WO2011118317A1 - Power transmission device and control method therefor - Google Patents
Power transmission device and control method therefor Download PDFInfo
- Publication number
- WO2011118317A1 WO2011118317A1 PCT/JP2011/053862 JP2011053862W WO2011118317A1 WO 2011118317 A1 WO2011118317 A1 WO 2011118317A1 JP 2011053862 W JP2011053862 W JP 2011053862W WO 2011118317 A1 WO2011118317 A1 WO 2011118317A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- output
- input
- torque
- slide
- shaft
- Prior art date
Links
Images
Classifications
-
- 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
- F16H61/664—Friction gearings
- F16H61/6649—Friction gearings characterised by the means for controlling the torque transmitting capability of the gearing
-
- 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
- F16H61/664—Friction gearings
- F16H61/6648—Friction gearings controlling of shifting being influenced by a signal derived from the engine and the main coupling
-
- 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
- F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
- F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
- F16H15/04—Gearings providing a continuous range of gear ratios
- F16H15/42—Gearings providing a continuous range of gear ratios in which two members co-operate by means of rings or by means of parts of endless flexible members pressed between the first mentioned members
Definitions
- the present invention relates to a power transmission device and a control method thereof.
- the input cone connected to the input shaft and the output cone connected to the output shaft are arranged in parallel opposite to each other, and the torque acting on the output shaft is adjusted with a narrow pressure.
- a continuously variable transmission that narrows a ring with both cones by converting it into an axial force by a mechanism and acting on an output cone (for example, see Patent Document 1).
- the power input to the input shaft is output to the output shaft with a change in the gear ratio by sliding the ring.
- the main purpose of the power transmission device and the control method thereof according to the present invention is to suppress deformation of the input member.
- the power transmission device and the control method thereof according to the present invention employ the following means in order to achieve the main object described above.
- the power transmission device of the present invention is A power transmission device having an input shaft and an output shaft arranged in parallel to the input shaft, and comprising a continuously variable transmission that continuously shifts the power input to the input shaft and outputs the power to the output shaft.
- a conical input member connected to the input shaft;
- a conical output member connected to the output shaft and disposed opposite to the input member;
- Narrow pressure adjusting means for adjusting the narrow pressure acting on the transmission member in a tendency to increase as the output torque that is the torque acting on the output shaft increases.
- Position acquisition means for acquiring the position of the transmission member;
- Output torque acquisition means for acquiring the output torque;
- Slide control means for controlling the slide means to slide; It is a summary to provide.
- the transmission member when the position of the transmission member is within a predetermined range including the large-diameter end of the output member and the output torque that is the torque acting on the output shaft is equal to or greater than the predetermined torque, the transmission member is The sliding means is controlled to slide to the small diameter side of the output member. As a result, the reduction ratio is reduced and the output torque is reduced, so that the force acting on the input member from the output shaft through the narrow pressure adjusting means, the output member, and the ring can be reduced, and the deformation of the input member is suppressed. can do.
- the “predetermined torque” may be a torque that is predetermined as a lower limit of the output torque that may cause the input member to be deformed or a slightly smaller torque, or at least one of the transmission members.
- the lower limit of the torque that may cause the portion to protrude from the output member (the contact area between the transmission member and the output member becomes small) or a slightly smaller torque may be used.
- the “predetermined range” may be a range that is determined in advance as a range in which torque that may cause deformation of the input member can act on the output shaft, and at least a part of the transmission member outputs It is also possible to set a predetermined range as a range in which a torque that may protrude from the member can act on the output shaft.
- the slide control means is a means for controlling the slide means so that the transmission member slides toward the small diameter side of the output member by a distance equal to or greater than the movable distance of the output member. It can also be. In this way, it is possible to more reliably suppress at least a part of the transmission member from protruding from the output member due to deformation of the input member.
- the slide control means controls the slide means so that the transmission member slides toward the smaller diameter side of the output member by a distance that tends to increase as the acquired output torque increases. It can also be a means to do. By doing so, the transmission member can be slid by a distance corresponding to the output torque.
- the power transmission device control method of the present invention includes: A conical input member connected to the input shaft, a conical output member connected to the output shaft and disposed in the direction opposite to the input member, and the input member and the output member are subjected to a narrow pressure.
- An annular transmission member that transmits power between the member and the output member, slide means that can change a gear ratio by sliding the transmission member, and output torque that is torque acting on the output shaft
- a narrow pressure adjusting means for adjusting a narrow pressure acting on the transmission member so as to increase as it increases, continuously changing the power input to the input shaft and outputting it to the output shaft.
- a method for controlling a power transmission device including a transmission When the position of the transmission member is within a predetermined range including the large-diameter end of the output member and the output torque is equal to or greater than a predetermined torque, the sliding means is configured to slide the transmission member to the small-diameter side of the output member. To control the It is characterized by that.
- the sliding means is controlled so that the transmission member slides to the small diameter side of the output member.
- the reduction ratio is reduced and the output torque is reduced, so that the force acting on the input member from the output shaft through the narrow pressure adjusting means, the output member, and the ring can be reduced, and the deformation of the input member is suppressed. can do.
- the “predetermined torque” may be a torque that is predetermined as a lower limit of the output torque that may cause the input member to be deformed or a slightly smaller torque, or at least one of the transmission members.
- the lower limit of the torque that may cause the portion to protrude from the output member (the contact area between the transmission member and the output member becomes small) or a slightly smaller torque may be used.
- the “predetermined range” may be a range that is determined in advance as a range in which torque that may cause deformation of the input member can act on the output shaft, and at least a part of the transmission member outputs It is also possible to set a predetermined range as a range in which a torque that may protrude from the member can act on the output shaft.
- FIG. 3 is a configuration diagram showing an outline of a configuration of a slide mechanism 62.
- FIG. 2 is a configuration diagram showing an outline of a configuration of a narrow pressure adjusting mechanism 50.
- FIG. 4 is a flowchart illustrating an example of a control routine for an output member maximum diameter executed by an electronic control unit 90. It is explanatory drawing which shows an example of the map for target slide distance setting.
- FIG. 1 is a configuration diagram showing an outline of a configuration of an automobile 10 equipped with a power transmission device 20 as an embodiment of the present invention.
- an automobile 10 according to the embodiment includes an engine 12 as an internal combustion engine that outputs power by explosion combustion of a hydrocarbon-based fuel such as gasoline or light oil, and left and right wheels by shifting power from the engine 12.
- a power transmission mechanism 20a for transmitting to 88a and 88b and an electronic control unit 90 for controlling the entire vehicle are provided.
- the power transmission device 20 of the embodiment corresponds to the power transmission mechanism 20a and the electronic control unit 90.
- the power transmission mechanism 20a is configured as a transaxle device that shifts the power input from the engine 12 via a starter (not shown) (for example, a torque converter) and transmits the power to the left and right wheels 88a, 88b. 2, a forward / reverse switching mechanism 24 connected to the output shaft 22 of the starting device and outputting power from the starting device with switching between forward rotation and reverse rotation, and an input connected to the forward / backward switching mechanism 24.
- a starter for example, a torque converter
- a CVT 30 as a continuously variable transmission that has a shaft 32 and an output shaft 38 disposed in parallel to the input shaft 32, and continuously shifts the power input to the input shaft 32 and outputs it to the output shaft 38; Connected to the output shaft 38 of the CVT 30 via the reduction gear 26 and connected to the left and right front wheels.
- a differential gear 28 which are accommodated in a case 21 made of a transaxle housing 21a and the converter housing 21b and the rear case 21c.
- a partition plate 21d that partitions a space in which the forward / reverse switching mechanism 24 and the differential gear 28 are disposed from a space in which the CVT 30 is disposed is provided inside the case 21.
- the forward / reverse switching mechanism 24 includes a double pinion planetary gear mechanism, a brake B1, and a clutch C1.
- the planetary gear mechanism of the double pinion includes an external gear sun gear 24a, an internal gear ring gear 24b arranged concentrically with the sun gear 24a, a plurality of first pinion gears meshed with the sun gear 24a, and the first pinion gear.
- a plurality of second pinion gears that mesh with each other and mesh with the ring gear 24b are coupled to each other and a carrier 24c that rotates and revolves freely.
- the sun gear 24a has an output shaft 22, and the carrier 24c has an input shaft 32 of the CVT 30. Each is connected.
- the ring gear 24b of the planetary gear mechanism is connected to the case 21 by a brake B1, and the ring gear 24b can be freely rotated or prohibited from rotating by turning on and off the brake B1.
- the sun gear 24a and the carrier 24c of the planetary gear mechanism are connected by a clutch C1, and the sun gear 24a and the carrier 24c are connected or disconnected by turning on and off the clutch C1.
- the forward / reverse switching mechanism 24 turns off the brake B1 and turns on the clutch C1 to transmit the rotation of the output shaft 22 to the input shaft 32 of the CVT 30 as it is to advance the vehicle or turn on the brake B1 and turn on the clutch C1.
- the rotation of the output shaft 22 is converted in the reverse direction and transmitted to the input shaft 32 of the CVT 30 to reverse the vehicle. Further, the output shaft 22 and the input shaft 32 of the CVT 30 can be disconnected by turning off the brake B1 and turning off the clutch C1.
- the forward / reverse switching mechanism 24 is constituted by a double-pinion planetary gear mechanism, a brake B1, and a clutch C1, but is constituted by a single-pinion planetary gear mechanism instead of the double-pinion planetary gear mechanism. It is good also as what is carried out and it is good also as what shall be set as another structure.
- the CVT 30 includes a conical input cone 34 integrally formed with an input shaft 32, and an output cone 36 that is substantially the same shape as the input cone 34 and is connected to the output shaft 38 so as to be opposite to the input cone 34.
- the ring 60 is inserted into the input cone 34 and is sandwiched between the input cone 34 and the output cone 36, and a slide mechanism 62 (see FIG. 4) that supports the ring 60 rotatably and allows the ring 60 to slide.
- a narrow pressure adjusting mechanism 50 for adjusting the narrow pressure applied to the ring 60 between the input cone 34 and the output cone 36, and the power from the input shaft 32 is generated by sliding the ring 60 by the slide mechanism 62. Change the output steplessly to output And outputs to shift 38.
- FIG. 3 shows how the CVT 30 shifts.
- the ring 60 is slid to the front side (left side in FIG. 2) to shift the power from the input cone 34 with a relatively small reduction ratio and transmit it to the output cone 36.
- the power from the input cone 34 is shifted with a relatively large reduction ratio and transmitted to the output cone 36.
- the input cone 34 and the input shaft 32 are rotatable by a bearing 41 formed as a cylindrical roller bearing which is attached to the partition plate 21d at the right end in FIG. 2 and cannot receive a thrust force but can receive a relatively large radial force. And at the left end is rotatably supported by a bearing 42 formed as a tapered roller bearing attached to the transaxle housing 21a and capable of receiving a thrust force.
- the output cone 36 is rotatably supported by a bearing 45 which is attached to the partition plate 21d and formed as a cylindrical roller bearing at the right end in FIG. 2, and is attached to the transaxle housing 21a and formed as a cylindrical roller bearing at the left end.
- the bearing 46 is rotatably supported.
- the output shaft 38 connected to the output cone 36 is rotatably supported by a bearing 49 which is attached to the converter housing 21b and formed as a tapered roller bearing at the right end in FIG.
- the slide mechanism 62 extends substantially parallel to the sliding direction of the ring 60 and is fitted to the guide rail 64 as a feed screw that is rotatably supported by the transaxle housing 21a.
