CN108412828B - Hydraulic control flow distribution valve - Google Patents
Hydraulic control flow distribution valve Download PDFInfo
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- CN108412828B CN108412828B CN201810258108.9A CN201810258108A CN108412828B CN 108412828 B CN108412828 B CN 108412828B CN 201810258108 A CN201810258108 A CN 201810258108A CN 108412828 B CN108412828 B CN 108412828B
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- 229910000831 Steel Inorganic materials 0.000 claims abstract description 33
- 239000010959 steel Substances 0.000 claims abstract description 33
- 230000000149 penetrating effect Effects 0.000 claims description 4
- 238000007789 sealing Methods 0.000 abstract description 16
- 230000007774 longterm Effects 0.000 abstract description 3
- 239000003921 oil Substances 0.000 description 85
- 239000010720 hydraulic oil Substances 0.000 description 17
- 239000002184 metal Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000032683 aging Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000004513 sizing Methods 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000002457 bidirectional effect Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000007747 plating Methods 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Check Valves (AREA)
Abstract
The invention discloses a hydraulic control flow distribution valve, which comprises a two-position five-way hydraulic lock, wherein the two-position five-way hydraulic lock comprises a valve body, a first interface and a fifth interface are sequentially arranged on the side wall of the valve body along the axial direction parallel to the valve body, the valve body is divided into an upper part and a lower part by a valve seat, a steel ball with an adjustable position is arranged in the upper part, a lining with a sliding cavity is arranged in the lower part, and a sliding valve rod capable of sliding along the axial direction of the valve body is arranged in the sliding cavity. The hydraulic cylinder adopts a two-position five-way hydraulic lock structure, and is matched with the inlet check valve and the bypass check valve, so that the functions of flow control and position self-locking are realized, two ends of the hydraulic cylinder with the traditional structure are sealed by the two check valves, only one check valve is needed instead, the sealing reliability is improved, and the long-term position self-locking of the hydraulic cylinder is facilitated. The bushing structure is arranged in the invention to control the clearance, so that the influence of temperature change on the movement fit clearance of the slide valve rod is reduced, and the possibility of occurrence of clamping stagnation is reduced.
Description
Technical Field
The invention relates to a hydraulic control flow distribution valve which is used for flow control, position self-locking and the like in hydraulic equipment such as electrohydraulic actuators and the like.
Background
The hydraulic control distributing valve is a core component for controlling the flow direction of the electrohydraulic actuator, and the tightness of the hydraulic control distributing valve determines the reliability of the position maintenance of the downstream hydraulic cylinder and influences the working efficiency of the upstream hydraulic pump. The traditional hydraulic control flow distribution valve generally adopts two structures, namely a double-conical surface sealing hydraulic lock, and the structure has a hard limit sealing condition and has poor sealing effect; the other structure is a two-position four-way hydraulic lock, and the structure ensures that two ends of a downstream hydraulic cylinder are sealed by two one-way valves, so that the leakage points are more, and the sealing reliability is low.
Disclosure of Invention
Aiming at the problems in the prior art, the invention aims to provide a hydraulic control distributing valve with good sealing performance and high reliability.
In order to realize the tasks, the invention adopts the following technical scheme:
The utility model provides a hydraulically controlled flow distribution valve, includes two-position five-way hydraulic lock, two-position five-way hydraulic lock include the valve body, set gradually first interface to fifth interface along being on the valve body lateral wall along being on a parallel with the valve body axial, separate into upper and lower two parts by the disk seat in the valve body, be provided with the steel ball of adjustable position in the upper portion, be provided with the bush that has the smooth chamber in the lower part, be equipped with the smooth valve rod that can follow valve body axial slip in the smooth chamber, wherein:
The first interface to the fourth interface are all communicated with the sliding cavity, a first oil passing hole to a third oil passing hole are formed in the sliding valve rod at intervals along the radial direction of the sliding valve rod, a push rod with the diameter smaller than that of the sliding valve rod is arranged at one end of the sliding valve rod, a limiting table with the length smaller than that of the push rod is arranged on the outer wall of the push rod, and a shaft side hole is formed in the position, facing the third oil passing hole, of the end face of the limiting table; the other end of the slide valve rod is axially provided with an axial hole which is communicated with the first oil passing hole and the second oil passing hole; the valve seat is provided with a locking hole, and the ejector rod can pass through the locking hole and be contacted with the steel ball; the fifth interface is communicated with the locking hole.
