WO2016093200A1 - Dispositif de transmission à vitesse variable - Google Patents

Dispositif de transmission à vitesse variable Download PDF

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Publication number
WO2016093200A1
WO2016093200A1 PCT/JP2015/084332 JP2015084332W WO2016093200A1 WO 2016093200 A1 WO2016093200 A1 WO 2016093200A1 JP 2015084332 W JP2015084332 W JP 2015084332W WO 2016093200 A1 WO2016093200 A1 WO 2016093200A1
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WO
WIPO (PCT)
Prior art keywords
control
input shaft
output shaft
planetary gear
shaft
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PCT/JP2015/084332
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English (en)
Japanese (ja)
Inventor
輝明 桜井
孝 渡部
Original Assignee
株式会社日立ニコトランスミッション
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Application filed by 株式会社日立ニコトランスミッション filed Critical 株式会社日立ニコトランスミッション
Priority to CN201580063757.8A priority Critical patent/CN107002831B/zh
Priority to RU2017123768A priority patent/RU2668772C1/ru
Publication of WO2016093200A1 publication Critical patent/WO2016093200A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid 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
    • F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion

Definitions

  • the present invention relates to a variable speed device that transmits the rotational power of a prime mover to a driven machine and changes the rotational speed of the driven machine.
  • inverter control Inverter control has an advantage that there is less loss compared to damper control on the discharge side and suction side of the fluid machine.
  • devices that perform inverter control are relatively expensive but have a short life span, and the supply of parts may be stopped. Has the disadvantage of becoming high.
  • variable speed device By mechanically configuring the variable speed device, not only the life of the device is extended, but also the procurement and production of parts are facilitated, so that it can be used for a long period of time. Moreover, since an inexpensive general-purpose motor can be used, the equipment cost can be reduced.
  • a mechanical variable speed device a planetary gear mechanism and a fluid coupling (torque converter) are combined to reduce mechanical loss especially during low-speed operation and increase power transmission efficiency.
  • torque converter fluid coupling
  • variable speed device described in Patent Document 1 distributes a part of the rotational power of the input shaft connected to the internal gear of the planetary gear mechanism to the fluid coupling having movable guide vanes.
  • the rotational speed of the output shaft connected to the planetary gear carrier is changed by changing the rotational speed of the sun gear by the control power output from the fluid coupling.
  • the output torque has a characteristic that the output torque is proportional to the square of the rotational speed on the input side and the fifth power of the size (size) of the fluid coupling. Therefore, the control power output from the fluid coupling is determined only by the rotational speed of the motor and the size of the fluid coupling regardless of the output (torque) of the motor. Therefore, in the design of the variable speed device described in Patent Document 1, it is necessary to prepare a large number of fluid coupling sizes in advance and select a fluid coupling having a size according to the use conditions from among them. In addition to costly to enhance the variations, optimal design may be difficult depending on the usage conditions.
  • variable speed device when changing the operating conditions after the variable speed device is once installed, it is not only necessary to change the fluid coupling to one of a different size, but if it is difficult to change only the fluid coupling, the variable speed device Since the whole has to be renewed, it is very expensive. Furthermore, since the fluid coupling and the planetary gear mechanism are coaxially arranged, the degree of freedom of arrangement of each part is low. For example, when the size of the fluid coupling needs to be increased, for example, when the rotational speed of the motor is low. In addition, the overall size of the variable speed device, particularly the axial dimension, becomes large, and it may be difficult to fit in the installation space.
  • the present invention seeks to provide a variable speed device that facilitates optimal design and can increase efficiency more than before.
  • the present invention provides an input shaft to which rotational power is input from the outside, an output shaft that outputs rotational power to the outside, and the input shaft and the output to any two of an internal gear, a sun gear, and a planetary gear carrier.
  • the shift control mechanism includes a control input shaft and a control output shaft that are separate from the input shaft, an input side transmission mechanism that transmits a part of the rotational power of the input shaft to the control input shaft, A transmission mechanism that transmits the rotational power of the control input shaft to the control output shaft and changes the rotational speed of the control output shaft, and the input of the internal gear, the sun gear, and the planetary gear carrier. Characterized in that it comprises an output side transmission mechanism shaft or said output shaft for transmitting the rotational power of the control output shaft that is not connected, and a variable speed device.
