GB2519949A - Switching assembly for dual speed final drive - Google Patents

Switching assembly for dual speed final drive Download PDF

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Publication number
GB2519949A
GB2519949A GB1319146.5A GB201319146A GB2519949A GB 2519949 A GB2519949 A GB 2519949A GB 201319146 A GB201319146 A GB 201319146A GB 2519949 A GB2519949 A GB 2519949A
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GB
United Kingdom
Prior art keywords
assembly
sleeve
final drive
speed
speed range
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
GB1319146.5A
Other versions
GB201319146D0 (en
Inventor
Christopher Smith
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Shrewsbury Ltd
Original Assignee
Caterpillar Shrewsbury Ltd
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 Caterpillar Shrewsbury Ltd filed Critical Caterpillar Shrewsbury Ltd
Priority to GB1319146.5A priority Critical patent/GB2519949A/en
Publication of GB201319146D0 publication Critical patent/GB201319146D0/en
Priority to PCT/GB2014/052719 priority patent/WO2015063450A2/en
Publication of GB2519949A publication Critical patent/GB2519949A/en
Withdrawn legal-status Critical Current

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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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
    • B60K17/344—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear
    • B60K17/346—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear
    • B60K17/3467—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a transfer gear the transfer gear being a differential gear combined with a change speed gearing, e.g. range gear
    • 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
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • F16H59/04—Ratio selector apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/14—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by repeated movement of the final actuating mechanism
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/08—Multiple final output mechanisms being moved by a single common final actuating mechanism
    • F16H63/16—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism
    • F16H63/18—Multiple final output mechanisms being moved by a single common final actuating mechanism the final output mechanisms being successively actuated by progressive movement of the final actuating mechanism the final actuating mechanism comprising cams
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)
  • Electronic Switches (AREA)

Abstract

Switching assembly 138, for final drive having drive shafts and epicyclic gear sets, having sleeve assembly 140 movable between first / high speed and second / low speed positions (see figures 4 and 5), groove 156 on circumferential face 154, displacement member 190 positioned around sleeve assembly 138 and having first teeth 194 and follower 192 received in groove 156, and actuation means 164 having second teeth 172 engaging first teeth 194. Sleeve assembly 140 may have first sleeve 142 with splines 146, second sleeve 144, and split bearing 152 coupling. A valve assembly 180, having first and second fluid valves 182, 184, may be fluidly coupled to actuation assembly 164. Rotation member 160, e.g. key 162, may restrict rotation of sleeve 140. Actuator 164 may have fixed piston 166, 168 and moving cylinder 170 having second toothed portion 172. A locking assembly 196 may lock sleeve assembly 138.

