CN111102259A - Two-dimensional pulse width modulation mechanism - Google Patents
Two-dimensional pulse width modulation mechanism Download PDFInfo
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- CN111102259A CN111102259A CN201811247484.4A CN201811247484A CN111102259A CN 111102259 A CN111102259 A CN 111102259A CN 201811247484 A CN201811247484 A CN 201811247484A CN 111102259 A CN111102259 A CN 111102259A
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- 230000007246 mechanism Effects 0.000 title claims abstract description 23
- 230000005540 biological transmission Effects 0.000 claims abstract description 46
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- QNRATNLHPGXHMA-XZHTYLCXSA-N (r)-(6-ethoxyquinolin-4-yl)-[(2s,4s,5r)-5-ethyl-1-azabicyclo[2.2.2]octan-2-yl]methanol;hydrochloride Chemical compound Cl.C([C@H]([C@H](C1)CC)C2)CN1[C@@H]2[C@H](O)C1=CC=NC2=CC=C(OCC)C=C21 QNRATNLHPGXHMA-XZHTYLCXSA-N 0.000 claims description 29
- 230000009471 action Effects 0.000 claims description 8
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- 239000010729 system oil Substances 0.000 claims description 3
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- 208000028659 discharge Diseases 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
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- 230000002441 reversible effect Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
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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
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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
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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Abstract
The two-dimensional pulse width modulation mechanism is characterized in that a transmission shaft shifting fork shifts the valve core through a roller component, so that the valve core axially slides while circumferentially rotating in the valve sleeve, the rotation of the valve core and the axial sliding are relatively independent, and a zero position spring is arranged between the valve core and the transmission shaft and is in a compressed state; one end of the transmission shaft is connected with the transmission mechanism; the valve core is arranged in the central through hole of the valve sleeve; the excircle of the valve sleeve is provided with four annular grooves which are respectively a control oil groove, an oil outlet groove, an oil inlet groove and an oil return groove from left to right, and a plurality of same radial holes are uniformly formed in the control oil groove, the oil outlet groove, the oil inlet groove and the oil return groove; a central flow passage is axially arranged at the center of the valve core, and the first circular through hole and the second circular through hole are communicated through the central flow passage of the valve core; two lines of staggered triangular flow distribution windows are arranged on the second shoulder of the valve core and are respectively a left triangular flow distribution window and a right triangular flow distribution window, the vertexes of the windows are in the same plane, and the plane is perpendicular to the axis of the valve core.
Description
Technical Field
The invention belongs to the technical field of fluid transmission and control, relates to a two-dimensional pressure feedback flow distribution mechanism, and particularly relates to a two-dimensional pulse width modulation mechanism.
Background
In the working process of the plunger pump, the plunger makes reciprocating motion in the cylinder body, so that the change of the sealed working volume is caused to realize oil absorption and oil discharge. Each plunger cavity of the axial plunger pump is periodically switched back and forth between the oil suction port and the oil discharge port, and the switching process of the oil ports needs to be realized through a flow distribution mechanism of the pump.
According to the flow distribution mode, the axial plunger pump is mainly divided into valve flow distribution and end face flow distribution. The valve flow distribution mainly realizes flow distribution by means of one-way valves, the two one-way valves are respectively arranged at an oil inlet and an oil outlet of the pump, and the plunger cavity respectively opens the one-way valves of the corresponding oil ports in the oil suction and discharge stage, so that oil suction and discharge are realized. The valve flow distribution mode does not need the cylinder body to rotate, and is generally used for a single-plunger pump. The one-way valve has certain opening pressure, and certain hysteresis exists in response, so that the self-sucking capacity of the pump is poor, cavitation is easily caused, and the rotating speed of the pump is limited. The end face flow distribution is the main flow distribution mode of the existing plunger pump, and the flow distribution mode requires that a cylinder body of the plunger pump rotates to enable a plunger cavity to be alternately communicated with an oil suction window and an oil discharge window on a flow distribution plate for oil suction and discharge. The plunger pump cylinder body is provided with a plurality of plunger holes, the diameter of the cylinder body is larger, and the high pressure and high rotating speed have higher design requirements on the key friction pair of the cylinder body and the valve plate; in order to reduce the starting time of the motor and increase the response speed of the system, the traditional method is to install an unloading valve at the outlet of the hydraulic pump, which increases the design and processing complexity of a mechanical system and a control system.
The existing two-dimensional (2D) pump adopts valve banks such as a two-dimensional unloading valve, a two-dimensional pressure stabilizing valve and the like to realize the regulation of pressure and flow, and has more parts, more control and regulation positions and larger pressure flow pulsation.
Disclosure of Invention
The invention provides a two-dimensional pressure feedback flow distribution mechanism which is a two-dimensional pulse width modulation mechanism and has the advantages of novel and compact structure, small volume, light weight, simple transmission, no friction pair, easy realization of high pressure and high rotating speed and realizes flow distribution by utilizing a valve core two-degree-of-freedom structure, and aims to overcome the problems of poor self-absorption property, low rotating speed, large cylinder body diameter, high technical requirement on friction pairs, complex mechanical system and control system and the like caused by valve flow distribution and end surface flow distribution of a plunger pump and overcome the defect that the conventional two-dimensional (2D) pump adjusts the flow distribution mode of a plurality of hydraulic valves. The invention not only solves the defects of the plunger pump flow distribution, but also simplifies and optimizes the flow distribution mechanism of the two-dimensional (2D) pump, simultaneously can save the unloading valve at the outlet of the hydraulic pump, can realize zero-pressure starting of the hydraulic pump in a hydraulic system, and is suitable for the flow distribution of the hydraulic pump, a motor and the like.
