EP0338036B1 - Linearantrieb mit hydraulischer verstärkung - Google Patents

Linearantrieb mit hydraulischer verstärkung Download PDF

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Publication number: EP0338036B1
Authority: EP; European Patent Office
Prior art keywords: actuator; piston; drive; hydraulic; control
Prior art date: 1987-10-20
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.): Expired - Lifetime

Application number

EP88908126A

Other languages

German (de)

English (en)

French (fr)

Other versions

EP0338036A1 (de

Inventor

Peter Fuchs

Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)

MAN B&W Diesel AS

Original Assignee

Nova Werke AG

Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)

1987-10-20

Filing date

1988-09-27

Publication date

1992-04-08

1988-09-27 Application filed by Nova Werke AG filed Critical Nova Werke AG

1988-09-27 Priority to AT88908126T priority Critical patent/ATE74652T1/de

1989-10-25 Publication of EP0338036A1 publication Critical patent/EP0338036A1/de

1992-04-08 Application granted granted Critical

1992-04-08 Publication of EP0338036B1 publication Critical patent/EP0338036B1/de

2008-09-27 Anticipated expiration legal-status Critical

Status Expired - Lifetime legal-status Critical Current

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Classifications

- 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
- F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
- F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
- F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
- F15B9/12—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which both the controlling element and the servomotor control the same member influencing a fluid passage and are connected to that member by means of a differential gearing