  • the present invention is also characterized in that, in the variable speed device of the above means, the input transmission mechanism is configured such that the rotational speed of the control input shaft is higher than the rotational speed of the input shaft.
  • the present invention is also characterized in that in the variable speed device of the above means, the speed change mechanism is arranged offset in the axial direction of the input shaft with respect to the planetary gear mechanism.
  • the present invention is also characterized in that, in the variable speed device of the above means, the speed change mechanism includes a fluid coupling.
  • the present invention is also characterized in that, in the variable speed device of the above means, the fluid coupling includes a movable guide vane.
  • the present invention is also characterized in that, in the variable speed device of the above means, the speed change mechanism includes a clutch capable of controlling a slip ratio.
  • the present invention is also characterized in that, in the variable speed device of the above means, the input side transmission mechanism is constituted by a gear train having idle gears.
  • variable speed device can achieve an excellent effect of facilitating optimum design and improving efficiency more than in the past.
  • FIG. It is the skeleton figure which showed the structure of the variable speed apparatus which concerns on embodiment of this invention. It is the skeleton figure which showed an example when not making a transmission mechanism offset with respect to a planetary gear mechanism.
  • (A) to (c) are skeleton diagrams showing examples of other connection modes to the planetary gear mechanism.
  • (A) And (b) is the skeleton figure which showed the example at the time of arrange
  • FIG. It is the skeleton figure which showed an example at the time of providing a clutch in a transmission mechanism. It is a figure showing an example at the time of providing a plurality of shift control mechanisms.
  • FIG. 1 is a skeleton diagram showing the configuration of the variable speed apparatus 1 according to the present embodiment.
  • the variable speed apparatus 1 includes a casing 10, an input shaft 20 and an output shaft 30 that are rotatably supported by the casing 10, and a planetary gear mechanism to which the input shaft 20 and the output shaft 30 are connected. 40, a shift control mechanism 50 that supplies control power for shifting the output shaft 30 to the planetary gear mechanism 40, and a control device 60 that controls the operation of the shift control mechanism 50.
  • the casing 10 rotatably supports each axis of the variable speed device 1 and accommodates and covers each part inside.
  • the casing 10 is also provided with a lubrication system for supplying lubricating oil to each part (not shown).
  • the input shaft 20 receives rotational power from an external motor (not shown) such as a motor.
  • An external prime mover is connected to one end (left end in the figure) of the input shaft 20, and an internal gear of the planetary gear mechanism 40 is connected to the other end (right end in the figure).
  • the output shaft 30 is for outputting rotational power to an external driven machine (not shown) such as a pump or a blower.
  • a sun gear 42 of the planetary gear mechanism 40 is connected to one end (left end in the figure) of the output shaft 30, and an external driven machine is connected to the other end (right end in the figure). Therefore, the variable speed apparatus 1 of this embodiment is used when the rotational speed of the driven machine is higher than the rotational speed of the prime mover.
  • the planetary gear mechanism 40 accelerates the rotational power of the input shaft 20 and transmits it to the output shaft 30.
  • the planetary gear mechanism 40 steps the rotational speed of the output shaft 30 within a predetermined range with respect to a constant rotational speed of the input shaft 20.
  • the planetary gear mechanism 40 includes an internal gear 41, a sun gear 42, and three planetary gears 43.
  • the planetary gear mechanism 40 includes a planetary gear carrier 44 that rotatably supports the three planetary gears 43 and that can rotate about the same rotation center as the internal gear 41 and the sun gear 42.
  • the input shaft 20 is connected to the internal gear 41 of the planetary gear mechanism 40, and the output shaft 30 is connected to the sun gear 42.
  • a transmission control mechanism 50 is connected to the planetary gear carrier 44 of the planetary gear mechanism 40. That is, the planetary gear mechanism 40 of the present embodiment changes the rotation speed of the output shaft 30 steplessly by changing the rotation speed of the planetary gear carrier 44 by the speed change control mechanism 50.
  • the shift control mechanism 50 changes the rotational speed of the planetary gear carrier 44 of the planetary gear mechanism 40 as described above.
