CN111102259B - Two-dimensional pulse width modulation mechanism - Google Patents
Two-dimensional pulse width modulation mechanism Download PDFInfo
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- CN111102259B CN111102259B CN201811247484.4A CN201811247484A CN111102259B CN 111102259 B CN111102259 B CN 111102259B CN 201811247484 A CN201811247484 A CN 201811247484A CN 111102259 B CN111102259 B CN 111102259B
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- 230000007246 mechanism Effects 0.000 title claims abstract description 20
- 230000005540 biological transmission Effects 0.000 claims abstract description 47
- 239000003921 oil Substances 0.000 claims description 183
- 229910003460 diamond Inorganic materials 0.000 claims description 27
- 239000010432 diamond Substances 0.000 claims description 27
- 230000009471 action Effects 0.000 claims description 8
- 238000000034 method Methods 0.000 claims description 7
- 230000008569 process Effects 0.000 claims description 6
- 238000007789 sealing Methods 0.000 claims description 6
- 230000033001 locomotion Effects 0.000 claims description 5
- 239000010729 system oil Substances 0.000 claims description 3
- 238000010586 diagram Methods 0.000 description 10
- 230000010349 pulsation Effects 0.000 description 6
- 238000004891 communication Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 230000001105 regulatory effect Effects 0.000 description 4
- 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 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000737 periodic effect Effects 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000087 stabilizing effect Effects 0.000 description 1
Classifications
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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
-
- 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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- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Multiple-Way Valves (AREA)
Abstract
The transmission shaft shifting fork shifts the valve core through the roller component, so that the valve core axially slides while circumferentially rotating in the valve sleeve, the valve core rotates and axially slides relatively independently, and the zero 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 outer circle of the valve sleeve is provided with four annular grooves from left to right, namely a control oil groove, an oil outlet groove, an oil inlet groove and an oil return groove, and a plurality of identical radial holes are uniformly formed in the control oil groove, the oil outlet groove, the oil inlet groove and the oil return groove; the center of the valve core is axially provided with a center flow passage, and the first circular through hole and the second circular through hole are communicated through the center flow passage of the valve core; the second shoulder of the valve core is provided with two staggered triangular flow distribution windows which are respectively a left triangular flow distribution window and a right triangular flow distribution window, the peaks of the two triangular flow distribution 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 reciprocates in the cylinder body, so that the change of the sealed working volume is caused to realize oil suction 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 is 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 is realized mainly by virtue of one-way valves, the two one-way valves are respectively arranged at oil inlet and outlet ports of the pump, and the plunger cavity respectively opens the one-way valves of the corresponding oil ports in the oil sucking and discharging stage, so that oil sucking and discharging are realized. The valve flow distribution mode does not require cylinder rotation and is generally used for a single plunger pump. The check valve has certain opening pressure and certain hysteresis in response, so that the self-absorption capacity of the pump is poor, cavitation is easy to cause, and the rotating speed of the pump is limited. The end face flow distribution is the main flow distribution mode of the current plunger pump, and the flow distribution mode requires the cylinder body of the plunger pump to rotate so that the plunger cavity is alternately communicated with the oil suction window and the oil discharge window on the flow distribution plate to suck and discharge oil. 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 rotation 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 complexity of design and processing of a mechanical system and a control system.
The existing two-dimensional (2D) pumps all adopt valve groups such as two-dimensional unloading valves, two-dimensional pressure stabilizing valves and the like to realize pressure and flow regulation, and have more parts, more control and regulation positions and larger pressure flow pulsation.
Disclosure of Invention
In order to overcome the problems of poor self-absorption, low rotating speed, large cylinder diameter, high technical requirements of friction pairs, complex mechanical system and control system and the like caused by valve flow distribution and end face flow distribution of a plunger pump, and overcome the defects of the conventional two-dimensional (2D) pump in a flow distribution mode of adjusting a plurality of hydraulic valves, the invention provides a two-dimensional pressure feedback flow distribution mechanism which has novel and compact structure, small volume, light weight, simple transmission, no friction pair, easy realization of high pressure and high rotating speed and realization of flow distribution by utilizing a valve core double-degree-of-freedom structure, and is a two-dimensional pulse width modulation mechanism. The invention solves the shortcomings and disadvantages of plunger pump flow distribution, is simple and convenient, optimizes the flow distribution mechanism of a two-dimensional (2D) pump, can omit an unloading valve at the outlet of a hydraulic pump, can realize zero pressure start of the hydraulic pump in a hydraulic system, and is suitable for 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: comprises a transmission shaft, a zero 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 and the roller assembly are matched to shift the valve core through the roller shaft, so that the valve core axially slides while circumferentially rotating in the valve sleeve, the valve core rotates and axially slides relatively independently, the front concentric ring and the rear concentric ring are respectively fixedly connected to two ends of the valve sleeve, and the zero 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, two U-shaped shifting forks are connected, the shifting fork surface is an incomplete cylindrical surface track extending axially, and the left roller assembly and the right roller assembly are matched, so that the valve core axially slides while rotating circumferentially; the axial middle end surface of the transmission shaft is provided with a circular groove for fixing the zero spring.
