EP0329208B1 - Hydraulically driven high-pressure cleaner - Google Patents

Hydraulically driven high-pressure cleaner Download PDF

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Publication number
EP0329208B1
EP0329208B1 EP89200131A EP89200131A EP0329208B1 EP 0329208 B1 EP0329208 B1 EP 0329208B1 EP 89200131 A EP89200131 A EP 89200131A EP 89200131 A EP89200131 A EP 89200131A EP 0329208 B1 EP0329208 B1 EP 0329208B1
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EP
European Patent Office
Prior art keywords
pressure cleaner
piston
pressure
water
oil
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EP89200131A
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German (de)
French (fr)
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EP0329208A2 (en
EP0329208A3 (en
Inventor
Ingo R. Dipl.-Ing. Friedrichs
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NERON SRL
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Neron Srl
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Classifications

    • BPERFORMING OPERATIONS; TRANSPORTING
    • B08CLEANING
    • B08BCLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B3/00Cleaning by methods involving the use or presence of liquid or steam
    • B08B3/02Cleaning by the force of jets or sprays
    • B08B3/026Cleaning by making use of hand-held spray guns; Fluid preparations therefor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/18Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • F04B1/184Cylindrical distribution members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26Control
    • F04B1/28Control of machines or pumps with stationary cylinders
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/1115Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members the movement of the pumping pistons in only one direction being obtained by a single-acting piston liquid motor, e.g. actuation in the other direction by spring means
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B08CLEANING
    • B08BCLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B2203/00Details of cleaning machines or methods involving the use or presence of liquid or steam
    • B08B2203/02Details of machines or methods for cleaning by the force of jets or sprays
    • B08B2203/0205Bypass pressure relief valves
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B08CLEANING
    • B08BCLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B2203/00Details of cleaning machines or methods involving the use or presence of liquid or steam
    • B08B2203/02Details of machines or methods for cleaning by the force of jets or sprays
    • B08B2203/0294Wobbling swash plates for high pressure cleaners