Further, a plug is arranged above the valve seat, and a gap is reserved between the plug and the valve seat; the lower surface of the plug is provided with a spring hole with the diameter larger than that of the steel ball along the axial direction of the plug, a self-locking spring is assembled in the spring hole, and the lower end of the self-locking spring is in contact with the steel ball; the outside of ejector pin cover be equipped with reset spring, reset spring's one end with the lower surface contact of disk seat, reset spring's the other end with the terminal surface contact of slide valve rod.
Further, the diameter of the part between the first oil passing hole on the slide valve rod and the other end of the slide valve rod is smaller than the diameter of the rest part on the slide valve rod.
Further, labyrinth seal groove groups are arranged on the slide valve rod between the first oil passing hole and the second oil passing hole, and between the third oil passing hole and the ejector rod.
Further, the inside smooth chamber of bush be the penetrating cavity of both ends and sizing, set gradually first oil guide hole to fourth oil guide hole along being on the bush outer wall along being parallel to the bush axial, first oil guide hole to fourth oil guide hole all along the circumferencial direction of bush on distribute a plurality of.
Further, the locking hole is a hole penetrating through the upper surface and the lower surface of the valve seat, the locking hole comprises a first taper hole positioned at the upper part and a second taper hole positioned at the lower part, and the first taper hole and the second taper hole are communicated through a connecting hole; the maximum inner diameter of the first taper hole is smaller than the diameter of the steel ball.
Further, a central hole with two through ends is arranged in the valve body, a step groove is arranged on the central hole, and a clamping table matched with the step groove is arranged on the outer wall of the bushing; the upper end of the valve body is sealed through an upper baffle, and the plug penetrates out of the upper baffle; the lower end of the valve body is sealed by a lower baffle.
Further, annular grooves corresponding to the positions of the first oil guide hole to the fourth oil guide hole are formed in the inner wall of the central hole at intervals.
Further, the two-position five-way hydraulic lock is provided with two parts, which are respectively marked as L and R, wherein: the first interfaces of the L and the R are connected to the hydraulic pump and are connected to the oil tank through a first inlet check valve and a second inlet check valve respectively; the first interface of the L is connected with the third interface of the R through a first bypass one-way valve, and the first interface of the R is connected with the third interface of the L through a second bypass one-way valve; the second interface of L is connected with the fourth interface of R, the fourth interface of L is connected with the second interface of R, and the fifth interfaces of L and R are respectively connected to two ends of the hydraulic cylinder.
The invention has the following technical characteristics:
1. The hydraulic cylinder adopts a two-position five-way hydraulic lock structure, and is matched with the inlet check valve and the bypass check valve, so that the functions of flow control and position self-locking are realized, two ends of the hydraulic cylinder with the traditional structure are sealed by the two check valves, only one check valve is needed instead, the sealing reliability is improved, and the long-term position self-locking of the hydraulic cylinder is facilitated.
2. The bushing structure is arranged in the invention, and adopts the same material as the sliding valve rod to control the clearance, and the high-low temperature aging treatment is carried out together, so that the influence of temperature change on the sliding valve rod movement fit clearance is reduced, and the possibility of occurrence of clamping stagnation is reduced.