- a slider 66 that has a fitting portion to be fitted and can move along the guide rail 64 without rotating when the guide rail 64 rotates, and is attached to the slider 66 so as to be swingable in the extending direction of the guide rail 64 and U
- a holding portion 68 that rotatably holds the ring 60 from the side surface by a U-shaped portion having a letter shape, and a motor 70 that rotates the guide rail 64 with a rotating shaft connected to one end of the guide rail 64.
- the guide rail 64 is rotated by the rotational drive of the motor 70, and the slider 66 is moved along the guide rail 64, whereby the ring 60 is moved to the front side (left side in FIG. 2) or the rear side in the figure. Slide to the side (right side in FIG. 2).
- the narrow pressure adjusting mechanism 50 is built in the output cone 36, and adjusts the narrow pressure acting on the ring 60 by the input cone 34 and the output cone 36 by a mechanical mechanism.
- FIG. 5 is a block diagram showing an outline of the configuration of the narrow pressure adjusting mechanism 50
- FIG. 6 is a partially enlarged view of the narrow pressure adjusting mechanism 50 partially enlarged.
- the narrow pressure adjusting mechanism 50 is a fixing member that is spline-fitted to a spline formed at the tip of the output shaft 38 and fixed to the output shaft 38 so as not to move in the axial direction.
- a moving member 54 that is spline-fitted to a spline formed on the inner peripheral surface of the output cone 36 and is formed so as to be movable in the axial direction together with the output cone 36, and a fixed member 52.
- a spring 58 for urging the moving member 54 in the axial direction with the fixing member 52 as a spring receiver, and attached to the output cone 36
- a support member 59 that supports the output cone 36 so as to be movable in the axial direction with respect to the output shaft 38, and converts the torque acting on the output shaft 38 into an axial force to act on the output cone 36.
- the narrow pressure of the ring 60 is adjusted.
- the ball receiver 52 a of the fixing member 52 and the ball receiver 54 b of the moving member 54 are just opposite to each other.
- no force is received (see FIG. 6A)
- a torque is applied to the output shaft 38
- a twist is generated between the ball receiver 52a of the fixing member 52 and the ball receiver 54a of the moving member 54, thereby fixing the member 52.
- a force for pushing out the moving member 54 with the ball 56 is generated using the reaction force from (see FIG. 6B).
- the output cone 36 is attached to the moving member 54, the output cone 36 is pushed out as the moving member 54 moves.
- the force that pushes out the output cone 36 increases as the torque acting on the output shaft 38 increases, whereby the narrow pressure of the ring 60 is adjusted. Therefore, since the torque acting on the output shaft 38 increases as the speed reduction ratio with respect to the torque input to the input shaft 32 increases, the CVT 30 is adjusted so that the narrow pressure of the ring 60 increases as the speed reduction ratio increases. Will be.
- the electronic control unit 90 is configured as a microprocessor centered on a CPU. In addition to the CPU, a ROM that stores a processing program, a RAM that temporarily stores data, an input / output port, and a communication port are provided. Prepare.
- the electronic control unit 90 includes signals from various sensors that detect the operating state of the engine 12, and ring positions Pr from a position detection sensor 72 (see FIG. 4) that is attached to the slider 66 and detects the position of the ring 60.
- Shift position sensor for detecting the rotational speed of the input shaft 32 from the rotational speed sensor attached to the input shaft 32, the rotational speed of the output shaft 38 from the rotational speed sensor attached to the output shaft 38, and the operating position of the shift lever 91
- a vehicle speed V from a speed sensor 98 is input through the input port.
- a control signal to the engine 12 a control signal to the clutch C1 and the brake B1 of the forward / reverse switching mechanism 24, a control signal to the motor 70 of the slide mechanism 62 of the CVT 30, and the like are output via the output port. It is output.
- FIG. 7 is a flowchart illustrating an example of the control routine for the maximum output member diameter executed by the electronic control unit 90. This routine is repeatedly executed at predetermined time intervals (for example, every several msec) when the change of the transmission ratio of the CVT 30 is not requested at the maximum output member diameter. Whether or not the maximum diameter of the output member is reached can be determined using the ring position Pr from the position detection sensor 72.
- the CPU of the electronic control unit 90 first inputs an input torque Tin as a torque input to the input shaft 32 (step S100), and based on the input torque Tin.
- An output torque Tout as a torque acting on the output shaft 38 is estimated (step S110).
- the input torque Tin a value estimated based on the operating state of the engine 12 (rotation speed, intake air amount, etc.) is used.
- the output torque Tout is determined in advance by experiment or analysis and stored in a ROM (not shown) as a map in relation to the reduction ratio of the input torque Tin and the CVT 30 and the output torque Tout. When the ratio is given, the corresponding output torque Tout is derived and set from the stored map. Since the maximum diameter of the output member is considered now, the maximum reduction ratio can be used as the reduction ratio.
- the output torque Tout is compared with a threshold value Tref (step S120).
- the threshold value Tref is set so that at least a part of the ring 60 has a lower limit of the output torque Tout at which the input cone 34 may be deformed or slightly smaller than the output torque Tout, deformation of the input cone 34, etc.
- a large force is applied to the input cone 34 from the output shaft 38 via the narrow pressure adjusting mechanism 50, the output cone 36, and the ring 60. May cause the input cone 34 to be deformed, leading to a reduction in power transmission performance, or at least a part of the ring 60 to protrude from the output cone 36.
- the comparison between the output torque Tout and the threshold value Tref in step S120 is processing for determining whether or not there is such a possibility.
- the strength of the input cone 34 may be improved. In this case, however, the input cone 34 is increased in size and weight.
- the movable distance Lomax is set to the position (reference position) of the output cone 36 when no torque acts on the output shaft 38 (when the output cone 36 is not pushed out by the narrow pressure adjusting mechanism 50).
- this is the maximum distance that the output cone 36 can move by receiving the force from the narrow pressure adjusting mechanism 50, and the positional relationship between the output cone 36 and the case 21, the bearing 46, etc.
- a distance determined in advance through experiments, analysis, or the like based on the distance that the toe cone 36 can be moved can be used.
- the output torque Tout is equal to or greater than the threshold Tref at the maximum diameter of the output member, sliding the ring 60 to the smaller diameter side of the output cone 36 reduces the reduction ratio and decreases the output torque Tout.
- the force acting on the input cone 34 from the shaft 38 via the narrow pressure adjusting mechanism 50, the output cone 36, and the ring 60 can be reduced, and deformation of the input cone 34 can be suppressed.
- the output torque Tout as the torque acting on the output shaft 38 when the position of the ring 60 is the maximum diameter of the output member that is the large diameter side end of the output cone 36 is as follows.
- the ring 60 is slid to the smaller diameter side of the output cone 36, so that the deformation of the input cone 34 can be suppressed.
- the ring 60 is slid to the smaller diameter side of the output cone 36 by a predetermined distance Ls1 longer than the movable distance Lomax of the output cone 36, so that the ring 60 is more sure to protrude from the output cone 36. Can be suppressed.
- the operation when the position of the ring 60 is the large diameter side end portion of the output cone 36 has been described.
- the operation is not limited to this, and the position of the ring 60 is the large size of the output cone 36.
- the predetermined range is a range in which a torque that may cause deformation of the input cone 34 can act on the output shaft 38, or at least a part of the ring 60 can protrude from the output cone 36 due to deformation of the input cone 34.
- a range in which a characteristic torque can act on the output shaft 38 can be determined and used in advance by experiment or analysis.
- the ring 60 obtained based on the specifications of the engine 12 or the reduction ratio at each position of the ring 60 can be used. Can be determined based on the maximum value of the output torque Tout for each of these positions, the specifications of the input cone 34, the output cone 36, the narrow pressure adjusting mechanism 50, the ring 60, and the like. Further, in this case, when the position of the ring 60 is within a predetermined range and the output torque Tout is equal to or greater than the threshold value Tref, the position of the ring 60 tends to become shorter from the predetermined distance Ls1 as it is farther from the large-diameter side end of the output cone 36. The ring 60 may be slid to the smaller diameter side of the output cone 36 by the distance.
- the predetermined distance Ls1 is set to the target slide distance Ls * and the ring 60 is output for the set target slide distance Ls *.
- a distance other than the predetermined distance Ls1 (a distance longer or shorter than the predetermined distance Ls1) may be set as the target slide distance Ls *, or the output torque Tout or the ring A distance corresponding to 60 narrow pressure or the like may be set as the target slide distance Ls *.
- the target slide distance Ls * is set based on the output torque Tout, the relationship between the output torque Tout and the target slide distance Ls * is determined in advance and stored in the ROM as a target slide distance setting map. If given, the corresponding target slide distance Ls * may be derived from the map and set.
- An example of the target slide distance setting map is shown in FIG. In the example of FIG. 8, the target slide distance Ls * is set to a predetermined distance Ls1 in the region where the output torque Tout is greater than or equal to the threshold Tref2 greater than the threshold Tref, and in the region where the output torque Tout is greater than or equal to the threshold Tref and less than the threshold Tref2. The larger Tout, the larger the distance toward the predetermined distance Ls1.
- the threshold value Tref2 is determined based on the lower limit value of the output torque Tout that is assumed that the movement distance from the reference position of the output cone 36 is equal to the movable distance Lomax, a torque slightly smaller than the output torque Tout, or the like. Can be used.
- the target slide distance Ls * is set in this way when the output torque Tout is equal to or greater than the threshold value Tref and less than the threshold value Tref2. This is based on the reason that at least part of the ring 60 moves and easily protrudes from the output cone 36.
- the ring 60 can be prevented from sliding more than necessary, and the reduction ratio of the CVT 30 can be reduced. A large change can be suppressed.
- the output torque Tout is estimated based on the input torque Tin.
- any device that acquires the output torque Tout may be used.
- the output torque Tout itself is detected. It is good also as what to do.
- the position detection sensor 72 is attached to the slider 66 and detects the position of the ring 60.
- the position detection sensor 72 may be any apparatus that acquires the position of the ring 60.
- it is attached to the transaxle housing 21a, the holding portion 68, etc. to detect the position of the ring 60, or is attached to the guide rail 64 to estimate the position of the ring 60 by detecting the position of the slider 66.
- the detection method may be any method such as a mechanical method or an optical method.
- the slide mechanism 62 includes a guide rail 64 that is rotatably attached to the transaxle housing 21a, and can slide along the guide rail 64 without rotating when the guide rail 64 rotates.
- the slider 66, the holding portion 68 that is attached to the slider 66 and rotatably holds the ring 60, and the motor 70 that rotates the guide rail 64 are configured.
- the reduction ratio can be reduced by sliding the ring 60. Any mechanism can be used as long as it can be changed.
- the narrow pressure adjusting mechanism 50 includes a fixing member 52 attached to the output shaft 38, a moving member 54 attached to the output cone 36, and a plurality of members formed on the fixing member 52.
- the torque (output torque Tout) acting on the output shaft 38 estimated from the torque input to the input shaft 32 (input torque Tin) and the transmission ratio of the CVT 30 (the position of the ring 60) increases, It may be configured by a mechanism that adjusts the narrow pressure to the ring 60 using hydraulic pressure or electric power so that the narrow pressure becomes large.
- the input shaft 32 and the input cone 34 are integrally formed, but may be formed separately.
- the power transmission mechanism 20a shifts the power from the engine 12 as a power source and transmits it to the left and right wheels 88a and 88b.
- a motor may be used.
- the power transmission mechanism 20a may not include the forward / reverse switching mechanism 24.
- the power transmission device 20 is mounted on the automobile 10, but may be mounted on a moving body other than the automobile 10, or may be incorporated in a non-moving facility such as a construction facility. .
