EP3178581B1 - High frequency hydraulic cylinder - Google Patents
High frequency hydraulic cylinder Download PDFInfo
- Publication number
- EP3178581B1 EP3178581B1 EP16002610.0A EP16002610A EP3178581B1 EP 3178581 B1 EP3178581 B1 EP 3178581B1 EP 16002610 A EP16002610 A EP 16002610A EP 3178581 B1 EP3178581 B1 EP 3178581B1
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- EP
- European Patent Office
- Prior art keywords
- piston
- high frequency
- cylinder
- pressure
- frequency cylinder
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- 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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- 238000013016 damping Methods 0.000 claims description 6
- 238000003825 pressing Methods 0.000 claims 1
- 238000011144 upstream manufacturing Methods 0.000 claims 1
- 238000005520 cutting process Methods 0.000 description 11
- 239000007789 gas Substances 0.000 description 11
- 230000009467 reduction Effects 0.000 description 5
- 238000013459 approach Methods 0.000 description 4
- 238000005242 forging Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 4
- 238000007789 sealing Methods 0.000 description 4
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/26—Supply reservoir or sump assemblies
- F15B1/265—Supply reservoir or sump assemblies with pressurised main reservoir
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under 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
- 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
- F15B15/1476—Special return means
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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
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/26—Locking mechanisms
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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
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
- F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position
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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
- F15B2211/60—Circuit components or control therefor
- F15B2211/625—Accumulators
Definitions
- the invention relates to a high-frequency cylinder with an extremely fast and yet reliable and very compact high-frequency drive for highest working speeds, for example for high-speed cutting (HGSS) or forging.
- HGSS high-speed cutting
- Fast rapid movements are for example desired in idle strokes of machines such as presses and are referred to as quick-stroke or rapid traverse cylinder. They move the press ram in the idle stroke much faster than it would be possible with the area far larger working cylinder. The oil of the working cylinder is sucked in only with negative pressure. They have the same structure as usual working cylinders. Furthermore, hydraulic cylinders are also referred to as rapid traverse or quick-lift cylinders when conventional hydraulic cylinders receive an oil feed via storage or servo valves ( DE102007010426B4 ).
- the dynamics can also be improved ( DE 3215795A1 ).
- Such known cylinders can be used for example in test benches, where it is required to accelerate a test object to a higher speed.
- Another field of application is the rapid supply and removal of parts in production processes.
- the DE 19602390 A1 relates to a working cylinder with a piston and a cylinder whose inner diameter is greater than the maximum piston diameter.
- the cylinder has an annular component with which the piston interacts during the working stroke, in that a functional space is formed between the piston, the annular component and the cylinder, which is sealed off from the remaining cylinder space and whose pressure can be controlled via a control valve.
- the object of the present invention is therefore to provide an extremely fast and yet reliable and very compact high-frequency drive with the highest operating speeds, for example for high-speed cutting (HGSS) or forging.
- HGSS high-speed cutting
- a hydraulic cylinder is designed so that the piston can extend at extremely high speeds.
- the return stroke of the piston should take place in the shortest possible time in order to enable the highest number of deliveries.
- the high-frequency cylinder comprises a piston and a cylinder tube whose inner diameter is larger than the maximum diameter of the piston, the piston being internally hydraulically locked and disengageable to a control ring by the switching of valves, the clutched state hydraulically released for the purpose of extremely fast extension of the piston is and at the same time internally comprises a piston enclosing the accumulator piston and from the storage space pressure accumulator whose energy is released during rapid extension of the piston practically without flow losses of hydraulic lines to the piston.
- An accumulator piston has an externally applied on its upper side with gas pressure outer annular storage area and an inner annular guide approach, which is acted upon at its top not with gas pressure but with the pressure of the return control chamber and is acted upon on its underside with the pressure of the cylinder chamber and at his Inner diameter forms a guide surface for the piston.
- a differential surface is formed, which is permanently subjected to oil pressure.
- the ratio of the area of the differential surface to the upper surface of the guide lug behaves as the surface of the lower piston portion with the diameter D1 to the effective area of the accumulator piston of D4 and D1.
- the volume of the return control chamber remains approximately constant, with the return control chamber being connected to a reservoir.
- the hydraulic control is carried out by means of a rotary valve, in whose rotor and stator oil connections for pump and tank are introduced.
- the rotor is mechanically coupled to a workpiece feed drive.
- the hydraulic coupling of the piston can be achieved by frontal pressure relief of the piston by means of a, in particular metallic, Control ring in the retracted state of the piston or by immersing the piston in a recess in the bottom element in subsequent pressure relief of the lower end face of the piston can be realized.
- the piston dips to the end of extension in the oil damping chamber on the accumulator piston or in a separate, located in front of the accumulator piston within an intermediate plate damping chamber.
