阅读说明：本技术 一种换辊大车电液混合传动控制方法及系统 (Roll changing cart electro-hydraulic hybrid transmission control method and system ) 是由 傅家彬 陆兆刚 方剑 黄福德 刁曲锋 凌应勇 于 2021-08-26 设计创作，主要内容包括：本发明公开了一种换辊大车电液混合传动控制方法及系统,其包括,驱动液压马达前进步骤,包括B端阀门关闭和马达前进调控阶段；以及,驱动液压马达后退步骤,包括A端阀门关闭和马达后退调控阶段。传动装置,设置在底座上的液压马达,液压马达的输出轴与UCP210轴承通过联轴器连接,液压马达、联轴器、UCP210轴承之间设置有键,UCP210轴承设置在齿轮轴前端,齿轮轴后端设置有UCP205轴承,UCP210轴承和UCP205轴承连接；控制装置,进油管路和回油管路依次穿过先导式减压阀、先导式比例换向阀、压力补偿器和溢流阀并与液压马达连接,与先导式比例换向阀连接的操作面板。该系统拆卸方便,且增加换辊大车驱动力、减少电机驱动载荷,提升设备运行的稳定性。(The invention discloses a roll-changing cart electro-hydraulic hybrid transmission control method and a roll-changing cart electro-hydraulic hybrid transmission control system, which comprises a step of driving a hydraulic motor to advance, wherein the step comprises a B-end valve closing stage and a motor advancing regulation and control stage; and driving the hydraulic motor to retreat, wherein the step comprises the steps of closing an A-end valve and regulating and controlling the retreat of the motor. The transmission device is a hydraulic motor arranged on the base, an output shaft of the hydraulic motor is connected with a UCP210 bearing through a coupler, keys are arranged among the hydraulic motor, the coupler and the UCP210 bearing, the UCP210 bearing is arranged at the front end of the gear shaft, the UCP205 bearing is arranged at the rear end of the gear shaft, and the UCP210 bearing is connected with the UCP205 bearing; the control device comprises an oil inlet pipeline and an oil return pipeline which sequentially penetrate through a pilot type pressure reducing valve, a pilot type proportional reversing valve, a pressure compensator and an overflow valve, are connected with a hydraulic motor and are connected with an operation panel of the pilot type proportional reversing valve. The system is convenient to disassemble, the driving force of the roll changing cart is increased, the motor driving load is reduced, and the running stability of the equipment is improved.)

1. The roll changing cart electro-hydraulic hybrid transmission control method is characterized by comprising the following steps: comprises the steps of (a) preparing a mixture of a plurality of raw materials,

driving the hydraulic motor to advance, wherein the step comprises the steps of closing a valve at the B end and regulating and controlling the advance of the motor; and the number of the first and second groups,

and driving the hydraulic motor to retreat, wherein the step comprises the steps of closing an A-end valve and regulating and controlling the retreat of the motor.

2. The roll-changing cart electro-hydraulic hybrid transmission control method as claimed in claim 1, characterized in that: the B-end valve closing phase comprises the following steps,

hydraulic oil enters from a system oil inlet, a valve at the B end of the pilot type proportional reversing valve is closed, and the hydraulic oil enters the pilot type reducing valve firstly.

3. The roll change cart electro-hydraulic hybrid transmission control method of claim 1 or 2, characterized in that: the motor advance control phase comprises the following steps,

when the pressure of the hydraulic oil is greater than the set value of the pilot type pressure reducing valve, the hydraulic oil greater than the set value of the pressure can be discharged back to the oil tank from the pilot type pressure reducing valve, the hydraulic oil in the set value enters ｃA P-A oil way of the pilot type proportional reversing valve, enters the pressure compensator and the overflow valve and is input into the hydraulic motor, and the hydraulic motor rotates and advances.