- the CVT 30 corresponds to a “continuously variable transmission”
- the input cone 34 corresponds to an “input member”
- the output cone 36 corresponds to an “output member”
- the ring 60 corresponds to a “transmission member”.
- the slide mechanism 62 corresponds to “slide means”
- the narrow pressure adjustment mechanism 50 corresponds to “narrow pressure adjustment means”
- the position detection sensor 72 corresponds to “position acquisition means”, and is based on the input torque Tin.
- the electronic control unit 90 that executes the process of step S110 of the output member maximum diameter control routine of FIG.
- the present invention can be used in the power transmission device manufacturing industry.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
- Control Of Transmission Device (AREA)
Abstract
A power transmission device is provided with a continuously variable transmission, wherein an input cone connected to an input shaft and an output cone connected to an output shaft are disposed in opposite directions to one another, and a ring is pinched with a pinching force, which increases as the torque that acts on the output shaft increases, according to a pinching force adjustment mechanism that converts the torque that acts on the output shaft into a force in the direction of the output shaft. When the ring position is at the maximum diameter of an output member, which is the large diameter end of the output cone, if the output torque (Tout) that acts on the output shaft is at or above a threshold value (Tref)(S120), the ring is made to slide to the small-diameter side of the output cone (S130, S140).
Description
本発明は、動力伝達装置およびその制御方法に関する。
The present invention relates to a power transmission device and a control method thereof.
従来、この種の動力伝達装置としては、インプットシャフトに接続されたインプットコーンとアウトプットシャフトに接続されたアウトプットコーンとを互いに逆向きに平行に配置し、アウトプットシャフトに作用するトルクを狭圧力調節機構によって軸方向の力に変換してアウトプットコーンに作用させることによって両コーンでリングを狭圧する無段変速機を備えるものが提案されている(例えば、特許文献1参照)。この装置における無段変速機では、リングをスライドさせることにより、インプットシャフトに入力された動力を変速比の変更を伴ってアウトプットシャフトに出力している。
Conventionally, as this kind of power transmission device, the input cone connected to the input shaft and the output cone connected to the output shaft are arranged in parallel opposite to each other, and the torque acting on the output shaft is adjusted with a narrow pressure. There has been proposed one provided with a continuously variable transmission that narrows a ring with both cones by converting it into an axial force by a mechanism and acting on an output cone (for example, see Patent Document 1). In the continuously variable transmission in this apparatus, the power input to the input shaft is output to the output shaft with a change in the gear ratio by sliding the ring.
こうした動力伝達装置では、リングがアウトプットコーンの大径側端部に位置するとき(減速比が最大のとき)などには、アウトプットシャフトに大きなトルクが作用しやすく、そのトルクの大きさによってはアウトプットシャフトから狭圧力調節機構やアウトプットコーン,リングを介してインプットコーンに大きな力が作用してインプットコーンが変形し、動力の伝達性能の低下を招く場合がある。このため、インプットコーンの変形を抑制することが望まれるが、インプットコーンの強度の向上などによってこうした変形を抑制しようとすると、インプットコーンの大型化や重量の増加につながる。
In such a power transmission device, when the ring is located at the end of the output cone on the large diameter side (when the reduction ratio is maximum), a large torque is likely to act on the output shaft, and depending on the magnitude of the torque A large force acts on the input cone from the output shaft through the narrow pressure adjusting mechanism, the output cone, and the ring, and the input cone may be deformed, resulting in a decrease in power transmission performance. For this reason, it is desired to suppress the deformation of the input cone. However, if such deformation is suppressed by improving the strength of the input cone, the input cone is increased in size and weight. *
本発明の動力伝達装置およびその制御方法は、入力部材の変形を抑制することを主目的とする。
The main purpose of the power transmission device and the control method thereof according to the present invention is to suppress deformation of the input member.
本発明の動力伝達装置およびその制御方法は、上述の主目的を達成するために以下の手段を採った。
The power transmission device and the control method thereof according to the present invention employ the following means in order to achieve the main object described above.
本発明の動力伝達装置は、
入力軸と該入力軸に平行に配置された出力軸とを有し、該入力軸に入力された動力を無段階に変速して該出力軸に出力する無段変速機を備える動力伝達装置であって、
前記入力軸に接続された円錐形状の入力部材と、
前記出力軸に接続され、前記入力部材とは逆向きに配置された円錐形状の出力部材と、 前記入力部材と前記出力部材とに狭圧され、該入力部材と該出力部材との間で動力の伝達を行なう環状の伝達部材と、
前記伝達部材をスライドさせることにより変速比を変更可能なスライド手段と、
前記出力軸に作用するトルクである出力トルクが大きいほど大きくなる傾向に前記伝達部材に作用する狭圧力を調節する狭圧力調節手段と、
前記伝達部材の位置を取得する位置取得手段と、
前記出力トルクを取得する出力トルク取得手段と、
前記取得された伝達部材の位置が前記出力部材の大径側端部を含む所定範囲内であり且つ前記取得された出力トルクが所定トルク以上のとき、前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御するスライド制御手段と、
を備えることを要旨とする。 The power transmission device of the present invention is
A power transmission device having an input shaft and an output shaft arranged in parallel to the input shaft, and comprising a continuously variable transmission that continuously shifts the power input to the input shaft and outputs the power to the output shaft. There,
A conical input member connected to the input shaft;
A conical output member connected to the output shaft and disposed opposite to the input member; An annular transmission member for transmitting
Slide means capable of changing a gear ratio by sliding the transmission member;
Narrow pressure adjusting means for adjusting the narrow pressure acting on the transmission member in a tendency to increase as the output torque that is the torque acting on the output shaft increases.
Position acquisition means for acquiring the position of the transmission member;
Output torque acquisition means for acquiring the output torque;
When the acquired position of the transmission member is within a predetermined range including the large-diameter side end of the output member and the acquired output torque is equal to or greater than a predetermined torque, the transmission member is placed on the small-diameter side of the output member. Slide control means for controlling the slide means to slide;
It is a summary to provide.
入力軸と該入力軸に平行に配置された出力軸とを有し、該入力軸に入力された動力を無段階に変速して該出力軸に出力する無段変速機を備える動力伝達装置であって、
前記入力軸に接続された円錐形状の入力部材と、
前記出力軸に接続され、前記入力部材とは逆向きに配置された円錐形状の出力部材と、 前記入力部材と前記出力部材とに狭圧され、該入力部材と該出力部材との間で動力の伝達を行なう環状の伝達部材と、
前記伝達部材をスライドさせることにより変速比を変更可能なスライド手段と、
前記出力軸に作用するトルクである出力トルクが大きいほど大きくなる傾向に前記伝達部材に作用する狭圧力を調節する狭圧力調節手段と、
前記伝達部材の位置を取得する位置取得手段と、
前記出力トルクを取得する出力トルク取得手段と、
前記取得された伝達部材の位置が前記出力部材の大径側端部を含む所定範囲内であり且つ前記取得された出力トルクが所定トルク以上のとき、前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御するスライド制御手段と、
を備えることを要旨とする。 The power transmission device of the present invention is
A power transmission device having an input shaft and an output shaft arranged in parallel to the input shaft, and comprising a continuously variable transmission that continuously shifts the power input to the input shaft and outputs the power to the output shaft. There,
A conical input member connected to the input shaft;
A conical output member connected to the output shaft and disposed opposite to the input member; An annular transmission member for transmitting
Slide means capable of changing a gear ratio by sliding the transmission member;
Narrow pressure adjusting means for adjusting the narrow pressure acting on the transmission member in a tendency to increase as the output torque that is the torque acting on the output shaft increases.
Position acquisition means for acquiring the position of the transmission member;
Output torque acquisition means for acquiring the output torque;
When the acquired position of the transmission member is within a predetermined range including the large-diameter side end of the output member and the acquired output torque is equal to or greater than a predetermined torque, the transmission member is placed on the small-diameter side of the output member. Slide control means for controlling the slide means to slide;
It is a summary to provide.
この本発明の動力伝達装置では、伝達部材の位置が出力部材の大径側端部を含む所定範囲内であり且つ出力軸に作用するトルクである出力トルクが所定トルク以上のときには、伝達部材が出力部材の小径側にスライドするようスライド手段を制御する。これにより、減速比が小さくなって出力トルクが小さくなるため、出力軸から狭圧力調節手段や出力部材,リングを介して入力部材に作用する力を小さくすることができ、入力部材の変形を抑制することができる。ここで、「所定トルク」は、入力部材が変形する可能性のある出力トルクの下限やそれよりも若干小さいトルクとして予め定められたトルクであるものとすることもできるし、伝達部材の少なくとも一部が出力部材からはみ出る(伝達部材と出力部材との接触面積が小さくなる)可能性のあるトルクの下限やそれよりも若干小さいトルクであるものとすることもできる。また、「所定範囲」は、入力部材が変形する可能性のあるトルクが出力軸に作用し得る範囲として予め定められた範囲であるものとすることもできるし、伝達部材の少なくとも一部が出力部材からはみ出る可能性のあるトルクが出力軸に作用し得る範囲として予め定められた範囲であるものとすることもできる。
In the power transmission device of the present invention, when the position of the transmission member is within a predetermined range including the large-diameter end of the output member and the output torque that is the torque acting on the output shaft is equal to or greater than the predetermined torque, the transmission member is The sliding means is controlled to slide to the small diameter side of the output member. As a result, the reduction ratio is reduced and the output torque is reduced, so that the force acting on the input member from the output shaft through the narrow pressure adjusting means, the output member, and the ring can be reduced, and the deformation of the input member is suppressed. can do. Here, the “predetermined torque” may be a torque that is predetermined as a lower limit of the output torque that may cause the input member to be deformed or a slightly smaller torque, or at least one of the transmission members. The lower limit of the torque that may cause the portion to protrude from the output member (the contact area between the transmission member and the output member becomes small) or a slightly smaller torque may be used. In addition, the “predetermined range” may be a range that is determined in advance as a range in which torque that may cause deformation of the input member can act on the output shaft, and at least a part of the transmission member outputs It is also possible to set a predetermined range as a range in which a torque that may protrude from the member can act on the output shaft.
こうした本発明の動力伝達装置において、前記スライド制御手段は、前記出力部材の移動可能距離以上の距離だけ前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御する手段である、ものとすることもできる。こうすれば、入力部材の変形などによって伝達部材の少なくとも一部が出力部材からはみ出るのをより確実に抑制することができる。
In such a power transmission device of the present invention, the slide control means is a means for controlling the slide means so that the transmission member slides toward the small diameter side of the output member by a distance equal to or greater than the movable distance of the output member. It can also be. In this way, it is possible to more reliably suppress at least a part of the transmission member from protruding from the output member due to deformation of the input member.
また、本発明の動力伝達装置において、前記スライド制御手段は、前記取得された出力トルクが大きいほど大きくなる傾向の距離だけ前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御する手段である、ものとすることもできる。こうすれば、出力トルクに応じた距離だけ伝達部材をスライドさせることができる。
In the power transmission device of the present invention, the slide control means controls the slide means so that the transmission member slides toward the smaller diameter side of the output member by a distance that tends to increase as the acquired output torque increases. It can also be a means to do. By doing so, the transmission member can be slid by a distance corresponding to the output torque.
