EP0058131B1 - Vibrator - Google Patents

Vibrator Download PDF

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Publication number
EP0058131B1
EP0058131B1 EP82810015A EP82810015A EP0058131B1 EP 0058131 B1 EP0058131 B1 EP 0058131B1 EP 82810015 A EP82810015 A EP 82810015A EP 82810015 A EP82810015 A EP 82810015A EP 0058131 B1 EP0058131 B1 EP 0058131B1
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EP
European Patent Office
Prior art keywords
cylinder
chambers
openings
working
cylinders
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EP82810015A
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German (de)
French (fr)
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EP0058131A2 (en
EP0058131A3 (en
Inventor
Mario Schelling
Bruno Schelling
Armin Schelling
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Individual
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Individual
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Priority to AT82810015T priority Critical patent/ATE13259T1/en
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Publication of EP0058131A3 publication Critical patent/EP0058131A3/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86638—Rotary valve

Definitions

  • the present invention relates to a vibration generator with working pistons displaceably guided in displacement working chambers and with a pressurized fluid as the working medium according to the preamble of the independent claim.
  • CH-A 524 771 describes a method and a device for adjusting a working piston in a cylinder.
  • the working piston is vibrated by supplying and removing a pressure medium, for which purpose a control unit is present between the working cylinder and a storage device for the pressure medium.
  • this control unit there is a control cylinder with a control piston provided with axial grooves.
  • the control piston is both axially displaceable and rotatably driven in order to direct a controlled amount of the pressure medium in the desired direction.
  • Such an arrangement requires three lines for the pressure medium between the accumulator and the working cylinder in a one-sided preloaded piston and four lines in a double-acting cylinder, which have to be sealed accordingly and, in addition to a loss of power, result in a delay in the effect on the working cylinder, so that the Vibration frequency can only be increased up to an order of magnitude of 100 Hz.
  • the invention is intended to create a perfectly functioning vibration generator which has no expensive processing points and with which mechanical vibrations of up to several 1000 Hz can be carried out.
  • a circular cylinder body 1 there are four cylinders 10, 20, 30, 40 arranged perpendicular to one another.
  • Each cylinder has a shoulder 17, 27, 37, 47 and in the cylinder part with the larger diameter there is a piston 13, 23, 33, 43, each with a piston rod 14, 24, 34, 44, which is sealed by a screwed-in sealing cover 78 are guided to the outside with a sealing washer 80 and a tension spring 82.
  • the piston 13, 23, 33, 43 divides the respective cylinder 10, 20, 30, 40 into an outer chamber 11, 21, 31, 41 and an inner chamber 12, 22, 32, 42.
  • the four inner chambers are together connected and filled with a hydraulic fluid.
  • Disks 50 and 60 with holes 51 and 61 lie on the outer surfaces.
  • the two disks 50 and 60 are rigidly connected to one another by means of a shaft 70 through the crossing point of the cylinder axes.
  • a housing 76 encloses the entire cylinder body 1 with the two disks 50 and 60, so that an upper pressure chamber 90 and a lower compensation chamber 92 are formed.
  • the pressure chamber 90 is connected via a connection 74 to a high-pressure store for fluid under pressure and the compensation chamber 92 is connected to a connection 72 to a low-pressure store.
  • the inner chambers 12, 22, 32, 42 are filled with liquid.
  • the disks 50 and 60 accordingly have two bores 51a, 51b and 61 a, 61 b. If the disks 50, 60 are rotated together, these bores lie over openings in the outer chambers of the cylinders of opposing cylinders. According to FIG. 3, the bores 51a, 51b lie over the openings 15, 45 and the bores 61a, 61 over the openings 26, 36.
  • Fluid under pressure thus flows according to the arrows A from the high pressure chamber 90 through the bores 51a, 51b and the openings 15, 45 into the outer chambers 11, 41 and the pistons 13, 43 are pressed into the position shown in FIG. 1. Because the bores 61a, 61b in the disk 60 and the openings 26, 36 are aligned with one another, the fluid can flow out of the outer chambers 21, 31 into the compensator drain chamber 92 so that the pistons 23, 33 can move under the pressure of the liquid in the inner chambers 12, 22, 32, 42 into the outer position, also shown in FIG. 1.
  • FIG. 4 shows another exemplary embodiment in which the pair of cylinders 100 is designed with a common axis and a circular jacket cross section.
  • the cylinder pair 100 is enclosed by a control cylinder 101, which is connected to a drive indicated by the arrow C.
  • the pair of cylinders 100 has openings 102, 103. These openings 102, 103 are elongated in the direction of the surface lines and their longitudinal axes lie in a common plane through the cylinder axis and on opposite cylinder sides.
  • the control cylinder 101 is provided with four holes 104, 105, 106, 107, the axes of which are likewise arranged in a common plane through the axis of the control cylinder 101. These holes are arranged in pairs offset from one another in such a way that they are alternately aligned with an outer part of the openings 102, 103 and with an inner part thereof.
  • the control cylinder 101 is encompassed by a likewise cylindrical housing 110.
  • the housing 110 has two annular webs 111, 112, so that three annular chambers 113, 114, 115 are formed between the control cylinder 101 and the housing 110.
  • the two outer annular chambers 113, 115 are connected by lines 116, 117, 118 to a fluid source for fluid under pressure and therefore represent the high-pressure chamber of the example described earlier.
  • the middle annular chamber 114 is connected via a drain 119 to the low-pressure side of the fluid source and therefore forms the compensation chamber according to the example described first.
  • the holes 104, 105, 106, 107 are now distributed such that the outer chamber 124 of the one cylinder divided by a piston 120 passes through the opening 102 and the hole 104 with the high-pressure chamber 113 and the outer chamber 125 of the other a piston 122 divided cylinder are connected to the compensation chamber 114 via the opening 103 and the hole 107.
  • the control cylinder 101 When the control cylinder 101 is rotated through 180 ° in the direction of arrow C, the high-pressure chamber 115 is connected to the outer chamber 125 via the hole 106 and the opening 103, and the compensation chamber 103 is connected to the outer chamber 124 via the hole 105 and the opening 102.
  • the two pistons 120, 122 and the piston rods 121, 123 therefore perform an opposite movement, directed to the left in the drawing.
  • a rotational movement of the control means namely the control piston 101, results in a translatory movement of the piston rods, the stroke also being determined here by the amount of fluid flowing in and out and the frequency by the speed.
  • more holes can be provided in the disks 50, 60 according to FIGS. 1-3 or more holes in the control cylinder 101 in order to achieve a higher frequency at a lower speed.
  • the pistons 120, 122 in the exemplary embodiment according to FIG. 4 are sealingly connected to the cylinder wall with a soft membrane 131, 132. The stroke of the pistons 120, 122 is therefore limited by the dimensions of these membranes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Actuator (AREA)
  • Surgical Instruments (AREA)
  • Ultra Sonic Daignosis Equipment (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