Drawings
FIG. 1 is a schematic diagram of the overall structure of the present invention;
FIG. 2 is a schematic cross-sectional view of two-position five-way hydraulic locks connected;
FIG. 3 is an axial cross-sectional view of a bushing of the present invention;
FIG. 4 is an axial cross-sectional view of the spool and spike of the present invention;
FIG. 5 is an axial cross-sectional view of a valve seat of the present invention;
FIG. 6 is an axial cross-sectional view (position 1) of the slider stem, bushing and valve seat assembly of the present invention;
FIG. 7 is an axial cross-sectional view (position 2) of the slider stem, bushing and valve seat assembly of the present invention;
FIG. 8 is a flow chart of hydraulic oil for forward operation of the pilot operated valve of the present invention;
FIG. 9 is a flow chart of reverse working hydraulic oil of the pilot operated valve of the present invention;
The reference numerals in the figures represent: 1-plug, 2-self-locking spring, 3-upper baffle, 4-valve body, 5-steel ball, 6-valve seat, 7-reset spring, 8-slide valve rod, 9-bushing, 10-lower baffle, 11-first bypass check valve, 12-first inlet check valve, 13-second bypass check valve, 14-second inlet check valve, 15-first interface, 16-second interface, 17-third interface, 18-fourth interface, 19-fifth interface, 20-annular groove, 21-first oil guide hole, 22-second oil guide hole, 23-third oil guide hole, 24-fourth oil guide hole, 25-sealing ring groove, 26-limit table, 27-axial hole, 28-first oil passing hole, 29-second oil passing hole, 30-third oil passing hole, 31-shaft side hole, 32-end face, 33-slide cavity, 34-locking hole, 35-first taper hole, 36-second taper hole, 37-ejector pin, 38-clamping table.
Detailed Description
The invention discloses a hydraulic control flow distribution valve, the structure diagram is shown in figure 1, the flow distribution valve comprises a two-position five-way hydraulic lock, the two-position five-way hydraulic lock comprises a valve body 4, a first interface 15 to a fifth interface 19, namely a first interface 15, a second interface 16, a third interface 17, a fourth interface 18 and a fifth interface 19 are sequentially arranged on the side wall of the valve body 4 along the axial direction parallel to the valve body 4, and the interfaces are used for guiding hydraulic oil by matching with slide valve rods 8 at different positions; the valve body 4 is divided into an upper part and a lower part by the valve seat 6, the lower part is larger, the upper part is smaller, the upper part is provided with a steel ball 5 with adjustable position, and the steel ball 5 has the function of forming metal seal with the valve seat 6 when contacting with the valve seat 6, thereby providing reliable seal for position self-locking of the hydraulic cylinder. A bushing 9 having a sliding chamber 33 is provided in the lower part, said sliding chamber 33 being fitted with a sliding valve stem 8 axially slidable along the valve body 4; preferably, the spool rod 8 is arranged in the central position of the valve body 4. Wherein:
The first to fourth interfaces 15 to 18 (the first, second, third and fourth interfaces 15, 16, 17 and 18) are all communicated with the sliding cavity 33, so that hydraulic oil can enter the sliding cavity 33 through the four interfaces or flow out of the sliding cavity 33 through the four interfaces, thereby being matched with different positions of the sliding valve rod 8 to realize different functions; the valve rod 8 is provided with first through third oil holes 28 to 30 (first through oil holes 28, second through oil holes 29 and third through oil holes 30) at intervals along the radial direction, the three oil holes all transversely penetrate through the valve rod 8 along the radial direction, and when the first through oil holes 28 are partially or completely overlapped with the first interface 15 in the axial direction, the second through oil holes 29 are partially or completely overlapped with the second interface 16 and the third through oil holes 30 and the third interface 17 in the axial direction; that is, when the hydraulic oil can enter or exit the first oil passing hole 28 through the first port 15, the hydraulic oil can also flow into or exit the second oil passing hole 29 and the third oil passing hole 30 through the second port 16 and the third port 17.
One end of the slide valve rod 8 is provided with a push rod 37 with the diameter smaller than that of the slide valve rod 8, and the push rod 37 has the function of pushing the steel ball 5 upwards through the push rod 37 when the slide valve rod 8 moves in the slide cavity 33, so that the steel ball 5 is separated from contact with the valve seat 6 to release the sealing state. The outer wall of the ejector rod 37 is provided with a limiting table 26 with the length smaller than the ejector rod 37 in the axial direction, and as shown in fig. 4, the limiting table 26 can be regarded as a cylinder for fastening the outer part of the top cover; one end of the limiting table 26 is contacted with the end of the slide valve rod 8, and the other end is separated from the end of the ejector rod 37 by a certain distance. The diameter of the spool stem 8 is the largest, the stop is 26 times, and the diameter of the ejector rod 37 is relatively smallest.
