CN215861562U

CN215861562U - Transmission device and feeder comprising the same

Info

Publication number: CN215861562U
Application number: CN202122085909.XU
Authority: CN
Inventors: 熊宏佳; 熊俞智
Original assignee: Foshan V Plus Machinery Co ltd
Current assignee: Foshan V Plus Machinery Co ltd
Priority date: 2021-08-31
Filing date: 2021-08-31
Publication date: 2022-02-18
Anticipated expiration: 2031-08-31

Abstract

The utility model relates to the technical field of variable-speed transmission, in particular to a transmission device and a feeder comprising the transmission device, wherein the transmission device comprises a shell, and a driving shaft and a driven shaft which are arranged in parallel, the driving shaft and the driven shaft are both rotationally connected in the shell, the driving shaft is coaxially sleeved with a plurality of driving gears, the driven shaft is sleeved with a plurality of driven gears, and the driving gears and the driven gears correspond to each other one by one and are meshed with the corresponding driving gears and the corresponding driven gears; the transmission device further comprises a clutch sleeve and a gear shifting mechanism, wherein the clutch sleeve can axially slide relative to the driven shaft and can be sleeved on the periphery of the driven shaft in a non-rotatable mode. The clutch sleeve is characterized in that transmission grooves are formed in two end faces of the clutch sleeve, a transmission part is arranged on the end face of the driven gear, the gear shifting mechanism is connected with the clutch sleeve and used for driving the clutch sleeve to move axially along the driven shaft. The utility model can realize speed change without dismounting any part, and the gear shifting mechanism is directly connected with the clutch sleeve without connecting a shifting fork, thereby having simple structure and lower manufacturing cost.

Description

Transmission device and feeder comprising the same

Technical Field

The present invention relates to the technical field of variable speed transmissions, and more particularly to a transmission device and a feeder including the transmission device.

Background

At present, when the feeder is changed in speed, only two gear speeds exist under the condition of the gear ratio set in a factory, the motor is fast and slow, if the speed beyond the gear ratio set in the factory is required to be obtained, parts such as a rear cover screw, a rear cover, a gear locking nut, a gasket, a gear and a flat key need to be disassembled, the parts are installed again after the gear with a new gear ratio is replaced, a new using speed can be obtained, if the speed obtained by replacing the new gear ratio does not accord with the actual use requirement of production, the disassembling and assembling steps need to be repeated, and the process is time-consuming and labor-consuming. Frequent disassembly and assembly of the feeder not only can increase the maintenance cost and influence the service life of parts of the feeder, but also a large amount of lubricating grease at the meshing position is easy to leak and pollute the working environment in the disassembly process; in addition, the disassembly and assembly of the feeder require technical requirements in the professional field and are complicated in disassembly and assembly operation, and potential safety hazards are left if the disassembly and assembly operation is improper.

Chinese patent CN112081880A and chinese patent CN112081881A both disclose a transmission structure, during shifting, the shift knob drives the shift shaft to rotate 180 degrees, the rotation of the boss drives the elongated slot of the shift fork to slide along the support, the shift fork therefore slides along the support, the support is parallel to the input shaft, the shift fork can drive the sliding guide sleeve to slide axially, the key of the sliding guide sleeve slides to the axial position corresponding to the gear sets with different gear ratios, thereby realizing the speed change and shifting. Above-mentioned scheme all adopts the rotatory drive of boss on the gear shifting shaft shifting fork slip again by shift fork drive slip guide pin bushing endwise slip, however above-mentioned scheme has following technical problem: the shifting fork is not a standard part, needs to be matched with a guide mechanism for use, needs a plurality of parts, has high matching requirement on the parts, and causes high cost and reduced working reliability; (2) when the shifting fork gear shifting scheme of multi-gear shifting is used for two-gear shifting, if the number of gears is directly reduced, the shifting fork gear shifting scheme is adopted, and the shifting fork is adopted to shift the guide sleeve to realize gear shifting, the design research and development cost is reduced, but the problem pointed out by the point (1) still exists; if the shifting fork is adopted to directly shift the gear, although the number of parts is reduced, under the condition of high rotating speed, the problems of gear striking and gear engaging failure can occur, and the cost and the working reliability are difficult to be considered; (3) when the gear shifting knob is rotated to shift gears, the gear cannot be accurately rotated, and the condition of neutral gear is easily caused by rotating a plurality of angles or rotating a plurality of angles less.

