阅读说明：本技术 一种可逆止和制动的双驱动液压径向柱塞式传动滚筒 (Dual-drive hydraulic radial plunger type transmission roller capable of reversing braking and braking ) 是由 陆兴华 于 2019-11-28 设计创作，主要内容包括：本发明公开了一种可逆止和制动的双驱动液压径向柱塞式传动滚筒,包括轴段上左右对称设有配油轴段的滚筒轴,滚筒轴上还设有制动机构和逆止结构,且筒体内对应配油轴段的位置设有包括空心活塞座盘、推杆、活塞的两套液压驱动滚筒驱动装置,利用高压油腔内的工作压力油通过活塞作用于推杆,而因偏心圆柱轴段的偏心设置造成的推杆的反作用力方向与活塞的移动方向之间存在夹角,进而使工作压力油通过活塞作用于推杆的作用力分解成两部分,一部分与推杆提供的反作用力抵消、另一部分对空心活塞座盘产生旋转力矩,两套滚筒驱动装置可以在保证足够的驱动力矩的前提下保证受力的均衡性,特别适用于高瓦斯矿井或者传动装置没有布置空间的带式输送机。(The invention discloses a double-drive hydraulic radial plunger type transmission roller capable of reversing braking and braking, which comprises roller shafts, wherein oil distribution shaft sections are symmetrically arranged on the left and right sides of a shaft section, a braking mechanism and a reverse stopping structure are also arranged on the roller shafts, two sets of hydraulic driving roller driving devices comprising a hollow piston seat disc, a push rod and a piston are arranged at positions corresponding to the oil distribution shaft sections in a roller body, working pressure oil in a high-pressure oil cavity acts on the push rod through the piston, an included angle exists between the direction of the reaction force of the push rod and the moving direction of the piston due to the eccentric arrangement of an eccentric cylindrical shaft section, so that the acting force of the working pressure oil acting on the push rod through the piston is decomposed into two parts, one part counteracts with the reaction force provided by the push rod, the other part generates rotating moment on the hollow piston seat disc, and the two sets of roller driving devices can ensure the balance of stress on the premise of ensuring enough driving, the belt conveyor is particularly suitable for high gas mines or belt conveyors with no space for arrangement of a transmission device.)

1. A double-drive hydraulic radial plunger type transmission roller capable of reversing braking and braking comprises a roller body (2), a spoke plate (4) and a roller shaft (10); the rubber layer (1) is coated on the outer surface of the cylinder body (2), the two radial plates (4) are fixedly arranged inside the cylinder body (2) in a bilateral symmetry mode, bearing seats (13) are fixedly arranged at the center positions of the two radial plates (4), bearings (5) are arranged in the bearing seats (13), the cylinder body (2) is erected and installed on a roller shaft (10) through the radial plates (4) and the bearing seats (13) in a rolling fit mode, and the left end and the right end of the roller shaft (10) are erected and installed on a rack of the belt conveyor through supporting seats (6) fixedly connected with the roller shaft; it is characterized in that the preparation method is characterized in that,

a brake mechanism is further arranged on a bearing seat (13) of at least one spoke plate (4), the brake mechanism sleeved on the drum shaft (10) is arranged at the outer side end of the bearing seat (13), the outer side end face of the bearing seat (13) is a friction brake end face, and the brake mechanism is sequentially provided with a sealing cylinder sleeve (35), a brake sleeve body (12), a disc spring group (11) and a disc spring pressing plate (32) from inside to outside along the axial direction of the drum shaft (10); the outer ring of the bearing (5) is axially positioned and installed in a bearing chamber of the bearing seat (13) through the hollow shaft pressure bearing cover (31), the sealing cylinder sleeve (35) is axially positioned and fixedly sleeved on the roller shaft (10) and penetrates through the hollow structure of the hollow shaft pressure bearing cover (31), the sealing cylinder sleeve (35) abuts against the end part of the inner ring of the bearing (5), and the sealing cylinder sleeve (35) is connected with the roller shaft (10) in a sealing and installing mode; the brake sleeve body (12) is arranged on the drum shaft (10) in a radial positioning sliding fit manner, the end surface of the outer edge of the inner side end of the brake sleeve body (12) is a friction brake surface matched with the end surface of the outer side of the bearing seat (13), the center position of the inner side end of the brake sleeve body (12) is provided with a brake piston structure which is arranged in a protruding manner towards the inner side direction, the outer diameter size of the brake piston structure is matched with the inner diameter size of the sealing cylinder sleeve (35), the brake piston structure is connected with the sealing cylinder sleeve (35) in a sealing manner, the whole brake sleeve body (12) is arranged in the sealing cylinder sleeve (35) in a sealing sliding fit manner by circumferential positioning of the brake piston structure, a brake liquid filling cavity is formed between the end surface of the inner side end of the brake piston structure and the end surface of the outer side end of the cylinder bottom of the sealing cylinder sleeve (35), the outer side end of the, a disc spring pressing plate (32) which is axially positioned and installed on the drum shaft (10) is abutted against the outer side end of the disc spring group (11), and the overall dimension of the disc spring pressing plate (32) is smaller than that of a disc spring installation space;

the brake device is characterized in that at least one set of brake mechanism is also provided with a non-return structure, a non-return sleeve extending outwards is arranged on the outer side end face of a bearing seat (13) provided with the non-return structure, the non-return structure comprises non-return grooves arranged on the outer circumferential face of a brake sleeve body (12) and non-return steel balls (37) arranged in the non-return grooves, the outer diameter size of the outer circumferential face of the brake sleeve body (12) is in clearance fit with the inner diameter size of the non-return sleeve, a plurality of non-return grooves uniformly distributed along the circumferential direction of the brake sleeve body (12) and the inner surface of the non-return sleeve form a non-return steel ball accommodating space with a nearly right-angled triangle-shaped longitudinal section, the left end and the right end of each non-return groove are arranged in a closed mode, the non-return grooves are located in the covering range of the non;

the roller shaft (10) is also symmetrically provided with two oil distribution shaft sections in a left-right mode on a shaft section between two radial plates (4), each oil distribution shaft section comprises an eccentric cylindrical shaft section (41) and an oil inlet flow distribution shaft section (42) which are arranged adjacently, the shaft axis of the eccentric cylindrical shaft section (41) and the shaft axis of the roller shaft (10) are arranged eccentrically, the shaft axis of the oil inlet flow distribution shaft section (42) and the shaft axis of the roller shaft (10) are arranged coaxially, an oil inlet flow distribution groove (16) is arranged on the outer cylindrical surface of the oil inlet flow distribution shaft section (42), the oil inlet flow distribution groove (16) is arranged in a 180-degree mode around the shaft axis of the oil inlet flow distribution shaft section (42), a connecting line between the eccentric shaft center of the eccentric cylindrical shaft section (41) and the shaft center of the roller shaft (10) is a vertical middle dividing line of the whole roller body (2), and the oil inlet flow distribution groove (16) is positioned on one side of the vertical middle dividing line of the whole roller;

