CN114233869A - Electro-hydraulic proportional pressure reducing valve for engineering vehicle - Google Patents
Electro-hydraulic proportional pressure reducing valve for engineering vehicle Download PDFInfo
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- CN114233869A CN114233869A CN202111643349.3A CN202111643349A CN114233869A CN 114233869 A CN114233869 A CN 114233869A CN 202111643349 A CN202111643349 A CN 202111643349A CN 114233869 A CN114233869 A CN 114233869A
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- valve
- magnetic yoke
- push rod
- sleeve type
- pressure reducing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
- F16K1/14—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces with ball-shaped valve member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K27/00—Construction of housing; Use of materials therefor
- F16K27/02—Construction of housing; Use of materials therefor of lift valves
- F16K27/0245—Construction of housing; Use of materials therefor of lift valves with ball-shaped valve members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
- F16K31/0665—Lift valves with valve member being at least partially ball-shaped
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
An electro-hydraulic proportional pressure reducing valve for an engineering vehicle belongs to the technical field of pressure reducing valves. The electro-hydraulic proportional pressure reducing valve for the engineering vehicle has the advantages of high proportional control characteristic, high response speed, compact structure and easiness in processing and assembling. The sleeve type armature is arranged between the sleeve type sliding rail I and the sleeve type sliding rail II, the sleeve type armature is fixedly sleeved on the sliding block, the upper end of the sliding block is connected with an adjusting spring of the electromagnetic assembly, the lower end of the sliding block is contacted with the push rod, the sliding block transmits electromagnetic force applied to the sleeve type armature to the push rod, meanwhile, spring force of the adjusting spring is transmitted to the push rod, the lower end of the push rod is contacted with the valve core, the valve core is matched with a valve seat of the valve body to form an oil inlet valve port A, and the push rod is matched with the valve seat to form an oil outlet valve port B. The upper magnetic yoke angle and the lower magnetic yoke angle can provide expected electromagnetic force-displacement characteristics, the proportional control characteristics of the electromagnetic force and current are high, meanwhile, the sleeve type sliding rail reduces the friction resistance of armature movement, and the effective power of the electromagnetic force is improved.
Description
Technical Field
The invention belongs to the technical field of pressure reducing valves, and particularly relates to an electro-hydraulic proportional pressure reducing valve for an engineering vehicle.
Background
The hydraulic mechanical automatic transmission has the self-adaptive performance of the hydraulic torque converter, and is simple and convenient to operate, so that the engineering vehicle shows good dynamic performance and adaptability under the heavy-load working condition in the extreme environment. The electro-hydraulic proportional pressure reducing valve is used as a pilot control valve of an electro-hydraulic control loop in the automatic torque converter, can control the opening of a main valve by outputting working pressure relatively lower than inlet pressure, and adjusts the pressure of a corresponding clutch oil cylinder, so that power switching and control of a clutch and a clutch are realized. The control characteristics of the pressure and the flow of the electro-hydraulic proportional pressure reducing valve are key factors of the gear shifting quality of the transmission, and play an important role in the speed changing and gear shifting processes of the engineering vehicle.
The electro-hydraulic proportional pressure reducing valve mainly comprises an electromagnet and a valve body. The electromagnet has relatively constant electromagnetic force-displacement characteristic, so that when different currents are loaded on an inner coil of the electromagnet, the electromagnetic force is irrelevant to the displacement of the armature, the value of the electromagnetic force is only in proportional relation with the current, the electro-hydraulic proportional pressure reduction characteristic of the electro-hydraulic control loop can be realized by adjusting the current, and the pressure and the flow of expected working oil can be output from the valve outlet. At present, in the field of practical engineering vehicles, the oil pressure output by an electro-hydraulic proportional pressure reducing valve has a ripple effect, the response speed is low, and the control characteristic is poor because on one hand, the design of an electromagnet part of the electro-hydraulic proportional pressure reducing valve cannot provide the expected electromagnetic force-displacement characteristic (the standard deviation of the electromagnetic force is less than 3), the proportional characteristic of the electromagnetic force and the current is poor, on the other hand, the design of a flow passage and a valve port of a valve body part is not compact enough, and the larger the valve cavity is due to the compressibility of oil, the response speed of the pressure and the flow can be limited. Meanwhile, the existing electro-hydraulic proportional pressure reducing valve has the defects of more embedded parts, complex pore passage of a processing structure and poor processing and assembling performance.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and further provides an electro-hydraulic proportional pressure reducing valve for an engineering vehicle, which has the advantages of high proportional control characteristic, high response speed, compact structure and easiness in processing and assembling.
The technical scheme adopted by the invention is as follows: an electro-hydraulic proportional pressure reducing valve for engineering vehicles comprises a shell, a valve body arranged on the shell, a valve core arranged in the valve body, an electromagnetic assembly and an armature assembly, wherein the electromagnetic assembly and the armature assembly are arranged in the shell; the armature component comprises a push rod, a slide block, a sleeve type armature, a sleeve type slide rail I and a sleeve type slide rail II; the electromagnetic valve comprises a valve body, a sleeve type slide rail I, a sleeve type slide rail II, a sleeve type armature, a slide block, a spring, a push rod, a valve core and a valve seat, wherein the sleeve type slide rail I and the sleeve type slide rail II are arranged at the center of the electromagnetic assembly in an up-down opposite mode, the sleeve type armature is arranged between the sleeve type slide rail I and the sleeve type slide rail II and fixedly sleeved on the slide block, the slide block slides in a gap between the sleeve type slide rail I and the sleeve type slide rail II, the upper end of the slide block is connected with an adjusting spring of the electromagnetic assembly, the lower end of the slide block is in contact with the push rod, the slide block transmits electromagnetic force received by the sleeve type armature to the push rod and transmits spring force of the adjusting spring to the push rod, the lower end of the push rod is in contact with the valve core, the valve core is matched with the valve seat of the valve body to form an oil inlet valve port A, and the push rod is matched with the valve seat to form an oil outlet valve port B.