The two flat end surfaces of the zero 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 spring is in a compressed state in the initial and working processes, the valve core in the initial state is guaranteed to be at the rightmost end, and the zero position of the valve core is maintained.
The roller shaft is a stepped cylindrical shaft, a shoulder is arranged in the middle of the roller shaft, and the diameter of the middle cylinder is larger than that of the cylinders on the two sides; the middle shoulder shaft is inserted into a cylindrical hole at the left end of the valve core and fixedly connected, and the two end shafts are respectively inserted into a central round hole of the left roller assembly and the right roller assembly and fixedly connected.
The right roller assembly and the left roller assembly are identical in structure and comprise a bearing sleeve and a deep groove ball bearing, the outside of the bearing sleeve is a spherical surface, the inside 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 surface of the U-shaped shifting fork of the transmission shaft.
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 in a circular shape, two end faces are planes, the inner hole is provided with a stepped hole for providing avoidance space for the 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 the right end shaft of the valve core.
The valve sleeve inner hole 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 the front concentric ring and the rear concentric ring; the excircle of valve pocket is equipped with four ring channels from left to right and is control oil groove, oil outlet groove, oil inlet groove and oil return groove respectively, evenly is equipped with a plurality of same radial control oilholes on the control oil groove, evenly is equipped with a plurality of same radial oil outlet holes on the oil outlet groove, evenly is equipped with a plurality of same radial diamond on the oil inlet groove and joins in marriage the flow window, and the summit of diamond joins in marriage the flow window and this plane perpendicular to case axis, evenly is equipped with a plurality of same radial oil return holes on the oil return groove.
The leftmost end of the valve core is provided with a stepped shaft for installing a zero spring, the right side of the stepped shaft is provided with a round through hole of a roller shaft, and the stepped shaft is fixedly connected with the roller shaft and is 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 from left to right in sequence, a first circular through hole is formed in the axial direction of the valve core between the first shoulder and the second shoulder, a second circular through hole is formed in the axial 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 central flow passage opening is plugged by the valve core plug, and the first circular through hole and the second circular through hole are communicated through the central flow passage of the valve core; the second shoulder of the valve core is provided with two staggered triangular flow distribution windows which are respectively a left triangular flow distribution window and a right triangular flow distribution window, the peaks of the two triangular flow distribution windows are in the same plane, and the plane is perpendicular to the axis of the valve core.
Preferably, the excircle sphere of the bearing sleeve is in clearance fit with the U-shaped shifting fork of the transmission shaft, single-side contact can be realized when the bearing sleeve is stressed, forward and reverse 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 axially slides under the action of hydraulic pressure to drive the bearing sleeve to axially roll on the U-shaped shifting fork of the transmission shaft.
Preferably, the outer circles of the front concentric ring and the rear concentric ring are respectively fixedly connected in a front stepped hole and a rear stepped hole of two end faces of the valve sleeve, the inner holes of the front concentric ring are sleeved on the left end shaft of the valve core for clearance sealing, and the inner holes of the rear concentric ring are sleeved on the right end shaft of the valve core for clearance sealing.
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 a control oil groove through a 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 valve sleeve inner cavity to form a high-pressure containing cavity, the high-pressure containing cavity is communicated with the oil outlet groove through an oil outlet hole, and meanwhile, the high-pressure containing cavity is communicated with an oil inlet groove through a diamond-shaped flow distribution window, the oil inlet groove is communicated with high-pressure oil of a hydraulic pump, 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 an oil return groove through an oil return hole, and the oil return groove is communicated with a low-pressure oil tank; the valve core third shoulder and the rear concentric ring seal the valve sleeve inner cavity to form a feedback cavity, the feedback cavity is communicated with the high-pressure cavity through the valve core first circular through hole, the central flow passage and the second circular through hole, 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 mutually communicated outside the valve sleeve. The valve core second shoulder is provided with two staggered triangular flow distribution windows which are respectively a left triangular flow distribution window and a right triangular flow distribution window, the valve sleeve diamond flow distribution window is positioned on the motion track of the valve core second shoulder, and the valve core axially slides under the action of hydraulic pressure while rotating at a uniform speed in the valve sleeve, so that the flow distribution time proportion of the left triangular flow distribution window and the right triangular flow distribution window of the valve core to the valve sleeve diamond flow distribution window is changed, and the oil outlet flow is changed to realize flow distribution.