In addition, chinese patent CN203754045U discloses an improved structure of feeding wheel transmission for material feeding machine, in which the worm gear shaft drives the driving pinion to drive the driving gearwheel, so as to link the driving shaft of the gear transmission set to sequentially drive the driving gear, the two pinions and the two driven gears to rotate, and the driven gears synchronously drive the gear transmission chain to rotate, so as to drive the first and second feeding wheel sets to operate. According to the scheme, transmission is carried out through a five-shaft structure of the driving pinion, the driving gearwheel, the driving gear, the pinion and the driven gear, the number of required gears is large, two transition shafts need to be arranged, the meshing relation between the gears is complex, the manufacturing cost and the installation cost are high, and the working stability of the feeder is influenced when the installation precision is insufficient.

SUMMERY OF THE UTILITY MODEL

The utility model aims to overcome the defects in the prior art, and provides a transmission device and a feeder comprising the transmission device.

In order to solve the technical problems, the utility model adopts the technical scheme that:

the transmission device comprises a shell, a driven shaft and a plurality of driven gears, wherein the driven shaft is rotatably connected in the shell; (ii) a The transmission device further comprises a clutch sleeve and a gear shifting mechanism, wherein the clutch sleeve can axially slide relative to the driven shaft and can be sleeved on the periphery of the driven shaft in a non-rotatable mode. The clutch sleeve is characterized in that transmission grooves are formed in two end faces of the clutch sleeve, a transmission part is arranged on the end face of the driven gear, the gear shifting mechanism is connected with the clutch sleeve and used for driving the clutch sleeve to axially move along a driven shaft, and the clutch sleeve is axially moved to the position where the transmission grooves are nested in the transmission part and then connected with the driven gear.

According to the transmission device, the gear shifting mechanism is directly connected with the clutch sleeve, a shifting fork is not required to be connected, the clutch sleeve axially slides to the axial position corresponding to the driven gear with different gear ratios, the transmission groove is nested with the transmission piece, gear shifting is realized, the structure is simple, the manufacture is easy, the manufacturing cost is saved, speed change can be realized without dismounting any part, the machine adjusting time can be shortened, the production efficiency is improved, the consumable service time and the service cost are reduced, the safety risk caused by dismounting is reduced, the requirement on the professional technology of a user is reduced, and the service life of equipment is prolonged; the driving mechanism provides power for the rotation of the driving shaft, and the driving shaft rotates to drive the driving gear on the driving shaft to rotate together so as to drive the driven gear nested with the clutch sleeve to rotate, so that the driven shaft is driven to rotate to output power, and speed change is realized. The transmission device has simple structure and reliable performance, and can reduce the manufacturing cost.

Furthermore, the peripheral face of the clutch sleeve is provided with a ring groove, the gear shifting mechanism comprises a gear shifting shaft and a protrusion located at the end of the gear shifting shaft, the axis of the gear shifting shaft is perpendicular to the axis of the driven shaft, the protrusion is eccentrically arranged at one end of the gear shifting shaft relative to the axis of the gear shifting shaft, and the protrusion is inserted into the ring groove.

Furthermore, the other end of the pulling and blocking shaft is provided with a cam step which is formed with wave crests and wave troughs in a way that the radial distance of the pulling and blocking shaft relative to the axis of the pulling and blocking shaft is changed, the pulling and blocking shaft is sleeved with a shaft sleeve end cover, and the shaft sleeve end cover is positioned on the periphery of the cam step; the end cover of the shaft sleeve is provided with a through hole, a spring ball structure comprising a ball and a spring is arranged in the through hole, one end of the spring is abutted against the shell, the other end of the spring is abutted against the ball, and the ball is abutted against the outer peripheral surface of the cam step; when shifting is completed, the ball is abutted to the trough of the cam step.

Furthermore, the structure of the spring balls is divided into two groups, and the two groups of the structure of the spring balls are symmetrical to two sides of the central axis of the cam step.

Furthermore, the periphery of the driven shaft is provided with a limiting block, a limiting groove is formed in the inner hole of the clutch sleeve, and the limiting block is connected with the limiting groove in a sliding mode.

Furthermore, the limiting block is an external spline step arranged on the periphery of the driven shaft, the limiting groove is a spline inner hole arranged at the inner hole of the clutch sleeve, and the external spline step is in sliding connection with the spline inner hole.

Furthermore, a plurality of first bosses which are equally spaced are arranged at two ends of the clutch sleeve, the transmission groove is positioned between the adjacent first bosses, and the transmission part is a second boss which is equally spaced from the driven gear and faces the end face of the clutch sleeve.