本発明の動力伝達装置の制御方法は、
入力軸に接続された円錐形状の入力部材と、出力軸に接続され前記入力部材とは逆向きに配置された円錐形状の出力部材と、前記入力部材と前記出力部材とに狭圧され該入力部材と該出力部材との間で動力の伝達を行なう環状の伝達部材と、前記伝達部材をスライドさせることにより変速比を変更可能なスライド手段と、前記出力軸に作用するトルクである出力トルクが大きいほど大きくなる傾向に前記伝達部材に作用する狭圧力を調節する狭圧力調節手段と、を有し、前記入力軸に入力された動力を無段階に変速して前記出力軸に出力する無段変速機を備える動力伝達装置の制御方法であって、
前記伝達部材の位置が前記出力部材の大径側端部を含む所定範囲内であり且つ前記出力トルクが所定トルク以上のとき、前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御する、
ことを特徴とする。 The power transmission device control method of the present invention includes:
A conical input member connected to the input shaft, a conical output member connected to the output shaft and disposed in the direction opposite to the input member, and the input member and the output member are subjected to a narrow pressure. An annular transmission member that transmits power between the member and the output member, slide means that can change a gear ratio by sliding the transmission member, and output torque that is torque acting on the output shaft A narrow pressure adjusting means for adjusting a narrow pressure acting on the transmission member so as to increase as it increases, continuously changing the power input to the input shaft and outputting it to the output shaft. A method for controlling a power transmission device including a transmission,
When the position of the transmission member is within a predetermined range including the large-diameter end of the output member and the output torque is equal to or greater than a predetermined torque, the sliding means is configured to slide the transmission member to the small-diameter side of the output member. To control the
It is characterized by that.
入力軸に接続された円錐形状の入力部材と、出力軸に接続され前記入力部材とは逆向きに配置された円錐形状の出力部材と、前記入力部材と前記出力部材とに狭圧され該入力部材と該出力部材との間で動力の伝達を行なう環状の伝達部材と、前記伝達部材をスライドさせることにより変速比を変更可能なスライド手段と、前記出力軸に作用するトルクである出力トルクが大きいほど大きくなる傾向に前記伝達部材に作用する狭圧力を調節する狭圧力調節手段と、を有し、前記入力軸に入力された動力を無段階に変速して前記出力軸に出力する無段変速機を備える動力伝達装置の制御方法であって、
前記伝達部材の位置が前記出力部材の大径側端部を含む所定範囲内であり且つ前記出力トルクが所定トルク以上のとき、前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御する、
ことを特徴とする。 The power transmission device control method of the present invention includes:
A conical input member connected to the input shaft, a conical output member connected to the output shaft and disposed in the direction opposite to the input member, and the input member and the output member are subjected to a narrow pressure. An annular transmission member that transmits power between the member and the output member, slide means that can change a gear ratio by sliding the transmission member, and output torque that is torque acting on the output shaft A narrow pressure adjusting means for adjusting a narrow pressure acting on the transmission member so as to increase as it increases, continuously changing the power input to the input shaft and outputting it to the output shaft. A method for controlling a power transmission device including a transmission,
When the position of the transmission member is within a predetermined range including the large-diameter end of the output member and the output torque is equal to or greater than a predetermined torque, the sliding means is configured to slide the transmission member to the small-diameter side of the output member. To control the
It is characterized by that.
この本発明の動力伝達装置の制御方法では、伝達部材の位置が出力部材の大径側端部を含む所定範囲内であり且つ出力軸に作用するトルクである出力トルクが所定トルク以上のときには、伝達部材が出力部材の小径側にスライドするようスライド手段を制御する。これにより、減速比が小さくなって出力トルクが小さくなるため、出力軸から狭圧力調節手段や出力部材,リングを介して入力部材に作用する力を小さくすることができ、入力部材の変形を抑制することができる。ここで、「所定トルク」は、入力部材が変形する可能性のある出力トルクの下限やそれよりも若干小さいトルクとして予め定められたトルクであるものとすることもできるし、伝達部材の少なくとも一部が出力部材からはみ出る(伝達部材と出力部材との接触面積が小さくなる)可能性のあるトルクの下限やそれよりも若干小さいトルクであるものとすることもできる。また、「所定範囲」は、入力部材が変形する可能性のあるトルクが出力軸に作用し得る範囲として予め定められた範囲であるものとすることもできるし、伝達部材の少なくとも一部が出力部材からはみ出る可能性のあるトルクが出力軸に作用し得る範囲として予め定められた範囲であるものとすることもできる。
In the control method of the power transmission device of the present invention, when the position of the transmission member is within a predetermined range including the large-diameter side end of the output member and the output torque that is the torque acting on the output shaft is equal to or greater than the predetermined torque, The sliding means is controlled so that the transmission member slides to the small diameter side of the output member. As a result, the reduction ratio is reduced and the output torque is reduced, so that the force acting on the input member from the output shaft through the narrow pressure adjusting means, the output member, and the ring can be reduced, and the deformation of the input member is suppressed. can do. Here, the “predetermined torque” may be a torque that is predetermined as a lower limit of the output torque that may cause the input member to be deformed or a slightly smaller torque, or at least one of the transmission members. The lower limit of the torque that may cause the portion to protrude from the output member (the contact area between the transmission member and the output member becomes small) or a slightly smaller torque may be used. In addition, the “predetermined range” may be a range that is determined in advance as a range in which torque that may cause deformation of the input member can act on the output shaft, and at least a part of the transmission member outputs It is also possible to set a predetermined range as a range in which a torque that may protrude from the member can act on the output shaft.
次に、本発明を実施するための形態を実施例を用いて説明する。
Next, modes for carrying out the present invention will be described using examples.
図1は、本発明の一実施例としての動力伝達装置20を搭載する自動車10の構成の概略を示す構成図である。実施例の自動車10は、図示するように、ガソリンや軽油などの炭化水素系の燃料の爆発燃焼により動力を出力する内燃機関としてのエンジン12と、エンジン12からの動力を変速して左右の車輪88a,88bに伝達する動力伝達機構20aと、車両全体をコントロールする電子制御ユニット90とを備える。ここで、実施例の動力伝達装置20としては、動力伝達機構20aおよび電子制御ユニット90が該当する。
FIG. 1 is a configuration diagram showing an outline of a configuration of an automobile 10 equipped with a power transmission device 20 as an embodiment of the present invention. As shown in the figure, an automobile 10 according to the embodiment includes an engine 12 as an internal combustion engine that outputs power by explosion combustion of a hydrocarbon-based fuel such as gasoline or light oil, and left and right wheels by shifting power from the engine 12. A power transmission mechanism 20a for transmitting to 88a and 88b and an electronic control unit 90 for controlling the entire vehicle are provided. Here, the power transmission device 20 of the embodiment corresponds to the power transmission mechanism 20a and the electronic control unit 90.
動力伝達機構20aは、エンジン12から図示しない発進装置(例えば、トルクコンバータなど)を介して入力された動力を変速して左右の車輪88a,88bに伝達するトランスアクスル装置として構成されており、図2に示すように、発進装置の出力軸22に接続され発進装置からの動力を正転と逆転との切替を伴って出力する前後進切替機構24と、前後進切替機構24に接続されたインプットシャフト32とこのインプットシャフト32に平行に配置されたアウトプットシャフト38とを有しインプットシャフト32に入力された動力を無段階に変速してアウトプットシャフト38に出力する無段変速機としてのCVT30と、CVT30のアウトプットシャフト38に減速ギヤ26を介して連結されると共に左右の前輪に連結されたデファレンシャルギヤ28とを備え、これらはトランスアクスルハウジング21aとコンバータハウジング21bとリアケース21cとからなるケース21に収容されている。なお、このケース21の内部には、前後進切替機構24とデファレンシャルギヤ28とが配置される空間とCVT30が配置される空間とを仕切る仕切プレート21dが設けられている。
The power transmission mechanism 20a is configured as a transaxle device that shifts the power input from the engine 12 via a starter (not shown) (for example, a torque converter) and transmits the power to the left and right wheels 88a, 88b. 2, a forward / reverse switching mechanism 24 connected to the output shaft 22 of the starting device and outputting power from the starting device with switching between forward rotation and reverse rotation, and an input connected to the forward / backward switching mechanism 24. A CVT 30 as a continuously variable transmission that has a shaft 32 and an output shaft 38 disposed in parallel to the input shaft 32, and continuously shifts the power input to the input shaft 32 and outputs it to the output shaft 38; Connected to the output shaft 38 of the CVT 30 via the reduction gear 26 and connected to the left and right front wheels. And a differential gear 28, which are accommodated in a case 21 made of a transaxle housing 21a and the converter housing 21b and the rear case 21c. In addition, a partition plate 21d that partitions a space in which the forward / reverse switching mechanism 24 and the differential gear 28 are disposed from a space in which the CVT 30 is disposed is provided inside the case 21.
前後進切替機構24は、ダブルピニオンの遊星歯車機構とブレーキB1およびクラッチC1とにより構成されている。ダブルピニオンの遊星歯車機構は、外歯歯車のサンギヤ24aと、このサンギヤ24aと同心円上に配置された内歯歯車のリングギヤ24bと、サンギヤ24aに噛合する複数の第1ピニオンギヤおよびこの第1ピニオンギヤに噛合すると共にリングギヤ24bに噛合する複数の第2ピニオンギヤを連結して自転かつ公転自在に保持するキャリア24cとを備え、サンギヤ24aには出力軸22が、キャリア24cにはCVT30のインプットシャフト32が、各々連結されている。遊星歯車機構のリングギヤ24bは、ブレーキB1によりケース21に接続されており、ブレーキB1をオンオフすることにより、リングギヤ24bを自由に回転するものとしたり、その回転を禁止したりする。遊星歯車機構のサンギヤ24aとキャリア24cは、クラッチC1により接続されており、クラッチC1をオンオフすることにより、サンギヤ24aとキャリア24cとを連結したり切り離したりする。前後進切替機構24は、ブレーキB1をオフすると共にクラッチC1をオンすることにより出力軸22の回転をそのままCVT30のインプットシャフト32に伝達して車両を前進させたり、ブレーキB1をオンすると共にクラッチC1をオフすることにより出力軸22の回転を逆方向に変換してCVT30のインプットシャフト32に伝達して車両を後進させたりする。また、ブレーキB1をオフすると共にクラッチC1をオフすることにより出力軸22とCVT30のインプットシャフト32とを切り離すこともできる。なお、実施例では、前後進切替機構24をダブルピニオンの遊星歯車機構とブレーキB1とクラッチC1とにより構成するものとしたが、ダブルピニオンの遊星歯車機構に代えてシングルピニオンの遊星歯車機構により構成するものとしてもよいし、その他の構成とするものとしてもよい。
The forward / reverse switching mechanism 24 includes a double pinion planetary gear mechanism, a brake B1, and a clutch C1. The planetary gear mechanism of the double pinion includes an external gear sun gear 24a, an internal gear ring gear 24b arranged concentrically with the sun gear 24a, a plurality of first pinion gears meshed with the sun gear 24a, and the first pinion gear. A plurality of second pinion gears that mesh with each other and mesh with the ring gear 24b are coupled to each other and a carrier 24c that rotates and revolves freely. The sun gear 24a has an output shaft 22, and the carrier 24c has an input shaft 32 of the CVT 30. Each is connected. The ring gear 24b of the planetary gear mechanism is connected to the case 21 by a brake B1, and the ring gear 24b can be freely rotated or prohibited from rotating by turning on and off the brake B1. The sun gear 24a and the carrier 24c of the planetary gear mechanism are connected by a clutch C1, and the sun gear 24a and the carrier 24c are connected or disconnected by turning on and off the clutch C1. The forward / reverse switching mechanism 24 turns off the brake B1 and turns on the clutch C1 to transmit the rotation of the output shaft 22 to the input shaft 32 of the CVT 30 as it is to advance the vehicle or turn on the brake B1 and turn on the clutch C1. Is turned off, the rotation of the output shaft 22 is converted in the reverse direction and transmitted to the input shaft 32 of the CVT 30 to reverse the vehicle. Further, the output shaft 22 and the input shaft 32 of the CVT 30 can be disconnected by turning off the brake B1 and turning off the clutch C1. In the embodiment, the forward / reverse switching mechanism 24 is constituted by a double-pinion planetary gear mechanism, a brake B1, and a clutch C1, but is constituted by a single-pinion planetary gear mechanism instead of the double-pinion planetary gear mechanism. It is good also as what is carried out and it is good also as what shall be set as another structure.
