JP2011163394A - Control device of power transmission device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a control device of a power transmission device for improving efficiency, responsiveness, and controllability regardless of using means by hydraulic pressure and mechanical mechanisms by centrifugal force. <P>SOLUTION: The control device of a power transmission device comprises: a rotary member 1 provided on an input shaft 3 in which power is transmitted; a movable part 5 equipped with the rotary member 1 moving longitudinally in the axial direction of the rotary member 1; a fluid pressure chamber 15 in which fluid is supplied to apply pressing force to the movable part 5 capable of moving longitudinally; and a thrust applying member 11 which applies thrust to the movable part 5 capable of moving longitudinally by centrifugal force generated by rotating the rotary member 1. In the control device, the thrust applying member 11 is stored in a thrust applying chamber equipped with the movable part 5 and the thrust applying chamber is isolated from the fluid pressure chamber 15. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a control device for a power transmission device that changes a power transmission state by applying pressure.

  The vehicle has a transmission on the output side of the driving force source in order to transmit the driving force from the internal combustion engine or the electric motor as the driving force source, that is, the output torque to the road surface under the optimum conditions according to the traveling state of the vehicle. Is provided. The transmission includes a continuously variable transmission that continuously controls the gear ratio and a stepped transmission that controls the gear ratio stepwise. The continuously variable transmission has two pulleys, a primary pulley to which the driving force from the driving force source is transmitted, a secondary pulley that changes the output torque transmitted to the primary pulley, and the primary pulley. There is known a belt-type continuously variable transmission that includes a belt that transmits a driving force to a secondary pulley.

  The primary pulley and the secondary pulley are two pulley shafts arranged in parallel, that is, a primary pulley shaft and a secondary pulley shaft, and a movable sheave that slides in the rotation axis direction of both pulleys (primary movable sheave and secondary movable sheave). And two fixed sheaves (primary fixed sheave and secondary fixed sheave) that face the two movable sheaves in the rotational axis direction and that form a V-shaped groove with the movable sheave, and rotate with respect to the belt A clamping pressure generating hydraulic chamber that applies clamping pressure in the axial direction is configured. The belt is wound around a V-shaped groove formed in each of the primary pulley and the secondary pulley.

  In this belt-type continuously variable transmission, each movable sheave slides on each pulley shaft in the direction of its rotational axis by each clamping pressure generating hydraulic chamber, and is formed in a V-shape formed on each of the primary pulley and the secondary pulley. Change the width of the groove. As a result, the wrapping radius between the belt, the primary pulley and the secondary pulley is continuously changed, and the gear ratio is continuously changed. That is, the output torque from the drive source is changed steplessly. In addition, when oil is supplied to and discharged from each clamping pressure generating hydraulic chamber and each movable sheave slides in the rotation axis direction of each pulley, the oil supplied to and discharged from each clamping pressure generating hydraulic chamber The belt type continuously variable transmission is controlled by appropriately adjusting the pressure of the belt using an on-off valve or the like.

  The belt-type continuously variable transmission described in Patent Document 1 has the same configuration as that described above, and has fixed pulley pieces on the input shaft and the output shaft, respectively. A movable pulley piece is provided so as to be movable in the longitudinal direction on the shaft facing the fixed pulley piece. A power transmission belt is hung on both V-shaped grooves formed by these pulley pieces. On the back of the movable pulley piece disposed on the input shaft, an oil-tight space is formed by a fixed piece fixed to the shaft at the back of the back and an inner and outer extending portion protruding from the back surface of the movable pulley piece. . A plurality of radial guide grooves are provided in the space, and a centrifugal force imparting material that can move in the guide grooves is accommodated in the guide grooves. The space is provided with an oil introduction hole, and the oil introduction hole is connected to an external oil feeding means.

  Patent Document 2 describes a pair of pulley main bodies that can also be applied to an engine accessory system driven by a belt, and includes an elastic member that urges one pulley main body toward the other pulley main body side. A characteristic variable diameter pulley is described.