Compared with the prior art, the invention has the following beneficial effects:
1. the design of the upper magnetic yoke angle and the lower magnetic yoke angle of the electromagnet part can provide expected electromagnetic force-displacement characteristics (the standard deviation of the electromagnetic force is less than 1), the proportional control characteristics of the electromagnetic force and current are high, and meanwhile, the design of the sleeve type slide rail reduces the friction resistance of armature motion and improves the effective power of the electromagnetic force.
2. The flow channel and the valve port of the valve body part are designed compactly, and a ball core and baffle plate type valve core matching form is used, so that a control cavity after the pressure of the ball core is reduced is optimally designed, working oil after the pressure is reduced directly flows out of the annular cavity, the response speed of the pressure of the working oil is improved, and the pressure controllability in the gear shifting control process is effectively improved.
3. The design of the baffle plate type structure ensures that after the oil inlet valve port is closed, oil in the control cavity flows out through the oil outlet valve port formed by the baffle plate and the step surface, thereby avoiding misoperation caused by pressure of the control cavity.
4. The whole valve body of the invention uses the valve seat embedding mode, and compared with the prior art, the valve body has the advantages of reduced number of embedded parts, reduced difficulty in processing pore channels, more compact structure and improved processing and assembling performance.
5. The invention has the advantages of high proportional control characteristic, high response speed, compact structure, easy processing and assembly, suitability for various fields of gear shifting and speed changing systems, anti-lock systems, fuel injection systems and the like in engineering vehicles and wide application range.
Drawings
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a cross-sectional view of the main body of the present invention;
FIG. 3 is a front view of the upper yoke;
FIG. 4 is a front cross-sectional view of the slider;
FIG. 5 is a front cross-sectional view of an outside cable;
FIG. 6 is a cross-sectional view A-A of FIG. 5;
FIG. 7 is a front cross-sectional view of the housing;
FIG. 8 is a left side elevation view in section of FIG. 7;
FIG. 9 is a front cross-sectional view of the lower yoke;
FIG. 10 is a front view of the valve body;
FIG. 11 is a left side elevation view in section of FIG. 10;
FIG. 12 is a front view of FIG. 10;
FIG. 13 is a front view of the push rod;
FIG. 14 is a front cross-sectional view of the valve seat;
FIG. 15 is a front cross-sectional view of the adjustment screw;
FIG. 16 is a top view of FIG. 15;
FIG. 17 is a schematic view of a front view of an electro-hydraulic proportional pressure reducing valve showing a closed position of an inlet valve port;
FIG. 18 is a schematic illustration of a left side view of an electro-hydraulic proportional pressure reducing valve showing a closed position of an inlet port valve port;
FIG. 19 is a schematic view of a front view of an electro-hydraulic proportional pressure reducing valve illustrating an open position of an inlet valve port;
FIG. 20 is a schematic diagram of the left side view direction inlet valve port opening position of the electro-hydraulic proportional pressure reducing valve.
Wherein: an upper magnet yoke 1, a first 1-1 outer circle surface of the upper magnet yoke, a first chamfer 1-2 outer circle surface, a first 1-3 step surface of the upper magnet yoke, a central threaded hole 1-4, a first 1-5 step surface of the upper magnet yoke, a first 1-6 inner circle surface of the upper magnet yoke, a second 1-7 step surface of the upper magnet yoke, a second 1-8 outer circle surface of the upper magnet yoke, a first 1-9 upper magnet yoke angle, a sleeve type slide rail 2, a first outer circle surface 2-1 slide rail, a first inner circle surface 2-2 slide rail, a slider 3, a first 3-1 outer circle surface of the slider, a second 3-2 outer circle surface of the slider, a first 3-3 annular groove surface, a circular groove 3-4 at the shaft end, a circular groove step surface 3-5 circular groove, a lower end surface 3-6, an external cable 4, a plug 4-1, a pore passage 4-2, a rectangular groove 4-3, a first 4-4 inner circle surface, 4-5 parts of connecting boss, 5 parts of coil, 6 parts of coil framework, 6-1 parts of annular groove, a sleeve type armature 7, 7-1 parts of inner circle surface of armature, 8 parts of shell, 8-1 parts of inner circle surface of shell, 8-2 parts of step surface of shell, 8-3 parts of inner circle surface of shell, 8-4 parts of step surface of shell, 8-5 parts of U-shaped groove, 8-6 parts of inner circle surface of shell, 9 parts of sleeve type slide rail, 9-1 parts of outer circle surface of slide rail, 9-2 parts of inner circle surface of slide rail, 10-1 parts of lower magnet yoke, 10-1 parts of outer circle surface of lower magnet yoke, 10-2 parts of shoulder surface of lower magnet yoke, 10-3 parts of inner circle surface of lower magnet yoke, 10-4 parts of outer circle surface of lower magnet yoke, 10-5 parts of angle of lower magnet yoke, 10-6 parts of inner circle surface of lower magnet yoke, 10-7 parts of central hole of lower magnet yoke, 11 parts of valve body, 11 parts of inner circle surface of valve body, 11-1 parts of valve body, 11-2 parts of the inner circle surface of the valve body, 11-3 parts of the first rectangular groove, 11-4 parts of the inner circle surface of the valve body, 11-5 parts of the inner circle surface of the valve body, 11-6 parts of the shoulder surface of the valve body, 11-7 parts of the inner circle surface of the valve body, 11-8 parts of the first rectangular through groove, 11-9 parts of the second rectangular through groove, 11-10 parts of the first annular groove, 11-11 parts of the second annular groove, 11-12 parts of the third annular groove, 11-13 parts of the fourth annular groove, 12 parts of the push rod, 12-1 parts of the fillet end, 12-2 parts of the outer circle surface of the push rod, 12-3 parts of the first step surface of the outer circle surface of the push rod, 12-4 parts of the plain surface end, 13 parts of the sealing ring, 14 parts of the ball core, 15 parts of the sealing ring, a filter screen 16 of the oil inlet, 17 parts of the valve seat, 17-1 parts of the outer circle surface of the valve seat, 17-2 parts of the conical surface of the valve seat, 17-3 parts of the central hole of the valve seat, 18 parts of the filter screen 18 parts of the control hole, a regulating spring 19 parts of the regulating spring, a regulating spring, The adjusting screw 20, the screw step surface I20-1, the tip 20-2, the screw step surface II 20-3, the cross groove 20-4, the oil inlet valve port A, the oil discharge port valve port B, the working air gap C, the oil inlet cavity y1, the control cavity y2, the communication cavity I y3, the communication cavity II y4 and the oil discharge cavity y 5.
