CN106246627B - A kind of rotary control type hydraulicdirectional control valve - Google Patents
A kind of rotary control type hydraulicdirectional control valve Download PDFInfo
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- CN106246627B CN106246627B CN201610732484.8A CN201610732484A CN106246627B CN 106246627 B CN106246627 B CN 106246627B CN 201610732484 A CN201610732484 A CN 201610732484A CN 106246627 B CN106246627 B CN 106246627B
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- oil
- radial direction
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- outlet
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
- F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
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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
The present invention relates to hydraulicdirectional control valve, more particularly, to a kind of rotary control type hydraulicdirectional control valve.It includes rotary spool, valve body, the first check valve and the second check valve are provided with rotary spool both sides, provided with radially straight-through oil duct in the middle part of rotary spool, both sides are radially provided with first, second unilateral radial direction oil input channel, first, second radial direction bilateral oil road and first, the unilateral pressure release oil duct of second radial direction, first, the entrance of the unilateral oil input channel of second radial direction successively can be connected by rotating with oil inlet, first, the outlet of second radial direction bilateral oil road successively can be connected by rotation with corresponding oil-out, first, the outlet of the unilateral pressure release oil duct of second radial direction successively can be connected by rotation with corresponding drain tap.Its purpose is to design one kind to realize that hydraulic pressure commutates using rotation mode, and the rotary control type hydraulicdirectional control valve of commutation process no-idle running.Compared with prior art, have the advantages that commutation is steady, dynamic characteristic is good, closed performance is good.
Description
Technical field
The present invention relates to hydraulicdirectional control valve, more particularly, to a kind of rotary control type hydraulicdirectional control valve.
Background technology
Hydraulicdirectional control valve is the key core part in Industry Control hydraulic system, and it stretches to hydraulic actuator oil cylinder
Direction controlling effect is played in contracting, the rotating of hydraulic motor.Industrial hydraulic reversal valves all at present are all by controlling hydraulic pressure
Valve element reaches the change in hydraulic oil direction as axial linear movement.In the work of actual hydraulic pressure system, due to pressure guarantor to be had
Hold, inevitable valve element needs certain seal length (amount of covering) with runner, therefore in the presence of one section of sky in switch operation
Stroke.Today, we had following problem to never have by used nearly all hydraulicdirectional control valve in actual applications
To solution.
1st, due to there is idle stroke, occur dead band during commutation, produce hydraulic shock.
2nd, due to there is idle stroke, the poor dynamic in commutation process.
3rd, due to there is idle stroke, hydraulic pressure overload overflow is produced in commutation process.
4th, in actual hydraulic pressure system, in order to keep suitable dynamic characteristic and pressure retaining ability, idle stroke can not mistake
It is long, can only be within a certain scope, therefore the cooperation requirement of valve element and valve opening is improved, considerably increase the manufacture difficulty of valve.
5th, in automatically controlling, the rotary motion of electronic commutation is changed into linear motion, it is necessary to increase switching mechanism, therefore increases
The reversing force increase that the big volume of valve and the efficiency of switching mechanism are brought.For there is the industrial products of space matching requirements,
There is certain limitation.
The content of the invention
The problem of existing for above-mentioned existing hydraulicdirectional control valve, the purpose of the present invention is that design one kind can use rotation side
Formula realizes that hydraulic pressure commutates, and the rotary control type hydraulicdirectional control valve of commutation process no-idle running.
