EP3443229B1 - Radial forging machine with hydraulic cylinder - Google Patents
Radial forging machine with hydraulic cylinder Download PDFInfo
- Publication number
- EP3443229B1 EP3443229B1 EP17715115.6A EP17715115A EP3443229B1 EP 3443229 B1 EP3443229 B1 EP 3443229B1 EP 17715115 A EP17715115 A EP 17715115A EP 3443229 B1 EP3443229 B1 EP 3443229B1
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- EP
- European Patent Office
- Prior art keywords
- machine according
- cylinder
- spaces
- fluid
- reshaping machine
- 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.)
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- 238000005242 forging Methods 0.000 title claims description 26
- 239000012530 fluid Substances 0.000 claims description 43
- 230000009471 action Effects 0.000 claims description 7
- 238000000926 separation method Methods 0.000 claims description 2
- 238000007493 shaping process Methods 0.000 claims description 2
- 238000009499 grossing Methods 0.000 claims 1
- 230000008901 benefit Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 238000003825 pressing Methods 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000004069 differentiation Effects 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
- B21J9/00—Forging presses
- B21J9/10—Drives for forging presses
- B21J9/12—Drives for forging presses operated by hydraulic or liquid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
- F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1428—Cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7055—Linear output members having more than two chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/75—Control of speed of the output member
-
- 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
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press
Definitions
- the invention relates to a forming machine according to claim 1.
- DE 198 46 348 A1 describes a forging press in which hydraulic cylinders are provided as drive units for forming tools. Such hydraulic cylinders allow both a large force and a large travel distance. The provision of these properties requires a correspondingly high delivery rate of a hydraulic pump.
- a hydraulic cylinder is generally understood to mean an actuator driven by a hydraulic, preferably liquid, fluid.
- the fluid is preferably a hydraulic oil, as is usually used in hydraulic cylinders.
- the cylinder of the hydraulic cylinder does not necessarily have a circular cross-section, so that the term "cylinder" in the present case relates to the function and not necessarily to a geometric shape.
- a circular cross-section of the cylinder is preferred.
- the cylinder can also have an elliptical cross-section. This would prevent the piston member from rotating in the cylinder.
- any transverse forces that may occur can be better absorbed.
- an active surface is a surface of the piston member on which the working pressure of the fluid can act in order to press the piston member in the active direction.
- the physical effective surface does not have to run flat and perpendicular to the effective direction, but only its projected portion perpendicular to the effective direction contributes to the driving force of the piston member.
- a cylinder space within the meaning of the invention is the entire space that the fluid fills in the cylinder depending on the position of the piston member.
- the entire cylinder space does not necessarily have to be under the working pressure of the fluid.
- one of the sub-spaces can also be pressure-free or essentially under atmospheric pressure. If necessary, both sub-spaces can also be under different working pressures. In the context of the invention, more than two sub-spaces that are hydraulically separated from one another can also be provided.
- a ratio of the sizes of the two partial areas can be adapted as required.
- a ratio in the range between 50:50 and 20:80 is appropriate for many applications.
- a ratio of the partial areas is asymmetrical and is between 45:55 and 20:80, particularly preferably between 40:60 and 20:80. This enables a targeted application of fluid to the subspaces, for example even during a forging process.
- a starting block is short and large in diameter. Heat loss is then low due to the surface-to-volume ratio. This means that in such a case, forging can be carried out with a low stroke frequency, but large pressing forces are required. If the starting block is reshaped to a final geometry in the course of forging, it cools down more quickly. This requires a higher stroke frequency, but the required pressing force is no longer so great because the pressed area becomes smaller.
- the subspaces run concentrically around a central axis of the cylinder.
- a particularly cylindrical step for separating the sub-spaces protrudes parallel to the direction of action on one of the two, piston member or cylinder.
- the one sub-space can form a fully cylindrical space which is surrounded by the second sub-space in the form of an annular cylinder, which is also arranged offset in the effective direction with respect to the first sub-space.
- the sub-spaces are connected to a hydraulic pump unit and a valve arrangement, the valve arrangement enabling fluid to be applied to the sub-spaces in at least two operating modes.
- most or all of the hydraulically switching components can thereby be arranged outside the hydraulic cylinder.
- the valve arrangement comprises a control valve with a pilot piston that can be displaced in the effective direction.
- pilot pistons as control valves are, for example, from the aforementioned DE 198 46 348 A1 known and allow a quick and precise control of the hydraulic cylinder.
- the pilot piston closes an outlet of the cylinder as it is advanced, which in turn leads to a pressure build-up and advance of the piston member.
- one of the sub-spaces can be connectable to a hydraulic reservoir through the valve arrangement.
- the hydraulic reservoir is pressureless. This ensures filling and emptying of the subchamber not acted upon by working pressure in the course of the piston movement, so that the second subchamber can be quickly charged with fluid under working pressure at any time.
- freedom from pressure in the hydraulic reservoir means that either atmospheric pressure or a higher pressure is present in the reservoir in order to ensure rapid fluid exchange.
- the hydraulic reservoir can in particular be designed as a pressure accumulator in the form of a hydraulic accumulator.
- the accumulator can be implemented, for example, as a spring accumulator or in some other way. In principle, however, it is also possible for the hydraulic reservoir to be pressurized if this is necessary.
- At least one of the partial spaces can be acted upon by the fluid by means of a valve arranged downstream of the partial space.
- the valve When the valve is open, the fluid then flows through the subchamber or a branch without pressure, and when the valve is closed or throttled, the respective subchamber is correspondingly pressurized.
- the hydraulic cylinder It is generally advantageous for the hydraulic cylinder to have a restoring active surface, the piston member being resettable against the direction of action by acting on the restoring active surface with the fluid. This allows a simple hydraulic return of the piston member.
- the provision can also be implemented in other ways, depending on the requirements.
- the present invention shows considerable advantages in the case of large hydraulic cylinders, since there is considerable effort involved in providing the hydraulic pumps and the electrical supply. Accordingly, it is advantageously provided that the entire effective area of the piston member is at least 1000 cm 2 , in particular at least 2000 cm 2 .
- the working pressures of the fluid are chosen conventionally and are typically in the range between 200 and 500 bar.
- Preferred maximum forces of the piston member are more than 3 MN, preferably between 5 and 30 MN or more.
- three or more hydraulically separable sub-spaces are provided with their respective associated sub-surfaces of the piston member. This allows a further differentiation of the pressing forces and stroke speeds of the piston member.
- the subspaces can each run concentrically to one another. A separation of the subspaces can take place in a similar way to designs with only two subspaces by means of corresponding gradations on the piston member and / or cylinder.
- the invention relates to a forming machine for shaping a workpiece, the forming machine being designed as a radial forging machine, and wherein a tool of the radial forging machine can be subjected to a forming force by means of a hydraulic cylinder as defined in claim 1.
- the forming force is exerted by several hydraulic cylinders so that no additional mechanical power transmission, such as a shaft, is required.
- Such a design of the forming machine is particularly favored by the flexibility of the hydraulic cylinder defined in claim 1.
- the forming machine is designed as a radial forging machine.
- the radial forging machine particularly preferably comprises at least four tools that work against one another in pairs.
- the workpiece in a first operating mode, is finished while only one of the subspaces is exposed to fluid under working pressure, whereas in a second operating mode of the forming machine, the workpiece is forged while both subspaces are exposed to fluid under working pressure. This allows the same forming machine to be used effectively for different forming processes.