Definitions

  • the invention relates to a hydraulically driven high-pressure cleaner with at least three pistons loaded with hydraulic oil on one side, which on the other side act in a continuous manner on a second liquid to be displaced, with a synchronizing rod and a rotating device having a swash ring, the rotating device being one Control drives.
  • US-A-3 133 503 shows an oil hydraulic pressure booster with a piston, a synchronizing rod, a rotator and a control and which further discloses that the control is driven by the rotator, the rotation of which is caused by the axial movement of the pistons.
  • high-pressure cleaners which contain a plurality of hydraulic pistons which drive a control in the center and from there a multiplicity of water pistons which are connected to the hydraulic pistons. Since the use of external rubber seals to seal the pistons is required, one becomes large Installation diameter required. Since the control must be arranged in such cases between the oil-hydraulic and the water-loaded piston surface, the radially required installation space is very large, especially since it increases square with the radius; the longitudinal installation space is also increased as a multiplier of the stroke required as a result of the additional installation space, which leads overall to a large weight and volume of the machine.
  • the invention has for its object to provide a pressure washer that is extremely light and compact, yet reliable and which allows easy use with forklifts, tractors, construction machines, trucks with on-board hydraulics, concrete mixers, etc.
  • this object is achieved in that the rotating device has a perforated disk, that the synchronizing rod is arranged on each driving oil side and against the piston side of the hydraulically driven piston facing the displacing fluid, the synchronizing rod being positively and movably connected to the rotatably mounted perforated disk in the swashplate so that it drives the axial movement of the pistons in a rotary movement of the Swash rings is implemented, the control unit controlling the hydraulic oil to and from the pistons so that their axial movement is generated.
  • the rotating device (9-12) and the control (22, 51) can be radially enlarged considerably and housed in a freely available space which is usefully formed by the common circumferential circle of all pistons, including their seals.
  • you can in turn the piston-cylinder-seal arrangements are placed next to each other as possible, so that a large rotating device (9-12) and control (22, 51) can be freely designed in such a way that the high synchronization forces are absorbed reliably.
  • the axial forces driving the rotating device (9-12) and control (22, 51) occur mainly as pulling forces only in one working direction, so that dangerous alternating forces are avoided and the machine life is thereby considerably increased.
  • the machine can be arranged so compactly with all the internal parts so close together that all oil-hydraulic and water-side control elements can be accommodated so close together in the cylinder block (1) or valve block (50) that external piping, connecting pieces, assembly arrangements etc. are avoided in favor of a totally integrated design.
  • the overall result is that the machine according to the invention is so compact, light, and yet reliable that simple work with forklifts, agricultural tractors, construction machinery, trucks. With working hydraulics, concrete mixers etc. is possible as a small and handy implement.
  • Perforated disc (9) is rotatably supported in the swash ring (12) by means of an inner bearing (11) which is held by circlips (16, 17).
  • Swash ring (12) on the other hand, is rotatably held on the outside by means of an outer bearing (13) between the cylinder block (1) and cover (14), and on the inside by means of a locking ring (15).
  • the swash ring (12) is set in rotary motion because of its inclined surface inclined to the left relative to the axis of rotation, which on the drive shaft (19) by means of bolts (20) and from there to the control (22) by means of bolts (21) is transmitted.
  • suction water (30) is drawn into the left-hand cylinder chambers via suction check valves (32) as soon as the piston (2) moves to the right. From there, the water is displaced to the outlet (34) via pressure check valves (33) as soon as the piston (2) is pushed to the left in the direction of the pressure and suction valves (32, 33). Since the driving hydraulic oil (23) is continuously fed into the machine, its inner parts also move continuously, whereby the pressurized water is also continuously displaced, preferably preferably by a number of three pistons (2), to the outlet (34).
  • a thrust washer (10) must be provided which e.g. is held by the locking ring (18) and tumbles together with the perforated disc (9).
  • a ventilation duct (5) can be provided which releases any leakage into the atmosphere.
  • a pressure relief and / or unloader valve can be provided.
  • the pistons (2) and synchronizing rods (6) can also be connected by a radially and angularly movable joint in order to compensate for manufacturing tolerances and deformations.
  • the piston (2) can remain free of lateral forces, so that a "floating" piston arrangement is possible, i.e. the pistons are only guided in the seals (3, 4) and / or relatively narrow guides of the cylinder block (1) and / or guide rings located therein.
  • controller (22) can be replaced by any other controller, e.g. described in: "2nd Fluid Power Symposium, January 1971, Paper E4, BHRA, Cranfield, Bedford, England.”
  • Fig. 3 shows another embodiment of the invention, according to which the control (22) is replaced by a mushroom head (51), which is balanced by a compensating head (52) and sealed in perforated disc (9) by means of seals (53, 54) and is pressed onto its counter surface by compression spring (55).
  • Figure 3 further shows an oil unloader (61-64) controlled by the water pressure spool system (70-74).
  • ball (62) can also be made to work in the opposite direction, i.e. by moving the ball seat to the other side of the ball.
  • ball (62) can also be made to work in the opposite direction, i.e. by moving the ball seat to the other side of the ball.
  • other directional control valves with piston tappets instead of balls can also be used.
  • piston axes of the machine according to the invention do not have to be parallel, but can also be arranged on a conical pitch circle (cone shell).
  • water-side piston part and the oil-side piston part can be completely separate, but can also be made of one piece and coated.
  • the water-side piston part can be sealed by two soft seals, the space between which is connected to the suction side. This can also be done on the oil side.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Die Erfindung betrifft einen hydraulisch angetriebenen Hochdruckreiniger mit wenigstens drei auf ihrer einen Seite mit Hydrauliköl beaufschlagten Kolben, die auf ihrer anderen Seite auf eine zweite und zu verdrängende Flüssigkeit in kontinuierlicher Arbeitsweise wirken, mit einer Synchronisierstange und einer einen Taumelring aufweisenden Dreheinrichtung, wobei die Dreheinrichtung eine Steuerung antreibt.The invention relates to a hydraulically driven high-pressure cleaner with at least three pistons loaded with hydraulic oil on one side, which on the other side act in a continuous manner on a second liquid to be displaced, with a synchronizing rod and a rotating device having a swash ring, the rotating device being one Control drives.

Die US-A-3 133 503 zeigt einen ölhydraulischen Druckverstärker mit einem Kolben, einer Synchronisierstange, einer Dreheinrichtung und einer Steuerung und welche ferner offenbart, daß die Steuerung von der Dreheinrichtung angetrieben wird, deren Drehung durch die Axialbewegung der Kolben verursacht wird.US-A-3 133 503 shows an oil hydraulic pressure booster with a piston, a synchronizing rod, a rotator and a control and which further discloses that the control is driven by the rotator, the rotation of which is caused by the axial movement of the pistons.

