EP1217209A2 - Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens - Google Patents
Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens Download PDFInfo
- Publication number
- EP1217209A2 EP1217209A2 EP01128052A EP01128052A EP1217209A2 EP 1217209 A2 EP1217209 A2 EP 1217209A2 EP 01128052 A EP01128052 A EP 01128052A EP 01128052 A EP01128052 A EP 01128052A EP 1217209 A2 EP1217209 A2 EP 1217209A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- piston
- spring
- return lever
- adjusting device
- Prior art date
- 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.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
Definitions
- the invention is based on an adjusting device the genus of the main claim.
- Adjustment devices that have an actuating piston, the on the displacement of a hydrostatic machine acts are known. By a pressure difference between two signal pressure chambers, each at one end Apply pressure to the actuating piston and steer the actuating piston from its neutral position and thus change that Displacement. From DE 195 40 654 C1 For example, a device is known in which the Deflection of the actuating piston via a feedback lever counteracting force generated.
- the position is supported by a swivel Depending on the direction of the deflection, return lever to one of transfer two rocker arms arranged opposite each other.
- the rocker arms are spring-loaded and thus generate one of the Deflection of the control piston opposing force.
- In the control piston is a recess for receiving the Rocker arm introduced by which the restoring force on the Control piston is transmitted.
- To generate a The pressure difference between the signal pressure chambers is the Control piston by a control pressure that in the Control pressure chambers on the front side of the control piston acts deflected and gives the flow path of one Supply pressure line to one of the two signal pressure chambers free.
- the adjustment device also has a centering valve and an attached switching valve. At a Pressure drop in both control lines under one through the Switching valve predetermined value is opened by opening a Relaxation line activates the centering valve. Thereby the higher pressure in the supply line to the Signal pressure chambers relieved until a pressure equilibrium is reached. The actuating piston is in its neutral position returned and the displacement of the hydrostatic machine is zero.
- the disadvantage of the specified adjustment device is high technical effort.
- a centering valve and a switching valve are required.
- the spool is on its opposite ends in the valve housing.
- the high pressures require precise processing, so no undesired leakage gaps due to component tolerances occur.
- the production of bores at right angles to each other in the valve housing and the corresponding sealing and Bearing areas on the control piston also increase the Production expense.
- control piston has no possibility Centering on.
- the installation dimension is due to the manufacturing dimensions of the components. Subsequent adjustment on fully assembled valve is not provided.
- the invention has for its object a Adjustment device to create a high Reliability guaranteed.
- the offset arrangement of the holes is advantageous Inclusion of the fasteners and the generated with it Preload with which the contact surface of the return lever the actuating piston is pressed.
- the through during operation additional forces are small compared to the Forces that act due to the preload, so that the Components only experience a quasi-static load.
- the Components are not moved relative to each other, so that over the lifespan does not consider an increase in one Movement play can occur.
- connection to the actuating piston can be done easily can be dismantled.
- the use of a Aid and one for producing the bias arranged dowel pin allows an inexpensive Assembly, including any disassembly that may be required is possible without component destruction, such as this would be necessary with a riveted joint.
- the independent setting option is equally advantageous the neutral position of the control valve by an in axial Direction of connection of the return lever to the Spring sleeve.
- the control valve and the control piston can brought into neutral position independently of each other and are only coupled to each other afterwards, by the return lever via a clamping device with the Spring sleeve is connected.
- the execution of the clamp connection in the form of a slit eye facilitates assembly because of a lockable hole in a housing a simple Access can be created.
- Fig. 1 shows schematically a first embodiment an adjusting device 1 according to the invention with a Control valve 2 and a control piston 3. With a fixed the actuating piston 3 connected return lever 4 is Control piston 3 with the control valve 2 mechanically in Operatively connected.
- Adjustment device 1 is described in more detail with reference to 1 first of all the construction of a first one Embodiment of an inventive Adjustment device 1 are explained in the neutral position.
- the adjusting piston 3 is with its two cylindrical ends in a first and second actuating pressure chamber recess 5a and 5b performed in a first and a second Signal pressure chamber housing 6a and 6b are introduced. That from the actuating piston 3 and the first and second Signal pressure chamber recess 5a and 5b formed volume forms the first and second signal pressure chambers 7a and 7b.
- the adjusting piston 3 has a recess 79 in which one first and second return springs 8a and 8b are arranged.