To achieve the above object, the present invention uses following technical solution：A kind of rotary control type hydraulicdirectional control valve, it
Comprising valve element, valve body, provided with the first oil inlet, the second oil inlet, the 3rd oil inlet, the first oil-out, the on the valve body
Two oil-outs, the 3rd oil-out and the first drain tap, the second drain tap, it is characterised in that the valve element is rotary spool,
The rotary spool couples the 3rd oil inlet and the 3rd and gone out respectively provided with radially straight-through oil duct, the straight-through oil duct two ends of the radial direction
Hydraulic fluid port, is provided with the first check valve and the second check valve, in the rotary spool both sides in the axial direction of the rotary spool both sides
Be radially respectively equipped with first radially unilateral oil input channel, the first radial direction bilateral oil road, first radially unilateral pressure release oil duct and
The unilateral oil input channel of second radial direction, the second radial direction bilateral oil road, the unilateral pressure release oil duct of the second radial direction, wherein：
The outlet of the unilateral oil input channel of first radial direction and the entrance of first check valve are connected, and described first radially
The center line of suction of unilateral oil input channel is on cross section with the first oil inlet center line of suction into angle α clockwise；
The outlet of the entrance and first check valve of the first radial direction bilateral oil road is connected, and described first radially
The first outlet center line of bilateral oil road on cross section with the first oil-out center line into angle α clockwise, it is described
The second outlet center line of first radial direction bilateral oil road is pressed from both sides on cross section with the first oil-out center line into counterclockwise
Angle α；
The outlet of the entrance and first check valve of the unilateral pressure release oil duct of first radial direction is connected, first footpath
To the center line of discharge of unilateral pressure release oil duct on cross section with the first drain tap center line into angle α counterclockwise；
The outlet of the unilateral oil input channel of second radial direction and the entrance of second check valve are connected, and described second is unilateral
The center line of suction of radial direction oil input channel is on cross section with the second oil inlet center line into angle α counterclockwise；
The outlet of the entrance and second check valve of the second radial direction bilateral oil road is connected, and described second radially
The first outlet center line of bilateral oil road on cross section with the second oil-out center line into angle α counterclockwise, it is described
The second outlet center line of second radial direction bilateral oil road is pressed from both sides on cross section with the second oil-out center line into clockwise
Angle α；
The outlet of the entrance and second check valve of the unilateral pressure release oil duct of second radial direction is connected, second footpath
To the center line of discharge of unilateral pressure release oil duct on cross section with the second drain tap center line into angle α clockwise；
The angle α is 10 ° of ＜ α≤90 °.
The present invention is in order that reversal valve diametrically has longer closing length, the further radial-sealing for improving reversal valve
Performance, is further set to the technical scheme：The angle α is 90 °.
Brief description of the drawings
Fig. 1 is the theory structure sketch that the present embodiment commutates when being in middle position.
Fig. 2 is Fig. 1 along C-C directional profile figures.
Fig. 3 is Fig. 1 along D-D directional profile figures.
Fig. 4 is Fig. 1 along E-E directional profile figures.
Fig. 5 is Fig. 1 along F-F directional profile figures.
Fig. 6 is Fig. 1 along G-G directional profile figures.
Fig. 7 is Fig. 1 along H-H directional profile figures.
Fig. 8 is the theory structure sketch that hydraulic oil flows to by P → A after the present embodiment commutates.
Embodiment
The present invention is described in further detail with reference to the accompanying drawings and examples.
As shown in figure 1, the present embodiment include rotary spool 6, valve body 1, on the valve body 1 provided with the first oil inlet 10,
Second oil inlet 13, the 3rd oil inlet 11, the first oil-out 3, the second oil-out 8, the 3rd oil-out 5 and the first drain tap 2,
Second drain tap 9, provided with radially straight-through oil duct 12 on the rotary spool 6, the radial direction leads directly to the two ends of oil duct 12 and joined respectively
The 3rd oil inlet 11 and the 3rd oil-out 5 are connect, the first check valve 4 and second is provided with the axial direction of the both sides of rotary spool 6
Check valve 7, the unilateral oil input channel 16 of the first radial direction, the first radial direction bilateral are radially respectively equipped with the both sides of rotary spool 6
Radially unilateral pressure release oil duct 14 and second radially unilateral oil input channel 17, the second radial direction bilateral oil road 18, the of oil road 15, first
The unilateral pressure release oil duct 19 of two radial directions, wherein：
As shown in figure 4, the outlet of the unilateral oil input channel 16 of the first radial direction and the entrance of first check valve 4 are connected