Desweiteren sind Hochdruckreiniger bekannt, die eine Mehrzahl von Hydraulikkolben beinhalten, die mittig eine Steuerung antreiben und von dort aus eine Vielzahl von Wasserkolben, die mit den Hydraulikkolben verbunden sind. Da die Verwendung von außenliegenden Gummidichtungen zur Abdichtung der Kolben erforderlich ist, wird ein großer Einbaudurchmesser benötigt. Da die Steuerung in solchen Fällen zwischen der ölhydraulisch und der wasserseitig beaufschlagten Kolbenfläche angeordnet werden muß, ist der radial erforderliche Einbauraum sehr groß, zumal er quadratisch mit dem Radius steigt; auch der longitudinale Einbauraum wird vergrößert als Vervielfacher des infolge zusätzlichen Einbauraums benötigten Hubes, was insgesamt zu einem großen Gewicht und Volumen der Maschine führt. Diese Probleme werden besonders klar, wenn die Synchronisierkräfte ermittelt werden, die z.B. aus Kolbenreibung, Dichtungsreibung sowie anderer Reibung, wie z.B. von Lagern und von Hydraulikkräften herrühren, die zur Überwindung des in den Totpunkten im Zylinder eingeschlossenen Kompressionsöls erforderlich sind. Als allgemeiner Erfahrungswert hat sich herausgestellt, daß die Dreheinrichtung und ihre Lager und/oder gleitenden Teile sehr groß im Verhältnis zu den Kolben- und Dichtungsdurchmessern ausgelegt werden müssen, wobei eine weitere mechanische Verstärkung bei Wechselbeanspruchungen erforderlich ist. Insgesamt wurden noch keine gattungsmäßigen Geräte in Serie produziert, sondern nur "konventionelle Bauarten", d.h. Geräte mit Hydraulikmotor, hydraulischen Steuerungselementen, Kupplungen, Wasserpumpe, wasserseitigen Steuerungseinrichtungen, Montagerahmen, Abdeckhaube etc., denn die technischen Schwierigkeiten mit bisherigen, gattungsgemäßen Geräten waren zu groß.Furthermore, high-pressure cleaners are known which contain a plurality of hydraulic pistons which drive a control in the center and from there a multiplicity of water pistons which are connected to the hydraulic pistons. Since the use of external rubber seals to seal the pistons is required, one becomes large Installation diameter required. Since the control must be arranged in such cases between the oil-hydraulic and the water-loaded piston surface, the radially required installation space is very large, especially since it increases square with the radius; the longitudinal installation space is also increased as a multiplier of the stroke required as a result of the additional installation space, which leads overall to a large weight and volume of the machine. These problems become particularly clear when the synchronizing forces are determined, which arise, for example, from piston friction, sealing friction and other friction, such as, for example, from bearings and from hydraulic forces which are required to overcome the compression oil enclosed in the dead center in the cylinder. As a general empirical value, it has been found that the rotating device and its bearings and / or sliding parts have to be designed very large in relation to the piston and seal diameters, a further mechanical reinforcement being required in the case of alternating loads. In total, no generic devices have yet been produced in series, but only "conventional designs", ie devices with hydraulic motors, hydraulic control elements, couplings, water pumps, water-side control devices, mounting frames, covers etc., because the technical difficulties with previous, generic devices were too great .

Der Erfindung liegt die Aufgabe zugrunde, einen Hochdruckreiniger zu schaffen, der äußerst leicht sowie kompakt gestaltet und trotzdem betriebssicher ist und welcher einen einfachen Einsatz mit Gabelstaplern, Ackerschleppern, Baumaschinen, Lastkraftwagen mit Bordhydraulik, Betonmischern usw. ermöglicht.The invention has for its object to provide a pressure washer that is extremely light and compact, yet reliable and which allows easy use with forklifts, tractors, construction machines, trucks with on-board hydraulics, concrete mixers, etc.

Die Lösung dieser Aufgabe besteht nach der Erfindung darin, daß die Dreheinrichtung eine Lochscheibe aufweist, daß die Synchronisierstange auf jeder antreibenden Ölseite und entgegen der dem verdrängenden Fluid zugewandten Kolbenseite eines hydraulisch angetriebenen Kolbens angeordnet ist, wobei die Synchronisierstange formschlüssig und beweglich mit der drehfähig im Taumelring gelagerten Lochscheibe diese antreibend so verbunden ist, daß die Axialbewegung der Kolben in eine Drehbewegung des Taumelrings umgesetzt wird, wobei die Steuerung das Hydrauliköl so zu den Kolben und von diesen wieder wegsteuert, daß deren Axialbewegung erzeugt wird.According to the invention, this object is achieved in that the rotating device has a perforated disk, that the synchronizing rod is arranged on each driving oil side and against the piston side of the hydraulically driven piston facing the displacing fluid, the synchronizing rod being positively and movably connected to the rotatably mounted perforated disk in the swashplate so that it drives the axial movement of the pistons in a rotary movement of the Swash rings is implemented, the control unit controlling the hydraulic oil to and from the pistons so that their axial movement is generated.

Vorteilhafte Ausführungsformen der Erfindung sind durch die in den Patentansprüchen 2 bis 14 angegebenen Merkmale gekennzeichnet.Advantageous embodiments of the invention are characterized by the features specified in claims 2 to 14.

Im Ergebnis können durch diese Anordnung die Dreheinrichtung (9-12) und die Steuerung (22,51) radial erheblich vergrößert und in einem frei verfügbaren Raum untergebracht werden, der sinnvollerweise vom gemeinsamen Umfangskreis aller Kolben einschließlich derer Dichtungen gebildet wird. Als Ergebnis daraus wiederum können die Kolben-Zylinder-Dichtungs-Anordnungen nächstmöglich aneinander gelegt werden, so daß eine große Dreheinrichtung (9-12) und Steuerung (22,51) konstruktiv frei gestaltbar so untergebracht werden können, daß die hohen Synchronisierkräfte betriebssicher aufgenommen werden.As a result of this arrangement, the rotating device (9-12) and the control (22, 51) can be radially enlarged considerably and housed in a freely available space which is usefully formed by the common circumferential circle of all pistons, including their seals. As a result, you can in turn the piston-cylinder-seal arrangements are placed next to each other as possible, so that a large rotating device (9-12) and control (22, 51) can be freely designed in such a way that the high synchronization forces are absorbed reliably.