  • the speed change control mechanism 50 includes a control input shaft 51 and a control output shaft 52 arranged substantially parallel to the input shaft 20 and the output shaft 30, and the control input shaft 51.
  • An input-side transmission mechanism 53 connected to the transmission, a transmission mechanism 54 connected between the control input shaft 51 and the control output shaft 52, and the control output shaft 52 to the planetary gear carrier 44 of the planetary gear mechanism 40.
  • an output-side transmission mechanism 55 to be connected.
  • the control input shaft 51 inputs rotational power from the input shaft 20 to the speed change mechanism 54, and the control output shaft 52 outputs rotational power from the speed change mechanism 54 to the output side transmission mechanism 55.
  • the degree of freedom of arrangement of each part of the variable speed device 1 is increased.
  • the efficiency of the variable speed device 1 can be increased.
  • the input side transmission mechanism 53 transmits a part of the rotational power of the input shaft 20 to the control input shaft 51.
  • the input side transmission mechanism 53 of the present embodiment is provided between the drive gear 53a provided on the input shaft 20, the driven gear 53b provided on the control input shaft 51, and the drive gear 53a and the driven gear 53b. And an idler gear 53c.
  • the input-side transmission mechanism 53 is configured such that the rotational speed of the control input shaft 51 is higher than the rotational speed of the input shaft 20. That is, the input side transmission mechanism 53 of the present embodiment is a speed increaser.
  • the transmission mechanism 54 transmits the rotational power of the control input shaft 51 to the control output shaft 52, and keeps the rotational speed of the control output shaft 52 within a predetermined range with respect to a constant rotational speed of the control input shaft 51. Is a stepless change.
  • the speed change mechanism 54 is composed of a fluid coupling (torque converter).
  • the speed change mechanism 54 includes a pump impeller 54a to which the control input shaft 51 is connected and a turbine impeller 54b to which the control output shaft 52 is connected, and the flow caused by the rotation of the pump impeller 54a. By rotating the turbine impeller 54b, the rotational power is transmitted.
  • the speed change mechanism 54 also includes a fixed guide blade 54c and a movable guide blade 54d that direct the fluid flowing out from the turbine impeller 54b to the pump impeller 54a again.
  • a fixed guide blade 54c By changing the angle of the movable guide blade 54d, the turbine blade
  • the rotation speed of the vehicle 54b that is, the rotation speed of the control output shaft 52 can be adjusted steplessly.
  • the angle of the movable guide blade 54d is changed by an actuator 61 controlled by the control device 60.
  • the output transmission mechanism 55 transmits the rotational power of the control output shaft 52 to the planetary gear carrier 44 of the planetary gear mechanism 40.
  • the output side transmission mechanism 55 of the present embodiment is connected to the planetary gear carrier 44 via a hollow shaft 45 disposed so as to cover the outer periphery of the output shaft 30, and is a drive gear provided on the control output shaft 52. 55a and a driven gear 55b provided on the hollow shaft 45.
  • the output side transmission mechanism 55 reduces the rotation speed of the control output shaft 52 with a predetermined reduction ratio and transmits it to the planetary gear carrier 44 to rotate the planetary gear carrier 44.
  • the rotational speed of the output shaft 30 changes according to the rotational speed of the planetary gear carrier 44, and a shift is performed.
  • the control device 60 includes a CPU, a ROM, a RAM, and the like, and controls the shift control mechanism 50.
  • the control device 60 controls the actuator 61 based on a command from an external control device (not shown) and the rotational speed of the output shaft 30 detected by the rotational speed detector 62, and adjusts the angle of the movable guide vane 54d. .
  • the rotational speed of the control output shaft 52 changes while the rotational speed of the control input shaft 51 is constant, the rotational speed of the planetary gear carrier 44 of the planetary gear mechanism 40 also changes.
  • the rotational speed of the planetary gear carrier 44 changes, the rotational speed of the sun gear 42 changes, and finally the rotational speed of the output shaft 30 changes, that is, the driven machine is shifted.
  • a part of the rotational power input to the input shaft 20 is distributed to the speed change control mechanism 50 as control power for changing the rotational speed of the output shaft 30.
  • the rotational speed of the output shaft 30 is changed by inputting the control power to the planetary gear mechanism 40 after adjusting the rotational speed.
  • the speed change mechanism 54 in the speed change control mechanism 50 is provided on a shaft different from the input shaft 20, thereby facilitating the optimum design of the variable speed apparatus 1 and increasing the efficiency.