Detailed Description
The electromagnetic high-speed switch valve divides the armature in the traditional form into a push rod 12, a slide block 3 and a sleeve type armature 7, effectively increases the magnetization degree and the electromagnetic force of the armature, and reduces the mass force of the armature in the displacement process; the design of the sleeve type slide rail reduces the friction resistance of the movement of the armature and improves the effective power of the electromagnetic force; the design of the chamfers of the upper magnetic yoke 1 and the lower magnetic yoke 10 ensures that the fluctuation standard deviation of the horizontal electromagnetic force characteristic of the armature is less than 1, and the horizontal characteristic of the electromagnetic force is improved; the valve body 11 part uses a valve core matching form of a ball core and a baffle plate, and a control cavity of the ball core 14 after pressure reduction is optimally designed, so that working oil after pressure reduction directly flows out of an annular cavity, and the response speed of the pressure of the working oil is improved; due to the design of the baffle plate type structure, after the oil inlet valve port is closed, oil in the control cavity flows out through the oil discharge valve port formed by the baffle plate and the step surface, so that misoperation caused by pressure of the control cavity is avoided; the whole valve body 11 adopts the valve seat embedding mode, and compared with the prior art, the valve body has the advantages that the number of embedded parts is reduced, the difficulty in processing pore channels is reduced, the structure is more compact, and the processing and assembling performance is improved.
The electro-hydraulic proportional pressure reducing valve improves the electromagnetic force-displacement horizontal characteristic and the electromagnetic force-current proportional characteristic of electromagnetic force, the response speed of valve core displacement and working oil pressure is improved due to the design of an internal flow passage and the reduction of a containing cavity, the pressure control performance in the gear shifting control process is effectively improved, and the design of a pore passage of the valve body 11 is matched with the structural form of the valve seat 17, so that the electro-hydraulic proportional pressure reducing valve has higher response speed and better oil pressure reduction control characteristic, and is compact in structure and convenient to process and assemble.
The first embodiment is as follows: the embodiment is described with reference to fig. 1 to 20, and the embodiment provides an electro-hydraulic proportional pressure reducing valve for a construction vehicle, which comprises a housing 8, a valve body 11 mounted on the housing 8, a valve core arranged in the valve body 11, an electromagnetic assembly mounted in the housing 8 and an armature assembly; the armature component comprises a push rod 12, a slide block 3, a sleeve type armature 7, a sleeve type slide rail I2 and a sleeve type slide rail II 9; the sleeve type slide rail I2 and the sleeve type slide rail II 9 are arranged at the center of the electromagnetic assembly in a vertically opposite mode, the sleeve type armature 7 is arranged between the sleeve type slide rail I2 and the sleeve type slide rail II 9 and fixedly sleeved on the sliding block 3, the sliding block 3 slides in a gap between the sleeve type slide rail I2 and the sleeve type slide rail II 9, the upper end of the sliding block 3 is connected with an adjusting spring 19 of the electromagnetic assembly, the lower end of the sliding block 3 is in contact with a push rod 12, the sliding block 3 transmits electromagnetic force borne by the sleeve type armature 7 to the push rod 12, meanwhile, spring force of the adjusting spring 19 is transmitted to the push rod 12, the lower end of the push rod 12 is in contact with a valve core, the valve core is matched with a valve seat 17 of the valve body 11 to form a valve port A, and the push rod 12 is matched with the valve seat 17 to form a valve port B.
In the embodiment, the armature in the traditional form is divided into a push rod 12, a slide block 3 and a sleeve type armature 7, so that the magnetization degree and the electromagnetic force of the armature are effectively increased, and the mass force of the armature in the displacement process is reduced; the design of the sleeve type slide rail reduces the friction resistance of the movement of the armature and improves the effective power of the electromagnetic force.
The second embodiment is as follows: the present embodiment is described with reference to fig. 2, 3, 5, 6, and 9, and the present embodiment further defines a first specific embodiment, and in the present embodiment, the electromagnetic assembly includes an upper yoke 1, an external cable 4, a bobbin 6, a lower yoke 10, and an adjusting spring 19; the coil 5 is wound on the outer circumferential surface of the coil framework 6, the external cable 4 is connected with the coil 5, the coil framework 6 and the external cable 4 are subjected to an integral injection molding packaging process, and the coil 5, the coil framework 6 and the external cable 4 are integrally installed in the shell 8; the upper magnetic yoke 1 and the lower magnetic yoke 10 are respectively arranged in the shell 8, the upper magnetic yoke 1 is sleeved outside the sleeve type sliding rail I2 in an interference mode, the lower magnetic yoke 10 is sleeved outside the sleeve type sliding rail II 9 in an interference mode, the adjusting spring 19 is arranged in a circular groove 3-4 at the shaft end of the upper magnetic yoke 1, and the lower end of the adjusting spring compresses the sliding block 3. Other components and connection modes are the same as those of the first embodiment.
The third concrete implementation mode: the present embodiment will be described with reference to fig. 3 and 9, and the present embodiment is further limited to a second embodiment, in which an upper yoke angle 1-9 is provided at an end portion of a bottom surface of the upper yoke 1, and an angle of the upper yoke angle 1-9 is 25 to 45 °; the upper end of the lower magnetic yoke 10 is provided with a lower magnetic yoke angle 10-5, the angle of the lower magnetic yoke angle 10-5 is 15-35 degrees, and the upper magnetic yoke angle 1-9 and the lower magnetic yoke angle 10-5 are used for changing the direction of magnetic lines of force. The other components and the connection mode are the same as those of the second embodiment.
