CN103775417A - Valve system - Google Patents
Valve system Download PDFInfo
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- CN103775417A CN103775417A CN201310494038.4A CN201310494038A CN103775417A CN 103775417 A CN103775417 A CN 103775417A CN 201310494038 A CN201310494038 A CN 201310494038A CN 103775417 A CN103775417 A CN 103775417A
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- Prior art keywords
- valve system
- piston
- main
- valve
- guide
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
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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
- 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
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
- F15B19/002—Calibrating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- 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
- F16K11/0708—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 comprising means to avoid jamming of the slide or means to modify the flow
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
- F15B2211/328—Directional control characterised by the type of actuation electrically or electronically with signal modulation, e.g. pulse width modulation [PWM]
Abstract
The valve device has a main stage (1) with a main piston (18) and a pilot stage (2) with a pilot piston (4). A directional valve is arranged between electronic control unit and main stage. An opening stroke with short duration is produced by the pilot piston through the electric pulses (26,28) generated over the electronic control unit, so that an interval is formed between start position and end or stop position of the pilot piston in reversal state.
Description
Technical field
The present invention relates to a kind of according to the valve system as described in the preamble of claim 1.
Background technique
By prior art known proportion selector valve, its valve body can also occupy neutral position except operating position and open position, only partially opens through flow cross section in neutral position.Therefore can in this selector valve, manipulate through-current capacity.Drawback is the device technique cost for this selector valve.
The valve that can regulate is disclosed in open source literature DE 10 2,010 045 504 A1, its valve body can occupy on positi and in addition can pulsed or impact type move, the short time is opened valve thus.Thisly open motion repeatedly.Can also realize the through-current capacity reducing with respect to opening completely by this so-called trajectory pattern (ballistischer Modus), can manipulate thus directly actuated valve.
In addition, in document DE 10 2,009 052 285 A1, also disclose digital hydraulic valve system, it has the parallel distributing valve (Schaltventil) of arranging mutually of multiple different sizes.Described distributing valve is opened with different combinations simultaneously, thus digital hydraulic valve system is obtained the opening cross-section of adduction.In order to make the classification of opening cross-section obtained, valve system or volume flowrate level and smooth, directly actuated equilibrium valve is proposed.Described equilibrium valve can be in ballistic method in rapid succession the short time open, and do not need valve body to reach the final position that it is opened.
The drawback of this ballistic valve is, it is only applicable to limited through-current capacity or needs high device technique cost.
Summary of the invention
On the other hand, task of the present invention is, a kind of valve system with ballistic selector valve is provided, and described selector valve is also applicable to larger through-current capacity or pressure.
This task solves by having the valve system with ballistic selector valve of feature described in claim 1.
The selector valve of described valve system according to the present invention by pilot control (Vorsteuern) and have correspondingly with the main of main piston with the pilot stage of guide piston.Be provided with manipulation electronic equipment in order to manipulate pilot stage, can produce electrical pulse by described manipulation electronic equipment, can on guide piston, form short pratial stroke of endurance by described electrical pulse.Can also on main piston, form thus short pratial stroke of endurance.Pratial stroke refers to, corresponding piston does not run to its final position and described two levels are not exclusively opened correspondingly.Described final position refers to the position that corresponding stage is at utmost opened that causes of respective pistons.Can realize thus continuous ballistic or the pulsed operation of two levels of the selector valve of pilot control.Described two levels can be equivalent to distribute those two levels of selector valve, and described distribution selector valve can be by the pulse of manipulation electronic equipment as the valve that can regulate thus.
So design and adjust described valve system, thereby can being formed until definite rollback point there is the pratial stroke of definite pilot stage endurance in the reproducible pulse duration.Make thus so pilot pressure medium of the amount of metering arrive main, thereby main is carried out until definite rollback point have the pratial stroke of definite endurance.Make thus valve system according to the present invention within the reproducible pulse duration by predetermined pressure medium amount.
Other favourable technological schemes of the present invention have been described in the dependent claims.
In order preferably, to form full stroke on main piston according to the through-flow maximization of pressure medium of the ballistic selector valve of valve system of the present invention, between its backward position and final position or stop member, there is no spacing yet.Described full stroke can also be within an endurance, and the described endurance is many times, for example a minute of pulse.To this respective design manipulation electronic equipment.