The technical scheme adopted by the invention is as follows:
the two-dimensional pulse width modulation mechanism is characterized in that: the automatic valve comprises a transmission shaft, a zero position spring, a roller shaft, a left roller assembly, a right roller assembly, a front concentric ring, a valve core, a valve sleeve, a rear concentric ring and a valve core plug. The transmission shaft shifting fork is matched with the roller component to shift the valve core through the roller shaft, so that the valve core rotates in the circumferential direction in the valve sleeve and slides axially, the rotation of the valve core and the axial sliding are relatively independent, the front concentric ring and the rear concentric ring are fixedly connected to two ends of the valve sleeve respectively, and the zero-position spring is arranged between the valve core and the transmission shaft and is in a compressed state.
One end of the transmission shaft is a cylindrical end and is connected with the transmission mechanism; the other end of the transmission shaft is in a door frame shape and is connected with two U-shaped shifting forks, and the shifting fork surfaces are incomplete cylindrical surface tracks extending axially and are matched with the left roller assembly and the right roller assembly to enable the valve core to axially slide while rotating circumferentially; the axial middle end surface of the transmission shaft is provided with a circular groove for fixing the zero spring.
Two flat end faces of the zero-position spring are respectively fixed at the circular groove of the transmission shaft and the stepped shaft at the left end of the valve core, the zero-position spring is in a compressed state in the initial and working processes, the valve core is ensured to be at the rightmost end in the initial state, and the zero position of the valve core is kept.
The roller shaft is a stepped cylindrical shaft, a shoulder is arranged in the middle of the stepped cylindrical shaft, and the diameter of the middle cylinder is larger than that of the cylinders at the two sides; the middle shoulder shaft is inserted into the cylindrical hole at the left end of the valve core and is fixedly connected with the cylindrical hole at the left end of the valve core, and the shafts at the two ends are respectively inserted into the central circular holes of the left roller assembly and the right roller assembly and are fixedly connected with the central circular holes of the left roller assembly and the right roller assembly.
The right roller assembly and the left roller assembly are completely the same in structure and comprise a bearing sleeve and a deep groove ball bearing, the outer portion of the bearing sleeve is a spherical surface, the inner portion of the bearing sleeve is a circular hole, two ends of the bearing sleeve are flat end surfaces, an inner hole of the bearing sleeve is sleeved on the outer circle of the deep groove ball bearing and fixedly connected with the outer circle of the deep groove ball bearing, and the spherical surface of the bearing sleeve is matched with the cylindrical surface.
The front concentric ring is circular, two end faces are planes, the outer circle of the front concentric ring is fixedly connected with the valve sleeve, and the inner hole is sleeved on the shaft at the left end of the valve core.
The back concentric ring is circular, two end faces are planes, an inner hole is provided with a stepped hole to provide an avoiding space for a second circular through hole of the valve core, the outer circle of the back concentric ring is fixedly connected with the valve sleeve, and the inner hole is sleeved on a shaft at the right end of the valve core.
The inner hole of the valve sleeve is a central through hole and is matched with the valve core, and a front stepped hole and a rear stepped hole are respectively arranged at two ends and are respectively fixedly connected with a front concentric ring and a rear concentric ring; the excircle of valve barrel is equipped with four ring channels and is respectively from left to right control oil groove, play oil groove, inlet tank and oil gallery, evenly is equipped with a plurality of the same radial control oilholes on the control oil groove, evenly is equipped with a plurality of the same radial oil outlet on going out the oil groove, evenly is equipped with a plurality of the same radial rhombus flow distribution windows on the inlet tank, and the summit of rhombus flow distribution window just this plane perpendicular to case axis in the coplanar evenly is equipped with a plurality of the same radial oil gallery on the oil gallery.
The leftmost end of the valve core is provided with a step shaft for mounting a zero position spring, and the right side of the step shaft is provided with a roller shaft circular through hole which is fixedly connected with the roller shaft and used for transmitting torque to the valve core to enable the valve core to rotate; the valve core is provided with three shoulders, namely a first shoulder, a second shoulder and a third shoulder in sequence from left to right, a first circular through hole is formed in the radial direction of a valve core shaft between the first shoulder and the second shoulder, a second circular through hole is formed in the radial direction of the valve core shaft close to the right end face of the third shoulder, a central flow passage is axially formed in the center of the valve core, a valve core plug is used for plugging the central flow passage, and the first circular through hole and the second circular through hole are communicated through the central flow passage of the valve core; two lines of staggered triangular flow distribution windows are arranged on the second shoulder of the valve core and are respectively a left triangular flow distribution window and a right triangular flow distribution window, the vertexes of the windows are in the same plane, and the plane is perpendicular to the axis of the valve core.
Preferably, the spherical surface of the outer circle of the bearing sleeve is in clearance fit with the U-shaped shifting fork of the transmission shaft, the spherical surface of the outer circle of the bearing sleeve is in unilateral contact with the shifting fork of the transmission shaft when stressed, the transmission shaft can rotate in a forward and reverse direction, the transmission shaft drives the valve core to rotate through the left roller assembly, the right roller assembly and the roller shaft, and the valve core slides axially under the action of hydraulic pressure to drive the bearing sleeve to roll axially on the U-.
Preferably, the outer circles of the front concentric ring and the rear concentric ring are fixedly connected in a front stepped hole and a rear stepped hole of two end faces of the valve sleeve respectively, an inner hole of the front concentric ring is sleeved on a shaft at the left end of the valve core and is sealed by a gap, and an inner hole of the rear concentric ring is sleeved on a shaft at the right end of the valve core and is sealed by a gap.