Connect, the center line of suction of the described first radially unilateral oil input channel 16 on cross section with the center line of suction of the first oil inlet 10
Into angle α clockwise, the angle α is 90 °, and the angle α being set forth below is 90 °；
As shown in Fig. 2 the outlet of the entrance and first check valve 4 of the first radial direction bilateral oil road 15 is connected
Connect, the first outlet center line of the first radial direction bilateral oil road 15 on cross section with the center line of the first oil-out 3
Into angle α clockwise, the second outlet center line of the first radial direction bilateral oil road 15 goes out on cross section with described first
The center line of hydraulic fluid port 3 is into angle α counterclockwise；
As shown in figure 1, the outlet of the entrance and first check valve 4 of the unilateral pressure release oil duct 14 of the first radial direction is connected
Connect, the center line of discharge of the described first radially unilateral pressure release oil duct 14 is on cross section with the center line of the first drain tap 2 into the inverse time
Pin angle α；
As shown in figure 5, the outlet of the unilateral oil input channel 17 of the second radial direction and the entrance of second check valve 7 are connected
Connect, the center line of suction of the second unilateral radial direction oil input channel 17 is on cross section with the center line of the second oil inlet 13 into inverse
Hour hands angle α；
As shown in fig. 6, the outlet of the entrance and second check valve 7 of the second radial direction bilateral oil road 18 is connected
Connect, the first outlet center line of the second radial direction bilateral oil road 18 on cross section with the center line of the second oil-out 8
Into angle α counterclockwise, the second outlet center line of the second radial direction bilateral oil road 18 goes out on cross section with described second
The center line of hydraulic fluid port 8 is into angle α clockwise；
As shown in fig. 7, the outlet of the entrance and second check valve 7 of the unilateral pressure release oil duct 19 of the second radial direction is connected
Connect, the center line of discharge of the described second radially unilateral pressure release oil duct 19 is on cross section with the center line of the second drain tap 9 into up time
Pin angle α；
Again as shown in figure 1, when rotary spool 6 does not commutate (middle position), pressure oil P is directly straight by the radial direction in the middle part of valve element
Oil canal 12 flows out from the 3rd oil-out 5, therefore can constitute the multiple directional control valve of multi-joint different oil circuit forms.Now, the 3rd
Oil inlet 11 and the first oil-out 3, the second oil-out 8, the drain tap 9 of the first drain tap 2 second be not connected, and hydraulic system is held
Units are in hold mode.
When rotary spool 6 is in commutation process, the first radial direction bilateral oil road 15 or the second radial direction bilateral oil road 18
Outlet and the radially outlet of straight-through oil duct 12 have an overlay region, therefore, the liquid of control is rotated by rotary spool 6 in commutation moment
Pressure reversal valve is not in the hydraulic shock that commutation dead band is produced and overflow power consumption.Only inswept envelope when commutating of rotary spool 6
Angle is closed, in motorized motions rotary spool 6, almost without commutating period, hydraulicdirectional control valve is similar to the zero lap of servo valve, moves
Step response is good.Due to there is axially and radially direction closing length, therefore, under equal pressure condition, by the rotary valve of the present invention
Core is bigger than conventional valve fit clearance with valve opening fit clearance, this reduces hydraulicdirectional control valve manufacture difficulty, and improves liquid
Press the reliability of reversal valve.
As shown in figure 8, after the rotate counterclockwise of rotary spool 6 commutates in place, the radial direction in the middle part of valve element leads directly to oil duct 12 and closed
Close the 3rd oil inlet 11, first radially unilateral oil input channel 16 by the entrance of the first check valve 4 and the UNICOM of the first oil inlet 10, first
Radial direction bilateral oil road 15 is by the outlet of the first check valve 4 and the UNICOM of the first oil-out 3, and pressure oil P is radially unilateral by first
Oil input channel 16 pushes the first check valve 4 open, and enters by the internal galleries of the first check valve 4, the first radial direction bilateral oil road 15
One oil-out 3, is operated A roads hydraulic system executive component.Meanwhile, described second radially unilateral pressure release oil duct 19 by second
The outlet of check valve 7 and the UNICOM of the second drain tap 9, the second radial direction bilateral oil road 18 are single by the second oil-out 8 and second
Enter the second drain tap 9 by the internal galleries of the second check valve 7 to the pressure oil gone out in oil pocket UNICOM, the second oil-out 8 of valve 7
Pressure release, makes B roads hydraulic system executive component be stopped.
Similarly, after rotary spool 6 turns clockwise commutation in place, B roads hydraulic system executive component is operated, A roads
Hydraulic system executive component is stopped.