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 triangular flow distribution windows and a valve sleeve groove diamond flow distribution window arranged on the second shoulder of the valve core are in circumferential relative rotation; the liquid pressure in the control holding cavity acts on the annular area of the left end face of the first land of the valve core to generate axial right thrust to the valve core, the liquid pressure in the feedback holding cavity acts on the annular area of the right end face of the third land of the valve core to generate axial left thrust to the valve core, the zeroing spring is compressed to generate axial right thrust to the valve core, if the resultant force of the axial right thrust to the valve core and the spring force is larger than the axial left thrust, the valve core axially slides to the right, and if the resultant force of the axial right thrust to the valve core and the spring force is smaller than the axial left thrust, the valve core axially slides to the left. When the forces at two ends of the valve core are balanced, the valve core stays at a certain working position of the valve sleeve, and as the valve core rotates, the left triangular distribution window and the right triangular distribution window of the valve core are communicated with the rhombic distribution windows of the valve sleeve alternately to form periodic changes, because the number of the left triangular distribution windows and the right triangular distribution windows of the valve core and the rhombic distribution windows of the valve sleeve are large, the area gradient of the valve port is large, so that the magnitude of the opening of the valve port has little influence on the flow passing through the valve port, the flow passing through the valve port can be regarded as a quantity which is irrelevant to the opening of the valve port and is only related to the opening time of the valve port, namely the ratio of the time required by the left triangular distribution window and the right triangular distribution window of the valve core to respectively and alternately sweep through the rhombic distribution windows of the valve sleeve in any period 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.
When the valve core is in zero position, the valve core is at the rightmost end in the valve sleeve, the valve sleeve oil inlet groove is in maximum communication with the oil outlet groove, the oil inlet groove is not in communication with the oil return groove, and high-pressure oil of the pump is guaranteed to flow into the system completely before the pressure is built up by the system, so that the pressure is built up by the system quickly until the pressure flow of the system is stable, and the valve core is in an equilibrium state. When the valve core is positioned at the leftmost end in the valve sleeve, the valve sleeve oil inlet groove is not communicated with the oil outlet groove, the oil inlet groove is maximally communicated with the oil return groove, high-pressure oil of the pump completely flows into the oil tank, and the hydraulic pump is in an unloading state; at this time, 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 pressure maintaining of the system.
When the pressure of the control containing 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 and slightly changed, so that the high-pressure containing cavity and the feedback Rong Qiangya force 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 by the left triangular flow distribution window and the right triangular flow distribution window of the valve core to the total time respectively to be alternately scanned through the valve sleeve diamond flow distribution window 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 containing 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 axially slides under the action of the axial resultant force, the time required by the left triangular flow distribution window and the right triangular flow distribution window of the valve core to alternately sweep through the valve sleeve diamond flow distribution window respectively accounts for 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, the feedback Rong Qiangya force is correspondingly changed, the system pressure is increased until the valve core axial resultant force is balanced again, and the valve core reaches a new balanced state.
The axial sliding of the valve core changes the flow distribution time ratio, thereby changing the oil flow entering the hydraulic system. Thus, the manner in which the system flow is regulated with this configuration can be considered as pulse width modulation controlled by the spool position. Because the valve core rotates fast, and the valve core circumference is equipped with many triangle-shaped and join in marriage the flow window, is equipped with corresponding diamond-shaped and join in marriage the flow window on the valve barrel circumference for pulse width modulation's frequency is very high, and pressure pulsation and flow pulsation hardly show in the system.
The valve core double-degree-of-freedom 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 torque transmitted to the valve core by the transmission shaft, and the axial sliding of the valve core is caused by different stress at the two ends of the valve core.
The axial direction refers to the direction of the central axis of the valve core or the direction parallel to the central axis of the valve core; the radial direction is perpendicular to the direction of the central axis of the valve core; the circumferential direction refers to the direction in which the valve core rotates around the central axis.