- the piston seal is connected in front of a relief groove, which is connected to the tank during extension of the piston.
- stroke rates of 1000 rpm are possible and that a limitation mainly occurs through the switching times of valves.
- the usual number of deliveries of hydraulic presses are far exceeded.
- the limitation is eliminated by switching times of valves for even higher stroke rates.
- the extremely fast extending piston can directly actuate a working element or serve as a drive for another drive, for example, designed for a hydraulic cylinder as a pressure booster.
- Fig. 1 describes the design of the high-frequency cylinder according to the invention.
- the control ring 33 forms with the lower part of the collar 5 a sealing surface 34, which shields the pressure prevailing in the cylinder chamber 23 pressure against the control chamber 38.
- the control chamber 38 is relieved via the control valve 32 to tank.
- the control ring 33 is acted upon on its underside with the pressure prevailing in the cylinder chamber 23 pressure. On its upper side, it is partially relieved of pressure via a small paragraph to the control chamber 38 and the pressure drop across the sealing surface 34 between the cylinder chamber 23 and the control chamber 38.
- the upper annular surface of the collar 5 is fully loaded with the pressure prevailing in the cylinder chamber 23, while the pressure axial opposite, lower collar surface is only partially acted upon by the pressure prevailing in the cylinder chamber 23 pressure. The piston is locked.
- the gas storage space formed between the parts 17 and 7, a gas, for example, nitrogen was introduced with the biasing pressure of 100 bar via the gas storage port 14 before the pressure buildup in the cylinder chamber 23.
- the accumulator piston 17 was seated on the spacer tube 24. As a result of a pressure buildup in the cylinder chamber 23 by oil supply via the oil port 29, for example to 300 bar, the accumulator piston 17 was moved upwards and reduces the volume of the gas storage space to 1/3.
- the piston should always reduce its energy externally in one operation. Should it happen due to an incorrect setting that no external energy reduction takes place, the collar 5 of the piston 1 enters the oil damping chamber 20. By entering into the formed on the oil damping chamber 20 slope energy of the piston is reduced there. The spring-back of the accumulator piston 17 in the direction of the gas storage space 21 supports the energy reduction.
- the piston 1 has an upper piston portion 2 and a lower piston portion 3. These form the differential area 4, via which the return stroke is realized by means of pressurization.
- oil is displaced through the differential surface 4 and must be able to flow with as little flow as possible, otherwise it would hinder the extension of the piston with the build-up of a flow pressure.
- the return control chamber 8 is permanently pressurized.
- a small oil reservoir ensures that there is always pressure in the return control chamber 8. Smaller area deviations deviating from the optimum ratio can thus be compensated.
- the magnitude of the differential area 4 is 1 cm 3 .
- the magnitude of the differential area 4 is 1 cm 3 .
- connection 29 into the cylinder chamber 23, in conjunction with the springs 36, ensures the renewed coupling between the collar 5 of the piston 1 and the control ring 33 for the renewed production of the starting position.
- Fig. 2 shows the fast and reliable control by means of a rotary valve.
- a rotary valve is for example from the Scriptures DE 10 2012 024 642 A1 known. It is able to realize a valve control at highest frequencies up to 2000 / min.
- stator 40 With the rotary valve shown, a stator 40 and a rotor 39 are provided. In the stator 40 oil connections are introduced for pump and tank.
- the rotor 39 has the recesses a to d. These connect depending on the rotation angle of the rotor 39, the terminals 29 and 30 of the high-frequency cylinder with pump and tank according to the present rotation angle.
- Fig. 2a and Fig. 2b represent in the rotary valve successively arranged cuts.
- the rotor may be mechanically coupled to the drive of a feed unit not shown via a direct shaft connection or a transmission. In this way it is ensured that the movement of the piston 1 runs absolutely synchronously with the feed at the highest stroke rates of the high-frequency cylinder.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Actuator (AREA)
Description
Die Erfindung betrifft einen Hochfrequenzzylinder mit einen extrem schnellen und dabei zuverlässigen und sehr kompakten Hochfrequenzantrieb für höchste Arbeitsgeschwindigkeiten, beispielsweise für das Hochgeschwindigkeitsscherschneiden (HGSS) oder das Schmieden.The invention relates to a high-frequency cylinder with an extremely fast and yet reliable and very compact high-frequency drive for highest working speeds, for example for high-speed cutting (HGSS) or forging.