Japanese Patent Laid-Open No. 5-340452 JP 2001-82559 A

  By the way, in the belt-type continuously variable transmission described in Patent Document 1 described above, the centrifugal force and the hydraulic pressure obtained by the centrifugal force imparting material are used as the thrust of the movable pulley piece. By combining with centrifugal thrust, the generation of hydraulic pressure can be made simpler, resulting in a device with less mechanical loss. Further, a plurality of centrifugal force imparting materials are arranged in the space portion, and a material having sufficient centrifugal force can be obtained. Furthermore, each centrifugal force imparting material moves only within the radial guide groove and does not contact each other. Furthermore, the space where the centrifugal force imparting material is accommodated is made oil tight and used as a hydraulic cylinder. This not only leads to compactness, but also helps to lubricate and smooth the movement of the centrifugal force imparting material in the guide groove.

  However, in the belt-type continuously variable transmission described in Patent Document 1, each of the plurality of centrifugal force imparting members arranged is moved by radial force in the radial guide groove. The guide groove is provided in a space portion, and this space portion is used as a hydraulic cylinder. Therefore, when the centrifugal force imparting material moves inside the hydraulic cylinder, that is, in the hydraulic oil, it receives the resistance of the hydraulic oil. Further, even when hydraulic pressure is applied inside the hydraulic cylinder, the centrifugal force imparting material becomes resistant. Therefore, the speed change responsiveness of the centrifugal force imparting material is lowered. As a result, the amount of work by the hydraulic pressure increases at the time of shifting, and the fuel efficiency cannot be improved.

  In addition, in the hydraulic oil of the hydraulic cylinder, it moves in contact with the guide groove, so that wear powder accumulates over time and causes problems in various mechanisms such as blocking the oil passage. There was a fear. The cause of the malfunction of the apparatus is that the centrifugal force imparting material is housed inside the hydraulic cylinder that is the space. As described above, there has been a problem in an apparatus using a hydraulic mechanism and a mechanical mechanism using a centrifugal force in a mechanism for moving a movable pulley of a belt type continuously variable transmission, that is, a movable portion of a power transmission device.

  The present invention has been made paying attention to the above technical problem, and in the case of using a hydraulic mechanism and a mechanical mechanism such as a centrifugal force to change the power transmission state by moving the movable part. However, an object of the present invention is to provide a control device for a power transmission device that can improve efficiency, responsiveness, and controllability.

  In order to achieve the above object, the invention of claim 1 includes a rotating member provided on an input shaft to which power is transmitted, and a movable part provided in the rotating member and moving back and forth in the axial direction of the rotating member. And a fluid pressure chamber for applying a pressing force for moving the movable part back and forth when supplied with fluid, and a thrust applying member for applying a thrust for moving the movable part back and forth by centrifugal force due to rotation of the rotating member In the control device for a power transmission device, the thrust imparting member is housed in a thrust imparting chamber provided in the movable portion, and the thrust imparting chamber and the fluid pressure chamber are isolated from each other. It is what.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, the pressing force by the fluid pressure chamber and the thrust by the thrust imparting member individually act on the movable part. It is a control device.

  According to a third aspect of the invention, in addition to the configuration of the first or second aspect, the movable portion includes a drive pulley provided on an input shaft to which power is transmitted, and a follower provided at a position facing the drive pulley. A movable sheave provided on the drive pulley of a belt-type continuously variable transmission that includes a pulley and a belt that is wound around the two pulleys and transmits output torque from a drive force source. The pressing force acts on the outer peripheral side of the movable sheave, and is a control device for a power transmission device.

  According to the invention of claim 1, the thrust imparting material is accommodated in the thrust imparting chamber provided in the movable portion, and since the thrust imparting chamber and the fluid pressure chamber are isolated, the thrust imparting material and The fluid supplied to the fluid pressure chamber by the thrust applying chamber can be reduced, and the operations of the thrust applying chamber and the fluid pressure chamber are not hindered from each other. Further, since the thrust applying chamber and the fluid pressure chamber individually act on the movable portion, it is possible to apply thrust and pressing force to the movable portion with high controllability.

  According to the invention of claim 2, the thrust force by the fluid pressure chamber and the thrust force by the thrust imparting material are such that the thrust of the thrust imparting chamber and the thrust force of the fluid pressure chamber individually act on the movable part. Therefore, thrust and pressing force can be applied to the movable part with good controllability.

