WO2009036655A1 - Transmission de synchronisation hydrocinetique - Google Patents

Transmission de synchronisation hydrocinetique Download PDF

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Publication number
WO2009036655A1
WO2009036655A1 PCT/CN2008/001620 CN2008001620W WO2009036655A1 WO 2009036655 A1 WO2009036655 A1 WO 2009036655A1 CN 2008001620 W CN2008001620 W CN 2008001620W WO 2009036655 A1 WO2009036655 A1 WO 2009036655A1
Authority
WO
WIPO (PCT)
Prior art keywords
bucket wheel
input shaft
gear
brake
synchronous transmission
Prior art date
Application number
PCT/CN2008/001620
Other languages
English (en)
Chinese (zh)
Inventor
Shizhang Liu
Weifeng Ren
Original Assignee
Shizhang Liu
Weifeng Ren
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Shizhang Liu, Weifeng Ren filed Critical Shizhang Liu
Publication of WO2009036655A1 publication Critical patent/WO2009036655A1/fr

Links

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
    • 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
    • F16H47/12—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 the members with orbital motion having vanes interacting with the fluid

Definitions

  • the present invention relates to a hydraulic synchronous transmission that belongs to the technical field of hydraulic transmission.
  • it relates to a hydraulic synchronous transmission for solving speed regulation of a high-power fan, a water pump, a conveyor belt, and the like.
  • a hydraulic synchronous transmission comprising: a first support base and a second support seat disposed opposite to the first support base; respectively rotatably disposed on the first support base and the second support An input shaft and an output shaft on the support base; an inner casing fixedly mounted on the input shaft; rotatably mounted in the inner casing a bucket wheel device on the input shaft, the bucket wheel device includes a plurality of transition gears rotatable about the input shaft and rotatable; a drive gear fixedly mounted on the input shaft, the drive gear passing a gear meshing manner engages with each of the transition gears to drive the drive gear through the transition gear; a large gear fixedly mounted on the output shaft, the large gear having an inner ring gear portion, the inner ring gear portion being located An outer portion of the plurality of transition gears and meshing with each of the transition gears by a gear meshing manner; and a brake system, the brake system continuously providing a braking force to cause the bucket wheel device and the second support
  • the bucket wheel device includes: a first support frame and a second support frame that are oppositely disposed, the first support frame and the second support frame are rotatably mounted on the input shaft; And a plurality of bucket wheels respectively rotatably mounted between the first support frame and the second support frame by the bucket wheel shaft, wherein each bucket wheel is fixedly mounted on the respective bucket wheel shaft and separately Located at the periphery of the input shaft; wherein each of the plurality of transition gears is fixedly mounted on the bucket wheel shaft.
  • the brake system includes: a brake device mounted on the second support base; and a connection mechanism, the connection mechanism being coupled to the bucket wheel device, the brake device Braking the relative rotation between the connecting mechanism and the second support.
  • the brake device is a liquid-stick brake.
  • the liquid-adhesive brake includes: a friction plate mounted on the connection mechanism; a brake pressure plate; and a control device that controls the brake pressure plate to apply to the friction plate The pressing force controls the relative rotation between the connecting mechanism and the second support.
  • the control device includes: an actuator; and a linkage mechanism that drives the brake platen to press the friction plate in accordance with an action of the actuator.
  • the above-described hydraulic synchronous transmission further includes a plurality of reversing gears mounted on the bucket wheel device and engaged between the transition gear and the drive gear.
  • the hydraulic synchronous transmission further includes a liquid level adjusting device, the liquid level adjusting device comprising: a conduit through which the conduit is inserted into the inner casing; and an actuator, the actuator acting The distal end portion of the catheter is adjusted to be inserted into the liquid in the liquid on the inner wall of the inner casing due to centrifugal force.
  • the above-described hydraulic synchronous transmission further includes a liquid level adjusting device, the liquid level adjusting device comprising: a conduit through which the conduit is inserted into the inner casing, the conduit being drivably coupled to the A linkage mechanism that drives the distal end portion of the catheter to insert a depth and/or an angle in the liquid attached to the inner wall of the inner casing due to centrifugal force in accordance with the action of the actuator.