Definitions

the invention relates to a linear drive with hydraulic reinforcement consisting of a hydraulic cylinder, the piston of which is connected to a first screw gear, which forms a mechanical return of the piston movements to a control valve piston, a control valve arranged in the longitudinal axis of the first screw drive for the pressure medium, the control valve piston Is displaceable via an actuator, one end of the actuator and the first screw gear are directed towards each other and these ends form the moving parts of a second screw gear and the actuator and the first screw gear are connected and interact with each other via this second screw gear and an actuator acting on the actuator and one Use of this linear drive for driving a fuel injection pump and use for driving the intake and exhaust valves on internal combustion engines.
Such a linear drive with hydraulic amplification is known from CH-A-594 141, the device shown being referred to as a linear amplifier.
This drive has a hydraulic cylinder, the piston rod of which transmits forces directly to machine parts to be moved.
a screw drive is arranged in the piston of the hydraulic cylinder, the nut of which is connected to the piston and the spindle of which is connected to the control piston of a control valve.
the spindle of the screw drive is made in two parts, which results in a reduction in the rotating masses and the second screw drive simultaneously forms an overload protection.
the control movements are generated by an electrically driven stepper motor, which drives the spindle of the screw drive is set in rotation.
the rotating spindle screws into or out of the nut and thereby moves the control piston of the control valve which is mounted on it. This regulates the oil inflow and outflow to the hydraulic cylinder and sets the hydraulic piston in motion.
the generation of the rotary motion on the electric motor requires only a small amount of energy and nevertheless causes large forces on the hydraulic piston.
a coupling must be connected between these elements, which permits axial displacements of the spindle.
This clutch has the disadvantage that the mass that has to be rotated by the motor is increased considerably.
the coupling In order for the accuracy of the transmission of the switching movement from the motor to the spindle to be ensured, the coupling must be designed to be as rigid as possible against rotation, which is associated with considerable difficulties. Due to the rapid and frequent switching operations, the clutch is very heavily loaded, which leads to rapid wear and loss of the accuracy of the motion transmission. In the case of fast drive processes, such as occur, for example, when driving fuel injection pumps and valves in internal combustion engines, and switching times in the range of fractions of a second, the electric stepping motors are in many cases unable to meet the switching times. Improvements are possible through complex technical measures, but lead to very expensive drives, which still have the disadvantage of a short life.
the present invention has for its object to provide a linear drive with hydraulic amplification, in which the movement paths of the control elements are as small as possible, no coupling with axial compensation is necessary between actuator and spindle, actuators with a long service life and very short switching intervals can be used, and at which the hydraulic piston can be moved against fixed stops.
the drive is also intended to allow mechanical limitation of the upper and lower stop positions of the hydraulic piston without electrical position measurement.
the actuator has an active element which generates translatory movements in the direction of the actuator axis, a translationally moving part of this active element and the actuator are connected to one another via a bearing such that the translationally moved part of the active element is connected to the actuator can be moved together along the actuator axis in the direction of the control piston, but the actuator can be rotated about the axis independently of the actuator and the translationally movable part can be moved in the opposite direction independently of the actuator, a lever rotatable with the actuator is attached to the actuator and on the housing of the linear drive there is arranged a stop element which is adjustable in the rotation range of the lever and which interacts with the lever in certain positions predetermined by the holding positions of the piston.
the actuator or its translationally moved active element generates a force acting in the direction of the axis of the linear drive, which acts on the actuator.
the spindle of the second screw drive rotates and thereby causes a displacement of the actuator in the longitudinal axis and at the same time a displacement of the control valve piston.
the control valve piston releases the inflow of pressure oil to the hydraulic piston, which also sets this in motion axially.
the axial movement of the hydraulic piston brings about a rotary movement of the first screw drive, this rotary movement of the first screw drive being transferred to the second screw drive.
the actuator can be rotated about its longitudinal axis independently of the actuator, the actuator rotates with the spindle of the first screw drive as long as the axial force generated by the actuator is maintained. As soon as this axial force is removed, the rotation of the first screw drive via the second screw drive causes the actuator and thus the control valve body to be returned to the starting position. As a result, the hydraulic piston automatically remains in its position.
the second screw drive is a ball screw drive, the nut of this ball screw drive rotatably mounted in the drive housing being firmly connected on the one hand to the spindle of the first screw drive and on the other hand receiving the end of the actuator with the ball screw spindle arranged at this end.
