WO2012013158A1 - Valve hydraulique, ensemble valve hydraulique et procédé de commande de valve hydraulique - Google Patents

Valve hydraulique, ensemble valve hydraulique et procédé de commande de valve hydraulique Download PDF

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Publication number
WO2012013158A1
WO2012013158A1 PCT/CN2011/077809 CN2011077809W WO2012013158A1 WO 2012013158 A1 WO2012013158 A1 WO 2012013158A1 CN 2011077809 W CN2011077809 W CN 2011077809W WO 2012013158 A1 WO2012013158 A1 WO 2012013158A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
hydraulic
sleeve
spool
core
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2011/077809
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English (en)
Chinese (zh)
Inventor
易小刚
刘永东
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hunan Sany Intelligent Control Equipment Co Ltd
Sany Heavy Industry Co Ltd
Original Assignee
Hunan Sany Intelligent Control Equipment Co Ltd
Sany Heavy Industry Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hunan Sany Intelligent Control Equipment Co Ltd, Sany Heavy Industry Co Ltd filed Critical Hunan Sany Intelligent Control Equipment Co Ltd
Publication of WO2012013158A1 publication Critical patent/WO2012013158A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • 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
    • F16K27/04—Construction of housing; Use of materials therefor of sliding valves
    • F16K27/041—Construction of housing; Use of materials therefor of sliding valves cylindrical slide valves

