JP5939673B2 - Shift control device for toroidal transmission mechanism - Google Patents

Description

  The present invention relates to a transmission control device for controlling a hydraulic pressure supplied to a hydraulic actuator connected to a trunnion of a toroidal transmission mechanism to change a transmission ratio.

  In a toroidal transmission mechanism that changes the transmission ratio steplessly by tilting a power roller sandwiched between an input disk and an output disk, a pair of oil is provided on both sides of a piston of a hydraulic actuator connected to a trunnion that supports the power roller. Forming a chamber, increasing the hydraulic pressure of one of the oil chambers and decreasing the hydraulic pressure of the other chamber to drive the trunnion in the axial direction to change the gear ratio, and to counteract the reaction load applied to the trunnion from the power roller What is supported by the oil pressure of the oil chamber is known from Patent Document 1 below.

  The shift control valve that controls the hydraulic pressure supplied to the hydraulic actuator includes a spool that is driven by being connected to one end of a step motor. By connecting the other end of the spool to the trunnion via a precess cam, the displacement of the trunnion Is fed back to control the spool position to the target position.

JP 2001-200904 A

  By the way, the one described in Patent Document 1 includes a screw mechanism that converts the rotation output of the step motor into a reciprocating motion, a precess cam that transmits the displacement of the trunnion to the spool, and the like because the speed change control valve is configured by a spool valve. There is a problem that the number of parts increases and the weight and cost increase, and there is a possibility that the spool valve is locked by foreign matter contained in the oil.

  The present invention has been made in view of the above-described circumstances, and it is an object of the present invention to simplify the structure of a speed change control device that controls the operation of a hydraulic actuator that drives a trunnion and to increase the toughness of foreign matter contained in oil. .

In order to achieve the above object, according to the first aspect of the present invention, an input disk that rotates together with an input shaft, an output disk that is rotatably supported by the input shaft, the input disk, and the output disk A power roller sandwiched between the disks, a trunnion that supports the power roller, a hydraulic actuator that has a speed increasing oil chamber and a speed reducing oil chamber, and that drives the trunnion in the trunnion axial direction; and A shift control valve that controls the oil pressure supplied to the speed increasing oil chamber and the speed reducing oil chamber, and the hydraulic actuator drives the trunnion in the trunnion axis direction to swing the power roller about the trunnion axis. By changing the position of the contact point with the input disk and the output disk In the transmission control device for a toroidal transmission mechanism that changes a speed ratio, the transmission control valve includes a rotary valve fixed to the trunnion, a sleeve fitted to the outer periphery of the rotary valve, and the sleeve as the rotary valve. An electrical actuator that rotates at a predetermined angle with respect to the sleeve, wherein the sleeve has an input port to which oil is supplied, a first output port connected to the speed increasing oil chamber, a drain port from which oil is discharged, A second output port connected to the deceleration oil chamber in order in a circumferential direction, and the rotary valve is provided with a first control port and a first control port recessed in a circumferentially spaced position on an outer circumferential surface thereof. 2 control ports, the first control port is always in communication with the input port and can be in communication with one of the first and second output ports, 2 control port communicates with the drain port at all times and can communicate with the other of the first and second output ports, and when the rotary valve moves to one side in the trunnion axial direction, the first control port Is in communication with the first output port, the second control port is in communication with the second output port, and when the rotary valve moves to the other side in the trunnion axial direction, the first control port is in the second output port. It said second control port communicated to said first output port communicated with the output port, said first, side of the second output port is inclined with respect to the trunnion axis direction, the first, second The side of the control port is parallel to the sides of the first and second output ports, and the first and second control ports include an upper side and a lower side that are orthogonal to the trunnion axis direction. The first and second output ports include an upper side and a lower side orthogonal to the trunnion axis direction, and a pair of side sides inclined with respect to the trunnion axis direction. A pair of side edges inclined with respect to the trunnion axis direction and formed in a parallelogram shape, and the distance between the upper side and the lower side of the first and second control ports is the upper side of the first and second output ports. And when the rotary valve and the sleeve move relative to each other in the trunnion axis direction, the upper and lower sides of the first and second control ports are the upper sides of the first and second output ports. In addition, a shift control device for a toroidal transmission mechanism is proposed, which is characterized by moving between the lower sides .