the ball screw drive enables a particularly smooth translational and rotary movement of the actuator. As a result, only very small axial forces have to be applied by the actuator in the direction of the actuator axis in order to generate a rotary movement of the spindle of the second screw drive.
a preferred embodiment of the invention is characterized in that a double-acting piston-cylinder unit is arranged on the actuator as an actuator and this unit generates axial movements of the actuator.
this piston-cylinder unit can be made very small, which enables extraordinarily short switching intervals and still maintains the long service life values known for such control valves.
the double-acting piston-cylinder unit is controlled in a known manner by an electro-hydraulic control valve which receives control impulses from known devices.
a further improvement of the linear drive can be achieved in that the active element of the actuator is a camshaft, a cam of this camshaft interacts with the translationally moving part of the actuator, and the end of the translationally moving part opposite the screw drive is at least partially engaged during one revolution of the camshaft the control surface of the camshaft and the cam. Furthermore, a spring is arranged on the actuator, which acts in the axial direction against the linear movement generated by the screwing in of the second screw mechanism and this spring is articulated on the one hand on the actuator and on the other hand on a fixed support. Since the axial switching paths of the control valve piston and the forces which are necessary for the production of these axial movements are relatively small, the camshaft can be made small and of low mass.
the switching function of the control valve piston is mechanically predetermined by the shape of the cam and the speed of the rotary movement of the camshaft. If an additional switching element in the form of a double-acting piston-cylinder unit is installed between the camshaft and the actuator or active element, the camshaft serves as an emergency drive in addition to the piston-cylinder unit acting as an actuator or can be the only one Serve actuator. This emergency drive is switched on when the electrical control of the piston-cylinder unit fails.
the spring arranged on the actuator is dimensioned such that the actuator is mechanically retracted when the axial force is removed.
the control valve piston is moved so that the hydraulic piston moves back, the spindles of the first and second screw drives rotating together in the same direction.
the lever arranged on the actuator rotates about the actuator axis until it abuts the adjustable stop element. From this moment on, the second screw drive generates an axial movement of the actuator, by means of which the control valve piston is brought into its neutral position. This also stops the hydraulic piston and holds it in this position.
an additional switching and control element displaceable transversely to the axis is installed between the camshaft and the end of the actuator formed by the translationally moved part, and this switching element rests on the control surface of the cam with a roller.
this control element enables the camshaft to be switched on and off and, on the other hand, the modulation of the control movement, which is generated by the cam on the camshaft.
the switching and control element which is displaceable transversely to the axis, has an area with increasing or decreasing thickness. By moving the switching element transversely to the axis, the roller and thus its point of contact on the cam is also moved. The result is a change in the axial movement generated by the cam, i.e. a modulation.
a further preferred embodiment of the invention is characterized in that the actuator and the hydraulic unit are each connected to a measuring device for determining the position in the axial direction. These measuring devices enable control of the current operating conditions and adaptation to any requirements via the control device.
An improvement of the linear drive can also be achieved in that a mechanical one parallel to the control element controlled control slide is arranged, the two pressure medium outputs of this slide open into the cylinder bore and act on the piston of the piston / cylinder unit with pressure medium and the mechanical switching element of this control slide cooperates with the control element and the camshaft.
This embodiment is an even more compact construction and enables the length to be saved.
the mass that has to be moved by the cam is further reduced, which leads to an additional and considerable reduction in the cam forces.
a further improvement in the movement sequences of the stop element in the linear drive can be achieved in that the stop element is adjustable via a rack and can be fixed in certain positions, at least one spring-loaded brake means is arranged on the rack, and this brake means the rack and thus the stop element in one certain position blocked. It is furthermore advantageous if the brake medium is equipped with a piston and a piston chamber, this piston chamber is connected to the pressure medium bore for the cylinder bore and the piston acts against the spring loading of the brake medium when pressure medium from the pressure medium bore is applied and releases it.
FIG. 1 Further preferred embodiments of the invention represent the use of the linear drive according to the invention for driving fuel injection pumps or intake and exhaust valves on internal combustion engines.
the linear drive according to the invention for driving fuel injection pumps or intake and exhaust valves on internal combustion engines.
very short switching times and at the same time an extraordinarily long service life of the device are required.
mechanical emergency running controls are advantageous, which are given in the linear drive according to the invention.
