CN111486149A - Servo power-assisted hydraulic cylinder - Google Patents
Servo power-assisted hydraulic cylinder Download PDFInfo
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- CN111486149A CN111486149A CN202010455580.9A CN202010455580A CN111486149A CN 111486149 A CN111486149 A CN 111486149A CN 202010455580 A CN202010455580 A CN 202010455580A CN 111486149 A CN111486149 A CN 111486149A
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- piston
- servo
- oil
- valve
- control
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
- F15B13/0435—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being sliding valves
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
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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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
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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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
Abstract
The invention discloses a servo power-assisted hydraulic cylinder which comprises a servo cylinder body, a piston valve sleeve and a valve core assembly, wherein the valve core assembly is connected in the piston valve sleeve in a sliding manner, the servo cylinder body is divided into a hydraulic cylinder control rod cavity and a hydraulic cylinder piston rod cavity, the valve core assembly comprises a slide valve core and a slide valve centering reset device, one end, located in the hydraulic cylinder control rod cavity, of the slide valve core is connected with a control rod for providing motion input, and one end, located in the hydraulic cylinder piston rod cavity, of the piston valve sleeve is connected with a piston; when the control rod is in control input, the piston rod overcomes the external load resistance to follow the movement of the control rod; when the control rod does not control input, the spool of the slide valve returns to the neutral position under the action of the centering resetting device of the slide valve, the valve sleeve of the piston is in a floating state, and the spool of the slide valve returns to the original position under the action of an external load. When the external power is lost, the servo hydraulic cylinder can realize the floating function of the piston of the servo hydraulic cylinder, namely, the piston rod in the servo hydraulic cylinder moves along with the movement of the external load.
Description
Technical Field
The invention belongs to the technical field of electro-hydraulic servo control, and particularly relates to a servo power-assisted hydraulic cylinder.
Background
The servo hydraulic cylinder is mainly characterized in that the output of the servo cylinder can follow the movement of input control at any time, and at present, 2 realization forms exist, one is a mechanical rod piece used as the control input of the servo cylinder, and the other is a digital hydraulic cylinder using a stepping motor as pulse input.
Patent application number CN101074691A discloses a servo hydraulic cylinder, which mainly comprises a cylinder body, a front end cover, an oil inlet and an oil return port. A piston and a piston rod connected with the piston are arranged in a cavity of the oil cylinder body, a cavity on one side of the piston is a rod cavity, a rodless cavity is arranged on the other side of the piston, a valve cavity and a flow passage are arranged in the piston, a movable valve core and a control valve port are arranged in the valve cavity, one end of the valve core is connected with a control rod, and the other end of the valve core is communicated with the cavity; the oil inlet is communicated with the rod cavity, and the oil return port is communicated with the control valve port. The control device and the execution device of the hydraulic servo system are combined into a whole to be designed into a hydraulic servo device, the oil cylinder body is used as a fixed part, the oil cylinder piston is used as a movable part, and the displacement input of the valve core is directly converted into the displacement output of the oil cylinder piston and the piston rod.
Patent CN204512235U discloses a power cylinder, a piston rod of the power cylinder is connected with a clutch pull rod through a connection fork, when a clutch pedal is stepped on, a throttle valve in the piston rod is powered firstly, so that a pressure difference is generated between an upper cavity and a lower cavity in the power cylinder, and the piston rod is pushed to pull the clutch pull rod, so as to separate the clutch.
Patent application number CN106369006A discloses a digital servo hydraulic cylinder, mainly comprises piston rod, ball screw, piston, screw nut, servo direction control case, stopper, axial clearance compensator and control motor. The piston rod is a hollow piston rod; a rod cavity of the digital servo hydraulic cylinder is communicated with high-pressure oil. The servo direction control valve where the servo direction control valve core is located is a three-position zero-opening valve, the servo direction control valve core and a ball screw are integrated, and the ball screw extends into a central hole of a piston rod and is meshed with a screw nut of the central hole; the other end of the servo direction control valve core is connected with one end of a limiting block, the other end of the limiting block is connected with one end of an axial clearance compensator, and the other end of the axial clearance compensator is connected with a shaft of a control motor; when the control motor rotates, the servo direction control valve core and the ball screw are driven to rotate together.
Although the mechanical servo hydraulic cylinder and the digital servo hydraulic cylinder can move along with the input action, when external power is lost, the floating function of the piston of the servo hydraulic cylinder cannot be realized, namely, the piston rod of the servo hydraulic cylinder moves along with the movement of an external load.