  • the invention can realize constant power stepless speed change, stepless torque change and soft start of 10-10000 kW power transmission.
  • the average efficiency is about 95%, and the efficiency can reach about 99% at the lowest speed and the highest speed.
  • the invention can be widely applied to various working situations such as automobiles, engineering machinery, mining machinery, power plants, steel plants, chemical machinery and the like, such as high-power fans, pumps or conveyor belts, which need to be operated at variable loads or difficult to match suitable power machines.
  • the hydraulic synchronous transmission of the invention has excellent performance in the stepless speed change, stepless torque change and soft start, and has obvious advantages in solving the load start of the high power load.
  • Figure 1 is a schematic illustration of one embodiment of a fluid synchronizer governor in accordance with the present invention
  • Figure 2 is a cross-sectional view taken along line A-A of Figure 1;
  • Fig. 3 is a cross-sectional view taken along line B-B of Fig. 1.
  • Figure 4 is a cross-sectional view showing an embodiment of a fluid synchronizer governor in accordance with the present invention
  • Figure 5 is a cross-sectional view taken along line C-C of Figure 4.
  • Figure 6 is a cross-sectional view taken along line D-D of Figure 4.
  • Figure 7 is an enlarged schematic view of the brake device portion of Figure 4.
  • a hydraulic synchronous transmission includes: a closed outer casing 100 including a first support base 2 and a second support disposed opposite the first support base 2
  • the seat 20, the first support base 2 and the second support base 20 may be respectively sealed and mounted to the outer casing 100, or at least one of them may be integrally formed with the outer casing 100;
  • An input shaft 1 and an output shaft 19 on a support base 2 and a second support base 20, in an exemplary embodiment, the input shaft 1 and the output shaft 19 are mounted on the same axis; and are disposed on the input shaft 1 and A coupling device between the output shafts 19 that couples the rotation of the input shaft 1 to the output shaft 19, thereby causing the output shaft 19 to drive the load.
  • the coupling device includes: an inner casing 200 disposed in the outer casing 100 and fixedly mounted on the input shaft 1, the inner casing 200 including and extending to First support a first end cover 3 to which the inner input shaft 1 is fixedly coupled, and a second end cover 9 rotatably mounted on the second support base 20; rotatably mounted on the input shaft in the inner casing 200 a bucket wheel device, the bucket wheel device including a plurality of transition gears 28 revolving around the input shaft 1 and rotatable; a plurality of commutations mounted on the bucket wheel device and meshing with the transition gear 28 a gear 26; a drive gear 27 fixedly mounted on the input shaft 1, the drive gear 27 meshing with each of the reversing gears 26 by means of gear meshing, so that the drive gear 27 drives the transition gear 28 through the reversing gear 26; a large gear 25 mounted on the output shaft 19, the large gear 25 having an inner ring gear portion external to the plurality of transition gears 28 and
  • the bucket wheel device comprises: a first support frame 4 and a second support frame 29 which are oppositely disposed, the first support frame 4 and the second support frame 29 are rotatably mounted on the input shaft 1 and located at the Between the end cap 3 and the second end cap 9; a plurality of bucket wheels 24, the plurality of bucket wheels 24 being rotatably mounted on the first support frame 4 and the second support frame 29 by the bucket wheel shaft 30 at equal intervals Between, wherein each bucket wheel 24 is fixedly mounted on a respective bucket wheel shaft 30, spaced apart from the input shaft 1 by a predetermined distance and located at the periphery of the input shaft 1, each bucket wheel shaft 30 being disposed at the center of the axis of the input shaft 1
  • a plurality of transition gears 28, each of which is fixedly mounted on the bucket wheel shaft 30 extending from the support frame 29, in one embodiment, the transition gear 28 and the bucket wheel shaft 30 are integrally formed.
  • the bull gear 25 includes a flange and an inner ring gear portion having an engaging tooth on the inner side extending perpendicularly from the end of the flange.
  • the number of the bucket wheel 24, the transition gear 28, and the reverse gear 26 may be 2 - 10, preferably 4 - 8 , which is 6 in the exemplary embodiment illustrated in the drawings.
  • the rotating shaft of the reverse gear 26 is mounted on the second support frame 29.