In the embodiment, the design of the chamfers of the upper magnetic yoke 1 and the lower magnetic yoke 10 enables the fluctuation standard deviation of the horizontal electromagnetic force characteristic of the armature to be less than 1, and the horizontal electromagnetic force characteristic is improved.
In the fourth embodiment, the present embodiment is described with reference to fig. 2, and the present embodiment is further limited to the second embodiment, in which an adjusting screw 20 is installed in the inner cavity of the upper yoke 1, and the lower end of the adjusting screw 20 presses the lower end of the adjusting spring 19 to adjust the elastic force of the adjusting spring (19).
The fifth concrete implementation mode: the present embodiment is described with reference to fig. 2, 13, and 14, and is further limited to the first specific embodiment, in the present embodiment, the valve core is a ball core 14, the push rod 12 is provided with a push rod baffle, the push rod baffle is inserted into the inner cavity of the valve body 11, and forms an oil discharge port valve port B with the valve body 11, the valve body 11 is internally provided with a valve seat 17, an end surface of the valve seat 17 is a valve seat conical surface 17-2, and the valve seat conical surface 17-2 cooperates with the ball core 14 to form an oil inlet valve port a. Other components and connection modes are the same as those of the first embodiment.
In the embodiment, the valve body 11 partially uses a valve core matching form of a ball core and a baffle, and a control cavity of the ball core 14 after pressure reduction is optimally designed, so that working oil after pressure reduction directly flows out of an annular cavity, and the response speed of the pressure of the working oil is improved; the design of baffle formula structure makes the oil feed valve port close the back, and the fluid of control chamber flows through the oil discharge valve port that baffle and step face formed, has avoided the malfunction that control chamber pressure arouses.
The sixth specific implementation mode: the present embodiment is described with reference to fig. 2, 10, and 11, and is further limited to the fifth embodiment, in the present embodiment, a chamber in which the push rod 12 is located in the valve body 11 is provided with a rectangular through groove one 11-8, the rectangular through groove one 11-8 is used as a passage through which oil flows out from the oil discharge port valve port B, a chamber in which the ball core 14 is located in the valve body 11 is provided with a rectangular through groove two 11-9, and the rectangular through groove two 11-9 is used as a passage through which oil flows out. The other components and the connection mode are the same as the fifth embodiment mode.
The seventh embodiment: the present embodiment is described with reference to fig. 10 to 11, and is further limited to a sixth specific embodiment, in the present embodiment, an outer circumferential surface of the valve body 11 is provided with, in order from top to bottom, a first annular groove 11-13, a first annular groove 11-10, a second annular groove 11-11, and a third annular groove 11-12, the first annular groove 11-10 disposed below the first rectangular through groove 11-8 is used for placing a first sealing ring 13, the second annular groove 11-11 disposed outside the second rectangular through groove 11-9 is used for placing a control port filter screen 18, the third annular groove 11-12 is used for placing a second sealing ring 15, and the fourth annular groove 11-13 is used for mounting and fixing the entire pressure reducing valve with an external device. Other components and connection modes are the same as those of the sixth embodiment.
The specific implementation mode is eight: referring to fig. 2, the embodiment is described, and the embodiment further defines a second embodiment, in the embodiment, the roughness of the inner circular surface of the first sleeve-type sliding rail 2 is ra0.4 to 0.8, and the roughness of the inner circular surface of the second sleeve-type sliding rail 9 is ra0.4 to 0.8, so as to provide a low friction track for the reciprocating motion of the sliding block 3. The other components and the connection mode are the same as those of the second embodiment.
The specific implementation method nine: referring to fig. 9, this embodiment is described, and further defines a sixth specific embodiment, in this embodiment, the second lower yoke inner circular surface 10-6 at the upper end of the lower yoke 10 cavity is used for the up-and-down sliding of the sleeve-type armature 7, and the central lower yoke hole 10-7 at the lower end of the lower yoke 10 cavity is used for the penetration of the push rod 12, so as to realize the spring force transmission from the sleeve-type armature 7 to the ball core 14. Other components and connection modes are the same as those of the sixth embodiment.
As shown in fig. 1, 2, and 3: the upper magnetic yoke 1 is made of soft magnetic material electric pure iron DT4C and is axisymmetric as a whole. The upper magnetic yoke 1 is provided with an upper magnetic yoke boss, a first 1-1 outer circular surface of the upper magnetic yoke boss is in clearance fit with a first 8-1 inner circular surface of the shell 8, a first 1-1 outer circular surface of the upper magnetic yoke is provided with a chamfer 1-2 outer circular surface which is used as a pressing surface for rolling and closing up a first 8-1 inner circular surface of the shell, and a first 1-3 step surface of the upper magnetic yoke boss presses a first 8-2 shell step surface of the shell 8 to realize the positioning of the rolling and closing up. The inner cavity of the upper magnet yoke 1 is a multi-stage multi-diameter inner cavity and sequentially comprises an upper magnet yoke hole I, a central threaded hole 1-4, an upper magnet yoke hole II, an upper magnet yoke hole III and an upper magnet yoke hole IV from top to bottom, the central threaded hole 1-4 is used for screwing the adjusting screw 20, the upper magnet yoke step surface I1-5 of the upper magnet yoke hole I is used for fixing the adjusting screw 20, the upper magnet yoke inner circle surface I1-6 of the upper magnet yoke hole III is in interference fit with the sliding rail outer circle surface I2-1 of the sleeve type sliding rail I2, and the fit tolerance is generally H7/s 6. And the step surface two 1-7 of the upper magnetic yoke hole four is used as the suction surface of the sleeve-type armature 7, the excircle surface two 1-8 of the upper magnetic yoke at the lower end of the upper magnetic yoke 1 is in clearance fit with the coil framework 6, and the end part of the excircle surface two 1-8 of the upper magnetic yoke is provided with an upper magnetic yoke angle 1-9 which is 25-45 degrees.
