CN205937281U - Spin control formula hydraulic directional control valve - Google Patents
Spin control formula hydraulic directional control valve Download PDFInfo
- Publication number
- CN205937281U CN205937281U CN201620950372.5U CN201620950372U CN205937281U CN 205937281 U CN205937281 U CN 205937281U CN 201620950372 U CN201620950372 U CN 201620950372U CN 205937281 U CN205937281 U CN 205937281U
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- Prior art keywords
- oil
- radial direction
- centrage
- unilateral
- outlet
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Abstract
The utility model relates to a hydraulic directional control valve especially relates to a spin control formula hydraulic directional control valve. It contains rotatory case, a valve body, be equipped with first check valve and second check valve in rotatory case both sides, be equipped with radial direct oil duct at rotatory case middle part, both sides radially are equipped with firstly, the radial oil feed way of second unilateral, it is first, the radial two oil ducts and first that incline out of second, the radial unilateral pressure release oil duct of second, it is first, the entry that the radial unilateral oil feed of second was said can successively link with the oil inlet through rotating, it is first, the export of the radial two oil ducts that incline out of second can successively link with corresponding oil -out through rotating, it is first, the export of the radial unilateral pressure release oil duct of second can successively link with corresponding drain tap through rotating. Its purpose can adopt rotatory mode to realize the hydraulic pressure switching -over in order to design one kind, and the switching -over process does not have the spin control formula hydraulic directional control valve of banking. Compared with the prior art, have advantages such as the switching -over is steady, dynamic characteristic is good, sealing property is good.
Description
Technical field
This utility model is related to hydraulicdirectional control valve, especially relates 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 is stretched to hydraulic actuator oil cylinder
Direction controlling effect is played in contracting, the rotating of hydraulic motor.All of industrial hydraulic reversal valve is all by controlling hydraulic pressure at present
Valve element to reach the change in hydraulic oil direction as axial linear movement.In the work of actual hydraulic pressure system, due to pressure will be had to protect
Hold, inevitable valve element and runner need certain seal length (amount of covering), there is one section of sky therefore in switch operation
Stroke.Nearly all hydraulicdirectional control valve that today, we were used has following problem to never have in actual applications
To solution.
1st, due to there being idle stroke, dead band occurs during commutation, produce hydraulic shock.
2nd, due to there being idle stroke, poor dynamic in commutation process.
3rd, due to there being idle stroke, commutation process produces hydraulic pressure overload overflow.
4th, in actual hydraulic pressure system, in order to keep suitable dynamic characteristic and pressure retaining ability, idle stroke can not mistake
Long, can only be within a certain scope, the cooperation that therefore improve valve element with valve opening requires, and considerably increases the manufacture difficulty of valve.
5th, in automatically controlling, the rotary motion of electronic commutation is changed into moving along a straight line, and needs to increase shifter, therefore increases
The reversing force that the big volume of valve and the efficiency of shifter are brought increases.For the industrial products having space matching requirements,
There is certain limitation.
Content of the invention
The problem existing for above-mentioned existing hydraulicdirectional control valve, the purpose of this utility model is that design one kind can be using rotation
The mode of turning realizes hydraulic pressure commutation, and the rotary control type hydraulicdirectional control valve of commutation process no-idle running.
For achieving the above object, this utility model adopts following technical solution：A kind of rotary control type hydraulic pressure commutation
Valve, it comprises valve element, valve body, is provided with the first oil-in, the second oil-in, the 3rd oil-in, first fuel-displaced on described valve body
Mouth, the second oil-out, the 3rd oil-out and the first drain tap, the second drain tap are it is characterised in that described valve element is rotary valve
Core, is provided with radially straight-through oil duct on described rotary spool, described radial direction lead directly to oil duct two ends couple respectively the 3rd oil-in and
3rd oil-out, is provided with the first check valve and the second check valve, in described rotary valve in the axial direction of described rotary spool both sides
Core both sides be radially respectively equipped with the first radially unilateral oil input channel, the first radial direction bilateral oil road, the first radially unilateral pressure release
Oil duct and second radially unilateral oil input channel, the second radial direction bilateral oil road, the unilateral pressure release oil duct of the second radial direction, wherein：
The described outlet of the first radial direction one side oil input channel and the entrance of described first check valve are connected, and described first radially
The center line of suction of unilateral oil input channel becomes angle α clockwise with described first oil-in center line of suction on cross section；
The entrance of described first radial direction bilateral oil road is connected with the outlet of described first check valve, and described first radially
The first outlet centrage of bilateral oil road becomes angle α clockwise with described first oil-out centrage on cross section, described
The second outlet centrage of the first radial direction bilateral oil road becomes folder counterclockwise on cross section with described first oil-out centrage
Angle α；
The entrance of described first radial direction one side pressure release oil duct is connected with the outlet of described first check valve, described first footpath
Become angle α counterclockwise to the center line of discharge of unilateral pressure release oil duct with the first drain tap centrage on cross section；
The described outlet of the second radial direction one side oil input channel and the entrance of described second check valve are connected, and described second is unilateral
The center line of suction of radial direction oil input channel becomes angle α counterclockwise with described second oil-in centrage on cross section；
The entrance of described second radial direction bilateral oil road is connected with the outlet of described second check valve, and described second radially
The first outlet centrage of bilateral oil road becomes angle α counterclockwise with described second oil-out centrage on cross section, described
The second outlet centrage of the second radial direction bilateral oil road becomes folder clockwise on cross section with described second oil-out centrage
Angle α；
The entrance of described second radial direction one side pressure release oil duct is connected with the outlet of described second check valve, described second footpath
Become angle α clockwise to the center line of discharge of unilateral pressure release oil duct with the second drain tap centrage on cross section；
Described angle α is 10 ° of ＜ α≤90 °.