  • the reversing gear 27 can be omitted and the bull gear 25 is only meshed with the drive gear 27 via the transition gear 18.
  • each bucket wheel 24 includes two spaced apart support plates 31 fixedly mounted on the bucket wheel axle 30, and a plurality of bucket wheel blades 32 mounted between the support plates 31 about the bucket wheel axle 30.
  • the cross section of the bucket wheel blade 32 in the direction perpendicular to the axial direction of the input shaft has an arcuate shape, so that the bucket wheel blade 32 and the two support plates 31 constitute an open container capable of accommodating a certain liquid. structure.
  • the specific number of bucket wheel blades can be set as desired, and each bucket wheel blade 32 has a predetermined spacing therebetween. In this way, when the inner box 200 is lost When the input shaft 1 rotates, the bucket wheel rotates, and the bucket wheel blade cuts in the liquid so that the liquid contained in the inner tank 200 enters the container structure due to the centrifugal force.
  • At least one (eg, one or two) fusible plugs 5 may be disposed on a sidewall of the case 200 between the first end cap 2 and the second end cap 9. .
  • the fusible plug 5 is automatically opened, thereby discharging the liquid (for example, oil, not shown) in the inner casing 200, thereby preventing the inner casing 200 oil temperature is too high, resulting in damage to the equipment and transmission system.
  • the output shaft 19 can be mounted on a sleeve on the input shaft 1 by a bearing structure to achieve a rotatably linear connection between the input shaft 1 and the output shaft 19, and can be Stability is provided in the direction perpendicular to the axial direction of the input shaft 1 and the output shaft 19.
  • the brake system includes: a brake device mounted on the second support base; and a connection mechanism 6, the connection mechanism 6 being coupled to the bucket wheel device, for example, connected to the bucket wheel The second support frame 29 of the device.
  • the brake device brakes the relative rotation between the connectable mechanism 6 and the second support base, even making the bucket wheel device relatively stationary relative to the output shaft 19.
  • a driving device such as an electric motor drives the inner casing 200 and the driving gear 27 to rotate through the input shaft 1, while the working fluid such as oil stored in the outer casing 1 is to be stored. (not shown) is delivered into the inner casing 200 using a work pump.
  • a load is applied to the output shaft 19, so that the large gear 25 fixedly coupled to the output shaft 19 does not rotate.
  • the translating gear 28 is driven by the input shaft 2 to drive the bucket wheel 24 to rotate around the bucket wheel shaft 30 in a direction opposite to the rotation direction of the input shaft 2, and at the same time,
  • the gear 25 does not rotate, and the transition gear 28 meshes with the large gear 25, thereby forcing the bucket wheel 24 to revolve around the input shaft 1.
  • the liquid contained in the inner casing 200 forms an annular liquid surface on the cylindrical inner surface of the inner casing 200 due to the centrifugal force.
  • the bucket wheel self-rotating liquid enters the concave bucket wheel blades 32 of the respective bucket wheels 24.
  • the liquid entering the bucket wheel 32 forces the rotation speed of the bucket wheel 24 to gradually decrease due to the centrifugal force, so that the rotational speed of the bucket wheel 24 and the transition gear 28 is not synchronized with the rotational speed of the input shaft 1.
  • the transition gear 28 gradually drives the large gear 25 meshing therewith to rotate, thereby rotating the output shaft 19, thereby driving the load coupled to the output shaft 19 from the stationary state to the moving state, realizing a soft start of the load.
  • the inner casing 200 continues to rotate, the liquid entering the concave bucket wheel blades 32 of each bucket wheel 24 continues to increase, and the centrifugal force increases, which forces the bucket wheel 24 and the transition gear 28 to no longer wrap around the bucket axle 30. rotation.
  • the transition gear 28 drives the large gear 25 meshing therewith to rotate synchronously with the input shaft 1, thereby making the input shaft 1
  • the output shaft 19 is rotated in synchronism, thereby achieving complete drive of the input shaft 1 to the output shaft 19. It can be understood that in the case of full drive, the centrifugal torque of the liquid is balanced by the action of the gear mechanism and the resistance torque of the load.
  • the brake device driving the brake system is actuated, and the second support frame 19 of the connection mechanism 6 and the bucket wheel device connected to the connection mechanism is no longer synchronized with the output shaft 19 under the action of the brake device.