4. The roll-changing cart electro-hydraulic hybrid transmission control method as claimed in claim 1, characterized in that: the closing phase of the A-end valve comprises,

hydraulic oil enters from a system oil inlet, a valve at the end A of the pilot type proportional reversing valve is closed, and the hydraulic oil enters the pilot type pressure reducing valve firstly.

5. The roll-changing cart electro-hydraulic hybrid transmission control method according to claim 3 or 4, characterized in that: the motor back-off regulation phase comprises that,

when the pressure of the hydraulic oil is greater than the set value of the pilot type pressure reducing valve, the hydraulic oil greater than the set value of the pressure can be discharged back to the oil tank from the pilot type pressure reducing valve, the hydraulic oil in the set value enters a P-B oil way of the pilot type proportional reversing valve, enters the pressure compensator and the overflow valve and is input into the hydraulic motor, and the hydraulic motor rotates and retreats.

6. A system adopting the roll-changing cart electro-hydraulic hybrid transmission control method as claimed in claims 1-5, characterized in that: comprises the steps of (a) preparing a mixture of a plurality of raw materials,

the transmission device (100) is arranged on a hydraulic motor (101) on a base (102), an output shaft of the hydraulic motor (101) is connected with a UCP210 bearing (106) through a coupler (103), a key (104) is arranged among the hydraulic motor (101), the coupler (103) and the UCP210 bearing (106), the UCP210 bearing (106) is arranged at the front end of a gear shaft (105), a UCP205 bearing (107) is arranged at the rear end of the gear shaft (105), and the UCP210 bearing (106) is connected with the UCP205 bearing (107); and the number of the first and second groups,

the oil inlet pipeline (201) and the oil return pipeline (202) of the control device (200) sequentially penetrate through a pilot type pressure reducing valve (203), a pilot type proportional reversing valve (204), a pressure compensator (205) and an overflow valve (206), are connected with the hydraulic motor (101), and are connected with an operation panel (207) of the pilot type proportional reversing valve (204).

7. The system of the roll-changing cart electro-hydraulic hybrid transmission control method according to claim 6, characterized in that: the transmission device (100) is further provided with a distance ring (108), a first nut (109) and a second nut (110);

the rear end of the gear shaft (105) is sequentially connected with the distance ring (108), the first nut (109) and the second nut (110).

8. The system of the roll changing cart electro-hydraulic hybrid transmission control method of claim 7, characterized in that: the transmission device (100) is further provided with a positioning pin (111), a first bolt (112) and a second bolt (113), and the UCP210 bearing (106) and the UCP205 bearing (107) are positioned through the positioning pin (111) and connected through the first bolt (112) and the second bolt (113).

9. The system of the roll-changing cart electro-hydraulic hybrid transmission control method according to claim 6, characterized in that: a leakage opening is formed in the hydraulic motor (101), a leakage oil return opening (208) is formed in the control device (200), and the leakage opening is connected with the leakage oil return opening (208);

wherein, transmission (100) still is equipped with third bolt (114), hydraulic motor (101) with base (102) pass through third bolt (114) be connected.

10. The system of the roll changing cart electro-hydraulic hybrid transmission control method according to claim 6, wherein two relief valves (206) are provided.

Technical Field

The invention relates to the technical field of steel rolling, in particular to a roll changing cart electro-hydraulic hybrid transmission control method and system.

Background

Along with the development of modern industry, the production efficiency of enterprises is higher and higher, the fault rate required for the operation of field equipment is lower and lower, a roll changing cart is more and more commonly used in the steel rolling fields of leveling, acid rolling stand roll changing and the like, the action accuracy of corresponding required mechanical equipment is higher, the roll changing cart of a leveling machine is only driven by a speed reducing motor, and the situation of slipping or insufficient driving force often occurs in plum rain seasons in the south, so that the roll changing cart cannot advance or retreat, the jam fault shutdown is caused, the production efficiency and the production benefit of the enterprises are influenced, and long-time shutdown equipment accidents are caused by insufficient driving force of the roll changing cart in some domestic steel mills. Aiming at the situation that the driving force of a speed reducing motor of a cold rolling leveling roll changing cart is insufficient, an electro-hydraulic hybrid transmission device of the roll changing cart is urgently needed to be designed to increase the driving force of the roll changing cart, reduce the load of the speed reducing motor and improve the running stability of the roll changing cart.