An oscillator is proposed which comprises a pair of cylinders having a common, circular-cylindrical outer wall (100) and two sealingly guided pistons (120, 122) each having one piston rod (121, 123), which are likewise guided in a sealing manner to the outside through the closure walls of the cylinder. The cylinder is divided by the pistons (120, 122) into outer chambers (124, 125) and inner chambers combined into one common chamber (126). The chamber (126) is filled with fluid. The outer chambers (124, 125) have two openings (102, 103) offset from one another by 180 DEG . A control cylinder (101) having axially offset, oppositely disposed holes (104, 105, 106, 107) connects the outer chambers in alternation with an annular high-pressure chamber (113, 115) and an equalization chamber (114) whenever the control cylinder (101) is rotated. The two pistons (120, 122) thereby execute movements in common toward the left or right, respectively. The stroke is determined by the quantity of fluid capable of flowing out of the high-pressure chamber and into the equalization chamber, and the frequency is determined by the speed of rotation of the control cylinder. A direct control of an oscillator is thus realized, without additional connecting lines and the delay associated with such lines. Frequencies of up to 7000 Hz and strokes up to 10 mm can be generated.

Description

Die vorliegende Erfindung betrifft einen Schwingungserzeuger mit in Verdrängerarbeitskammern verschieblich geführten Arbeitskolben und mit einem unter Druck stehenden Fluid als Arbeitsmedium gemäss dem Gattungsbegriff des unabhängigen Patentanspruchs.The present invention relates to a vibration generator with working pistons displaceably guided in displacement working chambers and with a pressurized fluid as the working medium according to the preamble of the independent claim.