  • Turn. If the braking force provided by the brake device is large enough, the bucket wheel device will stop rotating. However, at this time, the drive gear 27 still transmits the driving force from the input shaft 1 to the large gear 25 through the reverse gear 26 and the transition gear 28, and therefore, the large gear 25 continues to rotate. It can be understood that the rotation transmission process between the input shaft 1 and the output shaft 19 at this time is such that: the input shaft 1, the drive gear 27, the reverse gear 26, the transition gear 28, the large gear 25, and the output shaft 19 .
  • the input shaft 1 drives the output shaft 19 due to the meshing relationship between the drive gear 27, the reverse gear 26, the transition gear 28, and the large gear 25. It can be understood that this driving mode is driven by deceleration and torque increase, and the specific torque transmission ratio from the input shaft 1 to the output shaft 19 can be determined by designing the diameter (or the number of teeth) of each gear.
  • the drive gear 27, the reverse gear 26, the transition gear 28, and the large gear 25 can be used as a planetary gear reducer with a reduction ratio equal to the gear ratio of the large gear 25 and the drive gear 27, and the theoretical efficiency is 1.
  • the liquid level of the liquid attached to the inner surface of the inner casing 200 determines the magnitude of the centrifugal force, and the magnitude of the centrifugal force is determined.
  • the output shaft 19 can rotate in synchronization with the input shaft 1 is possible.
  • the larger the centrifugal force the more the output shaft 19 tends to rotate in synchronization with the input shaft 1, and the smaller the slip between the output shaft 19 and the input shaft 1. Conversely, the greater the slip. Therefore, in this case, synchronous rotation and continuously variable shift between the input shaft 1 and the output shaft 19 can be realized.
  • the input shaft 1 and the output shaft 19 can be driven to reduce the torque.
  • the bucket device cannot rotate synchronously with the output shaft 19, but can still rotate to a certain extent with respect to the output shaft 19. In this case, a certain degree of shifting and torque-changing driving between the input shaft 1 and the output shaft 19 can be realized.
  • the hydraulic synchronizing device braking device may be a liquid-adhesive brake 21.
  • the liquid-adhesive brake 21 includes: a plurality of friction plates 16 mounted on the coupling mechanism 6; a brake pressure plate 15; and a control device that controls the brake pressure plate 15 to apply a pressing force to the friction plates 16, Thereby the relative rotation between the connecting mechanism 6 and the second support base 20 is controlled.
  • a third support frame 7 is rotatably mounted between the second support base 20 and the link mechanism 6, and the third support frame 7 is rotatable relative to the second support base 20 and the link mechanism 6, respectively.
  • control device includes: an actuator 18 such as an electric motor; and a linkage mechanism that drives the brake pressure plate 15 to press according to the action of the actuator 18.
  • the friction linings 17 can also be combined with another friction lining 16, such that the plurality of frictional forces 16 and 17 cooperate to achieve an improved friction braking effect by oil film shearing.
  • the linkage mechanism includes: a link device 23 connected to the output mechanism of the actuator 18; a rack seat 11 fixedly mounted on the second support base 20; meshing with the rack base 11 and at the link A rack 12 that linearly moves on the rack housing 11 under the drive of the device 23; a gear 13 that meshes with the rack 12; and a differential screw mechanism 14 that meshes with the gear 13.
  • the differential screw mechanism 14 is threadedly coupled to the brake platen 15.
  • the differential screw mechanism 14 is also threadedly connected to the second support base 20 and the brake pressure plate 15 by different pitches by a threaded structure.
  • the second support base 20 and the brake pressure plate 15 are pitched. Differently, for each revolution, the distance between the brake platen 14 and the second support base 20 is increased or decreased by a distance equal to the pitch difference, thereby achieving fine adjustment of the pitch of the friction plate 16, since the liquid-adhesive brake is liquid-resistant.
  • the internal friction is used to transmit torque, and thus precise control of the torque applied to the bucket wheel device is achieved in this manner.
  • a liquid level adjusting device for adjusting the liquid level of the liquid in the inner casing 200 is provided.
  • the content described in the PCT International Patent Application No. PCT/CN2008/001939, filed by the Applicant, is hereby incorporated by reference.