Preferably, the valve core is rotatably arranged in the valve sleeve, the front concentric ring and the first shoulder of the valve core seal the inner cavity of the valve sleeve to form a control cavity, the control cavity is communicated with the control oil groove through the control oil hole, and the control oil groove is communicated with control pressure oil; the valve core first shoulder and the second shoulder seal the inner cavity of the valve sleeve to form a high-pressure cavity, the high-pressure cavity is communicated with the oil outlet groove through the oil outlet hole and is communicated with the oil inlet groove through the rhombic flow distribution window, high-pressure oil of the hydraulic pump is introduced into the oil inlet groove, and the oil outlet groove is communicated with a system oil way; the second shoulder and the third shoulder of the valve core seal the inner cavity of the valve sleeve to form a low-pressure cavity, the low-pressure cavity is communicated with the oil return groove through an oil return hole, and the oil return groove is communicated with a low-pressure oil tank; the third shoulder of the valve core and the back concentric ring seal the inner cavity of the valve sleeve to form a feedback cavity, the feedback cavity is communicated with the high-pressure cavity through the first circular through hole, the central flow channel and the second circular through hole of the valve core, and the pressures of the two cavities are the same; the valve sleeve controls the oil groove, the oil outlet groove, the oil inlet groove and the oil return groove to be not communicated with each other outside the valve sleeve. Two rows of staggered triangular flow distribution windows are formed in the second shoulder of the valve core and are respectively a left triangular flow distribution window and a right triangular flow distribution window, the rhombic flow distribution window of the valve sleeve is positioned on the motion track of the second shoulder of the valve core, the valve core axially slides under the action of hydraulic pressure while rotating at a constant speed in the valve sleeve, and the ratio of the left triangular flow distribution window and the right triangular flow distribution window of the valve core to the flow distribution time of the rhombic flow distribution window of the valve sleeve is changed, so that the flow distribution of the discharged oil is changed.
The specific working process is as follows:
the valve core is driven by the transmission shaft to rotate at a constant speed, and two staggered rows of triangular flow distribution windows arranged on the second shoulder of the valve core and the rhombic flow distribution windows of the valve sleeve groove rotate circumferentially and relatively; the liquid pressure in the control cavity acts on the annular area of the left end face of the first shoulder of the valve core to generate axial rightward thrust on the valve core, the liquid pressure in the feedback cavity acts on the annular area of the right end face of the third shoulder of the valve core to generate axial leftward thrust on the valve core, the zero setting spring is compressed to generate axial rightward thrust on the valve core, if the resultant force of the axial rightward thrust and the axial spring force of the valve core is greater than the axial leftward thrust, the valve core slides axially rightwards, and if the resultant force of the axial rightward thrust and the axial spring force of the valve core is less than the axial leftward thrust, the valve core slides axially left. When the forces at the two ends of the valve core are balanced, the valve core stays at a certain working position of the valve sleeve, and the left triangular flow distribution window, the right triangular flow distribution window and the rhombic flow distribution window of the valve sleeve are alternately communicated to form periodic change along with the rotation of the valve core.
When the valve core is in a zero position, the valve core is positioned at the rightmost end in the valve sleeve, the oil inlet groove of the valve sleeve is communicated with the oil outlet groove to the maximum extent, and the oil inlet groove is not communicated with the oil return groove, so that all high-pressure oil of the pump flows into the system before the pressure of the system is built, the pressure of the system is built rapidly, and the valve core is in a balanced state until the pressure flow of the system is stable. When the valve core is positioned at the leftmost end in the valve sleeve, the oil inlet groove of the valve sleeve is not communicated with the oil outlet groove, the oil inlet groove is communicated with the oil return groove to the maximum extent, high-pressure oil of the pump flows into the oil tank completely, and the hydraulic pump is in an unloading state; at the moment, if the hydraulic pump stops working, the system is in a pressure maintaining state, when the hydraulic pump starts under pressure again, the valve sleeve oil outlet groove is directly communicated with the oil return groove, namely, the oil outlet of the hydraulic pump is directly communicated with the oil tank, and the hydraulic pump can be started almost under zero load under the condition of system pressure maintaining.
When the pressure of the control cavity is unchanged, the pressure of the system is unchanged, and the flow required by the system is changed, the pressure of the system is correspondingly slightly changed, so that the pressures of the high-pressure cavity and the feedback cavity are correspondingly changed, the valve core axially slides under the action of axial resultant force, the valve core axially slides to cause the ratio of the time required for the left triangular flow distribution window and the right triangular flow distribution window of the valve core to alternately sweep the rhombic flow distribution window of the valve sleeve to the total time to be correspondingly changed, the oil outlet flow and the oil return flow are correspondingly changed, the flow entering the system is correspondingly changed, and the pressure of the feedback cavity is correspondingly changed until the valve core reaches a new balance state; when the system pressure needs to be changed, the control cavity pressure is changed, the valve core slides axially under the action of axial resultant force, the ratio of the time required for the valve core left triangular flow distribution window and the time required for the valve core right triangular flow distribution window to alternately sweep through the valve sleeve rhombic flow distribution window to the total time respectively changes correspondingly, the oil outlet flow and the oil return flow change correspondingly, the flow entering the system changes correspondingly, the feedback cavity pressure changes correspondingly, and the system pressure rises until the axial resultant force of the valve core is balanced again, so that the valve core reaches a new balance state.
The axial sliding of the valve core changes the proportion of the flow distribution time, thereby changing the oil flow entering the hydraulic system. Therefore, the manner in which the system flow is regulated using this configuration can be viewed as pulse width modulation controlled by the spool position. Because the valve core has high rotation speed, a plurality of triangular flow distribution windows are arranged on the circumference of the valve core, and corresponding rhombic flow distribution windows are arranged on the circumference of the valve sleeve, the frequency of pulse width modulation is high, and pressure pulsation and flow pulsation hardly appear in the system.