Description

SWITCHING ASSEMBLY FOR DUAL SPEED FINAL DRIVE
Technical Field
100011 Present disclosure relates to a dual speed final drive for a machine and more particularly to a switching assembly for the dual speed final drive.
Background
100021 A final drive in a machine is configured to provide multiple speed ranges to assist the machine during various operations such as normal driving, digging, loading etc. Further, the machines have a gear selector to select one ol the multiple speed ranges in the final drive assembly. For example, in a low speed range operation of the final drive, the machine travels at slow speed with high torque, which is required during, digging, earth moving, and the like.
Alternatively, in a high speed range operation of the final drive assembly, the machine travels at higher speed, which is required during a normal driving or cruising.
10003] A typical final drive assembly includes a pair of coupled cpicyclic gear sets to selectively engage the final drive in one of the multiple speed ranges.
Further, a switching assembly is provided to switch between the multiple speed ranges by engaging one or both of the epicyclic gear sets. The switching assembly is provided external to the final drives and operatively coupled to the epicyclic gear sets via a complex mechanism.
Summary
10004] In one aspect, the present disclosure provides a switching assembly for a dual speed final drive. The dual speed final drive includes a drive shall, a first epicyelie gear set, a second epieyelie gear set, and a driven shaft. The switching assembly includes a sleeve assembly movable between a first position and a second position corresponding to a high-speed range and a low-speed range of the dual speed final drive, respectively. The switching assembly further includes a groove disposed on a circumferential face of the sleeve assembly. The switching assembly further includes a displacement member disposed at least partway around the sleeve assembly. The displacement member having a follower and a first toothed portion, the Follower being received in the groove on the circumferential face of the sleeve assembly. The switching assembly further includes an actuation means comprises a second toothed portion engaged with the first toothed portion of the displacement member.
10005] In another aspect, the present disclosure provides a dual speed final drive for a machine. The dual speed final drive includes a first epicyclic gear set, and a second epicyclic gear set coupled to the first epicyclic gear set. The dual speed final drive further includes a drive shaft engaged to the first epicyclic gear set and a driven shaft engaged to the first epicyclic gear set. The dual speed final drive further includes a switching assembly configured to selectively operate the dual speed final drive in a high-speed range and a low-speed range. The switching assembly includes a sleeve assembly movable between a first position and a second position corresponding to the high-speed range and the low-speed range of the dual speed final drive, respectively. The switching assembly frirther includes a groove disposed on a circumFerential race olthe sleeve assembly. The switching assembly further includes a displacement member disposed at least partway around the sleeve assembly. The displacement member having a follower and a first toothed portion, the follower being received in the groove on the circumferential face of the sleeve assembly. The switching assembly further includes an actuation means comprises a second toothed portion engaged with the first toothed portion of the displacement member. The switching assembly frirther includes a locking assembly configured to lock the sleeve assembly in at least one of the first position and the second position.
10006] Other features and aspects of this disclosure will be apparent from the following description and the accompanying drawings.
Brief Description of the Drawings
10007] Figure 1 illustrates a schematic view of a dual final drive; 10008] Figure 2 illustrates an exemplary ftont side view oF the dual speed final drive; 10009] Figure 3 illustrates a detailed view of a portion of a switching assembly of Figure 2; 10010] Figure 4 illustrates an exemplary front side view of the dual speed final drive in the high mode of operation of the dual final drive; 100111 Figure 5 illustrates an exemplary front side view of the dual speed final drive in the low mode oloperation ofthe dual final drive; and 100121 Figure 6 illustrates an exemplary front side view of the dual speed final drive in the neutral mode of operation of the dual final drive.
Detailed Description
100131 Reference will now he made in detail to specific embodiments or features, examples of which are illustrated in the accompanying drawings.
Generally, corresponding or similar reference numbers will be used, when possible, to refer to the same or corresponding parts.
100141 The present disclosure relates to a final drive of a machine, and more particularly to a dual speed final drive configured to operate the machine in a high-speed range and a low-speed range of operation. Figure 1 illustrates a schematic of an exemplary dual spccd final drive 100, according to an embodiment of the present disclosure. The dual speed final drive 100 includes a coupled epicyclic gear set 102 disposed within an enclosure 104. The coupled epicyclic gear set 102 includes a first epieyclic gear set 106 and a second epicyclic gear set 108.