The time required by the valve core left triangular flow distribution window and the valve core right triangular flow distribution window to alternately sweep through the valve sleeve diamond flow distribution window respectively refers to the overlapping time of the valve core left triangular flow distribution window and the valve sleeve diamond flow distribution window from opening to closing respectively in any period.
The beneficial effects of the invention are as follows:
1. by using the traditional slide valve structure, the novel flow distribution mode of the double-free structure of the valve core is adopted, the structure is simple, the performance is reliable, the valve core is provided with pressure feedback in the axial direction, and the system pressure and the output flow can be simultaneously regulated.
2. The valve core rotates to enable the frequency of pulse width modulation to be high, and pressure and flow pulsation in a system are greatly improved.
3. The two-dimensional (2D) pump valve group control flow distribution before is replaced, an adjusting mechanism is reduced, and the design is simplified.
4. Compared with the end face flow distribution of the traditional plunger pump, the friction pair structure is eliminated, the abrasion is reduced, and the efficiency is improved.
5. The hydraulic pump can be started almost in zero load in the high-pressure system.
Drawings
Fig. 1 is a schematic diagram of a two-dimensional pulse width modulation mechanism.
Fig. 2 is a schematic structural view of the valve sleeve.
Fig. 2a is a cross-sectional view of fig. 2C-C.
Fig. 3 is a schematic structural view of the valve core.
Fig. 3a is a D-D cross-sectional view of fig. 3.
Fig. 4 is a schematic structural view of the transmission shaft.
Fig. 5 is a schematic structural view of the right roller assembly.
Fig. 6 is a schematic structural view of a roller shaft.
Fig. 7a is a schematic diagram of the valve sleeve flow distribution window principle.
Fig. 7b is a schematic diagram of the valve core flow distribution window principle.
Fig. 7c is a schematic diagram of flow distribution principle when the valve core is in the middle position.
Fig. 7d is a schematic diagram of the flow distribution principle when the valve core moves downwards.
Detailed Description
The technical solution of the present invention is further described below with reference to fig. 1 to 7 d.
The two-dimensional pulse width modulation mechanism is characterized in that: the device consists of a transmission shaft 1, a zero 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 axially slides while circumferentially rotating in the valve sleeve 7, the valve core 8 rotates and axially slides relatively independently, the front concentric ring 6 and the rear concentric ring 9 are respectively fixedly connected to two ends of the valve sleeve 7, and the zero 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 to enable the transmission shaft 1 to rotate; the other end of the transmission shaft 1 is in a door frame shape, two U-shaped shifting forks are connected, the shifting fork surface is an incomplete cylindrical surface track extending axially, and the left roller assembly 4 and the right roller assembly 5 are matched, so that the valve core 8 axially slides while rotating circumferentially; the axial middle end surface of the transmission shaft 1 is provided with a circular groove for fixing the zero spring 2.
The two flat end surfaces of the zero spring 2 are respectively fixed at the groove of the transmission shaft 1 and the stepped shaft at the left end of the valve core 8, the zero spring 2 is in a compressed state in the initial and working processes, the valve core 8 in the initial state is guaranteed to be at the rightmost end, and the zero position of the valve core 8 is maintained.
The roller shaft 3 is a stepped cylindrical shaft, a shoulder is arranged in the middle of the roller shaft, and the diameter of the middle cylinder is larger than that of the cylinders on the two sides; the middle shoulder shaft is inserted into a cylindrical hole at the left end of the valve core 8 and fixedly connected, and the two end shafts are respectively inserted into central round holes of the left roller assembly 4 and the right roller assembly 5 and fixedly connected.
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 outside of the bearing sleeve 51 is a spherical surface, the inside 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 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 a U-shaped shifting fork cylindrical surface of the transmission shaft 1.
The front concentric ring 6 is in a circular ring shape, 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 rear concentric ring 9 is in a circular shape, two end faces are plane, a stepped hole is formed in the inner hole to provide avoidance space for the second circular through hole B2 of the valve core 8, the outer circle of the rear concentric ring 9 is fixedly connected with the valve sleeve 7, and the inner hole is sleeved on the right end shaft 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 grooves from left to right and is control oil groove K, play oil groove A, advance oil groove P and oil return groove T respectively, evenly is equipped with a plurality of same radial control oilholes K on the control oil groove K, evenly is equipped with a plurality of same radial oil outlet holes a on the play oil groove A, evenly is equipped with a plurality of same radial diamond on the oil groove P and joins in marriage and flow window P, and the summit of diamond joins in marriage flow window P is in the coplanar and this plane perpendicular to case axis, evenly is equipped with a plurality of same radial oil return holes T1 on the oil return groove T.