A shaft side hole 31 is formed from the end surface 32 of the limiting table 26 to the third oil passing hole 30; as shown in fig. 4, the shaft side hole 31 includes a first shaft side hole formed in the interior of the limit table 26 in a direction parallel to the axial direction, and a second shaft side hole formed in the spool rod 8 in a direction parallel to the axial direction, one end of the second shaft side hole is connected to the end of the first shaft side hole, and the diameter of the second shaft side hole is larger than that of the first shaft side hole; the other end of the second shaft side hole is communicated with the third oil passing hole 30. The shaft side hole 31 allows hydraulic oil to enter the third oil passing hole 30 of the spool rod 8 from the shaft side hole 31. Preferably, the shaft side hole 31 is formed along the outer wall of the push rod 37.
The other end of the slide valve rod 8 is provided with an axial hole 27 which is communicated with a first oil passing hole 28 and a second oil passing hole 29 along the axial direction; one end of the axial hole 27 is provided on the end face 32 of the spool rod 8, and the other end extends axially toward the inside of the spool rod 8 until the first oil passing hole 28 and the second oil passing hole 29 are communicated. The valve seat 6 is provided with a locking hole 34, and the ejector rod 37 can pass through the locking hole 34 and be contacted with the steel ball 5; the diameter of the locking hole 34 is smaller than that of the steel ball 5, and the steel ball 5 is matched with the upper end of the locking hole 34 to realize metal sealing; the fifth port 19 communicates with the locking hole 34, so that external hydraulic oil can enter the spool rod 8 through the shaft side hole 31 through the fifth port 19 and the locking hole 34, or hydraulic oil in the spool cavity 33 flows out of the valve body 4 from the fifth port 19 through the locking hole 34.
As shown in fig. 1, a plug 1 is arranged above the valve seat 6, and a gap is formed between the plug 1 and the valve seat 6, and the gap allows hydraulic oil to flow between the locking hole 34 and the fifth interface 19; the lower surface of the plug 1 is provided with a spring hole with the diameter larger than that of the steel ball 5 along the axial direction of the plug 1, namely, the axial direction of the slide valve rod 8, the spring hole is a blind hole, a self-locking spring 2 is assembled in the spring hole, and the lower end of the self-locking spring 2 is in contact with the steel ball 5; the steel ball 5 can enter the spring hole under the pushing of the ejector rod 37; the outside of ejector pin 37 suit be equipped with reset spring 7, reset spring 7's one end with the lower surface contact of disk seat 6, reset spring 7's the other end with the terminal surface 32 of slide valve rod 8 (with ejector pin 37 connection). In this scheme, spring hole, locking hole 34, ejector pin 37, slide valve rod 8, smooth chamber 33 all set up coaxially.
Further, as shown in fig. 4, the diameter of the portion between the first oil passing hole 28 on the spool rod 8 and the other end of the spool rod 8 is smaller than the diameter of the rest of the spool rod 8. Defining the upper end of the spool rod 8 at which the ejector rod 37 is disposed, the diameters of the first oil passing hole 28 and the lower end of the spool rod 8 are smaller than those of other parts of the spool rod 8, and when the spool rod 8 is assembled in the spool cavity 33 of the bushing 9, a gap is formed between the side wall of the spool cavity 33 and the lower part of the spool rod 8, so that hydraulic oil can flow in through the first interface 15.
As shown in fig. 1 and 4, labyrinth seal groove groups are arranged on the slide valve rod 8 between the first oil passing hole 28 and the second oil passing hole 29, and between the third oil passing hole 30 and the ejector rod 37; each labyrinth seal groove group comprises a plurality of seal grooves, the width of each seal groove is 0.5-0.7mm, and the depth of each seal groove is 0.28-0.42mm, so that the leakage amount between the slide valve rod 8 and the bushing 9 is effectively reduced, and the working efficiency of the valve body 4 is improved.
In the invention, the fit clearance between the sliding valve rod 8 and the sliding cavity 33 is not more than 0.01mm. In order to avoid clamping stagnation of the slide valve rod 8 and the slide cavity 33 caused by temperature change in a small gap, the slide valve rod 8 and the bushing 9 are made of the same high-strength wear-resistant steel, so that the same temperature change rate is ensured; performing high-low temperature aging treatment, and reducing the influence of temperature change on materials; and (3) performing surface diamond-like carbon plating to improve the strength of the mutually moving surfaces.