Disclosure of Invention
The invention aims to provide a servo hydraulic cylinder, wherein a piston rod of the servo hydraulic cylinder has a motion input function of following a control rod of the servo hydraulic cylinder, and meanwhile, when external power is lost, the servo hydraulic cylinder can realize a piston floating function of the servo hydraulic cylinder, namely, the piston rod in the servo hydraulic cylinder moves along with the motion of an external load.
In order to solve the problems, the invention adopts the following technical scheme:
a servo-assisted hydraulic cylinder comprises a servo cylinder body, a piston valve sleeve and a valve core assembly, wherein the valve core assembly is connected in the piston valve sleeve in a sliding mode, the piston valve sleeve is connected in the servo cylinder body in a sliding mode and divides the interior of the servo cylinder body into a hydraulic cylinder control rod cavity and a hydraulic cylinder piston rod cavity, the valve core assembly comprises a slide valve core and a slide valve centering reset device, one end, located in the hydraulic cylinder control rod cavity, of the slide valve core is connected with a control rod used for providing motion input, and one end, located in the hydraulic cylinder piston rod cavity, of the piston valve sleeve is connected with; when the control rod is in control input, the piston rod overcomes the external load resistance to follow the movement of the control rod; when the control rod does not control input, the spool of the slide valve returns to the neutral position under the action of the centering resetting device of the slide valve, the piston valve sleeve is in a floating state, namely the piston rod moves along with the movement of an external load, and the piston valve sleeve can return to the original position under the action of the external load.
Optionally, an oil inlet P3, an oil return port T3, a control oil port a3 and a control oil port b3 are arranged in the piston valve sleeve, the control oil port a3 is communicated with the hydraulic cylinder control rod cavity through an oil passage, the control oil port b3 is communicated with the hydraulic cylinder piston rod cavity, and when the spool valve of the spool valve reciprocates in the piston valve sleeve, the oil inlet P3, the oil return port T3, the control oil port a3 and the control oil port b3 are communicated or closed through the matching of the spool valve and the piston valve sleeve.
Optionally, the spool and the piston valve housing of the spool valve are in a spool valve type five-position four-way reversing valve structure, and five positions of the spool valve type five-position four-way reversing valve are respectively a middle position, a left stop position, a left reversing position, a right stop position and a right reversing position, that is:
when the oil inlet is in a middle position, the oil inlet P3 is cut off, and the control oil port a3, the control oil port b3 and the oil return port T3 are communicated;
when the left stop position is reached, the oil inlet P3 is cut off, the control oil port a3 is cut off, and the control oil port b3 is communicated with the oil return port T3;
when the direction is changed leftwards, the oil inlet P3 is communicated with the control oil port a3, and the control oil port b3 is communicated with the oil return port T3;
when the oil inlet is stopped at the right stop position, the oil inlet P3 is stopped, the control oil port b3 is stopped, and the control oil port a3 is communicated with the oil return port T3;
when the direction of the oil inlet is changed rightwards, the oil inlet P3 is communicated with the control oil port b3, and the control oil port a3 is communicated with the oil return port T3. .
Optionally, when the spool valve type five-position four-way reversing valve is in a middle position, the covering amount of the oil inlet P3 is larger than or equal to the opening amount of the oil return port T3.
Optionally, a pilot oil inlet P1 and a pilot oil return port T1 are formed in the servo cylinder, an oil inlet groove P2 and an oil return groove T2 which are not communicated with each other are formed between the piston valve sleeve and the servo cylinder along the axial direction, the oil inlet P3 of the piston valve sleeve is communicated with the pilot oil inlet P1 through an oil inlet groove P2, the oil return port T3 of the piston valve sleeve is communicated with the pilot oil return port T1 through an oil return groove T2, the oil inlet groove P2 is always communicated with the pilot oil inlet P1, and the oil return groove T2 is always communicated with the pilot oil return port T1 in the moving process of the piston valve sleeve in the servo cylinder.
Optionally, four regions are arranged between the piston valve sleeve and the servo cylinder body, which are respectively a circumferential isolation region, an anti-rotation groove region, two oil groove regions which are not communicated with each other and an axial isolation region which separates the two oil groove regions, the two oil groove regions are respectively used as an oil inlet groove and an oil return groove, and the axial dimension of the oil inlet groove and the oil return groove is larger than the stroke of the piston valve sleeve.
Optionally, the piston valve sleeve and the servo cylinder body are respectively provided with an anti-rotation groove in an anti-rotation groove area, a flat key is installed between the two anti-rotation grooves, and the piston valve sleeve and the servo cylinder body are connected through the flat key.
Optionally, the control rod disposed at one end of the spool valve includes a control rod connecting portion and a spool connecting portion, and the spool connecting portion is detachably and fixedly connected with one end of the spool valve.
