CN106641170B - Hydraulic clutch device of double-drive planetary reducer - Google Patents

Hydraulic clutch device of double-drive planetary reducer Download PDF

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Publication number
CN106641170B
CN106641170B CN201611041412.5A CN201611041412A CN106641170B CN 106641170 B CN106641170 B CN 106641170B CN 201611041412 A CN201611041412 A CN 201611041412A CN 106641170 B CN106641170 B CN 106641170B
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CN
China
Prior art keywords
clutch
piston
input shaft
planetary reducer
friction plate
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Active
Application number
CN201611041412.5A
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Chinese (zh)
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CN106641170A (en
Inventor
于天龙
马定
谭大伟
韩荣光
尉巍
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Dalian Huarui Heavy Industry Group Co Ltd
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Dalian Huarui Heavy Industry Group Co Ltd
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Priority to CN201611041412.5A priority Critical patent/CN106641170B/en
Publication of CN106641170A publication Critical patent/CN106641170A/en
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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
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
    • F16H2047/025—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the fluid gearing comprising a plurality of pumps or motors

Abstract

The invention discloses a hydraulic clutch device of a double-drive planetary reducer, which comprises a planetary reducer base, an intermediate gear, a connecting flange, a clutch base, a clutch I and a clutch II, wherein the intermediate gear, the connecting flange and the clutch base are sequentially arranged along the axis of the planetary reducer base, the clutch I and the clutch II are positioned at two sides of the axis of the planetary reducer base, the axis of the clutch I is parallel to the axis of the planetary reducer base, the intermediate gear is connected with the planetary reducer base through a ball bearing, and the intermediate gear is connected with the connecting flange through a roller bearing. The invention can realize coaxial disconnection and combination functions, has reliable combination, flexible and portable disconnection, flexible and convenient switching operation between the clutch I and the clutch II, compact structure and automatic selection of single-input drive and switching and double-input drive. The piston and the clutch seat are arranged on the fixed shell, the oil way is convenient to set and control, the linkage control is easy to realize, the input shaft is simple in structure, and a bearing structure for bearing axial force is not required to be arranged.