The valve core double-freedom-degree structure means that the valve core can axially slide while circumferentially rotating, and the circumferential rotation and the axial sliding of the valve core are mutually independent; the rotation of the valve core is caused by the fact that external torque is transmitted to the torque of the valve core through the transmission shaft, and the axial sliding of the valve core is caused by the fact that the two ends of the valve core are stressed differently.
The axial direction refers to the direction in which the central axis of the valve core is positioned or parallel to the central axis of the valve core; the radial direction refers to the direction perpendicular to the central axis of the valve core; the circumferential direction refers to the direction in which the spool rotates about the central axis.
The time required for the left triangular flow distribution window and the right triangular flow distribution window of the valve core to alternately sweep through the rhombic flow distribution window of the valve sleeve respectively refers to the coincidence time from opening to closing of the left triangular flow distribution window and the right triangular flow distribution window of the valve core and the rhombic flow distribution window of the valve sleeve in any period.
The invention has the beneficial effects that:
1. by using the traditional slide valve structure for reference, the novel flow distribution mode of the valve core double-free structure is adopted, the structure is simple, the performance is reliable, the axial direction of the valve core is provided with pressure feedback, and the system pressure and the output flow can be adjusted simultaneously.
2. The rotation of the valve core enables the frequency of pulse width modulation to be very high, and pressure and flow pulsation in the system are greatly improved.
3. The two-dimensional (2D) pump valve group control flow distribution in the prior art is replaced, the adjusting mechanism is reduced, and the design is simplified.
4. Compared with the end surface flow distribution of the traditional plunger pump, the end surface flow distribution device cancels a friction pair structure, reduces abrasion and improves efficiency.
5. An almost zero load start of the hydraulic pump in the high pressure system can be achieved.
Drawings
Fig. 1 is a schematic structural diagram of a two-dimensional pulse width modulation mechanism.
Fig. 2 is a schematic view of the structure of the valve sleeve.
Fig. 2a is a cross-sectional view C-C of fig. 2.
Fig. 3 is a schematic structural diagram of the valve core.
Fig. 3a is a cross-sectional view D-D of fig. 3.
Fig. 4 is a schematic structural view of the transmission shaft.
Fig. 5 is a schematic structural diagram of the right roller assembly.
Fig. 6 is a schematic structural view of the roller shaft.
Fig. 7a is a schematic view of the valve sleeve flow distribution window.
Fig. 7b is a schematic view of a valve core flow distribution window.
Fig. 7c is a schematic diagram of the flow distribution principle when the valve core is in the neutral position.
Fig. 7d is a schematic diagram of the flow distribution principle when the valve core moves down.
Detailed Description
The technical solution of the present invention is further explained with reference to fig. 1 to 7 d.
The two-dimensional pulse width modulation mechanism is characterized in that: the valve consists of a transmission shaft 1, a zero position spring 2, a roller shaft 3, a left roller assembly 4, a right roller assembly 5, a front concentric ring 6, a valve sleeve 7, a valve core 8, a rear concentric ring 9 and a valve core plug 10. The shifting fork of the transmission shaft 1 is matched with the left roller assembly 4 and the right roller assembly 5 to shift the valve core 8 through the roller shaft 3, so that the valve core 8 rotates in the circumferential direction and slides axially in the valve sleeve 7, the rotation of the valve core 8 is relatively independent of the axial sliding, the front concentric ring 6 and the rear concentric ring 9 are fixedly connected to two ends of the valve sleeve 7 respectively, and the zero-position spring 2 is arranged between the valve core 8 and the transmission shaft 1 and is in a compressed state.
One end of the transmission shaft 1 is a cylindrical end and is connected with a transmission mechanism, so that the transmission shaft 1 rotates; the other end of the transmission shaft 1 is in a door frame shape and is connected with two U-shaped shifting forks, the shifting fork surfaces are incomplete cylindrical surface rails extending axially and are matched with the left roller assembly 4 and the right roller assembly 5, so that the valve core 8 axially slides while rotating in the circumferential direction; the axial middle end surface of the transmission shaft 1 is provided with a circular groove for fixing the zero position spring 2.
Two flat end faces of the zero-position spring 2 are respectively fixed at a groove of the transmission shaft 1 and a stepped shaft at the left end of the valve core 8, the zero-position spring 2 is in a compressed state in the initial and working processes, the valve core 8 is ensured to be at the rightmost end in the initial state, and the zero position of the valve core 8 is kept.
The roller shaft 3 is a stepped cylindrical shaft, a shoulder is arranged in the middle of the stepped cylindrical shaft, and the diameter of the middle cylinder is larger than that of the cylinders at the two sides; the middle shoulder shaft is inserted into the cylindrical hole at the left end of the valve core 8 and is fixedly connected with the cylindrical hole, and the two end shafts are respectively inserted into the central round holes of the left roller assembly 4 and the right roller assembly 5 and are fixedly connected with the central round holes.
The right roller assembly 5 and the left roller assembly 4 are identical in structure and comprise a bearing sleeve 51 and a deep groove ball bearing 52, the outer portion of the bearing sleeve 51 is a spherical surface, the inner portion of the bearing sleeve 51 is a circular hole, two ends of the bearing sleeve are flat end faces, an inner hole of the bearing sleeve 51 is sleeved on the outer circle of the deep groove ball bearing 52 and fixedly connected with the outer circle, and the spherical surface of the bearing sleeve 51 is matched with the cylindrical surface of a U-shaped shifting fork of the.
The front concentric ring 6 is circular, two end faces are planes, the outer circle of the front concentric ring 6 is fixedly connected with the valve sleeve 7, and an inner hole is sleeved on the left end shaft of the valve core 8.