Optionally, fixedly connected with piston left end lid can be dismantled to piston valve barrel's one end, and fixedly connected with piston right end lid can be dismantled to piston valve barrel's the other end, and piston left end lid and piston right end lid can be threaded connection respectively at piston valve barrel's both ends, and the cylinder cap before the servo cylinder of fixedly connected with can be dismantled to servo cylinder body's one end, and the cylinder cap behind the servo cylinder of fixedly connected with can be dismantled to servo cylinder body's the other end forms between piston left end lid and the servo cylinder front cylinder cap the pneumatic cylinder control rod chamber forms between piston right end lid and the servo cylinder rear cylinder.
Optionally, a stepped hole is formed in the left end cover of the piston, one end of the control rod arranged at one end of the spool of the sliding valve is slidably connected in the stepped hole, the stepped hole comprises a fine hole section and a coarse hole section, the coarse hole section of the stepped hole is provided with the sliding valve centering and resetting device, the sliding valve centering and resetting device comprises a sliding valve resetting spring and two spring seats, the two spring seats are slidably connected in the coarse hole section, the end face of one spring seat abuts against the end face of the coarse hole section, the end face of the other spring seat abuts against the end face of the shoulder of the spool of the sliding valve, and the distance between the two spring seats is the maximum relative displacement of the spool of the sliding valve relative to the piston valve sleeve of the servo.
By adopting the technical scheme, the invention has the following advantages:
1. the position of the piston rod in the piston rod cavity of the hydraulic cylinder is only related to the position of the control rod, so that the accurate position control of the piston rod of the servo hydraulic cylinder can be realized.
2. When the control rod does not have power input, a piston valve sleeve of the servo hydraulic cylinder is in a floating state, the position of the piston valve sleeve is determined by the external load of the piston rod, and the piston valve sleeve can be restored to the original position under the action of the external load.
3. The spool valve is arranged in the servo cylinder body, the four-way spool valve body is integrated with the piston, the whole servo cylinder is compact in structure, the design technology of the four-way spool valve is introduced into the servo cylinder, and the control function of the servo cylinder is expanded.
4. The servo power cylinder body is fixed, the positions of the oil inlet and the oil return port are fixed, and when the control rod is in unpowered input, the servo power cylinder is in an unloading state, so that the problems of reducing heating and improving the energy-saving effect can be effectively solved.
Drawings
FIG. 1 is a schematic view of an exploded structure of the present invention;
FIG. 2 is a perspective view of the piston valve sleeve of the present invention;
FIG. 3 is one of the schematic cross-sectional structural views of FIG. 1;
FIG. 4 is a second schematic cross-sectional view of FIG. 1;
FIG. 5 is a schematic diagram of the principle of the present invention;
FIG. 6 is a schematic diagram of the servo control of the present invention when the joystick is moved to the left in a multi-way valve.
Reference numerals:
11. a valve body; 12. a main valve element;
21. a manual operating device housing; 22. a main spool return spring;
31. a motor; 32. a ball screw; 33. a ball nut; 34. a sliding shell; 35. a moving block; 36. a bearing cover plate; 37. a motor mounting plate;
41. a servo cylinder; 411. a hydraulic cylinder control rod cavity; 412. a hydraulic cylinder piston rod cavity; 42. a piston valve housing; 421. a flat bond; 43. a spool valve core; 441. a spool return spring; 442. a spring seat; 45. a piston left end cover; 46. a piston right end cover; 462. a piston rod; 47. a servo cylinder front cylinder cover; 48. a servo cylinder rear cylinder cover; 49. a control lever; 491. a control lever connecting part; 492. a valve core connecting portion; 8. and (4) external loading.
Detailed Description
In order to make the technical objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be further described with reference to fig. 1 to 6 and the following embodiments, wherein the direction in which the spool 43 of the spool valve moves toward the operating lever 49 is the left direction, and the direction in which the spool 43 of the spool valve moves toward the piston rod 462 is the right direction.
As shown in fig. 5, the servo-assisted hydraulic cylinder of the present invention includes a servo cylinder body 41, a piston valve sleeve 42, and a valve core assembly, wherein the valve core assembly is slidably connected in the piston valve sleeve 42, and the piston valve sleeve 42 is slidably connected in the servo cylinder body 41 and divides the interior of the servo cylinder body 41 into a cylinder rod cavity 411 and a cylinder piston rod cavity 412. The valve core assembly and the piston valve sleeve 42 form a four-way slide valve, and the piston valve sleeve 42 is used as a piston of the servo power hydraulic cylinder and a valve sleeve of the four-way slide valve.