Description

Hydraulic clutch device of double-drive planetary reducer
Technical Field
The invention relates to a hydraulic clutch device of a double-drive planetary reducer, which is suitable for double-input configuration of a hydraulic motor, is integrated at the input end of the planetary reducer, and can be used for other occasions needing to disconnect and combine a transmission chain. The speed reducer matching market with extremely high reliability requirement and need to be provided with a standby driving unit or the speed reducer matching market with extremely large bearing load and limited installation space and need to be driven by double inputs.
Background
In some application occasions with extremely high requirements on the reliability of the speed reducer or extremely high bearing load of the speed reducer and limited installation space, the conventional planetary speed reducer cannot meet the requirements. The design of the double-input planetary reducer can meet the requirement, on one hand, for the occasion that the double-drive simultaneous work is required in full load, in order to save energy and reduce emission, one of the drives needs to be disconnected in the light-load or no-load working condition, and only the other drive is required to work; on the other hand, in the case of high reliability, one of the driving units is used as a spare in the designed dual input driving, and only one of the driving units is used in actual operation, and at this time, any one of the driving units needs to be disconnected and simultaneously can be conveniently switched between the two driving units.
However, the tooth clutch device in the prior art has the problems of incapability of stopping combination, incapability of high-speed combination and inconvenient operation; the hydraulic clutch device has the problems that the structure is not compact and the double-drive linkage cannot be realized.
Disclosure of Invention
In order to solve the problems, the hydraulic clutch device of the double-drive planetary reducer can realize coaxial disconnection and combination, can realize automatic selection of single-input drive and switching and double-input drive, is automatically controlled under the cooperation of a hydraulic oil way, is convenient to operate, and has reliable clutch combination, flexible and portable detachment. The clutch function requirement design of the planetary reducer is provided with a solution. The invention adopts the following technical means:
the hydraulic clutch device of the double-drive planetary reducer is characterized by comprising a planetary reducer seat, an intermediate gear, a connecting flange, a clutch seat, a clutch I and a clutch II, wherein the intermediate gear, the connecting flange and the clutch seat are sequentially arranged along the axis of the planetary reducer seat;
the intermediate gear is connected with the input end of the speed reducer through a spline,
the clutch I comprises an output gear I, an output shell I, a friction plate group I, a pressure plate I, a piston I, a baffle I, an input end cover I, a hydraulic motor I and an input shaft I which is positioned on the axis of the clutch I and connected with the hydraulic motor I, wherein the output gear I is connected with a planetary speed reducer seat through a tapered roller bearing and is connected with the output shell I through a bolt, the output gear I and the output shell I are integrally connected with a connecting flange through a tapered roller bearing, the input shaft I is connected with the output shell I through a ball bearing, the friction plate group I is further arranged between the input shaft I and the output shell I, a ball bearing and a thrust needle bearing are arranged between the pressure plate I and the piston I, a plurality of springs I are further arranged between the baffle I and the piston I, the input end cover I is connected with a clutch seat through bolts and is connected with the baffle I through the springs I, the pressure plate I presses the friction plate group I on the output shell I and is further provided with a sealing ring I between the clutch I and the piston I;
the clutch II comprises an output gear II, an output shell II, a friction plate group II, a pressure plate II and a piston II which are sequentially arranged along the axis of the clutch II, a baffle II, an input end cover II, a hydraulic motor II and an input shaft II which is positioned on the axis of the clutch II and connected with the hydraulic motor II, wherein the output gear II is connected with a planetary speed reducer seat through a tapered roller bearing and is connected with the output shell II through a bolt, the output gear II and the output shell II are integrally connected with a connecting flange through a tapered roller bearing, the input shaft II is connected with the output shell II through a ball bearing, the friction plate group II is further arranged between the input shaft II and the output shell II, a ball bearing and a thrust needle bearing are arranged between the pressure plate II and the piston II, a plurality of springs II are further arranged between the baffle II and the piston II, the input end cover II is connected with a clutch seat through bolts and is connected with the baffle II through the springs II, the pressure plate II presses the friction plate group II to the output shell II through the ball bearing and the piston II, and the oil cavity II is further provided with a sealing ring II between the clutch II and the piston II;
the brake oil way led out from the hydraulic motor I is communicated with the oil cavity II, the brake oil way led out from the hydraulic motor II is communicated with the oil cavity I,
the intermediate gear is meshed with the output gear I and the output gear II respectively.
The friction plate group I comprises a plurality of inner friction plates I and outer friction plates I which are arranged in a staggered mode, the inner friction plates I are connected with the input shaft I through splines, and the outer friction plates I are connected with the output shell I through splines;
the friction plate group II comprises a plurality of inner friction plates II and outer friction plates II which are arranged in a staggered mode, wherein the inner friction plates II are connected with the input shaft II through splines, and the outer friction plates II are connected with the output shell II through splines.
The piston I is provided with a hole for accommodating the fixed end of the spring I, and the piston II is provided with a hole for accommodating the fixed end of the spring II.
The hydraulic motor I is connected with the clutch seat through the input end cover I and is connected with the input shaft I through a spline;
the hydraulic motor II is connected with the clutch seat through the input end cover II and is connected with the input shaft II through a spline.
The friction plate of the friction plate group I, which is close to the end face of the pressure plate I, is an outer friction plate I; the friction plate of the friction plate group II, which is close to the end face of the pressure plate II, is an outer friction plate II.
When the hydraulic motor I is used for driving, pressure oil led out by the hydraulic motor I enters the oil cavity II, the piston II overcomes the pressure of the spring II under the action of hydraulic pressure to leave the friction plate group II, and the output shell II is separated from the input shaft II. At this moment, the hydraulic motor II does not work, the oil cavity I is free of pressure oil, the output shell I and the input shaft I are locked under the action of the spring I, and the input shaft I transmits input torque to the output shell I so as to achieve the purpose of transmitting power.