- a hydraulic cylinder as defined in claim 1 can be designed as a replacement for a conventional hydraulic cylinder in existing forming machines.
- a variable ratio of the partial areas enables the greatest possible flexibility with regard to achievable stroke rates, which is particularly advantageous when forming temperature-critical materials.
- By dividing the partial areas in combination with suitable forging strategies it is possible to reduce the installed power and thus save energy while at the same time achieving comparable productivity. It is also advantageous that the partial areas can also be divided up for existing systems.
- the advantage of saving energy is even greater when using an energy storage device, for example in the form of a flywheel, which stores energy when idling and releases it when required.
- the invention can be used independently of the forging strategy. For example, it is possible to use a conventional strategy such as that used in open die forging, which is characterized by a large feed rate without rotating the workpiece, but using four tools that act on the workpiece at the same time. When using this forging strategy, high numbers of strokes can be easily achieved. When using the invention in combination with a strategy in which two opposing tools of a radial forging machine act on the workpiece, high Stroke numbers can be realized in connection with a further optimized core forging.
- productivity can be increased again.
- the in Fig. 1 The hydraulic cylinder 1 shown comprises a cylinder 2 in which a piston member is guided so as to be linearly displaceable along an effective direction W.
- the piston member 3 has a cylindrical step 3 a, which protrudes into a corresponding step of the cylinder 2. This hydraulically creates a first sub-space 4 is defined over a first partial surface 5 of an active surface of the piston member 3.
- the first subspace essentially has the shape of a full cylinder.
- the first subchamber 4 is hydraulically separated by the step 3a from a second subchamber 6 over a second subarea 7 of the active area of the piston member 3.
- the second sub-space 6 essentially has the shape of an annular cylinder.
- the partial spaces 4, 6 together form a cylinder space of the cylinder 2.
- the effective area of the piston member 3 is the sum of the partial areas 5, 7.
- the size of the partial spaces 4, 6 varies depending on the current position of the piston member 3 in the cylinder 2.
- Each of the sub-spaces 4, 6 has a respective opening 4a, 6a through which a hydraulic fluid can flow into the sub-space 4, 6.
- the openings 4a, 6a are connected via hydraulic lines 8 to a valve arrangement 9 and a hydraulic pump unit (not shown).
- a direction of flow of the fluid when working pressure is applied by the pump unit is shown as arrow P.
- the sub-spaces 4, 6 are hydraulically separated from one another according to the above explanations, but can be hydraulically connected to one another depending on the design of the valve arrangement 9 if necessary.
- the valve arrangement 9 starting from the pump unit, comprises a first branch 10, a first valve 11 downstream of it and a second branch 12 downstream of it the fluid is acted upon under working pressure.
- the second branch 12 leads on the one hand to the second subchamber 6 and on the other hand to a reservoir 13, which is through a second valve 14 between the second branch 12 and the reservoir 13 can be shut off.
- the reservoir is filled with fluid at essentially atmospheric pressure.
- a drain 15 of the first subchamber 4 leads back to a sump and / or an intake side of the pump unit.
- the outlet 15 can be controllably closed by a pilot piston 16 that is drivably displaceable in the effective direction W, so that the pilot piston 16 forms a control valve of the valve arrangement 9 with the outlet 15.
- the position of the piston member 3 in the effective direction is set via the pilot piston 16.
- the pilot piston 16 is also hydraulically driven in the present case, but can also have an electric motor or some other drive, depending on the requirements.
- a significantly smaller, restoring force is also applied to the piston member 3 via a restoring active surface 17 in a restoring space 18.
- the restoring active surface 17 is also acted upon by fluid under working pressure. In contrast to the two sub-spaces, the working pressure of the fluid does not act in the effective direction, but in the opposite direction.
- the invention now works as follows: In a first operating mode, the first valve 10 is closed and the second valve 14 is open. As a result, only the first subchamber 4 is supplied with fluid under working pressure from the pump unit. the second subchamber is connected to the reservoir 13 via the second valve. This ensures a constant filling with fluid under atmospheric pressure or a slightly higher pressure to improve a flow rate.
- the first valve 10 is open and the second valve 14 is closed.
- the reservoir 13 is no longer connected to the cylinder 2, and the two sub-spaces 4, 6 are hydraulically connected in parallel.
- a simplified valve arrangement 9 without a pilot piston 16 is selected.
- Components with the same function are provided with the same reference symbols as in the first example.
- the piston member 3 is shown hatched in the schematic drawing.
- a cylindrical, protruding step 2a is formed in this example as part of the cylinder 2, so that the piston member essentially has the shape of a cup. This choice of shape is independent of the design of the valve arrangement 9.
- valve arrangement 9 has a first branch 19 which leads to the first subchamber 4.
- a valve 20 is arranged downstream of the branch 19.
- the second subchamber 6 and the restoring chamber 18 are charged directly with fluid and have drains 21, 22.
- Valves 23, 24 are arranged behind the drains 21, 22, respectively.
- one of the sub-spaces 4, 6 or the reset space 18 is acted upon with fluid under working pressure precisely when the valve 20, 23, 24 assigned to it is closed.
- the respective valve 20, 23, 24 is opened, the fluid flows in a circle without pressure build-up. Accordingly, the three feeds P are each connected separately to carry pressure and are not connected in parallel to one another. This can be achieved, for example, by using separate hydraulic pumps.
- the modes of operation of the hydraulic cylinder according to the second example are completely analogous to those of the first example.
- a hydraulic cylinder 1 according to one of the types described above is designed as part of a forming machine in the form of a radial forging press (not shown).
- the working pressure of the fluid is around 400 bar.
- the size ratio of the two partial areas 5, 7 is approximately 50:50.
- the forming machine comprises four tools working in pairs against one another in a cross shape, each of the tools being driven by a hydraulic cylinder 1 described above.
- a switch is made between the operating modes in order to move the tools quickly over longer distances while no forming takes place. This can take place, for example, in the course of a workpiece feed and allows the forging process to be accelerated overall.
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- Forging (AREA)
Description
Die Erfindung betrifft eine Umformmaschine nach dem Anspruch 1.