Definitions

  • Hydraulic valve, hydraulic valve group and hydraulic valve control method The present application claims the invention patent application No. 201010240847.9 entitled "Hydraulic valve, hydraulic valve group and hydraulic valve control method" submitted to the State Intellectual Property Office of China on July 30, 2010 Priority is hereby incorporated by reference in its entirety.
  • BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the field of hydraulic transmission and control technology, and more particularly to a hydraulic valve and a hydraulic valve group for controlling a flow direction or a liquid flow rate in a hydraulic system, and to a control method for the hydraulic valve.
  • Hydraulic valves for fluid direction control or flow control in hydraulic systems are widely used and come in many varieties.
  • FIG. 1 shows a prior art slide valve type hydraulic valve structure.
  • the hydraulic valve includes a first end cap, a first return spring 2', an integral spool 3', a valve body 4', a second return spring 5', and a second end cap 6'.
  • the integral spool 3' is disposed in the cavity of the valve body 4', is centered by the first return spring 2' and the second return spring 5', and is held in the neutral position.
  • the hydraulic pressure on both sides of the hydraulic valve is introduced by the X' and Y' ports. As shown in Fig.
  • the entire hydraulic valve is scrapped.
  • the valve core 3' is integral and the mating surface with the valve body 4' is long, the inner hole of the valve body 4' is processed for a long length, and the machining accuracy is difficult to ensure, and it is difficult to ensure a small and uniform assembly requirement. Clearance.
  • the excessive clearance between the valve core 3' and the valve body 4' leads to an increase in leakage between the internal bores, which affects the working performance of the reversing valve. If the clearance is too small, the spool 3' is easily issued, resulting in no commutation. normal.
  • a hydraulic valve includes a valve body, a valve core and a valve sleeve, the valve core is disposed in a cavity of the valve body, and the valve sleeve is sleeved on the valve core, the valve
  • the sleeve is a split valve sleeve, and includes at least a first valve sleeve and a second valve sleeve.
  • the valve core is a split valve core, and includes at least a first valve core and a second valve core.
  • valve sleeve is a stepped valve sleeve, and the cavity of the valve body is also arranged in a stepped manner to match the stepped structure of the valve sleeve. Further, the valve sleeve is provided with an oil passage corresponding to the pressure oil port on the valve body, and the valve sleeve and the valve body are sealed by a sealing ring.
  • the hydraulic valve further includes: a first following spring directly contacting the end of the first valve core; and a second following spring directly contacting the end of the second valve core,
  • the first follower spring and the second follower spring are configured to keep the first valve core and the second valve core in abutting state, wherein a portion where the first valve core and the second valve core abut each other is discharged through the drain port R
  • the hydraulic oil in the cavity at the outlet of the valve plug further includes a third valve core, and the third valve core is disposed between the first valve core and the second valve core.
  • the hydraulic valve further includes a third valve sleeve, and the third valve sleeve is matched with the third valve core.
  • the hydraulic valve is an electromagnetically driven hydraulic valve, and the end of the first valve core and the end of the second valve core are respectively provided with a first electromagnet and a second electromagnet for operating the valve The action of the core.
  • the hydraulic valve is a flow valve, and the electromagnet is a proportional electromagnet for controlling the flow rate through the flow valve through the current control through the proportional electromagnet.
  • the axis of the first spool is different from the axis of the second spool. Further, the outer diameters of the first valve core and the second valve core are different.
  • a control method for a hydraulic valve as described above wherein a drain port R on the valve body serves as a control port K at the same time, when the spool is at the center, left and right
  • the leakage oil between the first valve core and the second valve core is discharged through the rake, when the rake introduces the pressure oil, the first spool moves to the left, and the second spool to the right Movement, at this time, the mouth on the valve body communicates with the mouth, and the P port communicates with the B port to achieve four functions.
  • a hydraulic valve block includes a valve core, a valve sleeve and a valve block, the valve sleeve is sleeved on the valve core, the valve core is a split valve core, and includes a first valve core And the second valve core, the valve sleeve is a split valve sleeve, including a first valve sleeve and a second valve sleeve, and the valve core and the valve sleeve are integrated into the valve block.
  • a hydraulic control system is provided that includes a hydraulic valve or hydraulic valve block as previously described. The hydraulic valve according to the present invention has the following advantages:
  • valve core no longer directly cooperates with the valve body, but instead cooperates with the valve sleeve to transfer the high precision requirement from the valve body to the valve sleeve.
  • the valve sleeve can be processed separately, the processing is very convenient, the precision is easy to guarantee, and the processing precision of the valve body is greatly reduced.
  • the valve sleeve and the valve core adopt the split structure, which greatly shortens the matching length of the valve core with the valve sleeve and the valve body.
  • the hole in the valve body can be processed separately from both sides, which greatly reduces the processing difficulty.
  • the coaxiality between the inner holes on both sides of the valve body is greatly reduced. There is no need for coaxiality between the first valve sleeve and the second valve sleeve, and the first valve core and the second valve core do not require the same outer diameter. Even allowing eccentricity, the two valve cores can be machined separately.
  • the first valve core and the first valve sleeve need only be processed in a complete process, and the second valve core and the second valve sleeve are processed in a complete set, which is extremely convenient to process.