Aus der Patenliteratur sind Schnellhubzylinder genannte Hydraulikzylinder bekannt, die für die Erzeugung schneller Eilbewegungen in hydraulischen Pressen ausgelegt sind, beispielsweise bekannt aus der
Schnelle Eilbewegungen sind beispielsweise gewünscht bei Leerhüben von Arbeitsmaschinen wie Pressen und werden als Schnellhub- oder Eilgangzylinder bezeichnet. Sie bewegen den Pressenstößel im Leerhub wesentlich schneller als es mit dem flächenmäßig weitaus größeren Arbeitszylinder möglich wäre. Das Öl des Arbeitszylinders wird dabei lediglich mit Unterdruck angesaugt. Sie haben den gleichen Aufbau wie übliche Arbeitszylinder. Weiterhin werden gleichfalls Hydraulikzylinder als Eilgang- oder Schnellhubzylinder bezeichnet, wenn übliche Hydraulikzylinder eine Öleinspeisung über Speicher oder Servoventile erhalten (
Über eine Verringerung der Massen der bewegten Zylinderteile, beispielsweise durch Einsatz von Faserwerkstoffen, kann ebenfalls die Dynamik verbessert werden (
Für bestimmte Anwendungen sind jedoch noch wesentlich größere Geschwindigkeiten erwünscht bei gleichzeitig hohen Zylinderkräften. Hier kommen verschiedene Vorgänge der fertigungstechnischen Bearbeitung von Produkten in Frage, bei welchem höchste Geschwindigkeiten erwünscht sind. Dies trifft beispielsweise auf das Scherschneiden von Blech oder Stangenmaterial zu, wo bei hohen Schergeschwindigkeiten die Prozesswärme im unmittelbaren Scherbereich verbleibt und infolge der höheren Schertemperatur eine weitaus bessere Schnittflächenqualität erreichbar ist. Gleichfalls zutreffend ist der Vorteil höchster Arbeitsgeschwindigkeiten beim Schmieden. Bei Arbeitsmaschinen für das Warmschmieden ist man bestrebt, hohe Geschwindigkeiten zu realisieren, um die Berührzeit der Formhälften mit dem heißen Werkstück zu minimieren.For certain applications, however, much higher speeds are desired with high cylinder forces. Here come various processes of manufacturing processing of products in question, in which highest speeds are desired. This applies, for example, to the shear cutting of sheet metal or bar stock, where at high shear rates the process heat remains in the immediate shear area and, due to the higher shear temperature, a much better cut surface quality can be achieved. Equally true is the advantage of highest working speeds during forging. In hot forging machines, efforts are made to achieve high speeds to minimize the contact time of the mold halves with the hot workpiece.
In der
In der Patentschrift
In der
deutliche Verringerung der eigentlich erwünschten hohen Geschwindigkeit für den Arbeitshub.In the
significant reduction of the actually desired high speed for the working stroke.
Die
Die Aufgabe der vorliegenden Erfindung besteht deshalb darin, einen extrem schnellen und dabei zuverlässigen und sehr kompakten Hochfrequenzantrieb mit höchsten Arbeitsgeschwindigkeiten, beispielsweise für das Hochgeschwindigkeitsscherschneiden (HGSS) oder das Schmieden, zu schaffen.The object of the present invention is therefore to provide an extremely fast and yet reliable and very compact high-frequency drive with the highest operating speeds, for example for high-speed cutting (HGSS) or forging.
Diese Aufgabe wird durch die Erfindung gemäß dem Anspruch 1 gelöst. Vorteilhafte und zweckmäßige Ausgestaltungen sind den Unteransprüchen zu entnehmen.This object is achieved by the invention according to
Dabei wird ein Hydraulikzylinder so ausgebildet, dass der Kolben mit extrem hohen Geschwindigkeiten ausfahren kann. Gleichzeitig soll der Rückhub des Kolbens in kürzester Zeit erfolgen, um so höchste Stückzahlausbringungen zu ermöglichen.In this case, a hydraulic cylinder is designed so that the piston can extend at extremely high speeds. At the same time, the return stroke of the piston should take place in the shortest possible time in order to enable the highest number of deliveries.
Der Hochfrequenzzylinder umfasst einen Kolben und ein Zylinderrohr dessen Innendurchmesser größer ist als der maximale Durchmesser des Kolbens, wobei der Kolben intern hydraulisch mit einem Steuerring durch die Schaltung von Ventilen ver- und entkuppelbar ist, der Verkupplungszustand zum Zwecke des extrem schnellen Ausfahrens des Kolbens hydraulisch gelöst wird und der gleichzeitig intern einen aus den Kolben umschließenden Speicherkolben und aus dem Speicherraum bestehenden Druckspeicher aufweist, dessen Energie beim schnellen Ausfahren des Kolbens praktisch ohne Strömungsverluste von Hydraulikleitungen an den Kolben abgegeben wird.The high-frequency cylinder comprises a piston and a cylinder tube whose inner diameter is larger than the maximum diameter of the piston, the piston being internally hydraulically locked and disengageable to a control ring by the switching of valves, the clutched state hydraulically released for the purpose of extremely fast extension of the piston is and at the same time internally comprises a piston enclosing the accumulator piston and from the storage space pressure accumulator whose energy is released during rapid extension of the piston practically without flow losses of hydraulic lines to the piston.