This utility model, in order that reversal valve diametrically has longer closing length, improves the radial direction of reversal valve further
Closed performance, is arranged further to described technical scheme：Described angle α is 90 °.
Brief description
Fig. 1 is in theory structure sketch during middle position for the present embodiment commutation.
Fig. 2 is Fig. 1 along C-C directional profile figure.
Fig. 3 is Fig. 1 along D-D directional profile figure.
Fig. 4 is Fig. 1 along E-E directional profile figure.
Fig. 5 is Fig. 1 along F-F directional profile figure.
Fig. 6 is Fig. 1 along G-G directional profile figure.
Fig. 7 is Fig. 1 along H-H directional profile figure.
Fig. 8 flows to by the theory structure sketch of P → A for hydraulic oil after the present embodiment commutation.
Specific embodiment
The utility model is described in further detail with reference to the accompanying drawings and examples.
As shown in figure 1, the present embodiment comprises rotary spool 6, valve body 1, described valve body 1 is provided with the first oil-in 10,
Second oil-in 13, the 3rd oil-in 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, is provided with radially straight-through oil duct 12 on described rotary spool 6, and described radial direction leads directly to oil duct 12 two ends and joins respectively
Connect the 3rd oil-in 11 and the 3rd oil-out 5, the first check valve 4 and second is provided with the axial direction of described rotary spool 6 both sides
Check valve 7, is radially respectively equipped with the first radially unilateral oil input channel 16, the first radial direction bilateral in described rotary spool 6 both sides
Oil road 15, first radially unilateral pressure release oil duct 14 and second radially unilateral oil input channel 17, the second radial direction bilateral oil road 18, the
The unilateral pressure release oil duct 19 of two radial directions, wherein：
As shown in figure 4, the described outlet of the first radial direction one side oil input channel 16 and the entrance of described 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 described first oil-in 10 center line of suction
Become angle α clockwise, described angle α is 90 °, and the angle α being set forth below is 90 °；
As shown in Fig. 2 the entrance of described first radial direction bilateral oil road 15 and the outlet of described first check valve 4 are connected
Connect, the first outlet centrage of described first radial direction bilateral oil road 15 on cross section with described first oil-out 3 centrage
Become angle α clockwise, the second outlet centrage of described first radial direction bilateral oil road 15 goes out with described first on cross section
Hydraulic fluid port 3 centrage becomes angle α counterclockwise；
As shown in figure 1, the entrance of described first radial direction one side pressure release oil duct 14 is connected with the outlet of described first check valve 4
Connect, the center line of discharge of described first radial direction one side pressure release oil duct 14 becomes the inverse time with the first drain tap 2 centrage on cross section
Pin angle α；
As shown in figure 5, the described outlet of the second radial direction one side oil input channel 17 and the entrance of described second check valve 7 are connected
Connect, the center line of suction of the described second unilateral radial direction oil input channel 17 becomes inverse with described second oil-in 13 centrage on cross section
Hour hands angle α；
As shown in fig. 6, the entrance of described second radial direction bilateral oil road 18 and the outlet of described second check valve 7 are connected
Connect, the first outlet centrage of described second radial direction bilateral oil road 18 on cross section with described second oil-out 8 centrage
Become angle α counterclockwise, the second outlet centrage of described second radial direction bilateral oil road 18 goes out with described second on cross section
Hydraulic fluid port 8 centrage becomes angle α clockwise；
As shown in fig. 7, the entrance of described second radial direction one side pressure release oil duct 19 is connected with the outlet of described second check valve 7
Connect, the center line of discharge of described second radial direction one side pressure release oil duct 19 becomes up time with the second drain tap 9 centrage on cross section
Pin angle α；
Again as shown in figure 1, when rotary spool 6 does not commutate (middle position), the radial direction that pressure oil P directly passes through in the middle part of valve element is straight
Oil canal 12 flows out from the 3rd oil-out 5, therefore can be to form the multiple directional control valve of multi-joint difference oil circuit form.Now, the 3rd
Oil-in 11 is not connected with the first oil-out 3, the second oil-out 8, the first drain tap 2 second drain tap 9, the holding of hydraulic system
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 has an overlay region with the outlet of radially straight-through oil duct 12 in commutation moment, therefore, is rotated the liquid of control by rotary spool 6
Pressure reversal valve is not in the hydraulic shock and overflow power consumption that commutation dead band produces.Only inswept envelope during rotary spool 6 commutation
Close angle, in motorized motions rotary spool 6, almost there is no commutating period, hydraulicdirectional control valve is similar to the zero lap of servo valve, move
Step response is good.Due to there being axially and radially direction closing length, therefore, under equal pressure condition, by rotation of the present utility model
Rotary plate is bigger than conventional valve fit clearance with valve opening fit clearance, this reduces hydraulicdirectional control valve manufacture difficulty, and improves
The reliability of hydraulicdirectional control valve.