  According to the invention of claim 3, since the pressing force by the fluid pressure chamber acts on the outer peripheral side of the movable sheave, so-called sheave collapse due to tilting of the movable sheave can be prevented or suppressed.

It is a figure showing typically the 1st example which applied the control device of the power transmission device concerning this invention to the belt type continuously variable transmission. It is a figure showing typically the 2nd example which applied the control device of the power transmission device concerning this invention to the belt type continuously variable transmission. It is a figure which represents typically 3rd Example which applied the control apparatus of the power transmission device which concerns on this invention to the belt-type continuously variable transmission.

  Next, the present invention will be described with reference to specific examples. The present invention is a control device for a power transmission device that uses hydraulic means and a mechanical mechanism such as centrifugal force, and moves the movable part with its pressing force and thrust to change its power transmission state. is there. The specific example described below is an example in which the control device for a power transmission device according to the present invention is applied to a belt-type continuously variable transmission, and a pulley for changing the gear ratio of the belt-type continuously variable transmission. The movable sheave provided in the control is slid in the rotation axis direction. The control device for a power transmission device according to the present invention can be used for machines and devices in various fields such as a vehicle, an aircraft, a ship, and an industrial machine equipped with such a belt type continuously variable transmission.

  FIG. 1 shows a configuration example in which a control device for a power transmission device of the present invention is applied to a drive pulley 1 provided in a belt type continuously variable transmission mounted on a vehicle. The belt type continuously variable transmission is configured such that a belt 2 is wound around a drive pulley 1 and a driven pulley (not shown), and a torque converter (not shown) is supplied from a driving force source (not shown) such as an engine between these pulleys. (Not shown) or the like is transmitted to the input rotary shaft 3 and the wrapping radius of the belt 2 around the driving pulley 1 and the driven pulley (not shown) is changed to change the gear ratio. It is configured as follows.

  Specifically, the drive pulley 1 includes a fixed sheave 4 and a movable sheave 5 arranged so as to approach and separate from the fixed sheave 4, and V between the fixed sheave 4 and the movable sheave 5. A groove-shaped belt winding groove 6 is formed. On the other hand, the driven pulley (not shown) is also provided with a fixed sheave (not shown) and a movable sheave (not shown) arranged so as to approach / separate (back and forth) the fixed sheave. V-shaped belt winding grooves (not shown) are formed between the fixed sheave 4 and the movable sheave 5 of the pulley 1 and between the fixed sheave and the movable sheave of the driven pulley.

  The drive pulley 1 is provided with actuators 7 and 8 (described later) for moving the movable sheave 5 back and forth in the direction of the rotation axis, and the driven pulley is also used for moving the movable sheave back and forth in the direction of the rotation axis. An actuator (not shown) is provided. The actuator provided on the driven pulley side is provided on the back surface of the movable sheave of the driven pulley, and is configured by a hydraulic device including a spring, a torque cam, and a cylinder and a piston. On the other hand, the actuator provided in the drive pulley 1 is provided on the back surface of the movable sheave 5 of the drive pulley 1 and includes a hydraulic actuator 7 that is a hydraulic means and a mechanical actuator 8 that is a mechanism using centrifugal force. Hereinafter, configurations of the hydraulic actuator 7 and the mechanical actuator 8 will be described.

  The movable sheave 5 of the drive pulley 1 is provided with a boss portion 9 on the innermost peripheral portion of the back surface 5a. The boss portion 9 is formed in a cylindrical shape and is fitted to the input rotation shaft 3 so that the movable sheave 5 can rotate integrally with the input rotation shaft 3 in the rotation direction, and slides in the rotation axis direction. It is possible. A fixed plate 10 is fixed to the input rotary shaft 3 so as to face the back surface 5a of the movable sheave 5 of the drive pulley 1 in the rotational axis direction. This fixed plate 10 is formed in a taper shape, that is, its cross section is inclined toward the movable sheave 5 side. Further, since the movable sheave 5 forms the belt winding groove 6 having a V-groove shape as described above, the back surface 5a has a shape whose cross section is inclined toward the fixed plate 10 side.

