to face the inner surface of the front cover 4.
- the front cover 4 is released and the hydraulic pressure on the opposite side becomes relatively high. It is configured to be engaged to perform torque transmission by being pressed.
- the forward / reverse switching mechanism 10 is arranged on the same axis as the torque converter 3 following the torque converter 3 described above.
- the forward / reverse switching mechanism 10 is for switching between a forward state in which the input torque is output as it is and a reverse state in which the direction of the input torque is reversed and output.
- It is mainly composed of a pinion type planetary gear mechanism. That is, a ring gear 12 that is an internal gear is arranged concentrically with the sun gear 11 that is an external gear, and a plurality of pairs that are rotatably and revolved by the carrier 13 between these gears 11 and 12.
- the pinion gear is arranged.
- the two pinion gears 14, 15 that are paired with each other mesh with each other, one pinion gear 14 meshes with the sun gear 11, and the other pinion gear 15 meshes with the ring gear 12.
- the sun gear 11 is connected to the turbine runner 6 in the torque converter 3 described above via an intermediate shaft (not shown), and thus serves as an input element.
- a forward clutch 16 is provided between the sun gear 11 and the carrier 13, which is controlled by hydraulic pressure and selectively connects the sun gear 11 and the carrier 13 to set a forward state.
- a reverse brake 17 is provided for selectively stopping the rotation of the ring gear 12 to set a reverse state. Similar to the forward clutch 16, the reverse brake 17 is configured by a brake such as a wet multi-plate brake that is controlled to be engaged / released by hydraulic pressure and has a transmission torque capacity corresponding to the hydraulic pressure. Therefore, this ring gear 12 is a reaction force element.
- a primary pulley (drive pulley) 19 in the belt type continuously variable transmission 18 is disposed on the same axis as the torque converter 3 and the forward / reverse switching mechanism 10.
- the primary pulley 19 and the carrier 13 are connected. That is, the carrier 13 is an output element in the planetary gear mechanism described above.
- the belt-type continuously variable transmission 18 has the same configuration as that conventionally known, and a secondary pulley (driven pulley) 20 is disposed in parallel with the primary pulley 19, and these pulleys 19, 20 are arranged.
- the belt 21 is wound, torque is transmitted between the pulleys 19 and 20 via the belt 21, and the gear ratio is changed by changing the winding radius of the belt 21 with respect to the pulleys 19 and 20. It is configured as follows.
- each of the pulleys 19 and 20 includes a fixed sheave and a movable sheave that approaches and separates from the fixed sheave, and the cross-sectional shape of each of the fixed sheave and the movable sheave is V-shaped.
- a belt groove is formed, and a belt 21 is wound around the belt groove.
- the groove width is changed by moving the movable sheave back and forth with respect to the fixed sheave, and the gear ratio is controlled by changing the winding radius of the belt 21 accordingly. In this way, the movable sheaves are moved back and forth to change the gear ratio, and the hydraulic chambers 22 and 23 that press the movable sheaves so that the pulleys 19 and 20 pinch the belt 21 act on the pulleys 19.
- An output shaft 24 integrated with the secondary pulley 20 is connected to a differential 26 through a counter gear unit 25, and is configured to distribute and transmit power from the differential 26 to left and right wheels 27. Has been.
- the transmission path for transmitting the driving force from the engine 1 to the wheels 27 is mainly composed of the torque converter 3 and the forward / reverse switching mechanism 10 and the belt type continuously variable transmission 18 that are connected in series.
- a hydraulic control device 28 for controlling these transmission members is provided.
- the hydraulic control device 28 is configured to be electrically controlled and output a control hydraulic pressure to each transmission member.
- the hydraulic control device 28 outputs a command signal to the hydraulic control device 28 and supplies the engine 1 with the command signal.
- An electronic control unit 29 that outputs a command signal is provided.
- FIG. 1 shows an example of a hydraulic control apparatus according to the present invention for the belt type continuously variable transmission described above.
- the example shown in FIG. 1 is an example in which a hydraulic pump 30 and an accumulator 31 that stores the hydraulic pressure generated by the hydraulic pump 30 are used as a hydraulic source.
- the hydraulic pump 30 is driven by the engine 1 described above or illustrated. It is configured to generate hydraulic pressure when driven by a motor that does not.