Ein Speicherkolben weist eine an seiner Oberseite mit Gasdruck beaufschlagte außen liegende Speicherringfläche sowie einen innen liegenden ringförmigen Führungsansatz auf, der an seine Oberseite nicht mit Gasdruck sondern mit dem Druck des Rücksteuerraums beaufschlagt ist und an seiner Unterseite mit dem Druck des Zylinderraum beaufschlagt ist sowie an seinem Innendurchmesser eine Führungsfläche für den Kolben ausbildet.An accumulator piston has an externally applied on its upper side with gas pressure outer annular storage area and an inner annular guide approach, which is acted upon at its top not with gas pressure but with the pressure of the return control chamber and is acted upon on its underside with the pressure of the cylinder chamber and at his Inner diameter forms a guide surface for the piston.
Am Kolben ist eine Differenzfläche ausgebildet, welche permanent mit Öldruck beaufschlagt ist. Das Verhältnis der Fläche der Differenzfläche zur oberen Fläche des Führungsansatzes verhält sich so, wie die Fläche des unteren Kolbenabschnitts mit dem Durchmesser D1 zur Wirkfläche des Speicherkolbens aus D4 und D1.On the piston, a differential surface is formed, which is permanently subjected to oil pressure. The ratio of the area of the differential surface to the upper surface of the guide lug behaves as the surface of the lower piston portion with the diameter D1 to the effective area of the accumulator piston of D4 and D1.
Während des Ausfahrens des Kolbens bleibt das Volumen des Rücksteuerraums annähernd konstant wobei der Rücksteuerraum mit einem Speicher verbunden ist.During extension of the piston, the volume of the return control chamber remains approximately constant, with the return control chamber being connected to a reservoir.
Die hydraulische Steuerung erfolgt mittels eines Rotationsventils, in dessen Rotor und Stator Ölanschlüsse für Pumpe und Tank eingebracht sind. Der Rotor ist mit einem Werkstückzuführantrieb mechanisch gekoppelt.The hydraulic control is carried out by means of a rotary valve, in whose rotor and stator oil connections for pump and tank are introduced. The rotor is mechanically coupled to a workpiece feed drive.
Die hydraulische Kupplung des Kolbens kann durch stirnseitige Druckentlastung des Kolbens mit Hilfe eines, insbesondere metallischen, Steuerrings im eingefahrenen Zustand des Kolbens oder mittels des Eintauchens des Kolbens in eine Vertiefung im Bodenelement bei anschließender Druckentlastung der unteren Stirnseite des Kolbens realisiert werden.The hydraulic coupling of the piston can be achieved by frontal pressure relief of the piston by means of a, in particular metallic, Control ring in the retracted state of the piston or by immersing the piston in a recess in the bottom element in subsequent pressure relief of the lower end face of the piston can be realized.
Der Kolben taucht zum Ende des Ausfahrens in den Öldämpfungsraum am Speicherkolben ein bzw. in einen gesonderten, vor dem Speicherkolben innerhalb einer Zwischenplatte befindlichen Dämpfungsraum. Der Kolbendichtung ist nach innen eine Entlastungsnut vorgeschaltet, die während des Ausfahrens des Kolbens mit dem Tank verbunden ist.The piston dips to the end of extension in the oil damping chamber on the accumulator piston or in a separate, located in front of the accumulator piston within an intermediate plate damping chamber. The piston seal is connected in front of a relief groove, which is connected to the tank during extension of the piston.
In einer Beispielrechnung wird gezeigt, dass Hubzahlen von 1000/min möglich sind und vorwiegend durch die Schaltzeiten von Ventilen eine Begrenzung eintritt. Die üblichen Stückzahlausbringungen von hydraulischen Pressen werden weit übertroffen. In einer weiteren Ausführung mit einem speziellen Schaltantrieb wird die Begrenzung durch Schaltzeiten von Ventilen beseitigt für noch höhere Hubzahlen. Der extrem schnell ausfahrende Kolben kann ein Arbeitselement direkt betätigen oder auch als Antrieb für einen weiteren Antrieb, beispielsweise für einen als Druckübersetzer ausgebildeten Hydraulikzylinder dienen.In an example calculation it is shown that stroke rates of 1000 rpm are possible and that a limitation mainly occurs through the switching times of valves. The usual number of deliveries of hydraulic presses are far exceeded. In a further embodiment with a special switching drive, the limitation is eliminated by switching times of valves for even higher stroke rates. The extremely fast extending piston can directly actuate a working element or serve as a drive for another drive, for example, designed for a hydraulic cylinder as a pressure booster.