  A weight roller (thrust imparting material) 11 is accommodated between the back surface 5 a of the movable sheave 5 and the surface 10 a of the fixed plate 10 on the movable sheave 5 side. The weight roller 11 is, for example, a spherical weight that is set so that an appropriate thrust is applied to the movable sheave 5. The weight roller 11 is provided with a guide (sliding groove) (not shown) on at least one of the back surface 5a of the movable sheave 5 and the movable sheave 5 side of the fixed plate 10, and slides in the guide. And it moves by the centrifugal force from the inner peripheral side to the outer peripheral side, and it is comprised so that a thrust may be given to the fixed sheave 4 side with respect to the back surface 5a of the movable sheave 5 in the rotation axis direction. A plurality of guides are radially provided on at least one of the back surface 5a of the movable sheave 5 and the movable sheave 5 side of the fixed plate 10, and the weight roller 11 is accommodated in the guide.

  Thus, the weight roller 11 is sandwiched between the back surface 5a of the movable sheave 5 and the surface 10a of the fixed plate 10 on the movable sheave 5 side. Then, the back surface 5a and the surface 10a are narrowed in the direction of the outer peripheral side, and the weight roller 11 on which the centrifugal force acts is brought into contact therewith, so that the back surface 5a of the movable sheave 5 is rotated in the rotational axis direction. A mechanical actuator 8 is configured to apply thrust to the fixed sheave 4 side. The mechanical actuator 8 is configured to apply a thrust to the movable sheave 5 by the centrifugal force of the weight roller 11 caused by the rotation of the drive pulley 1. The thrust is applied according to the weight and shape of the weight roller 11. And the angle between the movable sheave 5 and the fixed plate 10 and the shape of the guide can be adjusted.

  The movable sheave 5 of the drive pulley 1 is provided with an outwardly extending portion 12 that extends from the outermost peripheral portion of the back surface 5a. The piston 13 of the hydraulic actuator 7 is connected to the end portion of the outer extending portion 12 that extends in a cylindrical shape from the outermost peripheral portion of the back surface 5 a of the movable sheave 5. That is, the movable sheave 5 is configured such that the boss portion 9, the V-groove belt winding groove 6 and the portion that forms the back surface 5 a, the outwardly extending portion 12, and the piston 13 integrally move in the rotational axis direction. ing. In addition, a cylinder case 14 fixed to rotate integrally with the input rotation shaft 3 is provided.

  The piston 13 and the cylinder case 14 constitute a hydraulic chamber (narrow pressure hydraulic chamber, cylinder) 15. The hydraulic chamber 15 is in communication with an oil passage 16 and an introduction hole 17 formed in the input rotary shaft 3. A hydraulic path is constituted by a hydraulic pump, a check valve, an accumulator, an oil passage, an on-off valve (all not shown) or the like that operates using a driving force source (not shown) as a power source or is operated by an electric motor. Oil (hydraulic oil) is supplied to and discharged from the hydraulic chamber 15 through the passage 16 and the introduction hole 17. Thus, oil is supplied to and discharged from the hydraulic chamber 15 and the piston 13 moves back and forth in the direction of the rotation axis. Since the piston 13 and the movable sheave 5 are integrally formed, the movable sheave 5 is configured to move back and forth with respect to the fixed sheave 4. When the movable sheave 5 moves back and forth with respect to the fixed sheave 4, the belt winding groove 6 in the shape of a V groove approaches and separates so as to clamp the belt 2. The hydraulic actuator 7 described above may have a configuration in which a fluid pressure chamber for sealing the working fluid using air or the like as a working fluid in addition to oil is provided.

  Next, the operation of the first embodiment will be described. The power of the vehicle is input from a driving force source (not shown) such as an engine to the input rotary shaft 3 of the driving pulley 1 in the belt type continuously variable transmission via a torque converter (not shown). The input power is transmitted to the fixed sheave 4 and the movable sheave 5 that are configured to rotate integrally with the input rotary shaft 3. The power from the fixed sheave 4 and the movable sheave 5 is transmitted to the belt 2 sandwiched between the sheaves 4 and 5 by the actuators 7 and 8. The power transmitted to the belt 2 is transmitted to a driven pulley in which the belt 2 is sandwiched between a fixed sheave and a movable sheave of a driven pulley (not shown) by a narrow pressure such as a torque cam or a spring, and provided on the driven pulley. Power is transmitted to the output rotating shaft (not shown). Power is transmitted from a wheel (not shown) to a road surface via a differential, an axle, or the like from an output rotating shaft provided with a driven pulley.