CVT30は、インプットシャフト32が一体的に形成された円錐形状のインプットコーン34と、インプットコーン34と略同一形状でインプットコーン34と逆向きとなるようアウトプットシャフト38に連結されたアウトプットコーン36と、インプットコーン34に挿入されてインプットコーン34とアウトプットコーン36とにより挟まれるよう配置されたリング60と、リング60を回転自在に支持しリング60をスライド可能なスライド機構62(図4参照)と、インプットコーン34とアウトプットコーン36との間のリング60への狭圧力を調節する狭圧力調節機構50とを備え、スライド機構62によってリング60をスライドさせることによりインプットシャフト32からの動力を無段階に変速してアウトプットシャフト38に出力する。図3に、CVT30の変速の様子を示す。図示するように、リング60を図中手前側(図2中左側)にスライドさせることによりインプットコーン34からの動力を比較的小さな減速比をもって変速してアウトプットコーン36に伝達し、リング60を図中奥側(図2中右側)にスライドさせることによりインプットコーン34からの動力を比較的大きな減速比をもって変速してアウトプットコーン36に伝達する。
The CVT 30 includes a conical input cone 34 integrally formed with an input shaft 32, and an output cone 36 that is substantially the same shape as the input cone 34 and is connected to the output shaft 38 so as to be opposite to the input cone 34. The ring 60 is inserted into the input cone 34 and is sandwiched between the input cone 34 and the output cone 36, and a slide mechanism 62 (see FIG. 4) that supports the ring 60 rotatably and allows the ring 60 to slide. And a narrow pressure adjusting mechanism 50 for adjusting the narrow pressure applied to the ring 60 between the input cone 34 and the output cone 36, and the power from the input shaft 32 is generated by sliding the ring 60 by the slide mechanism 62. Change the output steplessly to output And outputs to shift 38. FIG. 3 shows how the CVT 30 shifts. As shown in the figure, the ring 60 is slid to the front side (left side in FIG. 2) to shift the power from the input cone 34 with a relatively small reduction ratio and transmit it to the output cone 36. By sliding to the back side in the figure (right side in FIG. 2), the power from the input cone 34 is shifted with a relatively large reduction ratio and transmitted to the output cone 36.
インプットコーン34およびインプットシャフト32は、図2中右端では仕切プレート21dに取り付けられスラスト力を受けることができないが比較的大きなラジアル力を受けることができる円筒ころ軸受けとして形成された軸受け41により回転自在に支持されると共に左端ではトランスアクスルハウジング21aに取り付けられスラスト力を受けることができる円錐ころ軸受けとして形成された軸受け42により回転自在に支持されている。一方、アウトプットコーン36は、図2中右端では仕切プレート21dに取り付けられ円筒ころ軸受けとして形成された軸受け45により回転自在に支持されると共に左端ではトランスアクスルハウジング21aに取り付けられ円筒ころ軸受けとして形成された軸受け46により回転自在に支持されている。また、アウトプットコーン36に連結されたアウトプットシャフト38の図2中右端ではコンバータハウジング21bに取り付けられ円錐ころ軸受けとして形成された軸受け49により回転自在に支持されている。
The input cone 34 and the input shaft 32 are rotatable by a bearing 41 formed as a cylindrical roller bearing which is attached to the partition plate 21d at the right end in FIG. 2 and cannot receive a thrust force but can receive a relatively large radial force. And at the left end is rotatably supported by a bearing 42 formed as a tapered roller bearing attached to the transaxle housing 21a and capable of receiving a thrust force. On the other hand, the output cone 36 is rotatably supported by a bearing 45 which is attached to the partition plate 21d and formed as a cylindrical roller bearing at the right end in FIG. 2, and is attached to the transaxle housing 21a and formed as a cylindrical roller bearing at the left end. The bearing 46 is rotatably supported. Further, the output shaft 38 connected to the output cone 36 is rotatably supported by a bearing 49 which is attached to the converter housing 21b and formed as a tapered roller bearing at the right end in FIG.
スライド機構62は、図4に示すように、リング60のスライド方向に略平行に延在してトランスアクスルハウジング21aによって回転自在に支持される送りネジとしてのガイドレール64と、ガイドレール64に嵌合する嵌合部を有しガイドレール64の回転時には回転せずにガイドレール64に沿って移動可能なスライダ66と、ガイドレール64の延在方向に揺動可能にスライダ66に取り付けられると共にU字形状のU字部によってリング60を側面から回転自在に保持する保持部68と、ガイドレール64の一端に回転軸が接続されてガイドレール64を回転させるモータ70とを備える。このスライド機構62では、モータ70の回転駆動によってガイドレール64を回転させてスライダ66をガイドレール64に沿って移動させることにより、リング60を図中手前側(図2中左側)または図中奥側(図2中右側)にスライドさせる。
As shown in FIG. 4, the slide mechanism 62 extends substantially parallel to the sliding direction of the ring 60 and is fitted to the guide rail 64 as a feed screw that is rotatably supported by the transaxle housing 21a. A slider 66 that has a fitting portion to be fitted and can move along the guide rail 64 without rotating when the guide rail 64 rotates, and is attached to the slider 66 so as to be swingable in the extending direction of the guide rail 64 and U A holding portion 68 that rotatably holds the ring 60 from the side surface by a U-shaped portion having a letter shape, and a motor 70 that rotates the guide rail 64 with a rotating shaft connected to one end of the guide rail 64. In this slide mechanism 62, the guide rail 64 is rotated by the rotational drive of the motor 70, and the slider 66 is moved along the guide rail 64, whereby the ring 60 is moved to the front side (left side in FIG. 2) or the rear side in the figure. Slide to the side (right side in FIG. 2).
狭圧力調節機構50は、図2に示すように、アウトプットコーン36に内蔵されており、機械的な機構によりインプットコーン34とアウトプットコーン36とによりリング60に作用する狭圧力を調節する。図5は狭圧力調節機構50の構成の概略を示す構成図であり、図6は狭圧力調節機構50を部分的に拡大した部分拡大図である。狭圧力調節機構50は、図5および図6に示すように、アウトプットシャフト38の先端部に形成されたスプラインにスプライン嵌合されアウトプットシャフト38に対して軸方向に移動不能に固定された固定部材52と、アウトプットコーン36の内周面に形成されたスプラインにスプライン嵌合されアウトプットシャフト38に対してアウトプットコーン36と共に軸方向に移動可能に形成された移動部材54と、固定部材52に形成された複数の半球状のボール受け52aと移動部材54に形成された複数の半球状のボール受け54aとの間に配置された複数のボール56と、固定部材52と移動部材54との間に設けられ固定部材52をバネ受けとして移動部材54を軸方向に付勢するバネ58と、アウトプットコーン36に取り付けられアウトプットコーン36をアウトプットシャフト38に対して軸方向に移動可能に支持する支持部材59とを備え、アウトプットシャフト38に作用するトルクを軸方向の力に変換してアウトプットコーン36に作用させることによりリング60の狭圧力を調節する。図6に示すように、アウトプットシャフト38にトルクが作用していないときには、固定部材52のボール受け52aと移動部材54のボール受け54bとは丁度向かい合う位置にあり、移動部材54はボール56からの何らの力も受けないが(図6(a)参照)、アウトプットシャフト38にトルクが作用すると、固定部材52のボール受け52aと移動部材54のボール受け54aとの間にねじれが生じて固定部材52からの反力を用いてボール56で移動部材54を押し出す力が生じる(図6(b)参照)。前述したように、移動部材54にはアウトプットコーン36が取り付けられているから、移動部材54の移動に伴ってアウトプットコーン36も押し出されることになる。このとき、アウトプットコーン36を押し出す力はアウトプットシャフト38に作用するトルクが大きいほど大きくなり、これにより、リング60の狭圧力が調節される。したがって、CVT30は、インプットシャフト32に入力されたトルクに対して減速比が大きいほどアウトプットシャフト38に作用するトルクが大きくなるから、減速比が大きいほどリング60の狭圧力は大きくなる方向に調節されることになる。
As shown in FIG. 2, the narrow pressure adjusting mechanism 50 is built in the output cone 36, and adjusts the narrow pressure acting on the ring 60 by the input cone 34 and the output cone 36 by a mechanical mechanism. FIG. 5 is a block diagram showing an outline of the configuration of the narrow pressure adjusting mechanism 50, and FIG. 6 is a partially enlarged view of the narrow pressure adjusting mechanism 50 partially enlarged. As shown in FIGS. 5 and 6, the narrow pressure adjusting mechanism 50 is a fixing member that is spline-fitted to a spline formed at the tip of the output shaft 38 and fixed to the output shaft 38 so as not to move in the axial direction. 52, a moving member 54 that is spline-fitted to a spline formed on the inner peripheral surface of the output cone 36 and is formed so as to be movable in the axial direction together with the output cone 36, and a fixed member 52. Between the plurality of hemispherical ball receivers 52 a formed and the plurality of hemispherical ball receivers 54 a formed on the moving member 54, between the fixed member 52 and the moving member 54 And a spring 58 for urging the moving member 54 in the axial direction with the fixing member 52 as a spring receiver, and attached to the output cone 36 And a support member 59 that supports the output cone 36 so as to be movable in the axial direction with respect to the output shaft 38, and converts the torque acting on the output shaft 38 into an axial force to act on the output cone 36. As a result, the narrow pressure of the ring 60 is adjusted. As shown in FIG. 6, when no torque is applied to the output shaft 38, the ball receiver 52 a of the fixing member 52 and the ball receiver 54 b of the moving member 54 are just opposite to each other. Although no force is received (see FIG. 6A), when a torque is applied to the output shaft 38, a twist is generated between the ball receiver 52a of the fixing member 52 and the ball receiver 54a of the moving member 54, thereby fixing the member 52. A force for pushing out the moving member 54 with the ball 56 is generated using the reaction force from (see FIG. 6B). As described above, since the output cone 36 is attached to the moving member 54, the output cone 36 is pushed out as the moving member 54 moves. At this time, the force that pushes out the output cone 36 increases as the torque acting on the output shaft 38 increases, whereby the narrow pressure of the ring 60 is adjusted. Therefore, since the torque acting on the output shaft 38 increases as the speed reduction ratio with respect to the torque input to the input shaft 32 increases, the CVT 30 is adjusted so that the narrow pressure of the ring 60 increases as the speed reduction ratio increases. Will be.