When the hydraulic motor II works, pressure oil led out by the hydraulic motor II enters the oil cavity I, the piston I overcomes the pressure of the spring I under the action of hydraulic pressure to leave the friction plate group I, and the output shell I is separated from the input shaft I. At this moment, the hydraulic motor I does not work, the oil cavity II has no pressure oil, the output shell II and the input shaft II are locked under the action of the spring II, and the input shaft II transmits the input torque to the output shell II so as to achieve the purpose of transmitting power.
When the hydraulic motor I and the hydraulic motor II are driven simultaneously, hydraulic oil channels of the hydraulic motor I and the hydraulic motor II are closed, the oil cavity I and the oil cavity II are free of pressure oil, the output shell I and the input shaft I are locked under the action of the spring I, the input shaft I transmits input torque to the output shell I, the output shell II and the input shaft II are locked under the action of the spring II, and the input shaft II transmits the input torque to the output shell II so as to achieve the purpose of transmitting power simultaneously.
The disconnection and combination of the driving chains are controlled through the hydraulic motor I and the hydraulic motor II so as to select the two hydraulic motors to be driven simultaneously or driven by a single hydraulic motor.
The invention has the following advantages:
1. the coaxial disconnection and combination functions can be realized;
2. the invention has reliable combination, flexible and portable detachment, flexible and convenient switching operation between the clutch I and the clutch II;
3. the structure is compact, the piston and the clutch seat are arranged on the fixed shell, the oil way is convenient to set and control, and the linkage control is easy to realize;
4. the input shaft has a simple structure, and a bearing structure for bearing axial force is not required to be arranged;
5. when the planetary reducer is provided with a parking brake, the combined control of the brake, the clutch I and the clutch II on the brake oil way can be realized, the automatic control is easy to realize, and the number of hydraulic stations is reduced;
6. the automatic selection of single-input drive, switching and double-input drive can be realized.
For the reasons, the invention can be widely popularized in the fields of clutches and the like.
Drawings
The invention will be described in further detail with reference to the drawings and the detailed description.
Fig. 1 is a cross-sectional view of a dual drive planetary reducer hydraulic clutch device in an embodiment of the invention.
Fig. 2 is a front view of a hydraulic clutch device of a double-drive planetary reducer in an embodiment of the invention.
Detailed Description
As shown in fig. 1 and 2, the hydraulic clutch device of the double-drive planetary reducer comprises a planetary reducer base 1, an intermediate gear 2, a connecting flange 3, a clutch base 4, a clutch i and a clutch ii, wherein the intermediate gear 2, the connecting flange 3 and the connecting flange 3 are sequentially arranged along the axis of the planetary reducer base 1, the clutch i and the clutch ii are positioned on two sides of the axis of the planetary reducer base 1, the axis of the clutch i is parallel to the axis of the planetary reducer base 1, the intermediate gear 2 is connected with the planetary reducer base 1 through a ball bearing, the connecting flange 3 is connected with the planetary reducer base 1 through a bolt, and the clutch base 4 is connected with the connecting flange 3 through a bolt;
the clutch I comprises an output gear I5, an output shell I6, a friction plate group I7, a pressure plate I8, a piston I9, a baffle I10, an input end cover I11, a hydraulic motor I12 and an input shaft I13 which is positioned on the axis of the clutch I and connected with the hydraulic motor I12, wherein the output gear I5 is connected with the planetary reducer base 1 through a tapered roller bearing and is connected with the output shell I6 through a bolt, the output gear I5 and the output shell I6 are integrally connected with the connecting flange 3 through a tapered roller bearing, the input shaft I13 is connected with the output shell I6 through a ball bearing, the friction plate group I7 is further arranged between the input shaft I13 and the output shell I6, a ball bearing and a needle bearing are further arranged between the pressure plate I8 and the piston I9, a plurality of springs I14 are further arranged between the baffle I10 and the piston I9, the input end cover I11 is connected with the output shell I6 through a bolt seat 4, the piston I9 is further connected with the oil cavity I9 through a spring seat I10, and the piston I9 are further arranged between the piston I9 and the piston I6, and the piston I9 are further provided with an oil cavity I sealing ring I15;
the clutch II comprises an output gear II 17, an output shell II 18, a friction plate group II 19, a pressure plate II 20, a piston II 21, a baffle II 22, an input end cover II 23, a hydraulic motor II 24 and an input shaft II 25 which is positioned on the axis of the clutch II and connected with the hydraulic motor II 24, wherein the output gear II 17 is connected with the planetary reducer base 1 through a tapered roller bearing and is connected with the output shell II 18 through a bolt, the whole of the output gear II 17 and the output shell II 18 is connected with the connecting flange 3 through a tapered roller bearing, the input shaft II 25 is connected with the output shell II 18 through a ball bearing, the friction plate group II 18 is further arranged between the input shaft II 25 and the output shell II 18, a ball bearing and a needle bearing are further arranged between the pressure plate II 20 and the piston II 21, a plurality of springs II 26 are further arranged between the baffle II 22 and the piston II 21, the input end cover II 23 is connected with the output shell II 18 through a bolt 4 and is further connected with the pressure plate II, the piston II 20 is further provided with an oil cavity II groove II, and a seal ring II is further arranged between the piston II 21 and the piston II 20 through the spring II, and the piston II 21;
the brake oil way led out from the hydraulic motor I12 is communicated with the oil cavity II 27, the brake oil way led out from the hydraulic motor II 24 is communicated with the oil cavity I15,
the intermediate gear 2 meshes with the output gear i 5 and the output gear ii 17, respectively.
The friction plate group I7 comprises a plurality of inner friction plates I and outer friction plates I which are arranged in a staggered mode, the inner friction plates I are connected with the input shaft I13 through splines, and the outer friction plates I are connected with the output shell I6 through splines;
the friction plate group II 19 comprises a plurality of inner friction plates II and outer friction plates II which are arranged in a staggered mode, the inner friction plates II are connected with the input shaft II 25 through splines, and the outer friction plates II are connected with the output shell II 18 through splines.
The piston I9 is provided with a hole for accommodating the fixed end of the spring I14, and the piston II 21 is provided with a hole for accommodating the fixed end of the spring II 26.
The hydraulic motor I12 is connected with the clutch seat 4 through the input end cover I11 and is connected with the input shaft I13 through a spline;
the hydraulic motor II 24 is connected with the clutch seat 4 through the input end cover II 23 and is connected with the input shaft II 25 through a spline.
The friction plate of the friction plate group I7, which is close to the end face of the pressure plate I8, is an outer friction plate I; the friction plate of the friction plate group II 19, which is close to the end face of the pressure plate II 20, is an outer friction plate II.
The foregoing is only a preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art, who is within the scope of the present invention, should make equivalent substitutions or modifications according to the technical scheme of the present invention and the inventive concept thereof, and should be covered by the scope of the present invention.