Further, the span angle occupied by the first bosses is smaller than the span angle occupied by the interval between the adjacent first bosses, and the span angle occupied by the second bosses is smaller than the span angle occupied by the interval between the adjacent second bosses.

Furthermore, the driving shaft is rotatably connected in the shell, the driving shaft and the driven shaft are arranged in parallel, the driving shaft is connected with a driving mechanism for driving the driving shaft to rotate, the driving shaft is coaxially sleeved with a plurality of driving gears fixed relative to the driving shaft, the driven gear can rotate relative to the driven shaft but is sleeved on the driven shaft in a limited axial movement mode, and the driving gears and the driven gears are in one-to-one correspondence and are meshed with the corresponding driving gears and the corresponding driven gears.

Further, the driving gear comprises a first driving gear and a second driving gear, the driven gear comprises a first driven gear and a second driven gear, the first driving gear is meshed with the first driven gear, the second driving gear is meshed with the second driven gear, and the clutch sleeve is located between the first driven gear and the second driven gear.

Furthermore, the driving mechanism comprises a driving motor, a worm and a worm wheel, the worm is connected to the output end of the driving motor, the worm is meshed with the worm wheel, the worm wheel is coaxially and fixedly connected with the driving shaft, and the worm wheel is located between the first driving gear and the second driving gear.

The utility model also provides a feeder, which comprises a power distribution mechanism and the transmission device, wherein an input part of the power distribution mechanism is connected to an output end of the driven shaft.

Furthermore, the power distribution mechanism comprises a transition shaft which is balanced on the driven shaft and supported on the shell through a bearing and can freely rotate relative to the shell, two first driving shafts which are balanced on the transition shaft and supported on the shell through a bearing and can freely rotate relative to the shell, and two second driving shafts which are balanced on the first driving shafts and supported on the shell through a bearing and can freely rotate relative to the shell, wherein a driving chain wheel is fixedly sleeved on the part of the driven shaft protruding out of the shell, a driven chain wheel is fixedly sleeved on the transition shaft, the driving chain wheel is connected and meshed with the driven chain wheel through a chain, a transition gear is sleeved on the inner side edge of the driven chain wheel on the transition shaft, two driven gears are fixedly sleeved on the two first driving shafts respectively, and the transition gear is meshed with the two driven gears simultaneously; the end parts of the two first driving shafts are provided with first chain wheels, the end parts of the two second driving shafts are provided with second chain wheels, the number of teeth of the first chain wheels is equal to that of the second chain wheels, and power is transmitted through the meshing of the first chains and the second chains respectively.

By adopting the transmission device, smooth speed change can be realized without dismounting any part, the machine adjusting time can be shortened, the production efficiency can be improved, the consumable service time and the service cost can be reduced, the safety risk caused by dismounting can be reduced, the requirement on the professional technology of a user can be reduced, and the service life of equipment can be prolonged; and the structure is simple, the performance is reliable, and the manufacturing cost can be reduced. In addition, the number of transmission gears required by the power distribution mechanism of the feeder is reduced, the structure is simplified, and the manufacturing cost of products can be reduced.

Compared with the prior art, the utility model has the beneficial effects that:

the speed changer device and the feeder comprising the speed changer device can realize speed change without dismounting any part, can shorten the time for adjusting the speed changer, improve the production efficiency, reduce the time and the cost of using consumables, reduce the safety risk caused by dismounting, reduce the requirement on the professional technology of a user, and prolong the service life of equipment; the gear shifting mechanism is directly connected with the clutch sleeve, a shifting fork is not required to be connected, the structure is simple, the manufacturing cost is lower, and better economic benefits are achieved.

Drawings

FIG. 1 is an exploded schematic view of a transmission arrangement;

FIG. 2 is a schematic illustration of a portion of the transmission assembly;

FIG. 3 is a schematic diagram of a transmission device shifting;

FIG. 4 is a schematic illustration of a transmission device shift shaft;

FIG. 5 is a schematic view of another perspective of a transmission device shift shaft;

FIG. 6 is an exploded view of the feeder;

FIG. 7 is a schematic view of a feeder structure;