Solche Schwingungserzeuger sind in der Technik bekannt. Beispielsweise wurde in der CH-A 524 771 ein Verfahren und eine Vorrichtung zur Verstellung eines Arbeitskolbens in einem Zylinder beschrieben. Der Arbeitskolben wird durch Zu- und Wegführen eines Druckmittels vibriert, wozu ein Steuergerät zwischen dem Arbeitszylinder und einem Speicher für das Druckmittel vorhanden ist. In diesem Steuergerät ist ein Steuerzylinder mit einem mit axialen Nuten versehenen Steuerkolben vorhanden. Der Steuerkolben ist sowohl axialverschieblich, als auch drehbar angetrieben, um jeweils eine gesteuerte Menge des Druckmittels in die gewünschte Richtung zu leiten. Eine solche Anordnung braucht bei einem einseitig vorgespannten Kolben drei und bei einem beidseitig wirkenden Zylinder vier Leitungen für das Druckmittel zwischen dem Speicher und dem Arbeitszylinder, die entsprechend abgedichtet sein müssen und neben einem Leistungsverlust eine zeitliche Verzögerung der Wirkung auf den Arbeitszylinder ergeben, so dass die Schwingfrequenz nur bis zu einer Grössenordnung von 100 Hz gesteigert werden kann.Such vibrators are known in the art. For example, CH-A 524 771 describes a method and a device for adjusting a working piston in a cylinder. The working piston is vibrated by supplying and removing a pressure medium, for which purpose a control unit is present between the working cylinder and a storage device for the pressure medium. In this control unit there is a control cylinder with a control piston provided with axial grooves. The control piston is both axially displaceable and rotatably driven in order to direct a controlled amount of the pressure medium in the desired direction. Such an arrangement requires three lines for the pressure medium between the accumulator and the working cylinder in a one-sided preloaded piston and four lines in a double-acting cylinder, which have to be sealed accordingly and, in addition to a loss of power, result in a delay in the effect on the working cylinder, so that the Vibration frequency can only be increased up to an order of magnitude of 100 Hz.

In der US-A-3 678 803 und auch in der DE-A-28 21 339 sind hydraulische Schwingungserzeuger beschrieben, bei denen die Druckflüssigkeit direkt aus der Quelle an das Zylindergehäuse hin und von da wieder zurück geführt ist. Im Zylindergehäuse ist ein rotierbarer Arbeitskolben angeordnet, der mit Einlass- und Auslasskanälen versehen ist und dadurch in von der Rotation abhängiger abwechselnder Weise die beidseits des Kolben befindlichen Arbeitskammern mit Druckfluid versorgen und/oder entleeren kann. Nachteilig an einer solchen Anordnung sind die Kanäle im Kolben, weil diese und dazu noch die zugeordneten Oeffnungen in der Zylinderwand mit äusserst geringen Toleranzen zu bearbeiten sind und daher einen solchen Schwingungserzeuger verteuern.In US-A-3 678 803 and also in DE-A-28 21 339 hydraulic vibrators are described in which the pressure fluid is fed directly from the source to the cylinder housing and from there back again. A rotatable working piston is arranged in the cylinder housing, which is provided with inlet and outlet channels and can thereby supply the working chambers on both sides of the piston with pressurized fluid and / or empty them in an alternating manner depending on the rotation. The channels in the piston are disadvantageous in such an arrangement because they and the associated openings in the cylinder wall are to be machined with extremely small tolerances and therefore make such a vibration generator more expensive.

Demgegenüber soll durch die Erfindung ein einwandfrei arbeitender Schwingungserzeuger geschaffen werden, der keine teuren Bearbeitungsstellen aufweist und mit dem mechanische Schwingungen bis zu mehreren 1 000 Hz ausführbar sind.In contrast, the invention is intended to create a perfectly functioning vibration generator which has no expensive processing points and with which mechanical vibrations of up to several 1000 Hz can be carried out.

Erfindungsgemäss wird dies durch die Merkmale im kennzeichnenden Teil des unabhängigen Patentanspruchs 1 erreicht.According to the invention this is achieved by the features in the characterizing part of independent claim 1.