Es ist die Aufgabe der Erfindung, eine Radialschmiedemaschine mit einem Hydraulikzylinder auszustatten, der hohe Kräfte und große Stellwege mit niedriger Antriebsleistung kombiniert.It is the object of the invention to equip a radial forging machine with a hydraulic cylinder that combines high forces and large travel ranges with low drive power.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved according to the invention with the features of
Durch das Aufteilen der Wirkfläche bzw. des hydraulisch beaufschlagbaren Volumens in zumindest zwei Teilräume kann eine je nach Anforderungen verschiedene Ansteuerung realisiert werden. Zum Beispiel kann bei gleicher Zuführleistung des Fluids entweder ein schneller Vorschub des Kolbens bei geringer Arbeitskraft oder ein langsamer Vorschub bei hoher Arbeitskraft gewählt werden. Insgesamt erlaubt dies die Optimierung der Anwendungen des Hydraulikzylinders bezüglich einer Minimierung der Antriebsleistung. Solche Hydraulikzylinder, wobei das hydraulisch beaufschlagbare Volumen in zwei Teilräume aufgeteilt ist, sind im Stand der Technik bekannt, wie zum Beispiel im Dokument
Unter einem Hydraulikzylinder wird im Sinne der Erfindung allgemein ein mit einem hydraulischen, bevorzugt flüssigen Fluid angetriebenes Stellglied verstanden. Das Fluid ist bevorzugt ein Hydrauliköl, wie es üblicherweise bei Hydraulikzylinder zum Einsatz kommt. Der Zylinder des Hydraulikzylinders ist im Sinne der Erfindung nicht notwendig von kreisförmigem Querschnitt, so dass sich der Begriff "Zylinder" vorliegend auf die Funktion und nicht notwendig auf eine geometrische Form bezieht. Entsprechend der überwiegenden Praxis des Baus von Hydraulikzylindern wird aber ein kreisförmiger Querschnitt des Zylinders bevorzugt gewählt. Bei einer möglichen Alternative kann der Zylinder auch einen ellipsenförmigen Querschnitt aufweisen. Dies würde ein Verdrehen des Kolbenglieds im Zylinder verhindern. Zudem können gegebenenfalls auftretende Querkräfte besser aufgefangen werden.In the context of the invention, a hydraulic cylinder is generally understood to mean an actuator driven by a hydraulic, preferably liquid, fluid. The fluid is preferably a hydraulic oil, as is usually used in hydraulic cylinders. In the context of the invention, the cylinder of the hydraulic cylinder does not necessarily have a circular cross-section, so that the term "cylinder" in the present case relates to the function and not necessarily to a geometric shape. In accordance with the prevailing practice of building hydraulic cylinders, however, a circular cross-section of the cylinder is preferred. In a possible alternative, the cylinder can also have an elliptical cross-section. This would prevent the piston member from rotating in the cylinder. In addition, any transverse forces that may occur can be better absorbed.
Eine Wirkfläche ist im Sinne der Erfindung eine Oberfläche des Kolbenglieds, auf die der Arbeitsdruck des Fluids wirken kann, um das Kolbenglied in die Wirkrichtung zu drücken. Die körperliche Wirkfläche muss nicht eben und senkrecht zu der Wirkrichtung verlaufen, wobei aber nur ihr projizierter Anteil senkrecht zu der Wirkrichtung zu der Antriebskraft des Kolbenglieds beiträgt.In the context of the invention, an active surface is a surface of the piston member on which the working pressure of the fluid can act in order to press the piston member in the active direction. The physical effective surface does not have to run flat and perpendicular to the effective direction, but only its projected portion perpendicular to the effective direction contributes to the driving force of the piston member.
Ein Zylinderraum im Sinne der Erfindung ist der gesamte Raum, den das Fluid in dem Zylinder je nach Stellung des Kolbenglieds ausfüllt.A cylinder space within the meaning of the invention is the entire space that the fluid fills in the cylinder depending on the position of the piston member.
Gemäß der erfindungsgemäßen Aufteilung des Zylinderraums in zwei hydraulisch voneinander trennbare Teilräume muss nicht notwendig der gesamte Zylinderraum unter dem Arbeitsdruck des Fluid stehen. Es kann auch je nach Betriebsart einer der Teilräume druckfrei sein bzw. im Wesentlichen unter Atmosphärendruck stehen. Bei Bedarf können auch beide Teilräume unter verschiedenen Arbeitsdrücken stehen. Im Sinne der Erfindung können auch mehr als zwei hydraulisch voneinander getrennte Teilräume vorgesehen sein.According to the inventive division of the cylinder space into two hydraulically separable partial spaces, the entire cylinder space does not necessarily have to be under the working pressure of the fluid. Depending on the operating mode, one of the sub-spaces can also be pressure-free or essentially under atmospheric pressure. If necessary, both sub-spaces can also be under different working pressures. In the context of the invention, more than two sub-spaces that are hydraulically separated from one another can also be provided.
Ein Verhältnis der Größen der beiden Teilflächen kann je nach Bedarf angepasst sein. Ein Verhältnis im Bereich zwischen 50:50 und 20:80 ist für viele Anwendungen zweckmäßig. Bei einem asymmetrischen Verhältnis der Teilflächengrößen von z.B. 30:70 ergibt sich die Möglichkeit einer mehrfachen Abstufung einer Kraftbeaufschlagung, also z.B. 30%, 70% und 100% einer Maximalkraft je nach Beaufschlagung der Teilräume mit Fluid.A ratio of the sizes of the two partial areas can be adapted as required. A ratio in the range between 50:50 and 20:80 is appropriate for many applications. With an asymmetrical ratio of the partial area sizes of, for example, 30:70, there is the possibility of multiple gradations of force application, for example 30%, 70% and 100% of a maximum force depending on the application of fluid to the partial areas.
Bei einer bevorzugten Detailgestaltung ist ein Verhältnis der Teilflächen asymmetrisch und beträgt zwischen 45:55 und 20:80, besonders bevorzugt zwischen 40:60 und 20:80. Dies ermöglicht eine gezielte Beaufschlagung der Teilräume mit Fluid zum Beispiel auch während eines Schmiedevorgangs. So ist zu Beginn eines Schmiedevorgangs ein Ausgangsblock kurz und groß im Durchmesser. Ein Wärmeverlust ist dann gering, aufgrund des Oberflächen-Volumen-Verhältnisses. Das heißt, in einem solchen Fall kann mit einer geringen Hubfrequenz geschmiedet werden, wobei aber große Presskräfte benötigt werden. Wenn im Laufe des Schmiedens der Ausgangsblock auf eine Endgeometrie umgeformt wird, kühlt dieser schneller aus. Das erfordert eine höhere Hubfrequenz, wobei die erforderliche Presskraft aber nicht mehr so groß ist, da die gedrückte Fläche kleiner wird.In a preferred detailed design, a ratio of the partial areas is asymmetrical and is between 45:55 and 20:80, particularly preferably between 40:60 and 20:80. This enables a targeted application of fluid to the subspaces, for example even during a forging process. At the beginning of a forging process, for example, a starting block is short and large in diameter. Heat loss is then low due to the surface-to-volume ratio. This means that in such a case, forging can be carried out with a low stroke frequency, but large pressing forces are required. If the starting block is reshaped to a final geometry in the course of forging, it cools down more quickly. This requires a higher stroke frequency, but the required pressing force is no longer so great because the pressed area becomes smaller.
Im Interesse einer einfachen baulichen Realisierung kann es vorgesehen sein, dass die Teilräume konzentrisch um eine Mittelachse des Zylinders verlaufen. Bei einer besonders zweckmäßigen Detailgestaltung ragt dabei an einem von beiden, Kolbenglied oder Zylinder, eine insbesondere zylindrische Stufe zur Trennung der Teilräume parallel zu der Wirkrichtung vor. Auf diese Weise kann zum Beispiel der eine Teilraum einen vollzylindrischen Raum ausbilden, der von dem zweiten Teilraum in Form eines Ringzylinders umgeben ist, welcher zudem in der Wirkrichtung versetzt zu dem ersten Teilraum angeordnet ist.In the interest of a simple structural implementation, it can be provided that the subspaces run concentrically around a central axis of the cylinder. In a particularly expedient detail design, a particularly cylindrical step for separating the sub-spaces protrudes parallel to the direction of action on one of the two, piston member or cylinder. In this way, for example, the one sub-space can form a fully cylindrical space which is surrounded by the second sub-space in the form of an annular cylinder, which is also arranged offset in the effective direction with respect to the first sub-space.
