CN115199600B - Hydraulic motor back pressure angle automatic control method - Google Patents
Hydraulic motor back pressure angle automatic control method Download PDFInfo
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- CN115199600B CN115199600B CN202210980525.0A CN202210980525A CN115199600B CN 115199600 B CN115199600 B CN 115199600B CN 202210980525 A CN202210980525 A CN 202210980525A CN 115199600 B CN115199600 B CN 115199600B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
- F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/78—Control of multiple output members
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
本发明涉及一种液压马达背压式角度自动控制方法，属于液压传动领域。在液压泵与液压马达之间设置两位四通电磁换向阀、前置单向阀、双直径脉冲油缸以及背压溢流阀等部分，通过减压阀结合背压溢流阀、单向阀对双直径脉冲油缸进行持续补油，电磁换向阀控制双直径脉冲油缸的活塞换向运动，通过油缸中腔容积变化来对液压马达进行微流量供油驱动，以此实现了液压马达回转角度的精确、自动控制，使液压马达可步进式地转动微小的角度，为准确导向钻进和回转机构的自动化精确控制奠定了技术基础。
The present invention relates to a hydraulic motor back pressure angle automatic control method, belonging to the field of hydraulic transmission. A two-position four-way electromagnetic reversing valve, a front check valve, a dual-diameter pulse oil cylinder, a back pressure relief valve and other parts are arranged between the hydraulic pump and the hydraulic motor. The dual-diameter pulse oil cylinder is continuously replenished with oil through a pressure reducing valve combined with a back pressure relief valve and a check valve. The electromagnetic reversing valve controls the piston reversing movement of the dual-diameter pulse oil cylinder. The hydraulic motor is driven by micro-flow oil supply through the change in the volume of the oil cylinder cavity, thereby realizing accurate and automatic control of the hydraulic motor rotation angle, so that the hydraulic motor can be rotated step by step at a small angle, laying a technical foundation for accurate guided drilling and automatic and precise control of the rotary mechanism.
Description
Technical Field
The invention belongs to the field of hydraulic transmission, and particularly relates to a back pressure type angle automatic control method of a hydraulic motor.
Background
Most of the existing turning devices such as a power head of the coal mine drilling machine are driven by a hydraulic motor, an adopted hydraulic system has no accurate control function, the rotating angle of the motor is uncontrollable, and the requirements of accurate guide drilling and automatic control of the coal mine drilling machine are difficult to meet.
In the prior art, the angle measurement or control of the rotary parts such as the power head of the drilling machine, the rotary joint and the like is realized by adopting a rotary encoder or a combined proximity switch, the technology must adopt an electric control mode, the related system is more complex, and the application range of the technology under the coal mine is very limited. Such as 202010125678.8, 201610475239.3, 201410097402.8.
Disclosure of Invention
Therefore, the invention aims to provide a hydraulic motor back pressure type angle automatic control method so as to solve the problems that the existing coal mine drilling machine lacks an accurate control function and the motor rotation angle is uncontrollable.
In order to achieve the above purpose, the present invention provides the following technical solutions:
A back pressure type angle automatic control method of a hydraulic motor mainly comprises the following steps that a two-position four-way electromagnetic directional valve 2, a front one-way valve 3 and a double-diameter pulse oil cylinder 4 are arranged between a hydraulic pump 1 and a hydraulic motor 6, wherein the hydraulic pump 1 is connected with an oil inlet of the two-position four-way electromagnetic directional valve 2, an oil return opening of the two-position four-way electromagnetic directional valve 2 is communicated with an oil tank 10, an A opening 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, a B opening 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 formed between the hydraulic pump 1 and a middle cavity oil inlet of the double-diameter pulse oil cylinder 4, a pressure reducing valve 8 and the front one-way valve 3 are sequentially arranged on the oil way II along the pressure oil conveying direction, a middle cavity oil outlet of the double-diameter pulse oil cylinder 4 is communicated with the hydraulic motor 6, and the hydraulic motor 6 is communicated with the oil tank 10 through a back pressure overflow valve 9.