- the return springs 8a and 8b are in the form of spirals Compression springs run with their ends on a first and second spring bearings 9a and 9b arranged one inside the other.
- the actuating piston 3 has an end face a piston cover 10, which in the piston 3 screwed in and fixed by a locking ring.
- the force of the return springs 8a and 8b makes the first Spring bearing 9a against the bottom of the recess 79 of the Set piston 3 pressed, the opposite second Spring bearing 9b against the actuating piston cover 10.
- the spring bearings 9a and 9b each have a continuous, stepped receiving opening 82, in each one Spacer rods 11a and 11b protrude into the radial Level of the recess a corresponding enlargement have their radial extent.
- the spacer bars 11a and 11b penetrate the actuating piston 3 and Piston cover 10 and lie on one each Adjuster 12, the axial position of which with a Lock nut 14 fixed adjusting sleeve 13 is changeable.
- a cover cap 85 is placed on the adjusting sleeve 13 screwed. Due to the axial position of the adjuster 12 the relative neutral position of the control piston 3 with respect to those fixed in a common housing Signal pressure chamber housings 6a and 6b set.
- the housing is shown by the dash-dotted lines indicated.
- the spacer bars 11a and 11b are in the Actuating piston 3 and the actuating piston cover 10 in axial Slidable direction.
- the two spacer rods 11a and 11b both on the respective adjuster 12 and on the respective stage in the receiving opening 82 of the Spring bearing 9a or 9b, the spring bearing 9a and 9b simultaneously with the piston cover 10 and the bottom of the Recess 79 of the actuating piston 3 in contact.
- the control valve 2 has a control piston 17 on, which consists of a first spool part 18 and a second control piston part 19, which is in the axial direction are arranged sequentially and by one Piston tappets 20 are operatively connected to one another.
- the first control piston part 18 is on the one hand in one Control valve cover 22 and on the opposite side in a guide recess 25 of a control bush 23 guided.
- the control socket 23 is in one Control valve housing 24 screwed in and with a Lock nut 14 fixed.
- the control bushing 23 has at least three holes, each with a circumferential Channel 26a to 26c connected to the guide recess 25 is.
- Feed line 27 opens into a first rotating one Channel 26a out, a connecting line 28 into a second circumferential channel 26b and a third circumferential channel 26c is connected to a tank via a return line 29, e.g. formed by the inner volume of the housing is.
- the feed line 27 is by a not shown Device in every operating condition with hydraulic fluid depressed.
- the second control piston part 19 forms together with the Control bush 23 a throttle valve 47 and is in the Guide recess 25 of the control bush 23 guided and points two circumferential control grooves 30a and 30b, which are spaced in the axial direction so that the Part formed in between the control grooves 30a and 30b Neutral position of the throttle valve 23 to the middle circumferential channel 26b symmetrical bore closes.
- the axial extent of the control grooves 30a and 30b is so large that by axially moving the second control piston part 19 a connection between the Connection line 28 and the feed line 27 or between the connecting line 28 and the return line 29 can be produced.
- the second control piston part 19 projects with the first Spool part 18 facing away from the Guide recess 25 out in a spring space 86a Control bushing 23 and has a collar-shaped Extension 32 on which a centering spring 33 supported.
- the spring chamber 86a is not described in detail Way connected to the tank volume to equalize pressure to enable.
- the second end of the centering spring 33 supports down on an abutment 34, which is the front end one attached to the control bush 23
- Proportional magnet 31 forms.
- a sleeve 35 is arranged whose relative axial position is too the abutment 34 is adjustable, and as a limitation serves for an adjusting spring 36, the second end of which also supported on the collar-shaped extension 32.
- a Magnet plunger 37 performed a control force on the the front end of the second control piston part 19 transmits that are proportional to the electrical control signal and is generated by the proportional magnet 31.
- At the opposite end of the first Control piston part 18 is one Control device 38, the structure of the above Description of the second spool part 19 side equivalent.
- the collar-shaped extension 32 a disc 39 on the first control piston part 18, which is attached to a radial gradation of the first control piston part 18 is supported.
- first Spring seat body 40a and a second spring seat body 40b postponed On the first control piston part 18 are a first Spring seat body 40a and a second spring seat body 40b postponed.