Preferably, the full stroke of described main piston forms by the full stroke on guide piston.
In particularly advantageous improvement project, make guide piston centering by two Returnning springs.The home position of the regulation of guide piston is provided thus.In addition, the repeatability of its stroke and its motion are also improved as the response of paired pulses.
Preferably, said two Returnning springs are by pretension, or its spring constant is relatively large.Therefore realize in the time of end-of-pulsing guide piston Rapid reset in its home position, thereby improved the controllability according to selector valve of the present invention.
Described pilot stage can have a pump joint and two control channels, and described control channel is connected with the corresponding end face of main piston.
In particularly preferred improvement project, described main piston is by two Returnning spring centerings.The home position of the regulation of main piston is provided thus.In addition, the repeatability of its stroke and its motion are as the response of pilot stage is improved.Described selector valve avoids fault thus.
Preferably, described two Returnning springs are by pretension, or its corresponding spring constant is relatively large.Therefore realized in the time that the deflection of its pulsed finishes and made main piston Rapid reset in its home position by pilot stage, improved thus according to the controllability of the selector valve of valve system of the present invention.
Advantageously, between pump joint and each control channel, be provided with negative cover folded (ü berdeckung).Described negative covering foldedly formed by guide's housing and the guide piston in its home position.Leakage in having obtained thus from pump joint process control channel to the pilot pressure chamber forming in main piston side, thus make the motion (centering that for example main piston is undertaken by its spring) of main piston can not cause the no load running of control channel.
If pilot stage has two first magnet cases, described two first magnet cases are arranged on guide piston and relatively and work opposed to each other, and the pulse of staggering by two times on described two first magnet cases has realized the short opening time of pilot stage and then main.The first pulse is to open pulse and the second pulse is make pulse.Can form respectively thus short and strong pressure medium pulse and carry out main described in open and close, stop time (Totzeit) has been minimized and has been obtained the less deviation of overall pulse endurance.Under special circumstances, two pulses on two first magnet cases can overlap in time, thereby have also realized pilot stage and then also had resetting time fast of main.
At this preferably, described guide piston is clamped between two armature (Anker) of two first magnet cases.Described clamping can realize by corresponding push rod directly or indirectly, and described push rod is fixed on corresponding armature, and described push rod abuts on guide piston corresponding distolateral.Avoid thus the gap between corresponding armature and guide piston, improved thus the repeatability of selector valve for the response of pulse.
In order to form pretension, the spring being arranged in corresponding utmost point pipe can carry out pretension to corresponding armature (necessary time was connected its push rod) with respect to guide piston, or at two first magnet case places, lasting basic energising is set.
Possibility is, for fear of the gap between corresponding armature and guide piston, can also be for example by the sealed connection of shape, by screwing or between these two parts, connection being set by joggle.
If described main has pump joint and working joint, minimum in order to make to leak according to ballistic selector valve according to the present invention, between main casing and main piston between pump joint and each working joint preferred existence just covering folded.Make thus valve system according to the present invention be specially adapted to the load by its supply to carry out position regulation.
In order to improve the repeatability of response of pilot stage and then selector valve paired pulses, be preferably provided with and promote circuit (Boostschaltung).At this, can produce pulse by manipulation electronic equipment, for example make first magnet case cross energising with more than one double rated current by described pulse.Improve thus the movement velocity of piston, thereby improve the controllability of selector valve.
In order to improve the repeatability of response of pilot stage and then selector valve paired pulses, be preferably provided with low-impedance first magnet case (being less than 5 ohm).Improve thus the movement velocity of piston, thereby improve the controllability of selector valve.
According in the preferred variant of the valve system of the leakage rate with reduction of the present invention, pilot stage or main are seat valve (Sitzventil), are seat valve pistons thereby make described main piston or guide piston.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, described embodiments of the invention are described in detail.Wherein:
Fig. 1 shows according to the cross sectional view of the embodiment's of valve system of the present invention selector valve;
Fig. 2 shows according to the guide piston stroke of valve system of the present invention and the plotted curve of relation between the pulse duration;
Fig. 3 shows the time plot of guide piston stroke, main piston stroke and cylinder stroke;
Fig. 4 shows the cut-away view of the pilot stage of selector valve;
Fig. 5 shows the cut-away view of the main of selector valve; And
Fig. 6 shows the side direction partial cross section view of the utmost point pipe of selector valve.