Claims (5)

1. The hydraulic clutch device of the double-drive planetary reducer is characterized by comprising a planetary reducer seat, an intermediate gear, a connecting flange, a clutch seat, a clutch I and a clutch II, wherein the intermediate gear, the connecting flange and the clutch seat are sequentially arranged along the axis of the planetary reducer seat;
the clutch I comprises an output gear I, an output shell I, a friction plate group I, a pressure plate I, a piston I, a baffle I, an input end cover I, a hydraulic motor I and an input shaft I which is positioned on the axis of the clutch I and connected with the hydraulic motor I, wherein the output gear I is connected with a planetary speed reducer seat through a tapered roller bearing and is connected with the output shell I through a bolt, the output gear I and the output shell I are integrally connected with a connecting flange through a tapered roller bearing, the input shaft I is connected with the output shell I through a ball bearing, the friction plate group I is further arranged between the input shaft I and the output shell I, a ball bearing and a thrust needle bearing are arranged between the pressure plate I and the piston I, a plurality of springs I are further arranged between the baffle I and the piston I, the input end cover I is connected with a clutch seat through bolts and is connected with the baffle I through the springs I, the pressure plate I presses the friction plate group I on the output shell I and is further provided with a sealing ring I between the clutch I and the piston I;
the clutch II comprises an output gear II, an output shell II, a friction plate group II, a pressure plate II and a piston II which are sequentially arranged along the axis of the clutch II, a baffle II, an input end cover II, a hydraulic motor II and an input shaft II which is positioned on the axis of the clutch II and connected with the hydraulic motor II, wherein the output gear II is connected with a planetary speed reducer seat through a tapered roller bearing and is connected with the output shell II through a bolt, the output gear II and the output shell II are integrally connected with a connecting flange through a tapered roller bearing, the input shaft II is connected with the output shell II through a ball bearing, the friction plate group II is further arranged between the input shaft II and the output shell II, a ball bearing and a thrust needle bearing are arranged between the pressure plate II and the piston II, a plurality of springs II are further arranged between the baffle II and the piston II, the input end cover II is connected with a clutch seat through bolts and is connected with the baffle II through the springs II, the pressure plate II presses the friction plate group II to the output shell II through the ball bearing and the piston II, and the oil cavity II is further provided with a sealing ring II between the clutch II and the piston II;
the brake oil way led out from the hydraulic motor I is communicated with the oil cavity II, the brake oil way led out from the hydraulic motor II is communicated with the oil cavity I,
the intermediate gear is meshed with the output gear I and the output gear II respectively.
2. The double-drive planetary reducer hydraulic clutch device according to claim 1, wherein: the friction plate group I comprises a plurality of inner friction plates I and outer friction plates I which are arranged in a staggered mode, the inner friction plates I are connected with the input shaft I through splines, and the outer friction plates I are connected with the output shell I through splines;
the friction plate group II comprises a plurality of inner friction plates II and outer friction plates II which are arranged in a staggered mode, wherein the inner friction plates II are connected with the input shaft II through splines, and the outer friction plates II are connected with the output shell II through splines.
3. The double-drive planetary reducer hydraulic clutch device according to claim 1, wherein: the piston I is provided with a hole for accommodating the fixed end of the spring I, and the piston II is provided with a hole for accommodating the fixed end of the spring II.
4. The double-drive planetary reducer hydraulic clutch device according to claim 1, wherein: the hydraulic motor I is connected with the clutch seat through the input end cover I and is connected with the input shaft I through a spline;
the hydraulic motor II is connected with the clutch seat through the input end cover II and is connected with the input shaft II through a spline.
5. The double-drive planetary reducer hydraulic clutch device according to claim 2, wherein: the friction plate of the friction plate group I, which is close to the end face of the pressure plate I, is an outer friction plate I; the friction plate of the friction plate group II, which is close to the end face of the pressure plate II, is an outer friction plate II.
CN201611041412.5A 2016-11-22 2016-11-22 Hydraulic clutch device of double-drive planetary reducer Active CN106641170B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201611041412.5A CN106641170B (en) 2016-11-22 2016-11-22 Hydraulic clutch device of double-drive planetary reducer

