CN101512164A - Control system for hydraulic unit - Google Patents

Control system for hydraulic unit Download PDF

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Publication number
CN101512164A
CN101512164A CNA2007800281944A CN200780028194A CN101512164A CN 101512164 A CN101512164 A CN 101512164A CN A2007800281944 A CNA2007800281944 A CN A2007800281944A CN 200780028194 A CN200780028194 A CN 200780028194A CN 101512164 A CN101512164 A CN 101512164A
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CN
China
Prior art keywords
pressure
valve
pressure chamber
control system
piston
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CNA2007800281944A
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Chinese (zh)
Inventor
阿道夫·特莱茨
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Aros Hydraulik GmbH
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Aros Hydraulik GmbH
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Publication of CN101512164A publication Critical patent/CN101512164A/en
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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
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0406—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of balls
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/261—Locking mechanisms using positive interengagement, e.g. balls and grooves, for locking in the end positions
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)

Abstract

In the case of a control system for a hydraulic element (14) which, under the pressure of hydraulic fluid in a locking pressure space (16) on one side of the hydraulic element (14) enters into an unlocking pressure space (13) on the other side of the hydraulic element (14), wherein the two pressure spaces (13, 16) are connected via a respective line (19) and (20) to the same main line (3, 4), a pressure-regulating valve (18) is to be connected into the line (19) to the unlocking pressure space (13), preventing the fluid from flowing back out of the unlocking pressure space (13). Furthermore, a pressure-compensating valve (21) is to be connected into the line (20) to the locking pressure space (16).

Description

The control system that is used for hydraulic element
Technical field
The present invention relates to a kind of control system that is used for hydraulic element, sail in the pressure chamber of unlocking of hydraulic element opposite side under the pressure of its interlocking pressure chamber internal pressure fluid on hydraulic element one side, wherein, two pressure chambers respectively are connected on the identical person in charge by a pipe.
Background technique
The control system of hydraulic element has a lot.Exemplarily, can be referring to the clutch release slave cylinder that can interlock in certain location.The clutch release slave cylinder that has for example shown a kind of pressure medium-driven in DE 41 41 460 C2, wherein, a rotatable axle is mediated in the piston rod tube.If the respective pistons that belongs to this piston rod tube is exerted pressure, axle is also rotated, and the piston rod tube just can axial motion so.
In all these clutch release slave cylinders, all there is a problem, if the pressure of original main pressure chamber's (wherein the piston band is compressed into vapour) is the disintegration owing to the stuffing box gland ring scission for example, then under induced pressure or under the tractive force effect and voluntarily motion of this piston, the axle outside thread can rub bad piston rod tube internal thread.For avoiding this situation, consider the clutch release slave cylinder interlocking is also promptly stoped the motion of piston.According to EP 1,538 344 A2, the interlock body that is under the spring force is mediated in the interlocking hole in the axle, stop the rotation of axle, can realize this point.If will unlock, then overcome spring force by means of fluid working substance, make interlock body change the position of unlocking over to from interlocking position, in this position, axle can be rotated around running shaft.But the difficult problem of this structure is how to control pressure medium to flow into the pressure chamber and the pressure chamber of unlocking.In addition, when breaking down in fluid importing or guiding system, this controlling is integration problem.
But these problems are not only like this for the clutch release slave cylinder that can interlock, and for all hydraulic element can motion between two pressure chambers, but the hydraulic system that immerses in pressure chamber's (wherein two pressure chambers link to each other with the identical person in charge) of being bound to during in fault or analogue is also like this.
Summary of the invention
The invention task
Task of the present invention is to improve a kind of process of controlling as this type, and its " intelligently " is implemented the interlocking of hydraulic element and unlocked.
Solution
For solving described task, a pressure regulator valve need be inserted and lead in the pipe of the pressure chamber of unlocking, this pressure valve suppresses the backflow from the fluid of the pressure chamber of unlocking.
This pressure regulator valve has guaranteed, is closing under the situation of main valve, leads to pressure in the pipe of the pressure chamber of unlocking always than the value (for example 2bar) of the low expectation of the pressure in the pipe that leads to the pressure chamber that interlocks.