- the discharge port of the hydraulic pump 30 communicates with an accumulator (accumulator) 31 via a check valve 32.
- the check valve 32 is a one-way valve that opens when pressure oil flows from the hydraulic pump 30 toward the accumulator 31 and closes to prevent the flow of pressure oil in the opposite direction.
- the accumulator 31 is configured to store a piston, an elastic expansion body, and the like pressed by an elastic body in the pressure accumulating chamber in a container and store hydraulic pressure with a pressure higher than the elastic force.
- a regulator valve (not shown) for adjusting the hydraulic pressure discharged from the hydraulic pump 30 or the hydraulic pressure discharged from the accumulator 31 to an appropriate line pressure may be provided as appropriate.
- a supply control valve SP1 is provided in a supply oil passage 33 for supplying pressure oil from the hydraulic pump 30 or the accumulator 31, which is the hydraulic source, to the hydraulic chamber 22 in the primary pulley 19.
- This supply control valve SP1 is a so-called normally open type (normally open type) electromagnetic valve, and a spring that pushes the valve body to the valve open position and the elastic force of the spring are reduced to close the valve body to the valve closed position. Therefore, when the electromagnetic coil is not energized, the valve is opened by the elastic force of the spring. Therefore, in the example shown in FIG. 1, the supply control valve SP1 is constituted by an electromagnetic two-way valve.
- a supply oil passage 34 for supplying hydraulic pressure from a hydraulic source to the hydraulic chamber 23 in the secondary pulley 20 is provided.
- the supply oil passage 34 can be configured as an oil passage branched from a supply oil passage 33 that supplies pressure oil from the hydraulic source to the hydraulic chamber 22 of the primary pulley 19.
- a control valve SS1 is provided.
- This supply control valve SS1 is a so-called normally open type (normally open type) electromagnetic valve, similar to the supply control valve SP1 on the primary pulley 19 side, and a spring that pushes the valve body to the valve open position.
- the supply control valve SS1 is configured by an electromagnetic two-way valve.
- a discharge pressure control valve SP2 is provided in a discharge oil passage 35 for communicating the hydraulic chamber 22 in the primary pulley 19 with a drain location such as an oil pan.
- the exhaust pressure control valve SP2 is a so-called normally closed type (normally closed type) electromagnetic valve, and the spring that pushes the valve body to the closed position and the elastic force of the spring are reduced, and the valve body is opened. Therefore, when the electromagnetic coil is not energized, the valve is closed by the elastic force of the spring. Therefore, in the example shown in FIG. 1, the exhaust pressure control valve SP ⁇ b> 2 is configured by an electromagnetic two-way valve.
- a discharge pressure control valve SS2 is provided in the discharge oil passage 36 for releasing the hydraulic pressure from the hydraulic chamber 23 in the secondary pulley 20.
- the exhaust pressure control valve SS2 is a so-called normally closed type (normally closed type) electromagnetic valve, similar to the exhaust pressure control valve SP2 on the primary pulley 19 side, and a spring that pushes the valve body to the closed position.
- an electromagnetic coil that generates an electromagnetic force that reduces the elastic force of the spring and pushes the valve body to the open position. Therefore, when the electromagnetic coil is not energized, the spring is closed by the elastic force of the spring. It is comprised so that. Therefore, in the example shown in FIG. 1, the exhaust pressure control valve SS2 is constituted by an electromagnetic two-way valve.
- the control valves SP1, SP2, SS1, and SS2 are configured to operate according to the control signal output from the electronic control device 29 described above. Therefore, when the main switch (not shown) of the vehicle on which the belt type continuously variable transmission 18 is mounted is turned off or when an electrical failure occurs, the control valve SP1 , SP2, SS1, SS2 are not energized, and each is turned off. In this case, since the supply control valves SP1 and SS1 are normally open, the hydraulic chambers 22 and 23 in the pulleys 19 and 20 communicate with each other via the supply oil passages 33 and 34, and therefore The supply oil passages 33 and 34 and the supply control valves SP1 and SS1 form a communication passage in the present invention.
- the exhaust pressure control valves SP2 and SS2 are normally closed, the exhaust pressure control valves SP2 and SS2 are closed in a state where they cannot be energized, so that the hydraulic chambers 22 and 23 or these are connected.