Disclosure of Invention

This section is for the purpose of summarizing some aspects of embodiments of the invention and to briefly introduce some preferred embodiments. In this section, as well as in the abstract and the title of the invention of this application, simplifications or omissions may be made to avoid obscuring the purpose of the section, the abstract and the title, and such simplifications or omissions are not intended to limit the scope of the invention.

The invention is provided in view of the problems of the prior roll changing cart electro-hydraulic hybrid transmission control method.

Therefore, the invention aims to provide an electro-hydraulic hybrid transmission control method and system for a roll changing cart.

In order to solve the technical problems, the invention provides the following technical scheme: the roll changing cart electro-hydraulic hybrid transmission control method is characterized by comprising the following steps: the method comprises the steps of driving a hydraulic motor to advance, wherein the steps comprise the closing of a valve at the B end and the forward regulation and control of the motor; and driving the hydraulic motor to retreat, wherein the step comprises the steps of closing an A-end valve and regulating and controlling the retreat of the motor.

As a preferred scheme of the roll changing cart electro-hydraulic hybrid transmission control method, the roll changing cart electro-hydraulic hybrid transmission control method comprises the following steps: and the stage of closing the valve at the B end comprises the steps that hydraulic oil enters from an oil inlet of the system, the valve at the B end of the pilot type proportional reversing valve is closed, and the hydraulic oil enters the pilot type reducing valve firstly.

As a preferred scheme of the roll changing cart electro-hydraulic hybrid transmission control method, the roll changing cart electro-hydraulic hybrid transmission control method comprises the following steps: and the motor forward regulation and control stage comprises that when the pressure of the hydraulic oil is greater than the set value of the pilot type pressure reducing valve, the hydraulic oil greater than the set value of the pressure can be discharged back to the oil tank from the pilot type pressure reducing valve, the hydraulic oil in the set value enters ｃA P-A oil way of the pilot type proportional reversing valve, enters ｃA pressure compensator and an overflow valve and is input into the hydraulic motor, and the hydraulic motor rotates and advances.

As a preferred scheme of the roll changing cart electro-hydraulic hybrid transmission control method, the roll changing cart electro-hydraulic hybrid transmission control method comprises the following steps: and the stage of closing the valve at the end A comprises the steps that hydraulic oil enters from an oil inlet of the system, the valve at the end A of the pilot type proportional reversing valve is closed, and the hydraulic oil enters the pilot type reducing valve firstly.

As a preferred scheme of the roll changing cart electro-hydraulic hybrid transmission control method, the roll changing cart electro-hydraulic hybrid transmission control method comprises the following steps: and the motor backward regulation and control stage comprises that when the pressure of the hydraulic oil is greater than the set value of the pilot type pressure reducing valve, the hydraulic oil greater than the set value of the pressure can be discharged back to the oil tank from the pilot type pressure reducing valve, the hydraulic oil in the set value enters a P-B oil way of the pilot type proportional reversing valve, enters a pressure compensator and an overflow valve and is input into the hydraulic motor, and the hydraulic motor rotates backward.

In order to solve the technical problems, the invention provides the following technical scheme: the electro-hydraulic hybrid transmission control system of the roll changing cart comprises a transmission device and a hydraulic motor arranged on a base, wherein an output shaft of the hydraulic motor is connected with a UCP210 bearing through a coupler, keys are arranged among the hydraulic motor, the coupler and the UCP210 bearing, the UCP210 bearing is arranged at the front end of a gear shaft, the rear end of the gear shaft is provided with a UCP205 bearing, and the UCP210 bearing is connected with the UCP205 bearing; and the control device is an operation panel, wherein the oil inlet pipeline and the oil return pipeline sequentially penetrate through the pilot type pressure reducing valve, the pilot type proportional reversing valve, the pressure compensator and the overflow valve, are connected with the hydraulic motor, and are connected with the pilot type proportional reversing valve.