According to the invention described in claim 2, the input disk that rotates together with the input shaft, the output disk that is rotatably supported by the input shaft, and the power that is sandwiched between the input disk and the output disk. A roller, a trunnion for supporting the power roller, a hydraulic actuator having a speed increasing oil chamber and a speed reducing oil chamber for driving the trunnion in the trunnion axial direction, the speed increasing oil chamber of the hydraulic actuator, A shift control valve for controlling the hydraulic pressure supplied to the deceleration oil chamber, the trunnion is driven in the trunnion axis direction by the hydraulic actuator, the power roller is swung around the trunnion axis, and the input disk and the Trojan that changes the gear ratio by changing the position of the contact point with the output disk In the shift control device of the gear-type transmission mechanism, the shift control valve includes a rotary valve fixed to the trunnion, a sleeve fitted to the outer periphery of the rotary valve, and the sleeve rotated by a predetermined angle with respect to the rotary valve. An electrical actuator for allowing the sleeve to be supplied with oil, a first output port connected to the speed increasing oil chamber, a drain port for discharging oil, and the speed reducing oil chamber And the second output port connected in turn in the circumferential direction, and the rotary valve includes a first control port and a second control port that are recessed in a circumferentially spaced position on the outer circumferential surface of the rotary valve. The first control port is always in communication with the input port and can be in communication with one of the first and second output ports. The second control port is The first control port is connected to the first output port when the rotary valve moves to one side in the trunnion axial direction. The second control port communicates with the second output port, and the first control port communicates with the second output port when the rotary valve moves to the other side in the trunnion axial direction. the second control port communicated to said first output port, said first, side of the second output port is inclined with respect to the trunnion axis direction, the first, side of the second control port wherein The first and second control ports are non-parallel to the sides of the first and second output ports, the upper and lower sides orthogonal to the trunnion axis direction, and the trunnion axis direction The first and second output ports are formed in a rectangular shape with a pair of side sides parallel to the direction, and the upper and lower sides orthogonal to the trunnion axis direction and the trunnion axis direction The first and second control ports are formed in a parallelogram shape, and the distance between the upper and lower sides of the first and second control ports is the distance between the upper and lower sides of the first and second output ports. The upper and lower sides of the first and second control ports move between the upper and lower sides of the first and second output ports when the rotary valve and the sleeve move relative to each other in the trunnion axis direction. A transmission control device for a toroidal type transmission mechanism is proposed.

According to the configuration of claim 1 or claim 2 , when the sleeve of the speed change control valve is rotated in one direction by the electric actuator, the oil supplied from the input port is hydraulically supplied via the first control port and the first output port. The trunnion is supplied to the acceleration oil chamber of the actuator and the oil in the deceleration oil chamber of the hydraulic actuator is discharged to the drain port via the second output port and the second control port, so that the trunnion is moved in one axial direction. Move to reduce gear ratio. On the contrary, when the sleeve of the speed change control valve is rotated in the other direction by the electric actuator, the oil supplied from the input port is supplied to the deceleration oil chamber via the first control port and the second output port, and the speed is increased. As the oil in the oil chamber is discharged to the drain port via the first output port and the second control port, the trunnion moves to the other side in the axial direction, and the gear ratio increases. When the trunnion moves to a new position corresponding to the rotational position of the sleeve in this way, the gear ratio of the toroidal transmission mechanism changes to a gear ratio corresponding to the new position of the trunnion.

  When the trunnion position deviates from the position determined by the rotational position of the sleeve, the sleeve and the rotary valve move relative to each other so that the first output port and the second output port communicate with the input port or the drain port, and the hydraulic actuator moves the trunnion position. When a load for returning to the original position corresponding to the rotational position of the sleeve is generated, the trunnion position is feedback-controlled to the target position.

  In this way, the trunnion position is directly fed back to the rotary valve of the speed change control valve, which eliminates the need for a conventional cam and reduces the number of parts, weight, installation space, cost, etc. The adjustment process for compensating the variation is simplified and the productivity is improved, and the hysteresis due to the friction between the parts is reduced, so that the control accuracy is improved. In addition, since a large reaction force received by the power roller from the input disk and output disk is transmitted to the rotary valve of the speed change control valve via the trunnion, the foreign matter that is one of the causes of the valve block between the rotary valve and the sleeve is caught. The toughness against the embedding is increased, and the reliability is improved.