Reference numerals list
1 main
2 pilot stage
4 guide pistons
6 (pilot stage) longitudinal axis
8 guide's housings
10a (pilot stage) the first Returnning spring
10b (pilot stage) the second Returnning spring
The first magnet case of 12a first
The first magnet case of 12b second
14 main casings
16 (main) longitudinal axis
18 main pistons
20a the first pilot pressure chamber
20b the second pilot pressure chamber
22a (main) the first Returnning spring
22b (main) the second Returnning spring
24a the first pilot pressure passage
24b the second pilot pressure passage
26 compared with short burst
28 compared with long pulse
30 less and shorter strokes
32 more greatly and longer stroke
34 (pilot stage) stroke curve
36 (main) stroke curve
38 (pilot stage) pratial stroke
40 (main) pratial stroke
42 stroke curve
44 initial positions
46 (piston) final position
48 sealed department sections
50 (guide piston) recess
52 cones
54 V-shaped grooves
56 utmost point pipes
58 armature
62 locking mechanisms
64 springs
66 push rods
P'(pilot stage) pump joint
A', B'(pilot stage) control channel
T'(pilot stage) storage tank joint
P (main) pump joint
A, B (main) working joint
T (main) storage tank joint.
Embodiment
Fig. 1 shows according to the embodiment's of the ballistic selector valve of the pilot control of valve system of the present invention cross sectional view.This selector valve has main 1 and pilot control level or pilot stage 2.Described pilot stage 2 has pilot control piston or guide piston 4, and described guide piston is illustrated with its home position in Fig. 1.Described guide piston 4 can move along both direction along longitudinal axis 6.For this reason described guide piston 4 in the housing of guide's controlled stage or guide's housing 8 by two Returnning spring 10a, 10b that longitudinally axle 6 acts on by pretension on its home position and can be so mobile by two first magnet case 12a, 12b, thereby make pump joint P' be connected with the first control channel A' or be connected with the second control channel B'.Corresponding other control channel A' or B' unload towards storage tank joint at this.
Described pilot stage 2 is fixed on the main casing 14 of main 1 by its housing 8, and main piston 18 is movably received within described main casing along longitudinal axis 16.Figure 1 illustrates the main piston 18 in its locked position of coupler or home position, in described position, pump joint P is with respect to two working joint A, B locking.Two pilot pressure chamber 20a, 20b that relatively work are constructed main piston 18 distolateral, in described pilot pressure chamber, held respectively Returnning spring 22a, 22b, described Returnning spring is supported on main casing 14 and makes main piston 18 pretensions in home position.
One of each pilot pressure chamber 20a, 20b two control channel A', B' by pilot pressure passage 24a, 24b and pilot stage 2 are connected.By can mobile main piston 18 like this to the one-sided Loading Control pressure medium of pilot pressure chamber 20a, 20b, thereby pump joint P be connected with in two working joint A, B one.
In the time of valve system operation according to the present invention, for example pump joint P should be connected with the working joint A of main 1.For this, described the first first magnet case 12a is switched on, sees Fig. 1 thereby make described the first first magnet case overcome the second Returnning spring 10b() power guide piston 4 is moved right.Described pump joint P' is connected with control channel B' thus, thereby makes pilot pressure medium enter into pilot pressure chamber 20b by the second pilot pressure passage 24b.Thus, described main piston overcomes the first Returnning spring 22a(and sees Fig. 1) power to left movement, thereby pump joint P is connected with working joint A.Make working joint B unload towards storage tank joint T simultaneously.
According to the present invention, the selector valve pulsed of described pilot control or the operation of ballistic ground.Used (unshowned) amplifier, described amplifier impacts two first magnet case 12a, 12b loading current for this reason.Fig. 2 shows the stroke of guide piston 4 and the graph of relation in pulse duration, and the described pulse duration one of is delivered in two magnet 12a, 12b by amplifier.