the control valve and the hydraulic piston are to be adapted in a known manner to the needs of use.
linear drive according to the invention is further used in machines and drives in which the drive according to CH-A-594 described as prior art is already used 141 is used.
the advantages described can also be exploited for these other uses.
the linear drive shown in FIG. 1 consists of a hydraulic unit 1 with a piston 2 and a cylinder 3.
a piston rod 15 is led out of the hydraulic cylinder 3 and interacts with the machine element to be moved.
These machine elements, which are actuated by the piston rod 15, are not shown in FIG. 1.
an anti-rotation device 17 Arranged on the wall of the cylinder bore 16 is an anti-rotation device 17 which guides the piston 2 in the axial direction and prevents its rotation about the longitudinal axis.
a first helical gear 4 is arranged, which consists of the nut 18 and the spindle 19. The nut 18 is secured against rotation in the piston 2.
a control valve 5 known per se is arranged on the hydraulic cylinder 3.
the end face 20 of this control valve 5 forms the end flange of the cylinder bore 16 of the cylinder 3.
a control piston 6 which can be displaced in the axial direction and is provided with annular grooves and control edges.
An input line 21 connected to a pressure oil source, not shown, leads via the bores 22 and 23 pressure oil into the control valve 5 and from there, depending on the position of the control piston 6, via the bore 24 into the pressure chamber of the hydraulic unit 1 formed by the cylinder bore 16 Bore 25 and the output line 26 can flow 6 pressure medium from the cylinder bore 16 through the bore 24 when the control piston is in the correct position.
the control piston 6 is mounted on an actuator 7 which is guided through the center of the control piston 6.
This actuator 7 can rotate about its longitudinal axis, whereas the control piston 6 is secured against rotation about the axis by means of the anti-rotation device 27. In the axial direction, the control piston 6 is mounted on the actuator 7 without play.
the nut 28 of a ball screw drive is rotatably supported and secured against axial displacements.
This nut 28 is part of a second screw drive 8 and is fixedly connected to the spindle 19 of the first screw drive 4.
the ball screw 29 belonging to the second screw drive 8 is fastened to the upper end of the actuator 7 and firmly connected to it.
the space 30 between the control piston 6 and the nut 28 is in communication with a bore 31 which leads into a leakage line, not shown.
the actuator 7 is extended and interacts with the active elements of the actuator 9.
the actuator 9 consists in the example shown of a double-acting piston-cylinder unit 32 and one Control element 33.
the unit 32 has a cylinder bore 34, a piston 10, which is connected to a piston rod 35, and bores 36, 37 for the supply and discharge of pressure medium.
the piston rod 35 which forms the translationally moved part, is connected at the upper end via a bearing 38 to the actuator 7 without play, in such a way that the actuator 7 is independent of the piston rod 35, which forms the active element of the actuator 9 can rotate the longitudinal axis.
a measuring sensor 39 is arranged, which determines the position in the axial direction of this piston rod 35, which forms the active element, or of the actuator 7 and transmits it to the control element 33.
Additional control pulses are supplied to the control element 33 via the control line 40.
the oil required for moving the piston 10 is supplied and removed via the pressure oil lines 41 and 42.
Another measuring sensor 43 is located on the hydraulic unit 1, by means of which the position of the hydraulic piston 2 is determined and the corresponding measured values are transmitted to the control element 33 via the line 44.
an element 45 with a radially extending lever 13 is attached to the actuator 7.
a bushing 47 which can be rotated about the axis and has a stop element 14 is mounted in the housing 46.
This sleeve 47 rests on the bearing 48 and is provided on the circumference with a gear 49, in which a rack 50 engages.
This rack 50 is driven by a control unit 51 shown in FIG.
a spring guide cup 52 is arranged above the element 45 and rests on the bearing 53 in such a way that it does not rotate about the longitudinal axis of the actuator 7.
a compression spring 54 is arranged, which rests on the one hand on the cup 52 and on the other hand on the fixed support 55 of the housing. If applicable to the actuator 7 no axial force acts, this spring 54 pushes the actuator 7 and thus the control piston 6 away from the hydraulic unit 1 in the axial direction.
a camshaft 11 with a cam 12 is arranged below the piston-cylinder unit 32.
the piston rod or the translationally moved part 35 is led out of the element 32 in this area and thereby forms an extended end of the actuator 7. If the camshaft 11 is actuated, i.e. rotated about its axis, the end 56 of the piston rod 35 rests on the control surface of the cam 12 and is deflected by the latter in the axial direction. As a result, the actuator 7 and the control piston 6 are also shifted upward and a stroke movement of the hydraulic piston 2 is subsequently initiated.
the operation of the linear drive can be described in the following manner with reference to FIG. 1.
the control piston 6 and the hydraulic piston 2, or the piston rod 15 are in the lower starting position of a stroke movement.
the control element 33 receives a start signal for the initiation of a movement via the control line 40.
the electro-hydraulic control element 33 opens the inflow of pressure oil to the bore 37 and thus to the lower part of the cylinder bore 34 in the piston-cylinder unit 32.
the axial force acting on the piston 10 and the piston rod 35 is directed in the direction of the hydraulic unit 1. This axial force is transmitted to the actuator 7 via the bearing 38 and thus acts on the spindle 29 of the ball screw 8.