the non-return and braking double-drive hydraulic radial plunger type transmission roller also comprises a roller drive device which is arranged in the cylinder body (2) and is arranged corresponding to the oil distribution shaft section, and the roller drive device comprises an oil outlet and flow distribution flange plate (30), a hollow piston seat plate (25), a push rod (26) and a piston (22);

the oil outlet flow distribution flange plate (30) and the drum shaft (10) are coaxially arranged, the oil outlet flow distribution flange plate (30) is adjacently arranged on the other side of the eccentric cylindrical shaft section (41) relative to the oil inlet flow distribution shaft section (42), the oil outlet flow distribution flange plate (30) is axially positioned and fixedly arranged on the drum shaft (10), an oil outlet flow distribution groove (29) is formed in the outer cylindrical surface of the oil outlet flow distribution flange plate (30), the oil outlet flow distribution groove (29) is arranged at an angle of minus 180 degrees around the axial lead of the oil inlet flow distribution shaft section (42), and the oil outlet flow distribution groove (29) is positioned on the other side of the vertical middle line of the whole drum body (2);

the hollow piston seat disc (25) is axially positioned and is sleeved and erected on the outer cylindrical surfaces of the oil outlet flow distribution flange disc (30) and the oil inlet flow distribution shaft section (42) in a circumferential sliding fit manner, the hollow piston seat disc (25) is connected with the outer cylindrical surfaces of the oil outlet flow distribution flange disc (30) and the oil inlet flow distribution shaft section (42) in a sealing manner, the outer circumferential surface of the hollow piston seat disc (25) is fixedly connected with the inner surface of the cylinder body (2) through a positioning transmission key (33), a plurality of piston cavities are arranged in the hollow piston seat disc (25) and correspond to the outer cylindrical surface of the eccentric cylindrical shaft section (41), the piston cavities are arranged along the radial direction of the hollow piston seat disc (25) and are uniformly distributed along the circumferential direction of the hollow piston seat disc (25), the top of each piston cavity is respectively provided with a branch oil outlet (18) and a branch oil outlet (24), and the branch oil outlets (18) are communicated with the oil inlet flow distribution groove (16) through oil inlet channels (17), the oil distribution outlet (24) is communicated and connected with the oil outlet flow distribution groove (29) through an oil distribution outlet channel (27);

a piston (22) matched with the inner diameter of the piston cavity in size is arranged in the piston cavity in a sliding fit manner;

the top end of the push rod (26) is hinged and installed on the bottom end face of the piston (22) through a hinge pin (23), the bottom end of the push rod (26) is of a sliding shoe structure comprising an arc-shaped bottom face, and the arc-shaped bottom face of the push rod (26) is matched with the outer cylindrical surface of the eccentric cylindrical shaft section (41) in a radian mode and attached to the outer cylindrical surface of the eccentric cylindrical shaft section (41);

the left shaft end face and the right shaft end face of the roller shaft (10) are respectively provided with a main oil inlet (8), a main oil inlet channel, a main oil outlet (9) and a main oil outlet channel which are arranged along the axial direction of the roller shaft (10), the main oil outlet channel positioned at the left end of the roller shaft (10) is communicated and connected with an oil outlet flow distribution groove (29) of the roller driving device positioned at the left side, and the main oil inlet channel positioned at the left end of the roller shaft (10) is communicated and connected with an oil inlet flow distribution groove (16) of the roller driving device positioned at the left side; the total oil outlet channel positioned at the right end of the roller shaft (10) is communicated and connected with the oil outlet flow distribution groove (29) of the roller driving device positioned at the right side, and the total oil inlet channel positioned at the right end of the roller shaft (10) is communicated and connected with the oil inlet flow distribution groove (16) of the roller driving device positioned at the right side; the position of the drum shaft (10) corresponding to the brake liquid filling cavity is also provided with a brake oil filling hole channel (36) penetrating into the drum shaft (10) along the radial direction, and the brake oil filling hole channel (36) is communicated and connected with the total oil inlet channel or the total oil outlet channel.

2. The backreturnable and brakable dual drive hydraulic radial plunger drive drum of claim 1, wherein the number of piston cavities in the hollow piston seat disc (25) is an odd number of more than three.

3. The backstopping and braking dual drive hydraulic radial plunger type transmission roller as recited in claim 1, characterized in that a guide groove and a guide key (44) are arranged between the piston (24) and the inner wall of the piston cavity in a matching way, and the guide groove and the guide key (44) are arranged along the axial direction of the piston cavity.

4. The double-drive hydraulic radial plunger type transmission roller capable of realizing backstopping and braking as claimed in claim 1, 2 or 3, characterized in that the piston cavity of the hollow piston seat disk (25) is a through hole structure penetrating through the hollow piston seat disk (25), and the top end of the piston cavity is provided with a piston sealing cover (21) which is fixedly installed in a sealing way.

5. The double-drive hydraulic radial plunger type transmission roller capable of realizing backstopping and braking as claimed in claim 1, 2 or 3, characterized in that when the piston (24) is located at the upper limit position of the stroke, the piston (24) is in a state of plugging the oil dividing inlet (18) and the oil dividing outlet (24).

6. The backstop and brake dual-drive hydraulic radial plunger type transmission roller according to claim 1, 2 or 3, characterized in that the disc spring pressing plate (32) is sleeved on the roller shaft (10) in a sliding fit manner, and the disc spring pressing plate (32) is axially positioned and installed through a disc spring pressing plate locking nut (34) which is positioned at the outer end of the disc spring pressing plate and is installed on the roller shaft (10) in a screwing manner through threads.

7. Double-drive hydraulic radial plunger type driving roller capable of realizing backstopping and braking according to claim 1, 2 or 3, characterized in that the oil-dividing channel (17) and the oil-dividing channel (27) are channel structures arranged inside the hollow piston seat disc (25).

8. The double-drive hydraulic radial plunger type transmission roller capable of realizing backstopping and braking according to claim 1, 2 or 3, characterized in that a hollowed-out weight-reduction process hole is arranged between the piston cavities of two adjacent hollow piston seat discs (25).

9. Double-drive hydraulic radial plunger type drive drum with backstop and brake according to claim 1 or 2 or 3, characterized in that the positioning drive key (33) is a sliding key structure with sliding clearance along the axial direction of the drum (2).