100151 The first epieyclic gear set 106 includes a rotatable first sun gear 110, a plurality of first planet gears 112, a first planet carrier 114, and a first planet gears annulus 116. The first planet carrier 114 is attached to the first planet gears 112 which are engaged to rotate with the first sun gear 110. Further, the first planet gears annulus 116 rotatably supports the first planet gears 112 in the first epicyclic gear set 106. Similarly, the second epieyelie gear set 108 includes a rotatable second sun gear 118, a plurality of second planet gears 120, a second planet carrier 122, and a second planet gears annulus 124. The second planet carrier 122 is attached to the second planet gears 120 which arc engaged to rotatc with the second sun gear 118. The second planet carrier 122 is rigidly attached to the enclosure 104. Further, the second planet gears annulus 124 rotatably supports the second planet gears 120 in the second epicyclic gear set 108. As illustrated in Figure 1, the first planet gears annulus 116 is rotatably engaged with the second sun gear 118 to form the coupled epicyclic gear set 102. In an embodiment, the first epicyclic gear set 106 and the second epicyclic gear set 108 have dillerent gear ratios.
100161 The enclosure 104 includes a face plate 126 and a back plate 128. Thc face plate 126 includes a drive shaft opening 130 to receive a drive shaft 132 therein. The drive shaft 132 may be an engine output shaft, a transmission output shaft, or a torque converter output shaft and engaged to the first sun gear 110 of the first epicyclie gear set 106. The back plate 128 includes a driven shaft opening 134 to receive a driven shaft 136 therein. The driven shaft 136 may be a differential input shall and the 111cc and engaged to the first planet carrier 114.
100171 According to an embodiment of the present disclosure, the dual speed final drive 100 includes a switching assembly 138 to selectively operate the dual speed final drive 100 in a high-speed range and a low-speed range. The switching assembly 138 includes a sleeve assembly 140. The sleeve assembly is hydraulically controlled and movable between a first position (shown in Figure 1) and a second position (not shown). During the high-speed range of operation of the dual speed final drive 100, the sleeve assembly 140 is positioned in the first position to provide an output at the driven shaft 136 through the first epicyclic gear set 106 only. During the low-speed range of operation of the dual speed final drive 100, the sleeve assembly 140 is positioned in the second position to provide the output at the driven shaft 136 through the first epicyclic gear set 106 and the second cpicyclic gear set 108 together. Various details of the switching assembly 138, according to various embodiments of the present disclosure, arc now described in conjunction with Figurcs 2 to 6.
100181 Figure 2 illustrates an exemplary front side view of the dual speed final drive 100. As illustrated, a front cover of the dual speed final drive 100 is removed to illustrate the switching assembly 138. The switching assembly 138 is mounted on the face plate 126 such that the sleeve assembly 140 is disposed in the drive shaft opening 130 ol the lace plate 126. In an embodiment, as illustrated in detailed view in Figure 2, the sleeve assembly 140 may include a first sleeve 142 and a second sleeve 144. The first sleeve 142 includes splincs 146 on an inner face 148 and an outer face 150 of the first sleeve 142. The sleeve assembly 140 may further include a split bearing 152. The split bearing 152 is configured to couple the first sleeve 142 to the second sleeve 144. The second sleeve 144 includes a circumlerential race 154. In an embodiment, the circumferential face 154 may include one or more grooves 156 which may be at least partially helical, and key-ways 158 disposed thereon. As illustrated in Figure 2, the switching assembly 138 further includes a rotation member 160. In an embodiment, the rotation member 160 is a key-plate and includes keys 162 corresponding to the key-ways 158 on the second sleeve 144. The keys 162 on the rotation member 160 are engaged with the key-ways 158 provided on the second sleeve 144.
100191 According to an embodiment of the present disclosure, the switching assembly 138 fiwther includes an actuation means 164 configured to axially movc the sleeve assembly 140 between the first position and the second position. In an aspect of the present disclosure, the actuation means 164 is a fixed-piston and movable-cylinder type actuation means. The actuation means 164 includes a first piston 166 and a second piston 168 disposed at opposite ends of a movable-cylinder 170. In an embodiment, the actuation means 164 includes a second toothed portion 172 attached to a first surface 174 of the movable-cylinder 170.
The first piston 166 and the second piston 168 are rigidly attached to the face plate 126 through a first set of fasteners 176 and a second set of fasteners 178 respectively. Alternatively, in other embodiments, the actuation means 164 may include only one fixed-piston received in the movable-cylinder and the fixed-piston rigidly attached to the face plate 126.
10020] In an embodiment, the switching assembly 138 includes a valve assembly 180 attached to the face plate 126. The valve assembly 180 may be hydraulically andlor electronically coupled to one or more interface devices (not shown) located in an operator station of the machine. In an embodiment, the operator interface devices may include a parking brake, a selector switch, and the like. The valve assembly 180 includes a first fluid valve 182, and a second fluid valve 184. As shown in Figure 2, the first piston 166 and the second piston 168 are fluidly coupled to the first fluid valve 182 through a first fluid line 186 and a second fluid line 188, respectively.
100211 Figure 3 illustrates a detailed view of a portion of the switching assembly 138 of Figure 2. In an embodiment, the switching assembly 138 includes a displacement member 190 disposed around the sleeve assembly 140 (see Figure 2) and includes followers 192. The followers 192 are slidably received within the grooves 156 of the second sleeve 144 (see Figure 2). In an embodiment as shown in Figure 3, the displacement member 190 further includes a first toothed portion 194. The first toothed portion 194 is engaged with the second toothed portion 172 provided on the movable-cylinder 170 to form a rack and pinion arrangemenL 100221 In an embodiment, the switching assembly 138 further includes a locking assembly 196. The locking assembly 196 includes a locking plate 198.