In summary, the present invention has advantages below compared with prior art：
1st, commutate steady.The commutation of the present invention is not traditional linear motion but rotary motion, in commutation, hydraulic oil
Flowing to P → A and P → B has overlay region, therefore will not produce commutation dead band, will not produce compression shock, commutation is steady.Have simultaneously
Overflow power consumption will not be produced in commutation by having.
2nd, dynamic characteristic is good.The valve element of the present invention and runner are not traditional axial closings, but axially add radial-sealing,
Because valve element commutation is rotary motion, radial-sealing angle very little, therefore dynamic characteristic is good in commutation process, close to servo
Valve actuation step response (servo valve is zero closing).
3rd, closed performance is good, and manufacture difficulty is low.Valve element of the present invention is due to using radial-sealing is axially added, therefore, effectively sealing
Close length and close length two to more than three times more than conventional valve straight line, closed performance is good, it is possible to increases valve element and matches somebody with somebody with valve opening
Gap is closed, the manufacture difficulty of valve is greatly reduced.
4th, commutation is without rectilinear path, and requirements of installation space is small.The valve element of the present invention is a kind of rotary spool, without straight line fortune
Dynamic stroke, therefore hydraulicdirectional control valve requirements of installation space is small, disclosure satisfy that the demand of more industrial products hydraulic systems.
5th, multi-path above hydraulicdirectional control valve can be constituted.The axial direction that valve element of the present invention is used adds radially-arranged oil duct, because
This can accomplish more than multidigit (within tradition generally three) multi-path the reversal valve of (tradition generally six passes to interior), hydraulic pressure
The functions expanding of reversal valve is good, adaptable.
6th, can channeling hydraulicdirectional control valve.The axial direction that valve element of the present invention is used adds radially-arranged oil duct, therefore can be with
Channeling (more than two tunnels) and various oil circuit forms (series connection, in parallel, connection in series-parallel) multipath hydraulic change-over valve.
7th, Automated condtrol is easily realized.Valve element of the present invention is a kind of rotary spool, thus can directly with servo (stepping)
Motor is directly connected to, and easily realizes automation.
Described above is the preferred embodiment of the present invention, it is noted that for the person of ordinary skill of the art
Without departing from the principles of the invention, several modifications and improvements can also be made, these also should be regarded as the protection for belonging to invention
Scope.
Claims (2)
1. a kind of rotary control type hydraulicdirectional control valve, it includes valve element, valve body (1), and the first oil-feed is provided with the valve body (1)
Mouth (10), the second oil inlet (13), the 3rd oil inlet (11), the first oil-out (3), the second oil-out (8), the 3rd oil-out
(5) and the first drain tap (2), the second drain tap (9), it is characterised in that the valve element is rotary spool (6), in the rotation
Valve element (6) leads directly to oil duct (12) two ends and couples the 3rd oil inlet (11) respectively provided with radially straight-through oil duct (12), the radial direction
With the 3rd oil-out (5), the first check valve (4) and the second check valve are provided with the axial direction of the rotary spool (6) both sides
(7) the unilateral oil input channel (16) of the first radial direction, the first radial direction bilateral radially, are respectively equipped with the rotary spool (6) both sides
Radially unilateral pressure release oil duct (14) and the second radial direction one side oil input channel (17), the second radial direction bilateral are fuel-displaced for oil road (15), first
Road (18), the unilateral pressure release oil duct (19) of the second radial direction, wherein：
The outlet of the unilateral oil input channel (16) of first radial direction and the entrance of first check valve (4) are connected, and described first
Radially the center line of suction of unilateral oil input channel (16) on cross section with the first oil inlet (10) center line of suction into up time
Pin angle α；
The entrance of the first radial direction bilateral oil road (15) and the outlet of first check valve (4) are connected, and described first
The first outlet center line of radial direction bilateral oil road (15) is on cross section with the first oil-out (3) center line into clockwise
Angle α, the second outlet center line of the first radial direction bilateral oil road (15) on cross section with first oil-out (3)
Center line is into angle α counterclockwise；
Described first radially the entrance of unilateral pressure release oil duct (14) and the outlet of first check valve (4) be connected, described the
The center line of discharge of one radially unilateral pressure release oil duct (14) is on cross section with the first drain tap (2) center line into angle counterclockwise
α；
The outlet of the unilateral oil input channel (17) of second radial direction and the entrance of second check valve (7) are connected, and described second
Radially the center line of suction of unilateral oil input channel (17) is pressed from both sides on cross section with the second oil inlet (13) center line into counterclockwise
Angle α；
The entrance of the second radial direction bilateral oil road (18) and the outlet of second check valve (7) are connected, and described second
The first outlet center line of radial direction bilateral oil road (18) is on cross section with the second oil-out (8) center line into counterclockwise
Angle α, the second outlet center line of the second radial direction bilateral oil road (18) on cross section with second oil-out (8)
Center line is into angle α clockwise；
Described second radially the entrance of unilateral pressure release oil duct (19) and the outlet of second check valve (7) be connected, described the
The center line of discharge of two radially unilateral pressure release oil ducts (19) is on cross section with the second drain tap (9) center line into angle clockwise
α；
The angle α is 10 ° of ＜ α≤90 °.