In den Raum 21, dem Gasspeicherraum, der zwischen den Teilen 17 und 7 ausgebildet wird, wurde vor dem Druckaufbau im Zylinderraum 23 ein Gas, beispielsweise Stickstoff mit dem Vorspanndruck von 100 Bar über den Gasspeicheranschluss 14 eingebracht. Der Speicherkolben 17 saß dabei auf dem Distanzrohr 24 auf. Infolge eines Druckaufbaus im Zylinderraum 23 durch Ölzufuhr über den Ölanschluss 29, beispielsweise auf 300 Bar, wurde der Speicherkolben 17 nach oben bewegt und das Volumen des Gasspeicherraums auf 1/3 reduziert.In the
Wird nun der Steuerraum 38 über das Steuerventil 32 mit Druck beaufschlagt, ändern sich die Kräfteverhältnisse am Kolben 1 mit dem Bund 5 schlagartig. Die druckbeaufschlagte Fläche an der Unterseite des Kolbens 1 mit dem Bund 5 ist nun größer als die druckbeaufschlagte Fläche an der Oberseite des Bunds 5. Der Kolben 1 löst sich und bewegt sich praktisch ungehindert nach oben. Er wird mit einer Kraft beschleunigt, die sich aus dem Durchmesser D2 des oberen Kolbenabschnitts 2 sowie dem Druck im Zylinderraum 23 ergibt.Now, if the
Beispiel:
Auf einem Weg von 50mm erreicht der Kolben eine Geschwindigkeit von 28m/sec! Auf einem Weg von 10mm erreicht der Kolben eine Geschwindigkeit von 13m/sec!On a way of 50mm, the piston reaches a speed of 28m / sec! On a way of 10mm, the piston reaches a speed of 13m / sec!
Bei einer Maximalgeschwindigkeit von 28m/sec beträgt die Durchschnittsgeschwindigkeit 14m/sec. Damit benötigt der Kolben für 50mm Kolbenweg die Zeit von knapp 4msec! Für die Dauerhubzahl sind damit praktisch nur die Rückhubzeit und die Zeit zum erneuten Druckaufbau entscheidend. Bei dem Schneiden von Blech mit hohen Geschwindigkeiten ist man bestrebt, eine Geschwindigkeit von mindestens 10m/sec zu erreichen.At a maximum speed of 28m / sec the average speed is 14m / sec. Thus, the piston for 50mm piston travel requires the time of almost 4msec! For the Dauerhubzahl are practically only the return stroke and the time to repressurization crucial. When cutting sheet metal at high speeds, it is endeavored to achieve a speed of at least 10 m / sec.
In diesem Geschwindigkeitsbereich lassen sich erhebliche Verbesserungen bei der Teilequalität erzielen. Diese Geschwindigkeit wird beim Hochfrequenzzylinder bereits bei einem Beschleunigungsweg von 10mm erreicht!In this speed range, significant improvements in part quality can be achieved. This speed is already reached with the high frequency cylinder with an acceleration travel of 10mm!
Beim Schneiden von Blech resultiert der Aufwand für die zugehörige Maschine größtenteils darin, die erforderliche Maximalkraft zu erreichen. Pressen werden beim Kauf in erster Linie nach Tonnage abgerechnet. Mit dem erfindungsgemäßen Hochfrequenzzylinder wird jedoch die Arbeitsenergie beim Schneiden vorgegeben. So können mit einem relativ kleinen Kolbendurchmesser erstaunliche Maximalkräfte infolge der dynamischen Vorgänge erzielt werden.When cutting sheet metal, the cost of the associated machine is largely to achieve the required maximum force. Presses are accounted for at purchase primarily by tonnage. With the high-frequency cylinder according to the invention, however, the working energy is specified during cutting. Thus, with a relatively small piston diameter, astonishing maximum forces due to the dynamic processes can be achieved.
Gegeben sei 1.:
Gegeben sei 2.:
Given is 1 .:
Given is 2 .:
Zum Schneiden einer Ronde von 1000mm mit einer entsprechenden 6700kN-Presse (W= 10.000Nm) ist es ausreichend folgenden Hochfrequenzzylinder einzusetzen:
Derzeit finden hochfeste Bleche Eingang in die Produktionstechnik. Beim Schneiden hoch- und höchstfester Bleche stellt sich der Vorteil des Hochfrequenzzylinders noch deutlicher dar, da hier die Kräfte stark ansteigen während gleichzeitig der Bruch beim Durchschneiden früher eintritt.Currently, high-strength sheets are entering production technology. When cutting high-strength and ultra-high-strength metal sheets, the advantage of the high-frequency cylinder is even more pronounced, since the forces increase strongly here, while at the same time breaking occurs earlier when cutting through.