  • the gear 13 is drivably coupled to the duct 8, and the opening 31 of the distal end of the duct 8 extends to the vicinity of the inner wall of the inner casing 200 to The opening 31 can be inserted into the liquid on the inner wall of the inner casing 200 due to centrifugal force when the inner casing 200 is rotated.
  • the proximal end of the catheter extends to the exterior of the inner casing 200, such as within the attachment cavity between the inner casing 200 and the outer casing 100, and the opening direction of the opening 31 and the rotation of the inner casing 200 The directions are reversed so that liquid adhering to the inner wall of the inner casing 200 can enter the conduit 8 through the opening 31 and flow into the attachment cavity from the proximal end opening of the conduit 8. It will be appreciated that by adjusting the depth and/or angle of the conduit 8 into the liquid on the inner wall of the inner casing 200, the amount of liquid flowing from the conduit 8 into the cavity can be adjusted to adjust the attachment to the inner casing 200.
  • the depth (or how much) of the liquid on the inner wall regulates the continuously variable ratio between the input shaft 1 and the output shaft 19. It will be understood that in the above embodiment, since both the duct 8 and the brake platen 15 are driven by the gear 13, the action of the duct 8 and the brake 21 can be simultaneously controlled by the actuator 18. However, the present invention is not limited thereto, and the movement of the duct 8 and the brake 21 may be separately adjusted by different linkage mechanisms, or different linkage mechanisms may be selected to be driven by the same or different actuators.
  • the power transmission mode of the present invention is realized in such a manner that power from an input device such as an electric motor is transmitted through the input shaft 4 to the sun gear as the drive gear 27, and then transmitted to the reversing gear 26 by the drive gear 27, and then The reversing gear 26 is transmitted to the transition gear 28; the transition gear 28 is connected to the bucket wheel 24, and the connecting mechanism 6 is connected to the outer casing 1 through the liquid-adhesive brake 21; the power is transmitted from the transition gear 28 to the large gear 25, It is then transmitted to the output shaft 19 to complete the entire power transmission process.
  • an input device such as an electric motor
  • the stepless shifting and the stepless torque can be realized by adjusting the gap between the friction plates of the liquid viscous brake 21 and adjusting the amount of liquid in the inner tank.
  • the invention can realize constant power stepless speed change, stepless torque change and soft start of 10-30000 kW power transmission. Moreover, the average efficiency is about 95%, and the efficiency can reach about 99% at the lowest speed and the highest speed.
  • the invention can be widely applied to various working occasions such as automobiles, engineering machinery, mining machinery, power plants, steel plants, chemical machinery and the like, such as high-power fans, pumps or conveyor belts, which need to be operated at variable loads or difficult to match suitable power machines.
  • the hydraulic synchronous transmission of the present invention has excellent performance in continuously variable shifting, stepless torque change, and soft start, and has a significant advantage in solving the load start of a high power load.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une transmission de synchronisation hydrocinétique comprenant : un premier support et un deuxième support placé face au premier support ; un arbre d'entrée et un arbre de sortie disposés pivotants sur le premier et le deuxième support respectivement ; un boîtier interne fixé sur l'arbre d'entrée ; une unité roue-pelle formée solidaire avec le boîtier interne et montée rotative sur l'arbre d'entrée, ladite roue comportant plusieurs engrenages de transition pouvant tourner et pivoter autour de l'arbre d'entrée ; un engrenage menant fixé sur l'arbre d'entrée et venant en contact avec chaque engrenage de transition pour l'entraîner ; un grand engrenage fixé sur l'arbre de sortie et comportant une partie couronne interne placée à l'extérieur des engrenages de transition et venant en contact avec chacun d'entre eux ; ainsi qu'un système de freinage fournissant une force de freinage continue destinée à ralentir la rotation relative entre l'unité roue-pelle et le deuxième support, jusqu'à ce que l'unité roue-pelle soit relativement immobilisée par rapport au deuxième support.
PCT/CN2008/001620 2007-09-18 2008-09-17 Transmission de synchronisation hydrocinetique WO2009036655A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN200720028092.X 2007-09-18
CNU200720028092XU CN201074661Y (zh) 2007-09-18 2007-09-18 液力同步变速器