As shown in figure 8, after the commutation of rotary spool 6 rotate counterclockwise puts in place, the radial direction in the middle part of valve element leads directly to oil duct 12 and closes
Close the 3rd oil-in 11, first radially unilateral oil input channel 16 by the entrance of the first check valve 4 and the first oil-in 10 UNICOM, first
By the outlet of the first check valve 4 and the first oil-out 3 UNICOM, it is radially unilateral that pressure oil P passes through first to radial direction bilateral oil road 15
Oil input channel 16 pushes the first check valve 4 open, and enters the by the first check valve 4 internal galleries, the first radial direction bilateral oil road 15
One oil-out 3, makes A road hydraulic system executive component be operated.Meanwhile, described second radially unilateral pressure release oil duct 19 by second
The outlet of check valve 7 and the second drain tap 9 UNICOM, described second radial direction bilateral oil road 18 will be single for the second oil-out 8 and second
Go out oil pocket UNICOM to valve 7, the pressure oil in the second oil-out 8 enters the second drain tap 9 by the second check valve 7 internal galleries
Pressure release, makes B road hydraulic system executive component quit work.
In the same manner, when rotary spool 6 turn clockwise commutation put in place after, B road hydraulic system executive component is operated, A road
Hydraulic system executive component quits work.
In sum, this utility model compared with prior art has advantages below：
1st, commutate steadily.Commutation of the present utility model is not traditional linear motion but rotary motion, in commutation, liquid
Force feed flows to P → A and P → B overlay region, thus without producing commutation dead band, will not produce compression shock, commutation is steadily.With
When have commutation when will not produce overflow power consumption.
2nd, dynamic characteristic is good.Valve element of the present utility model and runner are not traditional axial closings, but axially add radially
Closing, because valve element commutation is rotary motion, radial-sealing angle very little, therefore in commutation process, dynamic characteristic is good, close
In servo valve dynamic characteristic (servo valve is zero closing).
3rd, closed performance is good, and manufacture difficulty is low.This utility model valve element is due to using axially adding radial-sealing, therefore, having
Effect closing length is more than conventional valve straight line closing length two to more than three times, closed performance good it is possible to increase valve element and valve
Hole fit clearance, greatly reduces the manufacture difficulty of valve.
4th, commutation no rectilinear path, requirements of installation space is little.Valve element of the present utility model is a kind of rotary spool, not straight
Line movement travel, therefore hydraulicdirectional control valve requirements of installation space is little, disclosure satisfy that the demand of more industrial products hydraulic systems.
5th, the above hydraulicdirectional control valve of multi-path can be formed.The axial direction that this utility model valve element adopts adds radially-arranged oil
Road, therefore can accomplish the commutation of more than multidigit (within tradition generally three) multi-path (within tradition is generally clematis stem)
Valve, the functions expanding of hydraulicdirectional control valve is good, adaptable.
6th, can channeling hydraulicdirectional control valve.The axial direction that this utility model valve element adopts adds radially-arranged oil duct, therefore
Can be with channeling (more than two tunnels) and various oil circuit form (series connection, in parallel, connection in series-parallel) multipath hydraulic change-over valve.
7th, easily realize Automated condtrol.This utility model valve element is a kind of rotary spool, therefore can directly (walk with servo
Entering) motor is directly connected to, and easily realizes automatization.