Therefore, when touching upon pressure regulator valve in this application, comprise the element that each suppression fluid refluxes.Equally, above-mentioned hydraulic element can have shape and structure arbitrarily.
Second structural design of the control system of the present invention of also asking for protection is separately led to the equilibrated valve access in the pipe of the pressure chamber that interlocks.It designs in hydraulic system, and this system both also can be with pressure regulator valve work with pressure regulator valve work.This equilibrated valve is at first to fault-resistant.For this purpose, with its special tectonic.Have a sliding piston in the axial step hole of equilibrated valve, it links to each other with the fluid import system.For this reason, form a T shape pipe in sliding piston, it converges along the internal surface towards shoulder hole radially, and preferably converges in the circular groove.The sliding piston that is connecting circular groove no longer is close to the internal surface of shoulder hole, but constructs an annular space there, and by this annular space, pressure fluid can flow in the flowing-through chamber and flow in addition in the pipe of the pressure chamber that interlocks leading to behind hydraulic element.
In addition, this sliding piston presses against on the spheroid that is under the spring pressure.Sliding piston can push into spheroid in the ball seat, calibrates (nivelliert) automatically at this ball seat interior spheroid.Thus, interrupted pressure medium and flow through flowing behind the Guan Erxiang hydraulic element that lead to the pressure chamber that interlocks, perhaps kept the pressure in the interlocking pressure chamber, thereby avoided unlocking of hydraulic element reliably.
In another embodiment of the present invention, sliding piston is configured to intercept the form of piston (Blendkolben).Sliding piston equally as previously discussed is such, and it also slides in shoulder hole, but it has a dividing plate in inside, dwindled opening substantially by it.Thus, percolation does not depend on that the temperature of pressure medium or viscosity change.But, intercept piston and work with spheroid one in the same way, wherein, it points to spheroid and constitutes an annular edge, formed body in this annular edge, forming, thus pressure medium can pass spheroid and intercept in the pipe that arrives between the piston thereafter.
Pressure regulator valve of the present invention before the pressure chamber of unlocking of hydraulic element according to following structure, promptly, make in fluid system when constituting hydrodynamic pressure pressure medium percolation overcurrent to the pressure chamber of unlocking, then by other pressure chambers that are responsible for feed with the pressure admission.At this on the one hand, the pressure regulator valve can regulate is proved to be favourable.In addition, inserted the load lock valve and distribute a safety check to it before other pressure chamber in bypass, this safety check all designs highlyer than the pressure regulator valve before the pressure chamber of unlocking in all cases.This just means to have only pressure fluid to flow to the pressure chamber of unlocking under certain pressure altitude in being no more than the fluid import system, and this just makes hydraulic element at first mobile.Have only when surpassing certain force value in fluid system, pressure fluid just flow in the pressure chamber via the safety check in the bypass of load lock valve.
If at the load lock valve or be assigned with the safety check that gives bypass internal burden lock valve when revealing the pressure medium from the pressure chamber reflux, then so on the one hand, if system is blocked, then it flow in the hydraulic element pressure chamber of unlocking before by pressure regulator valve, also flow in the hydraulic element interlocking pressure chamber afterwards by equilibrated valve and annular space but then.Pressure in the interlocking pressure chamber after hydraulic element under the situation that main valve is closed than the 2bar at least of the pressure height in the pressure chamber of unlocking before the hydraulic element.Because in the interlocking pressure chamber, exist the spring of supporting hydraulic element in addition, so hydraulic element always remain in the chain state.
If in contrast, it is malfunctioning fully that for example its safety check is given in load lock valve or distribution, then may be in reflow pipe moment produce pressure and raise.In this process, close to equilibrated valve same moment, because the amount of pressure fluid by T shape pipe is by circlet shape gap very and push sliding piston downwards and spheroid is pressed in its ball seat.This just causes the pump action of the interlocking pressure chamber internal pressure fluid after the hydraulic element, thereby makes the rising of the pressure chamber's internal pressure of unlocking that hydraulic element are preceding can not cause hydraulic element to come out from its lock state.Pressure in the interlocking pressure chamber behind the hydraulic element under the situation of the main valve of closing than the 2bar at least of the pressure height in the pressure chamber of unlocking before the hydraulic element.