Ausführungsbeispiele der Erfindung werden nachfolgend anhand der Zeichnung erläutert. Es zeigen :

  • Figur 1 eine Schnittansicht als Grundriss gemäss der Schnittlinie I-I in Fig. 2 einer ersten Ausführungsform,
  • Figur 2 eine Schnittansicht eines Paares von Zylindern gemäss der Schnittlinie 11-11 in Fig. 1
  • Figur 3 eine gedehnt gezeichnete schematische Darstellung der Anordnung gemäss Fig. 1 und 2, und
  • Figur 4 eine Schnittansicht durch ein Zylinderpaar einer zweiten Ausführungsform.
Embodiments of the invention are explained below with reference to the drawing. Show it :
  • FIG. 1 shows a sectional view as a plan according to section line II in FIG. 2 of a first embodiment,
  • FIG. 2 shows a sectional view of a pair of cylinders according to section line 11-11 in FIG. 1
  • FIG. 3 shows a schematic representation of the arrangement according to FIGS. 1 and 2, drawn in expanded form, and
  • Figure 4 is a sectional view through a pair of cylinders of a second embodiment.

In einem kreisförmigen Zylinderkörper 1 sind vier senkrecht zueinander angeordnete Zylinder 10, 20, 30, 40 vorhanden. Jeder Zylinder weist eine Schulter 17, 27, 37, 47 auf und im Zylinderteil mit dem grösseren Durchmesser befindet sich ein Kolben 13, 23,33,43 mit je einer Kolbenstange 14, 24, 34, 44, die abgedichtet durch einen eingeschraubten Dichtungsdeckel 78 mit einer Dichtscheibe 80 und einer Spannfeder 82 nach aussen geführt sind. Der Kolben 13, 23, 33, 43 unterteilt den jeweiligen Zylinder 10, 20, 30, 40 in eine äussere Kammer 11, 21, 31, 41 und in eine innere Kammer 12, 22, 32, 42. Die vier inneren Kammern sind miteinander verbunden und mit einem hydraulischen Fluid gefüllt.In a circular cylinder body 1 there are four cylinders 10, 20, 30, 40 arranged perpendicular to one another. Each cylinder has a shoulder 17, 27, 37, 47 and in the cylinder part with the larger diameter there is a piston 13, 23, 33, 43, each with a piston rod 14, 24, 34, 44, which is sealed by a screwed-in sealing cover 78 are guided to the outside with a sealing washer 80 and a tension spring 82. The piston 13, 23, 33, 43 divides the respective cylinder 10, 20, 30, 40 into an outer chamber 11, 21, 31, 41 and an inner chamber 12, 22, 32, 42. The four inner chambers are together connected and filled with a hydraulic fluid.

Die Aussenflächen des Zylinderkörpers 1, die parallel zur Ebene liegen, die die vier Achsen der Zylinder enthält, sind flach ausgebildet und von den äusseren Kammern 11, 21, 31, 41 sind Oeffnungen 15, 25, 35, 45 nach oben und Oeffnungen 16, 26, 36, 46 nach unten durch die Aussenflächen gebohrt (Fig. 3). Auf den Aussenflächen liegen Scheiben 50 und 60 mit Löchern 51 und 61. Die beiden Scheiben 50 und 60 sind mittels einer Welle 70 durch den Kreuzungspunkt der Zylinderachsen starr miteinander verbunden. Ein Gehäuse 76 umschliesst den gesamten Zylinderkörper 1 mit den beiden Scheiben 50 und 60, so dass eine obere Druckkammer 90 und eine untere Ausgleichskammer 92 gebildet werden. Die Druckkammer 90 ist über einen Anschluss 74 mit einem Hochdruckspeicher für Fluid unter Druck und die Ausgleichskammer 92 ist mit einem Anschluss 72 mit einem Niederdruckspeicher verbunden. Die inneren Kammern 12, 22, 32, 42 sind mit Flüssigkeit gefüllt.The outer surfaces of the cylinder body 1, which are parallel to the plane which contains the four axes of the cylinders, are flat and from the outer chambers 11, 21, 31, 41 are openings 15, 25, 35, 45 upwards and openings 16, 26, 36, 46 drilled down through the outer surfaces (Fig. 3). Disks 50 and 60 with holes 51 and 61 lie on the outer surfaces. The two disks 50 and 60 are rigidly connected to one another by means of a shaft 70 through the crossing point of the cylinder axes. A housing 76 encloses the entire cylinder body 1 with the two disks 50 and 60, so that an upper pressure chamber 90 and a lower compensation chamber 92 are formed. The pressure chamber 90 is connected via a connection 74 to a high-pressure store for fluid under pressure and the compensation chamber 92 is connected to a connection 72 to a low-pressure store. The inner chambers 12, 22, 32, 42 are filled with liquid.