  The clamping pressure for the belt 2 to be sandwiched between the drive pulley 1 during power transmission is controlled by the hydraulic actuator 7 and the mechanical actuator 8. A hydraulic pump (not shown) communicated with the hydraulic actuator 7 supplies and discharges oil to the hydraulic chamber 15 and generates a pressing force Fp so that the piston 13 moves back and forth in the direction of the rotation axis. As shown in FIG. 1, the pressing force Fp in the rotational axis direction by the piston 13 of the hydraulic actuator 7 is transmitted to the outer extending portion 12 and transmitted to the movable sheave 5 to move the movable sheave 5 back and forth in the rotational axis direction. As a result, a clamping pressure acts on the belt 2 by the fixed sheave 4 and the movable sheave 5. The control of the clamping pressure by the hydraulic actuator 7 is performed by sending a signal from a hydraulic sensor provided in the hydraulic chamber 15 or the like and a sensor for grasping the running state of the vehicle and the driver's request to an electronic control unit ECU (not shown). Thus, it is controlled in accordance with the running state of the vehicle and the driver's request and in cooperation with the mechanical actuator 8.

  On the other hand, in the mechanical actuator 8, the back surface 5 a and the surface 10 a are inclined by the centrifugal force caused by the weight roller 11 sandwiched between the fixed plate 10 and the movable sheave 5 rotating together with the fixed plate 10 and the movable sheave 5. Therefore, thrust Fw is generated. That is, the weight roller 11 slides and receives a reaction force by centrifugal force due to rotation in a plurality of guides radially provided on at least one of the back surface 5a of the movable sheave 5 and the movable sheave 5 side of the fixed plate 10. Thus, this thrust Fw is generated. Then, as shown in FIG. 1, the thrust Fw by the weight roller 11 of the mechanical actuator 8 is transmitted to the back surface 5a of the movable sheave 5, and this movable sheave 5 is moved back and forth in the rotation axis direction. As a result, a clamping pressure acts on the belt 2 by the fixed sheave 4 and the movable sheave 5. In this first embodiment, the pressing force Fp by the hydraulic actuator 7 and the thrust Fw by the mechanical actuator 8 individually act on the movable sheave 5. As shown in FIG. 1, the resultant force Ftotal of the pressing force Fp and the thrust force Fw acts as a sandwiching pressure, and the sandwiching pressure acts on the belt 2 by the fixed sheave 4 and the movable sheave 5.

  Since the hydraulic actuator 7 and the mechanical actuator 8 are provided in this way, the movable sheave 5 is moved only by the hydraulic actuator 7 by a hydraulic pump that is operated by power from a driving force source (not shown). The fixed sheave 4 and the movable sheave 5 are not configured to be clamped by the belt 2, but the movable sheave 5 is also moved by the mechanical actuator 8 that is operated by the centrifugal force generated by the rotation of the driving pulley 1. 5, the belt 2 is clamped. Therefore, loss due to a hydraulic pump (not shown) can be reduced, and fuel consumption and the like are improved. In addition, since the hydraulic chamber 15 of the hydraulic actuator 7 and the space in which the weight roller 11 of the mechanical actuator 8 is accommodated are separated from each other, the operations of the two actuators 7 and 8 are not hindered from each other. Furthermore, since the hydraulic chamber 15 of the hydraulic actuator 7 and the space in which the weight roller 11 of the mechanical actuator 8 is accommodated are separated from each other, the movable sheave 5 is individually acted on. The thrust and the pressing force can be applied to the movable sheave 5 with good responsiveness and controllability. Furthermore, since the pressing force by the hydraulic actuator 7 is transmitted from the piston 13 to the movable sheave 5 via the outer extending portion 12, the pressing force acts on the outer peripheral side of the movable sheave 5 and the movable sheave 5 is tilted. So-called sheave collapse can be prevented or suppressed.