The structure of the bushing 9 is shown in fig. 3. The sliding cavity 33 inside the bushing 9 is a cavity with two through ends and a sizing, the first oil guide holes 21 to the fourth oil guide holes 24 are sequentially formed in the outer wall of the bushing 9 along the axial direction parallel to the bushing 9, and the first oil guide holes 21 to the fourth oil guide holes 24 are distributed along the circumferential direction of the bushing 9. The function of the oil guide holes is to allow hydraulic oil to enter the slide chamber 33 through the interface. In the example shown in fig. 3, four first oil guide holes 21 are symmetrically arranged on the circumference of the bushing 9, and the number of the rest oil guide holes on the bushing 9 is the same as that of the first oil guide holes 21. Of the four oil guide holes, the first oil guide hole 21 is a high-pressure oil inlet hole, and the second oil guide hole 22 is a high-pressure oil outlet hole; as shown in fig. 6 and 7, when the spool rod 8 is located at the position 1, the third oil guiding hole 23 is a high-pressure oil inlet hole, and the fourth oil guiding hole 24 is a high-pressure oil outlet hole; when the slide valve rod 8 is located at the position 2, the third oil guide hole 23 is a low-pressure oil outlet hole, and the fourth oil guide hole 24 is a low-pressure oil inlet hole. Among the four oil guide holes, adjacent oil guide holes are sealed by a 0-shaped rubber ring, and the rubber ring is arranged in the sealing ring groove 25.
As shown in fig. 5, a schematic structural view of the valve seat 6 portion is shown. The locking hole 34 is a hole penetrating through the upper surface and the lower surface of the valve seat 6, the locking hole 34 comprises a first taper hole 35 positioned at the upper part and a second taper hole 36 positioned at the lower part, and the first taper hole 35 and the second taper hole 36 are communicated through a connecting hole; the maximum inner diameter of the first taper hole 35 is smaller than the diameter of the steel ball 5. When the steel ball 5 is jacked up by the ejector rod 37 through the locking hole 34 in the moving process of the slide valve rod 8, after the end face 32 of the limiting table 26 on the outer wall of the ejector rod 37 contacts with the second taper hole 36, the position of the ejector rod 37 is limited, and the upward movement cannot be continued. In the scheme, the sealing between the steel ball 5 and the valve seat 6 is critical, so that the sealing reliability is ensured, and the valve seat can be flexibly opened. In the invention, the metal conical surface is matched with the steel ball 5 for sealing, namely, when the steel ball 5 contacts with the first conical hole 35, the metal sealing is formed between the steel ball 5 and the valve seat 6. The angle a of the conical surface of the first conical hole 35 is 38-46 degrees, and the axial length L of the first conical hole 35 is 0.25-0.35mm. Through long-term tightness test verification, the sealing structure can reach 3600h without leakage.
As shown in fig. 1 and 5, a central hole with two through ends is arranged in the valve body 4, a step groove is arranged on the central hole, and a clamping table 38 matched with the step groove is arranged on the outer wall of the bushing 9; the upper end of the valve body 4 is sealed through the upper baffle 3, and the plug 1 penetrates out of the upper baffle 3; the plug 1 is of an inverted T-shaped structure; the lower end of the valve body 4 is sealed by a lower baffle 10. In order to facilitate the diversion of the hydraulic oil, annular grooves 20 corresponding to the positions of the first oil guiding hole 21 to the fourth oil guiding hole 24 are arranged on the inner wall of the central hole at intervals. Taking the first oil guide hole 21 as an example, when the hydraulic oil enters the first port 15, it then enters the circumferential groove 20, and flows from the circumferential groove 20 into the sliding chamber 33 through the four first oil guide holes 21.
As a specific embodiment, in actual use, the two-position five-way hydraulic lock is provided with two hydraulic locks, which are respectively marked as L and R and are arranged completely symmetrically, so that the medium bidirectional flow state is ensured all the time. As shown in fig. 2; wherein: the first ports 15 of L and R are each connected to the hydraulic pump and to the tank via a first inlet check valve 12, a second inlet check valve 14, respectively; the first port 15 of L is connected with the third port 17 of R through the first bypass check valve 11, and the first port 15 of R is connected with the third port 17 of L through the second bypass check valve 13; the second interface 16 of L is connected with the fourth interface 18 of R, the fourth interface 18 of L is connected with the second interface 16 of R, and the fifth interfaces 19 of L and R are respectively connected with two ends of the hydraulic cylinder.