In particular , according to the first aspect of the present invention, the sides of the first and second output ports are inclined with respect to the trunnion axis direction, and the sides of the first and second control ports are the first and second output ports. The opening area through which the first and second output ports and the first and second control ports communicate when the rotary valve and the sleeve move relative to each other in the trunnion axis direction or circumferential direction is Can be increased drastically, and the responsiveness of the feedback control can be improved.

In particular , according to the configuration of the second aspect, the sides of the first and second output ports are inclined with respect to the trunnion axis direction, and the sides of the first and second control ports are the first and second outputs. Since it is non-parallel to the side of the port, the first and second output ports and the first and second control ports communicate when the rotary valve and the sleeve move relative to each other in the trunnion axial direction or circumferential direction. The opening area can be increased slowly and the stability of the feedback control can be enhanced.

The skeleton figure of a toroidal type transmission mechanism. (First embodiment) The principal part enlarged view of FIG. (First embodiment) FIG. 3 is a sectional view taken along line 3-3 in FIG. 2. (First embodiment) The principal part enlarged view of FIG. (First embodiment) FIG. 5 is a sectional view taken along line 5-5 of FIG. (First embodiment) The 6A direction of FIG. 5 and the 6B direction arrow directional view. (First embodiment) Action explanatory drawing corresponding to FIG. (First embodiment) The exploded perspective view of the rotary valve and sleeve of a speed change control valve. (First embodiment) The operation explanatory view of a shift control valve. (First embodiment) The figure corresponding to FIG. (Second Embodiment) The figure corresponding to FIG. (Third embodiment)

First embodiment

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

  As shown in FIG. 1, a toroidal transmission mechanism T for an automobile includes an input shaft 13 connected to a crankshaft 11 of an engine E via a damper 12, and has substantially the same structure on the input shaft 13. The first continuously variable transmission mechanism 14F and the second continuously variable transmission mechanism 14R are supported. The first continuously variable transmission mechanism 14F includes a substantially cone-shaped input disk 15 fixed to the input shaft 13, and a substantially cone-shaped output disk 16 supported on the input shaft 13 so as to be relatively rotatable and axially slidable. And a pair of power rollers 19, 19 that are rotatably supported around the roller shaft 17 and are tiltably supported around the trunnion shafts 18, 18 and can come into contact with the input disk 15 and the output disk 16. . The opposing surfaces of the input disk 15 and the output disk 16 are formed of toroidal curved surfaces, and when the power rollers 19, 19 tilt around the trunnion shafts 18, 18, the power rollers 19, 19 with respect to the input disk 15 and the output disk 16 The contact point changes.

  The second continuously variable transmission mechanism 14R is disposed substantially in plane symmetry with the first continuously variable transmission mechanism 14F with the drive gear 20 in between, and the output disks of the first and second continuously variable transmission mechanisms 14F and 14R. 16, 16 and the drive gear 20 are integrally formed. However, the input disk 15 of the first continuously variable transmission mechanism 14F is fixed to the input shaft 13, whereas the input disk 15 of the second continuously variable transmission mechanism 14R is not rotatable relative to the input shaft 13 and moves in the axial direction. It is spline-coupled so as to be slidably fitted into a cylinder 35 formed at the left end of the input shaft 13. Therefore, when hydraulic pressure is supplied to the oil chamber 36 inside the cylinder 35, the input disk 15 of the second continuously variable transmission mechanism 14R and the output disks 16 and 16 of the first and second continuously variable transmission mechanisms 14F and 14R are: It is possible to generate a load that is pressed toward the input disk 15 of the first continuously variable transmission mechanism 14F and suppresses slipping between the input disks 15 and 15 and the output disks 16 and 16 and the power roller 19.

  As is clear from FIGS. 2 and 3, the first continuously variable transmission mechanism 14F (or the second continuously variable transmission mechanism 14R) includes a pair of left and right trunnions 21 and 21 arranged so as to sandwich the input shaft 13 therebetween. The lower part of each trunnion 21 is supported by a lower support plate 22 via a roller bearing 23 so as to be rotatable and slidable up and down. Further, one end of a pivot shaft 24 bent in a crank shape is rotatably supported on each trunnion 21, and the power roller 19 is rotatably supported on the other end of the pivot shaft 24.

  Piston rods 28, 28 of a pair of hydraulic actuators 27, 27 provided in the hydraulic control blocks 25, 26 are integrally formed at the lower ends of the trunnions 21, 21, respectively. Each hydraulic actuator 27 is divided into a cylinder 29 formed in the hydraulic control block 25, a piston 30 integrally formed with the piston rod 28 and slidably fitted into the cylinder 29, and a lower side of the piston 30. The speed increasing oil chamber 31 and a speed reducing oil chamber 32 partitioned on the upper side of the piston 30 are configured.