The above is preferred implementation of the present utility model it is noted that for those of ordinary skill in the art
For without departing from this utility model principle on the premise of, some deformation can also be made and improve, these also should be regarded as belonging to real
With new protection domain.
Claims (2)
1. a kind of rotary control type hydraulicdirectional control valve, it comprises valve element, valve body (1), is provided with the first oil-feed on described valve body (1)
Mouth (10), the second oil-in (13), the 3rd oil-in (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 described valve element be rotary spool (6), in described rotation
Valve element (6) is provided with radially straight-through oil duct (12), and described radial direction leads directly to oil duct (12) two ends and couples the 3rd oil-in (11) respectively
With the 3rd oil-out (5), the first check valve (4) and the second check valve are provided with the axial direction of described rotary spool (6) both sides
(7), radially it is respectively equipped with the first radially unilateral oil input channel (16), the first radial direction bilateral in described rotary spool (6) both sides
Radially unilateral oil input channel (17), the second radial direction bilateral are fuel-displaced for oil road (15), the unilateral pressure release oil duct (14) of the first radial direction and second
Road (18), the unilateral pressure release oil duct (19) of the second radial direction, wherein：
The outlet of described first radial direction one side oil input channel (16) is connected with the entrance of described first check valve (4), and described first
Radially the center line of suction of unilateral oil input channel (16) becomes up time with described first oil-in (10) center line of suction on cross section
Pin angle α；
The entrance of described first radial direction bilateral oil road (15) and the outlet of described first check valve (4) are connected, and described first
The first outlet centrage of radial direction bilateral oil road (15) becomes clockwise with described first oil-out (3) centrage on cross section
Angle α, the second outlet centrage of described first radial direction bilateral oil road (15) on cross section with described first oil-out (3)
Centrage becomes angle α counterclockwise；
The entrance of the described first radially unilateral pressure release oil duct (14) is connected with the outlet of described first check valve (4), and described the
The center line of discharge of the unilateral pressure release oil duct (14) of one radial direction becomes angle counterclockwise with the first drain tap (2) centrage on cross section
α；
The outlet of described second radial direction one side oil input channel (17) is connected with the entrance of described second check valve (7), and described second
The center line of suction of unilateral radial direction oil input channel (17) becomes folder counterclockwise on cross section with described second oil-in (13) centrage
Angle α；
The entrance of described second radial direction bilateral oil road (18) and the outlet of described second check valve (7) are connected, and described second
The first outlet centrage of radial direction bilateral oil road (18) becomes counterclockwise with described second oil-out (8) centrage on cross section
Angle α, the second outlet centrage of described second radial direction bilateral oil road (18) on cross section with described second oil-out (8)
Centrage becomes angle α clockwise；
The entrance of the described second radially unilateral pressure release oil duct (19) is connected with the outlet of described second check valve (7), and described the
The center line of discharge of the unilateral pressure release oil duct (19) of two radial directions becomes angle clockwise with the second drain tap (9) centrage on cross section
α；
Described angle α is 10 ° of ＜ α≤90 °.
2. a kind of rotary control type hydraulicdirectional control valve according to claim 1 is it is characterised in that described angle α is 90 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620950372.5U CN205937281U (en) | 2016-08-20 | 2016-08-20 | Spin control formula hydraulic directional control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620950372.5U CN205937281U (en) | 2016-08-20 | 2016-08-20 | Spin control formula hydraulic directional control valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN205937281U true CN205937281U (en) | 2017-02-08 |
Family
ID=57954744
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620950372.5U Withdrawn - After Issue CN205937281U (en) | 2016-08-20 | 2016-08-20 | Spin control formula hydraulic directional control valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN205937281U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106246627A (en) * | 2016-08-20 | 2016-12-21 | 黎明液压有限公司 | A kind of rotary control type hydraulicdirectional control valve |
| CN109027337A (en) * | 2018-09-12 | 2018-12-18 | 苏州丹顿机电有限公司 | A kind of check valve manually adjusting cut-off direction |
-
2016
- 2016-08-20 CN CN201620950372.5U patent/CN205937281U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106246627A (en) * | 2016-08-20 | 2016-12-21 | 黎明液压有限公司 | A kind of rotary control type hydraulicdirectional control valve |
| CN106246627B (en) * | 2016-08-20 | 2017-10-27 | 黎明液压有限公司 | A kind of rotary control type hydraulicdirectional control valve |
| CN109027337A (en) * | 2018-09-12 | 2018-12-18 | 苏州丹顿机电有限公司 | A kind of check valve manually adjusting cut-off direction |
| CN109027337B (en) * | 2018-09-12 | 2020-02-14 | 苏州丹顿机电有限公司 | Check valve capable of manually adjusting stop direction |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20170208 Effective date of abandoning: 20171027 |