Specifically, fixedly connected with piston left end lid 45 can be dismantled to piston valve barrel 42's one end, fixedly connected with piston right end lid 46 can be dismantled to piston valve barrel 42's the other end, and piston left end lid 45 and piston right end lid 46 can be threaded connection respectively at piston valve barrel 42's both ends, and cylinder cover 47 before the servo cylinder of fixedly connected with can be dismantled to servo cylinder 41's one end, and cylinder cover 48 behind the servo cylinder of fixedly connected with can be dismantled to servo cylinder 41's the other end forms between piston left end lid 45 and the servo cylinder cover 47 the pneumatic cylinder control rod chamber 411, form between piston right end lid 46 and the servo cylinder cover 48 pneumatic cylinder piston rod chamber 412.
The valve core assembly comprises a slide valve core 43 and a slide valve centering reset device, wherein one end of the slide valve core 43, which is positioned in a hydraulic cylinder control rod cavity, is in transmission connection with an external linear motion part through a control rod 49, and one end of the piston valve sleeve 42, which is positioned in a hydraulic cylinder piston rod cavity 412, is in transmission connection with an external load.
One end of the slide valve core 43, which is positioned in the hydraulic cylinder control rod cavity, is connected with a control rod for providing motion input, and one end of the piston valve sleeve 42, which is positioned in the hydraulic cylinder piston rod cavity, is connected with a piston rod for connecting with an external load; when the control rod has control input, the piston rod 462 overcomes the external load resistance to follow the movement of the control rod; when the control lever is not operated, the spool valve 43 returns to the neutral position under the action of the centering reset device of the spool valve, and the piston valve sleeve 42 is in a floating state, i.e., the piston rod 462 moves along with the movement of the external load.
The spool valve centering and resetting device may be installed at either or both ends of the spool 43 of the spool valve, and in this embodiment, the slide valve centering resetting device is arranged at one end of the slide valve spool 43 close to the operating rod, specifically, a stepped hole is arranged on the piston left end cover 45, one end of the operating rod is connected in the stepped hole in a sliding manner, the stepped hole comprises a fine hole section and a coarse hole section, the slide valve centering resetting device is arranged on the coarse hole section of the stepped hole, the slide valve centering resetting device comprises a slide valve resetting spring 441 and two spring seats 442, the two spring seats 442 are connected in the coarse hole section in a sliding manner, and the slide valve resetting spring 441 is in a natural state, the end surface of one of the spring seats 442 abuts against the end surface of the coarse hole section, the end surface of the other spring seat 442 abuts against the shoulder end surface of the spool valve 43, and the distance between the two spring seats 442 is the maximum relative displacement of the spool valve 43 relative to the piston valve sleeve of the servo cylinder.
As shown in fig. 3, an oil inlet P3, an oil return port T3, a control oil port a3 and a control oil port b3 are arranged in the piston valve sleeve 42, the control oil port a3 is communicated with the hydraulic cylinder control rod cavity 411 through an oil passage, the control oil port b3 is communicated with the hydraulic cylinder piston rod cavity 412, and when the spool valve 43 reciprocates in the piston valve sleeve 42, the oil inlet P3, the oil return port T3, the control oil port a3 and the control oil port b3 are communicated or closed through the matching of the spool valve 43 and the piston valve sleeve 42.
Specifically, at least one control oil hole a2 is formed in the piston left end cover 45, the control oil hole a3 is communicated with the hydraulic cylinder control rod cavity 411 through a control oil hole a2, at least one control oil hole b2 is formed in the piston right end cover 46, and the control oil hole b3 is communicated with the hydraulic cylinder piston rod cavity 412 through a control oil hole b 2.
Four regions are arranged between the piston valve sleeve 42 and the servo cylinder 41 in the servo hydraulic unit 4, namely a circumferential isolation region at two ends, an anti-rotation groove region, two oil groove regions which are not communicated with each other and an axial isolation region which separates the two oil groove regions, the two oil groove regions are respectively used as an oil inlet groove and an oil return groove, and the axial dimension of the oil inlet groove and the oil return groove is larger than the stroke of the piston valve sleeve 42, so that in the moving process of the piston valve sleeve 42 in the servo cylinder 41, the oil inlet groove is always communicated with an oil inlet oil way, and the oil return groove is always communicated with an oil return way.