Wegen der hohen Energie, die der Kolben während seiner Beschleunigung aufbaut, sollte der Kolben stets seine Energie extern in einem Arbeitsvorgang abbauen. Sollte es aufgrund einer Fehleinstellung dazu kommen, dass kein externer Energieabbau erfolgt, fährt der Bund 5 des Kolbens 1 in den Öldämpfungsraum 20 ein. Durch das Einfahren in die am Öldämpfungsraum 20 ausgebildete Schräge wird die Energie des Kolbens dort abgebaut. Das Nachfedern des Speicherkolbens 17 Richtung Gasspeicherraum 21 unterstützt den Energieabbau.Because of the high energy that builds up the piston during its acceleration, the piston should always reduce its energy externally in one operation. Should it happen due to an incorrect setting that no external energy reduction takes place, the
Im Regelfall kommt der Bund 5 des Kolbens 1 jedoch vorher durch den externen Arbeitsvorgang zum Stillstand.As a rule, however, the
Der Kolben 1 weist einen oberen Kolbenabschnitt 2 und einen unteren Kolbenabschnitt 3 auf. Diese bilden die Differenzfläche 4 aus, über die mittels Druckbeaufschlagung der Rückhub realisiert wird. Beim Ausfahren des Kolbens wird Öl durch die Differenzfläche 4 verdrängt und muss möglichst strömungsarm abfließen können, da es sonst mit dem Aufbau eines Strömungsdrucks das Ausfahren des Kolbens behindern würde.The
Der Aufbau eines merklichen Strömungsdrucks wird dadurch verhindert, das das abgedrängte Öl im Rücksteuerraum 8 an Ort und Stelle verbleiben kann. Dies wird realisiert, indem der Speicherkolben 17 einen Führungsansatz 18 aufweist und bestimmte Durchmesserverhältnisse eingehalten werden. Das Verhältnis der Geschwindigkeiten von Kolben 1 und Speicherkolben 17 ergibt sich aus deren Flächen. Es gilt:
Nimmt man ein wirksames Flächenverhältnis Speicherkolben/Kolben von 10 an, ergibt sich für den Kolben 1 die zehnfache Geschwindigkeit gegenüber dem Speicherkolben 17.Assuming an effective area ratio accumulator piston / piston of 10, resulting in the
Wenn nun weiterhin für die Differenzfläche 4 und die wirksame Fläche des Führungsansatzes 18 gilt:
dann wird die Verkleinerung des Rücksteuerraums 8 infolge des von der Differenzfläche 4 beim Ausfahren des Kolbens verdrängten Öls exakt kompensiert durch die Vergrößerung des Rücksteuerraums 8 infolge der Bewegung des Führungsansatzes 18 des Speicherkolbens 17 nach unten.If the differential area 4 and the effective area of the
then the reduction of the
Der Rücksteuerraum 8 ist permanent mit Druck beaufschlagt. Ein kleiner Ölspeicher sorgt dafür, dass immer Druck im Rücksteuerraum 8 anliegt. Kleinere, vom optimalen Verhältnis abweichende Flächenabweichungen können so kompensiert werden.The
Gleichzeitig steht schnell ausreichend Öl zur Verfügung, um den Rückhub in kürzester Zeit ausführen zu können. Vom Steuerventil 32 wird der Rückhub des Kolbens eingeleitet. Durch Umschalten des Steuerventils 32 wird nun der Zylinderraum 23 mit dem Tank verbunden. Die Unterseite des Kolbens 1 ist drucklos bis auf den sich einstellenden Restdruck infolge Strömung. An der Differenzfläche 4 liegt permanent der Druck des Speichers über den Ölspeicheranschluss 13 an. Der Kolben wird in seine Ausgangslage zurückbewegt bis er wieder auf die Dichtfläche 34 aufsetzt.At the same time there is quickly enough oil available to be able to carry out the return stroke in the shortest possible time. From the
Bei einem beispielhaften Durchmesser D1 von 30 und D2 von 28 liegt die Größenordnung der Differenzfläche 4 bei 1cm3. Für 50mm Rückhubweg werden so ca. 5cm3 Öl von benötigt. Mit einem Liter Öl von der Pumpe können somit 200 Rückhübe realisiert werden, für 1000 Hübe/min benötigt man so einen Ölfluss von 5L/min.For an exemplary diameter D1 of 30 and D2 of FIG. 28, the magnitude of the differential area 4 is 1 cm 3 . For 50mm Rückhubweg so about 5cm 3 oil of needed. With one liter of oil from the pump thus 200 return strokes can be realized, for 1000 strokes / min so you need an oil flow of 5L / min.