  Accordingly, when a high PH pressure is supplied to the speed increasing oil chamber 31 and a low pressure PL pressure is supplied to the deceleration oil chamber 32, the piston 30 and the piston rod 28 are raised, and conversely, the speed reducing oil chamber 32 is supplied to the speed reducing oil chamber 32. When a high PH pressure is supplied and a low PL pressure is supplied to the speed increasing oil chamber 31, the piston 30 and the piston rod 28 descend.

  The upper ends of a total of four trunnions 21 are pivotally supported at the four corners of the upper support plate 34 via spherical joints 33, respectively, and the two trunnions 21 and 21 are moved upward to the other two trunnions. When 21 and 21 move downward, their movements are synchronized.

  Next, the operation of the first continuously variable transmission mechanism 14F will be described. When the pair of trunnions 21, 21 are driven in opposite directions by the hydraulic actuators 27, 27, the power rollers 19, 19 tilt in the direction of arrow a in FIG. 1, and the contact point with the input disk 15 is relative to the input shaft 13. Since the contact point with the output disk 16 moves radially inward with respect to the input shaft 13, the rotation of the input disk 15 is accelerated and transmitted to the output disk 16. The speed ratio of the speed change mechanism T continuously decreases. On the other hand, when the power rollers 19, 19 tilt in the direction of arrow b in FIG. 1, the contact point with the input disk 15 moves radially inward with respect to the input shaft 13, and the contact point with the output disk 16 becomes the input point. Since it moves radially outward with respect to the shaft 13, the rotation of the input disk 15 is decelerated and transmitted to the output disk 16, and the gear ratio of the toroidal transmission mechanism T is continuously increased.

  The operation of the second continuously variable transmission mechanism 14R is the same as that of the first continuously variable transmission mechanism 14F described above, and the first and second continuously variable transmission mechanisms 14F and 14R perform a transmission operation in synchronization. Accordingly, the driving force input from the crankshaft 11 of the engine E to the input shaft 13 is steplessly shifted at an arbitrary speed ratio within the speed ratio range of the toroidal transmission mechanism T and output from the drive gear 20. .

  Next, the structure of the shift control valve V will be described with reference to FIGS.

  The shift control valve V includes a rotary valve 41 that is integrally fixed to the lower end of the piston rod 28, and a sleeve 42 that is fitted to the outer periphery of the rotary valve 41 so as to be relatively rotatable. The sleeve 42 is formed of a stepping motor. It is connected to the electric actuator 43 and can be rotated by a predetermined angle. Since the shift control valve V includes the rotary valve 41, it is not necessary to convert the rotational output of the electric actuator 43 into a reciprocating motion to drive the spool, and the structure can be simplified and the control accuracy can be improved.

  The sleeve 42 has an input port Pi connected to the PH hydraulic pressure source 44, a first output port Po1 connected to the speed increasing oil chamber 31 of the hydraulic actuator 27, and a drain port Pd connected to the PL hydraulic pressure source 45. The second output port Po2 connected to the deceleration oil chamber 32 of the hydraulic actuator 27 is sequentially formed in the circumferential direction so as to penetrate the sleeve 42 in the radial direction. The PH hydraulic power source 44 and the PL hydraulic power source 45 adjust the hydraulic pressure generated by the oil pump to a high PH pressure and a low PL pressure, and the PH pressure and the PL pressure are increased by the speed increasing oil chamber 31 and the speed reducing oil chamber 32, respectively. By selectively supplying to the hydraulic actuator 27, the hydraulic actuator 27 is driven by the differential pressure.

  In the present embodiment, two sets of the input port Pi, the first output port Po, the drain port Pd, and the second output port Po2 are provided for each central angle 180 ° of the sleeve 42. As apparent from FIGS. 6 and 8, the shapes of the input port Pi, the first output port Po, the drain port Pd, and the second output port Po2 are such that the upper side a and the lower side b are orthogonal to the trunnion shaft 18. The pair of sides c and d is inclined with respect to the trunnion shaft 18 to constitute a parallelogram.