Als weiteres Ergebnis des Erfindungsgedankens treten die die Dreheinrichtung (9-12) und Steuerung (22,51) antreibenden Axialkräfte hauptsächlich nur in einer Arbeitsrichtung als Zugkräfte auf, so daß gefährliche Wechselkräfte vermieden werden und dadurch die Maschinenlebensdauer erheblich vergrößert wird.As a further result of the concept of the invention, the axial forces driving the rotating device (9-12) and control (22, 51) occur mainly as pulling forces only in one working direction, so that dangerous alternating forces are avoided and the machine life is thereby considerably increased.

Als nochmals weiteres Ergebnis kann die Maschine so kompakt mit allen Innenteilen so dicht beieinander liegend angeordnet werden, daß alle ölhydraulischen und wasserseitigen Steuerungselemente so dicht beieinander im Zylinderblock (1) bzw. Ventilblock (50) untergebracht werden können, daß externe Verrohrungen, Anschlußstücke, Aufbauanordnungen usw. zugunsten einer total integrierten Bauweise vermieden werden.As a further result, the machine can be arranged so compactly with all the internal parts so close together that all oil-hydraulic and water-side control elements can be accommodated so close together in the cylinder block (1) or valve block (50) that external piping, connecting pieces, assembly arrangements etc. are avoided in favor of a totally integrated design.

Im Gesamtergebnis baut die erfindungsgemäße Maschine so kompakt, leicht und trotzdem betriebssicher, daß ein einfacher Arbeitseinsatz mit Gabelstaplern, Ackerschleppern, Baumaschinen, Lkw. mit Arbeitshydraulik, Betonmischern usw. als kleines und handliches Arbeitsgerät möglich wird.The overall result is that the machine according to the invention is so compact, light, and yet reliable that simple work with forklifts, agricultural tractors, construction machinery, trucks. With working hydraulics, concrete mixers etc. is possible as a small and handy implement.

Die beigefügten Zeichnungen erläutern die Erfindung und zeigen:

Fig. 1
einen Längsschnitt durch einen erfindungsgemäßen Hochdruckreiniger;
Fig. 2
einen Schnitt längs der Linie II-II der Fig. 1;
Fig. 3
einen Längsschnitt einer alternativen Ausführung des Erfindungsgedankens;
Fig. 4
einen Gewichts- und Volumenvergleich einer konventionellen Maschine im Vergleich mit einem realisierten, erfindungsgemäßen, hydraulisch angetriebenen Hochdruckreiniger
Der in Fig. 1 gezeigte, erfindungsgemäße Hochdruckreiniger besteht aus einem Zylinderblock (1), in dem ölhydraulisch angetriebene Kolben (2) axial beweglich angeordnet sind. Drucköl (23) wird in die Einlaßöffnung (24) und über einen Verbindungskanal (25) zu einer Steuerung (22) geleitet, d.h. über deren Umfangskanal (26), eine Verbindungsbohrung (27) zur Druckniere (28) und von dort zu einer Steuerbohrung (29) und von dort in den Zylinderraum zwischen dem rechten Ende des Kolbens (2) und dem linken Ende der Synchronisierstange (6).The accompanying drawings illustrate the invention and show:
Fig. 1
a longitudinal section through a pressure washer according to the invention;
Fig. 2
a section along the line II-II of Fig. 1;
Fig. 3
a longitudinal section of an alternative embodiment of the inventive concept;
Fig. 4
a weight and volume comparison of a conventional machine in comparison with a realized, hydraulically driven high-pressure cleaner according to the invention
The high-pressure cleaner according to the invention shown in FIG. 1 consists of a cylinder block (1) in which pistons (2) driven by oil hydraulics are arranged so as to be axially movable. Pressure oil (23) is fed into the inlet opening (24) and via a connecting channel (25) to a controller (22), ie via its peripheral channel (26), a connecting hole (27) to the pressure kidney (28) and from there to a control hole (29) and from there into the cylinder space between the right end of the piston (2) and the left end of the synchronizing rod (6).

Als Ergebnis dieser Anordnung bewegt sich bei Einleitung von Drucköl der Kolben (2) nach links, erzeugt über Synchronisierstange (6) eine auf die Dreheinrichtung (9-12) wirkende Zugkraft, wodurch der Taumelring (12) infolge seiner einseitigen Schrägfläche in Drehbewegung versetzt wird.As a result of this arrangement, when pressure oil is introduced, the piston (2) moves to the left, generates a pulling force on the rotating device (9-12) via the synchronizing rod (6), causing the swash ring (12) to rotate due to its one-sided inclined surface .