- the communication path is configured to be blocked from the drain location.
- the hydraulic pump 30 When the vehicle is running with the engine 1 functioning normally, the hydraulic pump 30 operates to generate hydraulic pressure, which is supplied to the above-described supply oil passages 33 and 34, and as necessary. Pressure is accumulated in the accumulator 31. Note that the oil pressure in each of the supply oil passages 33 and 34 is controlled to a line pressure corresponding to the output of the engine 1 or a line pressure corresponding to a requested amount of driving for the vehicle such as an accelerator opening by a primary regulator valve or the like.
- the exhaust pressure control valve SP2 for the primary pulley 19 when the exhaust pressure control valve SP2 for the primary pulley 19 is energized and opened, the hydraulic pressure is discharged from the hydraulic chamber 22 of the primary pulley 19 to the drain location. As a result, the groove width is increased and the winding radius of the belt 21 is reduced. That is, a downshift occurs. In this way, the shift is executed by controlling the pressure oil in the hydraulic chamber 22 of the primary pulley 19.
- the speed ratio is controlled so that the speed of the engine 1 becomes a speed with good fuel consumption, and at the time of acceleration or deceleration, transiently changes to the speed ratio at which acceleration or engine braking force is generated as required. Be controlled. Furthermore, when the vehicle is decelerated and stopped, the maximum speed ratio, which is the speed ratio on the lowest speed side, is controlled.
- the hydraulic pressure of the hydraulic chamber 23 in the secondary pulley 20 is controlled so as to generate a necessary clamping pressure.
- a control signal for opening the supply control valve SS1 for the secondary pulley 20 is output, and as a result, from the hydraulic source The hydraulic pressure is supplied to the hydraulic chamber 23 in the secondary pulley 20 to increase the clamping pressure.
- a control signal for opening the exhaust pressure control valve SS2 for the secondary pulley 20 is output, and the exhaust pressure control valve SS2 is opened to open the secondary pressure.
- the clamping pressure is reduced.
- the hydraulic pressure of the hydraulic chamber 23 in the secondary pulley 20, that is, the clamping pressure is controlled to a pressure corresponding to the torque output from the engine 1 or the torque input to the belt type continuously variable transmission 18.
- the hydraulic control device even if the control valves SP1, SP2, SS1, SS2 cannot be energized and cannot be operated, a shift can be caused. That is, when each of the supply control valves SP1 and SS1 is in an off state without being energized, the hydraulic chambers 22 and 23 in the pulleys 19 and 20 are opened because the springs are elastic. And communicate with each other via supply oil passages 33 and 34. On the other hand, when the control valves SP2 and SS2 for exhaust pressure are turned off without being energized, they are closed by the elastic force of the springs. 22 and 23 are blocked from the drain location. Since the supply oil passages 33 and 34 communicate with the accumulator 31, the hydraulic pressure of the accumulator 31 acts on the hydraulic chambers 22 and 23.
- the gear ratio is maximum, the winding radius of the belt 21 with respect to the primary pulley 19 is minimum, and the winding radius of the belt 21 with respect to the secondary pulley 20 is maximum.
- the belt type continuously variable transmission 18 is driven by the torque transmitted from the wheels 27. That is, when torque is transmitted from the output shaft 24 to the secondary pulley 20 and rotates, the torque is transmitted to the primary pulley 19 via the belt 21 and the primary pulley 19 rotates. In this case, the primary pulley 19 rotates at a higher speed than the secondary pulley 20 because the speed ratio is maximized.
- the hydraulic chambers 22 and 23 described above rotate integrally with the pulleys 19 and 20, and therefore centrifugal force acts on the pressure oil in the hydraulic chambers 22 and 23 to generate centrifugal hydraulic pressure. Since the centrifugal hydraulic pressure increases in proportion to the square of the rotational speed (the rotational speed), the rotational speed of the primary pulley 19 is higher than the rotational speed of the secondary pulley 20 when the speed ratio is large. The centrifugal hydraulic pressure generated in the hydraulic chamber 22 of the primary pulley 19 becomes higher than the centrifugal hydraulic pressure in the hydraulic chamber 23 of the secondary pulley 20.