  Since the sleeve 42 is rotated by the electric actuator 43, an oil passage 46 connecting the PH hydraulic pressure source 44 and the input port Pi, an oil passage 47 connecting the first output port Po1 and the speed increasing oil chamber 31, and a drain port Pd The oil passage 48 that connects the PL hydraulic pressure source 45 and the oil passage 49 that connects the second output port Po2 and the deceleration oil chamber 32 are configured by flexible pipes or the like.

  On the other hand, the first control port Pc1 and the second control port Pc2 are formed on the outer peripheral surface of the rotary valve 41 so as to be recessed from the outer surface in the circumferential direction. In the present embodiment, two sets of the first control port Pc1 and the second control port Pc2 are provided for each 180 ° central angle of the rotary valve 41. As apparent from FIGS. 6 and 8, the shapes of the first control port Pc1 and the second control port Pc2 are such that the upper side e and the lower side f are orthogonal to the trunnion shaft 18, and a pair of side sides g, h Are inclined with respect to the trunnion shaft 18 to form a parallelogram. The pair of sides c and d of the input port Pi, the first output port Po, the drain port Pd and the second output port Po2, and the pair of sides g and h of the first control port Pc1 and the second control port Pc2 They are parallel to each other.

  Next, the operation of the first embodiment of the present invention having the above configuration will be described.

  FIG. 5 shows a state in which the speed change control valve V is in the neutral position, and the first control port Pc1 connected to the PH hydraulic pressure source 44 via the input port Pi includes the first output port Po1 and the second output port Po2. And the second control port Pc2 connected to the PL hydraulic power source 45 via the drain port Pd is disconnected from both the first output port Po1 and the second output port Po2. As a result, both the speed increasing oil chamber 31 and the speed reducing oil chamber 32 of the hydraulic actuator 27 are closed, and the trunnion 21 is stopped and the gear ratio is kept constant.

  When the sleeve 42 of the speed change control valve V is rotated clockwise by the electric actuator 43 as shown in FIG. 7A from this neutral state, the first valve of the rotary valve 41 is shown in FIG. 6A. The control port Pc1 rotates relative to the sleeve 42 in the direction of arrow A, and the first control port Pc1 and the first output port Po1 communicate with each other in the region S1, and as shown in FIG. 6B, the rotary valve 41 The second control port Pc2 rotates relative to the sleeve 42 in the direction of arrow B, and the second control port Pc2 and the second output port Po2 communicate with each other in the region S2. As a result, the PH hydraulic pressure source 44 communicates with the speed increasing oil chamber 31 through the path of the input port Pi → the first control port Pc1 → the first output port Po1, and the speed reducing oil chamber 32 is connected with the second output port Po2 → the second output port Po2. 2 Since the control oil is connected to the PL oil pressure source 45 through the route of the control port Pc2 → the drain port Pd, the speed increasing oil chamber 31 becomes high pressure and the speed reducing oil chamber 32 becomes low pressure in FIG. The piston 30 of the actuator 27 rises together with the trunnion 21.

  At this time, since the power roller 19 receives torque around the trunnion shaft 18 due to the reaction force from the input disk 15 and the output disk 16, the trunnion 21 rotates in one direction while ascending, and the input disk 15 and output of the power roller 19 As the contact point with the disk 16 changes, the gear ratio changes in the speed increasing direction (decreasing direction).

  Conversely, when the sleeve 42 of the speed change control valve V is rotated counterclockwise by the electric actuator 43 as shown in FIG. 7B from the neutral state, as shown in FIG. 6A, the rotary valve 41 is turned on. The first control port Pc1 rotates relative to the sleeve 42 in the direction of arrow B, and the first control port Pc1 and the second output port Po2 communicate with each other in the region S2, as shown in FIG. The second control port Pc2 of the rotary valve 41 rotates relative to the sleeve 42 in the direction of arrow A, and the second control port Pc2 and the first output port Po1 communicate with each other in the region S1. As a result, the PH hydraulic pressure source 44 communicates with the deceleration oil chamber 32 through the path of the input port Pi → the first control port Pc1 → the second output port Po2, and the speed increase oil chamber 31 communicates with the first output port Po1 → the second output port Po2. 2 Since the control oil is connected to the PL oil pressure source 45 through the path of the control port Pc2 → the drain port Pd, the speed increasing oil chamber 31 becomes low pressure and the speed reducing oil chamber 32 becomes high pressure in FIG. The piston 30 of the actuator 27 moves down together with the trunnion 21.