Publications (1)

Publication Number Publication Date
WO2009036655A1 true WO2009036655A1 (fr) 2009-03-26

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Application Number Title Priority Date Filing Date
PCT/CN2008/001620 WO2009036655A1 (fr) 2007-09-18 2008-09-17 Transmission de synchronisation hydrocinetique

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CN (1) CN201074661Y (fr)
WO (1) WO2009036655A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102287510A (zh) * 2011-06-08 2011-12-21 徐州五洋科技有限公司 一种新型行星齿轮传动装置
US10161614B2 (en) 2014-07-15 2018-12-25 Koninklijke Philips N.V. Retrofit lamp for automotive headlights
CN110500393A (zh) * 2018-05-18 2019-11-26 福伊特专利有限公司 功率传输设备

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CN101392822B (zh) * 2007-09-18 2015-01-14 刘时章 液力同步变速器
CN201074661Y (zh) * 2007-09-18 2008-06-18 刘时章 液力同步变速器
CN102022505B (zh) * 2009-09-09 2014-06-18 吴志强 一种复合型双导轮式液力变矩器
CN102022510B (zh) * 2009-09-09 2014-07-02 吴志强 一种复合型综合式液力变矩器
CN102537270B (zh) * 2012-02-10 2014-07-30 中煤张家口煤矿机械有限责任公司 离合式大功率高效机械变矩器
CN102606709B (zh) * 2012-04-01 2014-08-20 威海凌云流体传动科技有限公司 液力同步双速器
US10400874B2 (en) * 2016-03-23 2019-09-03 Toyota Jidosha Kabushiki Kaisha Torque converter having torsional vibration damping device
CN106641173B (zh) * 2017-01-25 2023-04-28 威海团中变速器有限公司 无级变速器
CN112555382A (zh) * 2020-12-02 2021-03-26 *** 三极管离合器及其工作方法

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CN2197476Y (zh) * 1994-06-25 1995-05-17 哈尔滨工业大学 一种无滑差静液力机械偶合器
US6066058A (en) * 1997-10-23 2000-05-23 Fuji Jukogyo Kabushiki Kaisha Automatic transmission
JP2001004007A (ja) * 1999-06-17 2001-01-09 Exedy Corp 車両用多段変速機
CN1912426A (zh) * 2006-08-10 2007-02-14 刘时章 液力同步器
CN200940673Y (zh) * 2006-08-10 2007-08-29 刘时章 液力同步器
CN201074661Y (zh) * 2007-09-18 2008-06-18 刘时章 液力同步变速器

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Publication number Priority date Publication date Assignee Title
US3334529A (en) * 1964-04-15 1967-08-08 Inpower Works Ltd Fluid torque transmitter
CN1067299A (zh) * 1991-05-25 1992-12-23 王文贵 手动和自动无级动力变速箱
CN2197476Y (zh) * 1994-06-25 1995-05-17 哈尔滨工业大学 一种无滑差静液力机械偶合器
US6066058A (en) * 1997-10-23 2000-05-23 Fuji Jukogyo Kabushiki Kaisha Automatic transmission
JP2001004007A (ja) * 1999-06-17 2001-01-09 Exedy Corp 車両用多段変速機
CN1912426A (zh) * 2006-08-10 2007-02-14 刘时章 液力同步器
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CN201074661Y (zh) * 2007-09-18 2008-06-18 刘时章 液力同步变速器

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102287510A (zh) * 2011-06-08 2011-12-21 徐州五洋科技有限公司 一种新型行星齿轮传动装置
CN102287510B (zh) * 2011-06-08 2015-06-03 徐州五洋科技股份有限公司 一种行星齿轮传动装置
US10161614B2 (en) 2014-07-15 2018-12-25 Koninklijke Philips N.V. Retrofit lamp for automotive headlights
CN110500393A (zh) * 2018-05-18 2019-11-26 福伊特专利有限公司 功率传输设备

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