Lochscheibe (9) ist drehfähig im Taumelring (12) gelagert mittels eines inneren Lagers (11), das durch Sicherungsringe (16,17) gehalten wird. Taumelring (12) wird andererseits mittels eines äußeren Lagers (13) drehfähig zwischen Zylinderblock (1) und Deckel (14) außen gehalten, sowie innen mittels Sicherungsring (15). Sobald die Synchronisierstange (9) unter Zugkraft steht, wird der Taumelring (12) wegen seiner links gegenüber der Drehachse geneigten Schrägfläche in Drehbewegung versetzt, die auf Antriebswelle (19) mittels Bolzen (20) und von dort auf die Steuerung (22) mittels Bolzen (21) übertragen wird.Perforated disc (9) is rotatably supported in the swash ring (12) by means of an inner bearing (11) which is held by circlips (16, 17). Swash ring (12), on the other hand, is rotatably held on the outside by means of an outer bearing (13) between the cylinder block (1) and cover (14), and on the inside by means of a locking ring (15). As soon as the synchronizing rod (9) is under tensile force, the swash ring (12) is set in rotary motion because of its inclined surface inclined to the left relative to the axis of rotation, which on the drive shaft (19) by means of bolts (20) and from there to the control (22) by means of bolts (21) is transmitted.

Sobald Drucköl (23) in Einlaß (24) und über Steuerung (22) zur Ölseite von Kolben (2) geleitet wird, ziehen Kolben (2) und Synchronisierstange (6) an Lochscheibe (9), die dadurch zum Taumeln gebracht wird und dadurch wiederum Taumelring (12) dreht. Da diese Drehbewegung über Antriebswelle (19) auf die Steuerung (22) übertragen wird, gleitet Druckniere (28) über die Steuerbohrungen (29), so daß die Zylinder nacheinander mit Drucköl versorgt werden.As soon as pressure oil (23) is fed into the inlet (24) and via the control (22) to the oil side of the piston (2), the piston (2) and the synchronizing rod (6) pull on the perforated disc (9), which causes it to wobble and thereby turn swash ring (12). Since this rotary movement is transmitted to the control (22) via the drive shaft (19), the pressure kidney (28) slides over the control bores (29) so that the cylinders are supplied with pressure oil in succession.

Da entgegenliegende Steuerbohrungen (29) entgegenliegende Zylinder jeweils zur Tankniere (40) verbinden, wird das Öl über Verbindungsbohrung (41), Taumelraum (42) und Verbindungskanal (43) zum Auslaß (44) geleitet, von wo es als Tanköl (45) wieder zum Tank fließt.Since opposing control bores (29) connect opposing cylinders to the tank kidney (40), the oil is passed through the connecting bore (41), swash chamber (42) and connecting duct (43) to the outlet (44), from where it is used as tank oil (45) flows to the tank.

Wegen des Hubes einer Mehrzahl Von Kolben (2) wird Saugwasser (30) in die linken Zylinderräme über Saug-Rückschlagventile (32) gesaugt, sobald sich Kolben (2) nach rechts bewegt. Das Wasser wird von dort zum Auslaß (34) über Druck-Rückschlagventile (33) verdrängt, sobald der Kolben (2) nach links in Richtung der Druck- und Saugventile (32,33) geschoben wird. Da das antreibende Hydrauliköl (23) kontinuierlich in die Maschine hineingeleitet wird, bewegen sich deren Innenteile ebenfalls kontinuierlich, wodurch das Druckwasser gleichfalls kontinuierlich vorzugsweise durch eine Anzahl von drei Kolben (2) zum Auslaß (34) verdrängt wird.Because of the stroke of a plurality of pistons (2), suction water (30) is drawn into the left-hand cylinder chambers via suction check valves (32) as soon as the piston (2) moves to the right. From there, the water is displaced to the outlet (34) via pressure check valves (33) as soon as the piston (2) is pushed to the left in the direction of the pressure and suction valves (32, 33). Since the driving hydraulic oil (23) is continuously fed into the machine, its inner parts also move continuously, whereby the pressurized water is also continuously displaced, preferably preferably by a number of three pistons (2), to the outlet (34).

Es ist offensichtlich, daß wegen der taumelnden Schieflage von Lochscheibe (9) während einer Umdrehung die Köpfe der Synchronisierstangen (6) die Form von Teilkugeln (8) haben müssen, die durch Sicherungsringe (48) auf den Synchronisierstangen (6) gehalten werden. Diese Teilkugeln (8) werden wiederum gelenkig in Kugelkalotten (7) gehalten, die ein wenig auf Lochscheibe (9) gleiten, um einen geringfügigen Radialweg auf Grund des Taumelwinkels von Lochscheibe (9) auszugleichen.It is obvious that because of the wobbling of the perforated disc (9) during one revolution, the heads of the synchronizing rods (6) must have the shape of partial balls (8) which are held on the synchronizing rods (6) by locking rings (48). These partial balls (8) are in turn held in an articulated manner in spherical caps (7) which slide a little on the perforated disc (9) in order to compensate for a slight radial path due to the wobble angle of the perforated disc (9).