- the movable sheave moves to the fixed sheave side and the wrapping radius of the belt 21 increases, and at the same time, in the secondary pulley 20, the distance between the fixed sheave and the movable sheave is determined by the belt 21.
- the belt 21 is pushed out and the winding radius of the belt 21 is reduced. In this way, an upshift occurs in which the gear ratio decreases so as to approach “1”.
- the rotational speed of the primary pulley 19 that is the input rotational speed of the belt-type continuously variable transmission 18 decreases so as to approach the rotational speed of the secondary pulley 20 on the output side.
- the rotational speed of the forward / reverse switching mechanism 10 decreases, and noise such as gear noise generated in the forward / reverse switching mechanism 10 can be reduced. Further, since the centrifugal oil pressure is also generated in the secondary pulley 20 as described above, the belt clamping pressure by the secondary pulley 20 can be secured, and for that purpose, the vehicle is pulled with the main switch turned off. In addition, the slippage of the belt 21 can be prevented or suppressed.
- shut-off valve SAC is connected to a hydraulic pressure source such as the accumulator 31 and the hydraulic pump 30, and the above-described supply oil passages 33 and 34 are connected to the other port. Since the other configuration is the same as the configuration shown in FIG. 1, the same reference numerals as those in FIG.
- the example shown in FIG. 3 is an example in which an electromagnetic relief valve 37 is provided in place of the shutoff valve SAC in the configuration shown in FIG.
- the electromagnetic relief valve 37 is a discharge pressure valve configured to increase the relief pressure as the energization amount increases, and the relief pressure becomes the lowest when the energization is not conducted. Therefore, in the configuration shown in FIG. 3, the oil pressure in each of the supply oil passages 33 and 34 is limited to the relief pressure set by the electromagnetic relief valve 37.
- control valves SP1, SP2, SS1, and SS2 cannot be energized using the oil passages 33 and 34 that supply hydraulic pressure to the hydraulic chambers 22 and 23 in the pulleys 19 and 20, respectively.
- a “communication path” for communicating the hydraulic chambers 22 and 23 is formed.
- An oil passage that communicates the chambers 22 and 23 may be provided, and an electromagnetic shut-off valve that shuts off the oil passage when energized and opens when not energized may be provided.
- the supply control valve according to the present invention may be a normally open type that maintains the valve open state in a state in which it cannot be energized
- the exhaust pressure control valve is a normally closed type that maintains the valve in a state in which it cannot be energized.
- Any valve other than the electromagnetic two-way valve described above may be used.
- the transmission device targeted by the present invention may be a transmission device other than the belt-type continuously variable transmission.
- the chain can be wound around a rotating member such as a sprocket and the winding radius can be changed. It may be a transmission.
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Transmission Device (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
Description
Claims (7)