Technical Field

The invention relates to a transmission roller for a belt conveyor, in particular to a double-drive hydraulic radial plunger type transmission roller which is suitable for belt conveyors in places such as mine underground, ground, port wharfs and the like and can be used for backstopping and braking, and belongs to the technical field of belt conveyors.

Background

The belt conveyor is also called as a rubber belt conveyor and is widely applied to various industries such as machinery, electronics, tobacco, injection molding, post and telecommunications, printing, food and the like. The belt conveyor can be classified into a heavy belt conveyor such as a mining belt conveyor and a light belt conveyor such as those used in the industries of electronic plastics, food light industry, chemical engineering, medicine and the like according to the conveying capacity of the belt conveyor. The belt conveyer is a friction-driven machine for continuously conveying material, mainly comprising machine frame, conveyer belt, supporting roller, drum, tension device and driving device, etc. it can form a material conveying process from initial feeding point to final discharging point, and can be used for conveying broken material and finished articles, besides pure material conveying, it also can be matched with technological process requirements in production processes of various industrial enterprises to form rhythmic line production conveying line.

The traction force of the belt conveyor is transmitted by the friction force between the transmission roller and the conveying belt, so that the rubber belt must be tensioned by a tensioning device to ensure that the rubber belt has a certain initial tension at the separation position of the transmission roller. The transmission device of the traditional belt conveyor usually adopts a mode that a motor drives a transmission roller through a speed reducer, and in order to reduce the weight and the load of the transmission device, the traditional transmission roller is usually manufactured into a hollow cylindrical structure on the premise of ensuring the strength. The traditional belt conveyor transmission device needs to be installed at the side position of a transmission roller, and aiming at a heavy belt conveyor such as a mining belt conveyor, a driving motor and a speed reducer with huge volume not only need to additionally occupy installation space, but also need to additionally dig out the installation and maintenance space of the transmission device aiming at a coal mine underground coal conveying roadway with narrow space, and the coaxial installation and the complex installation and debugging of an output shaft of the speed reducer and the transmission roller need to be ensured in the installation process; in addition, due to the explosion-proof particularity of the underground operation of the coal mine, particularly for high-gas mines, the driving motors used by the traditional belt conveyor transmission device for the mine need to adopt explosion-proof motors, so that the production cost is increased, and the maintenance cost of supporting facilities is increased (the use of the high-power explosion-proof motor requires to improve the voltage grade).

Disclosure of Invention

Aiming at the problems, the invention provides a double-drive hydraulic radial plunger type transmission roller capable of realizing non-return and braking, which adopts a hydraulic driving mode, does not need to be provided with extra transmission device installation space, is convenient to install and maintain, can reduce the production cost and the maintenance cost of supporting facilities, and is particularly suitable for high gas mines or belt conveyors with transmission devices without arrangement space.

In order to achieve the purpose, the double-drive hydraulic radial plunger type transmission roller capable of reversing braking and braking comprises a cylinder body, a spoke plate and a roller shaft; the outer surface of the cylinder body is coated with a rubber layer, the two radial plates are fixedly arranged in the cylinder body in a bilateral symmetry manner, the center positions of the two radial plates are fixedly provided with bearing seats, bearings are arranged in the bearing seats, the cylinder body is erected and installed on a cylinder shaft through the radial plates and the bearing seats in a rolling fit manner, and the left end and the right end of the cylinder shaft are respectively erected and installed on a rack of the belt conveyor through supporting seats fixedly connected with the cylinder body;

the bearing seat of at least one radial plate is also provided with a brake mechanism, the brake mechanism sleeved on the drum shaft is arranged at the outer side end of the bearing seat, the outer side end surface of the bearing seat is a friction brake end surface, and the brake mechanism is sequentially provided with a sealing cylinder sleeve, a brake sleeve body, a disc spring group and a disc spring pressing plate from inside to outside along the axial direction of the drum shaft; the outer ring of the bearing is axially positioned and installed in a bearing chamber of the bearing seat through the hollow shaft bearing cover, the sealing cylinder sleeve is axially positioned and fixedly sleeved on the roller shaft and is connected in the hollow structure of the hollow shaft bearing cover in a penetrating manner, the sealing cylinder sleeve abuts against the end part of the inner ring of the bearing, and the sealing cylinder sleeve is connected with the roller shaft in a sealing and installing manner; the brake sleeve body is arranged on the roller shaft in a radial positioning sliding fit manner, the end surface of the outer edge of the inner side end of the brake sleeve body is a friction brake surface matched with the end surface of the outer side of the bearing seat, the center position of the inner side end of the brake sleeve body is provided with a brake piston structure which is arranged in a protruding manner towards the inner side direction, the outer diameter size of the brake piston structure is matched with the inner diameter size of the sealing cylinder sleeve, the brake piston structure is connected with the sealing cylinder sleeve in a sealing manner, the whole brake sleeve body is arranged in the sealing cylinder sleeve in a circumferential positioning and sealing sliding fit manner through the brake piston structure, a brake liquid filling cavity is formed between the end surface of the inner side end of the brake piston structure and the end surface of the outer side of the cylinder bottom of the sealing cylinder sleeve, the outer side end of the brake sleeve body is provided with a disc spring installation space, the overall dimension of the disc spring pressing plate is smaller than that of the disc spring mounting space;

the at least one set of brake mechanism is also provided with a non-return structure, a non-return sleeve extending outwards is arranged on the outer side end face of the bearing seat provided with the non-return structure, the non-return structure comprises a non-return groove arranged on the outer circumferential face of the brake sleeve body and a non-return steel ball arranged in the non-return groove, the outer diameter size of the outer circumferential face of the brake sleeve body is in clearance fit with the inner diameter size of the non-return sleeve, a plurality of non-return grooves uniformly distributed along the circumferential direction of the brake sleeve body and the inner surface of the non-return sleeve form a non-return steel ball accommodating space with a nearly right-angled triangle-shaped longitudinal section, the left end and the right end of each non-return groove are arranged in a closed mode, the non-return grooves are located in the covering range of the non-return;

the roller shaft is also provided with two oil distribution shaft sections in bilateral symmetry on a shaft section between two radial plates, each oil distribution shaft section comprises an eccentric cylindrical shaft section and an oil inlet flow distribution shaft section which are arranged adjacently, the shaft axis of the eccentric cylindrical shaft section and the shaft axis of the roller shaft are arranged eccentrically, the shaft axis of the oil inlet flow distribution shaft section and the shaft axis of the roller shaft are arranged coaxially, an oil inlet flow distribution groove is arranged on the outer cylindrical surface of the oil inlet flow distribution shaft section, the oil inlet flow distribution groove is arranged in a 180-degree manner around the shaft axis of the oil inlet flow distribution shaft section, the connecting line between the eccentric shaft center of the eccentric cylindrical shaft section and the shaft center of the roller shaft is the vertical middle dividing line of the whole roller body, and the oil inlet flow distribution groove is positioned on one side of the vertical middle dividing line of the whole;