The piston valve sleeve 42 and the servo cylinder 41 are respectively provided with an anti-rotation groove in an anti-rotation groove area, a flat key 421 is arranged between the two anti-rotation grooves, and the piston valve sleeve 42 and the servo cylinder 41 are connected through the flat key 421; during installation, the flat key 421 can be fixed in the anti-rotation groove of the piston valve sleeve 42 by a screw, then the piston valve sleeve 42 with the flat key 421 is installed in the servo cylinder 41, the flat key 421 can circumferentially restrict the piston valve sleeve 42, and the piston valve sleeve 42 can only reciprocate along the axial direction of the servo cylinder 41 and cannot rotate.
Further, the spool valve 43 and the piston valve housing 42 are in a spool valve type five-position four-way reversing valve structure, and five positions of the spool valve type five-position four-way reversing valve are respectively a middle position, a left stop position, a left reversing position, a right stop position and a right reversing position, that is:
when the oil inlet is in a middle position, the oil inlet P3 is cut off, and the control oil port a3, the control oil port b3 and the oil return port T3 are communicated;
when the left stop position is reached, the oil inlet P3 is cut off, the control oil port a3 is cut off, and the control oil port b3 is communicated with the oil return port T3;
when the direction is changed leftwards, the oil inlet P3 is communicated with the control oil port a3, and the control oil port b3 is communicated with the oil return port T3;
when the oil inlet is stopped at the right stop position, the oil inlet P3 is stopped, the control oil port b3 is stopped, and the control oil port a3 is communicated with the oil return port T3;
when the direction of the oil inlet is changed rightwards, the oil inlet P3 is communicated with the control oil port b3, and the control oil port a3 is communicated with the oil return port T3.
Furthermore, five undercut grooves for communicating oil are formed in the piston valve sleeve 42, the oil inlet P3, the oil return port T3, the control oil port a3 and the control oil port b3 are respectively formed in different undercut grooves, the spool 43 of the spool valve is provided with three shoulders for opening or closing the oil ports, and when the spool 43 of the spool valve reciprocates in the piston valve sleeve 42, the undercut grooves are opened or closed by the shoulders on the spool valve 43 of the spool valve, so that the oil ports communicated with the undercut grooves are switched on or closed; the oil inlet P3 is of a negative opening type, the oil return port T3 is of a positive opening type, when the slide valve type five-position four-way reversing valve is of a middle position, the oil inlet P3 is cut off, the control oil port a3, the control oil port b3 and the oil return port T3 are communicated, the covering amount of the oil inlet P3 is larger than or equal to the opening amount of the oil return port T3, and the flow rate of the slide valve type five-position four-way reversing valve is controlled through the opening amount of the valve port corresponding to each control edge.
Further, a pilot oil inlet P1 and a pilot oil return port T1 are formed in the servo cylinder 41, an oil inlet groove P2 and an oil return groove T2 which are not communicated with each other are formed between the piston valve sleeve 42 and the servo cylinder 41 along the axial direction, the oil inlet groove P2 and the oil return groove T2 can be formed on the periphery of the piston valve sleeve 42 or on the inner wall of the servo cylinder 41, an oil inlet P3 of the piston valve sleeve 42 is communicated with the pilot oil inlet P1 through the oil inlet groove P2, an oil return port T3 of the piston valve sleeve 42 is communicated with the pilot oil return port T1 through the oil return groove T2, the oil inlet groove P2 is communicated with the pilot oil inlet P1 all the time, and the oil return groove T2 is communicated with the pilot oil return port T1 all the time during the movement of.
Specifically, a valve sleeve hole coaxial with the spool valve 43 of the spool valve is formed in the piston valve sleeve 42, a shoulder is in clearance fit with the valve sleeve hole, the position of the drive unit 3 is left, the shoulder on the spool valve 43 is sequentially marked as a first shoulder, a second shoulder and a third shoulder from left to right, undercut grooves in the valve sleeve hole are sequentially marked as a first undercut groove, a second undercut groove, a third undercut groove, a fourth undercut groove and a fifth undercut groove from left to right, the first undercut groove, the second undercut groove, the third undercut groove, the fourth undercut groove and the fifth undercut groove respectively correspond to the left oil return port T3, the control oil port a3, the oil inlet P3, the control oil port b3 and the right oil return port T3, the width of the second shoulder is greater than that of the third undercut groove, the widths of the first shoulder and the second shoulder are greater than those of the first undercut groove and the fifth undercut groove, and the left and right oil return ports T3 are respectively communicated with.
Specifically, the joystick 49 includes a joystick connecting portion 491 and a spool connecting portion 492, the joystick connecting portion 491 is detachably and fixedly connected to the external linear motion member, and the spool connecting portion 492 is detachably and fixedly connected to one end of the spool 43 of the spool valve. The control rod connecting portion 491 and the external linear motion member may be connected by a screw, and the spool connecting portion 492 and the spool 43 of the spool valve may be connected by a screw or a pin (that is, pin holes are formed in the spool connecting portion 492 and the spool 43 of the spool valve in the same direction, and the spool connecting portion 492 and the spool 43 of the spool valve are connected into a whole by a positioning pin inserted into the two pin holes at the same time).