FIG. 8 is a schematic view of another view of the feeder;

in the drawings: 100. a transmission device; 110. a housing; 111. a box body; 112. a box cover; 120. a drive shaft; 121. a middle step; 122. a first step; 123. a second step; 124. a first bearing; 125. a second bearing; 130. a driven shaft; 131. an external spline step; 132. a third step; 133. a fourth step; 134. A third bearing; 135. a fourth bearing; 136. a drive sprocket; 140. a drive mechanism; 141. a drive motor; 142. a worm; 143. a worm gear; 150. a driven gear; 151. a transmission member; 152. a first driven gear; 153. a second driven gear; 160. a driving gear; 161. a first drive gear; 162. a second driving gear; 170. a clutch sleeve; 171. a transmission groove; 172. a spline inner bore; 173. a first boss; 174. a ring groove; 180. a gear shift mechanism; 181. pulling out the gear shaft; 182. a protrusion; 183. a knob; 184. a cam step; 185. A shaft sleeve end cover; 186. a through hole; 187. a spring; 189. a ball bearing; 200. a power split mechanism; 210. a transition shaft; 211. a driven sprocket; 220. a first drive shaft; 221. a driven gear; 222. a first sprocket; 230. A second drive shaft; 231. a second sprocket; 240. a spacer sleeve; 250. a transition gear; 260. a roller chain; 270. A first roller chain; 280. a second roller chain.

Detailed Description

The present invention will be further described with reference to the following embodiments. Wherein the showings are for the purpose of illustration only and are shown by way of illustration only and not in actual form, and are not to be construed as limiting the present patent; to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.

The same or similar reference numerals in the drawings of the embodiments of the present invention correspond to the same or similar components; in the description of the present invention, it should be understood that if there is an orientation or positional relationship indicated by the terms "upper", "lower", "left", "right", etc. based on the orientation or positional relationship shown in the drawings, it is only for convenience of describing the present invention and simplifying the description, but it is not intended to indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and therefore, the terms describing the positional relationship in the drawings are only used for illustrative purposes and are not to be construed as limiting the present patent, and the specific meaning of the terms may be understood by those skilled in the art according to specific circumstances.

Example one

As shown in fig. 1 to 5, an embodiment of a transmission device 100 of the present invention includes a housing 110, and a driving shaft 120 and a driven shaft 130 that are arranged in parallel, wherein the driving shaft 120 and the driven shaft 130 are both rotatably connected in the housing 110 through bearings, the driving shaft 120 is connected to a driving mechanism 140 that drives the driving shaft 120 to rotate, the driving shaft 120 is coaxially sleeved with a plurality of driving gears 160 that are fixed relative to the driving shaft 120, the driven shaft 130 is sleeved with a plurality of driven gears 150 that can rotate relative to the driven shaft 130 but are limited in axial movement, and the driving gears 160 and the driven gears 150 are in one-to-one correspondence and the corresponding driving gears 160 and driven gears 150 are engaged; the transmission device 100 further includes a clutch sleeve 170 and a shift mechanism 180, wherein the clutch sleeve 170 is axially slidable relative to the driven shaft 130 but non-rotatably sleeved on the periphery of the driven shaft 130. The two end surfaces of the clutch sleeve 170 are provided with transmission grooves 171, the end surface of the driven gear 150 is provided with a transmission piece 151, the gear shifting mechanism 180 is connected with the clutch sleeve 170, the gear shifting mechanism 180 is used for driving the clutch sleeve 170 to axially move along the driven shaft 130, and the clutch sleeve 170 is connected with the driven gear 150 when the transmission grooves 171 are nested in the transmission piece 151 after axially moving.

In the implementation of the embodiment, the gear shifting mechanism 180 is directly connected with the clutch sleeve 170 without connecting a shifting fork, so that the clutch sleeve 170 axially slides to the axial position corresponding to the driven gear 150 with different gear ratios, and the transmission groove 171 is nested with the transmission piece 151 to realize gear shifting; after gear shifting is completed, the driving mechanism 140 provides power for rotation of the driving shaft 120, the driving shaft 120 rotates to drive the driving gear 160 on the driving shaft 120 to rotate together, and then the driven gear 150 nested with the clutch sleeve 170 is driven to rotate, so that the driven shaft 130 is driven to rotate to output power, and speed changing is achieved. The shifting mechanism 180 and the clutch sleeve 170 of the present embodiment can be applied to two-gear shifting or even multi-gear shifting, and the two-gear shifting or multi-gear shifting can be realized by correspondingly arranging the positions and the number of the driving gear 160, the driven gear 150 and the clutch sleeve 170.