Allgemein vorteilhaft ist es vorgesehen, dass die Teilräume mit einer hydraulischen Pumpeinheit und einer Ventilanordnung verbunden sind, wobei die Ventilanordnung eine Fluidbeaufschlagung der Teilräume in mindestens zwei Betriebsarten ermöglicht. Insbesondere können hierdurch die meisten oder auch sämtliche hydraulisch schaltenden Bauteile außerhalb des Hydraulikzylinders angeordnet sein.It is generally advantageously provided that the sub-spaces are connected to a hydraulic pump unit and a valve arrangement, the valve arrangement enabling fluid to be applied to the sub-spaces in at least two operating modes. In particular, most or all of the hydraulically switching components can thereby be arranged outside the hydraulic cylinder.
In einer bevorzugten Ausführungsform liegt in einer ersten der Betriebsarten ein schneller Vorschub des Kolbenglieds bei verringerter Kolbenkraft vor, wobei in einer zweiten der Betriebsarten ein langsamer Vorschub des Kolbenglieds bei hoher Kolbenkraft vorliegt, und wobei die Betriebsarten durch unterschiedliche Beaufschlagung der Teilräume mit Fluid unter Arbeitsdruck realisiert werden.In a preferred embodiment, in a first of the operating modes there is a rapid advance of the piston member with reduced piston force, in a second of the operating modes there is a slow advance of the piston member with high piston force, and in which the operating modes are implemented by differently applying fluid to the subspaces under working pressure will.
Bei einer besonders bevorzugten Ausführungsform ist es vorgesehen, dass die Ventilanordnung ein Steuerventil mit einem in der Wirkrichtung verschiebbaren Pilotkolben umfasst. Solche Pilotkolben als Steuerventile sind zum Beispiel aus der eingangs genannten
Zur einfachen Realisierung einer geringeren Pumpleistung kann einer der Teilräume durch die Ventilanordnung mit einem Hydraulikreservoir verbindbar sein. Bei einer möglichen Ausführungsform ist das Hydraulikreservoir dabei druckfrei. Dies stellt ein Befüllen und Entleeren des nicht mit Arbeitsdruck beaufschlagten Teilraums im Zuge der Kolbenbewegung sicher, so dass jederzeit ein schnelles Beaufschlagen des zweiten Teilraums mit Fluid unter Arbeitsdruck ermöglicht ist. Eine Druckfreiheit des Hydraulikreservoirs bedeutet im Sinne der Erfindung, dass entweder atmosphärischer Druck oder auch ein höherer Druck in dem Reservoir anliegt, um einen schnellen Fluidaustausch zu gewährleisten. Eine Verbindung zu dem hohen Druck einer Hydraulikpumpe besteht jedoch nicht. Das Hydraulikreservoir kann insbesondere als ein Druckspeicher in Form eines hydraulischen Akkumulators ausgebildet sein. Der Akkumulator kann zum Beispiel als Federspeicher oder auf andere Weise realisiert sein. Grundsätzlich ist aber auch möglich, dass das Hydraulikreservoir mit Druck beaufschlagt ist, sofern dies erforderlich ist.For the simple implementation of a lower pumping capacity, one of the sub-spaces can be connectable to a hydraulic reservoir through the valve arrangement. In one possible embodiment, the hydraulic reservoir is pressureless. This ensures filling and emptying of the subchamber not acted upon by working pressure in the course of the piston movement, so that the second subchamber can be quickly charged with fluid under working pressure at any time. In the context of the invention, freedom from pressure in the hydraulic reservoir means that either atmospheric pressure or a higher pressure is present in the reservoir in order to ensure rapid fluid exchange. However, there is no connection to the high pressure of a hydraulic pump. The hydraulic reservoir can in particular be designed as a pressure accumulator in the form of a hydraulic accumulator. The accumulator can be implemented, for example, as a spring accumulator or in some other way. In principle, however, it is also possible for the hydraulic reservoir to be pressurized if this is necessary.
Bei einer weiteren Ausführungsform der Erfindung ist zumindest einer der Teilräume, bevorzugt beide Teilräume, mittels eines stromabwärts des Teilraums angeordneten Ventils mit dem Fluid beaufschlagbar. Bei offenem Ventil strömt das Fluid dann druckfrei durch den Teilraum oder einen Abzweig, und bei geschlossenem oder gedrosseltem Ventil erfolgt eine entsprechende Druckbeaufschlagung des jeweiligen Teilraums.In a further embodiment of the invention, at least one of the partial spaces, preferably both partial spaces, can be acted upon by the fluid by means of a valve arranged downstream of the partial space. When the valve is open, the fluid then flows through the subchamber or a branch without pressure, and when the valve is closed or throttled, the respective subchamber is correspondingly pressurized.
Allgemein vorteilhaft hat der Hydraulikzylinder eine rückstellende Wirkfläche, wobei das Kolbenglied durch Beaufschlagung der rückstellenden Wirkfläche mit dem Fluid entgegen der Wirkrichtung rückstellbar ist. Dies erlaubt eine einfache hydraulische Rückstellung des Kolbenglieds. Die Rückstellung kann je nach Anforderungen aber auch auf andere Weise realisiert sein.It is generally advantageous for the hydraulic cylinder to have a restoring active surface, the piston member being resettable against the direction of action by acting on the restoring active surface with the fluid. This allows a simple hydraulic return of the piston member. The provision can also be implemented in other ways, depending on the requirements.
Die vorliegende Erfindung zeigt erhebliche Vorteile bei großen Hydraulikzylindern, da hier erheblicher Aufwand in die Bereitstellung der hydraulischen Pumpen und der elektrischen Versorgung anfällt. Entsprechend ist es vorteilhaft vorgesehen, dass die gesamte Wirkfläche des Kolbenglieds wenigstens 1000 cm2, insbesondere wenigstens 2000 cm2, beträgt. Die Arbeitsdrücke des Fluids werden dabei herkömmlich gewählt und liegen typisch im Bereich zwischen 200 und 500 bar. Bevorzugte Maximalkräfte des Kolbenglieds betragen mehr als 3 MN, bevorzugt zwischen 5 und 30 MN oder darüber.The present invention shows considerable advantages in the case of large hydraulic cylinders, since there is considerable effort involved in providing the hydraulic pumps and the electrical supply. Accordingly, it is advantageously provided that the entire effective area of the piston member is at least 1000 cm 2 , in particular at least 2000 cm 2 . The working pressures of the fluid are chosen conventionally and are typically in the range between 200 and 500 bar. Preferred maximum forces of the piston member are more than 3 MN, preferably between 5 and 30 MN or more.
Bei einer möglichen Weiterbildung der Erfindung ist es vorgesehen, dass drei oder mehr hydraulisch voneinander trennbare Teilräume mit ihren jeweils zugeordneten Teilflächen des Kolbenglieds vorgesehen sind. Dies erlaubt eine noch weitere Differenzierung der Presskräfte und Hubgeschwindigkeiten des Kolbenglieds. Die Teilräume können insbesondere jeweils konzentrisch zueinander verlaufen. Eine Trennung der Teilräume kann analog zu Ausführungen mit nur zwei Teilräumen mittels entsprechender Abstufungen an Kolbenglied und/oder Zylinder erfolgen.In a possible development of the invention it is provided that three or more hydraulically separable sub-spaces are provided with their respective associated sub-surfaces of the piston member. This allows a further differentiation of the pressing forces and stroke speeds of the piston member. In particular, the subspaces can each run concentrically to one another. A separation of the subspaces can take place in a similar way to designs with only two subspaces by means of corresponding gradations on the piston member and / or cylinder.