the double-drive hydraulic radial plunger type transmission roller capable of realizing non-return and braking further comprises a roller drive device which is arranged in the roller body and corresponds to the oil distribution shaft section, and the roller drive device comprises an oil outlet and flow distribution flange plate, a hollow piston seat plate, a push rod and a piston;

the oil outlet flow distribution flange plate is coaxially arranged with the drum shaft, the oil outlet flow distribution flange plate is adjacently arranged at the other side of the eccentric cylindrical shaft section relative to the oil inlet flow distribution shaft section, the oil outlet flow distribution flange plate is axially positioned and fixedly arranged on the drum shaft, an oil outlet flow distribution groove is arranged on the outer cylindrical surface of the oil outlet flow distribution flange plate, the oil outlet flow distribution groove is arranged in a-180-degree manner around the axial lead of the oil inlet flow distribution shaft section, and the oil outlet flow distribution groove is positioned at the other side of the vertical middle branching line of the whole drum body;

the hollow piston seat disc is axially positioned and is circumferentially and slidably matched, sleeved and erected on the outer cylindrical surfaces of the oil outlet flow distribution flange disc and the oil inlet flow distribution shaft section, the hollow piston seat disc is connected with the oil outlet flow distribution flange disc and the outer cylindrical surface of the oil inlet flow distribution shaft section in a sealing and installing mode, the outer circumferential surface of the hollow piston seat disc is fixedly connected with the inner surface of the cylinder body through a positioning transmission key, a plurality of piston cavities are arranged in the hollow piston seat disc and correspond to the outer cylindrical surface of the eccentric cylindrical shaft section, the piston cavities are arranged along the radial direction of the hollow piston seat disc and are uniformly distributed along the circumferential direction of the hollow piston seat disc, the top of each piston cavity is respectively provided with an oil separating port and an oil outlet port, the oil separating ports are communicated and connected with the oil inlet flow distribution groove through oil separating channels, and the oil outlet ports are communicated and connected with the oil distribution groove through oil separating channels;

the piston matched with the inner diameter of the piston cavity in size is arranged in the piston cavity in a sliding fit manner;

the top end of the push rod is hinged and installed on the bottom end face of the piston through a hinge pin, the bottom end of the push rod is of a sliding shoe structure comprising an arc-shaped bottom face, and the arc-shaped bottom face of the push rod is matched with the radian of the outer cylindrical surface of the eccentric cylindrical shaft section and is attached to the outer cylindrical surface of the eccentric cylindrical shaft section;

the left shaft end face and the right shaft end face of the roller shaft are respectively provided with a main oil inlet, a main oil inlet channel, a main oil outlet and a main oil outlet channel which are arranged along the axial direction of the roller shaft, the main oil outlet channel positioned at the left end of the roller shaft is communicated and connected with the oil outlet flow distribution groove of the roller driving device positioned at the left side, and the main oil inlet channel positioned at the left end of the roller shaft is communicated and connected with the oil inlet flow distribution groove of the roller driving device positioned at the left side; the total oil outlet channel positioned at the right end of the roller shaft is communicated and connected with the oil outlet flow distribution groove of the roller driving device positioned on the right side, and the total oil inlet channel positioned at the right end of the roller shaft is communicated and connected with the oil inlet flow distribution groove of the roller driving device positioned on the right side.

As a further improvement of the invention, the number of the piston cavities in the hollow piston seat disc is an odd number of more than three.

As a further improvement scheme of the invention, a guide groove and a guide key which are arranged in a matched manner are arranged between the piston and the inner wall of the piston cavity, and the guide groove and the guide key are arranged along the axial direction of the piston cavity.

As a further improvement scheme of the invention, the piston cavity of the hollow piston seat disc is a through hole structure penetrating through the hollow piston seat disc, and the top end of the piston cavity is provided with a piston sealing cover which is fixedly installed in a sealing way.

As a further improvement scheme of the invention, when the piston is positioned at the upper limit position of the stroke, the piston is in a state of plugging the oil dividing inlet and the oil dividing outlet.

As a further improvement scheme of the invention, the disc spring pressing plate is sleeved on the drum shaft in a sliding fit manner, and the disc spring pressing plate is axially positioned and installed through a disc spring pressing plate locking nut which is positioned at the outer end of the disc spring pressing plate and is installed on the drum shaft in a screwed manner through threads.

As a preferable scheme of the invention, the oil inlet channel and the oil outlet channel are channel structures arranged inside the hollow piston seat disc.

As a further improvement scheme of the invention, a hollowed-out weight-reducing fabrication hole is arranged between the piston cavities of two adjacent hollow piston seat discs.

As a further improvement of the invention, the positioning transmission key is a sliding key structure with a sliding gap along the axial direction of the cylinder body.

Compared with the prior art, the double-drive hydraulic radial plunger type transmission roller capable of realizing non-return and braking is characterized in that two oil distribution shaft sections comprising an eccentric cylindrical shaft section and an oil inlet flow distribution shaft section which are adjacently arranged are arranged on the shaft section of the roller shaft between two radial plates in a bilateral symmetry manner, a hydraulic driving roller driving device comprising a hollow piston seat disc, a push rod and a piston is arranged at the position fixedly corresponding to the eccentric cylindrical shaft section in the roller body, working pressure oil in a high-pressure oil cavity acts on the push rod through the piston, an included angle exists between the direction of a reaction force of the push rod and the moving direction of the piston due to the eccentric arrangement of the eccentric cylindrical shaft section, and further the working pressure oil is decomposed into two parts through the action force of the piston acting on the push rod, one part is offset with the reaction force provided by the push rod, the other part generates a rotating moment on the hollow piston seat disc, and the hollow piston seat disc acts on the roller body, the cylinder is driven to rotate, a hollow piston seat disc, a radial plate, a bearing seat, an outer ring of a bearing and a hollow shaft bearing cover rotate along with the cylinder in the rotation process, and a drum shaft, an oil outlet flow distribution flange plate positioning sleeve, an oil outlet flow distribution flange plate, a hollow piston seat disc positioning sleeve, an inner ring of the bearing, a sealing cylinder sleeve and a brake sleeve body are in a static state; the two sets of roller driving devices are bilaterally symmetrical and synchronously arranged, so that the driving torque of the roller body can be improved, and the roller body can be stressed more uniformly when driven to roll; the bearing seat is also provided with a braking mechanism controlled by hydraulic pressure, so that the barrel can be in a braking state under the condition that the hydraulic pump station is stopped, and can be in a rotatable working state under the condition that the hydraulic pump station is started; because at least one set of brake mechanism is also provided with a non-return structure, the cylinder body can be prevented from reversing due to the fact that the cylinder body overcomes the brake force of the brake mechanism and is caused by a large external force after the cylinder body stops rotating; the roller driving device arranged in the barrel can fully utilize the inner space of the barrel on one hand, and adopts a mode of axially feeding and discharging working pressure oil from the roller shaft on the other hand, so that an additional transmission device installation space is not needed, and the installation and maintenance are convenient.