電子制御ユニット90は、CPUを中心としたマイクロプロセッサとして構成されており、CPUの他に処理プログラムを記憶するROMと、データを一時的に記憶するRAMと、入出力ポートと、通信ポートとを備える。電子制御ユニット90には、エンジン12の運転状態を検出する各種センサからの信号や、スライダ66に取り付けられてリング60の位置を検出する位置検出センサ72(図4参照)からのリング位置Pr,インプットシャフト32に取り付けられた回転数センサからのインプットシャフト32の回転数,アウトプットシャフト38に取り付けられた回転数センサからのアウトプットシャフト38の回転数,シフトレバー91の操作位置を検出するシフトポジションセンサ92からのシフトポジションSP,アクセルペダル93の踏み込み量を検出するアクセルペダルポジションセンサ94からのアクセル開度Acc,ブレーキペダル95の踏み込み量を検出するブレーキペダルポジションセンサ96からのブレーキペダルポジションBP車速センサ98からの車速Vなどが入力ポートを介して入力されている。電子制御ユニット90からは、エンジン12への制御信号や、前後進切替機構24のクラッチC1やブレーキB1への制御信号,CVT30のスライド機構62のモータ70への制御信号などが出力ポートを介して出力されている。
The electronic control unit 90 is configured as a microprocessor centered on a CPU. In addition to the CPU, a ROM that stores a processing program, a RAM that temporarily stores data, an input / output port, and a communication port are provided. Prepare. The electronic control unit 90 includes signals from various sensors that detect the operating state of the engine 12, and ring positions Pr from a position detection sensor 72 (see FIG. 4) that is attached to the slider 66 and detects the position of the ring 60. Shift position sensor for detecting the rotational speed of the input shaft 32 from the rotational speed sensor attached to the input shaft 32, the rotational speed of the output shaft 38 from the rotational speed sensor attached to the output shaft 38, and the operating position of the shift lever 91 The shift position SP from 92, the accelerator opening Acc from the accelerator pedal position sensor 94 that detects the depression amount of the accelerator pedal 93, and the brake pedal position BP from the brake pedal position sensor 96 that detects the depression amount of the brake pedal 95 And a vehicle speed V from a speed sensor 98 is input through the input port. From the electronic control unit 90, a control signal to the engine 12, a control signal to the clutch C1 and the brake B1 of the forward / reverse switching mechanism 24, a control signal to the motor 70 of the slide mechanism 62 of the CVT 30, and the like are output via the output port. It is output.
次に、こうして構成された実施例の動力伝達装置20の動作、特に、リング60の位置がアウトプットコーン36の大径側端部(最大減速比に相当する位置)である出力部材最大径時の動作について説明する。図7は、電子制御ユニット90により実行される出力部材最大径時制御ルーチンの一例を示すフローチャートである。このルーチンは、出力部材最大径時でCVT30の変速比の変更が要求されていないときに所定時間毎(例えば数msec毎)に繰り返し実行される。なお、出力部材最大径時であるか否かは、位置検出センサ72からのリング位置Prを用いて判定することができる。
Next, the operation of the power transmission device 20 of the embodiment configured as described above, particularly when the output member has the maximum diameter when the position of the ring 60 is the large-diameter side end of the output cone 36 (position corresponding to the maximum reduction ratio). Will be described. FIG. 7 is a flowchart illustrating an example of the control routine for the maximum output member diameter executed by the electronic control unit 90. This routine is repeatedly executed at predetermined time intervals (for example, every several msec) when the change of the transmission ratio of the CVT 30 is not requested at the maximum output member diameter. Whether or not the maximum diameter of the output member is reached can be determined using the ring position Pr from the position detection sensor 72.
出力部材最大径時制御ルーチンが実行されると、電子制御ユニット90のCPUは、まず、インプットシャフト32に入力されるトルクとしての入力トルクTinを入力し(ステップS100)、入力トルクTinに基づいてアウトプットシャフト38に作用するトルクとしての出力トルクToutを推定する(ステップS110)。ここで、入力トルクTinは、エンジン12の運転状態(回転数や吸入空気量など)に基づいて推定された値を用いるものとした。また、出力トルクToutは、入力トルクTinとCVT30の減速比と出力トルクToutとの関係を予め実験や解析などによって定めてマップとしてROM(図示せず)に記憶しておき、入力トルクTinと減速比とが与えられると記憶したマップから対応する出力トルクToutを導出して設定するものとした。なお、いま、出力部材最大径時を考えているから、減速比としては最大減速比を用いることができる。
When the output member maximum diameter time control routine is executed, the CPU of the electronic control unit 90 first inputs an input torque Tin as a torque input to the input shaft 32 (step S100), and based on the input torque Tin. An output torque Tout as a torque acting on the output shaft 38 is estimated (step S110). Here, as the input torque Tin, a value estimated based on the operating state of the engine 12 (rotation speed, intake air amount, etc.) is used. Further, the output torque Tout is determined in advance by experiment or analysis and stored in a ROM (not shown) as a map in relation to the reduction ratio of the input torque Tin and the CVT 30 and the output torque Tout. When the ratio is given, the corresponding output torque Tout is derived and set from the stored map. Since the maximum diameter of the output member is considered now, the maximum reduction ratio can be used as the reduction ratio.
続いて、出力トルクToutを閾値Trefと比較する(ステップS120)。ここで、閾値Trefは、インプットコーン34が変形する可能性のある出力トルクToutの下限またはそれよりも若干小さいトルクや、インプットコーン34の変形などによってリング60の少なくとも一部がアウトプットコーン36のからはみ出る(リング60とアウトプットコーン36との接触面積が小さくなる)可能性のある出力トルクToutの下限またはそれよりも若干小さいトルクなどを予め実験や解析などによって定めて用いることができる。出力部材最大径時にはアウトプットシャフト38に大きなトルクが作用しやすく、出力トルクToutの大きさによってはアウトプットシャフト38から狭圧力調節機構50やアウトプットコーン36,リング60を介してインプットコーン34に大きな力が作用してインプットコーン34が変形し、動力の伝達性能の低下を招いたり、リング60の少なくとも一部がアウトプットコーン36からはみ出たりする可能性がある。ステップS120の出力トルクToutと閾値Trefとの比較は、こうした可能性があるか否かを判定する処理である。なお、こうした問題を解消するために、インプットコーン34の強度を向上させることも考えられるが、この場合、インプットコーン34の大型化や重量の増加につながる。
Subsequently, the output torque Tout is compared with a threshold value Tref (step S120). Here, the threshold value Tref is set so that at least a part of the ring 60 has a lower limit of the output torque Tout at which the input cone 34 may be deformed or slightly smaller than the output torque Tout, deformation of the input cone 34, etc. A lower limit of the output torque Tout that may protrude from the ring 60 (the contact area between the ring 60 and the output cone 36 is reduced) or a torque slightly smaller than that may be determined and used in advance by experimentation or analysis. When the output member has the maximum diameter, a large torque is likely to act on the output shaft 38. Depending on the magnitude of the output torque Tout, a large force is applied to the input cone 34 from the output shaft 38 via the narrow pressure adjusting mechanism 50, the output cone 36, and the ring 60. May cause the input cone 34 to be deformed, leading to a reduction in power transmission performance, or at least a part of the ring 60 to protrude from the output cone 36. The comparison between the output torque Tout and the threshold value Tref in step S120 is processing for determining whether or not there is such a possibility. In order to solve these problems, the strength of the input cone 34 may be improved. In this case, however, the input cone 34 is increased in size and weight.
出力トルクToutが閾値Tref未満のときには、前述の可能性はないと判断し、そのまま本ルーチンを終了する。一方、出力トルクToutが閾値Tref以上のときには、前述の可能性があると判断し、リング60の目標スライド距離Ls*に所定距離Ls1を設定すると共に(ステップS130)、設定した目標スライド距離Ls*だけリング60がアウトプットコーン36の小径側にスライドするようモータ70を回転駆動させるスライド処理を実行して(ステップS140)、本ルーチンを終了する。ここで、所定距離Ls1は、アウトプットコーン36の移動可能距離Lomaxより長い距離を用いることができる。ここで、移動可能距離Lomaxは、アウトプットシャフト38にトルクが作用していないとき(狭圧力調節機構50によってアウトプットコーン36が押し出されていないとき)のアウトプットコーン36の位置(基準位置)に対してアウトプットコーン36が狭圧力調節機構50からの力を受けて移動可能な最大距離であり、アウトプットコーン36とケース21,軸受け46などとの位置関係や、狭圧力調節機構50によってアウトプットコーン36を移動させることが可能な距離などに基づいて予め実験や解析などによって定められた距離を用いることができる。このように、出力部材最大径時に出力トルクToutが閾値Tref以上のときには、リング60をアウトプットコーン36の小径側にスライドさせることにより、減速比が小さくなって出力トルクToutが小さくなるから、アウトプットシャフト38から狭圧力調節機構50やアウトプットコーン36,リング60を介してインプットコーン34に作用する力を小さくすることができ、インプットコーン34の変形を抑制することができる。この結果、インプットコーン34の変形による動力の伝達性能の低下や、リング60の少なくとも一部がアウトプットコーン36からはみ出ることやこれによる更なる動力の伝達性能の低下などを抑制することができる。
When the output torque Tout is less than the threshold value Tref, it is determined that there is no possibility described above, and this routine is terminated as it is. On the other hand, when the output torque Tout is equal to or greater than the threshold value Tref, it is determined that there is the possibility described above, and a predetermined distance Ls1 is set as the target slide distance Ls * of the ring 60 (step S130), and the set target slide distance Ls *. Only the ring 60 is slid to the small diameter side of the output cone 36 to execute the slide processing for rotating the motor 70 (step S140), and this routine is finished. Here, as the predetermined distance Ls1, a distance longer than the movable distance Lomax of the output cone 36 can be used. Here, the movable distance Lomax is set to the position (reference position) of the output cone 36 when no torque acts on the output shaft 38 (when the output cone 36 is not pushed out by the narrow pressure adjusting mechanism 50). On the other hand, this is the maximum distance that the output cone 36 can move by receiving the force from the narrow pressure adjusting mechanism 50, and the positional relationship between the output cone 36 and the case 21, the bearing 46, etc. A distance determined in advance through experiments, analysis, or the like based on the distance that the toe cone 36 can be moved can be used. Thus, when the output torque Tout is equal to or greater than the threshold Tref at the maximum diameter of the output member, sliding the ring 60 to the smaller diameter side of the output cone 36 reduces the reduction ratio and decreases the output torque Tout. The force acting on the input cone 34 from the shaft 38 via the narrow pressure adjusting mechanism 50, the output cone 36, and the ring 60 can be reduced, and deformation of the input cone 34 can be suppressed. As a result, it is possible to suppress a decrease in power transmission performance due to the deformation of the input cone 34, at least a part of the ring 60 protruding from the output cone 36, and a further decrease in power transmission performance due to this.
以上説明した実施例の動力伝達装置20によれば、リング60の位置がアウトプットコーン36の大径側端部である出力部材最大径時に、アウトプットシャフト38に作用するトルクとしての出力トルクToutが閾値Tref以上のときには、リング60をアウトプットコーン36の小径側にスライドさせるから、インプットコーン34の変形を抑制することができる。しかも、この際には、アウトプットコーン36の移動可能距離Lomaxより長い所定距離Ls1だけリング60をアウトプットコーン36の小径側にスライドさせるから、リング60がアウトプットコーン36からはみ出るのをより確実に抑制することができる。
According to the power transmission device 20 of the embodiment described above, the output torque Tout as the torque acting on the output shaft 38 when the position of the ring 60 is the maximum diameter of the output member that is the large diameter side end of the output cone 36 is as follows. When the value is equal to or greater than the threshold value Tref, the ring 60 is slid to the smaller diameter side of the output cone 36, so that the deformation of the input cone 34 can be suppressed. In addition, at this time, the ring 60 is slid to the smaller diameter side of the output cone 36 by a predetermined distance Ls1 longer than the movable distance Lomax of the output cone 36, so that the ring 60 is more sure to protrude from the output cone 36. Can be suppressed.