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, oil filling and energy storage processes:
The method comprises the steps of enabling an electromagnet Y1 of a two-position four-way electromagnetic reversing valve 2 to lose electricity at the beginning, enabling a valve core of the two-position four-way electromagnetic reversing valve 2 to be at a right position, enabling pressure oil output by a hydraulic pump 1 to be divided into two paths, enabling one path to pass through the two-position four-way electromagnetic reversing valve 2 and then enter a small-diameter cavity of a double-diameter pulse oil cylinder 4 to push a piston of the double-diameter pulse oil cylinder 4 to move from one end of the small-diameter cavity to one end of a large-diameter cavity, enabling the volume of a middle cavity to be increased, enabling the other path of pressure oil to continuously enter the middle cavity of the double-diameter pulse oil cylinder 4 through a pressure reducing valve 8 and a front one-way valve 3 which are sequentially arranged to supplement oil to the middle cavity, enabling oil in the large-diameter cavity of the double-diameter pulse oil cylinder 4 to be extruded under the action of the piston and then to return to an oil tank 10 through the two-position four-way electromagnetic reversing valve 2, and enabling the pressure p2 of the pressure reducing valve 8 to be smaller than the pressure p3 of a back pressure overflow valve 9 all the time in the process, enabling the pressure oil flowing to the middle cavity to be cut off at an inlet of the hydraulic motor 6, and enabling the pressure oil flowing to the pressure motor 6 to be prevented from the pressure.
S3, pulse rotation process:
The electromagnet Y1 of the two-position four-way electromagnetic reversing valve 2 is electrified, the valve core of the two-position four-way electromagnetic reversing valve 2 is switched from the right position to the left position at the moment, one of two paths of pressure oil output by the hydraulic pump 1 passes through the two-position four-way electromagnetic reversing valve 2 and then enters a large-diameter cavity of the double-diameter pulse oil cylinder 4 so as to push a piston of the double-diameter pulse oil cylinder 4 to move from one end of the large-diameter cavity to one end of a small-diameter cavity, the volume of a middle cavity at the moment is reduced, the other path of pressure oil passes through the pressure reducing valve 8 to reach the front one-way valve 3, the internal pressure of the middle cavity is larger than the oil supplementing pressure, the oil is cut off at the front one-way valve 3, the pressure oil in the middle cavity of the double-diameter pulse oil cylinder 4 is conveyed to reach the hydraulic motor 6, and the hydraulic motor 6 can be pushed to rotate by a small angle when the driving pressure is larger than the sum of the set pressure p3 of the back pressure valve 9 and the load pressure of the hydraulic motor 6.
And repeating the oil charge energy storage process and the pulse rotation process, and accumulating and rotating for a plurality of times to a required angle.
Further, a relief valve 7 is connected to an oil passage II between the hydraulic pump 1 and the relief valve 8, and the relief valve 7 is connected to an oil tank 10.
Further, the pressure of the relief valve 7 is set to p1, where p3< p1.
Further, the middle cavity oil outlet of the double-diameter pulse oil cylinder 4 is communicated with the hydraulic motor 6 through a rear one-way valve 5.
The invention has the beneficial effects that:
According to the scheme, the pressure reducing valve is combined with the back pressure overflow valve and the one-way valve to continuously supplement oil to the double-diameter pulse oil cylinder, the electromagnetic reversing valve is used for controlling the reversing motion of the piston of the double-diameter pulse oil cylinder, and the micro-flow oil supply driving is carried out on the hydraulic motor through the volume change of the middle cavity of 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 small angle in a stepping manner, and a technical foundation is laid for accurate guiding drilling and automatic accurate control of the 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 objects and other advantages of the invention may be realized and obtained by means of the instrumentalities and combinations particularly pointed out in the specification.
Drawings
For the purpose of making the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in the following preferred detail with reference to the accompanying drawings, in which:
Fig. 1 is a schematic diagram of the present invention.
Reference numerals:
The hydraulic pump comprises a hydraulic pump 1, a two-position four-way electromagnetic reversing valve 2, a preposed one-way valve 3, a double-diameter pulse oil cylinder 4, a postposed one-way valve 5, a hydraulic motor 6, a safety relief valve 7, a pressure reducing valve 8, a backpressure relief valve 9 and an oil tank 10, an oil inlet P, an oil return port T, an electromagnet Y1, a large-diameter cavity 401, a middle cavity 402 and a small-diameter cavity 403.
Detailed Description
Other advantages and effects of the present invention will become apparent to those skilled in the art from the following disclosure, which describes the embodiments of the present invention with reference to specific examples. The invention may be practiced or carried out in other embodiments that depart from the specific details, and the details of the present description may be modified or varied from the spirit and scope of the present invention. It should be noted that the illustrations provided in the following embodiments merely illustrate the basic idea of the present invention by way of illustration, and the following embodiments and features in the embodiments may be combined with each other without conflict.