The clutch sleeve 170 is provided with a circular groove 174 on the outer peripheral surface thereof, the shifting mechanism 180 includes a shift shaft 181 and a cylindrical protrusion 182 on the shift shaft 181, the axis of the shift shaft 181 is perpendicular to the axis of the driven shaft 130, the protrusion 182 is eccentrically disposed at one end of the shift shaft 181 relative to the axis of the shift shaft 181, and the protrusion 182 is inserted into the circular groove 174 without affecting the rotation of the clutch sleeve 170, as shown in fig. 3 and 4. When the gear shifting shaft 181 rotates by a certain angle, the protrusion 182 drives the clutch sleeve 170 to move a certain distance along the axial direction of the driven shaft 130, so that the clutch sleeve 170 is engaged with or disengaged from the driven gear 150: when the clutch sleeve 170 is engaged with the driven gear 150, the driven shaft 130 will follow the rotation of the driven gear 150 in the process of meshing with the driving gear 160; when the clutch sleeve 170 is disengaged from the driven gear 150, the driven shaft 130 does not rotate with the driven gear 150 during the rotation of the driven gear 150 in engagement with the driving gear 160. Wherein, the protrusion 182 is configured as a protrusion small cylinder so as to improve the smoothness of the protrusion 182 sliding in the ring groove 174, and the other end of the shift shaft 181 is connected with a knob 183 so as to facilitate the shift operation. It should be noted that the shifting by rotating the shift pulling shaft 181 is preferable for the convenience of operation, and is not a limiting rule of the present invention, and other shifting mechanisms 180 that can linearly push the clutch sleeve 170 to slide may also be applied to the present invention.

The other end of the shift shaft 181 is provided with a cam step 184 which has a radial distance change relative to the axis of the shift shaft 181 and forms a wave crest and a wave trough, the shift shaft 181 is sleeved with a shaft sleeve end cover 185, and the shaft sleeve end cover 185 is positioned on the periphery of the cam step 184; the sleeve cover 185 has a through hole 186, a spring ball structure including a ball 189 and a spring 187 is built in the through hole 186, one end of the spring 187 abuts against the housing 110, the other end of the spring 187 abuts against the ball 189, and the ball 189 abuts against the outer circumferential surface of the cam step 184, as shown in fig. 3, 4, and 5; upon completion of the shift, the balls 189 abut against the valleys of the cam steps 184. The spring ball structures are two sets, and the two sets of spring ball structures are symmetrical to two sides of the central axis of the cam step 184. In this embodiment, the wave crests and the wave troughs on the cam step 184 are symmetrically distributed, and during the process of rotating the shift shaft 181, the balls 189 always press and abut against the outer peripheral surface of the cam step 184: when shifting is completed, the balls 189 abut to the valleys of the cam steps 184; when the gear is not shifted to the right position, the ball 189 is abutted to the wave crest or other waist position of the cam step 184, and at the moment, under the action of the spring 187, the gear shifting shaft 181 continuously rotates and returns to the wave trough of the cam step 184, so that the neutral gear condition can be effectively prevented. For better reset and shifting effects, the wave peaks of the present embodiment can be set to a position intermediate the positions where the balls 189 abut the cam steps 184 in both shift positions, as shown in fig. 5. When the spring ball structures are arranged in two groups, the shaft sleeve end cover 185 is also radially and symmetrically provided with two through holes 186 penetrating through the inner hole, and the through holes 186 limit the balls 189 to move only along the axes of the through holes 186; the housing 110 is half-wrapped with the shaft sleeve end cap 185, i.e., the shaft sleeve end cap 185 is partially disposed inside the housing 110 and partially disposed outside the housing 110. In addition, the pulling shaft 181 of the present embodiment is sleeved with an O-ring, and the O-ring is pressed by the inner hole wall of the housing 110 and the step surface of the pulling shaft, so as to achieve the sealing effect.

The periphery of the driven shaft is provided with a limiting block, a limiting groove is formed in the inner hole of the clutch sleeve, and the limiting block is connected with the limiting groove in a sliding mode, so that the clutch sleeve 170 can axially slide relative to the driven shaft 130 but cannot rotate. Specifically, in this embodiment, the driven shaft 130 is provided with an external spline step 131, the clutch sleeve 170 is provided with a spline inner hole 172, the external spline step 131 serves as a limiting block, the spline inner hole 172 serves as a limiting groove, the external spline step 131 is slidably connected with the spline inner hole 172, the clutch sleeve 170 can axially move relative to the driven shaft 130, but the clutch sleeve 170 cannot rotate relative to the driven shaft 130, as shown in fig. 1. Of course, the sliding connection between the external spline steps 131 and the spline inner bore 172 is not the only type of connection between the clutch sleeve 170 and the driven shaft 130, and other limiting structures that can limit the rotation of the clutch sleeve 170 relative to the driven shaft 130 can be adapted to the present invention.