The locking plate 198 is attached to a second surface 200 of the movable-cylinder and extends therefrom. The locking plate 198 includes a hole 202 therein.
As shown in Figure 2, the locking plate 198 includes a first end 204 and a second end 206. In an embodiment, the locking assembly 196 includes a housing 208.
The housing 208 is hydraulically coupled to the second fluid valve 184, through a third fluid line 210. A locking member 212 extends from the housing 208 towards the locking plate 198. The locking member 212 is movable between an extended position and a retracted position. A hydraulic pressure from the second fluid valve 184 may bias the locking member 212 in the extended position. The housing 208 may frirther include a spring 214 operably coupled to the locking member 212 and configured to bias the locking member 212 in the retracted position.
100231 In an embodiment, the switching assembly 138 is configured to switch the dual speed final drive 100 into a high-speed range, a neutral-speed range, and a low-speed range. The high-speed range disclosed herein reFers to an operation of the machine while travelling on-road and off-road, and the low-speed range disclosed herein reFers to operation of the machine while performing operations such as digging, earth moving and the like. In neutral-speed range no torque is transmitted from the dual speed final drive 100 to the machine. Hence in an exemplary embodiment, the neutral-speed range may be engaged when the machine is receiving torque/power from external sources such as but nol limited to an exemplary situation of towing olthe machine through a tow vehicle.
100241 In an aspect of the present disclosure, the first fluid valve 182 is configured to selectively supply a fluid to the actuation means 164 to selectively move the movable-cylinder 170 to move the second toothed portion 172 and the locking plate 198 attached thereto. In an embodiment, the movable-cylinder 170 is selectively movable between a high-speed position, a neutral-speed position, and a low-speed position. In an exemplary embodiment, the high-speed position of the movable-cylinder 170 is indicative of a movement of the movable-cylinder towards the first piston 166, and the low-speed position of the movable-cylinder 170 is indicative of the movement of thc movable-cylinder 170 towards the second piston 168. The neutral-speed position of the movable-cylinder 170 is indicative of a position of the movable-cylinder 170 substantially midway to the first piston 166 and the second piston 168.
100251 In an embodiment, movement of the second toothed portion 172 initiates a rotation in the displacement member 190 via the first toothed portion 194. The second sleeve 144 is restricted from a rotational movement due to the inter-engagement of the key 162 at the key-ways 158. During rotation of the displacement member 190, the followers 192 ride along the grooves 156 on the second sleeve 144 to axially move the sleeve assembly 140. Thus disposing the second sleeve 144 in the first position or the second position. In an exemplary embodiment, the high-speed range, the low-speed range and the neutral-speed range arc selected by the positioning of the second sleeve 144 of the sleeve assembly 140. The high speed range, the low speed range and the neutral speed range at the driven shaft 136 are achieved though the first epicyclic gear set 106, both the first and second epicyclie gear sets 106, 108, and neither of the first or the second cpicyelie gear sets 106, 108 respectively.
100261 In an aspect of the present disclosure, the locking assembly 196 is configured to lock the switching assembly 138 in at least one of the high-speed range, the neutral-speed range and the low-speed range. The second fluid valve 184 is configured to selectively supply the fluid to the housing 208 of the locking assembly 196 to bias the locking member 212 into the extended position. In the extended position, the locking member 212 extends towards the locking plate 198 and maybe received in the hole 202 of the locking plate 198, or abut the first end 204, or abut the second end 206 to restrict the movement of the locking plate 198 therefrom. Restricting the movement of the locking plate 198 locks the switching assembly 138 in the high-speed range, the neutral-speed range, or the low-speed range based on the position of the locking plate 198. The spring 214 is configured to bias the locking member 212 in the retracted position upon loss of fluid in the housing 208 such that the locking plate 198 is unlocked and the movable-cylinder 170 may be moved in any of the high-speed position, a neutral-speed position, and a low-speed position. The operator may then choose to opcratc the dual spccd final drivc 100 in any of the high-spccd range, thc neutral-speed range, and the low-speed range.
Industrial Applicability
100271 The industrial applicability of the switching assembly 138 in the dual speed linal drive 100 described herein will be readily appreciated from the foregoing discussion. In an embodiment, the dual speed final drive 100 may he used in a machine such as a wheeled or tracked military vehicle. Alternatively, the machine may be any wheeled or tracked machine that performs at least one operation associated wiih for example mining, construction, and other industrial applications, for example, baekhoe loaders, skid steer loaders, wheel loaders, motor graders, tracked -type tractor, and many other machines.
100281 For the operation of the dual speed final drive 100, the first fluid valve 182 and the second fluid valve 184 is hydraulically coupled to the selector switch and parking brake lever located in the operator cabin respectively. When the machine is not operating, there is a loss of hydraulic pressure in the actuation means 164, and the locking assembly 196. The locking member 212 associated with the locking assembly 196 is in the retracted position such that the actuation means 164 is movable in any of the high-speed range, the neutral-speed range, and the low-speed range.