The back concentric ring 9 is circular, two end faces are planes, an inner hole is provided with a stepped hole to provide an avoiding space for a second circular through hole B2 of the valve core 8, the outer circle of the back concentric ring 9 is fixedly connected with the valve sleeve 7, and the inner hole is sleeved on a shaft at the right end of the valve core 8.
The inner hole of the valve sleeve 7 is a central through hole and is matched with the valve core 8, and a front stepped hole and a rear stepped hole are respectively arranged at two ends and are respectively fixedly connected with the front concentric ring 6 and the rear concentric ring 9; the excircle is equipped with four ring channels and is respectively from left to right control oil groove K, oil outlet tank A, oil feed tank P and oil return tank T, evenly be equipped with a plurality of the same radial control oilhole K on the control oil groove K, evenly be equipped with a plurality of the same radial oil outlet a on the oil outlet tank A, evenly be equipped with a plurality of the same radial rhombus flow distribution windows P on the oil feed tank P, the summit of rhombus flow distribution window P just this plane perpendicular to case axis in the coplanar, evenly be equipped with a plurality of the same radial oil return hole T1 on the oil return tank T.
A step shaft is arranged at the leftmost end of the valve core 8 and used for mounting the zero position spring 2, and a roller shaft circular through hole is formed in the right side of the step shaft and fixedly connected with the roller shaft 3 and used for transmitting torque to the valve core 8 to enable the valve core 8 to rotate; the valve core 8 is provided with three shoulders which are sequentially provided with a first shoulder 81, a second shoulder 82 and a third shoulder 83 from left to right, a first circular through hole B1 is arranged in the radial direction of a valve core shaft between the first shoulder 81 and the second shoulder 82, a second circular through hole B2 is arranged in the radial direction of the valve core shaft close to the right end face of the third shoulder 83, a central flow passage B is arranged in the central axial direction of the valve core 8, the central flow passage port is blocked by a valve core plug 10, and the first circular through hole B1 is communicated with the second circular through hole B2 through the central flow passage B of the valve core 8; two staggered triangular flow distribution windows are arranged on the second shoulder 82 of the valve core 8, namely a left triangular flow distribution window p1 and a right triangular flow distribution window p2, and the vertexes of the windows are in the same plane which is perpendicular to the axis of the valve core.
The spherical surface of the excircle of the bearing sleeve 51 is in clearance fit with the U-shaped shifting fork of the transmission shaft 1, and the bearing sleeve 51 is in unilateral contact with the U-shaped shifting fork of the transmission shaft 1 when stressed, so that forward and reverse rotation can be realized, the transmission shaft 1 drives the valve core 8 to rotate through the left roller assembly 4, the right roller assembly 5 and the roller shaft 3, and the valve core 8 axially slides under the action of hydraulic pressure to drive the bearing sleeve 51 to axially roll on the U-shaped shifting fork of the transmission shaft.
The outer circles of the front concentric ring 6 and the rear concentric ring 9 are fixedly connected in a front stepped hole and a rear stepped hole of two end faces of the valve sleeve 7 respectively, an inner hole of the front concentric ring 6 is sleeved on a shaft at the left end of the valve core 8 and is sealed by a gap, and an inner hole of the rear concentric ring 9 is sleeved on a shaft at the right end of the valve core 8 and is sealed by a gap.
The valve core 8 is rotatably arranged in the valve sleeve 7, the front concentric ring 6 and the first valve core shoulder 81 seal the inner cavity of the valve sleeve 7 to form a control cavity K1, the control cavity K1 is communicated with the control oil groove K through a control oil hole K, and the control oil groove K is communicated with control pressure oil; the first shoulder 81 and the second shoulder 82 of the valve core 8 seal the inner cavity of the valve sleeve 7 to form a high-pressure cavity A1, the high-pressure cavity A1 is communicated with an oil outlet groove A through an oil outlet hole a, and is communicated with an oil inlet groove P through a rhombic flow distribution window P, the oil inlet groove P is communicated with high-pressure oil of a hydraulic pump, and the oil outlet groove A is communicated with a system oil way; the second shoulder 82 and the third shoulder 83 of the valve core 8 seal the inner cavity of the valve sleeve 7 to form a low-pressure cavity T1, the low-pressure cavity T1 is communicated with an oil return groove T through an oil return hole T1, and the oil return groove T is communicated with a low-pressure oil tank; the third shoulder 83 of the valve core 8 and the rear concentric ring 9 seal the inner cavity of the valve sleeve 7 to form a feedback cavity A2, the feedback cavity A2 is communicated with the high-pressure cavity A1 through a first circular through hole B1, a central flow passage B and a second circular through hole B2 of the valve core 8, and the pressures of the two cavities are the same; the valve sleeve control oil groove K, the oil outlet groove A, the oil inlet groove P and the oil return groove T are not communicated with each other outside the valve sleeve. Two staggered triangular flow distribution windows, namely a left triangular flow distribution window p1 and a right triangular flow distribution window p2, are formed in the second shoulder 82 of the valve core 8, the rhombic flow distribution window p of the valve sleeve 7 is positioned on the motion track of the second shoulder 82 of the valve core 8, the valve core 8 axially slides under the action of hydraulic pressure while rotating at a constant speed in the valve sleeve 7, so that the ratio of the flow distribution time of the left triangular flow distribution window p1 and the flow distribution time of the right triangular flow distribution window p2 of the valve core 8 to the rhombic flow distribution window p of the valve sleeve 7 is changed, and the flow distribution of the discharged oil is changed to realize flow distribution.