  At this time, since the power roller 19 receives torque around the trunnion shaft 18 due to the reaction force from the input disk 15 and the output disk 16, the trunnion 21 rotates in the other direction while descending, and the input disk 15 and output of the power roller 19 As the contact point with the disk 16 changes, the gear ratio changes in the deceleration direction (increase direction).

  Next, the above operation will be described more specifically with reference to FIG.

  FIG. 9A shows a cruising state at a constant gear ratio. When the power roller 19 receives the downward reaction force Fr from the input disk 15 and the output disk 16, the trunnion 21 is urged downward while rotating. Is done. In order to keep the transmission ratio constant, it is necessary that the hydraulic actuator 27 urges the trunnion 21 upward against the downward reaction force Fr to keep the position constant. However, when the trunnion 21 is urged downward while rotating, the rotary valve 41 connected to the trunnion 21 has the first control port Pc1 communicating with the first output port Po1 and the second control port Pc2 being the first. In order to communicate with the 2-output port Po2 (see the region S4 in FIGS. 6A and 6B), the speed increasing oil chamber 31 on the lower side of the hydraulic actuator 27 becomes high pressure, and the upper speed reducing oil chamber 32 The trunnion 21 is biased upward by the differential pressure and balanced with the reaction force Fr, so that the position of the trunnion 21 is determined and the transmission ratio is kept constant.

  As shown in FIG. 9B, for example, when the sleeve 42 is rotated by an electric actuator to increase the gear ratio, the first control port Pc1 communicates with the first output port Po1, and the second control port Pc2 As shown in FIG. 9C, the speed increasing oil chamber 31 of the hydraulic actuator 27 becomes high pressure and the speed reducing oil chamber 32 becomes low pressure, and the differential pressure causes the trunnion 21 to communicate with the two output ports Po2. Is increased by being biased upward, and the speed ratio changes in an increasing direction.

  At this time, since the trunnion 21 rotates while rising, the rotary valve 41 of the speed change control valve V also rotates while rising (see FIG. 9C), and eventually the first control port Pc1 and the first output port Po1. When the communication is cut off and the communication between the second control port Pc2 and the second output port Po2 is cut off, the trunnion 21 stops at a position corresponding to the new gear ratio, and the shift is completed.

  When the rising trunnion 21 further rises due to inertia and overshoots the original stop position, the first control port Pc1 communicates with the second output port Po2 as shown in FIG. 2 Since the control port Pc2 communicates with the first output port Po1 (see the region S3 in FIGS. 6A and 6B), the speed increasing oil chamber 31 of the hydraulic actuator 27 becomes low pressure and the speed reducing oil chamber 32 becomes high pressure. As a result, as shown in FIG. 9 (E), the trunnion 21 is biased downward by the differential pressure and descends, so that the overshoot trunnion 21 is pushed back to the original stop position, and a new gear ratio is obtained. Stops automatically at the corresponding position.

  Thus, when the trunnion 21 is raised / lowered while rotating, the rotary valve 41 of the speed change control valve V is raised / lowered while rotating and the positional relationship with the sleeve 42 changes accordingly. Since the position is fed back to the transmission control valve V, the position of the trunnion 21 by the transmission control valve V, that is, the transmission ratio of the toroidal transmission mechanism T can be feedback-controlled with high accuracy.

  In addition, since the position of the trunnion 21 is directly fed back to the rotary valve 41 of the speed change control valve V, the conventional precess cam is not required, and not only the number of parts, weight, installation space, and cost can be reduced, but also the accuracy between the parts can be improved. The adjustment process for compensating the variation is simplified and the productivity is improved, and the hysteresis due to the friction between the parts is reduced, so that the control accuracy is improved.

  Further, since the large reaction force received by the power roller 19 from the input disk 15 and the output disk 16 is transmitted to the rotary valve 41 of the transmission control valve V via the trunnion 21, the cause of the valve block between the rotary valve 41 and the sleeve 42 is caused. The toughness with respect to the biting of a foreign substance, which is one of the above, becomes high, and its reliability is improved.

Second embodiment

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the first embodiment shown in FIG. 6, the first control port Pc1 and the second control port Pc2 of the rotary valve 41 of the speed change control valve V are parallelograms, and the sides g and h are relative to the trunnion shaft 18. In the second embodiment shown in FIG. 10, the first control port Pc <b> 1 and the second control port Pc <b> 2 are rectangular, and the sides g and h are parallel to the trunnion shaft 18.