The working process of the servo power-assisted hydraulic cylinder comprises the following steps:
when the control rod 49 has motion input, the position of the spool 43 of the spool valve is determined by the control rod, and when the control rod 49 has no motion input, the position of the spool 43 of the spool valve returns to the neutral position under the action of the centering reset device of the spool valve, the four-way spool valve is in an unloading state, and the piston valve sleeve is in a floating state.
The specific process is as follows: when the spool valve 43 moves rightwards under the drive of the control rod 49, the control rod 49 pushes the left spring seat 442 to move rightwards, the spool valve return spring 441 is compressed, the servo cylinder five-position four-way spool valve is in a left reversing position, the hydraulic cylinder control rod cavity 411 continuously feeds oil, the hydraulic cylinder piston rod cavity 412 feeds oil, and the piston rod follows the control rod 49 and the spool valve 43 to move rightwards by overcoming external load resistance;
when the operating rod 49 stops moving, namely the operating rod 49 stops with power, the piston valve sleeve 42 moves along with the slide valve core 43, at the moment, the five-position four-way slide valve is in a left stop position, the oil in the hydraulic cylinder operating rod cavity 411 stops, and the piston valve sleeve 42 stops moving; when the control rod 49 retracts leftwards, the hydraulic cylinder control rod cavity 411 returns oil, and the piston valve sleeve retracts along with the control rod under the action of external load;
when the control rod 49 has no motion input, under the action of the slide valve return spring 441, the slide valve core 43 moves leftwards to return to the middle position, the hydraulic cylinder control rod cavity 411 and the hydraulic cylinder piston rod cavity 412 are respectively communicated with the oil return port T3, the piston valve sleeve in the servo cylinder body is in a floating state, and under the action of an external load, the piston valve sleeve can return to the initial position;
on the contrary, when the spool valve 43 moves leftwards under the driving of the control rod 49, the shoulder on the spool valve 43 pushes the right spring seat 442 leftwards, the spool valve return spring 441 is compressed, the five-position four-way spool valve of the servo cylinder is in the right reversing position, the oil is continuously fed into the piston rod cavity 412 of the hydraulic cylinder, the oil is returned into the control rod cavity 411 of the hydraulic cylinder, and the piston rod follows the control rod 49 and the spool valve 43 to move leftwards by overcoming the external load resistance;
when the operating rod 49 stops moving, namely the operating rod 49 stops driving, the piston valve sleeve 42 moves along with the slide valve core 43, at the moment, the five-position four-way slide valve is in the right stop position, the oil in the piston rod cavity 412 of the hydraulic cylinder stops, and the piston valve sleeve 42 stops moving; when the control rod 49 retracts leftwards, the hydraulic cylinder piston rod cavity 412 returns oil, and the piston valve sleeve retracts along with the control rod under the action of an external load;
when the control rod 49 has no motion input, under the action of the slide valve return spring 441, the slide valve core 43 moves rightwards to return to the middle position, the hydraulic cylinder control rod cavity 411 and the hydraulic cylinder piston rod cavity 412 are respectively communicated with the oil return port T3, the piston valve sleeve in the servo cylinder body is in a floating state, and under the action of an external load, the piston valve sleeve can return to the initial position.
Further, as another embodiment of the present invention, based on the above structure, the servo-assisted hydraulic cylinder of the present invention can be applied to an electric proportional multi-way valve, as shown in fig. 6, the electric proportional multi-way valve mainly includes a valve body 11 having a plurality of reversing units, each reversing unit includes a main valve 12, one end of each main valve 12 is mounted with a set of electric proportional hydraulic control devices, the other end of the main valve 12 can be optionally mounted with a manual control device 2, and each reversing unit can replace the manual control device with the electric proportional hydraulic control device. The electro-proportional hydraulic control device comprises a driving unit for converting the rotary motion of the motor into linear motion and the servo hydraulic cylinder, wherein the servo hydraulic cylinder can amplify the power of signals (such as displacement, speed, electrification stop, power loss and the like) provided by the driving unit and then drive the main valve element 12.