  • a fluid coupling having a smaller size can be used as the speed change mechanism 54. That is, when the output torque of the fluid coupling is proportional to the square of the rotational speed on the input side and the fifth power of the size (size) of the fluid coupling, for example, the rotational speed of the input shaft 51 for control on the input side is By setting it to twice the number of rotations, the size of the fluid coupling can be reduced by up to about 24% compared to the conventional technique in which the fluid coupling is directly connected to the input shaft 20.
  • variable speed device 1 it is possible to use a fluid coupling that is more compact than the conventional variable speed device, and thus, the entire variable speed device 1 can be configured compactly and efficiently. Moreover, it is also possible to realize a large-capacity and high-efficiency variable speed device 1 by utilizing an existing fluid coupling without using a custom-sized fluid coupling.
  • the rotational speed of the control input shaft 51 can be easily adjusted by setting the speed increasing ratio of the input side transmission mechanism 53, the torque of the control output shaft 52 is appropriately adjusted to It is possible to input various control powers to the planetary gear mechanism 40.
  • the efficiency of the variable speed apparatus 1 be improved, but it is possible to cope with a wide range of use conditions by using one size of fluid coupling. That is, in this embodiment, it is possible to perform an optimum design corresponding to a wide range of use conditions even with a small size variation of the fluid coupling, and reduce the manufacturing cost while improving the efficiency and versatility of the variable speed device 1. It is possible to do.
  • the speed increasing ratio can be adjusted without changing the distance between the input shaft 20 and the control input shaft 51. Not only is it easy, but also when the usage conditions are changed after manufacturing or installation of the variable speed device 1, the speed change ratio is changed according to the new usage conditions to meet the required specifications, It is possible to maintain high efficiency.
  • the speed change mechanism 54 is provided on a separate shaft from the input shaft 20 to increase the degree of freedom of arrangement of the speed change mechanism 54 formed of a fluid coupling that tends to have a relatively large outer diameter. . That is, since the speed change mechanism 54 can be disposed at any of the upper, lower, left and right positions of the input shaft 20, the outer dimensions of the variable speed apparatus 1 can be set to dimensions corresponding to the installation space. Further, as described above, in the present embodiment, a fluid coupling having a smaller size than the conventional one can be used as the transmission mechanism 54, and the transmission mechanism 54 is replaced with the planetary gear mechanism 40 as shown in FIG. On the other hand, by offsetting in the axial direction of the input shaft 20, the width direction dimension or the height direction dimension of the variable speed apparatus 1 can be shortened, and the variable speed apparatus 1 can be configured compactly.
  • FIG. 2 is a skeleton diagram showing an example in which the speed change mechanism 54 is not offset with respect to the planetary gear mechanism 40.
  • the width direction dimension or the height direction dimension increases, but the axial dimension (in the figure). Therefore, even when the distance between the prime mover and the driven machine is short, the highly efficient variable speed apparatus 1 can be installed.
  • variable speed device 1 Next, examples of other forms of the variable speed device 1 will be described.
  • connection modes to the planetary gear mechanism 40 are skeleton diagrams showing examples of other connection modes to the planetary gear mechanism 40.
  • FIG. 1 the input shaft 20 is connected to the internal gear 41
  • the output shaft 30 is connected to the sun gear 42
  • the speed change control mechanism 50 is connected to the planetary gear carrier 44.
  • the connection mode to 40 may be other modes.
  • the connection mode to the planetary gear mechanism 40 is such that the input shaft 20 is connected to the planetary gear carrier 44, the output shaft 30 is connected to the sun gear 42, and the speed change control mechanism 50 is connected. May be connected to the internal gear 41.
  • the shift control mechanism 50 may be connected to the planetary gear carrier 44, or the input shaft 20 is connected to the sun gear 42 and the output shaft 30 is connected to the planetary gear carrier 44 as shown in FIG. 44 and the shift control mechanism 50 may be connected to the internal gear 41.
  • the speed change control mechanism 50 is connected to the planetary gear mechanism 40 via a hollow shaft 45 disposed so as to cover the outer periphery of the input shaft 20. Become.
  • connection mode to the planetary gear mechanism 40 is not particularly limited, and may be appropriately set according to the ratio of the rotational speed of the prime mover and the driven machine.
  • the connection mode shown in FIGS. This can be realized without greatly changing the arrangement configuration of each part.