If will design a plurality of pressure chambers, the suitable load lock valve that then preferably in bypass, has safety check apparently for each pressure chamber's design, wherein this system interconnects by changing valve, the pipe that leads to the pressure chamber of unlocking before hydraulic element therefrom diverges, and adjustable pressure regulator valve is placed pipe.In this case, the load lock valve always just control naturally with various situations under all lead each of other load lock valves be responsible for and interrelate, open other the load lock valve under the various situations thus, thereby make and become possibility from backflow not with the pressure medium of the pressure chamber of pressure medium admission.
When with the design of lockable valve when being used to supply with the main valve of whole fluid import system, equilibrated valve is particularly suitable.But also can consider to be provided with the valve that the authorized pressure medium refluxes simultaneously from two pipes, thereby can under slight situation of leaking, carry out pressure balance, while and the above-mentioned equilibrated valve of inoperation by this valve.In this case, also design pressure equilibrium valve there still, because it is when the moment rising of intrasystem pressure, in any case must be under the situation that main valve is closed to supply with interlocking pressure chamber after the hydraulic element exceeding the pressure of 2bar than the chamber of unlocking before the hydraulic element, thereby in any case make that unlocking of hydraulic element is impossible.
In another embodiment of hydraulic system of the present invention, save pressure regulator valve in the pipe of the pressure chamber before leading to lockweight.But it is important keeping equilibrated valve.In addition, but with the responsiveness (Ansprechbarkeit) of the safety check around the load lock valve reduce to basically, almost nil and in the person in charge, embed extra dividing plate.Form a system thus, this system does not rely on the viscosity of variation of temperature or pressure medium and it has guaranteed, the piston of the interlocked clutch release slave cylinder between two pressure pads is directed in the corresponding pressure chamber.Another advantage is that by the pressure limit of the safety check around the cancellation load lock valve, clutch release slave cylinder can overcome higher load in fact.
If make up a pressure in each is responsible for, then pressure medium flows in the corresponding pressure chamber of clutch release slave cylinder.But the piston of clutch release slave cylinder can not move, because other loads locking valves under every kind of situation are all by locking.This just means, is in the ingress pipe of the pressure chamber of leading to clutch release slave cylinder or is leading in the ingress pipe of the pressure chamber before the lockweight and all make up a higher in fact pressure, and described pressure causes closing of equilibrated valve.Then, just need further to improve the pressure in the lockweight pressure chamber before, the helical spring power after lockweight is overcome.The pressure medium of corresponding existence is opened by the safety check pushing.
This moment, lockweight was untied interlocking.As if further improving pressure this moment, then other load lock valve is corresponding carries out, thereby pent pressure chamber can emptying till feasible extremely this moment.At this moment, the piston of clutch release slave cylinder can move.
If break down, then guarantee lockweight work always as desired by equilibrated valve of the present invention and set dividing plate.
Other advantages of the present invention, feature and details are provided by preferred embodiment and following description with reference to the accompanying drawings; Accompanying drawing is
Description of drawings
Fig. 1 is the block diagram with the control system of the interlocked clutch release slave cylinder of longitudinal section demonstration.
Fig. 2 is the block diagram of another main valve that is used for the control system of Fig. 1.
Fig. 3 is the enlarged diagram from operational module in the equilibrated valve zone.
Fig. 4 runs through the amplification sectional view that intercepts piston.
Fig. 5 is the block diagram with another embodiment of the control system of the interlocked clutch release slave cylinder of longitudinal section demonstration.
1: the clutch release slave cylinder 2 that can interlock: operational module
3: be responsible for 4: be responsible for
5: main valve 6: piston
7: pressure chamber 8: pressure chamber
9: piston rod 10: axle
11: outside thread 12: index plate
13: the pressure chamber 14 of unlocking: lockweight
15: helical spring 16: the interlocking pressure chamber
17: changing valve 18: pressure regulator valve
19: pipe 20: pipe
21: equilibrated valve 22: safety check
23: safety check 24: the load lock valve
25: load lock valve 26: pipe
27: pipe 28: bypass
29: bypass 30: safety check
31: safety check 32: boring
33: inserting member 34: shoulder hole
35: ball seat 36: spheroid
37: helical spring 38: sliding piston
39:T shape pipe 40: circular groove
41: annular space 42: flowing-through chamber
43: internal surface 50: intercept piston
51: through hole 52: dividing plate
53: current mouthful 54: annular edge
55: interior formed body 56: dividing plate
57: dividing plate 58: dividing plate
59: dividing plate A: the longitudinal axis
Embodiment
According to Fig. 1, the clutch release slave cylinder that can interlock was equipped with the operational module 2 that a dotted line shows in 1 minute.Be responsible for 3 with 4 main valves 5 that are connected with the pressure source of the fluid that is not shown specifically from operational module 2 guiding.Gas, liquid, particularly hydraulic fluid are source pressures.