the applied axial force is here at least partially converted into a torque acting on the actuator 7, since the nut 28 of the ball screw 8 is stationary.
the spindle 29 screws into the nut 28 and thus follows the one generated by the piston 10 in the actuator 9 translational movement. Since the control valve piston 6 is supported on the actuator 7 without play is, this also shifts in the direction of the hydraulic unit 1 and thereby releases the inflow of pressure oil from the bores 22 and 23 to the bore 24 and thus to the cylinder bore 16.
the pressurized oil acting on the hydraulic piston 2 causes a lifting movement of the piston rod 15. This movement in the axial direction is also followed by the nut 18 of the first screw drive 4, which is fastened in the piston 2.
the slopes of the two spindles 19 and 29 are in opposite directions, so that the hydraulic piston 2 and the control piston 6 would have to move away from one another in the opposite direction in the case of freely rotating spindles 19 and 29.
the active element, or the piston 10 of the actuator 9 continues to press against the actuator 7 and thus onto the spindle 29 in the nut 28. This force is so great that the spindle 29 cannot turn back , whereby the control piston 6 remains in the deflected position.
the spindle 29 of the ball screw 8 thus rotates at the same speed as the nut 28 about the longitudinal axis. This is made possible by the mounting of the actuator 7 on the control piston 6 and the bearing 38 at the end of the piston rod 35.
a single-acting piston is used as the hydraulic piston 2.
the force acting on the piston 10 of the actuating device 9 is reduced by interrupting the pressurization and the bore 37 is connected to the return 42.
the control piston 6 In follow a residual rotational movement of the spindle 19, or nut 28 and / or due to the restoring force of the spring 54, which acts on the actuator 7, the control piston 6 is initially placed in its neutral position, and then in the return position.
the bore 24 is connected to the bore 25, and the oil in the cylinder bore 16 can flow out into the outlet line 26.
an air spring interacts with the piston rod 15, which is not shown in FIG. 1, but can be seen in FIG. 3. This air spring presses the piston rod 15, and thus the piston 2, back into the cylinder 3, ie against the region of the bottom dead center.
both the input line 21 and the output line 26 are separated from the bore 24, and the piston 2 stops, since no pressure medium inflow or outflow is possible from the cylinder bore 16. Since the piston 2 moves back relatively slowly and with little force, in contrast to the stroke movement, the lever 13 and the stop element 14 can be of simple and rigid design. As a result of the direct mechanical feedback via the spindle 19 and the actuator 7, the positioning of the piston 2 is very great repeatable exactly and arbitrarily. In the example shown, the stroke of the piston 2 or the piston rod 15 is measured from the top dead center, the bottom dead center of the piston 2 being variable. This results in a purely volumetric dimensioning for the total stroke of the piston 2, which is neither dependent on a timing element nor on other faulty measuring devices.
the stop element 14 is arranged on the bushing 47, which can be rotated about the longitudinal axis of the actuator 7.
the sleeve 47 is mounted in the housing 46 and rests on a bearing 48.
this rack is driven by a control unit 51 which is mounted on the housing 46.
the control unit 51 contains a corresponding known drive.
the control unit 51 receives the corresponding control signals from a central control device, not shown.
a braking means 92 is arranged, with which the movement of the rack 50 can be blocked.
the brake means 92 is pressed against the rack 50 by the plate spring 91, so that the control unit 51, which has limited feed forces, cannot move the rack 50 while the lever 13 is in contact with the stop element 14.
the piston chamber 93 is also pressurized via the bore 94, so that the piston 90 lifts the brake pin from the rack 50 and the control unit 51 up to the return stroke the new position of the stop element 14 can adjust.
the pitch of the spindle 19 and the stroke of the piston 2 are dimensioned such that the stop element 14 is adjustable in the range of one revolution around the axis.
the bushing 47 can also use the control unit 51 to make parts of one or more additional turns carry out in order to be fixed again in the desired position.
the measurement sensors 43 and 39 shown in FIG. 1 are used to monitor the correct position of the hydraulic piston 2 and the piston 10 acting as a translational active element in the actuating device 9. These devices are used to optimize and additionally refine the functional sequence of this device. In an emergency, the device shown here can also be operated in the event of failure of the electrical measuring and control devices if, as shown in FIG. 1, a camshaft 11 with a cam 12 is installed for actuation.
the control cam 12 acts with the control surface on the end 56 of the piston rod 35, which forms an extension of the actuator 7.
the cam 12 deflects the actuator 7 upwards, and the force acting on the spindle 29 of the ball screw 8 causes the actuator 7 to be screwed in, and thus an adjustment of the control piston 6 to the position in which pressure oil is introduced into the hydraulic unit 1.
the rest of the functional sequence corresponds to the steps described above.
the compression spring 54 causes the return of the control piston 6, and thus the return stroke of the hydraulic piston 2.
FIG. 3 shows a use of the linear drive according to the invention according to FIG. 1 in connection with a fuel injection pump 61 for a heat engine.
the fuel injection pump 61 consists of a pump piston 63 which is guided in a cylinder liner 64.
the cylinder liner 64 is in turn arranged and supported in the housing 62 of the injection pump 61.