  • any of the connection modes since appropriate control power can be input to the planetary gear mechanism 40 by adjusting the rotation speed of the control input shaft 51, high efficiency can be achieved.
  • FIG. 4 (a) and 4 (b) are skeleton diagrams showing an example in which the input shaft 20 and the output shaft 30 are arranged so as to be offset with respect to the central axis of the planetary gear mechanism 40.
  • the input shaft 20 is connected to the planetary gear mechanism 40 via the input side offset transmission mechanism 70 and the input side offset shaft 21.
  • the output shaft 30 is connected to the planetary gear mechanism 40 via the output-side offset transmission mechanism 80 and the hollow shaft 45.
  • the input-side offset transmission mechanism 70 is configured to include a drive gear 71 provided on the input shaft 20 and a driven gear 72 provided on the input-side offset shaft 21, and one end of the input-side offset shaft 21 ( The right end in the figure is connected to the internal gear 41 or the planetary gear carrier 44 of the planetary gear mechanism 40.
  • the output-side offset transmission mechanism 80 includes a drive gear 81 provided on the hollow shaft 45 and a driven gear 82 provided on the output shaft 30, and the hollow shaft 45 has one end ( The left end in the figure is connected to the planetary gear carrier 44 or the internal gear 41.
  • an output side offset shaft 46 penetrating through the inside of the hollow shaft 45 is connected to the sun gear 42 of the planetary gear mechanism 40, and the speed change control mechanism 50 is connected to the output side offset shaft.
  • the sun gear 42 is connected via 46.
  • the input shaft 20 and the output shaft 30 can be arranged in accordance with the positions of the prime mover and the driven machine. Further, by offsetting the output shaft 30 from the central axis of the planetary gear mechanism 40, the speed change control mechanism 50 can be connected to the sun gear 42 of the planetary gear mechanism 40. Therefore, the versatility of the variable speed device 1 is increased. Can be increased.
  • the input shaft 20 and the output shaft 30 can be offset from the central axis of the planetary gear mechanism 40 even when other connection modes to the planetary gear mechanism 40 are employed. Further, only one of the input shaft 20 and the output shaft 30 may be offset. 4A and 4B, the input-side offset transmission mechanism 70 is also used as a part of the input-side transmission mechanism 53. However, the input-side offset transmission mechanism 70 is used as the input-side transmission. It may be provided separately from the mechanism 53.
  • FIG. 5 is a skeleton diagram showing an example when the clutch 90 is provided in the transmission mechanism 54.
  • a clutch 90 capable of controlling the slip ratio and a fluid coupling 91 having no movable guide vanes are provided.
  • the clutch 90 includes a plurality of clutch plates 90a and a clutch piston 90b that presses these clutch plates 90a to contact each other.
  • the fluid coupling 91 includes a pump impeller 91a, a turbine impeller 91b, and a fixed guide vane 91c.
  • the input side of the clutch 90 is connected to the control input shaft 51, and the output side is connected to the pump impeller 91a of the fluid coupling 91 via the intermediate shaft 90c.
  • the turbine impeller 91 b of the fluid coupling 91 is connected to the control output shaft 52.
  • the control device 60 controls the slip ratio of the clutch 90 by controlling the pressing force of the clutch piston 90b, whereby the rotation of the intermediate shaft 90c with respect to a constant rotational speed of the control input shaft 51. Change the number.
  • the fluid coupling 91 absorbs the shock of the rotation speed change by the clutch 90 and smoothly changes the rotation speed, and transmits torque rotational power based on the characteristics of the fluid coupling 91 to the control output shaft 52.
  • the variable speed device 1 may be provided with the clutch 90 capable of controlling the slip ratio in the speed change mechanism 54, and in this case also, the variable speed device 1 exhibits the same function as the example shown in FIGS. be able to.
  • the fluid coupling 91 may be omitted, and the speed change mechanism 54 may be configured from only the clutch 90.
  • FIG. 6 is a diagram showing an example when a plurality of shift control mechanisms 50 are provided.
  • a plurality of shift control mechanisms 50 may be provided.
  • control power may be simultaneously input from the plurality of shift control mechanisms 50 to the planetary gear mechanism 40, or one of them may be backed up.
  • a plurality of shift control mechanisms 50 may be used alternately.
  • a clutch or the like that switches connection to the input shaft 20 and connection to the input shaft 20 may be provided.
  • the speed change mechanism 54 in the speed change control mechanism 50 is provided on a shaft different from the input shaft 20, the degree of freedom of arrangement of each part is increased. It is possible to arrange efficiently. Further, by providing a plurality of speed change control mechanisms 50, it is possible to extend the life of the variable speed device 1 and to facilitate quick recovery from trouble.