As shown in fig. 2: the sleeve type sliding rail I2 is made of alloy steel, the outer circle surface 2-1 of the sliding rail I2 of the sleeve type sliding rail I is in interference fit with the inner circle surface 1-6 of the upper magnetic yoke, the fit tolerance is generally H7/s6, the inner circle surface 2-2 of the sliding rail I2 of the sleeve type sliding rail I is in clearance fit with the outer circle surface two 3-2 of the sliding block 3 of the sliding block, the requirement on the roughness of the inner circle surface is high (Ra0.4-0.8), and a low friction track is provided for the reciprocating motion of the sliding block 3.
As shown in fig. 2 and 4: the slider 3, which is made of duralumin LC9, transmits the electromagnetic force experienced by the sleeve-type armature 7 to the push rod 12, while transmitting the spring force of the adjusting spring 19 to the push rod 12. An annular groove is arranged on the outer circumferential surface of the sliding block 3, the outer circumferential surface of the sliding block 3 is divided into a sliding block outer circular surface two 3-2 and a sliding block outer circular surface one 3-1 from top to bottom, the sliding block outer circular surface one 3-1 and the sliding block outer circular surface two 3-2 respectively realize clearance sliding with a sliding block two inner circular surface 9-2 of the sleeve type sliding rail two 9 and a sliding block one inner circular surface 2-2 of the sleeve type sliding rail one 2, the sliding block outer circular surface one 3-1 and the armature inner circular surface one 7-1 of the sleeve type armature 7 realize interference fit, the interference fit tolerance is generally H7/s6, the annular groove surface one 3-3 of the annular groove is used as a positioning surface which is in interference fit with the sleeve type armature 7, the upper end surface of the sliding block 3 is provided with an annular groove 3-4 at the shaft end, and the circular groove 3-4 at the shaft end is used for placing the adjusting spring 19, the adjusting spring 19 compresses the round groove step surface 3-5 of the round groove 3-4 of the shaft end under the adjusting action of the adjusting screw 20, and the lower end surface 3-6 of the sliding block 3 is used as the contact surface of the push rod 12.
As shown in fig. 2, 5, and 6: the external cable 4 is an assembly, the plug material is metal (generally copper Cu), and the others are non-metal plastic (generally PA), and the plug is used as a socket for a lead of the internal coil 5 and an external cable. Wherein, a plug 4-1 of the external cable 4 is welded with the coil 5 through the pore passage 4-2, and when the plug 4-1 of the external cable 4 is electrified, the coil 5 in the high-speed switch valve is electrified. The rectangular groove 4-3 of the external cable 4 corresponds to a wire cable socket of a user side, so that the external cable can be conveniently installed and fixed. The inner circular ring surface 4-4 of the external cable 4 is matched with the coil 5 and the coil framework 6 through an injection molding process. The connecting boss 4-5 of the external cable 4 is embedded in the U-shaped groove 8-5 of the shell 8 for fixing.
As shown in fig. 2: the coil framework 6 is made of epoxy phenolic glass cloth, an annular groove 6-1 formed in the outer circumferential surface of the coil framework 6 is used for winding the coil 5, the wound coil 5 and the coil framework 6 are integrally subjected to an injection molding packaging process with the external cable 4, and the whole coil framework is arranged in the inner circular surface 8-3 of the shell 8.
As shown in fig. 2: the sleeve type armature 7 is made of soft magnetic material electric pure iron DT4C and is axisymmetric as a whole. The armature inner circle surface 7-1 of the sleeve type armature 7 forms interference fit with the slider outer circle surface one 3-1, and the tolerance of the interference fit is H7/s 6. When the coil 5 is electrified, the working air gap C between the sleeve-type armature 7 and the upper magnetic yoke 1 is reduced, the sleeve-type armature 7 is subjected to upward electromagnetic force, overcomes the spring force to drive the push rod 12 to move upwards, the first 12-3 excircle step surface of the push rod 12 compresses the oil discharge port valve port B, and the oil discharge port valve port B is closed. The ball core 14 moves upward under the pressure of the inlet oil, and the inlet valve port a opens.
As shown in fig. 2, 7, and 8: the shell 8 is made of soft magnetic material electric pure iron DT4C, the inner cavity of the shell 8 is a stepped inner cavity, a first shell inner circle surface 8-1 at the upper end of the inner cavity of the shell 8 is in clearance fit with a first outer circle surface 1-1 of the upper magnetic yoke, and a first shell step surface 8-2 below the first shell inner circle surface 8-1 is used as a positioning compression surface for the rolling closing-in of the upper magnetic yoke 1. The coil 5, the coil framework 6 and the external cable 4 are arranged in the second shell inner circle surface 8-3 below the first shell step surface 8-2, the second shell step surface 8-4 below the second shell inner circle surface 8-3 serves as a pressing action surface of the first lower magnetic yoke shoulder surface 10-2, the U-shaped groove 8-5 formed in the shell wall of the shell 8 is used for embedding the connecting boss 4-5 of the external cable 4, and the third shell inner circle surface 8-6 at the bottom of the shell 8 is used for penetrating out and fixing the lower magnetic yoke 10.
As shown in fig. 2: the sleeve type sliding rail II 9 is made of alloy steel, the outer circular surface 9-1 of the sliding rail of the sleeve type sliding rail II 9 is in interference fit with the inner circular surface one 10-3 of the lower magnetic yoke, the fit tolerance is generally H7/s6, the inner circular surface 9-2 of the sliding rail II is in clearance fit with the outer circular surface one 3-1 of the sliding block, the requirement on the roughness of the inner circular surface is high (Ra0.4-0.8), and a low-friction track is provided for the reciprocating motion of the sliding block 3.