In which the drawings are for illustrative purposes only and are not intended to be construed as limiting the invention, and in which certain elements of the drawings may be omitted, enlarged or reduced in order to better illustrate embodiments of the invention, and not to represent actual product dimensions, it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
In the description of the present invention, it should be understood that, if there are terms such as "upper", "lower", "left", "right", "front", "rear", etc., the directions or positional relationships indicated are based on the directions or positional relationships shown in the drawings, only for convenience of describing the present invention and simplifying the description, rather than indicating or implying that the referred devices or elements must have a specific direction, be constructed and operated in a specific direction, so that the terms describing the positional relationships in the drawings are merely for exemplary illustration and are not to be construed as limitations of the present invention, and that the specific meanings of the terms described above may be understood by those skilled in the art according to specific circumstances.
Referring to fig. 1, a hydraulic motor back pressure type angle automatic control system is provided, which is composed of a hydraulic pump 1, a two-position four-way electromagnetic reversing 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 provides pressure oil for all elements in the system. The two-position four-way electromagnetic reversing valve 2 is used for switching the direction of an oil inlet path of the double-diameter pulse oil cylinder 4. The preposed one-way valve 3 is used for controlling the oil way between the middle cavity 402 of the double-diameter pulse oil cylinder 4 and the pressure reducing valve 8 to only enable the pressure reducing valve to flow unidirectionally in the direction of the oil cylinder. The double diameter pulse cylinder 4 is an element for accumulating and outputting oil, and is used for pushing the hydraulic motor 6 to rotate by a small angle. The double-diameter pulse oil cylinder 4 is structurally characterized in that cylinder diameters at the left end and the right end are different, an oil cylinder piston is also divided into two parts, the two parts are connected into a whole and synchronously move, one part is positioned in a large-diameter cylinder barrel and can move left and right in the large-diameter cylinder barrel, the other part is positioned in a small-diameter cylinder barrel and can move left and right in the small-diameter cylinder barrel, a large-diameter cavity 401 is formed in a region surrounded by a left end cylinder barrel and a large-diameter piston part corresponding to the cylinder barrel, a small-diameter cavity 403 is formed in a region surrounded by a right end cylinder barrel and a small-diameter piston part corresponding to the cylinder barrel, and a middle cavity 402 is formed in a region surrounded by the two parts of pistons (namely the large-diameter piston part and the small-diameter piston part) and the cylinder barrel. 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 change quantity of the volume is matched with the tiny angle of single rotation of the hydraulic motor. The hydraulic motor 6 is an actuator for rotational output. The pressure reducing valve 8 is used for controlling the oil inlet pressure of the cavity 402 in the double-diameter pulse 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 port of the two-position four-way electromagnetic directional valve 2, an oil return port T port of the two-position four-way electromagnetic directional valve 2 is connected with the oil tank 10, an A port of the two-position four-way electromagnetic directional valve 2 is connected with a large-diameter cavity 401 of the double-diameter pulse oil cylinder 4, a B port of the two-position four-way electromagnetic directional valve 2 is connected with a small-diameter cavity 403 of the double-diameter pulse oil cylinder 4, an oil path 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, a pressure reducing valve 8 and a front one-way valve 3 are sequentially arranged on the oil path II along the pressure oil conveying direction, a middle cavity oil outlet of the double-diameter pulse oil cylinder 4 is connected with the hydraulic motor 6, and the hydraulic motor 6 is connected with the oil tank 10 through a back pressure overflow valve 9.
The control method of the system 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, oil filling and energy storage processes:
At the beginning, the electromagnet Y1 of the two-position four-way electromagnetic directional valve 2 is powered off, and at the moment, the valve core of the two-position four-way electromagnetic directional valve 2 is at the right position.
The pressure oil output by the hydraulic pump 1 is divided into two paths, wherein one path is an oil path I, namely the oil path I enters a small-diameter cavity 403 of the double-diameter pulse oil cylinder 4 after passing through the two-position four-way electromagnetic reversing valve 2 so as to push a piston of the double-diameter pulse oil cylinder 4 to move from one end of the small-diameter cavity 403 to one end of a 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 the middle cavity 402 of the double-diameter pulse oil cylinder 4 through the pressure reducing valve 8 and the front one-way valve 3 which are sequentially arranged so as to supplement oil to the middle cavity 402. Meanwhile, the oil in the large-diameter cavity 401 of the double-diameter pulse oil cylinder 4 is extruded under the action of a piston (moving leftwards), and returns to the oil tank 10 through an A port and a T port of the two-position four-way electromagnetic directional valve 2.