Es ist ferner offensichtlich, daß die Stirnflächen (46) der Synchronisierstangen (6) den Taumelring (12) bei hoher Geschwindigkeit nicht berühren dürfen, um ein Festbremsen zu vermeiden. Deswegen muß erfindungsgemäß eine Druckscheibe (10) vorgesehen werden, die z.B. durch Sicherungsring (18) gehalten wird und gemeinsam mit Lochscheibe (9) taumelt.It is also evident that the end faces (46) of the synchronizing rods (6) must not touch the swash ring (12) at high speed in order to avoid braking. Therefore, according to the invention, a thrust washer (10) must be provided which e.g. is held by the locking ring (18) and tumbles together with the perforated disc (9).

Um Durchmischungen von Wasser und Öl zu vermeiden, kann ein Entlüftungskanal (5) vorgesehen werden, der eine eventuelle Leckage in die Atmosphäre entläßt. Natürlich kann ein Druckbegrenzungs und/oder Unloaderventil vorgesehen werden.In order to avoid mixing water and oil, a ventilation duct (5) can be provided which releases any leakage into the atmosphere. Of course, a pressure relief and / or unloader valve can be provided.

Weiter können die Kolben (2) und Synchronisierstangen (6) durch ein radial und winklig bewegliches Gelenk verbunden werden, um Fertigungstoleranzen und Verformungen auszugleichen.The pistons (2) and synchronizing rods (6) can also be connected by a radially and angularly movable joint in order to compensate for manufacturing tolerances and deformations.

Falls die Synchronisierstangen (6) zur Aufnahme von Radialkräften ausgestaltet sind, die aus der Schrägstellung von Lochscheibe (9) resultieren, kann Kolben (2) frei von Seitenkräften verbleiben, so daß eine "schwimmende" Kolbenanordnung möglich wird, d.h. die Kolben werden nur in den Dichtungen (3,4) und/oder relativ schmalen Führungen des Zylinderblocks (1) und/oder darin befindlichen Führungsringen geführt.If the synchronizing rods (6) are designed to absorb radial forces resulting from the inclined position of the perforated disc (9), the piston (2) can remain free of lateral forces, so that a "floating" piston arrangement is possible, i.e. the pistons are only guided in the seals (3, 4) and / or relatively narrow guides of the cylinder block (1) and / or guide rings located therein.

Selbstverständlich kann die Steuerung (22) durch eine beliebige andere Steuerung ersetzt werden, wie z.B. beschrieben in: "2nd Fluid Power Symposium, January 1971, Paper E4, BHRA, Cranfield, Bedford, England."Of course, the controller (22) can be replaced by any other controller, e.g. described in: "2nd Fluid Power Symposium, January 1971, Paper E4, BHRA, Cranfield, Bedford, England."

Fig. 3 zeigt eine andere Ausführung der Erfindung, wonach die Steuerung (22) durch einen Pilzkopf (51) ersetzt ist, der durch einen Ausgleichskopf (52) balanciert wird und in Lochscheibe (9) mittels Dichtungen (53,54) abgedichtet ist sowie durch Druckfeder (55) auf seine Gegenfläche gedrückt wird.Fig. 3 shows another embodiment of the invention, according to which the control (22) is replaced by a mushroom head (51), which is balanced by a compensating head (52) and sealed in perforated disc (9) by means of seals (53, 54) and is pressed onto its counter surface by compression spring (55).

Der Direktkontakt von Stirnflächen (46) der Synchronisierstangen (6) gegenüber der Druckscheibe (10) ist ersetzt durch flächig aufliegende Teilkugeln (56), welche eventuelle Druckschläge flächig auf Druckscheibe (10) verteilen. Kolben (2) ist in diesem Falle in einen Ölkolben (57) und einen Wasserkolben (58) abgestuft, um den Wasserdruck gegenüber dem Öldruck entsprechend den Flächenverhältnissen zu verstärken. Das Druckbegrenzungs- oder Unloaderventil (38) ist ersetzt durch ein Druckregelventil (59).The direct contact of end faces (46) of the synchronizing rods (6) with respect to the thrust washer (10) is replaced by flat partial balls (56) which distribute any pressure surges over the thrust washer (10). In this case, the piston (2) is stepped into an oil piston (57) and a water piston (58) in order to increase the water pressure compared to the oil pressure in accordance with the surface conditions. The pressure relief or unloader valve (38) is replaced by a pressure control valve (59).

Fig. 3 zeigt weiter einen Öl-Unloader (61-64), der durch das Wasserdruck-Steuerkolbensystem (70-74) gesteuert wird.Figure 3 further shows an oil unloader (61-64) controlled by the water pressure spool system (70-74).