Drawings

FIG. 1 is a schematic structural view of the present invention;

FIG. 2 is a cross-sectional view A-A of FIG. 1;

FIG. 3 is a cross-sectional view B-B of FIG. 1;

FIG. 4 is a cross-sectional view C-C of FIG. 1;

FIG. 5 is a cross-sectional view D-D of FIG. 1;

FIG. 6 is a cross-sectional view E-E of FIG. 2;

FIG. 7 is a view from direction F of FIG. 1;

FIG. 8 is a force-bearing schematic diagram of the push rod of the present invention providing a reaction force in the radial direction of the axis of the eccentric cylindrical shaft segment through the outer cylindrical surface of the eccentric cylindrical shaft segment;

fig. 9 is a sectional view G-G of fig. 1.

In the figure: 1. a rubber layer; 2. a barrel; 3. a spoke plate mounting bolt; 4. a web; 5. a bearing; 6. a supporting seat; 7. a roller shaft positioning key; 8. a main oil inlet; 9. a total oil outlet; 10. a drum shaft; 11. a disc spring set; 12. a brake sleeve body; 13. a bearing seat; 14. a hollow piston seat disc positioning spacer bush; 15. sealing an oil inlet flow distribution shaft section; 16. an oil inlet flow distribution groove; 17. an oil separating channel; 18. an oil inlet; 19. the piston sealing cover is used for sealing; 20. a bolt is arranged on the piston sealing cover; 21. a piston seal cover; 22. a piston; 23. a hinge pin; 24. an oil outlet; 25. a hollow piston seat disc; 26. a push rod; 27. an oil outlet channel; 28. sealing an oil outlet flow distribution flange plate; 29. an oil outlet flow distribution groove; 30. an oil outlet flow distribution flange plate; 31. a hollow shaft bearing cover; 32. a disc spring pressing plate; 33. positioning a transmission key; 34. a disc spring pressing plate locking nut; 35. sealing the cylinder sleeve; 36. a brake oil injection pore channel; 37. a steel ball is inverted; 39. mounting keys of the oil outlet flow distribution flange; 41. an eccentric cylindrical shaft section; 42. an oil inlet flow distribution shaft section; 43. a low pressure oil chamber; 44. a guide key; 45. and a high-pressure oil chamber.

Detailed Description

The present invention will be further explained with reference to the drawings (hereinafter, the left-right direction of fig. 1 is taken as the left-right direction, the direction pointing to the inside of the drum 2 along the axial direction of the drum shaft 10 is taken as the inside direction, and the direction pointing to the outside of the drum 2 along the axial direction of the drum shaft 10 is taken as the outside direction).

As shown in fig. 1 and fig. 2, the double-drive hydraulic radial plunger type transmission roller capable of reverse stopping and braking comprises a cylinder body 2, a radial plate 4 and a roller shaft 10; the outer surface of the cylinder body 2 is coated with a rubber layer 1, two radial plates 4 are fixedly arranged in the cylinder body 2 in a bilateral symmetry manner, the radial plates 4 are fixedly arranged in the cylinder body 2 through radial plate mounting bolts 3, the center positions of the two radial plates 4 are respectively and fixedly provided with a bearing seat 13, a bearing 5 is arranged in the bearing seat 13, the cylinder body 2 is arranged on a roller shaft 10 in an erected manner through rolling matching of the radial plates 4 and the bearing seats 13, the left end and the right end of the roller shaft 10 are respectively arranged on a rack of a belt conveyor in an erected manner through a supporting seat 6 fixedly connected with the roller shaft 10, and as shown in fig. 7, the roller shaft 10 is fixedly connected with the;

as shown in fig. 1 and 3, a brake mechanism is further disposed on the bearing seat 13 of at least one of the radial plates 4, the brake mechanism sleeved on the drum shaft 10 is disposed at an outer end of the bearing seat 13, an outer end face of the bearing seat 13 is a friction brake end face, and the brake mechanism is sequentially provided with a sealing cylinder sleeve 35, a brake sleeve body 12, a disc spring group 11 and a disc spring pressing plate 32 from inside to outside along an axial direction of the drum shaft 10; the outer ring of the bearing 5 is axially positioned and installed in a bearing chamber of the bearing seat 13 through the hollow bearing cover 31, the sealing cylinder sleeve 35 is axially positioned and fixedly sleeved on the roller shaft 10 and is connected in the hollow structure of the hollow bearing cover 31 in a penetrating manner, the sealing cylinder sleeve 35 abuts against the end part of the inner ring of the bearing 5, and the sealing cylinder sleeve 35 is connected with the roller shaft 10 in a sealing and installing manner; the brake sleeve body 12 is arranged on the drum shaft 10 in a radial positioning sliding fit manner, the outer edge end face of the inner side end of the brake sleeve body 12 is a friction brake face matched with the outer end face of the bearing seat 13, a brake piston structure which is arranged in a protruding manner towards the inner side direction is arranged at the center position of the inner side end of the brake sleeve body 12, the outer diameter size of the brake piston structure is matched with the inner diameter size of the sealing cylinder sleeve 35, the brake piston structure is connected with the sealing cylinder sleeve 35 in a sealing manner, the whole brake sleeve body 12 is arranged in the sealing cylinder sleeve 35 in a circumferential positioning and sealing sliding fit manner through the brake piston structure, a brake liquid filling cavity is formed between the inner end face of the brake piston structure and the outer end face of the cylinder bottom of the sealing cylinder sleeve 35, a disc spring installation space is arranged at the outer end of the brake sleeve body 12, the disc spring group 11 is arranged in a propping manner in the disc spring installation, And the overall dimension of the disc spring pressing plate 32 is smaller than that of the disc spring installation space;

at least one set of brake mechanism is also provided with a non-return structure, a non-return sleeve extending outwards is arranged on the outer side end face of the bearing seat 13 provided with the non-return structure, the non-return structure comprises a non-return groove arranged on the outer circumferential face of the brake sleeve body 12 and a non-return steel ball 37 arranged in the non-return groove, as shown in fig. 9, the outer diameter size of the outer circumferential face of the brake sleeve body 12 is in clearance fit with the inner diameter size of the non-return sleeve, a plurality of non-return grooves uniformly distributed along the circumferential direction of the brake sleeve body 12 and the inner surface of the non-return sleeve form a non-return steel ball accommodating space with a nearly right-angled triangle-shaped longitudinal section, the left end and the right end of each non-return groove are arranged in a closed mode, the non-return grooves are located in the covering range of the non-return;