The leftmost end of the valve core 8 is provided with a stepped shaft for installing the zero spring 2, the right side of the stepped shaft is provided with a round through hole of a roller shaft, and the stepped shaft is fixedly connected with the roller shaft 3 and is 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, namely 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 the 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 surface of the third shoulder 83, a central flow passage B is axially arranged in the center of the valve core 8, the central flow passage is blocked by a valve core plug 10, and the first circular through hole B1 and the second circular through hole B2 are communicated through the central flow passage B of the valve core 8; the second shoulder 82 of the valve core 8 is provided with two staggered triangular flow distribution windows, namely a left triangular flow distribution window p1 and a right triangular flow distribution window p2, the peaks of which are in the same plane and the plane is perpendicular to the axis of the valve core.
The outer circle spherical surface of the bearing sleeve 51 is in clearance fit with the U-shaped shifting fork of the transmission shaft 1, single-side contact can be realized when the bearing sleeve is stressed, 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 1.
The outer circles of the front concentric ring 6 and the rear concentric ring 9 are respectively fixedly connected in a front stepped hole and a rear stepped hole of two end faces of the valve sleeve 7, the inner hole of the front concentric ring 6 is sleeved on the left end shaft of the valve core 8 for gap sealing, and the inner hole of the rear concentric ring 9 is sleeved on the right end shaft of the valve core 8 for gap sealing.
The valve core 8 is rotatably arranged in the valve sleeve 7, the front concentric ring 6 and the valve core first shoulder 81 seal the inner cavity of the valve sleeve 7 to form a control containing cavity K1, the control containing cavity K1 is communicated with a 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 containing cavity A1, the high-pressure containing 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 diamond-shaped 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 path; 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 containing cavity T1, the low-pressure containing 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 diamond-shaped 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 uniform speed in the valve sleeve 7, so that the flow distribution time proportion of the left triangular flow distribution window p1 and the right triangular flow distribution window p2 of the valve core 8 to the diamond-shaped flow distribution window p of the valve sleeve 7 is changed, and the oil outlet flow is changed to realize flow distribution.
The working principle of the embodiment is as follows:
The valve core 8 rotates at a constant speed under the drive of the transmission shaft 1, and a left triangular distribution window p1, a right triangular distribution window p2 and a diamond distribution window p of the valve sleeve 7 which are arranged on a second shoulder 82 of the valve core 8 are in staggered arrangement and rotate relatively in the circumferential direction; the liquid pressure in the control containing cavity K1 acts on the annular area S1 of the left end face of the first land 81 of the valve core 8 to generate axial right thrust to the valve core 8, the liquid pressure in the feedback containing cavity A2 acts on the annular area S2 of the right end face of the third land 83 of the valve core 8 to generate axial left thrust to the valve core 8, the zeroing spring 2 is compressed to generate axial right thrust to the valve core 8, if the resultant force of the axial right thrust to the valve core 8 and the spring force is larger than the axial left thrust, namely 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 axially right, if the resultant force of the axial right thrust to the valve core 8 and the spring force is smaller than the axial left thrust, namely the resultant force of the left end of the valve core 8 is smaller than the resultant force of the right end, and if the resultant force of the axial right thrust to the valve core 8 and the spring force is equal to the axial left thrust, namely the resultant force of the left end of the valve core 8 is equal to the resultant force of the right end, and the valve core 8 keeps the axial position unchanged, and is in a balanced state.
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 flow distribution window p of the valve sleeve 7 of the valve core 8 are circumferentially unfolded, and are simplified into schematic diagrams, such as fig. 7a, 7b, 7c and 7d. The left-right linear motion of the valve core in the schematic diagram represents the circumferential rotation of the valve core in the schematic diagram, and the vertical movement of the valve core in the schematic diagram represents the axial sliding of the valve core in the schematic diagram. In fig. 7a and 7b, P0 is an oil inlet, equivalent oil inlet grooves P, A0 are oil outlets, equivalent oil outlet grooves a, T0 are oil return openings, and equivalent oil return grooves T.