- the two spring seat bodies 40a and 40b by one between the two spring seat bodies 40a and 40b arranged control spring 45 pushed apart until the first spring seat body 40a on one on the first Control piston part 18 fitted limiting sleeve 41 is present, for example, by a snap lock in a groove 87 of the first control piston part 18 against axial Moving is secured.
- the second spring seat body 40b is against the stop surface 42 by the control spring force pressed by a radial extension of the first Control piston part 18 is formed.
- the bottom 88 of the spring sleeve 43 and the stop disk 44 have central recesses that are larger than that radial dimensions of the stop surface 42 or Limit sleeve 41 and smaller than the largest radial Expansion of the spring seat body 40a and 40b are.
- the Spring sleeve 43 is against the spring force of the control spring 45 slidable relative to the first control piston part 18.
- the spring sleeve 43 has an approximately cylindrical Outer geometry and penetrates a clamping device 46, the at the end facing away from the actuating piston 3 Return lever 4 is arranged.
- Clamping device 46 is the return lever 4 on the Spring sleeve 43 slidably and thus the relative position of return lever 4 and spring sleeve 43 to each other adjustable.
- the clamping device 46 is in the illustrated embodiment as a slotted Eye running.
- the actuating piston 3 has for fastening the return lever 4 a mounting recess 49 in one Central piston part 50 e.g. is introduced by milling.
- the mounting recess 49 forms in the Central piston part 50 a first and a second Area 51 and 52.
- the first and second surfaces 51 and 52 are preferably oriented at right angles to one another and its surface normal is perpendicular to the central axis 53 the control piston 3.
- the return lever 4 has one with the first surface 51 corresponding contact surface 54 and one with the second Surface 52 corresponding mounting surface 55, the limit a return lever foot 56 on two sides.
- Attachment of the return lever 4 is the return lever foot 56 by means of dowel pins 57 and a fastening screw 58 the central piston part 50 fixed.
- the forces for the formation of the surface pressure are taken up by the dowel pins 57.
- the additional Fixing screw 58 is used for fixation. To their Recording is in the return lever foot 56 Through hole and in the central piston part 50 Thread introduced.
- the return lever foot 56 goes in the middle Return lever arm 59, whose central axis 60 is perpendicular to the contact surface 54 is oriented.
- a clamping device 46 slotted eye 63 arranged on that one Return lever foot 56 facing away from the end Return lever arm 59.
- the eye 63 has one corresponding to the outer geometry of the spring sleeve 43 Recess 61 on the one in the untensioned state has slightly greater radial expansion than that Spring sleeve 43.
- the central axis 62 of the recess 62 is parallel to the central axis 53 of the actuating piston 3.
- the movement of the control piston 17 lifts the Spring seat body 40a from the bottom 88 of the spring sleeve 43.
- the second spring seat body 40b is supported on the Stop disc 44 and lifts through the relative to the Spring sleeve 43 displacing control piston 17 from the Contact surface 42 from.
- the one between the two Spring seat bodies 40a and 40b build tensioned control spring 45 a counterforce against the control force of the deflecting proportional magnet 31 is directed until the Forces are in a new state of equilibrium.
- the opposite Spring bearing 9b is supported on the actuating piston cover 10.
- the compression of the return springs 8a and 8b causes one Restoring force on the control piston 3.
- Spacer bar 11a or 11b is required is one Compensating bore 89 introduced into the actuating piston 3, through a pressure equalization between the recess 79 of the Adjusting piston 3 and the interior of the housing takes place.
- the deflection of the control piston 3 is due to the rigid Connection of the return lever 4 to the spring sleeve 43 transfer.
- the direction of movement of the spring sleeve 43 is Deflection of the control piston 17 opposite.
- the relative position of the spring sleeve 43 to the control piston 3 changes in the same direction as described above relative movement of the control piston 3 by the control force of the proportional magnet 31.
- the control spring 45 is thereby further compressed and against the control force of the Proportional magnets 31 acting counterforce increases. With increasing travel of the control piston 3 is therefore the equilibrium position of the control piston 3 in the direction shifted to its neutral position.
- the throttle valve 47 is closed further.
- Closing the throttle valve 47 reduces the per unit time to the second Signal pressure chamber 7b replenished amount of hydraulic fluid, whereby the with increasing travel of the control piston 3 Movement of the adjusting piston 3 slows down.
- the movement of the Actuating piston 3 is ended when the control spring 45 generated force between the spring sleeve 43 and the Control piston 17 is so large that the resulting Counterforce on the magnetic plunger 37 of the same size Taxpayer is.