  Next, a second embodiment will be described. In the second embodiment, the configuration of the hydraulic actuator 20 and the mechanical actuator 21 is different from that of the first embodiment, and the other elements and parts are the same. . In the second embodiment, the movable sheave 5 is provided with a boss portion 22 on the innermost peripheral portion of the back surface 5a thereof, and the boss portion 22 and the piston 25 of the hydraulic actuator 20 are integrally formed. A fixed plate 23 is integrally formed at the open end of the outermost peripheral portion of the cylinder case 26. The weight roller 11 is sandwiched between the back surface 5a of the movable sheave 5 and the surface 5a of the fixed plate 23 on the movable sheave 5 side. Further, an outer extending portion 24 is provided on the outermost peripheral portion of the movable sheave 5. The back surface 5a of the movable sheave 5 and the surface 23a of the fixed plate 23 are brought into contact with the back surface 5a of the movable sheave 5 by abutment of the weight roller 11 that is narrowed in the direction of the outer peripheral side and acting with centrifugal force. Thus, the mechanical actuator 21 is configured to apply thrust to the fixed sheave 4 side in the direction of the rotation axis.

  On the other hand, a hydraulic chamber (narrow pressure hydraulic chamber, cylinder) 27 is configured by the cylinder case 26 integrally formed with the fixing plate 23 and the piston 25 of the hydraulic actuator 20 integrally formed with the boss portion 9. The configuration for supplying oil to the hydraulic chamber 27 is the same as in the first embodiment. The oil is supplied to and discharged from the hydraulic chamber 27 and the piston 25 moves back and forth in the direction of the rotation axis. Since the piston 25 and the movable sheave 5 are integrally formed, the movable sheave 5 is configured to move back and forth with respect to the fixed sheave 4. When the movable sheave 5 moves back and forth with respect to the fixed sheave 4, the belt winding groove 6 in the shape of a V groove approaches and separates so as to clamp the belt 2. The hydraulic actuator 20 shown above may have a configuration in which a fluid pressure chamber is provided that seals the working fluid using air or the like as a working fluid in addition to oil.

  The operation of the second embodiment will be described below. The description of the same operation as that of the first embodiment will be omitted. The clamping pressure for pinching the belt 2 on the drive pulley 1 during power transmission is controlled by the hydraulic actuator 20 and the mechanical actuator 21 as in the first embodiment. A hydraulic pump (not shown) communicated with the hydraulic actuator 20 or the like supplies and discharges oil to the hydraulic chamber 27 and generates a pressing force Fp so that the piston 25 moves back and forth in the direction of the rotation axis. As shown in FIG. 2, the pressing force Fp in the rotational axis direction by the piston 25 of the hydraulic actuator 20 is transmitted to the boss portion 22 and transmitted to the movable sheave 5 to move the movable sheave 5 back and forth. As a result, a clamping pressure acts on the belt 2 by the fixed sheave 4 and the movable sheave 5. The control of the clamping pressure by the hydraulic actuator 20 is performed by sending a signal from an oil pressure sensor provided in the oil pressure chamber 27 or the like, or a sensor for grasping the driving state of the vehicle or a driver's request to an electronic control unit ECU (not shown). Thus, it is controlled in accordance with the traveling state of the vehicle and the driver's request and in cooperation with the mechanical actuator 21.

  On the other hand, in the mechanical actuator 21, the back surface 5a and the surface 23a are inclined by the centrifugal force generated when the weight roller 11 sandwiched between the fixed plate 23 and the movable sheave 5 rotates together with the fixed plate 23 and the movable sheave 5. Therefore, thrust Fw is generated. That is, the weight roller 11 slides and receives a reaction force by centrifugal force due to rotation in a plurality of guides radially provided on at least one of the back surface 5a of the movable sheave 5 and the movable sheave 5 side of the fixed plate 25. Thus, this thrust Fw is generated. Then, as shown in FIG. 2, the thrust Fw by the weight roller 11 of the mechanical actuator 21 is transmitted to the back surface 5a of the movable sheave 5, and the movable sheave 5 is moved back and forth in the rotation axis direction. As a result, a clamping pressure acts on the belt 2 by the fixed sheave 4 and the movable sheave 5. The pressing force Fp by the hydraulic actuator 20 and the thrust Fw by the mechanical actuator 21 individually act on the movable sheave 5 in the second embodiment as in the first embodiment. As shown in FIG. 2, the resultant force Ftotal of the pressing force Fp and the thrust force Fw acts as a clamping pressure, and the clamping pressure acts on the belt 2 by the fixed sheave 4 and the movable sheave 5.