As shown in fig. 2 and 9: the lower yoke 10 is made of soft magnetic material, namely, electrician pure iron DT4C, and is axially symmetrical as a whole. The middle part of the lower magnetic yoke 10 is provided with a lower magnetic yoke boss, a first outer circular surface 10-1 below the lower magnetic yoke boss is in interference fit with a first valve body inner circular surface 11-1 of the valve body 11, the interference fit tolerance is generally H7/s6, a first lower magnetic yoke shoulder surface 10-2 of the lower magnetic yoke boss is embedded in the shell 11, the inner cavity of the lower magnetic yoke 10 is a coaxial reducing cavity, a first lower magnetic yoke inner circular surface 10-3 at the middle end of the inner cavity of the lower magnetic yoke 10 is in interference fit with a second sliding rail outer circular surface 9-1, the interference fit tolerance is generally H7/s6, a second lower magnetic yoke outer circular surface 10-4 end part at the upper end of the lower magnetic yoke 10 is provided with a lower magnetic yoke angle 10-5 for changing the direction of magnetic force lines, a second lower magnetic yoke inner circular surface 10-6 at the upper end of the inner cavity of the lower magnetic yoke 10 is used for up-down sliding of the sleeve type armature 7, a lower magnetic yoke center hole 10-7 at the lower end of the inner cavity of the lower magnetic yoke 10 is used for penetrating the push rod 12, the spring force transmission from the sleeve armature 7 to the ball core 14 is realized.
As shown in fig. 2, 10, 11, and 12: the valve body 11 is made of alloy steel, a first valve body inner circle surface 11-1 at the upper end of the inner cavity of the valve body 11 is in interference fit with a first lower magnetic yoke outer circle surface 10-1, a third valve body inner circle surface 11-2 in the middle of the inner cavity of the valve body 11, the first rectangular groove 11-3 communicated with the outer side of the third inner circle surface 11-2 of the valve body and the outer circle surface 12-2 of the push rod 12 form a volume which is used as a communicating cavity for controlling pressure oil to be connected with the oil discharge port valve port B, the second inner circle surface 11-4 of the valve body communicated with the upper part of the third inner circle surface 11-2 of the valve body is used as a communicating cavity for the oil discharge valve port B and the oil discharge cavity y5, the fourth inner circle surface 11-5 of the valve body at the lower part of the inner cavity of the valve body 11 is used as an interference matching surface for embedding the valve seat 17, the first valve body shoulder surface 11-6 below the fourth valve body surface 11-5 is used as a positioning surface for embedding the valve seat 17, and the fifth valve body surface 11-7 at the bottom of the inner cavity of the valve body 11 is used as an embedding surface of the oil inlet filter screen 16. A chamber in which a push rod 12 is positioned in a valve body 11 is provided with a rectangular through groove I11-8, the rectangular through groove I11-8 is used as a channel for oil liquid flowing out of a valve port B of an oil discharge port, a chamber in which a ball core 14 is positioned in the valve body 11 is provided with a rectangular through groove II 11-9, the rectangular through groove II 11-9 is used as a channel for controlling the oil to flow out,
an annular groove IV 11-13, an annular groove I11-10, an annular groove II 11-11 and an annular groove III 11-12 are sequentially formed in the outer circumferential surface of the valve body 11 from top to bottom, the annular groove I11-10 arranged below the rectangular through groove I11-8 is used for placing the sealing ring I13, the annular groove II 11-11 arranged on the outer side of the rectangular through groove II 11-9 is used for placing the control port filter screen 18, the annular groove III 11-12 is used for placing the sealing ring II 15, and the annular groove IV 11-13 is used for mounting and fixing the whole pressure reducing valve with an external device.
As shown in fig. 2 and 13: the push rod 12 is made of duralumin LC9, the round-corner end 12-1 of the push rod 12 is propped against the end face 3-6 of the slide block shaft, the outer circle face 12-2 of the push rod 12 is embedded into the inner circle face two 10-6 of the lower magnetic yoke, the push rod 12 is provided with a push rod baffle, the step face one 12-3 of the outer circle face of the push rod baffle and the end face of the inner circle face three 11-2 of the valve body form an oil discharge port valve port B, and the flat-circle face end 12-4 of the push rod 12 is propped against the ball core 14.
As shown in fig. 2: the ball core 14 is made of bearing steel and used as a valve core of a pressure reducing valve. When the coil 5 is not electrified, the adjusting spring 19 provides spring force, the slide block 3 and the push rod 12 act on the spherical surface of the ball core 14, so that the ball core 14 is tightly pressed on the valve seat conical surface 17-2 of the valve seat 17, the oil inlet valve port A is closed, and the oil outlet valve port B is opened; when the coil 5 is electrified, the sleeve-type armature 7 is subjected to upward electromagnetic force, the push rod 12 is driven to move upwards through the slide block 3, the ball core 14 moves upwards under the hydraulic pressure of inlet oil pressure, the valve port A of the oil inlet is opened, and the valve port B of the oil outlet is closed.
As shown in fig. 2 and 14: the valve seat 17 is made of alloy steel, a first valve seat excircle surface 17-1 of the valve seat 17 is in interference fit with a fourth valve body inner circle surface 11-5 of the valve body 11, the fit tolerance is H7/s6, and the end surface of the valve seat 17 is a valve seat conical surface 17-2 which is matched with the ball core 14 to form an oil inlet valve port A. The valve seat center hole 17-3 of the valve seat 17 forms an oil inlet oil chamber y 1.
As shown in fig. 2: the adjusting spring 19 is made of 40Cr and is integrally arranged in the circular groove 3-4 at the shaft end of the sliding block 3, one end of the adjusting spring presses the step surface 3-5 of the circular groove, and the other end of the adjusting spring presses the second screw shoulder surface 20-3 of the adjusting screw 20.
As shown in fig. 2, 15, and 16: the adjusting screw 20 is made of alloy steel and integrally embedded into a central threaded hole 1-4 of the upper magnetic yoke, a screw step surface I20-1 of the adjusting screw 20 is pressed on a step surface I1-5 of the upper magnetic yoke, a tip 20-2 of the adjusting screw 20 penetrates into the adjusting spring 19 to provide spring guidance, and a screw step surface II 20-3 at the lower part of the adjusting screw 20 presses one end of the adjusting spring 19. The cross-shaped recess 20-4 of the end face of the adjusting screw 20 is used for external screwdriver tightening.