the drum shaft 10 is provided with two oil distribution shaft sections which are bilaterally symmetrical on a shaft section between two radial plates 4, each oil distribution shaft section comprises an eccentric cylindrical shaft section 41 and an oil inlet flow distribution shaft section 42 which are adjacently arranged, the shaft axis of the eccentric cylindrical shaft section 41 and the shaft axis of the drum shaft 10 are eccentrically arranged, the shaft axis of the oil inlet flow distribution shaft section 42 and the shaft axis of the drum shaft 10 are coaxially arranged, an oil inlet flow distribution groove 16 is arranged on the outer cylindrical surface of the oil inlet flow distribution shaft section 42, as shown in fig. 5, the oil inlet flow distribution groove 16 is arranged in a 180-degree direction around the shaft axis of the oil inlet flow distribution shaft section 42, namely the oil inlet flow distribution groove 16 is integrally in a semicircular groove structure, a connecting line between the eccentric shaft center of the eccentric cylindrical shaft section 41 and the shaft center of the drum shaft 10 is a vertical middle dividing line of the whole drum body 2, and the oil inlet flow distribution groove 16 is positioned on one side of the vertical.

The non-return and braking double-drive hydraulic radial plunger type transmission roller also comprises a roller drive device which is arranged in the cylinder body 2 and is arranged corresponding to the oil distribution shaft section, wherein the roller drive device comprises an oil outlet and flow distribution flange plate 30, a hollow piston seat plate 25, a push rod 26 and a piston 22;

the oil outlet flow distribution flange 30 is coaxially arranged with the drum shaft 10, the oil outlet flow distribution flange 30 is adjacently arranged at the other side of the eccentric cylindrical shaft section 41 relative to the oil inlet flow distribution shaft section 42, the oil outlet flow distribution flange 30 is axially fixedly arranged on the drum shaft 10 through a positioning step on the drum shaft 10 and an oil outlet flow distribution flange mounting key 39, the outer cylindrical surface of the oil outlet flow distribution flange 30 is provided with an oil outlet flow distribution groove 29, as shown in fig. 4, the oil outlet flow distribution groove 29 is arranged at-180 degrees around the axial lead of the oil inlet flow distribution shaft section 42, namely, the oil outlet flow distribution groove 29 is arranged corresponding to the reverse walking direction of the oil inlet flow distribution groove 16, and the oil outlet flow distribution groove 29 is positioned at the other side of the vertical middle branching of the whole drum body 2, namely, the oil inlet flow distribution groove 16 and the oil outlet flow distribution groove 29 are symmetrically arranged relative to the vertical middle branching space of the whole drum body 2;

the hollow piston seat disk 25 is axially positioned by a positioning step on the oil outlet flow distribution flange disk 30 or the oil inlet flow distribution shaft section 42 and a hollow piston seat disk positioning spacer 14 which is propped against the inner ring of the bearing 5, and is circumferentially sleeved and installed on the outer cylindrical surfaces of the oil outlet flow distribution flange disk 30 and the oil inlet flow distribution shaft section 42 in a sliding fit manner, the hollow piston seat disk 25, the oil outlet flow distribution flange disk 30 and the outer cylindrical surface of the oil inlet flow distribution shaft section 42 are connected in a sealing manner by an oil outlet flow distribution flange disk seal 28 and an oil inlet flow distribution shaft section seal 15, the positioning step is processed and manufactured, the oil outlet flow distribution flange disk 30 can be a split structure which comprises a positioning ring and an oil outlet flow distribution flange support which are coaxially positioned, the outer circumferential surface of the hollow piston seat disk 25 is fixedly connected with the inner surface of the cylinder body 2 by a positioning transmission key 33, a plurality of piston cavities are arranged in the hollow piston seat disk 25 at positions corresponding to the outer cylindrical surface, the piston cavities are arranged along the radial direction of the hollow piston seat disc 25, the piston cavities are uniformly distributed along the circumferential direction of the hollow piston seat disc 25, the top of each piston cavity is respectively provided with an oil separating port 18 and an oil separating outlet 24, the oil separating ports 18 are communicated and connected with the oil inlet flow distribution groove 16 through oil separating channels 17, and the oil separating outlets 24 are communicated and connected with the oil outlet flow distribution groove 29 through oil separating channels 27;

the piston 22 matched with the inner diameter of the piston cavity in size is arranged in the piston cavity in a sliding fit mode, and a piston seal is arranged between the piston 22 and the inner wall of the piston cavity;

the top end of the push rod 26 is hinged to the bottom end face of the piston 22 through a hinge pin 23, the bottom end of the push rod 26 is a sliding shoe structure including an arc bottom face, the arc bottom face of the push rod 26 is matched with the outer cylindrical surface of the eccentric cylindrical shaft section 41 in a radian mode and is attached to the outer cylindrical surface of the eccentric cylindrical shaft section 41, and as shown in fig. 2, the direction of interaction force between the push rod 26 and the outer cylindrical surface of the eccentric cylindrical shaft section 41 is along the connecting line direction of the central axis of the eccentric cylindrical shaft section 41 and the central axis of the hinge pin 23.

The left shaft end face and the right shaft end face of the roller shaft 10 are respectively provided with a main oil inlet 8, a main oil inlet channel, a main oil outlet 9 and a main oil outlet channel which are arranged along the axial direction of the roller shaft 10, the main oil outlet channel positioned at the left end of the roller shaft 10 is communicated and connected with an oil outlet flow distribution groove 29 of the roller driving device positioned at the left side, and the main oil inlet channel positioned at the left end of the roller shaft 10 is communicated and connected with an oil inlet flow distribution groove 16 of the roller driving device positioned at the left side; the total oil outlet channel at the right end of the roller shaft 10 is communicated and connected with the oil outlet flow distribution groove 29 of the roller driving device at the right side, and the total oil inlet channel at the right end of the roller shaft 10 is communicated and connected with the oil inlet flow distribution groove 16 of the roller driving device at the right side; a braking oil filling hole channel 36 penetrating into the drum shaft 10 along the radial direction is further arranged on the drum shaft 10 at a position corresponding to the braking liquid filling cavity, and the braking oil filling hole channel 36 is communicated and connected with the main oil inlet channel or the main oil outlet channel.