  Thus, since the hydraulic actuator 20 and the mechanical actuator 21 are provided, the movable sheave 5 is moved only by the hydraulic actuator 20 by a hydraulic pump that is operated by power from a driving force source (not shown). The fixed sheave 4 and the movable sheave 5 are not configured to be clamped by the belt 2 but the movable sheave 5 is also moved by the mechanical actuator 21 that is operated by the centrifugal force generated by the rotation of the driving pulley 1 to thereby move the fixed sheave 4 and the movable sheave. 5, the belt 2 is clamped. Therefore, loss due to a hydraulic pump (not shown) can be reduced, and fuel consumption and the like are improved. Further, since the hydraulic chamber 27 of the hydraulic actuator 20 and the space in which the weight roller 11 of the mechanical actuator 21 is accommodated are separated from each other, the operations of the two actuators 20 and 21 are not hindered from each other. Furthermore, since the hydraulic chamber 27 of the hydraulic actuator 20 and the space in which the weight roller 11 of the mechanical actuator 21 is accommodated are separated from each other, the movable sheave 5 is individually acted on. The thrust and the pressing force can be applied to the movable sheave 5 with good responsiveness and controllability.

  Next, a third embodiment will be described. The third embodiment supplies fluid such as oil or air to the hydraulic chambers 15 and 27 in the first and second embodiments. Therefore, the third embodiment can be applied to the second embodiment, but the first embodiment is an example. An example applied to the embodiment will be described, and the same reference numerals will be given to portions that are the same as the configuration and operation of the first embodiment, and description thereof will be omitted. In the third embodiment, the exhaust pressure of exhaust gas discharged from an internal combustion engine such as a gasoline engine in a vehicle is used. As the internal combustion engine in the third embodiment, a gasoline engine, a diesel engine, an LPG engine, or the like can be used. Hereinafter, an example of an internal combustion engine is a gasoline engine as a specific example.

  As shown in FIG. 3, since the control device for a power transmission device according to the present invention is applied to a vehicle, a gasoline engine 30 (hereinafter simply referred to as the engine 30) is provided as a driving force source. Yes. The engine 30 is provided with a cylinder 32 that constitutes a combustion chamber 31 for burning fuel. The cylinder 32 is provided with a piston 33 disposed so as to be capable of reciprocating inside thereof. A cylinder head 34 is attached to the top of the cylinder 32. An intake port 35 is formed in the cylinder head 34. The intake port 35 is provided for supplying a mixture of fuel and air to the combustion chamber 31.

  Therefore, one side of the intake pipe 36 is connected to the intake port 35, and the other side of the intake pipe 36 is connected to an intake manifold (not shown) having an air purifier or a resonator (not shown). Air is sucked from outside air. An electronic throttle valve 37 is provided in the intake pipe 36. The electronic throttle valve 37 is configured to be able to set an increase / decrease in the amount of air taken in by an actuator (not shown) in accordance with an operation amount of an accelerator pedal (not shown) by an operation of a driver or the like. An intake valve 38 that controls the flow of the air-fuel mixture from the intake pipe 36 to the combustion chamber 31 is provided in the intake pipe 36. The intake valve 38 is formed with a valve head that directly opens and closes the combustion chamber 31, and is configured to move up and down in accordance with the timing of combustion by a cam mechanism and a spring (both not shown).

  The cylinder head 34 is provided with a spark plug 39. As described above, the spark plug 39 ignites the air-fuel mixture supplied from the intake port 35 in accordance with the rotation timing of the engine 30 and the compressed state of the air-fuel mixture in the combustion chamber 31. Further, an exhaust port 40 is formed in the cylinder head 34. The exhaust port 40 is provided for discharging exhaust gas generated by combustion of the air-fuel mixture compressed in the combustion chamber 31.

  Therefore, one exhaust pipe 41 communicates with the exhaust port 40, and the other exhaust pipe 41 communicates with an engine exhaust path (not shown) of an energy conversion device 43, which will be described later, to discharge exhaust gas to the outside air. It becomes the composition which is done. An exhaust valve 42 that controls the flow of exhaust gas from the combustion chamber 31 to the exhaust pipe 41 is provided in the exhaust pipe 41. The exhaust valve 42 is formed with a valve head that directly opens and closes the combustion chamber 31, and is configured to move up and down by a cam mechanism and a spring (both not shown).