実施例の動力伝達装置20では、リング60の位置がアウトプットコーン36の大径側端部であるときの動作について説明したが、これに限られず、リング60の位置がアウトプットコーン36の大径側端部を含む所定範囲内であるときには、実施例と同様の処理を行なえばよい。ここで、所定範囲は、インプットコーン34が変形する可能性のあるトルクがアウトプットシャフト38に作用し得る範囲や、インプットコーン34の変形などによってリング60の少なくとも一部がアウトプットコーン36からはみ出る可能性のあるトルクがアウトプットシャフト38に作用し得る範囲などを予め実験や解析によって定めて用いることができ、例えば、エンジン12の仕様やリング60の各位置における減速比などに基づいて得られるリング60の各位置についての出力トルクToutの最大値や、インプットコーン34やアウトプットコーン36,狭圧力調節機構50,リング60などの仕様などに基づいて定めることができる。また、この場合、リング60の位置が所定範囲内で出力トルクToutが閾値Tref以上のときには、リング60の位置がアウトプットコーン36の大径側端部から遠いほど所定距離Ls1から短くなる傾向の距離だけリング60をアウトプットコーン36の小径側にスライドさせるものとしてもよい。
In the power transmission device 20 of the embodiment, the operation when the position of the ring 60 is the large diameter side end portion of the output cone 36 has been described. However, the operation is not limited to this, and the position of the ring 60 is the large size of the output cone 36. When it is within a predetermined range including the radial end, the same processing as in the embodiment may be performed. Here, the predetermined range is a range in which a torque that may cause deformation of the input cone 34 can act on the output shaft 38, or at least a part of the ring 60 can protrude from the output cone 36 due to deformation of the input cone 34. A range in which a characteristic torque can act on the output shaft 38 can be determined and used in advance by experiment or analysis. For example, the ring 60 obtained based on the specifications of the engine 12 or the reduction ratio at each position of the ring 60 can be used. Can be determined based on the maximum value of the output torque Tout for each of these positions, the specifications of the input cone 34, the output cone 36, the narrow pressure adjusting mechanism 50, the ring 60, and the like. Further, in this case, when the position of the ring 60 is within a predetermined range and the output torque Tout is equal to or greater than the threshold value Tref, the position of the ring 60 tends to become shorter from the predetermined distance Ls1 as it is farther from the large-diameter side end of the output cone 36. The ring 60 may be slid to the smaller diameter side of the output cone 36 by the distance.
実施例の動力伝達装置20では、出力部材最大径時に出力トルクToutが閾値Tref以上のときには、所定距離Ls1を目標スライド距離Ls*に設定すると共に設定した目標スライド距離Ls*だけリング60をアウトプットコーン36の小径側にスライドさせるものとしたが、所定距離Ls1以外の距離(所定距離Ls1より長い距離または短い距離)を目標スライド距離Ls*に設定するものとしてもよいし、出力トルクToutやリング60の狭圧力などに応じた距離を目標スライド距離Ls*に設定するものとしてもよい。出力トルクToutに基づいて目標スライド距離Ls*を設定する場合、出力トルクToutと目標スライド距離Ls*との関係を予め定めて目標スライド距離設定用マップとしてROMに記憶しておき、出力トルクToutが与えられるとマップから対応する目標スライド距離Ls*を導出して設定するものとしてもよい。目標スライド距離設定用マップの一例を図8に示す。図8の例では、目標スライド距離Ls*は、出力トルクToutが閾値Trefより大きい閾値Tref2以上の領域では所定距離Ls1を設定し、出力トルクToutが閾値Tref以上で閾値Tref2未満の領域では出力トルクToutが大きいほど所定距離Ls1に向けて大きくなる傾向に設定するものとした。ここで、閾値Tref2は、アウトプットコーン36の基準位置からの移動距離が移動可能距離Lomaxに等しくなると想定される出力トルクToutの下限値やそれよりも若干小さいトルクなどを予め実験や解析などによって定めて用いることができる。また、出力トルクToutが閾値Tref以上で閾値Tref2未満のときにこのように目標スライド距離Ls*を設定するのは、出力トルクToutが大きくなるほどインプットコーン34が変形してリング60が軸方向に更に移動しリング60の少なくとも一部がアウトプットコーン36からはみ出しやすくなるという理由に基づく。このように目標スライド距離Ls*を設定することにより、出力トルクToutが閾値Tref以上で閾値Tref2未満のときに、リング60を必要以上にスライドさせるのを抑制することができ、CVT30の減速比が大きく変化するのを抑制することができる。
In the power transmission device 20 of the embodiment, when the output torque Tout is equal to or greater than the threshold Tref at the maximum output member diameter, the predetermined distance Ls1 is set to the target slide distance Ls * and the ring 60 is output for the set target slide distance Ls *. Although the slide is made to slide toward the small diameter side of the cone 36, a distance other than the predetermined distance Ls1 (a distance longer or shorter than the predetermined distance Ls1) may be set as the target slide distance Ls *, or the output torque Tout or the ring A distance corresponding to 60 narrow pressure or the like may be set as the target slide distance Ls *. When the target slide distance Ls * is set based on the output torque Tout, the relationship between the output torque Tout and the target slide distance Ls * is determined in advance and stored in the ROM as a target slide distance setting map. If given, the corresponding target slide distance Ls * may be derived from the map and set. An example of the target slide distance setting map is shown in FIG. In the example of FIG. 8, the target slide distance Ls * is set to a predetermined distance Ls1 in the region where the output torque Tout is greater than or equal to the threshold Tref2 greater than the threshold Tref, and in the region where the output torque Tout is greater than or equal to the threshold Tref and less than the threshold Tref2. The larger Tout, the larger the distance toward the predetermined distance Ls1. Here, the threshold value Tref2 is determined based on the lower limit value of the output torque Tout that is assumed that the movement distance from the reference position of the output cone 36 is equal to the movable distance Lomax, a torque slightly smaller than the output torque Tout, or the like. Can be used. The target slide distance Ls * is set in this way when the output torque Tout is equal to or greater than the threshold value Tref and less than the threshold value Tref2. This is based on the reason that at least part of the ring 60 moves and easily protrudes from the output cone 36. By setting the target slide distance Ls * in this way, when the output torque Tout is greater than or equal to the threshold Tref and less than the threshold Tref2, the ring 60 can be prevented from sliding more than necessary, and the reduction ratio of the CVT 30 can be reduced. A large change can be suppressed.
実施例の動力伝達装置20では、入力トルクTinに基づいて出力トルクToutを推定するものとしたが、出力トルクToutを取得するものであれば如何なるものとしてもよく、例えば、出力トルクTout自体を検出するものなどとしてもよい。
In the power transmission device 20 of the embodiment, the output torque Tout is estimated based on the input torque Tin. However, any device that acquires the output torque Tout may be used. For example, the output torque Tout itself is detected. It is good also as what to do.
実施例の動力伝達装置20では、位置検出センサ72は、スライダ66に取り付けられてリング60の位置を検出するものとしたが、リング60の位置を取得するものであれば如何なるものとしてもよく、例えば、トランスアクスルハウジング21aや保持部68などに取り付けられてリング60の位置を検出するものや、ガイドレール64に取り付けられてスライダ66の位置を検出することによってリング60の位置を推定するものなどとしてもよく、また、検出方式も機械式や光学式など如何なる方式としてもよい。
In the power transmission device 20 according to the embodiment, the position detection sensor 72 is attached to the slider 66 and detects the position of the ring 60. However, the position detection sensor 72 may be any apparatus that acquires the position of the ring 60. For example, it is attached to the transaxle housing 21a, the holding portion 68, etc. to detect the position of the ring 60, or is attached to the guide rail 64 to estimate the position of the ring 60 by detecting the position of the slider 66. The detection method may be any method such as a mechanical method or an optical method.
実施例の動力伝達装置20では、スライド機構62としては、トランスアクスルハウジング21aに回転自在に取り付けられたガイドレール64と、ガイドレール64の回転時に回転せずにガイドレール64に沿ってスライド可能なスライダ66と、スライダ66に取り付けられると共にリング60を回転自在に保持する保持部68と、ガイドレール64を回転させるモータ70とにより構成するものとしたが、リング60をスライドさせることにより減速比を変更可能なものであれば、如何なる機構により構成するものとしてもよい。
In the power transmission device 20 of the embodiment, the slide mechanism 62 includes a guide rail 64 that is rotatably attached to the transaxle housing 21a, and can slide along the guide rail 64 without rotating when the guide rail 64 rotates. The slider 66, the holding portion 68 that is attached to the slider 66 and rotatably holds the ring 60, and the motor 70 that rotates the guide rail 64 are configured. However, the reduction ratio can be reduced by sliding the ring 60. Any mechanism can be used as long as it can be changed.
実施例の動力伝達装置20では、狭圧力調節機構50としては、アウトプットシャフト38に取り付けられた固定部材52と、アウトプットコーン36に取り付けられた移動部材54と、固定部材52に形成された複数の半球状のボール受け52aと移動部材54に形成された複数の半球状のボール受け54aとの間に配置された複数のボール56とにより構成するものとしたが、アウトプットシャフト38に作用するトルクをアウトプットシャフト38の方向の力に変換してアウトプットコーン36に作用させることができるものであれば、如何なる機構により構成するものとしても構わない。また、インプットシャフト32に入力されるトルク(入力トルクTin)とCVT30の変速比(リング60の位置)とによって推定されるアウトプットシャフト38に作用するトルク(出力トルクTout)が大きいほどリング60への狭圧力が大きくなるように、油圧や電力を用いてリング60への狭圧力を調節する機構により構成するものとしても構わない。
In the power transmission device 20 of the embodiment, the narrow pressure adjusting mechanism 50 includes a fixing member 52 attached to the output shaft 38, a moving member 54 attached to the output cone 36, and a plurality of members formed on the fixing member 52. The hemispherical ball receiver 52a and the plurality of balls 56 arranged between the plurality of hemispherical ball receivers 54a formed on the moving member 54, the torque acting on the output shaft 38 Any mechanism can be used as long as it can be converted into a force in the direction of the output shaft 38 and applied to the output cone 36. Further, as the torque (output torque Tout) acting on the output shaft 38 estimated from the torque input to the input shaft 32 (input torque Tin) and the transmission ratio of the CVT 30 (the position of the ring 60) increases, It may be configured by a mechanism that adjusts the narrow pressure to the ring 60 using hydraulic pressure or electric power so that the narrow pressure becomes large.
実施例の動力伝達装置20では、インプットシャフト32とインプットコーン34とを一体的に形成するものとしたが、別体として形成するものとしてもよい。
In the power transmission device 20 of the embodiment, the input shaft 32 and the input cone 34 are integrally formed, but may be formed separately.
実施例の動力伝達装置20では、動力伝達機構20aにより、動力源としてのエンジン12からの動力を変速して左右の車輪88a,88bに伝達するものとしたが、動力源としては、エンジン12に代えてまたは加えてモータを用いるものとしてもよい。なお、動力源としてエンジンに代えてモータを用いる場合、動力伝達機構20aは、前後進切替機構24を備えないものとしてもよい。
In the power transmission device 20 of the embodiment, the power transmission mechanism 20a shifts the power from the engine 12 as a power source and transmits it to the left and right wheels 88a and 88b. Instead of or in addition, a motor may be used. When a motor is used as the power source instead of the engine, the power transmission mechanism 20a may not include the forward / reverse switching mechanism 24.
実施例の動力伝達装置20では、自動車10に搭載されるものとしたが、自動車10以外の移動体に搭載されるものとしてもよいし、建設設備などの移動しない設備に組み込まれるものとしてもよい。
In the power transmission device 20 of the embodiment, the power transmission device 20 is mounted on the automobile 10, but may be mounted on a moving body other than the automobile 10, or may be incorporated in a non-moving facility such as a construction facility. .