Die Erfindung betrifft eine Umformmaschine zur Formgebung eines Werkstücks, wobei die Umformmaschine als Radialschmiedemaschine ausgebildet ist, und wobei ein Werkzeug der Radialschmiedemaschine mittels eines Hydraulikzylinders wie im Anspruch 1 definiert mit einer Umformkraft beaufschlagbar ist.The invention relates to a forming machine for shaping a workpiece, the forming machine being designed as a radial forging machine, and wherein a tool of the radial forging machine can be subjected to a forming force by means of a hydraulic cylinder as defined in
Die Umformkraft wird durch mehrere Hydraulikzylinder ausgeübt, so dass keine zusätzliche mechanische Kraftübertragung wie etwa durch eine Welle erforderlich ist. Eine solche Auslegung der Umformmaschine ist durch die Flexibilität des im Anspruch 1 definierten Hydraulikzylinders besonders begünstigt.The forming force is exerted by several hydraulic cylinders so that no additional mechanical power transmission, such as a shaft, is required. Such a design of the forming machine is particularly favored by the flexibility of the hydraulic cylinder defined in
Erfindungsgemäß ist die Umformmaschine als Radialschmiedemaschine ausgebildet. Besonders bevorzugt umfasst die Radialschmiedemaschine wenigstens vier paarweise gegeneinander arbeitende Werkzeuge.According to the invention, the forming machine is designed as a radial forging machine. The radial forging machine particularly preferably comprises at least four tools that work against one another in pairs.
Allgemein vorteilhaft erfolgt in einer ersten Betriebsart ein Schlichten des Werkstücks unter Beaufschlagung nur eines des Teilräume mit Fluid unter Arbeitsdruck, wobei in einer zweiten Betriebsart der Umformmaschine ein Schmieden des Werkstücks unter Beaufschlagung beider Teilräume mit Fluid unter Arbeitsdruck erfolgt. Dies erlaubt einen effektiven Einsatz derselben Umformmaschine für verschiedene Formgebungsverfahren.Generally advantageously, in a first operating mode, the workpiece is finished while only one of the subspaces is exposed to fluid under working pressure, whereas in a second operating mode of the forming machine, the workpiece is forged while both subspaces are exposed to fluid under working pressure. This allows the same forming machine to be used effectively for different forming processes.
Weiterhin vorteilhaft erfolgt in einer Betriebsart der Umformmaschine eine schnelle Positionierung des Kolbenglieds unter Beaufschlagung nur eines des Teilräume mit Fluid unter Arbeitsdruck, wobei nach der Positionierung ein Umformen des Werkstücks unter Beaufschlagung beider Teilräume mit Fluid unter Arbeitsdruck erfolgt. Dies erlaubt eine verringerte Leistung einer hydraulischen Versorgungseinheit bei ansonsten gleichen Leistungsdaten bezüglich Geschwindigkeit und Maximalkraft der Umformmaschine.Furthermore, in one mode of operation of the forming machine, rapid positioning of the piston member takes place advantageously under the action of only one of the subspaces with fluid under working pressure, with a forming of the after the positioning Workpiece takes place with the application of both subspaces with fluid under working pressure. This allows a reduced performance of a hydraulic supply unit with otherwise the same performance data with regard to the speed and maximum force of the forming machine.
Allgemein vorteilhaft kann ein Hydraulikzylinder wie im Anspruch 1 definiert als Ersatz für einen herkömmlichen Hydraulikzylinder bestehender Umformmaschinen ausgebildet sein.Generally advantageously, a hydraulic cylinder as defined in
Vereinfacht kann die Erfindung sowie weitere Vorteile wie folgt beschrieben werden. Ein variables Verhältnis der Teilflächen je nach Erfordernis ermöglicht eine größtmögliche Flexibilität hinsichtlich erzielbarer Hubzahlen, was vor allem beim Umformen von temperaturkritischen Werkstoffen vorteilhaft ist. Durch die Aufteilung der Teilflächen in Kombination mit geeigneten Schmiedestrategien ist eine Reduzierung der installierten Leistung und somit eine Energieeinsparung, bei gleichzeitig vergleichbarer Produktivität möglich. Vorteilhaft ist zudem, dass eine Aufteilung der Teilflächen auch für bestehende Anlagen grundsätzlich möglich ist. Der Vorteil der Energieeinsparung wird bei Einsatz eines Energiespeichers, beispielsweise in Form eines Schwungrads welches Energie im Leerlauf speichert und bei Bedarf abgibt, nochmals größer.The invention and further advantages can be described in a simplified manner as follows. A variable ratio of the partial areas, depending on the requirements, enables the greatest possible flexibility with regard to achievable stroke rates, which is particularly advantageous when forming temperature-critical materials. By dividing the partial areas in combination with suitable forging strategies, it is possible to reduce the installed power and thus save energy while at the same time achieving comparable productivity. It is also advantageous that the partial areas can also be divided up for existing systems. The advantage of saving energy is even greater when using an energy storage device, for example in the form of a flywheel, which stores energy when idling and releases it when required.
Der Einsatz der Erfindung kann unabhängig von der Schmiedestrategie erfolgen. Beispielsweise ist es möglich eine konventionelle Strategie, wie sie beim Freiformschmieden zum Einsatz kommt, und durch großen Vorschub ohne Drehung des Werkstücks, jedoch unter Einsatz von vier zeitgleich auf das Werkstück einwirkenden Werkzeugen, charakterisiert ist, anzuwenden. Beim Einsatz bei dieser Schmiedestrategie können hohe Hubzahlen einfach realisiert werden. Beim Einsatz der Erfindung in Kombination mit einer Strategie, bei welcher jeweils zwei gegenüberliegende Werkzeuge einer Radialschmiedemaschine auf das Werkstück einwirken, können ebenfalls hohe Hubzahlen in Verbindung mit einer nochmal optimierten Kerndurchschmiedung realisiert werden.The invention can be used independently of the forging strategy. For example, it is possible to use a conventional strategy such as that used in open die forging, which is characterized by a large feed rate without rotating the workpiece, but using four tools that act on the workpiece at the same time. When using this forging strategy, high numbers of strokes can be easily achieved. When using the invention in combination with a strategy in which two opposing tools of a radial forging machine act on the workpiece, high Stroke numbers can be realized in connection with a further optimized core forging.
Sofern der Hydraulikzylinder mit einer Werkzeugschiebung, also eine Anpassung des Schmiedebereichs mittels Werkzeuge erfolgt, kann die Produktivität nochmals erhöht werden.If the hydraulic cylinder takes place with a tool shift, i.e. an adaptation of the forging area using tools, productivity can be increased again.
All diese Kombinationsmöglichkeiten führen zu einer signifikanten Produktivitätssteigerung durch Verbesserung der Kerndurchschmiedung der Werkstücke bei gleichzeitig geringerem Energiebedarf.All of these combination options lead to a significant increase in productivity by improving the core forging of the workpieces while at the same time using less energy.
Weitere Vorteile und Merkmale ergeben sich aus den nachfolgend beschriebenen Ausführungsbeispielen sowie aus den abhängigen Ansprüchen.Further advantages and features emerge from the exemplary embodiments described below and from the dependent claims.
Nachfolgend werden bevorzugte Ausführungsbeispiele der Erfindung beschrieben und anhand der anliegenden Zeichnungen näher erläutert.