As shown in fig. 8 and 9, the hydraulic oil of the hydraulic control distributing valve of the present invention is in forward and reverse flow diagrams. The hydraulic control distributing valve disclosed by the invention has two working modes according to the working mode of the hydraulic pump. For convenience of description, references L1 to L5, R1 to R5 denote first to fifth interfaces 15 to 19 of L, R, respectively.
When the hydraulic pump works positively, as shown in fig. 8, high-pressure oil enters L from an L1 port, the slide valve rod 8 of the L moves upwards until the valve seat 6 is limited (the end face 32 of the limiting table 26 is in contact with the second conical hole 36), at the moment, the ejector rod 37 pushes the steel ball 5 away from the valve seat 6, the high-pressure oil flows out from an L2 port and enters an R4 port, the steel ball 5 in the R is pushed upwards by a certain distance under the action of the high-pressure oil and enters a spring hole of the plug 1, and then the high-pressure oil flows out from the R5 and enters a hydraulic cylinder to push the piston of the hydraulic cylinder to move positively; the low-pressure hydraulic oil at the other end of the piston enters L from L5 along an oil path, passes through the locking hole 34, enters the third oil passing hole 30 from the shaft side hole 31, then flows out from the L3 port, returns to the R1 port after passing through the second bypass one-way valve 13, and completes the forward working cycle before flowing into the hydraulic pump.
When the hydraulic pump is reversely pressurized, as shown in fig. 9, high-pressure oil enters from an R1 port, a slide valve rod 8 of the R moves upwards to a valve seat 6 for limiting, a push rod 37 pushes up a steel ball 5, the high-pressure oil flows out from an R2 port and enters an L4 port, the steel ball 5 in the L is pushed up a certain distance under the action of the high-pressure oil, and the high-pressure oil flows out from the L5 and enters a hydraulic cylinder to push a piston to reversely move; the low-pressure hydraulic oil at the other end of the piston enters the R from the R5 port along the oil path, passes through the locking hole 34, enters the third oil passing hole 30 from the shaft side hole 31, flows out from the R3 port, returns to the L1 port after passing through the first bypass one-way valve 11, completes reverse working cycle before flowing into the hydraulic pump, and moves reversely.
Claims (6)
1. The utility model provides a hydraulically controlled flow distribution valve, includes two-position five-way hydraulic lock, its characterized in that, two-position five-way hydraulic lock include valve body (4), along being on a parallel with valve body (4) axial first interface (15) to fifth interface (19) have been set gradually on valve body (4) lateral wall, separate into upper and lower two parts by disk seat (6) in valve body (4), be provided with steel ball (5) with adjustable position in the upper portion, be provided with bush (9) that have smooth chamber (33) in the lower part, be equipped with in smooth chamber (33) and follow valve body (4) axial sliding's slide valve rod (8), wherein:
the first interface (15) to the fourth interface (18) are all communicated with the sliding cavity (33), a first oil passing hole (28) to a third oil passing hole (30) are formed in the sliding valve rod (8) at intervals along the radial direction of the sliding valve rod, a push rod (37) with the diameter smaller than that of the sliding valve rod (8) is arranged at one end of the sliding valve rod (8), a limiting table (26) with the length smaller than that of the push rod (37) is arranged on the outer wall of the push rod (37), and a shaft side hole (31) is formed in the third oil passing hole (30) from the end face (32) of the limiting table (26); the other end of the slide valve rod (8) is axially provided with an axial hole (27) communicated with the first oil passing hole (28) and the second oil passing hole (29); the valve seat (6) is provided with a locking hole (34), and the ejector rod (37) can pass through the locking hole (34) and be contacted with the steel ball (5); the fifth interface (19) is communicated with the locking hole (34);
The diameter of the part between the first oil passing hole (28) on the slide valve rod (8) and the other end of the slide valve rod (8) is smaller than the diameter of the rest part on the slide valve rod (8); labyrinth seal groove groups are arranged on the slide valve rod (8) between the first oil passing hole (28) and the second oil passing hole (29) and between the third oil passing hole (30) and the ejector rod (37), and each labyrinth seal groove group comprises a plurality of seal grooves; the fit clearance between the slide valve rod 8 and the slide cavity 33 is not more than 0.01mm;
The two-position five-way hydraulic lock is provided with two hydraulic locks which are respectively marked as L and R, wherein: the first ports (15) of the L and the R are connected to the hydraulic pump and are connected to the oil tank through a first inlet check valve (12) and a second inlet check valve (14) respectively; the first port (15) of the L is connected with the third port (17) of the R through the first bypass one-way valve (11), and the first port (15) of the R is connected with the third port (17) of the L through the second bypass one-way valve (13); the second interface (16) of L is connected with the fourth interface (18) of R, the fourth interface (18) of L is connected with the second interface (16) of R, and the fifth interfaces (19) of L and R are respectively connected to two ends of the hydraulic cylinder.