実施例の主要な要素と発明の概要の欄に記載した発明の主要な要素との対応関係について説明する。実施例では、CVT30が「無段変速機」に相当し、インプットコーン34が「入力部材」に相当し、アウトプットコーン36が「出力部材」に相当し、リング60が「伝達部材」に相当し、スライド機構62が「スライド手段」に相当し、狭圧力調節機構50が「狭圧力調節手段」に相当し、位置検出センサ72が「位置取得手段」に相当し、入力トルクTinに基づいて出力トルクToutを推定する図7の出力部材最大径時制御ルーチンのステップS110の処理を実行する電子制御ユニット90が「出力トルク取得手段」に相当し、リング60の位置がアウトプットコーン36の大径側端部である出力部材最大径時に出力トルクToutが閾値Tref以上のときには、リング60をアウトプットコーン36の小径側にスライドさせるスライド処理を実行する図7の出力部材最大径時制御ルーチンのステップS130,S140の処理を実行する電子制御ユニット90が「スライド制御手段」に相当する。
The correspondence between the main elements of the embodiment and the main elements of the invention described in the Summary of Invention will be described. In the embodiment, the CVT 30 corresponds to a “continuously variable transmission”, the input cone 34 corresponds to an “input member”, the output cone 36 corresponds to an “output member”, and the ring 60 corresponds to a “transmission member”. The slide mechanism 62 corresponds to “slide means”, the narrow pressure adjustment mechanism 50 corresponds to “narrow pressure adjustment means”, the position detection sensor 72 corresponds to “position acquisition means”, and is based on the input torque Tin. The electronic control unit 90 that executes the process of step S110 of the output member maximum diameter control routine of FIG. 7 for estimating the output torque Tout corresponds to the “output torque acquisition means”, and the position of the ring 60 is the size of the output cone 36. When the output torque Tout is greater than or equal to the threshold Tref at the maximum diameter of the output member that is the diameter side end, the ring 60 is slid to the small diameter side of the output cone 36. Electronic control unit 90 executing the processing in steps S130, S140 of the output member up 径時 control routine of FIG. 7 that performs a sliding process corresponds to "slide control means."
なお、実施例の主要な要素と発明の概要の欄に記載した発明の主要な要素との対応関係は、実施例が発明の概要の欄に記載した発明を実施するための形態を具体的に説明するための一例であることから、発明の概要の欄に記載した発明の要素を限定するものではない。即ち、発明の概要の欄に記載した発明についての解釈はその欄の記載に基づいて行なわれるべきものであり、実施例は発明の概要の欄に記載した発明の具体的な一例に過ぎないものである。
The correspondence between the main elements of the embodiment and the main elements of the invention described in the summary section of the invention is a specific form of the embodiment for carrying out the invention described in the summary section of the invention. Since this is an example for explanation, the elements of the invention described in the summary section of the invention are not limited. That is, the interpretation of the invention described in the Summary of Invention column should be made based on the description in that column, and the examples are only specific examples of the invention described in the Summary of Invention column. It is.
以上、本発明を実施するための形態について実施例を用いて説明したが、本発明はこうした実施例に何等限定されるものではなく、本発明の要旨を逸脱しない範囲内において、種々なる形態で実施し得ることは勿論である。
As mentioned above, although the form for implementing this invention was demonstrated using the Example, this invention is not limited at all to such an Example, In the range which does not deviate from the summary of this invention, it is with various forms. Of course, it can be implemented.
本発明は、動力伝達装置の製造産業などに利用可能である。
The present invention can be used in the power transmission device manufacturing industry.
Claims (4)
- 入力軸と該入力軸に平行に配置された出力軸とを有し、該入力軸に入力された動力を無段階に変速して該出力軸に出力する無段変速機を備える動力伝達装置であって、
前記入力軸に接続された円錐形状の入力部材と、
前記出力軸に接続され、前記入力部材とは逆向きに配置された円錐形状の出力部材と、 前記入力部材と前記出力部材とに狭圧され、該入力部材と該出力部材との間で動力の伝達を行なう環状の伝達部材と、
前記伝達部材をスライドさせることにより変速比を変更可能なスライド手段と、
前記出力軸に作用するトルクである出力トルクが大きいほど大きくなる傾向に前記伝達部材に作用する狭圧力を調節する狭圧力調節手段と、
前記伝達部材の位置を取得する位置取得手段と、
前記出力トルクを取得する出力トルク取得手段と、
前記取得された伝達部材の位置が前記出力部材の大径側端部を含む所定範囲内であり且つ前記取得された出力トルクが所定トルク以上のとき、前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御するスライド制御手段と、
を備える動力伝達装置。 A power transmission device having an input shaft and an output shaft arranged in parallel to the input shaft, and comprising a continuously variable transmission that continuously shifts the power input to the input shaft and outputs the power to the output shaft. There,
A conical input member connected to the input shaft;
A conical output member connected to the output shaft and disposed opposite to the input member; and the pressure between the input member and the output member is reduced between the input member and the output member. An annular transmission member for transmitting
Slide means capable of changing a gear ratio by sliding the transmission member;
Narrow pressure adjusting means for adjusting the narrow pressure acting on the transmission member in a tendency to increase as the output torque, which is the torque acting on the output shaft, increases.
Position acquisition means for acquiring the position of the transmission member;
Output torque acquisition means for acquiring the output torque;
When the acquired position of the transmission member is within a predetermined range including the large-diameter side end of the output member and the acquired output torque is equal to or greater than a predetermined torque, the transmission member is placed on the small-diameter side of the output member. Slide control means for controlling the slide means to slide;
A power transmission device comprising: - 請求項1記載の動力伝達装置であって、
前記スライド制御手段は、前記出力部材の移動可能距離以上の距離だけ前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御する手段である、
動力伝達装置。 The power transmission device according to claim 1,
The slide control means is means for controlling the slide means so that the transmission member slides toward the small diameter side of the output member by a distance that is equal to or greater than the movable distance of the output member.
Power transmission device. - 請求項1記載の動力伝達装置であって、
前記スライド制御手段は、前記取得された出力トルクが大きいほど大きくなる傾向の距離だけ前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御する手段である、
動力伝達装置。 The power transmission device according to claim 1,
The slide control means is means for controlling the slide means so that the transmission member slides toward the small diameter side of the output member by a distance that tends to increase as the acquired output torque increases.
Power transmission device. - 入力軸に接続された円錐形状の入力部材と、出力軸に接続され前記入力部材とは逆向きに配置された円錐形状の出力部材と、前記入力部材と前記出力部材とに狭圧され該入力部材と該出力部材との間で動力の伝達を行なう環状の伝達部材と、前記伝達部材をスライドさせることにより変速比を変更可能なスライド手段と、前記出力軸に作用するトルクである出力トルクが大きいほど大きくなる傾向に前記伝達部材に作用する狭圧力を調節する狭圧力調節手段と、を有し、前記入力軸に入力された動力を無段階に変速して前記出力軸に出力する無段変速機を備える動力伝達装置の制御方法であって、
前記伝達部材の位置が前記出力部材の大径側端部を含む所定範囲内であり且つ前記出力トルクが所定トルク以上のとき、前記伝達部材が前記出力部材の小径側にスライドするよう前記スライド手段を制御する、
ことを特徴とする動力伝達装置の制御方法。 A conical input member connected to the input shaft, a conical output member connected to the output shaft and disposed in the direction opposite to the input member, and the input member and the output member are subjected to a narrow pressure. An annular transmission member that transmits power between the member and the output member, slide means that can change a gear ratio by sliding the transmission member, and output torque that is torque acting on the output shaft A narrow pressure adjusting means for adjusting a narrow pressure acting on the transmission member so as to increase as it increases, continuously changing the power input to the input shaft and outputting it to the output shaft. A method for controlling a power transmission device including a transmission,
When the position of the transmission member is within a predetermined range including the large-diameter end of the output member and the output torque is equal to or greater than a predetermined torque, the sliding means is configured to slide the transmission member to the small-diameter side of the output member. To control the
A control method for a power transmission device.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010-073262 | 2010-03-26 | ||
JP2010073262A JP2011202791A (en) | 2010-03-26 | 2010-03-26 | Power transmission device and control method therefor |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011118317A1 true WO2011118317A1 (en) | 2011-09-29 |
Family
ID=44672889
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2011/053862 WO2011118317A1 (en) | 2010-03-26 | 2011-02-22 | Power transmission device and control method therefor |
Country Status (2)
Country | Link |
---|---|
JP (1) | JP2011202791A (en) |
WO (1) | WO2011118317A1 (en) |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006336861A (en) * | 2005-05-30 | 2006-12-14 | Getrag Ford Transmissions Gmbh | Cone ring type transmission |
JP2009243559A (en) * | 2008-03-31 | 2009-10-22 | Aisin Aw Co Ltd | Power transmission device |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH1163140A (en) * | 1997-08-22 | 1999-03-05 | Seishiro Yoshihara | Continuously variable transmission equipped with idle pulley |
-
2010
- 2010-03-26 JP JP2010073262A patent/JP2011202791A/en active Pending
-
2011
- 2011-02-22 WO PCT/JP2011/053862 patent/WO2011118317A1/en active Application Filing
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2006336861A (en) * | 2005-05-30 | 2006-12-14 | Getrag Ford Transmissions Gmbh | Cone ring type transmission |
JP2009243559A (en) * | 2008-03-31 | 2009-10-22 | Aisin Aw Co Ltd | Power transmission device |
Also Published As
Publication number | Publication date |
---|---|
JP2011202791A (en) | 2011-10-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN107061653B (en) | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components thereof | |
US10293688B2 (en) | Control device for four-wheel-drive vehicle and control method for four-wheel-drive vehicle | |
US10145472B2 (en) | Transfer for vehicle | |
US9222579B2 (en) | Belt-drive continuously variable transmission | |
US20030125150A1 (en) | Enhanced shift couplers for shift-on-the-go transmission | |
CN109642647B (en) | Belt wheel propulsion device of automatic transmission and control device of automatic transmission | |
US9751404B2 (en) | Transfer | |
EP2631508B1 (en) | Multi-CVT drive system having epicycle gear set | |
US20200347916A1 (en) | Apparatus for driving electric vehicle and method of controlling the same | |
US8413546B2 (en) | Power transmitting apparatuses | |
US20130244819A1 (en) | Automated manual transmission for vehicle | |
KR20150007307A (en) | Control device for vehicle transmission | |
US10035414B1 (en) | Automatically-shiftable hybrid transaxle | |
US11420610B2 (en) | Vehicle and control method of the same | |
JP2019148334A (en) | Motor vehicle gearbox with range selector device | |
US20160084362A1 (en) | Continuously variable transmission for vehicle | |
US20180058575A1 (en) | Shift-by-wire control of vehicle transmission | |
WO2011118317A1 (en) | Power transmission device and control method therefor | |
US10286772B2 (en) | Powertrain including an electric machine, an internal combustion engine and a continuously variable transmission | |
JP5018923B2 (en) | POWER OUTPUT DEVICE, ITS CONTROL METHOD, AND POWER TRANSMISSION DEVICE | |
WO2011118529A1 (en) | Power transmission device | |
Shinojima et al. | Development of the next-generation half-toroidal CVT with geared neutral and power-split systems for 450 Nm engines | |
US9163711B2 (en) | Automated manual transmission for vehicle | |
US10385967B2 (en) | Method and apparatus to control a continuously variable transmission | |
JP4779414B2 (en) | Fastening force control device for starting friction element |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 11759125 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 11759125 Country of ref document: EP Kind code of ref document: A1 |