2. a kind of rotary control type hydraulicdirectional control valve according to claim 1, it is characterised in that the angle α is 90 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610732484.8A CN106246627B (en) | 2016-08-20 | 2016-08-20 | A kind of rotary control type hydraulicdirectional control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610732484.8A CN106246627B (en) | 2016-08-20 | 2016-08-20 | A kind of rotary control type hydraulicdirectional control valve |
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| Publication Number | Publication Date |
|---|---|
| CN106246627A CN106246627A (en) | 2016-12-21 |
| CN106246627B true CN106246627B (en) | 2017-10-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201610732484.8A Active CN106246627B (en) | 2016-08-20 | 2016-08-20 | A kind of rotary control type hydraulicdirectional control valve |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201103579Y (en) * | 2007-08-09 | 2008-08-20 | 石拓 | Rotation-controlled reversal valve |
| CN103542132A (en) * | 2013-10-20 | 2014-01-29 | 湖南众联工程机械有限公司 | Eight-direction rotary valve |
| CN203413168U (en) * | 2013-08-12 | 2014-01-29 | 龙工（上海）精工液压有限公司 | Anti-reversion valve for rotary motor of excavator |
| CN103851225A (en) * | 2012-11-01 | 2014-06-11 | 宋久林 | Rotary multi-way reversing valve |
| CN105298962A (en) * | 2015-10-30 | 2016-02-03 | 柳州柳工液压件有限公司 | Rotary-valve-type control valve |
| CN205383298U (en) * | 2016-01-12 | 2016-07-13 | 郑瑞源 | Structure of rotation type hydrovalve improvement |
| CN205937281U (en) * | 2016-08-20 | 2017-02-08 | 黎明液压有限公司 | Spin control formula hydraulic directional control valve |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6904936B2 (en) * | 2002-04-19 | 2005-06-14 | Archidex | Flow-diverting rotary valves of multiple paths |
-
2016
- 2016-08-20 CN CN201610732484.8A patent/CN106246627B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201103579Y (en) * | 2007-08-09 | 2008-08-20 | 石拓 | Rotation-controlled reversal valve |
| CN103851225A (en) * | 2012-11-01 | 2014-06-11 | 宋久林 | Rotary multi-way reversing valve |
| CN203413168U (en) * | 2013-08-12 | 2014-01-29 | 龙工（上海）精工液压有限公司 | Anti-reversion valve for rotary motor of excavator |
| CN103542132A (en) * | 2013-10-20 | 2014-01-29 | 湖南众联工程机械有限公司 | Eight-direction rotary valve |
| CN105298962A (en) * | 2015-10-30 | 2016-02-03 | 柳州柳工液压件有限公司 | Rotary-valve-type control valve |
| CN205383298U (en) * | 2016-01-12 | 2016-07-13 | 郑瑞源 | Structure of rotation type hydrovalve improvement |
| CN205937281U (en) * | 2016-08-20 | 2017-02-08 | 黎明液压有限公司 | Spin control formula hydraulic directional control valve |
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| Publication number | Publication date |
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| CN106246627A (en) | 2016-12-21 |
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