Specifically, the joystick 49 includes a joystick connecting portion 491 and a spool connecting portion 492, the joystick connecting portion 491 is detachably and fixedly connected to the outer linear motion member 35, and the spool connecting portion 492 is detachably and fixedly connected to one end of the spool 43 of the spool valve. The driving unit includes: a motor 31 and a motion conversion mechanism, wherein the motion conversion mechanism adopts a screw transmission structure in the embodiment, the rotary motion member is a ball screw 32, and the linear motion member is a ball nut 33. Furthermore, the periphery of the motion conversion mechanism is provided with a sliding shell 34 for limiting the rotation of the linear motion part, two ends of the sliding shell 34 are respectively connected with the motor 31 and the servo power-assisted hydraulic cylinder, the ball nut 33 is detachably and fixedly connected with the control rod connecting part 491 through a moving block 35, when the cross section of the moving block 35 is square, the cross section of an inner cavity of the sliding shell 34 is also square, so that the moving block 35 can only reciprocate in the sliding shell 34 and cannot rotate.
Furthermore, one side of the piston rod 462 of the servo hydraulic power cylinder is mechanically connected with the main valve core of the multi-way valve, and the rear cylinder cover 48 of the servo hydraulic power cylinder is fixedly connected with the multi-way valve body 11.
The invention can be applied to a multi-way valve to control the main valve core in the multi-way valve, and can also be applied to other environments needing servo assistance, such as clutch assistance, brake assistance and the like of large-scale vehicles.
The hydraulic symbols (such as the oil inlet P3, the oil return port T3, the control oil port a3, the control oil port b3, and the like) used in the present invention are only for distinguishing the control oil ports, and are not limitations on the technical solution of the present invention, and the above embodiments do not impose any form of limitation on the shape, material, structure, and the like of the present invention, and any simple modification, equivalent change, and modification made on the above embodiments according to the technical substance of the present invention belong to the protection scope of the technical solution of the present invention.
Claims (10)
1. A servo-assisted hydraulic cylinder is characterized in that: the servo cylinder comprises a servo cylinder body, a piston valve sleeve and a valve core assembly, wherein the valve core assembly is connected in the piston valve sleeve in a sliding mode, the piston valve sleeve is connected in the servo cylinder body in a sliding mode and divides the interior of the servo cylinder body into a hydraulic cylinder control rod cavity and a hydraulic cylinder piston rod cavity, the valve core assembly comprises a slide valve core and a slide valve centering reset device, one end, located in the hydraulic cylinder control rod cavity, of the slide valve core is connected with a control rod used for providing motion input, and one end, located in the hydraulic cylinder piston rod cavity, of the piston valve sleeve is; when the control rod is in control input, the piston rod overcomes the external load resistance to follow the movement of the control rod; when the control rod does not control input, the spool of the slide valve returns to the neutral position under the action of the centering resetting device of the slide valve, and the piston valve sleeve is in a floating state, namely the piston rod moves along with the movement of an external load.
2. A servo-assisted hydraulic cylinder according to claim 1, wherein: an oil inlet P3, an oil return port T3, a control oil port a3 and a control oil port b3 are arranged in the piston valve sleeve, the control oil port a3 is communicated with a hydraulic cylinder control rod cavity through an oil duct, the control oil port b3 is communicated with the hydraulic cylinder piston rod cavity, and when the slide valve core reciprocates in the piston valve sleeve, the oil inlet P3, the oil return port T3, the control oil port a3 and the control oil port b3 are communicated or closed through the matching of the slide valve core and the piston valve sleeve.
3. A servo-assisted hydraulic cylinder according to claim 2, wherein: the slide valve spool and the piston valve pocket are of a slide valve type five-position four-way reversing valve structure, and five positions of the slide valve type five-position four-way reversing valve are respectively a middle position, a left stop position, a left reversing position, a right stop position and a right reversing position, namely:
when the oil inlet is in a middle position, the oil inlet P3 is cut off, and the control oil port a3, the control oil port b3 and the oil return port T3 are communicated;
when the left stop position is reached, the oil inlet P3 is cut off, the control oil port a3 is cut off, and the control oil port b3 is communicated with the oil return port T3;
when the direction is changed leftwards, the oil inlet P3 is communicated with the control oil port a3, and the control oil port b3 is communicated with the oil return port T3;
when the oil inlet is stopped at the right stop position, the oil inlet P3 is stopped, the control oil port b3 is stopped, and the control oil port a3 is communicated with the oil return port T3;
when the direction of the oil inlet is changed rightwards, the oil inlet P3 is communicated with the control oil port b3, and the control oil port a3 is communicated with the oil return port T3.
4. A servo-assisted hydraulic cylinder according to claim 3, wherein: when the slide valve type five-position four-way reversing valve is in a middle position, the covering amount of the oil inlet P3 is larger than or equal to the opening amount of the oil return port T3.