Der vom Anschluss 29 in den Zylinderraum 23 einströmende Druck sorgt in Verbindung mit den Federn 36 für die erneute Verkupplung zwischen dem Bund 5 des Kolbens 1 und dem Steuerring 33 zur erneuten Herstellung der Ausgangslage.The pressure flowing from the
Das in den Zylinderraum 23 einströmende Öl sorgt für die erneute Speicheraufladung durch die Verkleinerung des Gasspeicherraums 21 infolge Verschiebung des Speicherkolbens 17 nach oben. Bei einem oberen Kolbendurchmesser von 28 mm und einer aus dem Zylinder herausgeschobenen Kolbenlänge von 50mm ergibt sich ein erforderliches Ölvolumen von ca. 31cm3. Zusammen mit dem Ölbedarf für den Rückhub von ca. 5cm3 ergibt sich ein Ölbedarf von 36cm3 pro Hub.The inflowing into the
Mit einem Liter Öl von der Pumpe können somit ca. 28 Hübe realisiert werden.With one liter of oil from the pump thus approx. 28 strokes can be realized.
Mit einem Pumpenvolumen von 36L/min können somit 1000 Hübe/min gefahren werden. Die Hubzahleinschränkung kommt dann hautsächlich infolge der Schaltzeiten von Hydraulikventilen zustande. Eine Lösung zur Eliminierung der Schaltzeiten von Hydraulikventilen ist in
Bei gezeigtem Rotationsventil sind ein Stator 40 und ein Rotor 39 vorhanden. Im Stator 40 sind Ölanschlüsse eingebracht für Pumpe und Tank. Der Rotor 39 besitzt die Aussparungen a bis d. Diese verbinden in Abhängigkeit vom Drehwinkel des Rotors 39 die Anschlüsse 29 und 30 des Hochfrequenzzylinders mit Pumpe und Tank entsprechend des vorliegenden Rotationswinkels.With the rotary valve shown, a
- 11
- Kolbenpiston
- 22
- Oberer KolbenabschnittUpper piston section
- 33
- Unterer KolbenabschnittLower piston section
- 44
- Differenzflächedifferential area
- 55
- BundFederation
- 66
- Zentrierbolzencentering
- 77
- Steuerteilcontrol part
- 88th
- RücksteuerraumBack control space
- 99
- Obere KolbenführungUpper piston guide
- 1010
- SpeicherkolbenführungMemory piston guide
- 1111
- Entlastungsnutrelief
- 1212
- Kolbendichtungpiston seal
- 1313
- ÖlspeicheranschlussOil storage terminal
- 1414
- GasspeicheranschlussGas storage terminal
- 1515
- LeckölanschlussDrain port
- 1616
- Schutzrohrthermowell
- 1717
- Speicherkolbenaccumulator piston
- 1818
- Führungsansatzleadership approach
- 1919
- Gasdichtunggas seal
- 2020
- ÖldämpfungsraumOil damping space
- 2121
- GasspeicherraumGas storage space
- 2222
- Zylinderrohrcylinder tube
- 2323
- Zylinderraumcylinder space
- 2424
- Distanzrohrspacer tube
- 2525
- Zylinderdichtungcylinder seal
- 2626
- Bodenelementfloor element
- 2727
- Zentrierbohrungcentering
- 2828
- Ringnutring groove
- 2929
- Ölanschluss ZylinderraumOil connection cylinder room
- 3030
- Ölanschluss SteuerraumOil connection control room
- 3131
- Bodendichtungfloor seal
- 3232
- Steuerventilcontrol valve
- 3333
- Steuerringcontrol ring
- 3434
- Dichtflächesealing surface
- 3535
- Steuerdichtungcontrol seal
- 3636
- Federfeather
- 3737
- Halteringretaining ring
- 3838
- Steuerraumcontrol room
- 3939
- Rotorrotor
- 4040
- Statorstator
- 4141
- SpeicherringflächeStorage ring surface
Claims (8)
- High-frequency cylinder having a piston (1) and a cylinder tube (22) whose inner diameter is larger than the maximum diameter of the piston (1), and a storage piston (17) having an outer storage ring surface (41) whose upper surface is acted upon by gas pressure,
characterised in that
the storage piston (17) has an internal annular guide extension (18) which is not acted upon on its upper surface by gas pressure but instead by pressure from a reverse control chamber (8) and on its lower surface by pressure from a cylinder chamber (23), and in which a guide surface for the piston (1) is present on the inside diameter. - High frequency cylinder according to claim 1,
characterised in that
the piston (1) has an upper piston section (2) and a lower piston section (3) which form a differential surface (4) and by which the return stroke of the piston (1) can be realised by applying pressure, the differential surface (4) being permanently subjected to oil pressure. - High frequency cylinder according to claims 1 and 2,
characterised in that
the volume of the return control chamber (8) remains approximately constant during the extension of the piston (1), and in that the return control chamber (8) can be connected to an accumulator. - Arrangement with a high-frequency cylinder according to claims 1 to 3, a rotation valve and a workpiece feed drive,
characterised in that
the high frequency cylinder is hydraulically controlled by the rotary valve, into whose rotor (39) and stator (40) are introduced oil connections for pump and tank, the rotor (39) being mechanically coupled to the workpiece feed drive. - Arrangement according to claim 4 or high frequency cylinder according to claims 1 to 3,