The clutch sleeve 170 has a plurality of first bosses 173 at equal intervals at both ends, the transmission grooves 171 are located between the adjacent first bosses 173, and the transmission member 151 is a second boss at equal intervals on the end surface of the driven gear 150 facing the clutch sleeve 170, as shown in fig. 1. When the second boss is fitted into the driving groove 171, the clutch sleeve 170 is engaged with the driven gear 150, and the relative rotational movement between the driven gear 150 and the driven shaft 130 can be restricted. The span angle occupied by the first bosses 173 is smaller than the span angle occupied by the interval between the adjacent first bosses 173, and the span angle occupied by the second bosses is smaller than the span angle occupied by the interval between the adjacent second bosses. The span angle occupied by all the bosses with equal intervals is smaller than that occupied by the adjacent bosses, and when the bosses are embedded into the interval gaps, a certain span angle virtual position exists, so that the bosses are more easily embedded when being matched from a disengagement state under the condition of relatively large rotation speed difference.

Example two

The embodiment of the transmission device 100 of the present invention is similar to the first embodiment, except that: the transmission device 100 of the present embodiment performs two-speed change. The driving gear 160 includes a first driving gear 161 and a second driving gear 162, the driven gear 150 includes a first driven gear 152 and a second driven gear 153, the first driving gear 161 is engaged with the first driven gear 152, the second driving gear 162 is engaged with the second driven gear 153, and the clutch sleeve 170 is located between the first driven gear 152 and the second driven gear 153. The driving mechanism 140 includes a driving motor 141, a worm 142 and a worm wheel 143, the worm 142 is connected to an output end of the driving motor 141, the worm 142 is engaged with the worm wheel 143, the worm wheel 143 is coaxially and fixedly connected with the driving shaft 120, and the worm wheel 143 is located between the first driving gear and the second driving gear. In the present embodiment, the housing 110 includes a case 111 and a case cover 112 detachably connected.

Specifically, the worm wheel 143 is fixedly sleeved at the middle step 121 of the driving shaft 120, a first step 122 and a second step 123 are arranged on two sides of the middle step 121, the first driving gear 161 and the second driving gear 162 are respectively fixed on the first step 122 and the second step 123, specifically, the first driving gear 161, the second driving gear 162 and the worm wheel 143 are all fixedly connected and installed with the driving shaft 120 through flat keys, the worm wheel 143 is fixedly connected and installed integrally with the driving shaft 120, the worm wheel 143 is meshed and matched with the worm 142, and when power is input from the worm 142, the worm wheel 143 and the driving shaft 120 are integrally driven to rotate around the axis according to a certain proportion of rotation speed. In addition, a first bearing 124 and a second bearing 125 are further installed at both ends of the driving shaft 120, the first bearing 124 and the second bearing 125 are respectively supported on the case 111 and the case cover 112, and the driving shaft 120 is rotatable but fixed in axial position with respect to the housing 110. The driven shaft 130 is provided with an external spline step 131, the external spline step 131 is arranged in the middle of the driven shaft 130, a third step 132 and a fourth step 133 are arranged on two sides of the external spline step 131, the first driven gear 152 and the second driven gear 153 are respectively arranged on the third step 132 and the fourth step 133, and the first driven gear 152 and the second driven gear 153 can freely rotate relative to the driven shaft 130 but are limited in axial movement. In addition, a third bearing 134 and a fourth bearing 135 are further installed at two ends of the driven shaft 130, the third bearing 134 and the fourth bearing 135 are respectively supported on the box body 111 and the box cover 112, a sealing ring is installed at the outer side of the fourth bearing 135, and is pressed by a corresponding step surface of the driven shaft and an inner hole surface of the box cover 112 to achieve a sealing effect, the driven shaft 130 can rotate relative to the housing 110 but is fixed in the axial position, when the clutch sleeve 170 is matched with the first driven gear 152 or the second driven gear 153, the rotation of the first driven gear 152 or the second driven gear 153 can drive the driven shaft 130 to rotate around the axis according to a certain proportion of rotation speed, as shown in fig. 1.