  In the first embodiment, when the rotary valve 41 moves in the direction of the trunnion shaft 18 or the circumferential direction with respect to the sleeve 42, the first control port Pc1 or the second control port Pc2 becomes the first output port Po1 or the second output port Po1. While the opening area communicating with the output port Po2 increases rapidly, in the second embodiment, the opening area increases slowly. Accordingly, the first embodiment has a characteristic that the feedback control responsiveness is high and the stability is low, while the second embodiment has low feedback control responsiveness and high stability. There is a characteristic. Therefore, the shapes of the first control port Pc1 and the second control port Pc2 of the first and second embodiments may be selected according to the required characteristics.

Third embodiment

  Next, a third embodiment of the present invention will be described with reference to FIG.

  In the first embodiment shown in FIG. 5, the first control port Pc1 and the second control port Pc2 of the rotary valve 41 of the speed change control valve V, the input port Pi of the sleeve 42, the first output port Po1, and the second output port. Two Po2s and two drain ports Pd are provided, but it is sufficient that at least one of these ports is provided as in the third embodiment shown in FIG.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, the toroidal transmission mechanism T of the embodiment is of a double cavity type, but may be of a single cavity type.

13 Input shaft 15 Input disk 16 Output disk 18 Trunnion shaft 19 Power roller 21 Trunnion 27 Hydraulic actuator 31 Oil chamber for acceleration 32 Oil chamber for deceleration 41 Rotary valve 42 Sleeve 43 Electric actuator Pc1 First control port Pc2 Second control port Pd Drain port Pi Input port Po1 First output port Po2 Second output port V Shift control valve
a first, upper side of the second output port
b Lower side of the first and second output ports c Side of the first and second output ports d Side of the first and second output ports
e Upper side of the first and second control ports
f lower side of first and second control ports g side of first and second control ports h side of first and second control ports

Claims (2)