Bei Entlastung wirkt der Öldruck von Kammer (65) auf eine Kugel (62), die entgegen der Kraft von Feder (71) öffnet, wobei die Kraftübertragung über den Wasserkolben (72) und Ölkolben (63) erfolgt, so daß der Ölstrom weitgehend drucklos in Kanal (67) entlädt. Wenn der Wasserdruck steigt, addiert sich die resultierende Kraft des Wasserkolbens (72) zur Federkraft so, daß die Kugel (62) stärker auf ihren Sitz im Einsatz (61) gepreßt wird, bis die Kugel bei Höchstdruck völlig schließt. Wenn das Druckwasser (75) abgesperrt wird (z.B. durch Loslassen einer Spritzpistole), öffnet Druckregelventil (59), so daß Hochdruck im Auslaß (75) und Kammer(76) gehalten wird, während Kammer 77 entspannt wird. Dadurch verbleibt Wasserkolben (72) in seiner linken Position entgegen der Kraft von Feder (71), und volle Ölentlastung tritt ein, da sich die Kugel (62) frei nach links bewegen kann.When the pressure is released, the oil pressure from chamber (65) acts on a ball (62) which opens against the force of spring (71), the force being transmitted via the water piston (72) and oil piston (63), so that the oil flow is largely depressurized discharges into channel (67). When the water pressure increases, the resulting force of the water piston (72) is added to the spring force so that the ball (62) is pressed more firmly into its seat in the insert (61) until the ball closes completely at maximum pressure. When the pressurized water (75) is shut off (e.g. by releasing a spray gun), the pressure control valve (59) opens so that high pressure is maintained in the outlet (75) and chamber (76) while chamber 77 is depressurized. As a result, the water piston (72) remains in its left position against the force of the spring (71) and full oil relief occurs, since the ball (62) can move freely to the left.

Es muß ausdrücklich festgestellt werden, daß Kugel (62) auch entgegengesetzt zum Arbeiten gebracht werden kann, d.h. indem der Kugelsitz auf die andere Seite der Kugel verlegt wird. Natürlich können auch andere Wegeventile mit Kolbenstößel statt Kugel zum Einsatz gebracht werden.It must be expressly stated that ball (62) can also be made to work in the opposite direction, i.e. by moving the ball seat to the other side of the ball. Of course, other directional control valves with piston tappets instead of balls can also be used.

Fig. 4 zeigt schließlich einen Vergleich konventioneller Maschinen hinsichtlich Größe bzw. Bauvolumen und Gewicht W2 gegenüber dem erfindungsgemäßen Gerät.4 finally shows a comparison of conventional machines with regard to size or construction volume and weight W2 compared to the device according to the invention.

Es ist offensichtlich, daß konventionelle Maschinen bekannter Bauart nicht allgemein auf vorgenannten Fahrzeugen verwendet werden können wie z.B. Gabelstapler, Baumaschinen, Lkw usw.It is obvious that conventional machines of known design cannot be used generally on the aforementioned vehicles, e.g. Forklifts, construction machinery, trucks, etc.

Ferner ist offensichtlich, daß die Kolbenachsen der erfindungsgemäßen Maschine keinesfalls parallel liegen müssen, sondern auch auf einem konischen Teilkreis (Kegelmantel) angeordnet sein können.Furthermore, it is obvious that the piston axes of the machine according to the invention do not have to be parallel, but can also be arranged on a conical pitch circle (cone shell).

Auch ist es selbstverständlich, daß der wasserseitige Kolbenteil und der ölseitige Kolbenteil vollständig getrennt ausgeführt, aber auch aus einem Stück sowie beschichtet sein können. Der wasserseitige Kolbenteil kann durch zwei Weichdichtungen abgedichtet sein, deren Zwischenraum mit der Saugseite verbunden ist. Dieses kann auch ölseitig durchgeführt werden.It goes without saying that the water-side piston part and the oil-side piston part can be completely separate, but can also be made of one piece and coated. The water-side piston part can be sealed by two soft seals, the space between which is connected to the suction side. This can also be done on the oil side.

Natürlich können alle bekannten Hydraulikelemente wie Druckbegrenzungsventile, Mengenregler, Ölunloader, Rückschlagventile, Dichtungen usw. zusammen mit dem erfindungsgemäßen Hochdruckreiniger oder in diesem selbst eingesetzt werden. Dasselbe betrifft die wasserseitigen Steuerelemente.Of course, all known hydraulic elements such as pressure limiting valves, flow regulators, oil unloaders, check valves, seals etc. can be used together with the high-pressure cleaner according to the invention or in this itself. The same applies to the water-side controls.