  • the valve plug and the valve sleeve A suitable and uniform gap between the two, reduces the risk of stagnation, strong anti-pollution ability, and because the spool is separated, the valve can be used to eliminate the stuck of the other spool through one spool, so that the hydraulic valve
  • the work efficiency and work stability are greatly improved.
  • the split valve core wears evenly during the commutation process, which can improve the life of the spool and improve the service life of the hydraulic valve. Due to the disassembly of the split valve sleeve, one of the spools can be replaced separately or the valve sleeve can be repaired and compensated for by replacing the valve sleeve. The interchangeability and reusability of the components are good, and the use cost is reduced.
  • the prior art hydraulic valve body can only be formed by casting.
  • the valve core and the valve sleeve adopt a split structure, the processing is convenient, and the valve body can be realized by a forging.
  • FIG. 1 is a schematic structural view of a prior art hydraulic valve
  • FIG. 1a is a schematic view of a prior art hydraulic valve in a left position
  • FIG. 1a is a schematic view of a prior art hydraulic valve in a left position
  • FIG. 1b is a schematic view of a prior art hydraulic valve in a right position during operation;
  • 2 is a schematic structural view of a hydraulic valve according to a first embodiment of the present invention;
  • FIG. 2a is a schematic view showing a hydraulic valve according to a first embodiment of the present invention when it is in a left position;
  • FIG. 2b is a diagram according to the present invention.
  • FIG. 3 is a schematic structural view of a hydraulic valve according to a second embodiment of the present invention;
  • FIG. 4 is a schematic structural view of a hydraulic valve according to a third embodiment of the present invention
  • 5 is a schematic structural view of a hydraulic valve according to a fourth embodiment of the present invention
  • 5a is a schematic structural view of a hydraulic valve according to a modification of the fourth embodiment of the present invention
  • FIG. 6 is a schematic structural view of a hydraulic valve according to a fifth embodiment of the present invention
  • FIG. 6a is a flow valve according to the present invention.
  • Figure 6b is a schematic view showing the structure of a hydraulic valve according to the present invention when it is manually driven
  • Figure 7 is a schematic view showing the structure of a hydraulic valve according to a sixth embodiment of the present invention
  • Figure 8 is a seventh embodiment of the present invention.
  • FIG. 9 shows a structure in which the split valve core and the valve sleeve have different lengths in the hydraulic valve according to the present invention
  • FIG. 10 shows that the hydraulic valve according to the present invention adds a control port to realize four positions.
  • Schematic diagram of the function control method FIG. 10a is a schematic view of the two hydraulic valve spools in the hydraulic valve control method shown in FIG. 10; and
  • FIG. 11 shows the valve core and the valve sleeve integrated into the valve according to the present invention.
  • the structure of the hydraulic valve block is formed in the block. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS It should be noted that the embodiments in the present application and the features in the embodiments may be combined with each other without conflict.
  • the hydraulic valve includes a valve body 10, a valve core and a valve sleeve, the valve sleeve is sleeved on the valve core, and the valve core and the valve sleeve are disposed in the cavity of the valve body 10.
  • the valve core is a split valve core, and includes a first valve core 31 and a second valve core 32.
  • Both valve cores are disposed in the cavity of the valve body 10, and abut each other, and the valve sleeve is
  • the split valve sleeve includes a first valve sleeve 21 and a second valve sleeve 22, which are respectively sleeved on the first valve core 31 and the second valve core 32.
  • a reset mechanism is further included, and the reset mechanism is disposed at an end of the spool for driving the spool to be reset.
  • the reset mechanism includes a first elastic member 51 and a second elastic member 52.
  • the first elastic member 51 is disposed at an end of the first valve core 31 for pressing the end of the first valve core 31.
  • the second elastic member 52 is disposed at the end of the second valve core 32 for pressing the end of the second valve core 32.
  • the resilient member described above may be a spring or other component or mechanism that enables the spool 30 to be reset.
  • the hydraulic valve of the present invention is further provided with an end cap assembly, including a first end cap assembly 71 and a second end cap assembly 72, which are respectively disposed at both ends of the valve body 10, and are used for accommodating and positioning.
  • the first elastic member 51 and the second elastic member 52 are respectively disposed at both ends of the valve body 10.
  • the specific form of the first spool 31 and the second spool 32 can be specifically designed according to the required median function, and the two spools 31, 32 are held in the middle by the resultant force of the first elastic member 51 and the second elastic member 52. Bit. It can be understood that when the valve body 10 corresponding to the valve sleeve is provided with an oil port, an oil port corresponding to the oil port on the valve body 10 is also provided on the valve sleeve. As shown in Fig. 2, a sealing ring 40 is provided between the valve sleeve and the valve body 10 for sealing action. Preferably, the sealing ring 40 is a 0-type sealing ring. As shown in FIG.
  • the pressure oil is introduced into the cavity of the second elastic member 52 through the Y port, and the second valve core 32 and the first valve core 31 can be pushed to the left side of the valve body 10 at the same time to realize the P port and the B. Port, A port and T port.
  • the sealing between the valve body and the valve sleeve is achieved by the sealing ring, the machining precision of the inner hole of the valve body 10 is reduced, and the valve body and the valve in the conventional hydraulic valve are simultaneously
  • the cooperation of the core is transferred between the inner hole of the valve sleeve and the valve core, and the valve sleeve can be processed separately, the processing is extremely convenient, and the precision is easy to ensure.
  • the valve sleeve is of a split type, the inner hole of the valve body 10 can be separately processed from both sides, and the processing length on both sides is reduced, which is easy to realize, and the coaxiality between the inner holes on both sides of the valve body 10 is greatly required.