When the double-drive hydraulic radial plunger type transmission roller capable of reverse stopping and braking is installed on a belt conveyor to be used, a main oil inlet 8 and a main oil outlet 9 on the end faces of a left shaft and a right shaft of a roller shaft 10 are respectively connected with a hydraulic pump station through hydraulic pipelines, namely, a roller driving device on the left side and a roller driving device on the right side are both connected with the hydraulic pump station and can simultaneously provide rotating power of a barrel body 2.

The braking principle is as follows: when a hydraulic pump station stops and a single-drive hydraulic radial plunger type transmission roller with brake stops working, working hydraulic oil in a brake oil filling hole channel 36 communicated and connected with a total oil inlet channel or a total oil outlet channel does not have working pressure, at the moment, a disc spring group 11 overcomes the pressure of the working hydraulic oil in a brake liquid filling cavity under the positioning prevention action of a disc spring pressing plate 32 to release reset elastic force towards the inner side direction, the working hydraulic oil in the brake liquid filling cavity is pushed into the brake oil filling hole channel 36 to flow back to a hydraulic oil tank, the brake sleeve body 12 is pushed to slide towards the inner side direction in the process that the disc spring group 11 releases the reset elastic force, the outer edge end face of the inner side end of the brake sleeve body 12 is attached to the outer end face of the bearing seat 13 to generate friction force and is in a brake state of tightly holding the bearing; when the hydraulic pump station is started and the single-drive hydraulic radial plunger type transmission roller with the brake starts to work, working hydraulic oil in a brake oil filling hole channel 36 communicated and connected with a total oil inlet channel or a total oil outlet channel has working pressure, the working hydraulic oil in the brake oil filling hole channel 36 enters a brake liquid filling cavity to push a brake piston structure of the brake sleeve body 12 to overcome the elastic force of the disc spring group 11 to enable the brake sleeve body 12 to slide towards the outer side direction, the outer edge end face of the inner side end of the brake sleeve body 12 is separated from the outer end face of the bearing seat 13 and is in a yielding state of loosening the bearing seat 13, and the barrel body 2 is in a rotatable working state.

The rotary working principle of the cylinder body 2 is as follows: taking the drum driving device on the left side as an example, the working pressure oil enters the oil inlet flow distribution groove 16 from the main oil inlet 8 through the main oil inlet channel shown in fig. 3, then is divided and enters each piston cavity through each oil distribution channel 17, as shown in fig. 2, the connecting line between the eccentric shaft center of the eccentric cylindrical shaft section 41 and the shaft center of the drum shaft 10 is the vertical middle branch line of the whole drum body 2, due to the flow distribution function of the oil inlet flow distribution shaft section 42 on the oil inlet flow distribution shaft section 42, the upper cavities of all the pistons 22 located behind the vertical middle branch line of the drum body 2 (i.e. all the pistons 22 on the right side of the vertical middle branch line in fig. 2) are all communicated with the high-pressure hydraulic medium to form a high-pressure oil cavity 45, and due to the flow distribution function of the oil outlet flow distribution groove 29 on the oil outlet flow distribution flange 30, the upper cavities of all the pistons 22 located in front of the vertical middle branch line of the drum body 2 (i.e. all the pistons, The oil distributing channel 27 is communicated with the main oil outlet 9 through the oil outlet distributing groove 29 and the main oil outlet channel to form a low-pressure oil chamber 43, hydraulic oil in the low-pressure oil chamber 43 flows back to a hydraulic oil tank of a hydraulic pump station under the extrusion of the piston 22, the direction of the acting force of the piston 22 in each high-pressure oil chamber 45 acting on the push rod 26 passes through the axis of the drum shaft 10, the push rod 26 provides a reaction force along the radial direction of the axis of the eccentric cylindrical shaft section 41 through the outer cylindrical surface of the eccentric cylindrical shaft section 41, namely F1, F2 and F3 shown in figure 8, due to the eccentric arrangement of the eccentric cylindrical shaft section 41, the acting force of the working pressure oil acting on the push rod 26 through the piston 22 is decomposed into two parts, one part is counteracted with the reaction force provided by the push rod 26, the other part generates a rotating moment on the hollow piston seat disc 25, the hollow piston seat disc 25 acts on the cylinder 2 through, rotation of the drum 2 in a clockwise direction as shown by the arrow in figure 2 is achieved. The hollow piston seat disc 25, the radial plate 4, the bearing seat 13, the outer ring of the bearing 5 and the hollow bearing pressure bearing cover 31 rotate along with the cylinder 2 in the rotating process; the roller shaft 10, the oil outlet flow distribution flange plate positioning sleeve 13, the oil outlet flow distribution flange plate 30, the hollow piston seat plate positioning sleeve 21, the inner ring of the bearing 5, the sealing cylinder sleeve 35 and the brake sleeve body 12 are in a static state; each piston cavity crosses the vertical middle line of the whole cylinder body 2 at the eccentric big end position of the eccentric cylindrical shaft section 41 to become a high-pressure oil cavity 45, each piston cavity crosses the vertical middle line of the whole cylinder body 2 at the eccentric small end position of the eccentric cylindrical shaft section 41 to become a low-pressure oil cavity 43, and the working hydraulic oil circularly flows to realize the continuous rotation of the roller 2.

The non-return principle is as follows: in the rotation process of the cylinder body 2, the bearing seat 13 rotates clockwise as shown in fig. 9, the check steel ball 37 is always positioned in the large space section of the check steel ball accommodating space in the shape of a nearly right-angled triangle, and the rotation of the bearing seat 13 is not influenced; after the rotation of the cylinder 2 is stopped, if the cylinder 2 is reversed by overcoming the braking force of the braking mechanism due to a large external force, the bearing seat 13 is reversed, at this time, the bearing seat 13 rotates counterclockwise as shown in fig. 9, the inner surface of the non-return sleeve of the bearing seat 13 rubs the non-return steel ball 37 to move towards the small space section of the non-return steel ball accommodating space in the shape of a nearly right-angled triangle until the non-return steel ball 37 and the inner surface of the non-return sleeve of the bearing seat 13 are stuck, the bearing seat 13 stops reversing, and the reverse rotation of the cylinder 2 is prevented.