  As described above, the air-fuel mixture of the air in the combustion chamber 31 and the sprayed fuel is ignited by the spark plug 39 to burn and generate exhaust gas. Thereafter, the exhaust gas is discharged from the exhaust port 40 by the expansion pressure accompanying combustion. In the control device for the power transmission device according to the present invention, the energy conversion device uses the kinetic energy due to the exhaust pressure of the exhaust gas discharged from the combustion chamber 31 through the exhaust pipe 41 through the exhaust pipe 41 due to the expansion pressure accompanying combustion. 43 is provided.

  The energy conversion device 43 includes a pressure conversion mechanism 44 and a pressure control mechanism 45. The pressure conversion mechanism 44 is provided with an engine exhaust path (not shown), and kinetic energy due to exhaust pressure of exhaust gas from the engine is converted into energy for applying pressure to a fluid such as oil or air. Note that exhaust gas from an engine exhaust path (not shown) is sent to the catalyst after energy conversion. The pressure control mechanism 45 is provided with a flow path and an on-off valve (both not shown) in order to control the pressure of the fluid converted by the pressure conversion mechanism 44. The pressure control mechanism 45 is controlled by an electronic control unit (ECU) 46. The electronic control unit (ECU) 46 controls the pressure control mechanism 45 in cooperation with a hydraulic electronic control unit, a shift electronic control unit, an engine electronic control unit (all not shown), and the like.

  In this third embodiment, the kinetic energy due to the pressure of the exhaust gas generated in the engine 30 is converted into energy for applying pressure to a fluid such as oil or air by the pressure conversion mechanism 44 provided in the energy conversion device 43, The pressure is controlled by the pressure control mechanism 45 and supplied to the hydraulic chamber 15 (or 27). Then, the fluid actuated by the pressure conversion mechanism 44 is supplied to the pressure chamber, whereby the movable sheave 5 can be moved to change the speed ratio of the belt type continuously variable transmission. Therefore, the control of changing the gear ratio of the belt type continuously variable transmission can be performed without effectively losing power of the hydraulic pump or the like by effectively using the pressure of the exhaust gas discharged from the engine 30.

  The correspondence relationship between the embodiment described above and the present invention will be described below. The thrust imparting material according to claim 1 of the present application, ie, claim 1 in claims, corresponds to the weight roller 11 in the mechanical actuator 8 (or 21). The thrust applying chamber is surrounded by the back surface 5a of the movable sheave 5, the surface 10a (or 23a) of the fixed plate 10 (or 21), the boss portion 9 (or 22), and the extended portion 12 (or 24). It corresponds to the space formed.

  DESCRIPTION OF SYMBOLS 1 ... Rotating member, 3 ... Input shaft, 5 ... Movable part, 11 ... Thrust imparting material, 15 ... Fluid pressure chamber.

Claims (3)

A rotating member provided on an input shaft to which power is transmitted, a movable part provided in the rotating member and moving back and forth in the axial direction of the rotating member, and a pressing force for moving the movable part back and forth when fluid is supplied In a control device for a power transmission device, comprising: a fluid pressure chamber for applying a force; and a thrust applying material for applying a thrust for moving the movable portion back and forth by a centrifugal force generated by rotation of the rotating member.
The thrust imparting member is accommodated in a thrust imparting chamber provided in the movable portion, and the thrust imparting chamber and the fluid pressure chamber are isolated from each other.   2. The control device for a power transmission device according to claim 1, wherein the pressing force by the fluid pressure chamber and the thrust by the thrust imparting member act individually on the movable part.   The movable part is wound around a driving pulley provided on an input shaft to which power is transmitted, a driven pulley provided at a position facing the driving pulley, and the two pulleys, and outputs from a driving force source. A movable sheave provided in the drive pulley of a belt-type continuously variable transmission having a belt for transmitting torque, wherein a pressing force by a fluid pressure chamber acts on an outer peripheral side of the movable sheave. The control device for a power transmission device according to claim 1 or 2.

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