  • first valve sleeve 21 lowering, there is no need for coaxiality between the first valve sleeve 21 and the second valve sleeve 22.
  • first spool 31 and the second spool 32 since the position of the first spool 31 and the second spool 32 is not high after the valve core of the present invention is changed from the conventional integral type, only the first spool 31 and the first valve are required.
  • a valve sleeve 21 is processed in a complete set, and the second valve core 32 and the second valve sleeve 22 are processed in a complete set.
  • the first valve core 31 and the second valve core 32 can be separately processed, and the processing is convenient.
  • the outer diameters of the first valve body 31 and the second valve body 32 are not required to be uniform, and the function can be realized even if the eccentricity is achieved.
  • the spool operation mode can still be realized in accordance with the conventional hydraulic valve, and the neutral function that can be realized when the conventional hydraulic valve is used as the reversing valve can be realized.
  • the hydraulic valve adopts the split valve sleeve and the valve core the first valve core 31 and the second valve core 32 are separately processed, the machining precision and the assembly precision are easily ensured, and the assembly is convenient, the valve core mating length is shortened, and the jam is reduced. Hidden danger, and the action of the spool can be used to eliminate the jam of the other spool with one spool.
  • the two spools wear evenly during the commutation process, which increases the life of the spool and increases the life of the hydraulic valve.
  • One of the spools can be replaced or replaced by a valve sleeve to repair and compensate for the wear of the spool.
  • the interchangeability is good, the reusability is good, and the use cost is reduced.
  • the embodiment of the above FIG. 2 of the present invention provides a three-position four-way hydraulic valve, and the valve body and the valve sleeve are provided with corresponding pressure oil ports (P), oil return ports (T), and first working oil ports. ( ⁇ ), the second working port ( ⁇ ), and the drain port (R), the drain port (R) is set between the first spool (31) and the second spool (32) .
  • FIG. 3 is a schematic view showing the structure of a hydraulic valve according to a second embodiment of the present invention. As shown in the figure, in the embodiment, the first valve body 31 and the second valve body 32 of the split type are also provided. A valve sleeve 21 and a second valve sleeve 22.
  • first valve sleeve 21 and the second valve sleeve 22 are designed in a stepped manner, and the cavity of the valve body 10 is also arranged in a stepped manner, and the stepped structure of the first valve sleeve 21 and the second valve sleeve 22 Match.
  • the stepped valve sleeve structure described above provides great convenience for the installation of the first valve sleeve 21 and the second valve sleeve 22, and is convenient to be assembled from the opposite direction to the valve body 10 by the sealing manner of the 0-type sealing ring 40. In the middle, it is possible to avoid scratching the 0-ring 40.
  • the sealing is performed by means of the 0-type sealing ring 40, and the first valve sleeve 21 and the second valve sleeve 22 are easily taken out from the valve body 10 and repeatedly assembled from the opposite direction.
  • the contact surface of the first spool 31 and the second spool 32 communicates with the drain port R, and the leakage oil between the first spool 31 and the second spool 32 can be returned to the tank. It is prevented from being separated by the oil pressure generated between the first valve body 31 and the second valve body 32, and the commutation cannot be synchronized.
  • a third embodiment of the present invention is also provided.
  • a hydraulic valve structure according to a third embodiment of the present invention is shown.
  • the first elastic member 51 is disposed in the first end cap assembly 71 and abuts against the end of the first valve core 31 through a first sleeve member 61
  • the second elastic member 52 is disposed at the second end.
  • the cover assembly 72 is seated against the end of the second spool 32 by a second sleeve member 62.
  • a first follower spring 81 is disposed in the first sleeve member 61.
  • first follower spring 81 directly abuts the end of the first spool 31; the second follower spring 82 is disposed in the second Sleeve member 62 The one end of the second following spring 82 directly abuts the end of the second valve body 32.
  • the first follower spring 81 and the second follower spring 82 are used to maintain the first spool 31 and the second spool 32 in an abutting state. During the entire stroke of the spool movement, the first follower spring 81 and the second follower spring 82 will always follow the mating faces of the first spool 31 and the second spool 32, that is, always maintain contact with the spool. .
  • the center of the spool is still maintained by the resultant force of the first elastic member 51 and the second elastic member 52.
  • the second spool 32 has been separated from the second elastic member 52.
  • the first elastic member 51 will push the first spool 31 and the second spool 32 to the neutral position, and the second spool 32 is caused by the transient hydraulic power when the spool is actuated.
  • the first spool 31 is separated to affect the commutation stability of the hydraulic valve, and the added first follower spring 81 is always attached to the left end surface of the first spool 31 to generate a top pressure on the first spool 31, thereby maintaining The first valve body 31 is in contact with the second valve body 32.
  • the first spool 31 and the second spool 32 are in the right position of the valve body 10
  • the first spool 31 has been separated from the first elastic member 51, and after the control oil is released from the X port, the second The elastic member 52 will push the second valve core 32 and the first valve core 31 to move to the neutral position.
  • the transient hydraulic power during the action of the spool will separate the first valve core 31 from the second valve core 32, affecting the hydraulic valve.
  • Fig. 5 shows a hydraulic valve structure according to a fourth embodiment of the present invention. As shown in FIG. 4 and other figures, the portion of the first spool 31 and the second spool 32 abutting each other through the drain port R to discharge the hydraulic oil in the cavity of the spool body to maintain the first The end surface of the spool 31 is in abutment with the end surface of the second valve body 32.