the lower end 75 of the pump piston 63 is connected to a piston 74, which is part of the air spring 58.
This air spring 58 has known compressed air supply lines and pressure limiting devices, which are not shown.
the piston rod 15 of the hydraulic unit 1 of the linear drive is articulated to the piston 74 of the compressed air spring 58.
the housing 62 of the injection pump 61 is fixed and rigidly connected to the cylinder 3 of the hydraulic unit 1. This ensures that movements of the piston rod 15 are transmitted without errors to the piston 74 and thus to the pump piston 63 of the injection pump 61.
the pump piston 63 of the injection pump 61 can be displaced in the direction of the longitudinal axis 76 of the injection pump, the end face 68 delimiting the cylinder space 65.
the lower end 67 of a valve body 66 projects into this cylinder space 65.
the valve body 66 has a valve seat 77, via which the cylinder space 65 is connected to the inlet bore 69 or the outlet bore 70 or is separated therefrom.
a bore 71 is arranged in the center of the valve body 66, via which pressure oil is guided from the cylinder space 65 to a pressure line 72.
This pressure line 72 is connected to an injection nozzle of an internal combustion engine and supplies this fuel under high pressure.
the amount of fuel which is pumped by the pump piston 63 and ejected into the pressure line 72 is metered volumetrically.
the end face 68 of the pump piston 63 abuts the lower end 67 of the valve body 66 and holds the valve seat 77 open in this position.
the position of the top dead center is thus precisely determined and remains the same in all operating states.
the position of the bottom dead center of the pump piston 63 is variable depending on the size of the desired fuel output volume, with the aid of the method of operation of the linear drive according to the invention described in FIG. 1.
FIG. 4 shows the device by means of which the camshaft 11 used as an active element can be connected to the actuator and the lifting movement of the cam 12 can be controlled.
a control element 80 is switched on between the cams 12 of the camshaft 11 and the end 56 of the actuator 7.
the control element 80 has a roller 81, which rests on the control surfaces of the camshaft 11 or the cam 12.
the end 56 of the actuator 7 rests on the opposite sliding surface 85 of the control element 80.
the control element 80 can be pivoted about the pivot point 84 and is supported in this pivot point 84 via a roller 83 in the bearing 82.
the control element 80 can be displaced transversely to the actuator axis 60 by means of a rod 86.
control element 80 In the position shown, the control element 80 is fully engaged in the operative position, and the deflection movement of the cam 12 on the camshaft 11 acts on the actuator 7 to the full extent. If the control element 80 is moved in the direction of arrow 87, the obliquely arranged part causes it the area 85 that the camshaft is decoupled from the end 56 of the actuator 7 when the element 80 is fully deflected. If the control element 80 is not completely disengaged or is moved in the hydraulic unit 1 in one of the two directions of the arrows 87 and 88 during the lifting process of the piston, there is a modulation of the piston movement, since the control piston 6 immediately reacts to the axial movements of the actuator 7 .
an earlier stroke movement can be generated, for example, by moving the control element 80 in the direction of the arrow 88, ie in the example shown against the cam rotation direction.
This advanced stroke movement can be caused by sudden movement of the Control element 80 in the direction of arrow 87 are interrupted during the movement.
the roller 81 is shifted with the control element 80 until it touches the base circle or a desired lower point on the camshaft 11 again.
An adjustable stop 89 is provided for the exact determination of the main stroke movement.
the control element 80 is moved to the stop 89, and the cam 12 can carry out the main stroke or residual stroke movement via the roller 81.
Modulations of the stroke movement of the piston 2 of the hydraulic unit 1 can also be obtained in the exemplary embodiments shown in the figures by actuating the other active elements of the actuator 9 if the camshaft 11 is not present or is not in operative connection.
the piston 10 shown in FIG. 1 can perform additional movements in the direction of the actuator axis 60 and thereby effect modulation movements of the control piston 6.
the corresponding control commands are fed to the actuator 9 via the electro-hydraulic control elements 33, which in turn are controlled by corresponding position controls. It is obvious that the device according to the invention shown allows movement modulations to a large extent. Nevertheless, the stroke movement of the piston 2 and its bottom dead center always remain precisely dimensionable and positionable.
an additional hydraulic control slide 95 is arranged parallel to the electro-hydraulic control element 33.
the control piston of this control slide 95 is provided with a switching element 98 which interacts with the control element 80 and the camshaft 11.
the control slide 95 is not shown in FIG Pressure medium lines are fed and controls the inflow of oil to the pressure medium outlets 96 and 97. These lines 96 and 97 lead into the cylinder bore 34 and act on one side of the piston 10 of the piston / cylinder unit 32. Because the mass of the control piston in the control slide 95 is very small is, the camshaft 11 can be made very small and thin. This means that all active forces can be reduced considerably and faster switching operations can be carried out.
the control element 33 and the control slide 95 are combined in a known manner in one assembly. In any case, the arrangement of the mechanical cam slide 11 outside the longitudinal axis 60 results in a reduction in the overall length.