In this embodiment, the other end of the pulling-blocking shaft 181 is provided with a cam step 184 which is formed with peaks and troughs in a radial distance variation manner relative to the axis of the pulling-blocking shaft 181, and the cam step 184 is provided with four peaks and four troughs which are distributed at intervals, uniformly and symmetrically, as shown in fig. 4 and 5. The spring ball structures are two sets, and the two sets of spring ball structures are symmetrical to both sides of the central axis of the cam step 184, as shown in fig. 3. The position marked as the ball 189 when the clutch sleeve 170 is engaged with the first driven gear 152 and disengaged from the second driven gear 153 is marked as the position a, the position marked as the ball 189 when the clutch sleeve 170 is disengaged from the first driven gear 152 and engaged with the second driven gear 153 is marked as the position B, the wave crest is in the middle position of the included angle between the position a and the position B, and the position a and the position B are both positioned at the wave trough. The balls 189 are pressed by the spring 187 to abut against the shift lever cam steps 184. when the shift lever is rotated, the cam steps 184 force the balls 189 to move radially over the peaks and the contact between the balls 189 and the shift lever cam steps 184 is not at the valley, the spring 187 forces the shift lever to rotate in the direction of the nearest valley so that the balls 189 fall into one of the valleys of the cam steps 184.

EXAMPLE III

As shown in fig. 6 to 8, the feeder of the present invention includes a power distribution mechanism 200 and a transmission device 100 according to the first embodiment or the second embodiment, wherein an input member of the power distribution mechanism 200 is connected to an output end of a driven shaft 130. Specifically, the portion of the end of the driven shaft 130 protruding out of the housing 110 is connected to the input of the power split device 200, and the power split device 200 includes a transition shaft 210 supported by the housing 110 through a bearing in balance with the driven shaft 130, two first driving shafts 220 supported by the housing 110 through a bearing in balance with the transition shaft 210, and rotatable with respect to the housing 110, and two second driving shafts 230 supported by the housing 110 through a bearing in balance with the first driving shafts 220 and rotatable with respect to the housing 110. The reduction gearbox driven shaft 130 is fixedly sleeved with a driving chain wheel 136 at the end protruding out of the reduction gearbox, the transition shaft 210 is fixedly sleeved with a driven chain wheel 211, and the driving chain wheel 136 is connected and meshed with the driven chain wheel 211 through a roller chain 260.

The inner side edge of the driven sprocket 211 on the transition shaft 210 is sleeved with a spacer 240, the inner side of the spacer 240 is fixedly sleeved with a transition gear 250, and the two first driving shafts 220 are respectively and fixedly sleeved with two driven gears 221. The transition gear 250 meshes with both driven gears 221 simultaneously. When the transition gear 250 rotates, the two driven gears 221 are driven to rotate simultaneously to distribute power. The end parts of the two first driving shafts 220 are provided with first chain wheels 222, the end parts of the two second driving shafts 230 are provided with second chain wheels 231, the number of teeth of the first chain wheels 222 is equal to that of the second chain wheels 231, and the first chain wheels 222 and the second chain wheels 231 are meshed with each other through first roller chains 270 and second roller chains 280 respectively to transmit power.

With the power split mechanism 200 of the present embodiment, the number of required transmission gears is reduced, and the structure is simplified, so that the manufacturing cost of the product can be reduced.

It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.

Claims

1. A transmission device (100) comprises a shell (110), a driven shaft which is rotatably connected in the shell (110) and a plurality of driven gears (150) which are sleeved on the driven shaft (130); the clutch mechanism is characterized by further comprising a clutch sleeve (170) and a gear shifting mechanism (180), wherein the clutch sleeve (170) can axially slide relative to the driven shaft (130) and is non-rotatably sleeved on the periphery of the driven shaft (130), transmission grooves (171) are formed in two end faces of the clutch sleeve (170), a transmission piece (151) is arranged on the end face of the driven gear (150), the gear shifting mechanism (180) is connected with the clutch sleeve (170), the gear shifting mechanism (180) is used for driving the clutch sleeve (170) to axially move along the driven shaft (130), and the clutch sleeve (170) axially moves to the state that the transmission grooves (171) are connected with the driven gear (150) when being nested in the transmission piece (151).

2. The transmission device (100) according to claim 1, wherein the clutch sleeve (170) is provided at an outer peripheral surface thereof with a ring groove (174), the shift mechanism (180) includes a shift shaft (181) and a protrusion (182) at an end of the shift shaft (181), an axis of the shift shaft (181) is perpendicular to an axis of the driven shaft (130), the protrusion (182) is eccentrically disposed at one end of the shift shaft (181) with respect to an axial center of the shift shaft (181), and the protrusion (182) is inserted into the ring groove (174).