  • Fig. 5 shows a hydraulic valve structure according to a fourth embodiment of the present invention. As shown in FIG.
  • a third spool 33 may be further included, and the third spool 33 is disposed between the first spool 31 and the second spool 32.
  • Fig. 5a shows the structure of a modification of the hydraulic valve according to the fourth embodiment of the present invention.
  • the hydraulic valve also includes a third valve sleeve 23 that mates with the third valve core 33.
  • the embodiment of FIG. 5a of the present invention provides a three-position six-way hydraulic valve, and the valve body and the valve sleeve are provided with corresponding pressure oil ports (P), oil return ports (T), and first work.
  • FIG. 6 is a schematic view showing the structure of a hydraulic valve according to a fifth embodiment of the present invention.
  • the hydraulic valve is an electromagnetically driven hydraulic valve, and the end of the first valve core 31 and the end of the second valve core 32 are respectively provided with the first electromagnetic The iron 91 and the second electromagnet 92 are used to operate the spool. As shown in Fig.
  • the hydraulic valve of the present invention can also be used as a flow valve.
  • the electromagnets on both sides are proportional electromagnets 93 and 94.
  • the electromagnet of the proportional electromagnet The force is adjusted by the current of the proportional electromagnet, and the appropriate electromagnetic force is obtained by controlling the current through the proportional electromagnets 93, 94, and the magnitude of the electromagnetic force determines the displacement of the spool, thereby obtaining the displacement of the spool 31, 32.
  • the hydraulic valve of the present invention may also be a manually driven hydraulic valve, and 95, 96 are manual drive handles.
  • Fig. 7 it is a structure of a hydraulic valve according to a sixth embodiment of the present invention.
  • the axis of the first spool 31 is different from the axis of the second spool 32, and the distance between the two axes is shown as L1.
  • a step surface 311 and a step surface 321 are respectively disposed on the first valve core 31 and the second valve core 32, and an outer diameter of the step surface 311 of the first valve core 31 is smaller than an outer diameter of the second valve core 32,
  • the outer diameter of the stepped surface 321 of the two valve cores 32 is smaller than the outer diameter of the first valve body 31 so that no interference occurs between the respective stepped surfaces and the corresponding valve core holes. Therefore, in the state where the axes of the first valve body 31 and the second valve body 32 are deviated, the normal operation of the valve body can still be achieved.
  • Figure 8 is a schematic view showing the structure of a hydraulic valve according to a seventh embodiment of the present invention. As shown in FIG.
  • the outer diameters of the first valve body 31 and the second valve body 32 may be different.
  • the outer diameter of the first valve body 31 shown in Fig. 8 is L2
  • the outer diameter of the second valve body 32 is L3. It is not difficult to understand that due to the split valve core structure adopted by the present invention, the normal operation of the hydraulic valve can still be achieved in the case where the outer diameters of the two valve cores are different.
  • the oil port originally used as the drain port R can be used as the control oil port.
  • the oil ports, the first valve body 31 and the second valve core 32 maintain the neutral type 0 function under the action of the first elastic member 51 and the second elastic member 52, ⁇ , ⁇ , ⁇ oil ports are not connected to each other.
  • the first valve body 31 moves to the right, and the first valve core 31 transmits the force to the second valve core 32 through the abutting surface of the second valve body 32, and the second valve core 32 follows the first valve core 32.
  • a valve core 31 moves to the right, compresses the second elastic member 52 and realizes the left position function.
  • the P port communicates with the B port, and the A port communicates with the T port.
  • the spool returns to the neutral position under the force of the second elastic member 52.
  • the second valve core 32 moves to the left, and the second valve core 32 transmits the force to the first valve core 31 through the abutting surface of the first valve body 31, and the first valve core 31 follows The second valve core 32 moves to the left to compress the first elastic member 51 and realize the right position function.
  • the P port communicates with the A port, and the B port communicates with the T port. After the pressure oil is released, the spool returns to the neutral position under the force of the first elastic member 51.
  • the split valve sleeve and spool structure of the present invention can also be applied to other forms of hydraulic valves or hydraulic control systems.
  • a hydraulic valve block includes a valve core, a valve sleeve and a valve block 11
  • the valve sleeve is sleeved on the valve core
  • the valve core is a split valve core, including the first valve core 31.
  • the valve sleeve is a split valve sleeve, including a first valve sleeve 21 and a second valve sleeve 22, wherein the split valve cores 31, 32 and the valve sleeves 21, 22 are integrated into the valve block 11.
  • valve core and the valve sleeve can be conveniently integrated into the valve block to realize the function of the hydraulic valve.
  • the hydraulic valve group is different from the traditional independent structure hydraulic valve, because the valve core passes
  • the valve sleeve is directly inserted into the inner hole of the valve block, which can reduce the connection between the traditional hydraulic valve and the valve block, that is, reduce the leakage link, and the control and implementation are very convenient, and the design of the valve block can realize the rational layout of the entire hydraulic system. .
  • the integration of the spool into the valve block reduces the mass and volume of the entire valve block assembly, resulting in a significant reduction in material costs.
  • a hydraulic control system can be provided in accordance with the present invention, which includes the hydraulic valve or hydraulic valve block previously described.
  • the hydraulic valve and hydraulic valve block of the invention can be widely used in various construction machinery, including concrete machinery, road construction machinery, excavation machinery, lifting machinery, port machinery and pile machinery.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Multiple-Way Valves (AREA)