An input disk (15) that rotates together with the input shaft (13), an output disk (16) that is rotatably supported by the input shaft (13), and the input disk (15) and the output disk (16). The trunnion (21), the trunnion (21) supporting the power roller (19), the speed increasing oil chamber (31), and the speed reducing oil chamber (32). ) In the direction of the trunnion shaft (18), and the hydraulic pressure supplied to the speed increasing oil chamber (31) and the speed reducing oil chamber (32) of the hydraulic actuator (27) is controlled. A shift control valve (V), and the hydraulic actuator (27) drives the trunnion (21) in the direction of the trunnion shaft (18). Shifting the toroidal transmission mechanism that changes the gear ratio by swinging (19) around the trunnion shaft (18) and changing the position of the contact point between the input disk (15) and the output disk (16). In the control device,
The shift control valve (V) includes a rotary valve (41) fixed to the trunnion (21), a sleeve (42) fitted to the outer periphery of the rotary valve (41), and the sleeve (42). An electric actuator (43) that rotates a predetermined angle with respect to the rotary valve (41),
The sleeve (42) includes an input port (Pi) through which oil is supplied, a first output port (Po1) connected to the speed increasing oil chamber (31), and a drain port (Pd) through which oil is discharged. And a second output port (Po2) connected to the deceleration oil chamber (32) in order in the circumferential direction,
The rotary valve (41) includes a first control port (Pc1) and a second control port (Pc2) that are recessed at positions spaced apart in the circumferential direction on the outer peripheral surface thereof.
The first control port (Pc1) always communicates with the input port (Pi) and can communicate with one of the first and second output ports (Po1, Po2), and the second control port (Pc2). Can communicate with the drain port (Pd) at all times and with the other of the first and second output ports (Po1, Po2).
When the rotary valve (41) moves to one side in the direction of the trunnion shaft (18), the first control port (Pc1) communicates with the first output port (Po1) and the second control port (Pc2). ) Communicates with the second output port (Po2), and when the rotary valve (41) moves to the other side in the direction of the trunnion shaft (18), the first control port (Pc1) becomes the second output port. the second control port communicated with the (Po2) (Pc2) is in communication with the first output port (Po1),
The sides (c, d) of the first and second output ports (Po1, Po2) are inclined with respect to the direction of the trunnion axis (18), and the first and second control ports (Pc1, Pc2) The sides (g, h) are parallel to the sides (c, d) of the first and second output ports (Po1, Po2),
The first and second control ports (Pc1, Pc2) are inclined with respect to the upper side (e) and the lower side (f) orthogonal to the direction of the trunnion axis (18) and the direction of the trunnion axis (18). A parallelogram having a pair of side edges (g, h),
The first and second output ports (Po1, Po2) are inclined with respect to the upper side (a) and the lower side (b) orthogonal to the direction of the trunnion axis (18) and the direction of the trunnion axis (18). A parallelogram having a pair of side edges (c, d);
The distance between the upper side (e) and the lower side (f) of the first and second control ports (Pc1, Pc2) is the upper side (a) and the lower side (b) of the first and second output ports (Po1, Po2). ) Less than the distance between
When the rotary valve (41) and the sleeve (42) are relatively moved in the direction of the trunnion shaft (18), the upper side (e) and the lower side (f) of the first and second control ports (Pc1, Pc2) are A shift control device for a toroidal transmission mechanism, wherein the shift control device moves between the upper side (a) and the lower side (b) of the first and second output ports (Po1, Po2) . An input disk (15) that rotates together with the input shaft (13), an output disk (16) that is rotatably supported by the input shaft (13), and the input disk (15) and the output disk (16). The trunnion (21), the trunnion (21) supporting the power roller (19), the speed increasing oil chamber (31), and the speed reducing oil chamber (32). ) In the direction of the trunnion shaft (18), and the hydraulic pressure supplied to the speed increasing oil chamber (31) and the speed reducing oil chamber (32) of the hydraulic actuator (27) is controlled. A shift control valve (V), and the hydraulic actuator (27) drives the trunnion (21) in the direction of the trunnion shaft (18). Shifting the toroidal transmission mechanism that changes the gear ratio by swinging (19) around the trunnion shaft (18) and changing the position of the contact point between the input disk (15) and the output disk (16). In the control device,
The shift control valve (V) includes a rotary valve (41) fixed to the trunnion (21), a sleeve (42) fitted to the outer periphery of the rotary valve (41), and the sleeve (42). An electric actuator (43) that rotates a predetermined angle with respect to the rotary valve (41),
The sleeve (42) includes an input port (Pi) through which oil is supplied, a first output port (Po1) connected to the speed increasing oil chamber (31), and a drain port (Pd) through which oil is discharged. And a second output port (Po2) connected to the deceleration oil chamber (32) in order in the circumferential direction,
The rotary valve (41) includes a first control port (Pc1) and a second control port (Pc2) that are recessed at positions spaced apart in the circumferential direction on the outer peripheral surface thereof.
The first control port (Pc1) always communicates with the input port (Pi) and can communicate with one of the first and second output ports (Po1, Po2), and the second control port (Pc2). Can communicate with the drain port (Pd) at all times and with the other of the first and second output ports (Po1, Po2).
When the rotary valve (41) moves to one side in the direction of the trunnion shaft (18), the first control port (Pc1) communicates with the first output port (Po1) and the second control port (Pc2). ) Communicates with the second output port (Po2), and when the rotary valve (41) moves to the other side in the direction of the trunnion shaft (18), the first control port (Pc1) becomes the second output port. (Po2) and the second control port (Pc2) communicates with the first output port (Po1) ,
The sides (c, d) of the first and second output ports (Po1, Po2) are inclined with respect to the direction of the trunnion axis (18), and the first and second control ports (Pc1, Pc2) The side (g, h) is non-parallel to the side (c, d) of the first and second output ports (Po1, Po2),
The first and second control ports (Pc1, Pc2) are parallel to the trunnion axis (18) and the upper side (e) and the lower side (f) orthogonal to the direction of the trunnion axis (18). A rectangular shape having a pair of side edges (g, h),
The first and second output ports (Po1, Po2) are inclined with respect to the upper side (a) and the lower side (b) orthogonal to the direction of the trunnion axis (18) and the direction of the trunnion axis (18). A parallelogram having a pair of side edges (c, d);
The distance between the upper side (e) and the lower side (f) of the first and second control ports (Pc1, Pc2) is the upper side (a) and the lower side (b) of the first and second output ports (Po1, Po2). ) Less than the distance between
When the rotary valve (41) and the sleeve (42) are relatively moved in the direction of the trunnion shaft (18), the upper side (e) and the lower side (f) of the first and second control ports (Pc1, Pc2) are A shift control device for a toroidal transmission mechanism, wherein the shift control device moves between the upper side (a) and the lower side (b) of the first and second output ports (Po1, Po2) .

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