- 一対の回転部材に環状の伝動部材が巻き掛けられるとともに、それらの回転部材が油圧が供給されることにより前記伝動部材が巻き掛けられている溝の幅を狭くするように作用する油圧室をそれぞれ備え、それらの油圧室がそれぞれ電気的に制御される供給用制御弁を介して油圧源に接続されているとともに、前記各油圧室がそれぞれ電気的に制御される排圧用制御弁を介してドレイン箇所に接続されている巻掛け伝動装置の油圧制御装置において、
前記供給用制御弁および排圧用制御弁のいずれにも通電できない場合に、前記各油圧室を前記油圧源およびドレイン箇所に対して遮断するように構成されるとともに、
前記各油圧室を互いに連通させる連通路を備えている
ことを特徴とする巻掛け伝動装置の油圧制御装置。 - 前記供給用制御弁は、通電できないことにより油路を開く常開型の弁によって構成されるとともに、
前記排圧用制御弁のそれぞれは、通電できないことにより油路を閉じる常閉型の弁によって構成され、
前記連通路は、一方の前記回転部材に対して一方の前記供給用制御弁を介して前記油圧源から油圧を供給する第1の油路と、その第1の油路の前記一方の供給用制御弁より前記油圧源側の所定箇所に連通しかつ他方の前記回転部材に対して他方の前記供給用制御弁を介して前記油圧源から油圧を供給する第2の油路とを含む
ことを特徴とする請求項1に記載の巻掛け伝動装置の油圧制御装置。 - 前記油圧源から前記連通路に供給される油圧を制限する油圧制限手段を更に備えていることを特徴とする請求項1または2に記載の巻掛け伝動装置の油圧制御装置。
- 前記油圧制限手段は、前記供給用制御弁および前記排圧用制御弁に通電できない場合に前記油圧源と前記連通路との連通を遮断する遮断弁を含むことを特徴とする請求項3に記載の巻掛け伝動装置の油圧制御装置。
- 前記油圧制限手段は、前記油圧源と前記連通路との間に接続されかつ前記供給用制御弁および前記排圧用制御弁に通電できない場合にリリーフ圧が低下させられるリリーフ弁を含むことを特徴とする請求項3に記載の巻掛け伝動装置の油圧制御装置。
- 前記一対の回転部材のうち駆動力源からトルクが入力される入力側回転部材が、その入力側回転部材に対して入力されるトルクの方向を反転させる前後進切替機構に連結されていることを特徴とする請求項1ないし5のいずれかに記載の巻掛け伝動装置の油圧制御装置。
- 前記伝動部材は、ベルトを含み、
前記一対の回転部材は、前記ベルトが巻き掛けられる溝の幅を変更可能な駆動側プーリと、前記ベルトが巻き掛けられる溝の幅を変更可能な従動側プーリとを含む
ことを特徴とする請求項1ないし6のいずれかに記載の巻掛け伝動装置の油圧制御装置。
Priority Applications (5)
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JP2012537533A JP5376067B2 (ja) | 2010-10-08 | 2010-10-08 | 巻掛け伝動装置の油圧制御装置 |
US13/808,842 US20130109516A1 (en) | 2010-10-08 | 2010-10-08 | Hydraulic control system for a wrapping transmission |
PCT/JP2010/067717 WO2012046335A1 (ja) | 2010-10-08 | 2010-10-08 | 巻掛け伝動装置の油圧制御装置 |
EP10858141.4A EP2626596A4 (en) | 2010-10-08 | 2010-10-08 | HYDRAULIC CONTROL DEVICE FOR WINDING GEAR |
CN201080069464.8A CN103154579B (zh) | 2010-10-08 | 2010-10-08 | 卷挂传动装置的液压控制装置 |
Applications Claiming Priority (1)
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PCT/JP2010/067717 WO2012046335A1 (ja) | 2010-10-08 | 2010-10-08 | 巻掛け伝動装置の油圧制御装置 |
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WO2012046335A1 true WO2012046335A1 (ja) | 2012-04-12 |
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PCT/JP2010/067717 WO2012046335A1 (ja) | 2010-10-08 | 2010-10-08 | 巻掛け伝動装置の油圧制御装置 |
Country Status (5)
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US (1) | US20130109516A1 (ja) |
EP (1) | EP2626596A4 (ja) |
JP (1) | JP5376067B2 (ja) |
CN (1) | CN103154579B (ja) |
WO (1) | WO2012046335A1 (ja) |
Cited By (1)
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CN109307071A (zh) * | 2017-07-26 | 2019-02-05 | 上海汽车集团股份有限公司 | 一种变速器电磁阀的特性曲线调整方法及装置 |
Families Citing this family (3)
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EP2860427A4 (en) * | 2012-06-08 | 2016-09-07 | Jatco Ltd | CONTINUOUSLY VARIABLE TRANSMISSION AND HYDRAULIC PRESSURE CONTROL METHOD RELATING THERETO |
US10047860B2 (en) * | 2016-06-02 | 2018-08-14 | GM Global Technology Operations LLC | Pump switching control systems and methods for continuously variable transmissions |
US9970540B2 (en) * | 2016-06-02 | 2018-05-15 | GM Global Technology Operations LLC | Transmission fluid pressure control systems and methods for continuously variable transmissions |
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CN103154579B (zh) | 2014-11-26 |
CN103154579A (zh) | 2013-06-12 |
JPWO2012046335A1 (ja) | 2014-02-24 |
JP5376067B2 (ja) | 2013-12-25 |
EP2626596A4 (en) | 2014-05-21 |
EP2626596A1 (en) | 2013-08-14 |
US20130109516A1 (en) | 2013-05-02 |
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