The working principle of the embodiment is as follows:
the valve core 8 is driven by the transmission shaft 1 to rotate at a constant speed, and the left triangular flow distribution window p1 and the right triangular flow distribution window p2 which are arranged in a staggered mode on the second shoulder 82 of the valve core 8 and the rhombic flow distribution window p of the valve sleeve 7 rotate relatively in the circumferential direction; the liquid pressure in the control chamber K1 acts on the annular area S1 of the left end surface of the first land 81 of the valve core 8 to generate axial rightward thrust to the valve core 8, the liquid pressure in the feedback chamber A2 acts on the annular area S2 of the right end surface of the third land 83 of the valve core 8 to generate axial leftward thrust to the valve core 8, the zero-setting spring 2 is compressed to generate axial rightward thrust to the valve core 8, if the resultant force of the axial rightward thrust and the spring force of the valve core 8 is greater than the axial leftward thrust, namely the resultant force of the left end of the valve core 8 is greater than the resultant force of the right end, the valve core 8 slides axially rightward, if the resultant force of the axial rightward thrust and the spring force of the valve core 8 is less than the axial leftward thrust, namely the resultant force of the left end of the valve core 8 is less than the resultant force of the right end, the valve core 8 slides axially leftward, and if the resultant force of the, an equilibrium state is established.
In order to explain the flow distribution principle of the two-dimensional pulse width modulation mechanism, the left triangular flow distribution window p1, the right triangular flow distribution window p2 and the diamond-shaped flow distribution window p of the valve sleeve 7 of the valve core 8 are circumferentially expanded and simplified into a schematic diagram, such as fig. 7a, 7b, 7c and 7 d. The left and right linear motion of the valve core in the principle schematic diagram represents the circumferential rotation of the valve core in the structural schematic diagram, and the up and down vertical motion of the valve core in the principle schematic diagram represents the axial sliding of the valve core in the structural schematic diagram. In fig. 7a and 7b, P0 is an oil inlet, an equivalent oil inlet groove P, a0 is an oil outlet, an equivalent oil outlet groove a, T0 is an oil return opening, and an equivalent oil return groove T.
The valve core 8 can freely rotate and axially slide in the valve sleeve 7, along with the rotation of the valve core 8, the left triangular flow distribution window p1, the right triangular flow distribution window p2 and the rhombic flow distribution window p of the valve sleeve 7 are alternately communicated and periodically changed, because the left triangular flow distribution window p1, the right triangular flow distribution window p2 and the rhombic flow distribution window p of the valve sleeve 7 are in a large number, the gradient of the valve port area is large, so that the influence of the valve port opening degree on the flow passing through the valve port is small, the flow through the valve port can be considered as an amount that is independent of the opening degree of the valve port and is only dependent on the opening time of the valve port, namely, the ratio of the time required for the left triangular flow distribution window p1 and the right triangular flow distribution window p2 of the valve core 8 to alternately sweep the rhombic flow distribution window p of the valve sleeve 7 in any period to the total time is the distribution ratio of the oil inlet flow, and the oil outlet flow and the oil return flow are distributed according to the ratio;
as shown in fig. 7c and 7d, the ordinate is the flow Q of the oil inlet P0, the abscissa is the time T, and within any cycle time Δ T, the time Δ T1 required by the left triangular flow distribution window P1 of the valve core 8 to sweep through the rhombic flow distribution window P of the valve sleeve 7, the time Δ T2 required by the right triangular flow distribution window P2 of the valve core 8 to sweep through the rhombic flow distribution window P of the valve sleeve 7, the flow of the oil outlet a0 is Q · Δ T1/Δ T, and the flow of the oil return port T0 is Q · Δ T2/Δ T. As can be seen by comparing fig. 7c and 7d, the axial sliding of the spool changes the ratio of Δ t1 and Δ t2, thereby changing the flow of oil into the hydraulic system, and therefore, the manner in which the flow of the system is regulated by this structure can be regarded as pulse width modulation controlled by the position of the spool. Because the valve core 8 rotates fast, a plurality of left and right triangular flow distribution windows p1 and p2 are arranged on the circumference of the valve core 8, and the corresponding rhombic flow distribution window p is arranged on the circumference of the valve sleeve 7, the frequency of pulse width modulation is very high, and pressure pulsation and flow pulsation hardly appear in the system.
When the valve core 8 is in a zero position, the valve core 8 is at the rightmost end in the valve sleeve 7, the oil inlet P0 is communicated with the oil outlet A0 to the maximum extent, and the oil inlet P0 is not communicated with the oil return port T0, so that all high-pressure oil of the hydraulic pump flows into the system before the pressure of the system is built, the pressure of the system is built quickly, and the valve core is in a balanced state until the pressure flow of the system is stable. When the valve core 8 is positioned at the leftmost end in the valve sleeve 7, the oil inlet P0 is not communicated with the oil outlet A0, the oil inlet P0 is communicated with the oil return port T0 to the maximum extent, high-pressure oil of the hydraulic pump completely flows into the oil tank, and the hydraulic pump is in an unloading state; at the moment, if the hydraulic pump stops working, the system is in a pressure maintaining state, when the hydraulic pump starts under pressure again, the oil inlet P0 is directly communicated with the oil return port T0, namely, the oil outlet of the hydraulic pump is directly communicated with the oil tank, and the hydraulic pump can be started under almost zero load in the pressure maintaining state of the system.