Abstract

L'invention concerne une valve hydraulique, un ensemble valve hydraulique et un procédé de commande de valve hydraulique. La valve hydraulique comprend un corps de valve (10), un mécanisme de valve, logé dans le corps de chambre du corps de valve, et un manchon de valve, disposé sur le mécanisme de valve et présentant une structure séparée, et comprenant un premier manchon de valve (21) et un second manchon de valve (22). La structure séparée du mécanisme de valve comprend un premier mécanisme de valve (31) et un second mécanisme de valve (32). L'ensemble valve hydraulique comprend un premier manchon de valve et un second manchon de valve à structure séparée, un premier mécanisme de valve et un second mécanisme de valve, le mécanisme de valve et le manchon de valve formant un bloc de valve (11). L'utilisation du mécanisme de valve et du manchon de valve à structure séparée permet de palier aux problèmes liés à la longueur de la surface de couplage du corps de valve et du mécanisme de valve de la valve hydraulique, à la difficulté de garantir la précision, aux inconvénients liés à l'usinage, au montage et à la réparation après usure de l'orifice de la valve. Le mécanisme de valve et le manchon de valve à structure séparée permettent l'agencement aisé du mécanisme de valve sans sans coincement, tout en préservant la résistance à la pollution. Les pièces sont facilement interchangeables, réparables et remplaçables, d'où un prolongement de leur durée de vie.
PCT/CN2011/077809 2010-07-30 2011-07-29 Valve hydraulique, ensemble valve hydraulique et procédé de commande de valve hydraulique Ceased WO2012013158A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201010240847.9 2010-07-30
CN2010102408479A CN101893011A (zh) 2010-07-30 2010-07-30 液压阀、液压阀组及其控制方法

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WO2012013158A1 true WO2012013158A1 (fr) 2012-02-02

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PCT/CN2011/077822 Ceased WO2012013160A1 (fr) 2010-07-30 2011-07-29 Valve hydraulique d'inversion, ensemble valve hydraulique d'inversion et procédé de commande de valve hydraulique d'inversion
PCT/CN2011/077809 Ceased WO2012013158A1 (fr) 2010-07-30 2011-07-29 Valve hydraulique, ensemble valve hydraulique et procédé de commande de valve hydraulique

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Application Number Title Priority Date Filing Date
PCT/CN2011/077822 Ceased WO2012013160A1 (fr) 2010-07-30 2011-07-29 Valve hydraulique d'inversion, ensemble valve hydraulique d'inversion et procédé de commande de valve hydraulique d'inversion

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WO2015071675A3 (fr) * 2013-11-15 2015-08-27 Blagdon Actuation Research Limited Soupapes asservies
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CN118391318A (zh) * 2024-04-10 2024-07-26 苏州航发航空零部件有限公司 一种二位三通液控换向阀
CN120506407A (zh) * 2025-06-30 2025-08-19 华中科技大学 一种管路破损自动关断阀及液压系统

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CN102297171A (zh) 2011-12-28
CN101893011A (zh) 2010-11-24

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