For more elaborating the clutch release slave cylinder that to interlock, consult P102005015059.4 especially.In this clutch release slave cylinder 1, a slidably piston 6 is arranged between two pressure chambers 7 and 8.On this piston 6, connect a piston rod that outwards travels 9.An axle 10 is arranged in described piston 6, and the corresponding internal thread synergy in its outside thread 11 and axle 6 or the piston rod 9 makes this axle 10 around its longitudinal axis A rotation.Wherein, this axle 10 is carried index plate 12, and it has many radially-arranged pressure chambers 13 of unlocking.Lockweight 14 under one (or a plurality of) that radially travel and pressure that be in helical spring 15 can sail in this pressure chamber 13 of unlocking, and wherein, this helical spring 15 is arranged in the interlocking pressure chamber 16 after the lockweight 14.
The above-mentioned person in charge 4 is from main valve pilot pressure chambers 75, thereby when stuffing pressure chamber 7, piston rod 9 is drawn into.Be responsible for 3 from main valve pilot pressure chambers 85, thereby when stuffing pressure chamber 8, piston rod 9 is pushed out or is pushed extrusion.
In addition, two be responsible for 3 with 4 via changing valve 17 be connected via the adjustable pressure regulator valve 18 in the pipe 19.
Interlocking pressure chamber 16 via another pipe 20 on the one hand by equilibrated valve 21 be responsible for 3 and be connected, on the other hand by divide other recoil valve 22 with 23 with the person in charge 3 or be responsible for 4 and be connected.
No matter be responsible in 3 or be responsible in 4, access load lock valve 24 or 25 before being connected to corresponding pressure chamber 7 or 8.Each load lock valve 24 or 25 be adjustable and via the pipe 26 of the signal of dotted line separately or 27 with divide other another load lock valve 25 or 24 before the person in charge 3 or 4 link to each other.In addition, each load lock valve 24 or 25 has bypass 28 or 29, wherein inserts safety check 30 or 31.
This control system is allowed following possibility and function, and the coordinated of clutch release slave cylinder and control system can be called as " intelligent cylinder ".
Normal running
Conspicuous, before piston 6 motions, it must be interlocked, this means that lockweight 14 must leave the interlocking pressure chamber.There is not special inductor to observe under the situation of this lockweight 14, must how cylinder is known be carried out this process before setting up pressure within pressure chamber 7 or 8?
For this purpose, make the safety check 30 and 31 on adjustable pressure regulator valve 18 harmonious.If will be for example shown in Figure 1ly with pressure fluid stuffing pressure chamber 8, this just means that clutch release slave cylinder plays the pushing effect, position shown in then changing valve 17 is positioned at and pressure flow physical efficiency flow into the pressure chamber 13 of unlocking via the pressure regulator valve 18 that is adjusted to 2bar with pipe 19, until the pressure that reaches 20bar there, but lockweight 14 is forced out from the pressure chamber 13 of unlocking along the longitudinal under this pressure.Have only when having set up the pressure of 20bar in the system, the safety check 31 in the bypass 29 of load maintaining valve 25 just can be overcome and pressure chamber 8 is filled.
On the contrary, if want stuffing pressure chamber 7 and make that thus clutch release slave cylinder is drawn, then pressure fluid is imported among the person in charge 4 by promoting main valve 5 to the right.The changing valve 17 of transferring thus, thus locking this moment is led to and is responsible for 3 path.In contrast, the person in charge 4 is connected with lockweight 14 pressure chamber 13 of unlocking before via adjustable pressure regulator valve 18.In addition, send signal to load lock valve 25, make it open via pipe 27, thus pressure fluid can be from the pressure chamber 8 via be responsible for 3 and main valve 5 spill.