  • variable speed apparatus 1 includes the input shaft 20 to which rotational power is input from the outside, the output shaft 30 that outputs rotational power to the outside, the internal gear 41, the sun gear 42, and A planetary gear mechanism 40 in which the input shaft 20 and the output shaft 30 are connected to any two of the planetary gear carriers 44, and the input shaft 20 or the output shaft of the internal gear 41, the sun gear 42, and the planetary gear carrier 44.
  • a shift control mechanism 50 that changes the number of revolutions, although not connected to the control shaft 30.
  • the shift control mechanism 50 includes a control input shaft 51 and a control output shaft 52 that are different from the input shaft 20, and a control An input-side transmission mechanism 53 that transmits a part of the rotational power of the input shaft 20 to the input shaft 51, and the rotational power of the control input shaft 51 to the control output shaft 52 are transmitted to the control output shaft 52.
  • change Output side transmission mechanism for transmitting the rotational power of the control output shaft 52 to the transmission gear mechanism 54, the internal gear 41, the sun gear 42 and the planetary gear carrier 44 to which the input shaft 20 or the output shaft 30 is not connected. 55.
  • the rotational speed of the rotational power distributed to the speed change control mechanism 50 can be set appropriately, and the degree of freedom of arrangement of each part of the variable speed device 1 is increased. It is easy to make an optimum design according to the above, and the variable speed device 1 can be configured more efficiently than before.
  • the input-side transmission mechanism 53 is configured such that the rotational speed of the control input shaft 51 is higher than the rotational speed of the input shaft 20. By doing so, it is possible to apply a small-sized fluid coupling to the speed change control mechanism 50, and thus the variable speed device 1 can be configured with high efficiency and compactness.
  • the speed change mechanism 54 is arranged to be offset in the axial direction of the input shaft 20 with respect to the planetary gear mechanism 40. By doing so, the width direction dimension or the height direction dimension of the variable speed device 1 can be shortened while realizing high efficiency by providing the speed change mechanism 54 on a separate shaft from the planetary gear mechanism 40. .
  • the speed change mechanism 54 includes a fluid coupling 91 or a fluid coupling 91. By doing so, a smooth speed change without a shock becomes possible, and the power transmission efficiency and the speed change efficiency can be enhanced by utilizing the characteristics of the fluid coupling.
  • the fluid coupling constituting the speed change mechanism 54 includes a movable guide blade 54d.
  • the transmission mechanism 54 may include a clutch 90 that can control the slip ratio. Even if it does in this way, the function equivalent to the case provided with 54 d of movable guide blades can be exhibited.
  • the input side transmission mechanism 53 is composed of a gear train having an idle gear 53c.
  • variable speed apparatus according to the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.
  • shape and arrangement configuration of each part of the variable speed device 1 are not limited to those shown in the above embodiment, and any other arbitrary shape and arrangement configuration can be adopted.
  • control input shaft 51 and the control output shaft 52 are not limited to those arranged substantially in parallel with the input shaft 20.
  • a bevel gear is provided in the input side transmission mechanism 53 and the output side transmission mechanism 55.
  • control input shaft 51 and the control output shaft 52 may be disposed so as to be substantially orthogonal to the input shaft 20.
  • the input side transmission mechanism 53 may not include an idle gear
  • the output side transmission mechanism 55, the input side offset transmission mechanism 70, and the output side offset transmission mechanism 80 include idle gears. Also good.
  • the number of gears constituting the input side transmission mechanism 53, the output side transmission mechanism 55, the input side offset transmission mechanism 70, and the output side offset transmission mechanism 80 is not particularly limited.
  • the input side transmission mechanism 53, the output side transmission mechanism 55, the input side offset transmission mechanism 70, and the output side offset transmission mechanism 80 are configured by known transmission mechanisms other than the gear train, such as a chain transmission mechanism and a belt transmission mechanism. It may be a thing.
  • the speed change mechanism 54 is not limited to a fluid coupling having a movable guide vane 54d or a mechanism that changes the number of revolutions of the control output shaft 52 by a clutch 90 that can control the slip rate.
  • a planetary gear mechanism or a differential gear mechanism For example, the rotational speed of the control output shaft 52 may be changed by another known mechanism.
  • variable speed device can be used in various fields such as various industrial machines and transport machines that require transmission of power accompanied by gear shifting.