In this process, even if the middle chamber 402 is filled with oil, since the pressure p2 of the pressure reducing valve 8 provided in the system is always smaller than the pressure p3 of the back pressure relief valve 9, the pressure oil flowing from the middle chamber 402 to the hydraulic motor 6 is cut off at the inlet of the hydraulic motor 6, and thus the hydraulic motor 6 is not driven to rotate.
S3, pulse rotation process:
The electromagnet Y1 of the two-position four-way electromagnetic reversing valve 2 is electrified, and at the moment, the valve core of the two-position four-way electromagnetic reversing valve 2 is switched from the right position to the left position.
In the two paths of pressure oil output by the hydraulic pump 1, an oil path I passes through a P port and an A port of the two-position four-way electromagnetic reversing valve 2 and then enters a large-diameter cavity 401 of the double-diameter pulse oil cylinder 4 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 at the moment, the volume of the middle cavity 402 is reduced. 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 stopped at the front check valve 3 (i.e., in this process, the front check valve 3 prevents the high-pressure oil from flowing reversely).
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 delivered to the hydraulic motor 6. When the driving pressure is larger than the sum of the set pressure p3 of the back pressure relief 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 further the stepping small-angle rotation of the rotating angle is realized.
And repeating the oil charge energy storage process and the pulse rotation process, and accumulating and rotating for a plurality of times to a required angle.
In this scheme, connect safety relief valve 7 on the oil circuit II between hydraulic pump 1 and relief valve 8, this safety relief valve 7 is linked together with oil tank 10. The relief valve 7 is used for adjusting the driving force of the hydraulic motor 6 to ensure the safety of the system pressure. The pressure of the relief valve 7 is set to p1, wherein p3< p1, i.e. p2< p3< p1 should be satisfied for the overall 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 the hydraulic motor 6 through a rear one-way valve 5. The rear check 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 flow unidirectionally from the oil cylinder to the motor, so as to prevent the oil in the oil path from the double-diameter pulse oil cylinder 4 to the hydraulic motor 6 from being sucked into the oil cylinder by negative pressure when the volume of the middle cavity is increased.
According to the scheme, the pressure reducing valve is combined with the back pressure overflow valve and the one-way valve to continuously supplement oil to the double-diameter pulse oil cylinder, the electromagnetic reversing valve is used for controlling the reversing motion of the piston of the double-diameter pulse oil cylinder, and the micro-flow oil supply driving is carried out on the hydraulic motor through the volume change of the middle cavity of 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 small angle in a stepping manner, and a technical foundation is laid for accurate guiding drilling and automatic accurate control of the rotation mechanism.
Finally, it is noted that the above embodiments are only for illustrating the technical solution of the present invention and not for limiting the same, 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 and equivalents may be made thereto without departing from the spirit and scope of the present invention, which is intended to be covered by the claims of the present invention.
Claims (4)
1. The back pressure type angle automatic control method of the hydraulic motor is characterized by mainly comprising the following steps that a two-position four-way electromagnetic reversing valve (2), a preposed one-way valve (3) and a double-diameter pulse oil cylinder (4) are arranged between a hydraulic pump (1) and a hydraulic motor (6);
in the double-diameter pulse oil cylinder (4), cylinder diameters at the left end and the right end are different, the oil cylinder pistons are also divided into two parts, the oil cylinder pistons at the left end and the right end are connected into a whole and synchronously move, the left end piston is a large-diameter piston which is positioned in the large-diameter cylinder barrel and can move left and right in the large-diameter cylinder barrel, the right end piston is a small-diameter piston which is positioned in the small-diameter cylinder barrel and can move left and right in the small-diameter cylinder barrel, a region surrounded by the left end cylinder barrel and the large-diameter piston part corresponding to the large-diameter piston positioned in the end cylinder barrel is a large-diameter cavity (401), a region surrounded by the right end cylinder barrel and the small-diameter piston part corresponding to the end cylinder barrel is a small-diameter cavity (403), and a region surrounded by the large-diameter piston, the small-diameter piston and the cylinder barrel together is a middle cavity (402);