- Fig. 1
- zeigt eine Schnittansicht eines Hydraulikzylinders einer Umformmaschine gemäß einem ersten Ausführungsbeispiel der Erfindung.
- Fig. 2
- zeigt den Hydraulikzylinder aus
Fig. 1 in einer weiteren Betriebsart. - Fig. 3
- zeigt eine Schnittansicht eines Hydraulikzylinders einer Umformmaschine gemäß einem zweiten Ausführungsbeispiel der Erfindung.
- Fig. 1
- shows a sectional view of a hydraulic cylinder of a forming machine according to a first embodiment of the invention.
- Fig. 2
- shows the hydraulic cylinder
Fig. 1 in another operating mode. - Fig. 3
- shows a sectional view of a hydraulic cylinder of a forming machine according to a second embodiment of the invention.
Der in
Das Kolbenglied 3 hat eine zylindrische Stufe 3a, die in eine entsprechende Abstufung des Zylinders 2 vorragt. Hierdurch wird hydraulisch ein erster Teilraum 4 über einer ersten Teilfläche 5 einer Wirkfläche des Kolbenglieds 3 definiert. Der erste Teilraum hat im Wesentlichen die Form eines Vollzylinders.The
Der erste Teilraum 4 ist durch die Stufe 3a von einem zweiten Teilraum 6 über einer zweiten Teilfläche 7 der Wirkfläche des Kolbenglieds 3 hydraulisch abgetrennt. Der zweite Teilraum 6 hat im Wesentlichen die Form eines Ringzylinders.The
Die Teilräume 4, 6 bilden insgesamt einen Zylinderraum des Zylinders 2. Die Wirkfläche des Kolbenglieds 3 ist die Summe der Teilflächen 5, 7. Die Größe der Teilräume 4, 6 variiert je nach momentaner Position des Kolbenglieds 3 in dem Zylinder 2.The
Jeder der Teilräume 4, 6 hat eine jeweilige Öffnung 4a, 6a, durch die ein hydraulisches Fluid in den Teilraum 4, 6 fließen kann. Die Öffnungen 4a, 6a sind über Hydraulikleitungen 8 mit einer Ventilanordnung 9 und einer hydraulischen Pumpeinheit (nicht dargestellt) verbunden. Eine Fließrichtung des Fluids bei Beaufschlagung mit Arbeitsdruck durch die Pumpeinheit ist als Pfeil P dargestellt.Each of the
Die Teilräume 4, 6 sind gemäß den vorstehenden Ausführungen hydraulisch voneinander getrennt, können aber je nach Auslegung der Ventilanordnung 9 bei Bedarf hydraulisch miteinander verbunden werden.The
Vorliegend umfasst die Ventilanordnung 9 ausgehend von der Pumpeinheit einen ersten Abzweig 10, ein diesem nachgeordnetes erstes Ventil 11 und einen diesem nachgeordneten zweiten Abzweig 12. Der erste Abzweig 10 führt zu dem ersten Teilraum 4, so dass dieser im vorliegenden Beispiel permanent durch die Pumpeinheit mit dem Fluid unter Arbeitsdruck beaufschlagt wird.In the present case, the
Der zweite Abzweig 12 führt einerseits zu dem zweiten Teilraum 6 und andererseits zu einem Reservoir 13, das durch ein zweites Ventil 14 zwischen dem zweiten Abzweig 12 und dem Reservoir 13 absperrbar ist. Das Reservoir ist mit Fluid im Wesentlichen unter Atmosphärendruck gefüllt.The
Ein Ablauf 15 des ersten Teilraums 4 führt zu einem Sumpf und/oder einer Ansaugseite der Pumpeinheit zurück. Der Ablauf 15 ist durch einen in der Wirkrichtung W antreibbar verschiebbaren Pilotkolben 16 steuerbar verschließbar, so dass der Pilotkolben 16 mit dem Ablauf 15 ein Steuerventil der Ventilanordnung 9 ausbildet. Über den Pilotkolben 16 wird vorliegend die Position des Kolbenglieds 3 in Wirkrichtung eingestellt. Der Pilotkolben 16 ist vorliegend ebenfalls hydraulisch angetrieben, kann aber je nach Anforderungen auch einen elektromotorischen oder sonstigen Antrieb aufweisen.A
Zur dynamischen Veränderung der Position des Kolbenglieds 3 in beiden Richtungen liegt zudem eine wesentlich kleinere, rücktreibende Kraft über eine rückstellende Wirkfläche 17 in einem Rückstellraum 18 an dem Kolbenglied 3 an. Die rückstellende Wirkfläche 17 wird ebenfalls durch Fluid unter Arbeitsdruck beaufschlagt. Hier wirkt der Arbeitsdruck des Fluids im Gegensatz zu den beiden Teilräumen nicht in der Wirkrichtung, sondern in umgekehrter Richtung.In order to dynamically change the position of the
Das Funktionsprinzip des Pilotkolbens ist zudem in der
Die Erfindung funktioniert nun wie folgt:
Bei einer ersten Betriebsart ist das erste Ventil 10 geschlossen und das zweite Ventil 14 geöffnet. Hierdurch wird nur der erste Teilraum 4 mit Fluid unter Arbeitsdruck von der Pumpeinheit versorgt. der zweite Teilraum ist über das zweite Ventil mit dem Reservoir 13 verbunden. Dies stellt eine ständige Füllung mit Fluid unter Atmosphärendruck oder einem geringfügig höheren Druck zur Verbesserung einer Fließgeschwindigkeit sicher.The invention now works as follows:
In a first operating mode, the
Unter diesen Bedingungen ist eine Maximalkraft des Kolbenglieds 3 reduziert, wobei zugleich eine schnelle Kolbenbewegung bei gegebenem Volumenstrom durch die Pumpeinheit erreicht wird.Under these conditions, a maximum force of the
Bei einer zweiten Betriebsart ist das erste Ventil 10 geöffnet und das zweite Ventil 14 geschlossen. Hierdurch steht das Reservoir 13 nicht mehr mit dem Zylinder 2 in Verbindung, und die beiden Teilräume 4, 6 sind hydraulisch parallel verbunden.In a second operating mode, the
Dies entspricht einem Betrieb eines herkömmlichen Hydraulikzylinders, dessen Arbeitsraum der Summe der Teilräume 4, 6 und dessen Wirkfläche der Summe der Teilflächen 5, 7 beträgt. Hierdurch wird im Vergleich zu der ersten Betriebsart eine größere Maximalkraft des Kolbenglieds 3 erreicht, wobei eine Geschwindigkeit der Kolbenbewegung bei gleichem Volumenstrom des Fluids geringer ist.This corresponds to an operation of a conventional hydraulic cylinder, the working space of which is the sum of the
Bei einer zweiten Ausführungsform der Erfindung gemäß
Das Kolbenglied 3 ist in der schematischen Zeichnung schraffiert dargestellt. Eine zylindrische, vorragende Stufe 2a ist bei diesem Beispiel als Teil des Zylinders 2 ausgebildet, so dass das Kolbenglied im Wesentlichen eine Becherform aufweist. Diese Wahl der Formgebung ist von der Auslegung der Ventilanordnung 9 unabhängig.The
Vorliegend hat die Ventilanordnung 9 einen ersten Abzweig 19, der zu dem ersten Teilraum 4 führt. Stromabwärts des Abzweigs 19 ist ein Ventil 20 angeordnet.In the present case, the
Der zweite Teilraum 6 und der Rückstellraum 18 werden unmittelbar mit Fluid beschickt und haben Abflüsse 21, 22. Hinter den Abflüssen 21, 22 sind jeweils Ventile 23, 24 angeordnet.The
Erkennbar wird einer der Teilräume 4, 6 oder der Rückstellraum 18 genau dann mit Fluid unter Arbeitsdruck beaufschlagt, wenn das ihm zugeordnete Ventil 20, 23, 24 geschlossen wird.It can be seen that one of the
Im Fall der Öffnung des jeweiligen Ventils 20, 23, 24 strömt das Fluid ohne Druckaufbau im Kreis. Entsprechend sind die drei Zuführungen P jeweils separat druckführend und nicht parallel zueinander geschaltet. Dies kann zum Beispiel durch separate hydraulische Pumpen erreicht werden.If the