- the control piston 17 then moves through the centering springs 33 and adjusting spring 36 in its Neutral position and the throttle valve 47 is closed.
- the actuating piston 3 reaches the differential control signal proportional deflection without overshoot.
- the deflection takes place in the opposite direction reversed analog by a differential control signal Sign, wherein the first spool part 18 by the Proportional magnets 31 acted upon by an actuating force is that by the piston rod 20 to the second Control piston part 19 is transmitted.
- the tax groove 30 connects the connecting line 28 with the Return line 29 and so relaxes the second Signal pressure chamber 7b in the tank.
- the pressure in the first Signal pressure chamber 7a is larger than that in the second Signal pressure chamber 7b, so that the resulting actuating force Actuating piston 3 in the direction of the second actuating pressure chamber 7b deflects.
- the control piston 17 has a non-adjustable Total length that fluctuate due to manufacturing tolerances can. So that both proportional magnets 31 in their ideal Distance can be adjusted.
- the Proportional magnet 31 on the side of the first Control piston part 18 is for this purpose via a threaded connection connected to the control valve cover 22 and with a Fix lock nut 14.
- the position of the throttle valve-side proportional magnet 31, which with the Control bush 23 is connected, relative to the control piston 17 is relative to that by the position of the control bushing 23 Control housing 24 adjustable by a threaded connection.
- Balancing the spring forces for the neutral position is done by adjusting the relative position of the Sleeves 35 to the abutments 34, so that a through Setting the stroke range of the proportional magnets 31 changed spring tension of the centering springs 33 a compensating correction of the preload of the adjusting springs 36 can be achieved.
- the an influence on the neutral position of the throttle valve 47 can have the connection between the throttle valve-side proportional solenoids 31 and Control socket 23 can also be made adjustable.
- the two to each other have pointing ends of the spool parts 18 and 19 for this purpose recesses, the addition of the lengths of the Recesses is smaller than the length of the Piston tappet 20.
- At least one of the recesses is designed as a compensation receptacle 15 and has a radial Expansion that is large enough to accommodate the angular error and the offset of the central axes of the two control piston parts 18 and 19 to be able to compensate, without that between the two Spool parts 18 and 19 transverse forces are transmitted.
- FIG. 2 is a partial section through the first Embodiment along the line II-II of FIG. 1st shown, based on which the connection of the return lever 4 on the actuating piston 3 and the spring sleeve 43 in detail is explained.
- Eye 63 is a device for clamping the eye 63 appropriate.
- a radial enlargement 64 of the eye 63 is in the direction of the center M of the recess 61 Slot 65 arranged, the width B is greater than that Difference in the inner circumference of the untensioned eye 63 to the extent of the corresponding investment area of Spring sleeve 43 and the radial extension 64 in two Splits legs 66 and 67.
- the first leg 66 is one Threaded hole 68 introduced, the central axis of which is vertical is arranged to the slot 65.
- a through opening 69 is introduced, the central axis thereof in the untensioned state of the eye 63 with the central axis of the Threaded bore 68 is identical.
- a clamping surface 70 which is at least as large that the corresponding contact surface of a Screw head 71 of a clamping screw 72 completely rests.
- the radial extent of the through opening 69 is such that the deviation of the angle of the Central axis relative to the threaded bore 68 not to one Jamming of the clamping screw 72 leads.
- a removable Sealing plug 73 arranged in the extension of the Center axis of threaded hole 68.
- the clamping screw 72 easily accessible through the opening.
- first bores 74 are for receiving Dowel pins 57 as fasteners continuous first Bores 74 introduced, the central axis parallel to the Is contact surface 54, one of which it is preferred have constant first distance A.
- Central piston part 50 are to the first bores 74
- Corresponding second bores 75 introduced, one with the first bores 74 of identical diameter have and their central axes identical distances from each other in the direction of the central axis 53 of the actuating piston 3, like the central axes of the first bores 74.
- the central axes of the second bores 75 are perpendicular to the first surface 51 of the mounting recess 49 of the Oriented piston center part 50, of which it is one have a second distance a which is smaller than the first Distance A of the central axes of the first bores 74 from the Contact surface 54.