As a preferred scheme of the roll-changing cart electro-hydraulic hybrid transmission control system, the roll-changing cart electro-hydraulic hybrid transmission control system comprises the following steps: the transmission device is also provided with a distance ring, a first nut and a second nut; the rear end of the gear shaft is sequentially connected with the distance ring, the first nut and the second nut.

As a preferred scheme of the roll-changing cart electro-hydraulic hybrid transmission control system, the roll-changing cart electro-hydraulic hybrid transmission control system comprises the following steps: the transmission device is further provided with a positioning pin, a first bolt and a second bolt, and the UCP210 bearing and the UCP205 bearing are positioned through the positioning pin and are connected through the first bolt and the second bolt.

As a preferred scheme of the roll-changing cart electro-hydraulic hybrid transmission control system, the roll-changing cart electro-hydraulic hybrid transmission control system comprises the following steps: the hydraulic motor is provided with a leakage port, the control device is provided with a leakage oil return port, and the leakage port is connected with the leakage oil return port; the transmission device is further provided with a third bolt, and the hydraulic motor is connected with the base through the third bolt.

As a preferred scheme of the roll-changing cart electro-hydraulic hybrid transmission control system, the roll-changing cart electro-hydraulic hybrid transmission control system comprises the following steps: the overflow valve is provided with two overflow valves.

The invention has the beneficial effects that: the driving force of the roll changing cart is increased, the motor driving load is reduced, and the running stability of the equipment is improved; and the system is more convenient to mount and dismount.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise. Wherein:

FIG. 1 is a control schematic diagram of the roll-changing cart electro-hydraulic hybrid transmission control method.

FIG. 2 is a dimensional diagram of a gear shaft of the roll-changing cart electro-hydraulic hybrid transmission control system of the invention.

FIG. 3 is a dimensional diagram of a base of the roll-changing cart electro-hydraulic hybrid transmission control system of the present invention.

FIG. 4 is a schematic diagram of the installation and use of the roll-changing cart electro-hydraulic hybrid transmission control system.

FIG. 5 is an assembly view of the roll change cart electro-hydraulic hybrid transmission control system of the present invention.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, but the present invention may be practiced in other ways than those specifically described and will be readily apparent to those of ordinary skill in the art without departing from the spirit of the present invention, and therefore the present invention is not limited to the specific embodiments disclosed below.

Furthermore, reference herein to "one embodiment" or "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment is included in at least one implementation of the invention. The appearances of the phrase "in one embodiment" in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments.

Furthermore, the present invention is described in detail with reference to the drawings, and in the detailed description of the embodiments of the present invention, the cross-sectional view illustrating the structure of the device is not enlarged partially according to the general scale for convenience of illustration, and the drawings are only exemplary and should not be construed as limiting the scope of the present invention. In addition, the three-dimensional dimensions of length, width and depth should be included in the actual fabrication.

Example 1

Referring to fig. 1, the roll-changing cart electro-hydraulic hybrid transmission control method comprises a step of driving a hydraulic motor to advance, and comprises a stage of closing a valve at the B end and regulating and controlling the advance of the motor; and driving the hydraulic motor to retreat, wherein the step comprises the steps of closing an A-end valve and regulating and controlling the retreat of the motor.