Figure 2 illustrates two embodiments.In the first embodiment, described amplifier has loaded relatively short current pulse 26 to first magnet case 12a, 12b.On guide piston 4, form thus relatively little and short stroke 30.When current pulse 28 on magnet case 12a, 12b is longer in the ban, on guide piston 4, form relatively larger and longer stroke 32 of endurance.Described two strokes 30,32 start and end in the home position of the guide piston 4 shown in Fig. 1.Short time open pilot stage 2 by transition ground, utilize the pressure medium of corresponding short time to promote main piston 18 to be transported in one of two pilot pressure chamber 20a, 20b, thereby make the deflection in short time of described main piston and open the corresponding connection of control (aufsteuern) from compression fittings P to one of working joint A, B.
Fig. 3 shows the exemplary curve of stroke curve 34 of guide piston 4 and the stroke curve 36 of main piston 18 forming thus.In this embodiment, first one of first magnet case 12a, 12b are switched on relatively longways, thereby make guide piston 4 remain within a certain period of time (100% guide piston) in its final position.The response of main piston 18 be in time stagger and equally main piston 18 is remained within a certain period of time to (100% main piston) in its final position.
Subsequently, in time graph to first magnet case 12a, 12b with the endurance pulsed that constantly reduces switch on four times, thereby make guide piston 4 implement to have four pratial strokes 38 of the stroke that (with by a small margin) reduce.Show the stroke curve 36 of main piston 18, the pratial stroke 40 that described main piston staggered on four times of same enforcement and (with by a larger margin) reduces for this reason.Each pratial stroke 40 of main piston 18 has formed certain oil mass, and described oil mass is moved out of from working joint A, the B of main 1.
Fig. 3 shows the stroke curve 42 of (the unshowned cylinder) piston being connected on working joint A, B in addition.Shown in time graph move in final position 46 by continuing that energising makes piston near initial position 44 moves to final position 46 and there is with four the movement step that reduces value by four pulses with the endurance reducing the meaning in position regulation subsequently while starting.Utilize and realized by this way position regulation according to valve system of the present invention.
Fig. 4 shows the cut-away view of pilot stage 2.At this, described guide's housing 8 and guide piston 4 only illustrate being connected to pressure chamber on pump joint P' and being connected in the region of the pressure chamber on control channel A' or B'.Pilot stage 2 between described two pressure chambers, have respectively negative cover folded, thereby even also provide pilot pressure medium for filling two pilot pressure chamber 20a, 20b in the home position of guide piston 4.Described negative covering is foldedly made up of recesses 50 on multiple peripheries that are distributed in sealed department section 48, that form by milling.Can make thus flowing to two control channel A', B' from pump joint P' constantly of pilot pressure medium and so on.At guide piston, 4(is shown in Fig. 4) open stroke (pratial stroke of full stroke) to the right time, connect and offside unloaded towards T' by the complete pressure medium of controlling from pump joint P' to control channel A' or B' of circumferentially opening of cone 52 being configured in sealed department section 48.Fold and especially realized the soft shock-free manipulation (volume flowrate increase stably) to main piston 18 by the geometrical shape of guide piston 4 by described negative covering.
Fig. 5 shows the cut-away view of main 1, and described main has its main casing 14 and its main piston 18.At this, described main piston 18 is shown in the region of the pressure chamber being connected with working joint A or B, and wherein adjacent to described pressure chamber, a side has arranged that the pressure chamber and the opposite side that are connected with storage tank joint T arranged the pressure chamber being connected with pump joint P.In the home position of (shown in Fig. 5) main piston 18, be provided with pressure chamber A/B on the one hand with respect to pressure chamber T and folded with respect to just covering of pressure chamber P on the other hand.Make thus the leakage of described main 1 minimize, thereby can not make to supply with and carry out by working joint A/B the load movement of position regulation.Even also can carry out soft shock-free running (velocity curve stably) in order to make supplied with load under pulsed operation according to the present invention, on the one hand, between working joint A/B and storage tank joint T and arranged respectively on the other hand four recesses that are evenly distributed on periphery between working joint A/B and pump joint P, described recess is made up of triangular groove or V-shaped groove 54.