If the control pressure is unchanged, the system pressure is unchanged, and the flow required by the system is changed, the system pressure is slightly changed. When the required flow of the system is increased and the pressure of the system is reduced, the pressure of the high-pressure oil chamber A1 and the pressure of the feedback chamber A2 are reduced, the pressure of the control chamber K1 is unchanged, the balance state of the valve core 8 is broken, the resultant force of the left end of the valve core 8 is greater than the resultant force of the right end of the valve core 8, the valve core 8 slides to the right in the axial direction, the opening degrees of the oil inlet P0 and the oil outlet A0 are increased, the opening degrees of the oil inlet P0 and the oil return port T0 are reduced, the time of the left triangular flow distribution window P1 of the valve core 8 sweeping the rhombic flow distribution window P of the valve sleeve 7 is prolonged, the time of the right triangular flow distribution window P2 of the valve core 8 sweeping the rhombic flow distribution window P of the valve sleeve 7 is shortened, the flow of the oil outlet A0 is increased to supply energy, the system. On the contrary, when the required flow of the system is reduced and the system pressure is increased, the pressure of the high-pressure oil cavity a1 and the feedback cavity a2 is increased, the pressure of the control cavity K1 is unchanged, the balance state of the valve core 8 is broken, the resultant force of the left end of the valve core 8 is smaller than the resultant force of the right end, the valve core 8 slides axially leftwards, at this time, the opening degrees of the oil inlet P0 and the oil outlet a0 are reduced, the opening degrees of the oil inlet P0 and the oil return port T0 are increased, the time of the valve core 8 left triangular flow distribution window P1 sweeping the valve sleeve 7 rhombic flow distribution window P is shortened, the time of the valve core 8 right triangular flow distribution window P2 sweeping the valve sleeve 7 rhombic flow distribution window P is lengthened, the flow of the oil return port T0 is increased to enable more oil to flow back to the oil tank, the flow of the oil outlet a0 is reduced, the inflow system flow is reduced until the system pressure, the valve cartridge 8 reaches the equilibrium state again.
If the system pressure needs to be changed, the original balance state of the valve core is broken and a new balance state is established by changing the pressure value of the control oil port. When the pressure of the control cavity K1 rises, the resultant force of the left end of the valve core 8 is larger than the resultant force of the right end, the valve core 8 slides to the right in the axial direction, at this time, the opening degrees of the oil inlet P0 and the oil outlet A0 are increased, the opening degrees of the oil inlet P0 and the oil return port T0 are decreased (until the valve core is completely closed), the pressure of the oil outlet A0 rises along with the increase of the flow of oil entering the system, and the valve core reaches a new balance state until the resultant forces of. When the pressure of the control cavity K1 is reduced, the resultant force of the left end of the valve core 8 is smaller than the resultant force of the right end, the valve core 8 slides leftwards in the axial direction, at this time, the opening degrees of the oil inlet P0 and the oil outlet a0 become smaller (until the valve core is completely closed), the opening degrees of the oil inlet P0 and the oil return port T0 become larger, the pressure of the oil outlet a0 is reduced along with the reduction of the flow of oil entering the system, and the valve core reaches a new balance state until the resultant forces.
By reasonably setting the annular area S1 of the left end surface of the first shoulder 81 of the valve core 8, the annular area S2 of the right end surface of the third shoulder 83 of the valve core 8 and the stiffness of the zero position spring, the proportional relation between the outlet pressure of the two-dimensional pulse width modulation mechanism and the pressure of the control oil port can be established, so that the outlet pressure value can be adjusted by changing the value of the pressure of the control oil port, and the pressure and the flow of the system can be adjusted.
The embodiments described in this specification are merely illustrative of implementations of the inventive concept and the scope of the present invention should not be considered limited to the specific forms set forth in the embodiments but rather by the equivalents thereof as may occur to those skilled in the art upon consideration of the present inventive concept.
Claims (4)
1. Two-dimensional pulse width modulation mechanism, its characterized in that: the device comprises a transmission shaft, a zero position spring, a roller shaft, a left roller assembly, a right roller assembly, a front concentric ring, a valve core, a valve sleeve, a rear concentric ring and a valve core plug; the transmission shaft shifting fork is matched with the roller component to shift the valve core through the roller shaft, so that the valve core rotates in the circumferential direction in the valve sleeve and slides axially at the same time, the rotation and the axial sliding of the valve core are relatively independent, the front concentric ring and the rear concentric ring are respectively and fixedly connected to two ends of the valve sleeve, and the zero position spring is arranged between the valve core and the transmission shaft and is in a compressed state;
one end of the transmission shaft is a cylindrical end and is connected with the transmission mechanism; the other end of the transmission shaft is in a door frame shape and is connected with two U-shaped shifting forks, and the shifting fork surfaces are incomplete cylindrical surface tracks extending axially and are matched with the left roller assembly and the right roller assembly to enable the valve core to axially slide while rotating circumferentially; the axial middle end surface of the transmission shaft is provided with a circular groove for fixing a zero spring;
two flat end faces of the zero-position spring are respectively fixed at the circular groove of the transmission shaft and the stepped shaft at the left end of the valve core, the zero-position spring is in a compressed state in the initial and working processes, the valve core is ensured to be at the rightmost end in the initial state, and the zero position of the valve core is kept;
the roller shaft is a stepped cylindrical shaft, a shoulder is arranged in the middle of the stepped cylindrical shaft, and the diameter of the middle cylinder is larger than that of the cylinders at the two sides; the middle shoulder shaft is inserted into and fixedly connected with the cylindrical hole at the left end of the valve core, and the shafts at the two ends are respectively inserted into and fixedly connected with the central circular holes of the left roller assembly and the right roller assembly;
the right roller assembly and the left roller assembly are completely the same in structure and comprise a bearing sleeve and a deep groove ball bearing, the outer part of the bearing sleeve is a spherical surface, the inner part of the bearing sleeve is a round hole, the two ends of the bearing sleeve are flat end surfaces, an inner hole of the bearing sleeve is sleeved on the outer circle of the deep groove ball bearing and fixedly connected with the outer circle of the deep groove ball bearing, and the spherical surface of the bearing sleeve is matched with the cylindrical;