Specifically, the pilot-operated pressure reducing valve is normally opened, and pressure is set according to requirements, so that the pressure stabilizing effect is achieved; an oil pipe in the pilot-operated proportional reversing valve is provided with an A, B end, when a forward command is sent, the oil pipe valve at the B end is closed, hydraulic oil enters from the A end, when a backward command is sent, the oil pipe valve at the A end is closed, the hydraulic oil enters from the B end, and the pilot-operated proportional reversing valve realizes the reversing and stepless speed regulation functions of the hydraulic motor; the pressure compensator mainly eliminates pressure instability caused by impact, reduces instability caused by impact of the hydraulic motor, and plays roles of pressure stabilization and buffering for the whole working environment, and the pressure compensator can automatically adjust the balance of oil inlet and outlet of the oil pipe according to the opening degree of the pilot type proportional reversing valve; the overflow valves are arranged, because the hydraulic motor needs to realize two functions of advancing and retreating, the oil pipes P-A and P-B need to be switched continuously, the overflow valves are used for preventing the hydraulic motor from leaking to the oil return tank due to overhigh pressure, the effect of protecting the hydraulic motor is achieved, and the service life is prolonged.

In the operation process, when ｃA forward command is sent, hydraulic oil enters from an oil inlet of the system, ｃA valve at the end B of the pilot type proportional reversing valve is closed, the hydraulic oil firstly passes through an oil pipe in the pilot type pressure reducing valve, when the pressure of the hydraulic oil is greater than the set pressure value of the pilot type proportional reversing valve, the hydraulic oil greater than the set pressure value can be discharged back to an oil tank from the pilot type pressure reducing valve, the hydraulic oil in the set value enters ｃA P-A oil pipe of the pilot type proportional reversing valve, then enters an oil pipe of ｃA pressure compensator, finally enters an overflow valve oil pipe and is input into ｃA hydraulic motor, and the hydraulic motor rotates to advance.

When ｃA backward instruction is sent out, hydraulic oil enters from an oil inlet of the system, ｃA valve at the end A of the pilot type proportional reversing valve is closed, the hydraulic oil firstly passes through an oil pipe in the pilot type pressure reducing valve, when the pressure of the hydraulic oil is greater than the set pressure value of the pilot type proportional reversing valve, the hydraulic oil which is greater than the set pressure value can be discharged back to an oil tank from the pilot type pressure reducing valve, the hydraulic oil in the set value enters ｃA P-A oil pipe of the pilot type proportional reversing valve, then enters an oil pipe of ｃA pressure compensator, finally enters an oil pipe of an overflow valve and is input into ｃA hydraulic motor, and the hydraulic motor rotates and then retreats.

Furthermore, two gears are arranged for advancing and retreating, when the first gear is started, the opening of the pilot type proportional reversing valve is set to be 15000, and the current of the speed reducing motor is between 21A and 21.6A; when the second gear is started, the opening of the pilot proportional reversing valve is set to 17000, and the current of the speed reducing motor is stabilized at 19.5A.

According to the original speed reducing motor parameters, the opening degrees of the pilot type pressure reducing valve and the overflow valve are adjusted, and the control precision of the system is improved; the opening degree of the pilot-operated proportional reversing valve is adjusted, the rotation speed of the hydraulic motor is matched with the speed of the speed reducing motor, and equivalently, one set of traction device is added to the roll changing cart, so that the driving force of the roll changing cart is increased, the driving load of the motor is reduced, the problem of walking jamming of the roll changing cart is solved, and the running stability of equipment is improved

Example 2

Referring to fig. 1, an electro-hydraulic hybrid transmission control system of a roll changing cart comprises a transmission 100 and a control device 200.

Specifically, the transmission device 100 includes a hydraulic motor 101 disposed on a base 102, an output shaft of the hydraulic motor 101 is connected to a UCP210 bearing 106 through a coupler 103, keys 104 are disposed among the hydraulic motor 101, the coupler 103, and the UCP210 bearing 106, the UCP210 bearing 106 is disposed at a front end of a gear shaft 105, a UCP205 bearing 107 is disposed at a rear end of the gear shaft 105, and the UCP210 bearing 106 is connected to the UCP205 bearing 107.