Zur Erläuterung der Wirkungsweise wird noch Fig. 3 zur Hilfe genommen. Die Scheiben 50 und 60 haben demgemäss zwei Bohrungen 51a, 51b und 61 a, 61 b. Werden die Scheiben 50, 60 zusammen rotiert, so liegen diese Bohrungen über Oeffnungen in den äussern Kammern der Zylinder von sich gegenüberliegenden Zylindern. Gemäss Fig. 3 liegen die Bohrungen 51a, 51b über den Oeffnungen 15, 45 und die Bohrungen 61a, 61 über den Oeffnungen 26, 36.3 is used to explain the mode of operation. The disks 50 and 60 accordingly have two bores 51a, 51b and 61 a, 61 b. If the disks 50, 60 are rotated together, these bores lie over openings in the outer chambers of the cylinders of opposing cylinders. According to FIG. 3, the bores 51a, 51b lie over the openings 15, 45 and the bores 61a, 61 over the openings 26, 36.

Fluid unter Druck fliesst somit gemäss den Pfeilen A aus der Hochdruckkammer 90 durch die Bohrungen 51a, 51 b und die Oeffnungen 15, 45 in die äusseren Kammern 11, 41 und die Kolben 13, 43 werden in die in Fig. 1 dargestellte Lage gepresst. Dadurch, dass die Bohrungen 61a, 61 b in der Scheibe 60 und die Oeffnungen 26, 36 miteinander fluchten, kann das Fluid aus den äusseren Kammern 21, 31 in die Ausgleichskammer 92 abfliessen, so dass sich die Kolben 23, 33 unter dem Druck der Flüssigkeit in den inneren Kammern 12, 22, 32, 42 in die äussere, ebenfalls aus Fig. 1 ersichtliche Lage bewegen können.Fluid under pressure thus flows according to the arrows A from the high pressure chamber 90 through the bores 51a, 51b and the openings 15, 45 into the outer chambers 11, 41 and the pistons 13, 43 are pressed into the position shown in FIG. 1. Because the bores 61a, 61b in the disk 60 and the openings 26, 36 are aligned with one another, the fluid can flow out of the outer chambers 21, 31 into the compensator drain chamber 92 so that the pistons 23, 33 can move under the pressure of the liquid in the inner chambers 12, 22, 32, 42 into the outer position, also shown in FIG. 1.

Werden die Scheiben 50, 60 weiter rotiert, so geschieht dasselbe bei den benachbarten Zylindern. Die Kolbenstangen 14, 44 und 24, 34 führen damit paarweise bezüglich des Zentrums der Anordnung gleichgerichtete Bewegungen aus, deren Amplitude von der Menge des zugeführten Fluids und deren Frequenz von der Drehzahl der Scheibe abhängen.If the disks 50, 60 are rotated further, the same happens with the neighboring cylinders. The piston rods 14, 44 and 24, 34 thus perform movements in pairs with respect to the center of the arrangement, the amplitude of which depends on the amount of fluid supplied and the frequency of which depends on the speed of the disk.

Dies zeigt, dass nur mit einer Kraft zum Drehen der Scheiben und mit einer Kraft zur Erzeugung des Druckes im Fluid ein Schwingantrieb betrieben werden kann, und dass kein zusätzliches Steuergerät mit zusätzlichen drei bis vier Leitungen benötigt wird. Mit einem Versuchsaufbau konnten Schwingungen bis zu 10 mm Amplitude und Frequenzen bis zu 7 000 Hz erzeugt werden, wobei ein Druck im Fluid von 1-2 bar genügten.This shows that an oscillating drive can only be operated with a force for rotating the disks and with a force for generating the pressure in the fluid, and that no additional control device with additional three to four lines is required. With an experimental setup, vibrations of up to 10 mm amplitude and frequencies of up to 7,000 Hz could be generated, whereby a pressure in the fluid of 1-2 bar was sufficient.