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Engineering & Computer Science (AREA)
Physics & Mathematics (AREA)
Fluid Mechanics (AREA)
Mechanical Engineering (AREA)
General Engineering & Computer Science (AREA)
Transmission Devices (AREA)
Valve Device For Special Equipments (AREA)
Actuator (AREA)
Lubricants (AREA)
Mechanically-Actuated Valves (AREA)
Braking Systems And Boosters (AREA)
Fluid-Pressure Circuits (AREA)
Vehicle Body Suspensions (AREA)
Load-Engaging Elements For Cranes (AREA)

EP88908126A 1987-10-20 1988-09-27 Linearantrieb mit hydraulischer verstärkung Expired - Lifetime EP0338036B1 (de)

Priority Applications (1)

Application Number	Priority Date	Filing Date	Title
AT88908126T ATE74652T1 (de)	1987-10-20	1988-09-27	Linearantrieb mit hydraulischer verstaerkung.

Applications Claiming Priority (2)

Application Number	Priority Date	Filing Date	Title
CH4101/87		1987-10-20
CH410187		1987-10-20

Publications (2)

Publication Number	Publication Date
EP0338036A1 EP0338036A1 (de)	1989-10-25
EP0338036B1 true EP0338036B1 (de)	1992-04-08

Family

ID=4269844

Family Applications (1)

Application Number	Title	Priority Date	Filing Date
EP88908126A Expired - Lifetime EP0338036B1 (de)	1987-10-20	1988-09-27	Linearantrieb mit hydraulischer verstärkung