The valve core 8 can freely rotate and axially slide in the valve sleeve 7, as the valve core 8 rotates, the left triangular flow distribution window p1 and the right triangular flow distribution window p2 of the valve core 8 are communicated with the diamond flow distribution window p of the valve sleeve 7 alternately to form periodic changes, and as the number of the left triangular flow distribution windows p1 and the right triangular flow distribution windows p2 of the valve core 8 and the diamond flow distribution window p of the valve sleeve 7 is large, the valve port area gradient is large, so that the magnitude of the valve port opening has little influence on the flow passing through the valve port, the flow passing through the valve port can be considered as a quantity which is irrelevant to the valve port opening and is only related to the valve port opening time, namely the time required by the left triangular flow distribution window p1 and the right triangular flow distribution window p2 of the valve core 8 respectively and alternately sweep through the diamond flow distribution window p of the valve sleeve 7 in any period is the distribution ratio of the total time, and the oil outlet flow and the oil return flow are distributed according to the ratio;
As shown in fig. 7c and 7d, the flow Q with the ordinate of the oil inlet P0, the abscissa time T, and the time Δt1 required by the left triangular flow distribution window P1 of the valve core 8 to sweep the diamond flow distribution window P of the valve sleeve 7 are set, the time Δt2 required by the right triangular flow distribution window P2 of the valve core 8 to sweep the diamond flow distribution window P of the valve sleeve 7 are set, the flow of the oil outlet A0 is q·Δt1/Δt, and the flow of the oil return port T0 is q·Δt2/Δt. As can be seen from comparing fig. 7c and 7d, the axial sliding of the spool changes the duty ratio of Δt1 and Δt2, thereby changing the oil flow into the hydraulic system, and thus the manner in which the system flow is regulated by this structure can be regarded as pulse width modulation controlled by the spool position. Because the valve core 8 rotates fast, and the circumference of the valve core 8 is provided with a plurality of left and right triangle flow distribution windows p1 and p2, and the circumference of the valve sleeve 7 is provided with a corresponding diamond flow distribution window p, the frequency of pulse width modulation is very high, and pressure pulsation and flow pulsation are hardly reflected in the system.
When the valve core 8 is in the zero position, the valve core 8 is at the rightmost end in the valve sleeve 7, the oil inlet P0 is in maximum communication with the oil outlet A0, the oil inlet P0 is not in communication with the oil return port T0, and the high-pressure oil of the hydraulic pump is ensured to fully flow into the system before the pressure is built up by the system, so that the pressure is quickly built up by the system until the pressure and the flow of the system are stable, and the valve core is in a balanced state. 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 maximally communicated with the oil return port T0, high-pressure oil of the hydraulic pump completely flows into the oil tank, and the hydraulic pump is in an unloading state; at this time, 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 almost zero load starting of the hydraulic pump can be realized under the pressure maintaining state of the system.
If the control pressure is unchanged, the system pressure is unchanged, and the system demand flow is changed, the system pressure is also changed slightly. When the system demand flow is increased and the system pressure is reduced, the pressure of the high-pressure oil cavity A1 and the pressure of the feedback containing cavity A2 are reduced, the pressure of the control containing 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 larger than the resultant force of the right end, the valve core 8 axially slides to the right, at the moment, the opening degree of an oil inlet P0 and an oil outlet A0 is increased, the opening degree of an oil inlet P0 and an oil return opening T0 is reduced, the time that a left triangular flow distribution window P1 of the valve core 8 sweeps through a valve sleeve 7 diamond flow distribution window P is prolonged, the time that a right triangular flow distribution window P2 of the valve core 8 sweeps through the valve sleeve 7 diamond flow distribution window P is shortened, the flow of the oil outlet A0 becomes energy for the system, the pressure of the high-pressure containing cavity A1 and the feedback containing cavity A2 is increased until the pressure of the system is increased and is restored to the original pressure, the resultant force of the left end of the valve core 8 is equal to the resultant force of the right end, and the valve core 8 reaches the balance state again. Conversely, when the system demand flow 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 axially slides leftwards, the opening degree of the oil inlet P0 and the oil outlet A0 is reduced, the opening degree of the oil inlet P0 and the oil return opening T0 is increased, the time that the left triangular distributing window P1 of the valve core 8 sweeps through the diamond distributing window P of the valve sleeve 7 is shortened, the time that the right triangular distributing window P2 of the valve core 8 sweeps through the diamond distributing window P of the valve sleeve 7 is prolonged, the flow of the oil return opening T0 is increased, so that more oil flows back to the oil tank, the flow of the oil outlet A0 is reduced, the inflow system flow is reduced until the system pressure is reduced to restore to the original pressure, the resultant force of the left end of the valve core 8 is equal to the resultant force of the right end, and the valve core 8 reaches the balance state again.