Fig. 4 zeigt ein anderes Ausführungsbeispiel, bei dem das Zylinderpaar 100 mit gemeinsamer Achse und kreisförmigem Mantelquerschnitt ausgebildet ist. Das Zylinderpaar 100 ist von einem Steuerzylinder 101 umschlossen, der mit einem durch den Pfeil C angedeuteten Antrieb verbunden ist. Das Zylinderpaar 100 weist Oeffnungen 102, 103 auf. Diese Oeffnungen 102, 103 sind in Richtung der Mantellinien länglich ausgebildet und deren Längsachsen liegen in einer gemeinsamen Ebene durch die Zylinderachse und an entgegengesetzten Zylinderseiten.FIG. 4 shows another exemplary embodiment in which the pair of cylinders 100 is designed with a common axis and a circular jacket cross section. The cylinder pair 100 is enclosed by a control cylinder 101, which is connected to a drive indicated by the arrow C. The pair of cylinders 100 has openings 102, 103. These openings 102, 103 are elongated in the direction of the surface lines and their longitudinal axes lie in a common plane through the cylinder axis and on opposite cylinder sides.

Der Steuerzylinder 101 ist mit vier Löchern 104, 105,106,107 versehen, deren Achsen ebenfalls in einer gemeinsamen Ebene durch die Achse des Steuerzylinders 101 angeordnet sind. Diese Löcher sind paarweise gegeneinander versetzt angeordnet, derart, dass sie abwechselnd mit einer äusseren Partie der Oeffnungen 102, 103 und mit einer inneren Partie derselben fluchten.The control cylinder 101 is provided with four holes 104, 105, 106, 107, the axes of which are likewise arranged in a common plane through the axis of the control cylinder 101. These holes are arranged in pairs offset from one another in such a way that they are alternately aligned with an outer part of the openings 102, 103 and with an inner part thereof.

Der Steuerzylinder 101 ist von einem ebenfalls zylindrisch ausgebildeten Gehäuse 110 umfasst. Das Gehäuse 110 weist zwei ringförmige Stege 111, 112 auf, so dass zwischen dem Steuerzylinder 101 und dem Gehäuse 110 drei Ringkammern 113, 114, 115 ausgebildet sind. Die beiden aussenliegenden Ringkammern 113, 115 sind mit Leitungen 116, 117, 118 mit einer Fluidquelle für Fluid unter Druck verbunden und stellen daher die Hochdruckkammer des früher beschriebenen Beispiels dar. Die mittlere Ringkammer 114 ist über einen Abfluss 119 mit der Niederdruckseite der Fluidquelle verbunden und bildet daher die Ausgleichskammer gemäss dem zuerst beschriebenen Beispiel.The control cylinder 101 is encompassed by a likewise cylindrical housing 110. The housing 110 has two annular webs 111, 112, so that three annular chambers 113, 114, 115 are formed between the control cylinder 101 and the housing 110. The two outer annular chambers 113, 115 are connected by lines 116, 117, 118 to a fluid source for fluid under pressure and therefore represent the high-pressure chamber of the example described earlier. The middle annular chamber 114 is connected via a drain 119 to the low-pressure side of the fluid source and therefore forms the compensation chamber according to the example described first.

Die Löcher 104, 105, 106, 107 sind nun derart verteilt angeordnet, dass die äussere Kammer 124 des einen, durch einen Kolben 120 unterteilten Zylinders über die Oeffnung 102 und das Loch 104 mit der Hochdruckkammer 113 und die äussere Kammer 125 des anderen, durch einen Kolben 122 unterteilten Zylinders über die Oeffnung 103 und das Loch 107 mit der Ausgleichskammer 114 verbunden sind.The holes 104, 105, 106, 107 are now distributed such that the outer chamber 124 of the one cylinder divided by a piston 120 passes through the opening 102 and the hole 104 with the high-pressure chamber 113 and the outer chamber 125 of the other a piston 122 divided cylinder are connected to the compensation chamber 114 via the opening 103 and the hole 107.

Indem selbstverständlich auch hier die beiden zu einer gemeinsamen Kammer 126 zusammengefassten inneren Kammern der Zylinder mit Flüssigkeit gefüllt sind, bewirkt diese Anordnung in der dargestellten Phase eine Bewegung der beiden Kolben 120, 122 und daher auch der beiden Kolbenstangen 121, 123 nach rechts in der Zeichnung.Since the two inner chambers of the cylinders combined to form a common chamber 126 are of course also filled with liquid here, this arrangement causes the two pistons 120, 122 and therefore also the two piston rods 121, 123 to move to the right in the drawing in the phase shown .