Country Status (10)

Country	Link
US (1)	US5056414A (pl)
EP (1)	EP0338036B1 (pl)
JP (1)	JPH0768961B2 (pl)
KR (1)	KR950009554B1 (pl)
CN (1)	CN1020786C (pl)
AT (1)	ATE74652T1 (pl)
DE (1)	DE3869949D1 (pl)
FI (1)	FI90279C (pl)
PL (1)	PL160607B1 (pl)
WO (1)	WO1989003939A1 (pl)

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DK170122B1 (da) *	1993-06-04	1995-05-29	Man B & W Diesel Gmbh	Stor totakts forbrændingsmotor
DK170121B1 (da) *	1993-06-04	1995-05-29	Man B & W Diesel Gmbh	Gliderventil og stor totakts forbrændingsmotor
US5592973A (en) *	1995-06-19	1997-01-14	Pope; Kenneth E.	Pressure capture valve
US6439101B1 (en) *	1999-10-13	2002-08-27	Teijin Seiki Co., Ltd.	Electro-hydraulic servomotor
DE10311493B4 (de) *	2003-03-15	2005-01-05	Man B & W Diesel A/S	Zweitakt-Dieselmotor
JP5548157B2 (ja) *	2011-03-30	2014-07-16	アズビル株式会社	パイロットリレー
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DE102012104927A1 (de) *	2012-06-06	2013-12-12	Emitec Gesellschaft Für Emissionstechnologie Mbh	Thermoelektrisches Modul und Verfahren zum Betrieb
CN107024381A (zh) *	2017-06-02	2017-08-08	西南交通大学	一种正弦位移激励加载装置及测试设备
JP6568613B1 (ja) *	2018-03-09	2019-08-28	株式会社ジャパンエンジンコーポレーション	注水ポンプ
CN116292813A (zh) *	2023-05-25	2023-06-23	哈尔滨船舶锅炉涡轮机研究所(中国船舶集团有限公司第七0三研究所)	一种串接式液压加载器

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- 1988-09-27 KR KR1019890701116A patent/KR950009554B1/ko not_active IP Right Cessation
- 1988-09-27 JP JP63507534A patent/JPH0768961B2/ja not_active Expired - Lifetime
- 1988-09-27 EP EP88908126A patent/EP0338036B1/de not_active Expired - Lifetime
- 1988-09-27 AT AT88908126T patent/ATE74652T1/de not_active IP Right Cessation
- 1988-09-27 WO PCT/CH1988/000174 patent/WO1989003939A1/de active IP Right Grant
- 1988-09-27 US US07/381,649 patent/US5056414A/en not_active Expired - Fee Related
- 1988-10-18 CN CN88107292A patent/CN1020786C/zh not_active Expired - Fee Related
- 1988-10-20 PL PL1988275399A patent/PL160607B1/pl unknown
1989
- 1989-05-31 FI FI892654A patent/FI90279C/fi not_active IP Right Cessation

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CN103410602B (zh) *	2013-08-26	2017-08-08	湖南天雁机械有限责任公司	电控液压执行器

Also Published As

Publication number	Publication date
EP0338036A1 (de)	1989-10-25
FI892654A (fi)	1989-05-31
CN1020786C (zh)	1993-05-19
PL160607B1 (pl)	1993-04-30
JPH0768961B2 (ja)	1995-07-26
PL275399A1 (en)	1989-05-02
KR890701903A (ko)	1989-12-22
WO1989003939A1 (en)	1989-05-05
FI90279C (fi)	1994-01-10
JPH02501847A (ja)	1990-06-21
CN1033310A (zh)	1989-06-07
FI892654A0 (fi)	1989-05-31
KR950009554B1 (ko)	1995-08-24
FI90279B (fi)	1993-09-30
DE3869949D1 (de)	1992-05-14
US5056414A (en)	1991-10-15
ATE74652T1 (de)	1992-04-15

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