CN217873510U - Hydraulic motor angle control device with back pressure - Google Patents
Hydraulic motor angle control device with back pressure Download PDFInfo
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- CN217873510U CN217873510U CN202222159184.9U CN202222159184U CN217873510U CN 217873510 U CN217873510 U CN 217873510U CN 202222159184 U CN202222159184 U CN 202222159184U CN 217873510 U CN217873510 U CN 217873510U
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Abstract
The utility model relates to a take hydraulic motor angle control device of backpressure belongs to the hydraulic transmission field. The device is characterized in that a two-position four-way electromagnetic directional valve, a front one-way valve, a double-diameter pulse oil cylinder, a back pressure overflow valve and the like are arranged between a hydraulic pump and a hydraulic motor, the back pressure overflow valve and the one-way valve are combined to continuously supplement oil to the double-diameter pulse oil cylinder through a pressure reducing valve, the electromagnetic directional valve controls the piston reversing motion of the double-diameter pulse oil cylinder, and micro-flow oil supply driving is carried out on the hydraulic motor through the volume change of a cavity in the oil cylinder, so that the accurate and automatic control of the rotation angle of the hydraulic motor is realized, the hydraulic motor can rotate by a tiny angle in a stepping mode, and a technical foundation is laid for accurate guiding drilling and automatic accurate control of a rotation mechanism.
Description
Technical Field
The utility model belongs to the hydraulic transmission field, concretely relates to hydraulic motor angle control device of area backpressure.
Background
The power head and other rotating devices of the existing coal mine drilling machine are mostly driven by a hydraulic motor, an adopted hydraulic system has no precise control function, the rotating angle of the motor is not controllable, and the requirements of accurate guiding drilling and automatic control of the coal mine drilling machine are difficult to meet.
In the prior art, the angle measurement or control of rotating parts such as a drilling machine power head, a rotating joint and the like adopts a rotary encoder or a combined proximity switch, the technology must adopt an electric control mode, the related system is complex, and the application range of the technology in the underground coal mine is very limited. Such as 202010125678.8, 201610475239.3, 201410097402.8.
SUMMERY OF THE UTILITY MODEL
In view of this, the utility model aims at providing a take hydraulic motor angle control device of backpressure to solve current colliery rig and lack the accurate control function, the uncontrollable problem of motor rotation angle.
In order to achieve the above purpose, the utility model provides a following technical scheme:
a hydraulic motor angle control device with back pressure comprises a two-position four-way electromagnetic directional valve, a front one-way valve and a double-diameter pulse oil cylinder, wherein the two-position four-way electromagnetic directional valve, the front one-way valve and the double-diameter pulse oil cylinder are arranged between a hydraulic pump and a hydraulic motor; the hydraulic pump is connected with an oil inlet of the two-position four-way electromagnetic reversing valve, an oil return port of the two-position four-way electromagnetic reversing valve is communicated with an oil tank, an A port of the two-position four-way electromagnetic reversing valve is communicated with a large-diameter cavity of the double-diameter pulse oil cylinder, and a B port of the two-position four-way electromagnetic reversing valve is communicated with a small-diameter cavity of the double-diameter pulse oil cylinder; an oil way II is indirectly arranged between the hydraulic pump and an oil inlet of a middle cavity of the double-diameter pulse oil cylinder, and a pressure reducing valve and a front check valve are sequentially arranged on the oil way II along the pressure oil conveying direction; an oil outlet of a middle cavity of the double-diameter pulse oil cylinder is communicated with a hydraulic motor, and the hydraulic motor is communicated with an oil tank through a back pressure overflow valve; the pressure of the pressure reducing valve is p2, and the pressure of the back pressure relief valve is p3, wherein p2< p3.
Furthermore, a safety overflow valve is connected to an oil path II between the hydraulic pump and the pressure reducing valve, and the safety overflow valve is communicated with an oil tank.
And the oil outlet of the middle cavity of the double-diameter pulse oil cylinder is communicated with the hydraulic motor through the rear one-way valve.
Further, the pressure reducing valve is communicated with the oil tank.
Further, the cylinder diameters of the left end and the right end of the double-diameter pulse oil cylinder are different, the oil cylinder piston comprises a large-diameter piston and a small-diameter piston, the large-diameter piston and the small-diameter piston are connected into a whole and move synchronously, and the large-diameter piston is positioned in the large-diameter cylinder and can move left and right in the large-diameter cylinder; the small-diameter piston is positioned in the small-diameter cylinder barrel and can move left and right in the small-diameter cylinder barrel; the area surrounded by the large-diameter piston, the small-diameter piston and the cylinder barrel together is a middle cavity.