If the system pressure needs to be changed, only the pressure value of the control oil port needs to be changed, the original balance state of the valve core is broken, and a new balance state is established. When the pressure of the control cavity K1 is increased, 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 axially to the right, at the moment, the opening degree of the oil inlet P0 and the opening degree of the oil outlet A0 are increased, the opening degree of the oil inlet P0 and the opening degree of the oil return opening T0 are reduced (until the oil inlet P0 is completely closed), the pressure of the oil outlet A0 is increased along with the increase of the flow of oil entering the system, and when the resultant forces of the two ends of the valve core 8 are equal again, the valve core reaches a new balance state. 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 axially slides leftwards, at the moment, the opening degree of the oil inlet P0 and the opening degree of the oil outlet A0 become smaller (until the oil inlet P0 and the oil outlet T0 are completely closed), the opening degree of the oil inlet P0 and the opening degree of the oil outlet 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 force of the two ends of the valve core 8 is equal again.
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 by reasonably setting the annular area S1 of the left end face of the first land 81 of the valve core 8, the annular area S2 of the right end face of the third land 83 of the valve core 8 and the zero spring stiffness, so that the outlet pressure value is regulated by changing the pressure value of the control oil port, and the regulation of the pressure flow of the system is achieved.
The embodiments described in the present specification are merely examples of implementation forms of the inventive concept, and the scope of protection of the present invention should not be construed as being limited to the specific forms set forth in the embodiments, and the scope of protection of the present invention and equivalent technical means that can be conceived by those skilled in the art based on the inventive concept.
Claims (2)
1. The two-dimensional pulse width modulation mechanism is characterized in that: the device comprises a transmission shaft, a zero 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 and the roller assembly are matched to shift the valve core through the roller shaft, so that the valve core axially slides while circumferentially rotating in the valve sleeve, the valve core rotates and axially slides relatively independently, the front concentric ring and the rear concentric ring are respectively fixedly connected to two ends of the valve sleeve, and the zero 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, two U-shaped shifting forks are connected, the shifting fork surface is an incomplete cylindrical surface track extending axially, and the left roller assembly and the right roller assembly are matched, so that the valve core axially slides while rotating circumferentially; the axial middle end surface of the transmission shaft is provided with a circular groove for fixing the zero spring;
The two flat end surfaces of the zero 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 spring is in a compressed state in the initial and working processes, the valve core in the initial state is ensured to be at the rightmost end, and the zero position of the valve core is maintained;
The roller shaft is a stepped cylindrical shaft, a shoulder is arranged in the middle of the roller shaft, and the diameter of the middle cylinder is larger than that of the cylinders on the two sides; the middle shoulder shaft is inserted into a cylindrical hole at the left end of the valve core and fixedly connected, and the two end shafts are respectively inserted into a central round hole of the left roller assembly and a central round hole of the right roller assembly and fixedly connected;
the right roller assembly and the left roller assembly have the same structure and comprise a bearing sleeve and a deep groove ball bearing, wherein 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 surface of a U-shaped shifting fork of the transmission shaft;
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 in a circular shape, two end surfaces are plane, a stepped hole is formed in the inner hole to provide 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 the right end shaft of the valve core;
the valve sleeve inner hole 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 the front concentric ring and the rear concentric ring; the outer circle of the valve sleeve is provided with four annular grooves from left to right, namely a control oil groove, an oil outlet groove, an oil inlet groove and an oil return groove, wherein a plurality of identical radial control oil holes are uniformly arranged on the control oil groove, a plurality of identical radial oil outlet holes are uniformly arranged on the oil outlet groove, a plurality of identical radial diamond flow distribution windows are uniformly arranged on the oil inlet groove, the peaks of the diamond flow distribution windows are in the same plane and the plane is perpendicular to the axis of the valve core, and a plurality of identical radial oil return holes are uniformly arranged on the oil return groove;
The leftmost end of the valve core is provided with a stepped shaft for installing a zero spring, the right side of the stepped shaft is provided with a round through hole of a roller shaft, and the stepped shaft is fixedly connected with the roller shaft and is 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 from left to right in sequence, a first circular through hole is formed in the axial direction of the valve core between the first shoulder and the second shoulder, a second circular through hole is formed in the axial 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 central flow passage opening is plugged by the valve core plug, and the first circular through hole and the second circular through hole are communicated through the central flow passage of the valve core; two staggered triangular flow distribution windows are respectively arranged on the second shoulder of the valve core, wherein the peaks of the two staggered triangular flow distribution windows are in the same plane and are perpendicular to the axis of the valve core;
the outer spherical surface of the bearing sleeve is in clearance fit with the U-shaped shifting fork of the transmission shaft, single-side contact can be realized when the bearing sleeve is stressed, forward and reverse 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 axially slides under the action of hydraulic pressure to drive the bearing sleeve to axially roll on the U-shaped shifting fork of the transmission shaft;
The outer circles of the front concentric ring and the rear concentric ring are respectively fixedly connected in a front stepped hole and a rear stepped hole of two end faces of the valve sleeve, the inner holes of the front concentric ring are sleeved on the left end shaft of the valve core for clearance sealing, and the inner holes of the rear concentric ring are sleeved on the right end shaft of the valve core for clearance sealing.