2. The hydraulic control flow distribution valve according to claim 1, wherein a plug (1) is arranged above the valve seat (6), and a gap is formed between the plug (1) and the valve seat (6); the lower surface of the plug (1) is provided with a spring hole with the diameter larger than that of the steel ball (5) along the axial direction of the plug (1), a self-locking spring (2) is assembled in the spring hole, and the lower end of the self-locking spring (2) is in contact with the steel ball (5); the outside of ejector pin (37) cover be equipped with reset spring (7), reset spring (7) one end with the lower surface contact of disk seat (6), reset spring (7) the other end with terminal surface (32) of slide valve rod (8).
3. The hydraulic control flow distribution valve according to claim 2, wherein the sliding cavity (33) inside the bushing (9) is a cavity with two through ends and fixed diameter, the outer wall of the bushing (9) is sequentially provided with a first oil guide hole (21) to a fourth oil guide hole (24) along the axial direction parallel to the bushing (9), and the first oil guide hole (21) to the fourth oil guide hole (24) are distributed along the circumferential direction of the bushing (9).
4. The pilot operated valve as claimed in claim 1, wherein the locking hole (34) is a hole penetrating through the upper and lower surfaces of the valve seat (6), the locking hole (34) comprises a first tapered hole (35) at the upper part and a second tapered hole (36) at the lower part, and the first tapered hole (35) and the second tapered hole (36) are communicated through a connecting hole; the maximum inner diameter of the first taper hole (35) is smaller than the diameter of the steel ball (5).
5. A pilot operated flow distribution valve as set forth in claim 3, wherein said valve body (4) is internally provided with a central hole with two through ends, said central hole is provided with a step groove, and said bushing (9) is provided with a clamping table (38) on the outer wall thereof for cooperating with the step groove; the upper end of the valve body (4) is sealed through the upper baffle (3), and the plug (1) penetrates out of the upper baffle (3); the lower end of the valve body (4) is sealed by a lower baffle (10).
6. The pilot operated valve as set forth in claim 5, wherein circumferential grooves (20) corresponding to the positions of the first through fourth oil guide holes (21) through (24) are provided on the inner wall of the center hole at intervals.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810258108.9A CN108412828B (en) | 2018-03-27 | 2018-03-27 | Hydraulic control flow distribution valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810258108.9A CN108412828B (en) | 2018-03-27 | 2018-03-27 | Hydraulic control flow distribution valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108412828A CN108412828A (en) | 2018-08-17 |
| CN108412828B true CN108412828B (en) | 2024-06-28 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810258108.9A Active CN108412828B (en) | 2018-03-27 | 2018-03-27 | Hydraulic control flow distribution valve |
Country Status (1)
| Country | Link |
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| CN110513356B (en) * | 2019-09-09 | 2020-12-01 | 江西理工大学 | A hydraulic lock control structure of a slug oil circuit |
| CN112983919B (en) * | 2021-03-31 | 2021-12-31 | 同济大学 | Large-impulse hydraulic power mechanism based on shaft flow distribution |
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| CN105275484A (en) * | 2014-07-14 | 2016-01-27 | 巨隆集团芜湖兴隆液压有限公司 | Hydraulic control one-way valve |
| CN205744643U (en) * | 2016-05-05 | 2016-11-30 | 四川重汽王牌兴城液压件有限公司 | Constant voltage self-locking derrick crane hydraulic lifting system |
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