100291 Figure 4 illustrates an exemplary front side view of the dual speed final drive 100 in the high-speed range of the dual speed final drive 100. When the operator selects the high-speed range through the selector switch, the first fluid valve 182 supplies the fluid in the first fluid line 186. The first piston 166 receives the fluid from the first fluid line 186 and supplies the fluid into the movable-cylinder 170 initiating a movement of the movable-cylinder 170 along the first piston 166. Hence, the second toothed portion 172 and the locking plate 198 attached to the movable-cylinder 170 are displaced towards the first set of fasteners 176. The second toothed portion 172 rotates the first toothed portion 194 associated with the displacement member 190 in a clockwise direction. The followers 192 associated with the displacement member 190 traverse in the grooves 156 to displace the sleeve assembly 140 in the first position. The splines 146 on the outer face 150 of the first sleeve 142 are engaged with the second sun gear 118 and the second planet gears annulus 124 of the second epicyclic gear set 108. Therefore, the second epicyclic gear set 108 remains stationary and the torque/power is transmitted through the first epicyclic gear set 106 only. The operator may then release a parking brake by operating the parking brake lever.
The second fluid valve 184 then supplies fluid to the housing 208 such that the locking member 212 is biased in the extended position to abut the first end 204 of the locking plate 198. As shown in Figure 4, the extended position of the locking member 212 restricts the movement of the locking plate 198 attached to the movable-cylinder 170 and locks the switching assembly 138 locking the dual speed final drive 100 in the high-speed range.
100301 Figure 5 illustrates an exemplary front side view of the dual speed final drive 100 in the low-speed range of the dual speed final drive 100. When the operator selects low-speed range, the first fluid valve 182 supplies the fluid in the second fluid line 188. The second piston 168 receives the fluid from the second fluid line 188 and supplies the fluid into the movable-cylinder 170 initiating a movement of the movable-cylinder 170 along the second piston 168.
Hence, the second toothed portion 172 and the locking plate 198 attached to the movable-cylinder 170 are displaced towards the second set or fasteners 178. The second toothed portion 172 rotates the first toothed portion 194 associated with the displacement member 190 in an anti-clockwise direction. The followers 192 associated with the displacement member 190 traverses in the grooves 156 to displace the sleeve assembly 140 in the second position. The splines 146 on the outer face 150 of the first sleeve 142 are engaged with the second planet gears annulus 124 olthe second epicyclic gear set 108 and the splines 146 on the inner face 148 are engaged with the first planet carrier 114 of the first epicyclic gear set 106. Therefore, the torque/power is transmitted through both the first epicyclic gear set 106 and the second epicyclie gear set 108. The operator may then release the parking brake by operating the parking brake lever. The second fluid valve 184 then supplies fluid to the housing 208 such that the locking member 212 is biased in the extended position to abut the second end 206 of the locking plate 198. As shown in Figure 5, the extended position of the locking member 212 restricts the movement of the locking plate 198 attached to the movable-cylinder and locks the switching assembly 138 locking the dual speed final drive 100 in the low-speed range.
100311 Figure 6 illustrates an exemplary front side view of the dual speed final drive 100 in the neutral-speed range of the dual speed final drive 100.
When the operator selects the neutral-speed range, the first fluid valve 182 supplies the fluid in both the first fluid line 186, and the second fluid line 188.
The movable-cylinder 170 remains midway to the first piston 166 and the second piston 168. The splines 146 of the first sleeve 142 are disengaged from both the first epicyclic gear set 106 and the second epicyclic gear set 108. Therefore, no torque/power is transmitted through the coupled epicyclic gear set 102. The operator may then release the parking brake by operating the parking brake lever.
The second fluid valve 184 then supplies fluid to the housing 208 such that the locking member 212 is biased in the extended position and located in the hole 202 disposed on the locking plate 198. As shown in Figure. 5, the extended position of the locking member 212 restricts the movement of the locking plate 198 attached to the movable-cylinder 170 and locks the switching assembly 138 locking the dual speed final drive 100 in the neutral-speed range.
100321 From the Foregoing it will he appreciated that, although specific embodiments have been described herein for purposes of illustration, various modifications or variations may be made without deviating from the spirit or scope of inventive features claimed herein. Other embodiments will be apparent to those skilled in the art from consideration of the specification and figures and practice of the arrangements disclosed herein. It is intended that the specification and disclosed examples be considered as exemplary only, with a true inventive scope and spirit being indicated by the following claims and their equivalents. c1
GB1319146.5A 2013-10-30 2013-10-30 Switching assembly for dual speed final drive Withdrawn GB2519949A (en)

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GB1319146.5A GB2519949A (en) 2013-10-30 2013-10-30 Switching assembly for dual speed final drive
PCT/GB2014/052719 WO2015063450A2 (en) 2013-10-30 2014-09-09 Switching assembly for dual speed final drive

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GB2519949A true GB2519949A (en) 2015-05-13

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CN108799343A (en) * 2018-06-20 2018-11-13 杨胜 A kind of anti skid bearing

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WO2015063450A3 (en) 2015-09-17
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