- dowel pins 57 By means of the in the first and second bores 74 and 75 introduced dowel pins 57 the contact surface of the return lever foot 56 against the first surface 51 of the mounting recess 49 of the Central piston part 50 pressed.
- the depth of the second bores 75 is so great that at fully sunk roll pin 57 between the bottom of the second bores 75 and the front end of the Dowel pin 57 has a free bore length, which is provided for receiving a disassembly aid.
- Fig. 2 is the dismantling aid a cylindrical Pin 76 with an internal thread 77.
- the outer diameter of the Pin 76 forms with the second bore 75 Match fit, so that to insert and remove the Pin 76 compared to the pressing in and out of Spring pin 75 negligible forces are required.
- the internal thread 77 has a diameter that is smaller is as the inner diameter of the dowel pins 57, so that for Disassembly of a puller, not shown, with is provided with an external thread, by means of the roll pin 57 inserted and screwed into the pin 76. Draft the pin 76 together with the roll pin 57 from the first and second holes 74 and 75 pulled out.
- the arrangement of the first and second bores 74 and 75 of the Interface between the return lever foot 56 and the Central piston part 50 is shown in FIG. 3.
- a first bore 74 is shown, the Central axis the first distance A from the contact surface 54 having.
- the first bore 74 is divided axially Direction to a first and a second section 78 and 80, the first section 78 being a larger one Has diameter than the second section 80 that to the Fastening surface 55 is oriented.
- the Bore diameter of the second section 80 is identical with the diameter of the second bores 75 in the Central piston part 50.
- the second bores 75 are as Blind holes executed and have a second distance a from the first surface 51 of the mounting recess 49 of the Adjusting piston 3, is smaller than the first distance A first bores 74.
- FIG. 4A A second embodiment is shown in Fig. 4A. Identically designed components are reused the introduced reference numerals corresponding to the above Description adopted. Unlike the first one Embodiments are the first and the second Legs 66 and 67 arranged off-center on the eye 63. The slot 65 runs parallel to the return lever arm 59. The distance of the clamping screw 58 to the opening in the Control valve housing 24 is thereby reduced and Accessibility improved.
- the second bore 75 in the central piston part 50 has again a greater length than to accommodate the Tension pin required, the length of the Bore 75 in a first and a second section 81 and 83 sections.
- the first section 81 has one with the Bore diameter of the first bore 74 in the Return lever foot 56 identical diameter on and corresponds in its axial extent with the Press-in depth of the dowel pin 57.
- the second Section 83 In the axial direction in the Central piston part 50 closes the second Section 83, which has a smaller diameter.
- the second section 83 of the second bore 75 is a Internal thread introduced.
- a Disassembly tools Before mounting the spring pin 57 is a Disassembly tools inserted into the second bore 75, which has an external thread.
- a disassembly aid for example, a grub screw 84 can be used, whose hexagon socket for screwing out a maximum has radial expansion that is less than that Inner diameter of the dowel pin 57.
- the grub screw 84 is not by a Tool shown from the central piston part 50th unscrewed.
- the roll pin 57 is located on the front side on the grub screw 84 and is thereby from the Bores 74 and 75 pressed out.
- the length of the Set screw 84 is preferably at least so large that the Roll pin 57 completely from the second bore 75 of the Central piston part 50 can be pressed out.
- Fig. 5 shows the interface of the actuating piston 3 and Return lever foot 56.
- the return lever 4 is the first Bore 74 introduced, the central axis of the first Distance A from the contact surface 54.
- the first Bore 74 divides in the axial direction in the first and the second section 78 and 80, the first Section 78 has a larger diameter than that second section 80 facing the mounting surface 55 is oriented.
- the bore diameter of the second Section 80 is identical to the diameter of the first Section 81 of the second holes 75 in the Central piston part 50.
- the second bores 75 are as Blind holes executed and the central axes have the second distance a from the first surface 51 of the Fastening recess 49 of the actuating piston 3, smaller is as the first distance A of the first bores 74.
- the Central axis with the central axis of the first section 81 of FIG second holes 75 is identical, the thread brought in.