Bei einer Drehung des Steuerzylinders 101 um 180° in Richtung des Pfeiles C wird die Hochdruckkammer 115 über das Loch 106 und die Oeffnung 103 mit der äusseren Kammer 125 und die Ausgleichskammer 103 über das Loch 105 und die Oeffnung 102 mit der äusseren Kammer 124 verbunden. Die beiden Kolben 120, 122 und die Kolbenstangen 121, 123 führen daher eine gegenläufige, nach links in der Zeichnung gerichtete Bewegung aus. Somit ergibt auch in diesem Beispiel eine Rotationsbewegung des Steuermittels, nämlich des Steuerkolbens 101, eine translatorische Bewegung der Kolbenstangen, wobei auch hier der Hub durch die Menge des ein- und ausfliessenden Fluids und die Frequenz durch die Drehzahl bestimmt sind.When the control cylinder 101 is rotated through 180 ° in the direction of arrow C, the high-pressure chamber 115 is connected to the outer chamber 125 via the hole 106 and the opening 103, and the compensation chamber 103 is connected to the outer chamber 124 via the hole 105 and the opening 102. The two pistons 120, 122 and the piston rods 121, 123 therefore perform an opposite movement, directed to the left in the drawing. Thus, in this example as well, a rotational movement of the control means, namely the control piston 101, results in a translatory movement of the piston rods, the stroke also being determined here by the amount of fluid flowing in and out and the frequency by the speed.

Selbstverständlich können in beiden Ausführungsbeispielen mehr Löcher in den Scheiben 50, 60 gemäss Fig. 1-3 oder mehr Löcher im Steuerzylinder 101 vorgesehen sein, um bei niedrigerer Drehzahl eine höhere Frequenz zu erzielen. Die Kolben 120, 122 im Ausführungsbeispiel nach Fig. 4 sind mit einer weichen Membran 131, 132 dichtend mit der Zylinderwand verbunden. Der Hub der Kolben 120, 122 ist daher durch die Abmessungen dieser Membranen begrenzt.Of course, in both exemplary embodiments, more holes can be provided in the disks 50, 60 according to FIGS. 1-3 or more holes in the control cylinder 101 in order to achieve a higher frequency at a lower speed. The pistons 120, 122 in the exemplary embodiment according to FIG. 4 are sealingly connected to the cylinder wall with a soft membrane 131, 132. The stroke of the pistons 120, 122 is therefore limited by the dimensions of these membranes.

Claims (8)

1. A vibrator having working! pistons displaceably guided in working chambers and pressurized fluid serving as a working medium, characterised in that the working chambers are formed by at least one pair of cylinders closed with respect to the outside, each cylinder being divided by one said working piston in an outer and inner chamber, that the working pistons are connected to each other, via the inner chambers, through a hydraulic fluid so that they transmit energy, and that the outer chambers have an axial passage passing therethrough for a sealingly guided piston rod and openings for the passage of the working fluid, and that at least in the region of the passages are provided control means bearing on the cylinders, to guide working fluid alternately and periodically in to one cylinder of the pair and from the other cylinder.
2. A vibrator according to ÕÌaÌmI 1, characterised in that two pairs of cylinders are provided crossing each other, in which the four cylinder axes lie in the same plane.
3. A vibrator according to Claim 2, characterised in that the outer walls of the cylinders form two surfaces parallel to the common plane of the cylinder axes and the openings for admission are arranged in the one surface and the openings for discharge are arranged in the other surface, that the control means are rotatable disks firmly connected to each other of which each sealingly bears on to respective one of said surfaces, and that the disks are provided with holes which may be aligned with the openings.
4. A vibrator according to Claim 3, characterised in that each disk has a least two holes situated diametrically opposite each other, and that the holes in one of the disks extend at 90° to the holes in the other disk.
5. A vibrator according to Claim 4, characterised in that the two disks are connected together by a shaft passing through the centre of the cylinder pairs.
6. A vibrator according to Claim 5, characterised in that said surfaces of the outer walls of the cylinders and the disks are arranged in respective fluid chambers.
7. A vibrator according to Claim 1, characterised in that the axes of the cylinder pairs form a straight line and that the outer walls of the cylinders form a circular cylinder.
8. A vibrator according to Claim 7, characterised in that the control means are a second circular cylinder and a third circular cylinder which surrounds everything and has three chambers, the chambers which are outer chambers in axial direction being connected together outside the third cylinder and being connected together and to a source of fluid, and that the second circular cylinder is arranged rotatably between the outer walls of the cylinder pair and the third circular cylinder and are provided with holes alignable with the openings, the openings being axially extending elongate holes which may be aligned with the holes which open in two of the three chambers.
EP82810015A 1981-02-06 1982-01-15 Vibrator Expired EP0058131B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82810015T ATE13259T1 (en) 1981-02-06 1982-01-15 VIBRATION GENERATOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH815/81 1981-02-06
CH81581 1981-02-06