At this moment, pressure fluid adjustable pressure regulator valve 18 of at first flowing through is because safety check 30 has only when having set up the pressure of 20bar in the system and just opens in the bypass 28 of load maintaining valve 24.But this lockweight 14 is also unlocked under 20bar.
Be interlocking, main valve 5 is inserted the central position,, be responsible for 3 or 4 decompressions for two in this position.Under the pressure of helical spring 15, lockweight 14 is pushed and is pressed in the pressure chamber 13 of unlocking.Stop the rotation of axle 10 thus, make piston 6 remain on this position reliably.
Fault
Have only in the time may causing lockweight 14 by mistake to unlock, fault is only significantly.For example when on load maintaining valve 24 or 25 and particularly on safety check 30 or 31, may mistake occur the time, for example block or during spring breakage, be exactly this situation when valve.In this case, in each system, may set up a pressure, and pressure fluid flow into via adjustable pressure regulator valve 18 in the pressure chamber 13 of unlocking and may unlock to lockweight 14.Can once pass through to select main valve 5, promptly such as shown in Figure 2, avoid this situation.For this main valve,, be responsible for 3 and 4 not by locking, but open wide for backflow at center position.This means, in whole system, can not set up the pressure that causes lockweight 14 to unlock.
But it is desirable for the main valve 5 that uses in other respects as Fig. 1 in many cases.In this case, equilibrated valve 21 of the present invention is used in just special hope.Be this equilibrated valve 21, in operational module 2, design a boring 32, in this hole, have an inserting member 33 the person in charge 3 with between managing 20.This inserting member 33 extends through shoulder hole 34, and forms a ball seat 35 that is used for spheroid 36 in this shoulder hole.It is supported that described spheroid 36 heads on helical spring 37, makes it break away from from ball seat 35.
On the other hand, sliding piston 38 is pressed on the spheroid 36, and this sliding piston is run through by a T shapes pipe 39 that is connected with the person in charge 3.This T shape pipe 39 converges via annular space 41 and connects in the circular groove 40 of flowing-through chamber 42.For forming annular space 41, make sliding piston 38 in this zone of the internal surface 43 of shoulder hole 34, keep a very little space.Adjusting color screw spring 37 makes equilibrated valve 21 close when being responsible for internal pressure for 5bar.In this process, the interaction of spheroid 36 and ball seat 35 has the special benefits that improves than the validity of mitre velve, because the spheroid that is promoted by sliding piston 38 can calibration voluntarily in ball seat 35, thereby balances possible inaccuracy.
If this moment, load maintaining valve 25 or safety check 31 were malfunctioning, then cross T shape pipe 39 at the situation downforce fluid percolation of slowly revealing, circular groove 40 and annular space 41, the spheroid 36 of also flowing through is in intake channel 20 and the interlocking pressure chamber 16.Even reveal the pressure that has surpassed 2bar, between the pressure chamber 13 of unlocking, pipe 19, pressure regulator valve 18, the person in charge 3, equilibrated valve 21, pipe 20 and interlocking pressure chamber 16, carry out pressure balance with pressure reduction in the system of 2bar.In this case, the power of helical spring 15 accounts for leading with the pressure that exceeds 2bar and keeps lockweight 14 at interlocking position.
If load lock valve 25 or safety check 31 are malfunctioning fully, then also can moment improve pressure, this pressure overcomes pressure regulator valve 18 subsequently, but wherein not having enough pressure fluids is transferred by equilibrated valve 21, in order to produce balance.But in this case, sliding piston 38 downward promotions cause pressure moment to be improved, thereby are pressed in spheroid 36 on the ball seat 35 and carry out pressure fluid by managing 20 pump actions that enter in the interlocking pressure chamber 16.In all cases, this pump action surmounts the pressure that enters the pressure fluid in the pressure chamber 13 of unlocking by pressure regulator valve 18 and pipe 19, thereby makes lockweight 14 remain on interlocking position.