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201611041412.5A CN106641170B (en) 2016-11-22 2016-11-22 Hydraulic clutch device of double-drive planetary reducer

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CN106641170A CN106641170A (en) 2017-05-10
CN106641170B true CN106641170B (en) 2023-09-26

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7176391B2 (en) * 2018-12-11 2022-11-22 株式会社ジェイテクト clutch device

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CN102221055A (en) * 2011-06-16 2011-10-19 东风汽车有限公司 Wet-type double clutch
CN102328886A (en) * 2011-07-20 2012-01-25 徐州科源液压有限公司 Winch reducer
CN102632802A (en) * 2012-05-03 2012-08-15 陕西航天动力高科技股份有限公司 Double-drive device of vehicle compressor
CN103256364A (en) * 2012-02-16 2013-08-21 甘亚冰 Dual output intermittent two-way driving mechanism, two-way overrunning clutch and self-locking differential
CN103883686A (en) * 2014-03-11 2014-06-25 徐州科源液压股份有限公司 Double-speed ratio walking speed reducer
CN104986680A (en) * 2015-06-22 2015-10-21 宁波赤马绞盘有限公司 Dual-drive winch
CN205446574U (en) * 2016-04-05 2016-08-10 哈尔滨广瀚动力传动有限公司 Coaxial vapour, electricity is two to drive boiler fan planet speed governing clutch for system
CN206190843U (en) * 2016-11-22 2017-05-24 大连华锐重工集团股份有限公司 Two planetary reducer hydraulic clutch devices that drive

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JP2012233528A (en) * 2011-04-28 2012-11-29 F C C:Kk Power transmission device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6338689B1 (en) * 2000-06-16 2002-01-15 Sauer-Danfoss Inc. Hydromechanical transmission
CN102221055A (en) * 2011-06-16 2011-10-19 东风汽车有限公司 Wet-type double clutch
CN102328886A (en) * 2011-07-20 2012-01-25 徐州科源液压有限公司 Winch reducer
CN103256364A (en) * 2012-02-16 2013-08-21 甘亚冰 Dual output intermittent two-way driving mechanism, two-way overrunning clutch and self-locking differential
CN102632802A (en) * 2012-05-03 2012-08-15 陕西航天动力高科技股份有限公司 Double-drive device of vehicle compressor
CN103883686A (en) * 2014-03-11 2014-06-25 徐州科源液压股份有限公司 Double-speed ratio walking speed reducer
CN104986680A (en) * 2015-06-22 2015-10-21 宁波赤马绞盘有限公司 Dual-drive winch
CN205446574U (en) * 2016-04-05 2016-08-10 哈尔滨广瀚动力传动有限公司 Coaxial vapour, electricity is two to drive boiler fan planet speed governing clutch for system
CN206190843U (en) * 2016-11-22 2017-05-24 大连华锐重工集团股份有限公司 Two planetary reducer hydraulic clutch devices that drive

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