The beneficial effects of the utility model reside in that:
the scheme adopts the pressure reducing valve to combine a backpressure overflow valve and a one-way valve to continuously supplement oil for the double-diameter pulse oil cylinder, adopts the electromagnetic directional valve to control the piston reversing motion of the double-diameter pulse oil cylinder, and carries out micro-flow oil supply driving on the hydraulic motor through the volume change of the middle cavity of the oil cylinder, thereby realizing the accurate and automatic control of the rotation angle of the hydraulic motor, enabling the hydraulic motor to rotate a tiny angle in a stepping way, and laying a technical foundation for accurate guiding drilling and automatic accurate control of a rotation mechanism.
Additional advantages, objects, and features of the invention will be set forth in part in the description which follows and in part will become apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention. The objectives and other advantages of the invention may be realized and attained by the means of the instrumentalities and/or combinations particularly pointed out in the appended claims.
Drawings
For the purposes of promoting a better understanding of the objects, features and advantages of the invention, reference will now be made to the following detailed description taken in conjunction with the accompanying drawings in which:
fig. 1 is a schematic view of the device of the present invention.
Reference numerals:
the hydraulic control system comprises a hydraulic pump 1, a two-position four-way electromagnetic directional valve 2, a front check valve 3, a double-diameter pulse oil cylinder 4, a rear check valve 5, a hydraulic motor 6, a safety overflow valve 7, a pressure reducing valve 8, a back pressure overflow valve 9 and an oil tank 10; an oil inlet P, an oil return port T and an electromagnet Y1; a large diameter cavity 401, a middle cavity 402 and a small diameter cavity 403.
Detailed Description
The following description of the embodiments of the present invention is provided for illustrative purposes, and other advantages and effects of the present invention will be readily apparent to those skilled in the art from the disclosure herein. The present invention can also be implemented or applied through other different specific embodiments, and various details in the present specification can be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that the drawings provided in the following embodiments are only for illustrating the basic idea of the present invention, and the features in the following embodiments and examples may be combined with each other without conflict.
Wherein the showings are for the purpose of illustration only and not for the purpose of limiting the invention, the figures are shown in schematic form and not in pictorial form; for a better understanding of the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
The same or similar reference numerals in the drawings of the embodiments of the present invention correspond to the same or similar parts; in the description of the present invention, it should be understood that if there are terms such as "upper", "lower", "left", "right", "front", "back", etc., indicating directions or positional relationships based on the directions or positional relationships shown in the drawings, it is only for convenience of description and simplification of description, but it is not intended to indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore, the terms describing the positional relationships in the drawings are only used for illustrative purposes and are not to be construed as limiting the present invention, and those skilled in the art can understand the specific meanings of the terms according to specific situations.
Referring to fig. 1, the device is a hydraulic motor angle control device with back pressure, and the device is composed of a hydraulic pump 1, a two-position four-way electromagnetic directional valve 2, a front check valve 3, a double-diameter pulse oil cylinder 4, a hydraulic motor 6 and the like. The hydraulic pump 1 is a power element of the system and supplies pressure oil to each element in the system. The two-position four-way electromagnetic directional valve 2 is used for switching the direction of an oil inlet path of the double-diameter pulse oil cylinder 4. The preposed check valve 3 is used for controlling the oil circuit between the middle cavity 402 of the double-diameter pulse oil cylinder 4 and the pressure reducing valve 8, and the oil circuit can only realize one-way flow of the pressure reducing valve to the direction of the oil cylinder. The double-diameter pulse oil cylinder 4 is an element for accumulating and outputting oil and is used for pushing the hydraulic motor 6 to rotate by a tiny angle. The double-diameter pulse oil cylinder 4 has the structural characteristics that: the diameters of the cylinder barrels at the left end and the right end are different, the oil cylinder piston is also divided into two parts, the two parts are connected into a whole and move synchronously, and one part is positioned in the large-diameter cylinder barrel and can move left and right in the large-diameter cylinder barrel; the other part is positioned in the small-diameter cylinder barrel and can move left and right in the small-diameter cylinder barrel; the area surrounded by the left end cylinder and the large diameter piston part corresponding to the end cylinder is a large diameter cavity 401, the area surrounded by the right end cylinder and the small diameter piston part corresponding to the end cylinder is a small diameter cavity 403, and the area surrounded by the two parts of pistons (i.e. the large diameter piston part and the small diameter piston part) and the cylinder is a middle cavity 402. When the piston moves, the volume of the middle cavity changes due to the movement of the piston, so that the switching between the oil charging state and the oil discharging state is realized, and the variable quantity of the volume is matched with the single-rotation tiny angle of the hydraulic motor. The hydraulic motor 6 is an actuator of the rotation output. The pressure reducing valve 8 is used to control the inlet pressure of the chamber 402 in the dual diameter impulse cylinder 4. The back pressure relief valve 9 is used to control the outlet back pressure of the hydraulic motor 6.