Fig. 6 shows the utmost point pipe 56 of first magnet case 12a or 12b.Therein, armature 58 is contained in the portion's section that deviates from guide piston 4, and described armature can move along longitudinal axis 6 in utmost point pipe 56.In the outside end portion section of utmost point pipe 56, be provided with locking mechanism 62, spring 64 is supported on described locking mechanism.By described spring 64 make armature 58 and be especially fixed on push rod 66 on armature 58 with respect to distolateral (with reference to Fig. 1) accordingly of guide piston 4 by pretension.Thus, described guide piston 4 is clamped between described two push rods 66 always, thereby in the time giving (unshowned) coil electricity of first magnet case 12a, 12b, described guide piston 4 just can start desired stroke movement without time delay or stop time.Improve thus according to the controllability of the selector valve of valve system of the present invention.
Different from the position regulation shown in Fig. 3, also can realize pressure adjusting or speed adjusting (with low speed) by described selector valve.
The invention discloses a kind of ballistic selector valve of pilot control.Described selector valve has with the main of main piston with the pilot stage of guide piston.Be provided with manipulation electronic equipment in order to manipulate pilot stage, can produce electrical pulse by described manipulation electronic equipment, can on guide piston, form short pratial stroke of endurance by described electrical pulse.Can also on main piston, form thus short pratial stroke of endurance.Described pratial stroke refers to, corresponding piston does not arrive in its final position and described two levels are not opened correspondingly completely.Continuous ballistic or the pulsed operation of two levels of selector valve are realized thus.
Claims (14)
1. valve system, described valve system has selector valve, described selector valve has with the main of main piston (18) (1), described valve system also has manipulation electronic equipment, can form electrical pulse (26 by described manipulation electronic equipment, 28), by described electrical pulse can described main piston (18) upper form the endurance short open stroke (40), final position or the stop member of its backward position and described main piston (18) have spacing, it is characterized in that, described selector valve has the pilot stage (2) being connected between described manipulation electronic equipment and described main (1), described pilot stage has guide piston (4), on described guide piston, can pass through described electrical pulse (26, 28) what the formation endurance was short opens stroke (38), its backward position and its final position or its stop member have spacing.
2. valve system according to claim 1 wherein can form full stroke on described main piston (18), and its backward position and final position or stop member do not have spacing.
3. valve system according to claim 1 and 2, wherein said guide piston (4) carries out centering by two Returnning springs (10a, 10b).
4. valve system according to claim 3, wherein, described two Returnning springs (10a, 10b) are relatively large by pretension or its corresponding spring constant.
5. according to the valve system described in any one in the claims, wherein said pilot stage (2) has pump joint (P') and two control channels (A', B'), corresponding distolateral being connected of described control channel and described main piston (18).
6. according to the valve system described in any one in the claims, wherein said main piston (18) carries out centering by two Returnning springs (22a, 22b).
7. valve system according to claim 6, wherein said two Returnning springs (22a, 22b) are relatively large by pretension or its corresponding spring constant.
8. according to the valve system described in any one in claim 5 to 7, wherein between described guide piston (4) and guide's housing (8), between described pump joint (P') and each control channel (A', B'), be provided with negative cover folded.
9. according to the valve system described in any one in the claims, wherein, described pilot stage (2) has two first magnet cases (12a, 12b), and described first magnet case is arranged in opposed to each other described guide piston (4) above and relatively works.
10. valve system according to claim 9, wherein said guide piston (4) is clamped between the armature (58) of described two first magnet cases (12a, 12b).
11. according to the valve system described in any one in the claims, wherein said main (1) has pump joint (P) and two working joints (A, B), and wherein between described main piston (18) and main casing (14), between described pump joint (P) and each working joint (A, B), be provided with just cover folded.
12. according to the valve system described in any one in claim 9 to 11, and wherein said manipulation electronic equipment can form pulse, in described pulse, described first magnet case (12a, 12b) is carried out to energising.
13. according to the valve system described in any one in claim 9 to 12, and wherein said first magnet case (12a, 12b) has 5 ohm of <, the impedance of especially≤2 ohm.