The distance between the central shaft of the transmission device 100 and the end face of the frame of the roll changing cart is calculated to be less than or equal to 50mm, so that the diameter of an output shaft of the hydraulic motor 101 is 32mm, the diameter of the size of the mounting flange is 134mm, the diameter of a bolt hole is 13mm, the length of the bolt hole is 226.4mm, and the hydraulic motor 101 mainly provides driving force for the transmission device 100; the base 102 is designed to be 235mm long, 225mm wide, 45mm high and 86mm diameter of a mounting hole according to the mounting size of the hydraulic motor 101, and the base 102 is mainly used for mounting and fixing the hydraulic motor 101 and plays a supporting role; the coupler 103 is a coupler with the model of ML3 according to the diameter of 32mm of the output shaft of the hydraulic motor 101, the length of the coupler is 103mm, the diameter of the coupler is 70mm, and the coupler is mainly used for connecting the hydraulic motor 101 with the gear shaft 105 to play a role in transmitting motion and torque; the key 104 is designed to be 10mm multiplied by 8mm multiplied by 36mm in size, and mainly functions to fix the coupler 103, prevent the coupler 103 from moving and play a role in transmitting motion and torque; the design size length of the gear shaft 105 is 879mm, the diameter of the addendum circle of the gear is 234mm, the sizes of the positions where the coupler 103 and the UCP210 bearing 106 are installed are 32mm and 40mm, the sizes of the positions where the UCP205 bearing 107 is installed are 25mm and 640mm, and the gear shaft 105 mainly drives the roll changing cart frame to move so as to play a role in transmitting power; UCP210 bearing 106 and UCP205 bearing 107 are self-contained bearing seats, and play a role in fixing gear shaft 105 and preventing gear shaft 105 from moving.

In the using process, the base 102 is fixed on the end face of the frame of the roll changing cart in a welding mode by determining the installation size of the base 102, and then the hydraulic motor 101 is welded on the base 102; the key 104 is arranged on the output shaft of the hydraulic motor 101, and then the coupler 103 (one half of the coupler) and the plum blossom pad are arranged on the output shaft; the front end of the gear shaft 105 is provided with a UCP210 bearing 106, a key 104 and a coupling 103 (the other half), the rear end of the gear shaft 105 is provided with a UCP205 bearing 107, and then the coupling 103 of the half at the front end of the gear shaft 105 is butted with the coupling 103 of the other half at the end of the hydraulic motor 101 in place; finally, the UCP210 bearing seat and UCP205 bearing seat are welded.

Further, the control device 200 is used for matching the rotation speed of the hydraulic motor 101 with the speed reducing motor, so that the driving force of the roll changing cart is increased, and the driving load of the motor is reduced.

The oil inlet line 201 and the oil return line 202 sequentially pass through the pilot type pressure reducing valve 203, the pilot type proportional directional valve 204, the pressure compensator 205 and the overflow valve 206 and are connected with the hydraulic motor 101, and an operation panel 207 is connected with the pilot type proportional directional valve 204 and is used for controlling the forward and backward movement of the hydraulic motor 101.

When the operation panel 207 sends ｃA forward command, hydraulic oil enters from the oil inlet pipeline 201, the valve at the B end of the pilot-operated proportional directional valve 204 is closed, the hydraulic oil first passes through the oil pipe in the pilot-operated pressure reducing valve 203, when the pressure of the hydraulic oil is greater than the pressure value set by the pilot-operated proportional directional valve 203, the hydraulic oil greater than the pressure set value is discharged back to the oil tank from the pilot-operated pressure reducing valve 203, the hydraulic oil in the set value enters the P- ｃA oil pipe of the pilot-operated proportional directional valve 204, then enters the oil pipe of the pressure compensator 205, finally enters the oil pipe of the overflow valve 206 and is input into the hydraulic motor 101, and the hydraulic motor 101 rotates forward.