Specifically, the hydraulic pump 1 is connected with an oil inlet P of the two-position four-way electromagnetic directional valve 2, an oil return port T of the two-position four-way electromagnetic directional valve 2 is communicated with the oil tank 10, a port A of the two-position four-way electromagnetic directional valve 2 is communicated with a large-diameter cavity 401 of the double-diameter pulse oil cylinder 4, and a port B of the two-position four-way electromagnetic directional valve 2 is communicated with a small-diameter cavity 403 of the double-diameter pulse oil cylinder 4; an oil way II is connected between the hydraulic pump 1 and an oil inlet of a middle cavity 402 of the double-diameter pulse oil cylinder 4, and a pressure reducing valve 8 and a front check valve 3 are sequentially arranged on the oil way II along the pressure oil conveying direction; the oil outlet of the middle cavity of the double-diameter pulse oil cylinder 4 is communicated with a hydraulic motor 6, and the hydraulic motor 6 is communicated with an oil tank 10 through a back pressure overflow valve 9.
The control method of the device mainly comprises the following steps:
s1, system setting:
the pressure of the pressure reducing valve 8 is set to p2, and the pressure of the back pressure relief valve 9 is set to p3, where p2< p3.
S2, an oil-filled energy storage process:
initially, the electromagnet Y1 of the two-position four-way electromagnetic directional valve 2 is de-energized, and at the moment, the valve core of the two-position four-way electromagnetic directional valve 2 is in the right position.
The pressure oil output by the hydraulic pump 1 is divided into two paths: one path is an oil path I, namely the oil path I passes through the two-position four-way electromagnetic directional valve 2 and then enters the small-diameter cavity 403 of the double-diameter pulse oil cylinder 4 so as to push the piston of the double-diameter pulse oil cylinder 4 to move from one end of the small-diameter cavity 403 to one end of the large-diameter cavity 401, and the volume of the middle cavity 402 is increased at the moment. The other path is an oil path II, namely pressure oil continuously enters a middle cavity 402 of the double-diameter pulse oil cylinder 4 through a pressure reducing valve 8 and a front check valve 3 which are sequentially arranged so as to supplement oil to the middle cavity 402. Meanwhile, oil in the large-diameter cavity 401 of the double-diameter pulse oil cylinder 4 is extruded out under the action of the piston (moving leftwards), and returns to the oil tank 10 through the port A and the port T of the two-position four-way electromagnetic directional valve 2.
In this process, even if the intermediate chamber 402 is filled with oil, the pressure p2 of the pressure reducing valve 8 provided in the system is always lower than the pressure p3 of the back pressure relief valve 9, and the pressure oil flowing from the intermediate chamber 402 to the hydraulic motor 6 is stopped at the inlet of the hydraulic motor 6, so that the hydraulic motor 6 is not driven to rotate.
S3, a pulse rotation process:
and the electromagnet Y1 of the two-position four-way electromagnetic reversing valve 2 is electrified, and the valve core of the two-position four-way electromagnetic reversing valve 2 is switched from the right position to the left position.
In two paths of pressure oil output by the hydraulic pump 1, an oil path I enters a large-diameter cavity 401 of the double-diameter pulse oil cylinder 4 after passing through a port P and a port A of the two-position four-way electromagnetic directional valve 2 so as to push a piston of the double-diameter pulse oil cylinder 4 to move from one end of the large-diameter cavity 401 to one end of a small-diameter cavity 403, and the volume of a middle cavity 402 is reduced at the moment. The pressure oil in the oil path ii reaches the front check valve 3 through the pressure reducing valve 8, and at this time, the internal pressure of the middle cavity 402 is greater than the oil supplementing pressure, so that the oil path is cut off at the front check valve 3 (i.e., the front check valve 3 prevents the high-pressure oil from flowing reversely in the process).
As the volume of the middle chamber 402 becomes smaller, the pressure oil in the middle chamber 402 of the double-diameter pulse cylinder 4 is supplied to the hydraulic motor 6. When the driving pressure is greater than the sum of the set pressure p3 of the backpressure overflow valve 9 and the load pressure of the hydraulic motor 6, the hydraulic motor 6 can be pushed to rotate by a small angle, and the stepping type small-angle rotation of the rotation angle is further realized.
And repeating the two steps of the oil charging and energy storing process and the pulse rotating process, and accumulating and rotating to a required angle for many times.