Can consider also that as other faults the helical spring 15 before the lockweight 14 ruptures.In this case, in interlocking pressure chamber 16, also possess (anstehen) all system pressures, because do not hindered by the percolation of equilibrated valve 21.On the contrary, pressure regulator valve 18 causes the pressure loss of 2bar at pipe in 19, thereby makes possess the system pressure that reduces 2bar in the pressure chamber 13 of unlocking.Therefore, lockweight 14 be retained in Interlock Status or under the situation of the helical spring of fracture and the main valve of closing the pressure by the 2bar that exceeds in the interlocking pressure chamber 16 lockweight is pushed into interlocking position.
Naturally also can consider,, second equilibrated valve be distributed give load lock valve 24 when described cylinder is being urged when drawing insertion (einsetzen).
In another embodiment, sliding piston is designed to intercept the form of piston 50 according to Fig. 4.This just means that it is arranged on the internal surface 43 of circular groove 40 relatively hermetically, but slips in this circular groove.
This obstruct piston 50 has a through hole 51, and inserts a dividing plate 52 in this hole.This dividing plate 52 feature at first is that it is specifically thin towards current mouthful 53 very little receipts.Known in fluid mechanics, this dividing plate at first at current mouth as far as possible in short-term, has following advantage, and promptly for example oily percolation does not depend on the viscosity of temperature or percolation medium comparatively speaking.
Blocked by interior formed body 55 with spheroid 36 synergistic annular edge 54 down, it has guaranteed that the percolation medium can enter in the shoulder hole 34 and through helical spring 37 and enter in the pipe 20.
Setting at first is inserted in the hydraulic systems with the equilibrated valve 21 of this obstruct piston 50, promptly as shown in Figure 5.Lack pressure regulator valve 18 in this hydraulic systems, be responsible for two dividing plates 56 of existence and 57 in 3 and 4 for this reason, they also can be integrated in the main valve 5.Be connected to before two dividing plates 58 and 59 in addition changing valve 17 and after be connected to recoil valve 23.
The function of this hydraulic systems is as follows:
Normal running
Regulate non-return 30 and 31 this moment, makes them under very little pressure, opens under promptly about 0.5bar.If for example will use pressure fluid stuffing pressure chamber 8, this means that clutch release slave cylinder plays the pushing effect, position and pressure fluid shown in then changing valve 17 is positioned at can arrive pressure chambers 8 via the person in charge 3 with via safety check 31.But piston 6 does not move, because axle 10 is not unlocked.Therefore set up a pressure in the person in charge 3, this pressure causes equilibrated valve 21 to be closed when about 30bar.
Pressure medium flows into via pipe 19 and goes in the chain pressure chamber 13, reaches the pressure of about 50bar until the there, and lockweight is resisting the power (this power is very difficult to (hart) and is conditioned) of helical spring 15 and be pushed extrusion from the pressure chamber 13 of unlocking under this pressure.
But piston 6 still can not move, because load lock valve 24 is in locked position of coupler.Have only when having set up the pressure of about 100bar in the system,, thereby make pressure medium 7 backflows to pass through the person in charge 4 and main valve 5 from the pressure chamber just via pipe 26 control load lock valves 24 and with its release.
In this preferred hydraulic system as can be seen, piston 6 fully consciously and specifically sail into pressure chamber 8 and 7 in two hydraulic die cushions between.Piston 6 always is clamped between this pressure pad.
In contrast, then pressure fluid is imported to the clutch release slave cylinder traction among the person in charge 4 if want stuffing pressure chamber 7 and therefore make by promoting main valve 5 to the right.Changing valve 17 switches thus, makes locking this moment lead to and is responsible for 3 path.In contrast, the person in charge 4 is connected with lockweight 14 pressure chamber 13 of unlocking before via pipe 19.In case the pressure here also surpasses about 50bar, then lockweight 14 heads on the power of helical spring 15 and is unlocked.But, to have only when also therefore load lock valve 25 is switched on the percolation at the pressure of setting up about 100bar in the pipe 27 of load lock valve 25, this moment, piston 6 can move.Therefore, pressure fluid may be from the pressure chamber 8 via be responsible for 3 and main valve 5 leak out, this makes piston to move.