The hydraulic pump (1) is connected with an oil inlet of a two-position four-way electromagnetic directional valve (2), an oil return port of the two-position four-way electromagnetic directional valve (2) is connected with an oil tank (10), an A port of the two-position four-way electromagnetic directional valve (2) is connected with a large-diameter cavity of a double-diameter pulse oil cylinder (4), a B port of the two-position four-way electromagnetic directional valve (2) is connected 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 a middle-cavity oil inlet of the double-diameter pulse oil cylinder (4), a pressure reducing valve (8) and a preposed one-way valve (3) are sequentially arranged on the oil way II along the pressure oil conveying direction, a middle-cavity oil outlet of the double-diameter pulse oil cylinder (4) is connected with a hydraulic motor (6), and the hydraulic motor (6) is connected with the oil tank (10) through a back pressure overflow valve (9);
s1, system setting:
The pressure of the pressure reducing valve (8) is set to be p2, and the pressure of the back pressure relief valve (9) is set to be p3, wherein p2< p3;
s2, oil filling and energy storage processes:
The method comprises the steps of enabling an electromagnet (Y1) of a two-position four-way electromagnetic reversing valve (2) to lose electricity, enabling a valve core of the two-position four-way electromagnetic reversing valve (2) to be positioned at the right position, enabling pressure oil output by a hydraulic pump (1) to be divided into two paths, enabling one path to pass through the two-position four-way electromagnetic reversing valve (2) and then enter a small-diameter cavity of a double-diameter pulse oil cylinder (4) so as to push a piston of the double-diameter pulse oil cylinder (4) to move from one end of the small-diameter cavity to one end of a large-diameter cavity, enabling the volume of a middle cavity to be increased, enabling the other path of pressure oil to continuously enter the middle cavity of the double-diameter pulse oil cylinder (4) through a pressure reducing valve (8) and a front one-way valve (3) which are sequentially arranged so as to supplement oil to the middle cavity, enabling oil in the large-diameter cavity of the double-diameter pulse oil cylinder (4) to be extruded under the action of the piston, enabling the pressure p2 of the pressure reducing valve (8) to be smaller than the pressure p3 of a back pressure overflow valve (9) to always in the process, enabling the pressure oil flowing to the middle cavity to flow to the hydraulic motor (6) to the inlet of the hydraulic motor (6) to be not driven by the hydraulic motor (6);
s3, pulse rotation process:
The method comprises the steps of enabling an electromagnet (Y1) of a two-position four-way electromagnetic directional valve (2) to be electrified, switching a valve core of the two-position four-way electromagnetic directional valve (2) from a right position to a left position at the moment, enabling one of two paths of pressure oil output by a hydraulic pump (1) to enter a large-diameter cavity of a double-diameter pulse oil cylinder (4) after passing through 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 to one end of a small-diameter cavity, enabling the volume of a middle cavity to be reduced at the moment, enabling the other path of pressure oil to reach a front one-way valve (3) through a pressure reducing valve (8), enabling the internal pressure of the middle cavity to be larger than the oil supplementing pressure, enabling the oil to be cut off at the front one-way valve (3), and enabling pressure oil in the middle cavity of the double-diameter pulse oil cylinder (4) to be conveyed to reach the position of a hydraulic motor (6), and pushing the hydraulic motor (6) to rotate a small angle when the driving pressure is larger than the sum of a set pressure p3 of a back pressure overflow valve (9) and the load pressure of the hydraulic motor (6);
And repeating the oil charge energy storage process and the pulse rotation process, and accumulating and rotating for a plurality of times to a required angle.
2. The automatic control method for the back pressure type angle of the hydraulic motor according to claim 1 is characterized in that a safety relief valve (7) is connected to an oil path II between the hydraulic pump (1) and the pressure reducing valve (8), and the safety relief valve (7) is communicated with an oil tank (10).
3. The method for automatically controlling the back pressure angle of the hydraulic motor according to claim 2, wherein the pressure of the relief valve (7) is set to p1, wherein p3< p1.
4. The automatic control method for the back pressure type angle of the hydraulic motor according to claim 1, wherein the middle cavity oil outlet of the double-diameter pulse oil cylinder (4) is communicated with the hydraulic motor (6) through a rear one-way valve (5).
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| JP4809949B2 (en) * | 2007-09-25 | 2011-11-09 | 豊興工業株式会社 | Hydraulic device |
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| CN104279200A (en) * | 2013-07-03 | 2015-01-14 | 卢志刚 | Impulse type micro-adjustment oil supply device |
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| CN113883108A (en) * | 2021-11-11 | 2022-01-04 | 科达制造股份有限公司 | A continuous flow amplifier and hydraulic press |
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