In the scheme, a safety overflow valve 7 is connected to an oil way II between the hydraulic pump 1 and the pressure reducing valve 8, and the safety overflow valve 7 is communicated with an oil tank 10. The safety relief valve 7 is used for adjusting the driving force of the hydraulic motor 6 and ensuring the safety of the system pressure. The pressure of the safety relief valve 7 is set to p1, where p3< p1, i.e. p2< p3< p1 should be satisfied for the entire system setting.
As a further optimization of the scheme, the oil outlet of the middle cavity 402 of the double-diameter pulse oil cylinder 4 is communicated with a hydraulic motor 6 through a rear one-way valve 5. The rear one-way valve 5 is used for controlling the oil path between the middle cavity 402 of the double-diameter pulse oil cylinder 4 and the hydraulic motor 6 to only realize one-way flow from the oil cylinder to the motor, so that when the volume of the middle cavity is increased, the oil in the oil path from the double-diameter pulse oil cylinder 4 to the hydraulic motor 6 is prevented from being sucked into the oil cylinder by negative pressure.
The scheme adopts the pressure reducing valve combined with the backpressure overflow valve and the one-way valve to continuously supplement oil for the double-diameter pulse oil cylinder, adopts the electromagnetic directional valve to control the piston reversing motion of the double-diameter pulse oil cylinder, and carries out micro-flow oil supply driving on the hydraulic motor through the volume change of the middle cavity of the oil cylinder, thereby realizing the accurate and automatic control of the rotation angle of the hydraulic motor, enabling the hydraulic motor to rotate a tiny angle in a stepping manner, and laying a technical foundation for accurate guiding drilling and automatic accurate control of a rotation mechanism.
Finally, it should be noted that the above embodiments are only used for illustrating the technical solutions of the present invention and not for limiting, and although the present invention is described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that the technical solutions of the present invention can be modified or substituted by equivalents without departing from the spirit and scope of the technical solutions, which should be covered by the scope of the claims of the present invention.
Claims (4)
1. The utility model provides a take hydraulic motor angle control device of backpressure which characterized in that: the hydraulic control system comprises a two-position four-way electromagnetic directional valve (2), a front one-way valve (3) and a double-diameter pulse oil cylinder (4), wherein the two-position four-way electromagnetic directional valve is arranged between a hydraulic pump (1) and a hydraulic motor (6); the hydraulic pump (1) is connected with an oil inlet of the two-position four-way electromagnetic directional valve (2), an oil return port of the two-position four-way electromagnetic directional valve (2) is communicated with the oil tank (10), an A port of the two-position four-way electromagnetic directional valve (2) is communicated with a large-diameter cavity of the double-diameter pulse oil cylinder (4), and a B port of the two-position four-way electromagnetic directional valve (2) is communicated with a small-diameter cavity of the double-diameter pulse oil cylinder (4); an oil way II is connected between the hydraulic pump (1) and an oil inlet of a middle cavity of the double-diameter pulse oil cylinder (4), and a pressure reducing valve (8) and a front check valve (3) are sequentially arranged on the oil way II along the pressure oil conveying direction; an oil outlet of a middle cavity of the double-diameter pulse oil cylinder (4) is communicated with a hydraulic motor (6), and the hydraulic motor (6) is communicated with an oil tank (10) through a backpressure overflow valve (9);
the pressure of the pressure reducing valve (8) is p2, the pressure of the back pressure overflow valve (9) is p3, wherein p2< p3.
2. The hydraulic motor angle control with back pressure of claim 1, wherein: a safety overflow valve (7) is connected on an oil way II between the hydraulic pump (1) and the pressure reducing valve (8), and the safety overflow valve (7) is communicated with an oil tank (10).
3. The hydraulic motor angle control with back pressure of claim 1, wherein: the double-diameter pulse oil cylinder is characterized by further comprising a rear one-way valve (5), and an oil outlet of a middle cavity of the double-diameter pulse oil cylinder (4) is communicated with the hydraulic motor (6) through the rear one-way valve (5).
4. The hydraulic motor angle control with back pressure of claim 1, wherein: the pressure reducing valve (8) is communicated with the oil tank (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222159184.9U CN217873510U (en) | 2022-08-16 | 2022-08-16 | Hydraulic motor angle control device with back pressure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202222159184.9U CN217873510U (en) | 2022-08-16 | 2022-08-16 | Hydraulic motor angle control device with back pressure |
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| Publication Number | Publication Date |
|---|---|
| CN217873510U true CN217873510U (en) | 2022-11-22 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202222159184.9U Active CN217873510U (en) | 2022-08-16 | 2022-08-16 | Hydraulic motor angle control device with back pressure |
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| CN (1) | CN217873510U (en) |
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2022
- 2022-08-16 CN CN202222159184.9U patent/CN217873510U/en active Active
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