For interlocking lockweight 14 when drawing and when pushing, switch to through-flow main valve 5 or the neutral position, make two to be responsible for 3 or 4 decompressions and to make pressure medium to flow in the groove respectively simultaneously via dividing plate 56 or 57.Under the pressure of helical spring 15 lockweight 14 is pressed in the pressure chamber 13 of unlocking, this process takes place soon.Stop the rotation of axle 10 thus, thereby piston 6 is retained on this position reliably.
Fault
If load lock valve 24 (25) or safety check (30) 31 are malfunctioning, then when slowly revealing, in pipe 19,20 and 3, carry out pressure balance owing to equilibrated valve.In this case, the power of helical spring 15 accounts for leading, makes lockweight 14 enter its interlocking position thus.
If load lock valve 25 or safety check 31 are malfunctioning fully, then also can moment improve pressure.In this case, the pressure of moment is elevated to cause above 30bar and intercepts piston 50 and promotes downwards, thereby is pressed into spheroid 36 on the ball seat 35 and carries out pressure fluid and pass pipe 20 and enter the interior pump actions in interlocking pressure chamber 16.In this case, this pump action surmounts the pressure of the pressure fluid in the pipe 19, makes lockweight 14 be retained in the interlocking position place.
Can consider also that as other faults the helical spring 15 before the lockweight 14 ruptures.In this case, when build-up pressure in conduit 19, too lockweight 14 is unlocked naturally, just slightly hurry up.But still stop the motion of piston by the locking of existing load lock valve 24.
In this case, interlocking is possessed whole system pressures in the pressure chamber 16, because be not prevented from by the percolation of equilibrated valve 21.On the contrary, regulate dividing plate 58 and 59, make and in pipe 20, always possess the higher pressure that causes lockweight 14 to be closed than equilibrated valve 21 ground.

Claims (22)

1, the control system that is used for hydraulic element (14), sail in the pressure chamber of unlocking (13) of hydraulic element (14) opposite side under the pressure of its interlocking pressure chamber (16) internal pressure fluid on hydraulic element (14) one sides, wherein, two pressure chambers (13,16) each is connected to the identical person in charge (3 by a pipe (19) or (20), 4) on, it is characterized in that
Cut-in pressure modulating valve (18) in the pipe that leads to the pressure chamber of unlocking (13) (19), it stops the backflow from the fluid of the pressure chamber of unlocking (13).
2, the control system that is used for hydraulic element (14), sail in the pressure chamber of unlocking (13) of hydraulic element (14) opposite side under the pressure of its interlocking pressure chamber (16) internal pressure fluid on hydraulic element (14) one sides, wherein, two pressure chambers (13,16) each is connected to the identical person in charge (3 by a pipe (19) or (20), 4) on, it is characterized in that cut-in pressure equilibrium valve (21) in the pipe (20) that leads to interlocking pressure chamber (16).
3, control system as claimed in claim 2 is characterized in that, inserts one and head on the spheroid (36) that spring (37) supports in the axial step hole (34) of equilibrated valve (21), and the ball seat (35) of the corresponding shaping in the shoulder hole (34) is given in its distribution.
4, control system as claimed in claim 3 is characterized in that, is pressing a piston (38,50) that is positioned over slidably in the shoulder hole (34) on spheroid (36).
5, control system as claimed in claim 4 is characterized in that, described piston (38) at least in part with inwall (43) the looping gap (41) of shoulder hole (34).
6, control system as claimed in claim 4 is characterized in that, described piston (50) is to intercept piston, wherein has dividing plate (52).
7, as at least one described control system of claim 1 to 6, it is characterized in that, pressure regulator valve (18) guarantees, in the pipe that leads to the pressure chamber of unlocking (13) (19), closing under the situation of main valve (5), always possess than lower pressure in the pipe (20) that leads to interlocking pressure chamber (16) for being responsible for (3,4).
8, as at least one described control system of claim 1 to 7, it is characterized in that described pressure regulator valve (18) is adjustable.
9, as at least one described control system of claim 1 to 8, it is characterized in that the described person in charge (3) imports in another pressure chamber (7) via the tight locking-valve of load (24), wherein in bypass (28), load maintaining valve (24) is given in safety check (30) distribution.