3. The transmission device (100) according to claim 2, wherein the other end of the shift shaft (181) is provided with a cam step (184) which has wave crests and wave troughs formed by changing the radial distance relative to the axial center of the shift shaft (181), the shift shaft (181) is sleeved with a shaft sleeve end cover (185), and the shaft sleeve end cover (185) is positioned on the periphery of the cam step (184); the shaft sleeve end cover (185) is provided with a through hole (186), a spring ball structure comprising a ball (189) and a spring (187) is arranged in the through hole (186), one end of the spring (187) is abutted against the shell (110), the other end of the spring (187) is abutted against the ball (189), and the ball (189) is abutted against the outer peripheral surface of the cam step (184); when the gear shifting is completed, the ball (189) abuts against the wave trough of the cam step (184).

4. The variator device (100) of claim 3, wherein the spring ball structures are two sets of spring ball structures that are symmetrical to either side of a central axis of the cam step (184).

5. The transmission device (100) according to claim 1, wherein a limiting block is arranged on the periphery of the driven shaft (130), a limiting groove is arranged in the inner hole of the clutch sleeve (170), and the limiting block is connected with the limiting groove in a sliding manner.

6. The transmission device (100) according to claim 5, wherein the limiting block is an external spline step (131) arranged on the outer periphery of the driven shaft (130), the limiting groove is a spline inner hole (172) arranged at the inner hole of the clutch sleeve (170), and the external spline step (131) is in sliding connection with the spline inner hole (172).

7. A transmission arrangement (100) according to claim 1, wherein the clutch sleeve (170) is provided with a plurality of equally spaced first bosses (173) at each end, the transmission grooves (171) are located between adjacent first bosses (173), and the transmission members (151) are second bosses equally spaced from the end face of the driven gear (150) facing the clutch sleeve (170).

8. The transmission arrangement (100) of claim 7, wherein the first boss (173) occupies a smaller span angle than a spacing between adjacent first bosses (173), and the second boss occupies a smaller span angle than a spacing between adjacent second bosses.

9. The transmission device according to any one of claims 1 to 8, further comprising a driving shaft (120) rotatably connected in the housing (110), wherein the driving shaft (120) and the driven shaft (130) are arranged in parallel, the driving shaft (120) is connected with a driving mechanism (140) for driving the driving shaft (120) to rotate, the driving shaft (120) is coaxially sleeved with a plurality of driving gears (160) fixed relative to the driving shaft (120), the driven gear (150) can be sleeved on the driven shaft (130) in a manner of rotating relative to the driven shaft (130) but limited in axial movement, and the driving gears (160) and the driven gears (150) are in one-to-one correspondence and the corresponding driving gears (160) and driven gears (150) are meshed.

10. The transmission arrangement (100) of claim 9, wherein the drive gear (160) comprises a first drive gear (161) and a second drive gear (162), and the driven gear (150) comprises a first driven gear (152) and a second driven gear (153), the first drive gear (161) and the first driven gear (152) being in mesh, the second drive gear (162) and the second driven gear (153) being in mesh, and the clutch sleeve (170) being located between the first driven gear (152) and the second driven gear (153).

11. The transmission arrangement (100) according to claim 9, wherein the drive mechanism (140) comprises a drive motor (141), a worm (142) and a worm wheel (143), the worm (142) is connected to an output of the drive motor (141), the worm (142) is engaged with the worm wheel (143), and the worm wheel (143) is coaxially and fixedly connected with the drive shaft (120).

12. Feeder, characterized by comprising a power splitting mechanism (200) and a transmission device (100) according to any one of claims 1 to 11, the input of the power splitting mechanism (200) being connected to the output of the driven shaft (130).

13. The feeder of claim 12, wherein the power distribution mechanism (200) includes a transition shaft (210) rotatably supported by the housing (110) and balanced to the driven shaft (130) via bearings, two first driving shafts (220) rotatably supported by the housing (110) and balanced to the transition shaft (210) via bearings, two second driving shafts (230) rotatably supported by the housing (110) and balanced to the first driving shafts (220) and supported by the housing (110) via bearings, a driving sprocket (136) is fixedly secured to a portion of the driven shaft (130) protruding from the housing (110), a driven sprocket (211) is fixedly secured to the transition shaft (210), the driving sprocket (136) is engaged with the driven sprocket (211) via a chain connection, a transition gear (250) is secured to an inner side edge of the driven sprocket (211) on the transition shaft (210), two driven gears (221) are fixedly sleeved on the two first driving shafts (220), and the transition gear (250) is meshed with the two driven gears (221) simultaneously; the end parts of the two first driving shafts (220) are provided with first chain wheels (222), the end parts of the two second driving shafts (230) are provided with second chain wheels (231), and the first chain wheels (222) and the second chain wheels (231) are respectively meshed with each other through first chains (270) and second chains (280) to transmit power.