Die Betriebsarten des Hydraulikzylinders gemäß dem zweiten Beispiel sind vollständig analog denen des ersten Beispiels. Im zweiten Beispiel kann zudem auf einfache Weise selektiert werden, welcher der Teilräume 4, 6 einzeln mit Arbeitsdruck beaufschlagt werden soll. Hierdurch kann der Betrieb noch flexibler gewählt werden, zum Beispiel wenn die Teilflächen unterschiedlich groß ausgelegt werden.The modes of operation of the hydraulic cylinder according to the second example are completely analogous to those of the first example. In the second example, it is also possible to easily select which of the
Vorliegend ist ein Hydraulikzylinder 1 gemäß einer der vorstehend beschriebenen Bauarten als Teil einer Umformmaschine in Form einer Radial-Schmiedepresse (nicht dargestellt) ausgebildet. Die Summe der Wirkflächen, entsprechend der gesamten Querschnittsfläche des Zylinderraums des Zylinders 2, beträgt etwa 5000 cm2. Der Arbeitsdruck des Fluids liegt bei etwa 400 bar. Das Größenverhältnis der beiden Teilflächen 5, 7 beträgt etwa 50:50.In the present case, a
Die Umformmaschine umfasst vier in Kreuzform paarweise gegeneinander arbeitende Werkzeuge, wobei jedes der Werkzeuge durch einen vorstehend beschriebenen Hydraulikzylinder 1 angetrieben wird.The forming machine comprises four tools working in pairs against one another in a cross shape, each of the tools being driven by a
Gemäß den vorstehend beschriebenen Betriebsarten des Hydraulikzylinders 1 werden folgende Betriebsarten der Umformmaschine bzw. Schmiedepresse unterstützt:
- Schlichten: Hierbei sind schnelle Werkzeughübe von hoher Frequenz erforderlich, wobei die Maximalkraft aufgrund eines geringeren Umformhubs kleiner ausgelegt sein darf. Entsprechend werden die
Hydraulikzylinder 1 in der ersten der vorstehend beschriebenen Betriebsarten eingesetzt. - Schmieden: Hierbei sind langsame Werkzeughübe von niedriger und mittlerer Frequenz erforderlich, wobei die Maximalkraft aufgrund eines hohen Umformhubs groß sein muss. Entsprechend werden die
Hydraulikzylinder 1 in der zweiten der vorstehend beschriebenen Betriebsarten eingesetzt.
- Finishing: This requires fast tool strokes with a high frequency, whereby the maximum force can be designed to be smaller due to a smaller forming stroke. Accordingly, the
hydraulic cylinders 1 are used in the first of the operating modes described above. - Forging: Slow tool strokes of low and medium frequency are required, whereby the maximum force must be high due to a high forming stroke. Accordingly, the
hydraulic cylinders 1 are used in the second of the operating modes described above.
Zudem kann beim Schmieden vorgesehen sein, dass bei Bedarf zwischen den Betriebsarten umgeschaltet wird, um die Werkzeuge über größere Strecken schnell zu verfahren, während keine Umformung erfolgt. Dies kann zum Beispiel im Zuge eines Werkstückvorschubs erfolgen und erlaubt insgesamt eine Beschleunigung des Schmiedevorgangs.In addition, it can be provided during forging that, if necessary, a switch is made between the operating modes in order to move the tools quickly over longer distances while no forming takes place. This can take place, for example, in the course of a workpiece feed and allows the forging process to be accelerated overall.
- 11
- HydraulikzylinderHydraulic cylinder
- 22
- Zylindercylinder
- 2a2a
- vorragende Stufe am Zylinderprotruding step on the cylinder
- 33
- KolbengliedPiston member
- 3a3a
- vorragende Stufe am Kolbengliedprotruding step on the piston member
- 44th
- erster Teilraumfirst subspace
- 4a4a
- Öffnung erster TeilraumOpening of the first sub-space
- 55
- erste Teilflächefirst face
- 66th
- zweiter Teilraumsecond subspace
- 6a6a
- Öffnung zweiter TeilraumOpening of the second sub-space
- 77th
- zweite Teilflächesecond partial area
- 88th
- HydraulikleitungenHydraulic lines
- 99
- VentilanordnungValve arrangement
- 1010
- AbzweigBranch
- 1111
- VentilValve
- 1212th
- AbzweigBranch
- 1313th
- Reservoirreservoir
- 1414th
- VentilValve
- 1515th
- Ablaufsequence
- 1616
- PilotkolbenPilot piston
- 1717th
- rückstellende Wirkflächerestoring effective area
- 1818th
- RückstellraumStorage room
- 1919th
- AbzweigBranch
- 2020th
- Ventil erster TeilraumValve first subspace
- 2121
- Abfluss zweiter TeilraumDrain second subspace
- 2222nd
- Abfluss RückstellraumDrain storage room
- 2323
- Ventil zweiter TeilraumValve second compartment
- 2424
- Ventil RückstellraumValve reset space
- WW.
- WirkrichtungEffective direction
- PP.
- hydraulische Zuführunghydraulic feed
Claims (14)
- Reshaping machine for shaping a workpiece, wherein a tool of the reshaping machine can be acted on with a reshaping force by means of a hydraulic cylinder (1), the hydraulic cylinder (1) comprisinga cylinder (2),a piston element (3), which is guided in the cylinder (2) to be movable in an effective direction W, with a effective area (5, 7), anda first opening for the feed of a fluid to a cylinder space (4, 6) above the effective area (5, 7),wherein a working pressure, which acts on the effective area (5, 7), of the fluid drives the piston element (3) in the effective direction,characterised in thatthe effective area has a first part area (5) and at least one second part area (7),wherein the cylinder space is divided into a first part space (4) with the first opening (4a) above the first effective area (5) and a second part space (6) with a second opening (6a) above the second part area (7), andwherein the part spaces (4, 6) are hydraulically separated from one another at least in a selectable mode of operation,and the reshaping machine is constructed as a radial forging machine, particularly with at least four tools operating in pairs in opposition.
- Reshaping machine according to claim 1, characterised in that in a first mode of operation a smoothing of the workpiece under the action of only one of the part spaces (4, 6) with fluid under working pressure takes place, wherein in a second mode of operation of the reshaping machine a forging of the workpiece under the action of both part spaces (4, 6) with fluid under working pressure takes place.
- Reshaping machine according to one of claims 1 and 2, characterised in that in one mode of operation a rapid positioning of the piston element (3) under the action of only one of the part spaces (4, 6) with fluid under working pressure takes place, wherein after the positioning a reshaping of the workpiece under the action of both part spaces (4, 6) with fluid under working pressure takes place.