the front concentric ring is annular, two end faces are planes, the outer circle of the front concentric ring is fixedly connected with the valve sleeve, and the inner hole is sleeved on the left end shaft of the valve core;
the rear concentric ring is annular, two end faces are planes, an inner hole is provided with a stepped hole to provide an avoidance space for a second circular through hole of the valve core, the outer circle of the rear concentric ring is fixedly connected with the valve sleeve, and the inner hole is sleeved on a shaft at the right end of the valve core;
the inner hole of the valve sleeve is a central through hole and is matched with the valve core, and a front stepped hole and a rear stepped hole are respectively arranged at two ends and are respectively fixedly connected with a front concentric ring and a rear concentric ring; the excircle of the valve sleeve is provided with four annular grooves which are a control oil groove, an oil outlet groove, an oil inlet groove and an oil return groove from left to right, the control oil groove is uniformly provided with a plurality of same radial control oil holes, the oil outlet groove is uniformly provided with a plurality of same radial oil outlet holes, the oil inlet groove is uniformly provided with a plurality of same radial rhombic flow distribution windows, the vertexes of the rhombic flow distribution windows are positioned in the same plane, the plane is vertical to the axis of the valve core, and the oil return groove is uniformly provided with a plurality of same radial oil return holes;
the leftmost end of the valve core is provided with a step shaft for mounting a zero position spring, and the right side of the step shaft is provided with a roller shaft circular through hole which is fixedly connected with the roller shaft and used for transmitting torque to the valve core to enable the valve core to rotate; the valve core is provided with three shoulders, namely a first shoulder, a second shoulder and a third shoulder in sequence from left to right, a first circular through hole is formed in the radial direction of a valve core shaft between the first shoulder and the second shoulder, a second circular through hole is formed in the radial direction of the valve core shaft close to the right end face of the third shoulder, a central flow passage is axially formed in the center of the valve core, a valve core plug is used for plugging the central flow passage, and the first circular through hole and the second circular through hole are communicated through the central flow passage of the valve core; two lines of staggered triangular flow distribution windows are arranged on the second shoulder of the valve core and are respectively a left triangular flow distribution window and a right triangular flow distribution window, the vertexes of the windows are in the same plane, and the plane is perpendicular to the axis of the valve core.
2. The two-dimensional pulse width modulation mechanism of claim 1, wherein: the spherical surface of the outer circle of the bearing sleeve is in clearance fit with the U-shaped shifting fork of the transmission shaft, the spherical surface of the outer circle of the bearing sleeve is in unilateral contact with the shifting fork of the transmission shaft when stressed, the positive and negative rotation can be realized, the transmission shaft drives the valve core to rotate through the left roller assembly, the right roller assembly and the roller shaft, and the valve core slides axially under the action of hydraulic pressure to drive the bearing sleeve to roll axially on the U-shaped shifting.
3. The two-dimensional pulse width modulation mechanism of claim 1, wherein: the outer circles of the front concentric ring and the rear concentric ring are fixedly connected in a front stepped hole and a rear stepped hole of two end faces of the valve sleeve respectively, an inner hole of the front concentric ring is sleeved on a shaft at the left end of the valve core and is in clearance seal, and an inner hole of the rear concentric ring is sleeved on a shaft at the right end of the valve core and is in clearance seal.
4. The two-dimensional pulse width modulation mechanism of claim 1, wherein: the valve core is rotatably arranged in the valve sleeve, the front concentric ring and the first shoulder of the valve core seal the inner cavity of the valve sleeve to form a control cavity, the control cavity is communicated with the control oil groove through the control oil hole, and the control oil groove is communicated with control pressure oil; the valve core first shoulder and the second shoulder seal the inner cavity of the valve sleeve to form a high-pressure cavity, the high-pressure cavity is communicated with the oil outlet groove through the oil outlet hole and is communicated with the oil inlet groove through the rhombic flow distribution window, high-pressure oil of the hydraulic pump is introduced into the oil inlet groove, and the oil outlet groove is communicated with a system oil way; the second shoulder and the third shoulder of the valve core seal the inner cavity of the valve sleeve to form a low-pressure cavity, the low-pressure cavity is communicated with the oil return groove through an oil return hole, and the oil return groove is communicated with a low-pressure oil tank; the third shoulder of the valve core and the back concentric ring seal the inner cavity of the valve sleeve to form a feedback cavity, the feedback cavity is communicated with the high-pressure cavity through the first circular through hole, the central flow channel and the second circular through hole of the valve core, and the pressures of the two cavities are the same; the valve sleeve controls the oil groove, the oil outlet groove, the oil inlet groove and the oil return groove to be not communicated with each other outside the valve sleeve; two rows of staggered triangular flow distribution windows are formed in the second shoulder of the valve core and are respectively a left triangular flow distribution window and a right triangular flow distribution window, the rhombic flow distribution window of the valve sleeve is positioned on the motion track of the second shoulder of the valve core, the valve core axially slides under the action of hydraulic pressure while rotating at a constant speed in the valve sleeve, and the ratio of the left triangular flow distribution window and the right triangular flow distribution window of the valve core to the flow distribution time of the rhombic flow distribution window of the valve sleeve is changed, so that the flow distribution of the discharged oil is changed.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113565818A (en) * | 2021-07-22 | 2021-10-29 | 上海理工大学 | Electric control pressure regulating valve for hydraulic traction bed and control system thereof |
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| DE19938884A1 (en) * | 1999-08-17 | 2001-02-22 | Schaeffler Waelzlager Ohg | Oil flow valve for an IC motor has a small an inexpensive proportional magnet to move the slide against a low pressure spring with ring grooves of a structured geometry for the oil flows |
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