- the radial extent of the maximum depth of the Threads is smaller than the radial extension of the first section 81 of second bore 75.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Servomotors (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
- Fig. 1
- einen schematischen Teilschnitt eines ersten Ausführungsbeispiels einer erfindungsgemäßen Verstellvorrichtung;
- Fig. 2
- einen schematischen Teilschnitt entlang der Linie II-II des ersten Ausführungsbeispiels der erfindungsgemäßen Verstellvorrichtung; und
- Fig. 3
- eine schematische Darstellung der Bauteilschnittstelle des ersten Ausführungsbeispiels im Ausschnitt III der Fig. 2;
- Fig. 4A
- einen schematischen Teilschnitt eines zweiten erfindungsgemäßen Ausführungsbeispiels entlang der Linie II-II der Fig. 1; und
- Fig. 4B
- eine schematische Darstellung des Ausführungsbeispiels aus Fig. 4A in teilweiser Demontage.
- Fig. 5
- eine schematische Darstellung der Bauteilschnittstelle des zweiten Ausführungsbeispiels im Ausschnit V der Fig. 4.
Claims (8)
- Verstellvorrichtung zum Verstellen eines zwischen zwei Stelldruckkammern angeordneten auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens (3), welcher aus einer durch die Kraft zumindest einer Rückstellfeder (8a, 8b) vorgegebenen Neutralstellung zwischen zwei Endlagen bewegbar ist, mit einem zur Regelung der Stelldrücke in den Stelldruckkammern (7a, 7b) vorgesehenen Steuerventil (2), mit einem Steuerkolben (17), der durch von Steuereinrichtungen (38) erzeugte Steuerkräfte in axialer Richtung aus einer Neutralstellung beidseitig auslenkbar ist, wobei den Steuerkräften jeweils eine mit der Auslenkung des Stellkolbens (3) korrelierte Gegenkraft entgegengerichtet ist,
dadurch gekennzeichnet, daß die Auslenkung des Stellkolbens (3) über einen starr mit dem Stellkolben (3) verbundenen Rückführhebel (4) als lineare Bewegung auf eine Federhülse (43) übertragbar ist, die über eine Steuerfeder (45) in Wirkverbindung steht. - Verstellvorrichtung nach Anspruch 1,
dadurch gekennzeichnet, daß der Rückführhebel (4) einen Rückführhebelfuß (56) mit einer Anlagefläche (54) aufweist, die mit einer parallel zu der Bewegungsrichtung des Stellkolbens (3). ausgebildeten ersten Fläche (51) einer Befestigungsausnehmung (49) des Stellkolbens (3) korrespondiert und
daß durch Befestigungselemente zwischen der ersten Fläche (51) der Befestigungsausnehmung (49) und der Anlagefläche (54) eine Flächenpressung ausgebildet ist, die größer ist als die durch die im Betriebsfall an dem Rückstellhebel (4) angreifenden Kräfte ausgebildete Flächenpressung. - Verstellvorrichtung nach Anspruch 2,
dadurch gekennzeichnet, daß die Befestigungselemente zumindest teilweise Spannstifte (57) sind, zu deren Aufnahmen erste Bohrungen (74) in den Rückführhebelfuß (56) und zweite korrespondierende Bohrungen (75) in den Stellkolben (3) eingebracht sind, wobei der Abstand der Mittelachsen der ersten Bohrungen (74) von der Anlagefläche (54) größer ist als der Abstand der Mittelachsen der zweiten Bohrungen (75) von der ersten Fläche (51) der Befestigungsausnehmung (49) des Stellkolbens (3). - Verstellvorrichtung nach Anspruch 3,
dadurch gekennzeichnet, daß in die zweiten Bohrungen (75) auf der dem Rückführhebel (4) abgewandten Seite jeweils ein Hilfsmittel (76,84) eingebracht ist, durch das der Spannstift (57) in Richtung des Rückstellhebels (4) aus der ersten und zweiten Bohrung (74, 75) herausdrückbar ist. - Verstellvorrichtung nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet, daß der Rückstellhebel (4) mit der Federhülse (43) durch eine Klemmverbindung (46) fest verbindbar ist. - Verstellvorrichtung nach Anspruch 5
dadurch gekennzeichnet, daß bei gelöster Klemmverbindung (46) die axiale Position der Federhülse (43) relativ zu dem Rückführhebel (4) einstellbar ist. - Verstellvorrichtung nach Anspruch 5,
dadurch gekennzeichnet, daß die Klemmvorrichtung (46) als ein geschlitztes Auge (63) ausgeführt ist, dessen innere radiale Ausdehnung mit der äußeren radialen Ausdehnung der Federhülse (43) korrespondiert. - Verstellvorrichtung nach einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß der Stellkolben (3) parallel zu dem Steuerkolben (17) angeordnet ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2000163526 DE10063526C1 (de) | 2000-12-20 | 2000-12-20 | Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens |
DE10063526 | 2000-12-20 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1217209A2 true EP1217209A2 (de) | 2002-06-26 |
EP1217209A3 EP1217209A3 (de) | 2003-12-03 |
EP1217209B1 EP1217209B1 (de) | 2007-06-06 |
Family
ID=7667955
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01128052A Expired - Lifetime EP1217209B1 (de) | 2000-12-20 | 2001-11-26 | Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1217209B1 (de) |
DE (2) | DE10063526C1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007017197A1 (de) * | 2005-08-09 | 2007-02-15 | Brueninghaus Hydromatik Gmbh | Regelventileinheit mit wechselanschlag |
WO2013045182A1 (de) * | 2011-09-29 | 2013-04-04 | Robert Bosch Gmbh | Ansteuergerät und verfahren zur montage eines ansteuergeräts |
CN103573573A (zh) * | 2012-08-04 | 2014-02-12 | 罗伯特·博世有限公司 | 静液压的轴向活塞式机器 |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011117543A1 (de) | 2011-11-03 | 2013-05-08 | Robert Bosch Gmbh | Axialkolbenmaschine |
DE102012214373A1 (de) | 2012-08-13 | 2014-05-15 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine |
DE102012214696A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Anker für eine Aktoreinrichtung |
DE102012214621A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | olrohr für eine Aktoreinrichtung |
DE102012214626A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Aktoreinrichtung und Axialkolbenmaschine |
DE102012214628A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Anker für eine Aktoreinrichtung |
DE102012214698A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Polrohr für eine Aktoreinrichtung |
DE102012214624A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Polrohr für eine Aktoreinrichtung |
DE102012214622A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Aktoreinrichtung und Axialkolbenmaschine |
DE102012214619A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Aktoreinrichtung und Axialkolbenmaschine |
DE102012214655A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Anker für eine Aktoreinrichtung |
DE102012214620A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Polrohr für eine Aktoreinrichtung |
DE102012214618A1 (de) | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Spule für eine Aktoreinrichtung |
DE102013205455A1 (de) | 2013-03-27 | 2014-10-02 | Robert Bosch Gmbh | Verfahren zur Positionserfassung mindestens eines Ankers |
DE102020201171A1 (de) | 2020-01-31 | 2021-08-05 | Inline Hydraulik Gmbh | Verstelleinrichtung für eine Hydromaschine, Hydromaschine |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19540654C1 (de) | 1995-10-31 | 1996-12-19 | Brueninghaus Hydromatik Gmbh | Verstellvorrichtung mit hydraulischer Zentriereinrichtung |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3429225A (en) * | 1966-06-09 | 1969-02-25 | Abex Corp | Electrohydraulic displacement control with mechanical feedback |
DE2913534A1 (de) * | 1979-04-04 | 1980-10-16 | Bosch Gmbh Robert | Einrichtung zur regelung des foerderstroms und zur begrenzung des foerderdrucks einer verstellbaren pumpe |
DE3232695C2 (de) * | 1982-09-02 | 1984-08-16 | Hydromatik GmbH, 7915 Elchingen | Leistungsregel-Vorrichtung für eine Hydropumpe |
JPH0751947B2 (ja) * | 1985-01-18 | 1995-06-05 | 石炭露天掘機械技術研究組合 | 液圧閉回路に介在された液圧ポンプの制御装置 |
-
2000
- 2000-12-20 DE DE2000163526 patent/DE10063526C1/de not_active Expired - Fee Related
-
2001
- 2001-11-26 EP EP01128052A patent/EP1217209B1/de not_active Expired - Lifetime
- 2001-11-26 DE DE50112594T patent/DE50112594D1/de not_active Expired - Lifetime
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19540654C1 (de) | 1995-10-31 | 1996-12-19 | Brueninghaus Hydromatik Gmbh | Verstellvorrichtung mit hydraulischer Zentriereinrichtung |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007017197A1 (de) * | 2005-08-09 | 2007-02-15 | Brueninghaus Hydromatik Gmbh | Regelventileinheit mit wechselanschlag |
CN101151464B (zh) * | 2005-08-09 | 2010-08-25 | 布鲁宁赫斯海诺马帝克有限公司 | 具有交替止动的控制阀单元 |
WO2013045182A1 (de) * | 2011-09-29 | 2013-04-04 | Robert Bosch Gmbh | Ansteuergerät und verfahren zur montage eines ansteuergeräts |