As shown in fig. 2: the inlet strainer 16, which is disposed in the valve body inner circumferential surface five 11-7, for preventing external dust particles from entering the oil inlet chamber y 1; and the control port filter screen 18 is arranged in the second annular groove 11-11 of the valve body and is used for preventing external dust particles from entering the control cavity y 2.
As shown in fig. 2: the first sealing ring 13 and the second sealing ring 15 are O-shaped sealing rings and are made of hydrogenated nitrile rubber. The first sealing ring 13 is placed in the first annular groove 11-10 of the valve body to ensure the sealing performance of the oil relief cavity y5 and the control cavity y2, and the second sealing ring 15 is placed in the third annular groove 11-12 of the valve body to ensure the sealing performance of the control cavity y2 and the oil inlet y 1.
As shown in fig. 1 and 2: the relationship among the parts of the electro-hydraulic proportional pressure reducing valve main body is as follows: the lower magnetic yoke 10 is placed from the inner circle surface two 8-3 of the shell, the shoulder surface one 10-2 of the lower magnetic yoke is embedded in the shell 8, the sleeve type slide rail one 2 and the sleeve type slide rail two 9 are respectively in interference fit with the inner circle surface one 1-6 of the upper magnetic yoke and the inner circle surface one 10-3 of the inner circle surface of the lower magnetic yoke, the sleeve type armature 7 is embedded in the outer circle surface one 3-1 of the slide block 3 through interference fit, the adjusting spring 19 is integrally arranged in the shaft end circular groove 3-4 of the slide block 3, the coil 5, the coil framework 6 and the external cable 4 are embedded in the shell 8 after injection molding and packaging, the connecting boss 4-5 of the external cable 4 is embedded in the U-shaped groove 8-5 of the shell 8 to be fixed, the outer circle surface one 1-1 of the upper magnetic yoke is in clearance fit with the inner circle surface one 8-1 of the shell, the closing chamfer 1-2 of the outer circle surface is used as a pressing surface one 8-1 of the inner circle surface of the shell, the adjusting screw 20 is screwed into a threaded hole 1-4 in the center of the upper magnetic yoke, the lower part of the valve body 11 of the push rod 12 is embedded into a center hole 10-7 of the lower magnetic yoke, the valve body 11 of the ball core 14 is embedded into the lower part of the push rod 12 of the ball core 14, a first outer circle surface 17-1 of the valve seat and a fourth inner circle surface 11-5 of the valve body realize interference fit, the oil inlet filter screen 16 and the control port filter screen 18 are respectively embedded into a fifth inner circle surface 11-7 of the valve body and a second annular groove 11-11, and a first sealing ring 13 and a second sealing ring 15 are respectively embedded into a first annular groove 11-10 and a third annular groove 11-12 of the valve body.
The working process of the electro-hydraulic proportional pressure reducing valve of the invention is specifically described as follows: as shown in fig. 17-20, when the magnetic field is removed (when the coil is not energized), the magnetic field is transmitted to the ball core 14 through the slider 3 and the push rod 12 under the action of the spring force of the adjusting spring 19, so that the ball core 14 presses the valve seat conical surface 17-2 of the valve seat 17, the oil inlet valve port a is closed, the oil outlet valve port B is opened, the control chamber y2 is not communicated with the oil inlet chamber y1, the communication chamber one y3, the communication chamber two y4, and the oil outlet chamber y5 are communicated with the control chamber y2, the working oil in the control chamber y2 flows into the y oil outlet chamber 5 through the communication chamber one y3, the oil outlet valve port B, and the communication chamber two y4, and is released due to the communication with the atmosphere; when in an excitation state (when the coil is electrified), a loop magnetic flux D is generated among the upper magnetic yoke 1, the sleeve-type armature 7, the lower magnetic yoke 10 and the shell 8 (the trend of the loop magnetic flux is shown in figures 19 and 20), at the moment, the sleeve-type armature 7 is subjected to electromagnetic force opposite to initial spring force, under the action of the electromagnetic force, the sleeve-type armature 7 drives the slider 3 to overcome the spring force, a working air gap C is reduced to zero, at the moment, the ball core 14 is subjected to hydraulic pressure of the oil inlet cavity y1 to move upwards and leave the conical surface 17-2 of the valve seat, the valve port A of the oil inlet is opened, the valve port B of the oil outlet is closed, the control cavity y2 and the first communication cavity y3 are communicated with the oil inlet cavity y1, oil flows into the control cavity through the valve port A of the oil inlet, and the second communication cavity y4 and the first communication cavity y5 are not communicated with the first communication cavity y 3. The spring force output by the adjusting spring 19 can be adjusted by changing the screwing depth of the adjusting screw 20, and the electromagnetic force received by the sleeve type armature 7 can be adjusted by adjusting the current in the coil 5. The electromagnetic force is independent of the position of the sleeve-type armature 7, and is only dependent on the magnitude of the current of the coil 5, and the current and the electromagnetic force have a proportional relationship. The oil output from the throttling and pressure-reducing control cavity of the valve port A of the oil inlet is used for controlling the pressure and the flow of a pilot oil cavity of a clutch main valve.
It is to be understood that the present invention has been described with reference to certain embodiments, and that various changes in the features and embodiments, or equivalent substitutions may be made therein by those skilled in the art without departing from the spirit and scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.
Claims (9)
1. An electro-hydraulic proportional pressure reducing valve for engineering vehicles comprises a shell (8), a valve body (11) arranged on the shell (8), a valve core arranged in the valve body (11), an electromagnetic assembly arranged in the shell (8) and an armature assembly; the method is characterized in that: the armature component comprises a push rod (12), a slide block (3), a sleeve type armature (7), a sleeve type slide rail I (2) and a sleeve type slide rail II (9); the sleeve type slide rail I (2) and the sleeve type slide rail II (9) are oppositely arranged at the center of the electromagnetic component, the sleeve type armature iron (7) is arranged between the sleeve type sliding rail I (2) and the sleeve type sliding rail II (9) and is fixedly sleeved on the sliding block (3), the slide block (3) slides in the clearance between the sleeve type slide rail I (2) and the sleeve type slide rail II (9), the upper end of the slide block (3) is connected with an adjusting spring (19) of an electromagnetic component, the lower end of the slide block (3) is contacted with a push rod (12), the slide block (3) transmits the electromagnetic force applied to the sleeve type armature iron (7) to the push rod (12), simultaneously, the spring force of the adjusting spring (19) is transmitted to the push rod (12), the lower end of the push rod (12) is contacted with the valve core, the valve core is matched with a valve seat (17) of the valve body (11) to form an oil inlet valve port A, and the push rod (12) is matched with the valve seat (17) to form an oil outlet valve port B.
2. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 1, characterized in that: the electromagnetic assembly comprises an upper magnet yoke (1), an external cable (4), a coil framework (6), a lower magnet yoke (10) and an adjusting spring (19); the coil (5) is wound on the outer circumferential surface of the coil framework (6), the external cable (4) is connected with the coil (5), the coil framework (6) and the external cable (4) are subjected to an integral injection molding packaging process, and the coil framework, the coil framework and the external cable are integrally installed in the shell (8); the upper magnetic yoke (1) and the lower magnetic yoke (10) are respectively installed in the shell (8), the upper magnetic yoke (1) is sleeved on the outer side of the sleeve-type sliding rail I (2) in an interference mode, the lower magnetic yoke (10) is sleeved on the outer side of the sleeve-type sliding rail II (9) in an interference mode, the adjusting spring (19) is arranged in the circular groove (3-4) at the shaft end of the upper magnetic yoke (1), and the lower end of the adjusting spring compresses the sliding block (3).
3. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 2, characterized in that: an upper magnetic yoke angle (1-9) is arranged at the end part of the bottom surface of the upper magnetic yoke (1), and the angle of the upper magnetic yoke angle (1-9) is 25-45 degrees; the upper end of the lower magnetic yoke (10) is provided with a lower magnetic yoke angle (10-5), the angle of the lower magnetic yoke angle (10-5) is 15-35 degrees, and the upper magnetic yoke angle (1-9) and the lower magnetic yoke angle (10-5) are used for changing the direction of magnetic lines of force.
4. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 2, characterized in that: an adjusting screw (20) is installed in the inner cavity of the upper magnetic yoke (1), and the lower end of the adjusting screw (20) presses the lower end of the adjusting spring (19) and is used for adjusting the elasticity of the adjusting spring (19).
5. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 1, characterized in that: the valve core adopts a ball core (14), a push rod baffle is arranged on the push rod (12), the push rod baffle is inserted into an inner cavity of the valve body (11) and forms an oil discharge port valve port B with the valve body (11), a valve seat (17) is installed in the valve body (11), the end surface of the valve seat (17) is a valve seat conical surface (17-2), and the valve seat conical surface (17-2) is matched with the ball core (14) to form an oil inlet valve port A.
6. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 5, characterized in that: a first rectangular through groove (11-8) is formed in a cavity where a push rod (12) in a valve body (11) is located, the first rectangular through groove (11-8) serves as a channel for oil outflow from an oil discharge port valve port B, a second rectangular through groove (11-9) is formed in a cavity where a ball core (14) in the valve body (11) is located, and the second rectangular through groove (11-9) serves as a channel for controlling oil outflow.
7. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 6, characterized in that: the outer circumferential surface of the valve body (11) is sequentially provided with a fourth annular groove (11-13), a first annular groove (11-10), a second annular groove (11-11) and a third annular groove (11-12) from top to bottom, the first annular groove (11-10) arranged below the first rectangular through groove (11-8) is used for placing the first sealing ring (13), the second annular groove (11-11) arranged on the outer side of the second rectangular through groove (11-9) is used for placing a control port filter screen (18), the third annular groove (11-12) is used for placing the second sealing ring (15), and the fourth annular groove (11-13) is used for installing and fixing the whole pressure reducing valve and an external device.
8. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 2, characterized in that: the roughness of the inner circular surface of the first sleeve-type sliding rail (2) is Ra0.4-0.8, the roughness of the inner circular surface of the second sleeve-type sliding rail (9) is Ra0.4-0.8, and a low-friction track is provided for the reciprocating motion of the sliding block (3).
9. The electro-hydraulic proportional pressure reducing valve for engineering vehicles according to claim 6, characterized in that: and a second lower magnetic yoke inner circle surface (10-6) at the upper end of the inner cavity of the lower magnetic yoke (10) is used for sliding the sleeve-type armature (7) up and down, and a lower magnetic yoke center hole (10-7) at the lower end of the inner cavity of the lower magnetic yoke (10) is used for penetrating the push rod (12), so that the spring force transmission from the sleeve-type armature (7) to the ball core (14) is realized.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111643349.3A CN114233869A (en) | 2021-12-29 | 2021-12-29 | Electro-hydraulic proportional pressure reducing valve for engineering vehicle |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111643349.3A CN114233869A (en) | 2021-12-29 | 2021-12-29 | Electro-hydraulic proportional pressure reducing valve for engineering vehicle |
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| CN114233869A true CN114233869A (en) | 2022-03-25 |
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| CN202111643349.3A Withdrawn CN114233869A (en) | 2021-12-29 | 2021-12-29 | Electro-hydraulic proportional pressure reducing valve for engineering vehicle |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115932683A (en) * | 2023-02-20 | 2023-04-07 | 无锡学院 | Electromagnetic force testing device and method for electromagnetic valve |
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| CN111102362A (en) * | 2020-01-16 | 2020-05-05 | 北京理工大学 | Plug-in type proportional solenoid valve for clutch control |
| CN111927980A (en) * | 2020-08-05 | 2020-11-13 | 北京理工大学 | High-speed proportional electromagnetic valve for vehicle and hydraulic assembly |
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| JP2007092874A (en) * | 2005-09-28 | 2007-04-12 | Time Engineering Co Ltd | Solenoid valve |
| CN101842625A (en) * | 2007-08-04 | 2010-09-22 | 谢夫勒科技有限两合公司 | Electromagnetic actuating unit |
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Application publication date: 20220325 |