When the operation panel 207 sends a backward command, hydraulic oil enters from the oil inlet pipeline 201, the valve at the end of the pilot-operated proportional directional valve 204A is closed, the hydraulic oil first passes through the oil pipe in the pilot-operated pressure reducing valve 203, when the pressure of the hydraulic oil is greater than the pressure value set by the pilot-operated proportional directional valve 203, the hydraulic oil greater than the pressure set value is discharged back to the oil tank from the pilot-operated pressure reducing valve 203, the hydraulic oil in the set value enters the P-B oil pipe of the pilot-operated proportional directional valve 204, then enters the oil pipe of the pressure compensator 205, finally enters the oil pipe of the overflow valve 206 and is input into the hydraulic motor 101, and the hydraulic motor 101 rotates backward.

Example 3

Referring to fig. 2, this embodiment is different from the second embodiment in that: the transmission 100 is more convenient to mount and dismount.

Specifically, the transmission device 100 is further provided with a distance ring 108, a first nut 109 and a second nut 110, wherein the rear end of the gear shaft 105 is further connected with the distance ring 108, the first nut 109 and the second nut 110 in sequence; the first nut 109 is contacted with the end face of the distance ring 108, is tightly twisted and rotates together with the inner ring of the bearing, and plays a role in fastening; the second nut 110 reinforces the first nut 109, and plays a role of looseness prevention.

Furthermore, the transmission device 100 is further provided with a positioning pin 111, a first bolt 112 and a second bolt 113, wherein the positioning pin 111 prevents the UCP210 bearing 106 and the UCP205 bearing 107 from being dislocated, so that the positioning function is achieved, and the mounting accuracy is improved; first bolt 109 and second bolt 110 serve to secure the bearing seats of UCP210 bearing 106 and UCP205 bearing 107.

Further, the transmission 100 is further provided with a third bolt 114, and the hydraulic motor 101 and the base 102 are provided with bolt holes and detachably connected through the third bolt 114.

Preferably, the hydraulic motor 101 is provided with a leakage port 101a, the control device 200 is provided with a leakage oil return port 208, and the leakage port 101a is connected with the leakage oil return port 208, so that the cleaning is convenient.

Furthermore, two overflow valves 206 are provided, because the hydraulic motor 101 needs to realize two functions of advancing and retreating, the oil pipes P- ｃA and P-B need to be switched continuously, and the overflow valves 206 prevent the hydraulic motor 101 from leaking to the oil tank due to overhigh pressure, so as to protect the hydraulic motor 101 and prolong the service life.

The connection of the device is detachable connection, so that the installation in the early stage and the maintenance in the later stage are facilitated, and the use is also guaranteed.

It is important to note that the construction and arrangement of the present application as shown in the various exemplary embodiments is illustrative only. Although only a few embodiments have been described in detail in this disclosure, those skilled in the art who review this disclosure will readily appreciate that many modifications are possible (e.g., variations in sizes, dimensions, structures, shapes and proportions of the various elements, values of parameters (e.g., temperatures, pressures, etc.), mounting arrangements, use of materials, colors, orientations, etc.) without materially departing from the novel teachings and advantages of the subject matter recited in this application. For example, elements shown as integrally formed may be constructed of multiple parts or elements, the position of elements may be reversed or otherwise varied, and the nature or number of discrete elements or positions may be altered or varied. Accordingly, all such modifications are intended to be included within the scope of this invention. The order or sequence of any process or method steps may be varied or re-sequenced according to alternative embodiments. In the claims, any means-plus-function clause is intended to cover the structures described herein as performing the recited function and not only structural equivalents but also equivalent structures. Other substitutions, modifications, changes and omissions may be made in the design, operating conditions and arrangement of the exemplary embodiments without departing from the scope of the present inventions. Therefore, the present invention is not limited to a particular embodiment, but extends to various modifications that nevertheless fall within the scope of the appended claims.

Moreover, in an effort to provide a concise description of the exemplary embodiments, all features of an actual implementation may not be described (i.e., those unrelated to the presently contemplated best mode of carrying out the invention, or those unrelated to enabling the invention).

It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation-specific decisions may be made. Such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure, without undue experimentation.

It should be noted that the above-mentioned embodiments are only for illustrating the technical solutions of the present invention and not for limiting, and although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, which should be covered by the claims of the present invention.