CN103573573A (zh) * | 2012-08-04 | 2014-02-12 | 罗伯特·博世有限公司 | 静液压的轴向活塞式机器 |
Also Published As
Publication number | Publication date |
---|---|
EP1217209B1 (de) | 2007-06-06 |
DE50112594D1 (de) | 2007-07-19 |
DE10063526C1 (de) | 2002-07-11 |
EP1217209A3 (de) | 2003-12-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE10063526C1 (de) | Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens | |
DE10063525B4 (de) | Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens | |
DE102008038455A1 (de) | Axialkolbenmaschine in Schrägscheibenbauweise mit einer Stellvorrichtung | |
DE102011111816B4 (de) | Vorrichtung mit Exzenter-Kolbenbolzen zur Erzielung eines variablen Verdichtungsverhältnisses in einem Hubkolbenmotor | |
DE4012524A1 (de) | Feststellvorrichtung fuer eine linearbewegungseinheit | |
EP1504191B1 (de) | Verstellvorrichtung für hydrostatische kolbenmaschinen | |
DE2625909A1 (de) | Fluidischer verstaerker | |
AT519652B1 (de) | Dichtungsvorrichtung und Hydraulikkolben mit Dichtungsvorrichtung | |
CH664194A5 (de) | Dieselmotor mit jedem zylinder zugeordneter einspritzpumpe. | |
EP0284634A1 (de) | Elektromechanisches Stellglied | |
DE2118604B2 (de) | Steuerventil zur einstellung eines arbeitsdrucks | |
DE4334395C2 (de) | Nocken-Umschaltmechanismus für Motoren | |
DE102004014293B4 (de) | Verstelleinheit | |
DE2361591A1 (de) | Schieberventil zur steuerung des arbeitsdrucks eines arbeitsmediums | |
EP1377732A1 (de) | Verbindung zwischen einem schaftende eines gaswechselventils einer brennkraftmaschine und einem hülsenförmigen stellkolben eines ventilstellers | |
WO1997018568A1 (de) | Hubmagnetanordnung | |
DE2508268C3 (de) | Steuerkolben fur hydraulische Druckmittelfolgesteuerungen, insbesondere für ein Lenkventil einer Servolenkeinrichtung von Fahrzeugen | |
DE102013206975A1 (de) | Hydraulische Steuervorrichtung mit einseitiger Schieberansteuerung | |
DE3132909A1 (de) | "ventilvorrichtung, insbesondere fuer druckgiessmaschinen | |
EP1306561A2 (de) | Druckmittelzylinder mit einer Einrichtung zur Verstellung des Kolbenhubs | |
DE3504268C2 (de) | ||
DE102010006988A1 (de) | Verstellvorrichtung für eine hydrostatische Kolbenmaschine | |
DE9115061U1 (de) | Magnetventil | |
DE2505126C3 (de) | Zweistufiges elektrohydraulisches Servoventil mit mechanischer Rückführung | |
WO2012130452A1 (de) | Einspritzventil |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A2 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
PUAL | Search report despatched |
Free format text: ORIGINAL CODE: 0009013 |
|
AK | Designated contracting states |
Kind code of ref document: A3 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR |
|
AX | Request for extension of the european patent |
Extension state: AL LT LV MK RO SI |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: 7F 04B 49/10 B Ipc: 7F 04B 49/00 B Ipc: 7F 04B 1/32 A Ipc: 7F 04B 49/08 B |
|
17P | Request for examination filed |
Effective date: 20040303 |
|
AKX | Designation fees paid |
Designated state(s): DE FR GB IT SE |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT SE |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20070606 |
|
REF | Corresponds to: |
Ref document number: 50112594 Country of ref document: DE Date of ref document: 20070719 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20080307 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20101130 Year of fee payment: 10 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20101123 Year of fee payment: 10 Ref country code: SE Payment date: 20101124 Year of fee payment: 10 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20111126 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20120731 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20111126 Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20111127 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20111130 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20121123 Year of fee payment: 12 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20131126 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20210126 Year of fee payment: 20 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R071 Ref document number: 50112594 Country of ref document: DE |