Claims (14)

  1. Hydraulically driven high-pressure cleaner comprising at least three pistons (2) on one side being impinged with hydraulic oil and on their other side in continuous operation acting on a second liquid to be displaced, a synchronization rod (6) and a turning means (9 to 12) including a wobble ring (12), wherein the turning means (9 to 12) drives a control (22 or 51, resp.), characterized in that said turning means (9 to 12) comprises a perforated disc (9), that said synchronization rod (6) is arranged on each driving oil side and oppositely to the piston side facing the fluid to be displaced, of an hydraulically operated piston, wherein said synchronization rod (6) has positive fit and is movably connected to said perforated disc (9) rotatably supported in said wobble ring (12) and driving it such that the axial movement of said piston (2) is converted into a rotational movement of said wobble ring (12), wherein said control (22 or 51, resp.) directs the hydraulic oil to said piston (2) and again away from it such that the axial movement thereof is caused.
  2. High-pressure cleaner as defined in claim 1, characterized in that a hinge is disposed between said piston (2) and its synchronization rod (6) such that a slight radial and angular movement becomes possible between said pistion (2) and said synchronization rod (6).
  3. High-pressure cleaner as defined in one of claims 1 to 2, characterized in that said piston (2) has different diameters at the water-side end and the other oil-side end thereof.
  4. High-pressure cleaner as defined in one of clams 1 to 3, characterized in that said piston (2) is guided by its seals (3, 4) and/or the support rings thereof.
  5. High-pressure cleaner as defined in one of claims 1 to 3, characterized in that at least a first fluid-side of said piston (2) is sealed by at least two seals of which at least one clearing is connected to the low-pressure area of the first liquid.
  6. High-pressure cleaner as defined in one of claims 1 to 5, characterized in that the central lines of said pistons (2) lie on a cone envelope.
  7. High-pressure cleaner as defined in one of claims 3 to 6, characterized in that in the water-side valve block a water-controlled water control piston (72) is arranged such that it actuates an hydraulic Valve (61 to 64) disposed in said cylinder block (1).
  8. High-pressure cleaner as defined in claim 7, characterized in that said hydraulic valve (61 to 64) at least to a high degree leaves the hydraulic oil without pressure as long as high water pressure only is present at the outlet (75).
  9. High-pressure cleaner as defined in one of claims 3 to 8, characterized in that all hydraulic and/or all water-side valve elements are arranged within the housing of said high-pressure cleaner.
  10. High-pressure cleaner as defined in one of claims 1 to 9, characterized in that the free ends of said synchronization rods (6) each comprise a partial ball (56).
  11. High-pressure cleaner as defined in one of claims 1 to 10, characterized in that said wobble ring (12) includes an axis of rotation in parallel to the outside diameter and/or a axis of rotation inclined with respect thereto.
  12. High-pressure cleaner as defined in one of claim 1 to 11, characterized in that said wobble ring (12) touches at least one outside bearing and at least one inside bearing.
  13. High-pressure cleaner as defined in one of claims 1 to 12, characterized in that a stop disc (10) is arranged between the free end of said synchronization rods (6) and the inside bearing (11) of said wobble ring (12).
  14. High-pressure cleaner as defined in one of claims 7 to 8, characterized in that said hydraulic valve (61 to 64) closes in case of high pressure acting only in the water outlet (75).
EP89200131A 1988-01-25 1989-01-24 Hydraulically driven high-pressure cleaner Expired - Lifetime EP0329208B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
AT12988 1988-01-25
AT12888 1988-01-25
AT128/88 1988-01-25
AT129/88 1988-01-25

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EP0329208A2 EP0329208A2 (en) 1989-08-23
EP0329208A3 EP0329208A3 (en) 1989-10-11
EP0329208B1 true EP0329208B1 (en) 1995-07-12

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1081953C (en) * 1998-12-18 2002-04-03 中国科学院沈阳自动化研究所 Seawater flusher
CN105179026B (en) * 2015-10-10 2016-07-27 山东电力建设第一工程公司 The rinse-system of Turbo-generator Set lubricating oil system and purging method
CN111255651A (en) * 2020-03-02 2020-06-09 韩国昊 Air compressor

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2548501A (en) * 1947-08-19 1951-04-10 Hobson Ltd H M Hydraulic pump
DE900529C (en) * 1950-11-29 1953-12-28 Schweizerische Lokomotiv Pump with parallel pistons arranged in a circle and with variable delivery rate, which is controlled by means of pistons through openings in the cylinder walls
DE921554C (en) * 1951-09-30 1954-12-20 Wilhelm Bussmann K G Hydraulic high pressure pump
US3133503A (en) * 1962-05-25 1964-05-19 Bendix Corp Hydraulic pressure transformer
US4286927A (en) * 1978-08-14 1981-09-01 Mcdonnell Douglas Corporation Hydraulic power transfer unit
US4363211A (en) * 1980-02-01 1982-12-14 The Boeing Company Quasi-open loop hydraulic ram incremental actuator with power conserving properties
US4790236A (en) * 1983-09-12 1988-12-13 Beckman Instruments, Inc. Floating piston coupling for plunger type pumps
DE3347307A1 (en) * 1983-12-28 1985-07-11 Speck-Kolbenpumpen-Fabrik Otto Speck Kg, 8192 Geretsried PLUNGER PUMP
JPS6238257A (en) * 1985-08-09 1987-02-19 R D Kosan Kk Ultrahigh pressure water jet apparatus

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EP0329208A2 (en) 1989-08-23
EP0329208A3 (en) 1989-10-11

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