5. A servo-assisted hydraulic cylinder according to claim 3, wherein: the servo cylinder body is provided with a pilot oil inlet P1 and a pilot oil return port T1, an oil inlet groove P2 and an oil return groove T2 which are not communicated with each other are axially formed between the piston valve sleeve and the servo cylinder body, the oil inlet P3 of the piston valve sleeve is communicated with the pilot oil inlet P1 through the oil inlet groove P2, the oil return port T3 of the piston valve sleeve is communicated with the pilot oil return port T1 through the oil return groove T2, the piston valve sleeve is moved in the servo cylinder body, the oil inlet groove P2 is always communicated with the pilot oil inlet P1, and the oil return groove T2 is always communicated with the pilot oil return port T1.
6. A servo-assisted hydraulic cylinder according to claim 1, wherein: four areas are arranged between the piston valve sleeve and the servo cylinder body, namely a circumferential isolation area, an anti-rotation groove area, two oil groove areas which are not communicated with each other and an axial isolation area which separates the two oil groove areas, the two oil groove areas are respectively used as an oil inlet groove and an oil return groove, and the axial dimension of the oil inlet groove and the oil return groove is larger than the stroke of the piston valve sleeve.
7. A servo-assisted hydraulic cylinder according to claim 6, wherein: the piston valve sleeve and the servo cylinder body are respectively provided with an anti-rotation groove in an anti-rotation groove area, a flat key is arranged between the two anti-rotation grooves, and the piston valve sleeve and the servo cylinder body are connected through the flat key.
8. A servo-assisted hydraulic cylinder according to claim 1, wherein: the control rod arranged at one end of the spool of the sliding valve comprises a control rod connecting part and a spool connecting part, and the spool connecting part is detachably and fixedly connected with one end of the spool of the sliding valve.
9. A servo-assisted hydraulic cylinder according to any one of claims 1 to 8, wherein: fixedly connected with piston left end cover can be dismantled to piston valve barrel's one end, and fixedly connected with piston right end cover can be dismantled to piston valve barrel's the other end, and piston left end cover and piston right end cover can be threaded connection respectively at the both ends of piston valve barrel, and the cylinder cap before the servo jar of fixedly connected with can be dismantled to servo cylinder body's one end, and the cylinder cap behind the servo jar can be dismantled to servo cylinder body's the other end forms between piston left end cover and the servo jar cylinder cap the pneumatic cylinder control rod chamber forms between piston right end cover and the servo jar rear cylinder cap the pneumatic cylinder piston rod.
10. A servo-assisted hydraulic cylinder according to claim 9, wherein: the left end cover of the piston is provided with a stepped hole, one end of a control rod arranged at one end of the sliding valve core is connected in the stepped hole in a sliding mode, the stepped hole comprises a fine hole section and a coarse hole section, the coarse hole section of the stepped hole is provided with the sliding valve centering reset device, the sliding valve centering reset device comprises a sliding valve reset spring and two spring seats, the two spring seats are connected in the coarse hole section in a sliding mode, the end face of one spring seat is abutted to the end face of the coarse hole section, the end face of the other spring seat is abutted to the end face of a shoulder of the sliding valve core, and the distance between the two spring seats is the maximum relative displacement of the sliding valve core relative to the servo power cylinder piston valve sleeve.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010455580.9A CN111486149A (en) | 2020-05-26 | 2020-05-26 | Servo power-assisted hydraulic cylinder |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010455580.9A CN111486149A (en) | 2020-05-26 | 2020-05-26 | Servo power-assisted hydraulic cylinder |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112112793A (en) * | 2020-09-15 | 2020-12-22 | 秦皇岛卓飞科技有限公司 | Large-flow ultrahigh-pressure hydraulic pump |
| CN112177842A (en) * | 2020-09-27 | 2021-01-05 | 秦皇岛卓飞科技有限公司 | Linear hydraulic pneumatic motor |
| CN113107918A (en) * | 2021-04-22 | 2021-07-13 | 浙江工业大学 | Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on clearance compensation displacement amplification coupling |
-
2020
- 2020-05-26 CN CN202010455580.9A patent/CN111486149A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112112793A (en) * | 2020-09-15 | 2020-12-22 | 秦皇岛卓飞科技有限公司 | Large-flow ultrahigh-pressure hydraulic pump |
| CN112177842A (en) * | 2020-09-27 | 2021-01-05 | 秦皇岛卓飞科技有限公司 | Linear hydraulic pneumatic motor |
| CN113107918A (en) * | 2021-04-22 | 2021-07-13 | 浙江工业大学 | Two-dimensional half-bridge electro-hydraulic proportional reversing valve based on clearance compensation displacement amplification coupling |
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