2. 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 containing cavity, the control containing cavity is communicated with a control oil groove through a 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 valve sleeve inner cavity to form a high-pressure containing cavity, the high-pressure containing cavity is communicated with the oil outlet groove through an oil outlet hole, and meanwhile, the high-pressure containing cavity is communicated with an oil inlet groove through a diamond-shaped flow distribution window, the oil inlet groove is communicated with high-pressure oil of a hydraulic pump, 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 an oil return groove through an oil return hole, and the oil return groove is communicated with a low-pressure oil tank; the valve core third shoulder and the rear concentric ring seal the valve sleeve inner cavity to form a feedback cavity, the feedback cavity is communicated with the high-pressure cavity through the valve core first circular through hole, the central flow passage and the second circular through hole, 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 mutually communicated outside the valve sleeve; the valve core second shoulder is provided with two staggered triangular flow distribution windows which are respectively a left triangular flow distribution window and a right triangular flow distribution window, the valve sleeve diamond flow distribution window is positioned on the motion track of the valve core second shoulder, and the valve core axially slides under the action of hydraulic pressure while rotating at a uniform speed in the valve sleeve, so that the flow distribution time proportion of the left triangular flow distribution window and the right triangular flow distribution window of the valve core to the valve sleeve diamond flow distribution window is changed, and the oil outlet flow is changed to realize flow distribution.
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2302355A1 (en) * | 1973-01-18 | 1974-08-08 | Ilie Chivari | LOWERING BRAKE VALVE |
| 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 |
| EP1577593A1 (en) * | 2004-03-16 | 2005-09-21 | HYDAC Electronic GmbH | Spool valve |
| CN105822795A (en) * | 2016-05-23 | 2016-08-03 | 浙江工业大学 | Inclined trough type 2D electro-hydraulic high-speed switching valve with variable transmission ratio transmission mechanism |
| CN106122146A (en) * | 2016-07-19 | 2016-11-16 | 浙江工业大学 | The microminiature 2D electromagnetic switch valve that a kind of hydraulic pressure resets |
| CN108005983A (en) * | 2017-12-01 | 2018-05-08 | 宁波文泽机电技术开发有限公司 | A kind of big flow Solenoid ball valve |
| CN209164221U (en) * | 2018-10-25 | 2019-07-26 | 浙江工业大学 | Two-dimentional pulsewidth modulation mechanism |
-
2018
- 2018-10-25 CN CN201811247484.4A patent/CN111102259B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2302355A1 (en) * | 1973-01-18 | 1974-08-08 | Ilie Chivari | LOWERING BRAKE VALVE |
| 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 |
| EP1577593A1 (en) * | 2004-03-16 | 2005-09-21 | HYDAC Electronic GmbH | Spool valve |
| CN105822795A (en) * | 2016-05-23 | 2016-08-03 | 浙江工业大学 | Inclined trough type 2D electro-hydraulic high-speed switching valve with variable transmission ratio transmission mechanism |
| CN106122146A (en) * | 2016-07-19 | 2016-11-16 | 浙江工业大学 | The microminiature 2D electromagnetic switch valve that a kind of hydraulic pressure resets |
| CN108005983A (en) * | 2017-12-01 | 2018-05-08 | 宁波文泽机电技术开发有限公司 | A kind of big flow Solenoid ball valve |
| CN209164221U (en) * | 2018-10-25 | 2019-07-26 | 浙江工业大学 | Two-dimentional pulsewidth modulation mechanism |
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