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Abstract

L'invention concerne un dispositif de transmission à vitesse variable dont la conception optimale peut être facilitée et l'efficacité améliorée par rapport aux antériorités. Le dispositif de transmission à vitesse variable (1) selon l'invention comprend : un mécanisme d'engrenage planétaire (40) auquel sont reliés un arbre d'entrée (20) et un arbre de sortie (30) ; ainsi qu'un mécanisme de commande de transmission (50). Le mécanisme de commande de transmission (50) comprend : un arbre d'entrée à usage de commande (51) et un arbre de sortie à usage de commande (52) ; un mécanisme de transmission côté entrée (53) qui transmet une partie de la force d'entraînement rotative de l'arbre d'entrée (20) à l'arbre d'entrée à usage de commande (51) ; un mécanisme de transmission(54) qui transmet la force d'entraînement rotative de l'arbre d'entrée à usage de commande (51) à l'arbre de sortie à usage de commande (52) et modifie la fréquence de rotation de l'arbre de sortie à usage de commande (52) ; ainsi qu'un mécanisme de transmission côté sortie (55) qui transmet la force d'entraînement rotative de l'arbre de sortie à usage de commande (52) à un composant formant le mécanisme d'engrenage planétaire (40) et non relié à l'arbre d'entrée (20) ou à l'arbre de sortie (30), c'est-à-dire, à une roue intérieure (41), un planétaire (42) ou un support d'engrenage planétaire (44).
PCT/JP2015/084332 2014-12-08 2015-12-07 Dispositif de transmission à vitesse variable WO2016093200A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201580063757.8A CN107002831B (zh) 2014-12-08 2015-12-07 可变速装置
RU2017123768A RU2668772C1 (ru) 2014-12-08 2015-12-07 Трансмиссия с регулируемой скоростью

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014-247752 2014-12-08
JP2014247752A JP5778844B1 (ja) 2014-12-08 2014-12-08 可変速装置

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WO2016093200A1 true WO2016093200A1 (fr) 2016-06-16

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PCT/JP2015/084332 WO2016093200A1 (fr) 2014-12-08 2015-12-07 Dispositif de transmission à vitesse variable

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CN (1) CN107002831B (fr)
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DE102022120840A1 (de) 2022-08-18 2024-02-29 Voith Patent Gmbh Hydrodynamisch-mechanische Kraftübertragungsvorrichtung

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JPH06264975A (ja) * 1992-12-22 1994-09-20 Dana Corp 差動制限装置
JP2009220618A (ja) * 2008-03-13 2009-10-01 Toyota Motor Corp 車両用駆動装置

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DE102020124864A1 (de) 2020-09-24 2022-03-24 Voith Patent Gmbh Monitoring von regelbaren Getrieben
DE102022120840A1 (de) 2022-08-18 2024-02-29 Voith Patent Gmbh Hydrodynamisch-mechanische Kraftübertragungsvorrichtung

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JP2016109217A (ja) 2016-06-20
RU2668772C1 (ru) 2018-10-02
CN107002831B (zh) 2019-07-30
JP5778844B1 (ja) 2015-09-16

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