characterised in that
the hydraulic coupling of the piston (1) can be realised by relieving the pressure on the end face of the piston (1) by means of the high frequency cylinder's metal control ring (33) in the retracted state of the piston (1). - Arrangement as per claim 4 or high frequency cylinder as per claims 1 to 3 and 5,
characterised in that
the hydraulic coupling can be realised by immersing the piston (1) into a depression in a base element (26) of the high frequency cylinder with subsequent pressure relief of the lower end face of the piston (1). - Arrangement according to claim 4 or high frequency cylinder according to claims 1 to 3 and 5 to 6,
characterised in that
an inside-facing relief groove, which can be connected to the tank during the extension of the piston (1), is connected upstream of a piston seal (12). - Arrangement as per claim 4 or high frequency cylinder as per claims 1 to 3 and 5 to 7,
characterised in that
the piston (1) is immersed at the end of the extension into a separate damping space of the high frequency cylinder which is located in front of the storage piston (17) within an intermediate plate.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015016149.0A DE102015016149A1 (en) | 2015-12-12 | 2015-12-12 | RF cylinder |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3178581A1 EP3178581A1 (en) | 2017-06-14 |
EP3178581B1 true EP3178581B1 (en) | 2019-11-27 |
Family
ID=57542663
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16002610.0A Active EP3178581B1 (en) | 2015-12-12 | 2016-12-08 | High frequency hydraulic cylinder |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP3178581B1 (en) |
DE (1) | DE102015016149A1 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN112176997B (en) * | 2020-09-16 | 2021-12-31 | 林清辉 | High-frequency vibration type pile driving mechanism |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2127605C3 (en) | 1971-06-03 | 1980-01-24 | Shigeo Chosi Chiba Ando (Japan) | Automatic hydraulic high-speed press |
US3990351A (en) * | 1972-03-10 | 1976-11-09 | Atlas Copco Aktiebolag | Pneumatic impact device |
DE2845924C2 (en) * | 1978-10-21 | 1984-04-26 | Schwelmer Eisenwerk Müller & Co GmbH, 5830 Schwelm | High-speed punching press |
DE3215795C2 (en) | 1982-04-28 | 1986-08-14 | Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen | Pressurized working cylinder |
JPS6182011A (en) * | 1984-09-27 | 1986-04-25 | Shimadzu Corp | Hydraulic cylinder |
DE3913866A1 (en) * | 1989-04-27 | 1990-10-31 | Krupp Maschinentechnik | HYDRAULIC STRIKE |
DE4233115C2 (en) | 1992-10-02 | 1995-04-13 | Ulrich Keller | Hydraulically operated locking and coupling device |
DE19602390A1 (en) * | 1995-01-28 | 1996-08-01 | Ulrich Keller | Work cylinder with piston and cylinder |
DE19642635A1 (en) | 1996-03-28 | 1997-10-02 | Horst Baltschun | Hydraulically or mechanically driven ram of fine-blanking press |
AT8048U1 (en) | 2004-10-13 | 2006-01-15 | Engel Austria Gmbh | METHOD FOR OPERATING AN INJECTION MOLDING MACHINE |
FR2894303B1 (en) * | 2005-12-02 | 2010-09-03 | Pommier S C E B P | DAMPING HYDRAULIC CYLINDER |
DE102007010426B4 (en) | 2007-03-01 | 2008-11-13 | Ortwin Prof. Dr.-Ing. Hahn | Test device for samples under impact load |
DE102007018066B4 (en) | 2007-04-17 | 2010-03-25 | Grimm, Georg, Dipl.-Ing. | Apparatus for pulsed internal high pressure Forming of sheet-like workpieces |
DE102011109066A1 (en) * | 2011-07-28 | 2013-01-31 | Thomas Sauer | Working machine e.g. hydraulic excavator has sealing ring and guide ring/belt that are provided at sealing and sliding surfaces of chambers |
DE102012019386A1 (en) | 2012-10-02 | 2014-04-03 | Institut für Umformtechnik der mittelständischen Wirtschaft GmbH | Device for driving high-speed tool parts for e.g. high-speed shearing process, has energy storage causing spontaneous release of knee lever from extended position, and bringing of movable tool parts in short paths in high speeds |
DE102012024642A1 (en) | 2012-12-15 | 2014-06-18 | Ulrich Keller | Radio frequency valve for use in radio frequency oscillation device for creation of oscillations in fluid system, has dimensioned annular chambers provided with control holes that are assigned to stator and rotor |
-
2015
- 2015-12-12 DE DE102015016149.0A patent/DE102015016149A1/en not_active Withdrawn
-
2016
- 2016-12-08 EP EP16002610.0A patent/EP3178581B1/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
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EP3178581A1 (en) | 2017-06-14 |
DE102015016149A1 (en) | 2017-06-14 |
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