- Reshaping machine according to any one of the preceding claims, characterised in that a ratio of the part areas is asymmetrical and is between 45:55 and 20:80, particularly between 40:60 and 20:80.
- Reshaping machine according to any one of the preceding claims, characterised in that the part spaces extend concentrically around a centre axis of the cylinder (2).
- Reshaping machine according to any one of the preceding claims, characterised in that a step (2a, 3a), which is, in particular, cylindrical, for separation of the part spaces (4, 6) projects parallelly to the effective direction (W) at one of the two of the piston element and (3) or cylinder (2).
- Reshaping machine according to any one of the preceding claims, characterised in that the part spaces (4, 6) are connected with a hydraulic pump unit and a valve arrangement (9), wherein the valve arrangement (9) enables fluid loading of the part spaces (4, 6) in at least two modes of operation.
- Reshaping machine according to claim 7, characterised in that in a first one of the modes of operation a rapid advance of the piston element (3) with reduced piston force is present, wherein in a second one of the modes of operation a slower advance of the piston element (3) with high piston force is present, and wherein the modes of operation are realised by different loading of the part spaces (4, 6) with fluid under working pressure.
- Reshaping machine according to claim 7 or 8, characterised in that the valve arrangement (9) comprises a control valve with a pilot piston (16) displaceable in the effective direction.
- Reshaping machine according to any one of claims 7 to 9, characterised in that one of the part spaces (4, 6) is connectible by the valve arrangement (9) with a hydraulic reservoir which is, in particular, free of pressure.
- Reshaping machine according to any one of claims 7 to 10, characterised in that at least one of the part spaces (4, 6), particularly both part spaces (4, 6), can be loaded with the fluid by means of a valve (20, 23) arranged downstream of the part space.
- Reshaping machine according to any one of the preceding claims, characterised in that the hydraulic cylinder (1) has a resetting effective area (17), wherein the piston element (3) is resettable by loading of the resetting effective area (17) with the fluid against the effective direction (W).
- Reshaping machine according to any one of the preceding claims, characterised in that the entire effective area (5, 7) of the piston element is at least 1,000 cm2, particularly at least 2,000 cm2.
- Reshaping machine according to any one of the preceding claims, characterised in that three or more part spaces, which are hydraulically separable from one another, together with part areas, which are respectively associated therewith, of the piston element are provided.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016205973.4A DE102016205973A1 (en) | 2016-04-11 | 2016-04-11 | hydraulic cylinders |
PCT/EP2017/057708 WO2017178249A2 (en) | 2016-04-11 | 2017-03-31 | Hydraulic cylinder |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3443229A2 EP3443229A2 (en) | 2019-02-20 |
EP3443229B1 true EP3443229B1 (en) | 2021-11-10 |
Family
ID=58464552
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17715115.6A Active EP3443229B1 (en) | 2016-04-11 | 2017-03-31 | Radial forging machine with hydraulic cylinder |
Country Status (6)
Country | Link |
---|---|
US (1) | US11167338B2 (en) |
EP (1) | EP3443229B1 (en) |
JP (1) | JP2019516934A (en) |
CN (1) | CN109072953A (en) |
DE (1) | DE102016205973A1 (en) |
WO (1) | WO2017178249A2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102022206855A1 (en) | 2022-06-30 | 2024-01-04 | Sms Group Gmbh | Forging strategy SMX |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
IT201900012969A1 (en) * | 2019-07-26 | 2021-01-26 | Mecolpress S P A | EQUIPMENT FOR MATERIALS MOLDING. |
Family Cites Families (15)
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US3186305A (en) * | 1963-07-02 | 1965-06-01 | Ex Cell O Corp | Hydraulic actuator mechanism |
DE2220180A1 (en) | 1972-04-25 | 1973-11-08 | Geb Maier Gisela Bieber | HYDRAULIC CYLINDER WITHOUT THROUGH PISTON ROD WITH THE SAME FEED AND RETURN SURFACES, AS WELL AS A FAST SPEED DEVICE |
PT68274A (en) * | 1978-07-11 | 1978-08-01 | A A Ribeiro De Almeida | Device applicable to presses and metal bending presses to syncronize the movements of the hydraulic cylinders and control slider cross member |
JPH0814212A (en) * | 1994-04-26 | 1996-01-16 | Mitsubishi Plastics Ind Ltd | Multicavity cylinder |
JPH08334102A (en) * | 1995-06-07 | 1996-12-17 | Nikko Tokki Kk | Step-up system and forging machine |
DE19543876A1 (en) * | 1995-11-24 | 1997-05-28 | Rexroth Mannesmann Gmbh | Method and device for controlling a hydraulic system of an implement |
ATE211036T1 (en) | 1997-10-15 | 2002-01-15 | Sms Eumuco Gmbh | HYDRAULIC DRIVE SYSTEM FOR SLIDES OF FORGING PRESSES OR FORGING MACHINES |
US6240758B1 (en) * | 1999-06-21 | 2001-06-05 | Toyokoki Co., Ltd. | Hydraulic machine |
JP3782710B2 (en) * | 2001-11-02 | 2006-06-07 | 日邦興産株式会社 | Hydraulic press device |
JP3782725B2 (en) * | 2001-12-06 | 2006-06-07 | カヤバ工業株式会社 | Hydraulic cylinder |
NL1025806C2 (en) * | 2004-03-25 | 2005-09-27 | Demolition And Recycling Equip | Hydraulic cylinder, for example, for use with a hydraulic tool. |
DE102009052531A1 (en) * | 2009-11-11 | 2011-05-12 | Hoerbiger Automatisierungstechnik Holding Gmbh | machine press |
CN201526558U (en) * | 2009-11-17 | 2010-07-14 | 姚国志 | Variable pressure-and-speed double-cylinder tandem hydraulic oil cylinder |
JP2012002272A (en) * | 2010-06-16 | 2012-01-05 | Takayoshi Numakura | Hydraulic cylinder and hydraulic drive unit |
CN103752747A (en) * | 2014-01-16 | 2014-04-30 | 焦作市华科液压机械制造有限公司 | Mechanical-hydraulic radial forging machine |
-
2016
- 2016-04-11 DE DE102016205973.4A patent/DE102016205973A1/en not_active Withdrawn
-
2017
- 2017-03-31 CN CN201780022864.5A patent/CN109072953A/en active Pending
- 2017-03-31 EP EP17715115.6A patent/EP3443229B1/en active Active
- 2017-03-31 US US16/092,871 patent/US11167338B2/en active Active
- 2017-03-31 WO PCT/EP2017/057708 patent/WO2017178249A2/en active Application Filing
- 2017-03-31 JP JP2019503624A patent/JP2019516934A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102022206855A1 (en) | 2022-06-30 | 2024-01-04 | Sms Group Gmbh | Forging strategy SMX |
Also Published As
Publication number | Publication date |
---|---|
WO2017178249A3 (en) | 2017-12-14 |
WO2017178249A2 (en) | 2017-10-19 |
US11167338B2 (en) | 2021-11-09 |
CN109072953A (en) | 2018-12-21 |
US20190217373A1 (en) | 2019-07-18 |
EP3443229A2 (en) | 2019-02-20 |
DE102016205973A1 (en) | 2017-10-12 |
JP2019516934A (en) | 2019-06-20 |
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