Publications (3)

Publication Number Publication Date
EP0058131A2 EP0058131A2 (en) 1982-08-18
EP0058131A3 EP0058131A3 (en) 1982-08-25
EP0058131B1 true EP0058131B1 (en) 1985-05-15

Family

ID=4195837

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82810015A Expired EP0058131B1 (en) 1981-02-06 1982-01-15 Vibrator

Country Status (5)

Country Link
US (1) US4548123A (en)
EP (1) EP0058131B1 (en)
JP (1) JPS57146902A (en)
AT (1) ATE13259T1 (en)
DE (1) DE3263453D1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59180102A (en) * 1983-03-31 1984-10-13 Koubi Seiki Kk Hydraulic vibrator
CN109277653B (en) * 2018-10-10 2020-12-29 南京工程学院 Vibration-assisted arc milling spindle based on positive and negative pressure double cylinders
CN110332175A (en) * 2019-08-14 2019-10-15 百灵气动科技有限公司 A kind of four axis cylinders

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2564220A (en) * 1947-04-14 1951-08-14 Hamill William Wilson Control means for power units, including internal-combustion engines and gearboxes
NL145924B (en) * 1962-07-10 1975-05-15 Philips Nv EQUIPMENT CONTAINING A CYLINDER AND A MOVABLE PISTON WITH A DRIVE-COUPLED IN IT, WHERE THE SEAL BETWEEN THE PISTON AND THE CYLINDER IS DESIGNED AS A ROLLER DIAPHRAGM.
US3485139A (en) * 1968-07-01 1969-12-23 John M Sheesley Center bar rotary motor
US3678803A (en) * 1969-08-25 1972-07-25 Shell Oil Co Hydraulic sonic oscillator
DE2006879A1 (en) * 1970-02-14 1971-08-19 Krupp Gmbh Hydraulic vibrator
GB1330073A (en) * 1970-08-28 1973-09-12 Eckardt Ag J Pneumatic square wave generator
AT368607B (en) * 1971-02-24 1982-10-25 Sieke Helmut DEVICE FOR VIBRATING ADJUSTMENT OF A WORKING PISTON
US3702143A (en) * 1971-08-30 1972-11-07 Norman L Van Wagenen Kidney valve for fluid motor and other uses
DE2203278A1 (en) * 1972-01-25 1973-08-02 Bosch Gmbh Robert AXIAL PISTON MACHINE
US3810417A (en) * 1972-01-31 1974-05-14 H Sieke Method and apparatus for producing vibratory motion
DE2433765A1 (en) * 1974-07-13 1976-01-22 Monforts Fa A Fluidic oscillator with crystal registering frequency - in which oscillation crystal seals one outlet of the oscillator
DD115206A5 (en) * 1974-07-13 1975-09-12 Monforts Fa A Fluidic OSC
DE2821339C3 (en) * 1977-05-18 1982-03-04 Kabushiki Kaisha Takahashi Engineering, Tokyo Hydraulic piston-cylinder device for generating axial piston oscillation
DE2917830A1 (en) * 1979-05-03 1980-11-06 Tuenkers Maschinenbau Gmbh HYDRAULIC PULSE VIBRATION BEAR
US4350080A (en) * 1980-12-16 1982-09-21 Page John S Jr Apparatus to pump multiple wells

Also Published As

Publication number Publication date
EP0058131A2 (en) 1982-08-18
ATE13259T1 (en) 1985-06-15
JPS57146902A (en) 1982-09-10
US4548123A (en) 1985-10-22
EP0058131A3 (en) 1982-08-25
DE3263453D1 (en) 1985-06-20

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