In order to ensure the working efficiency of the piston cavities, as a further improvement of the invention, the number of the piston cavities in the hollow piston seat disc 25 is an odd number of more than three. The connecting line between the eccentric shaft center of the eccentric cylindrical shaft section 41 and the shaft center of the drum shaft 10 is the vertical middle dividing line of the whole drum body 2, when the piston cavity passes through the vertical middle dividing line of the whole drum body 2, the direction of the interaction force between the push rod 26 and the outer cylindrical surface of the eccentric cylindrical shaft section 41 is in a collinear state with the vertical middle dividing line of the whole drum body 2, at this time, because no eccentricity exists, pressure oil cannot provide the rotation moment of the hollow piston seat disc 25, if even number of piston cavities are adopted, the vertical middle dividing line that two piston cavities pass through the whole drum body 2 can appear at the same time, and the arrangement of odd number of piston cavities can enable the central axis of only one piston cavity to pass through the vertical middle dividing line of the whole drum body 2 in the rotation process of the drum body 2, and the pressure oil in the high-pressure oil cavities 45 of other piston cavities provides the rotation moment of the hollow piston seat disc 25, thereby realizing that the direction of the interaction force between the push rod 26 and the outer cylindrical shaft section 41 The number of the piston cavities in the collinear state of the vertical middle parting lines of the cylinder body 2 realizes the stable and continuous rotation of the cylinder body 2.

In order to ensure that the piston 22 accurately slides along the axial direction of the piston cavity and prevent the push rod 26 from twisting and further preventing the sliding shoe from being locked due to the circumferential displacement of the piston 22, as a further improvement of the present invention, as shown in fig. 2, a guide groove and a guide key 44 which are arranged in a matching manner are arranged between the piston 22 and the inner wall of the piston cavity, and the guide groove and the guide key 44 are arranged along the axial direction of the piston cavity.

In order to facilitate the processing of the piston cavity on the hollow piston seat disc 25, as a further improvement of the present invention, as shown in fig. 1 and fig. 2, the piston cavity is a through hole structure penetrating through the hollow piston seat disc 25, and the top end of the piston cavity is provided with a piston seal cover 21 which is fixedly and hermetically mounted through a piston seal cover mounting bolt 20 and a piston seal cover seal 19.

In order to reduce power consumption and effectively distribute the working pressure oil to the high pressure oil chamber 45, as shown in fig. 2, when the piston 22 is located at the upper limit of the stroke, the piston 22 is in a state of blocking the split oil inlet 18 and the split oil outlet 24, that is, when the piston chamber rotates to a position located at the eccentric large end of the eccentric cylindrical shaft section 41 during the rotation of the cylinder 2, the piston 22 is located at the upper limit of the stroke, and since there is no eccentricity, the working pressure oil cannot provide the rotation torque of the hollow piston seat disc 25, and the piston 22 is in a state of blocking the split oil inlet 18 and the split oil outlet 24, the working pressure oil cannot enter the piston chamber and is distributed to the high pressure oil chamber 45, thereby reducing power consumption.

In order to facilitate the magnitude of the braking force, as a further improvement of the invention, the disc spring pressing plate 32 is sleeved on the drum shaft 10 in a sliding fit manner, and the disc spring pressing plate 32 is axially positioned and installed through a disc spring pressing plate locking nut 34 which is positioned at the outer end of the disc spring pressing plate and is installed on the drum shaft 10 in a screwing manner through threads. By adjusting the screwing amount of the disc spring pressing plate locking nut 34, the pressing force of the disc spring group 11 can be adjusted through the disc spring pressing plate 32, so that the braking force and the size of the braking gap can be adjusted.

The branch oil passage 17 and the branch oil passage 27 may be of a hose structure or a passage structure provided inside the hollow piston seat disc 25, and the latter is preferable because the latter can reduce the probability of leakage of the hydraulic oil, that is, as a preferable aspect of the present invention, as shown in fig. 1 and 6, the branch oil passage 17 and the branch oil passage 27 are of a passage structure provided inside the hollow piston seat disc 25, and the internal passage structure may be directly cast.

In order to reduce weight and power consumption, as a further improvement of the present invention, as shown in fig. 2, a hollowed-out weight-reduction process hole is provided between the piston cavities of two adjacent hollow piston seat discs 25.

In order to realize various displacements of the compensating bearing 5 caused by the clearance during the rotation of the cylinder 2, so that the hollow piston seat disc 25 is not subjected to additional load caused by the displacement during the rotation, as a further improvement of the invention, the positioning transmission key 33 is a sliding key structure with a sliding clearance along the axial direction of the cylinder 2.

The double-drive hydraulic radial plunger type transmission roller capable of realizing non-return and braking is characterized in that two oil distribution shaft sections comprising an eccentric cylindrical shaft section 41 and an oil inlet flow distribution shaft section 42 which are adjacently arranged are arranged on the shaft section of the roller shaft 10 positioned between two radial plates 4 in a bilateral symmetry manner, a hydraulic driving roller driving device comprising a hollow piston seat disc 25, a push rod 26 and a piston 22 is arranged at the position fixedly corresponding to the eccentric cylindrical shaft section 41 in the roller body 2, working pressure oil in a high-pressure oil cavity 45 acts on the push rod 26 through the piston 22, an included angle exists between the direction of a reaction force of the push rod 26 and the moving direction of the piston 22 caused by the eccentric arrangement of the eccentric cylindrical shaft section 41, and further the acting force of the working pressure oil acting on the push rod 26 through the piston 22 is decomposed into two parts, one part is counteracted with the reaction force provided by the push rod 26, and the other part generates a rotating moment on the, the hollow piston seat disc 25 acts on the cylinder body 2 through the positioning transmission key 33 to drive the cylinder body 2 to rotate, the hollow piston seat disc 25, the radial plate 4, the bearing seat 13, the outer ring of the bearing 5 and the hollow shaft pressure bearing cover 31 rotate along with the cylinder body 2 in the rotating process, and the drum shaft 10, the oil outlet flow distribution flange plate positioning sleeve 13, the oil outlet flow distribution flange plate 30, the hollow piston seat disc positioning sleeve 21, the inner ring of the bearing 5, the sealing cylinder sleeve 35 and the brake sleeve body 12 are in a static state; the two sets of roller driving devices are arranged symmetrically left and right and synchronously, so that the driving moment of the roller body 2 can be improved, and the roller body 2 can be stressed more uniformly when driven to roll; because the bearing seat 13 is also provided with a braking mechanism controlled by hydraulic pressure, the cylinder body 2 can be in a braking state under the condition that the hydraulic pump station is stopped, and the cylinder body 2 can be in a rotatable working state under the condition that the hydraulic pump station is started; because at least one set of brake mechanism is also provided with a non-return structure, the cylinder 2 can be prevented from reversing when being overcome the brake force of the brake mechanism due to larger external force after the cylinder 2 stops rotating; the roller driving device arranged in the barrel 2 can fully utilize the internal space of the barrel 2 on one hand, and adopts a mode of axially entering and exiting working pressure oil from the roller shaft 10 on the other hand, so that an additional transmission device installation space is not needed, and the installation and maintenance are convenient, and the two sets of driving devices can reduce the production cost and the maintenance cost of supporting facilities, and are particularly suitable for high gas mines or belt conveyors with no space for arranging the transmission devices.