14. valve systems according to claim 1 and 2, wherein said guide piston or main piston are seat valve pistons.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE201210020582 DE102012020582A1 (en) | 2012-10-22 | 2012-10-22 | Valve arrangement with ballistic servo-controlled directional valve, has pilot piston that produces opening stroke with short duration through electric pulses generated over electronic control unit |
| DE102012020582.1 | 2012-10-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103775417A true CN103775417A (en) | 2014-05-07 |
Family
ID=50436744
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310494038.4A Pending CN103775417A (en) | 2012-10-22 | 2013-10-21 | Valve system |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN103775417A (en) |
| DE (1) | DE102012020582A1 (en) |
| IT (1) | ITMI20131729A1 (en) |
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| CN105384092A (en) * | 2015-12-24 | 2016-03-09 | 中联重科股份有限公司 | Hydraulic control method |
| CN108518377A (en) * | 2018-05-18 | 2018-09-11 | 宁波真格液压科技有限公司 | A kind of automatic diverter valve for garbage compression station |
| CN109072949A (en) * | 2016-03-02 | 2018-12-21 | 莫戈公司 | Enclosed center pressure flow control valve |
| CN109723892A (en) * | 2018-06-12 | 2019-05-07 | 珠海市思卡净化技术有限公司 | A kind of novel intaking & discharging combined valve for air |
| GB2584970A (en) * | 2014-11-14 | 2020-12-23 | Domin Fluid Power Ltd | Improvements in and relating to servo valves |
| CN113357214A (en) * | 2021-06-10 | 2021-09-07 | 涌镇液压机械（上海）有限公司 | Hydraulic proportional reversing valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104196792A (en) * | 2014-07-31 | 2014-12-10 | 红安安达新材料有限责任公司 | Three-position four-way directional control valve |
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| CN101349358A (en) * | 2008-08-22 | 2009-01-21 | 三一重工股份有限公司 | Control method and control system of proportion valve |
| CN201372979Y (en) * | 2009-02-20 | 2009-12-30 | 台湾油研股份有限公司 | Electro-hydraulic reversing valve |
| CN101886642A (en) * | 2010-07-26 | 2010-11-17 | 海门市油威力液压工业有限责任公司 | Pilot-operated electrical feedback proportional direction valve |
| CN102402228A (en) * | 2010-09-15 | 2012-04-04 | 罗伯特·博世有限公司 | Method For Controlling A Ballistic Movement Of A Retaining Element Of A Valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE102009052285B4 (en) | 2009-11-09 | 2020-10-15 | Robert Bosch Gmbh | Digital hydraulic valve |
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- 2013-10-21 CN CN201310494038.4A patent/CN103775417A/en active Pending
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| CN201372979Y (en) * | 2009-02-20 | 2009-12-30 | 台湾油研股份有限公司 | Electro-hydraulic reversing valve |
| CN101886642A (en) * | 2010-07-26 | 2010-11-17 | 海门市油威力液压工业有限责任公司 | Pilot-operated electrical feedback proportional direction valve |
| CN102402228A (en) * | 2010-09-15 | 2012-04-04 | 罗伯特·博世有限公司 | Method For Controlling A Ballistic Movement Of A Retaining Element Of A Valve |
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| GB2584970A (en) * | 2014-11-14 | 2020-12-23 | Domin Fluid Power Ltd | Improvements in and relating to servo valves |
| GB2584970B (en) * | 2014-11-14 | 2021-05-12 | Domin Fluid Power Ltd | Improvements in and relating to servo valves |
| CN105384092A (en) * | 2015-12-24 | 2016-03-09 | 中联重科股份有限公司 | Hydraulic control method |
| CN105384092B (en) * | 2015-12-24 | 2017-05-17 | 中联重科股份有限公司 | Hydraulic control method |
| CN109072949A (en) * | 2016-03-02 | 2018-12-21 | 莫戈公司 | Enclosed center pressure flow control valve |
| CN109072949B (en) * | 2016-03-02 | 2020-06-16 | 莫戈公司 | Closed central pressure flow control valve |
| CN108518377A (en) * | 2018-05-18 | 2018-09-11 | 宁波真格液压科技有限公司 | A kind of automatic diverter valve for garbage compression station |
| CN109723892A (en) * | 2018-06-12 | 2019-05-07 | 珠海市思卡净化技术有限公司 | A kind of novel intaking & discharging combined valve for air |
| CN113357214A (en) * | 2021-06-10 | 2021-09-07 | 涌镇液压机械（上海）有限公司 | Hydraulic proportional reversing valve |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102012020582A1 (en) | 2014-04-24 |
| ITMI20131729A1 (en) | 2014-04-23 |
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Application publication date: 20140507 |