10, control system as claimed in claim 9 is characterized in that, regulates the safety check (30) of the tight locking-valve of load (24) higher than the pressure regulator valve in the pipe that leads to the pressure chamber of unlocking (13) (18).
As at least one described control system of claim 1 to 10, it is characterized in that 11, second pressure chamber (8) is set, and its person in charge (4) is same and main valve (5,5.1) is continuous, wherein, in this person in charge (4), insert the tight locking-valve of another load (25).
12, control system as claimed in claim 11 is characterized in that, leads to before at the pressure regulator valve (18) towards the pressure chamber of unlocking (13) in the connection of the person in charge (3,4) to insert changing valve (17).
As claim 11 or 12 described control systems, it is characterized in that 13, the person in charge (3,4) of other the tight locking-valve of load can connect under tight locking-valve of each load (24,25) and the various situations.
14, as at least one described control system of claim 1 to 13, it is characterized in that the fluid import system is connected with the three-four-way valve of allowing liquid return (5.1).
15, as at least one described control system of claim 1 to 14, it is characterized in that, at least one person in charge (3,4), insert dividing plate (56,57).
16, in order to insert the equilibrated valve of fluid import system and/or fluid guiding system, it is characterized in that, in axial shoulder hole (34), insert and head on the spheroid (36) that spring (37) supports, in shoulder hole (34), distribute the ball seat (35) that gives an one corresponding shaping.
17, equilibrated valve as claimed in claim 16 is characterized in that the piston (38,50) of pressing to be positioned over slidably in the shoulder hole (34) on spheroid (36).
18, equilibrated valve as claimed in claim 17 is characterized in that, described piston (38) at least in part with inwall (43) the looping gap (41) of shoulder hole (34).
19, equilibrated valve as claimed in claim 18 is characterized in that, the T shape manifold that passes sliding piston (38) is incorporated in the circular groove before of annular space (41).
20, equilibrated valve as claimed in claim 17 is characterized in that, is provided with to intercept piston (50) in shoulder hole (34).
21, equilibrated valve as claimed in claim 20 is characterized in that, current mouthful (53) of a very little width are set in intercepting piston (50).
22, as claim 20 or 21 described equilibrated valves, it is characterized in that, interior formed body (55) is set towards the annular edge (54) of the obstruct piston (50) of spheroid (36).
CNA2007800281944A 2006-07-25 2007-07-25 Control system for hydraulic unit Pending CN101512164A (en)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE102006034864.8 2006-07-25
DE102006034867 2006-07-25
DE102006034867.2 2006-07-25
DE102006058271.3 2006-12-08
DE102007002866.2 2007-01-15
DE102007007054.5 2007-02-08

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CN101512164A true CN101512164A (en) 2009-08-19

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DE (1) DE102007007054A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102852869A (en) * 2011-06-30 2013-01-02 日立建机株式会社 Hydraulic circuit for counterweight attaching/detaching device
CN103527534A (en) * 2013-10-24 2014-01-22 连云港天明装备有限公司 Novel feeding hydraulic system of all-hydraulic drill
CN104632782A (en) * 2015-02-10 2015-05-20 无锡智能自控工程股份有限公司 Hydraulic stroke locking mechanism for pneumatic actuator

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Publication number Priority date Publication date Assignee Title
FR3083536B1 (en) * 2018-07-05 2021-06-11 Guima Palfinger LIFTING DEVICE INCLUDING A PERFECTED HYDRAULIC CIRCUIT TO AUTHORIZE A QUICK DUMP RETURN PHASE

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102852869A (en) * 2011-06-30 2013-01-02 日立建机株式会社 Hydraulic circuit for counterweight attaching/detaching device
CN102852869B (en) * 2011-06-30 2016-02-24 日立建机株式会社 Counterweight attaching/detaching apparatus oil hydraulic circuit
CN103527534A (en) * 2013-10-24 2014-01-22 连云港天明装备有限公司 Novel feeding hydraulic system of all-hydraulic drill
CN103527534B (en) * 2013-10-24 2015-09-23 连云港天明装备有限公司 All-hydraulic drill is novel feeds hydraulic system
CN104632782A (en) * 2015-02-10 2015-05-20 无锡智能自控工程股份有限公司 Hydraulic stroke locking mechanism for pneumatic actuator

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