EP0329208A2 - Hydraulically driven high-pressure cleaner - Google Patents
Hydraulically driven high-pressure cleaner Download PDFInfo
- Publication number
- EP0329208A2 EP0329208A2 EP89200131A EP89200131A EP0329208A2 EP 0329208 A2 EP0329208 A2 EP 0329208A2 EP 89200131 A EP89200131 A EP 89200131A EP 89200131 A EP89200131 A EP 89200131A EP 0329208 A2 EP0329208 A2 EP 0329208A2
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- EP
- European Patent Office
- Prior art keywords
- pressure cleaner
- cleaner according
- piston
- pressure
- water
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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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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B08—CLEANING
- B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
- B08B3/00—Cleaning by methods involving the use or presence of liquid or steam
- B08B3/02—Cleaning by the force of jets or sprays
- B08B3/026—Cleaning by making use of hand-held spray guns; Fluid preparations therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
- F04B1/184—Cylindrical distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston 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
- F04B9/111—Piston 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
- F04B9/1115—Piston 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B08—CLEANING
- B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
- B08B2203/00—Details of cleaning machines or methods involving the use or presence of liquid or steam
- B08B2203/02—Details of machines or methods for cleaning by the force of jets or sprays
- B08B2203/0205—Bypass pressure relief valves
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B08—CLEANING
- B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
- B08B2203/00—Details of cleaning machines or methods involving the use or presence of liquid or steam
- B08B2203/02—Details of machines or methods for cleaning by the force of jets or sprays
- B08B2203/0294—Wobbling swash plates for high pressure cleaners
Definitions
- the invention relates to a hydraulically driven high-pressure cleaner with at least three pistons, on one side of which hydraulic oil is applied, which on the other side act on a second liquid to be displaced in a continuous manner, e.g. for the purpose of high pressure cleaning.
- Pressure washers of the entire genus are known. These include a plurality of hydraulic pistons that drive a control in the middle and from there a plurality of water pistons that are connected to the hydraulic pistons. Since the use of external rubber seals to seal the pistons is required, a large installation diameter is required. Since in such cases the control system must be arranged between the piston surface acted on by the oil hydraulics and the water side, the radially required installation space is very large, especially since it increases quadratically 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 aims to design a generic cleaning device in an extremely light, compact and yet reliable manner in order to enable simple use with forklifts, agricultural tractors, construction machinery, trucks with on-board hydraulics, concrete mixers, etc.
- a synchronizing rod (6) is arranged on each oil side of an axially movable and oil-hydraulically driven piston (2), which is connected to a rotating device (9-12) driving it so that the axial movement of the pistons ( 2) is converted into a rotary movement of the swash ring (12), the rotary device (9-12) driving a controller (22) which controls the hydraulic oil to and from the piston (2) in such a way 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 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 internal parts so close together that all oil-hydraulic and water-side control elements can be housed so close together in the cylinder block (1) or valve block (50) that external piping, connecting pieces, assembly arrangements etc. can be 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.
- 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), i.e. Via the circumferential channel (26), a connecting bore (27) to the pressure kidney (28) and from there to a control bore (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) .
- 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 is on the drive shaft (19) by means of bolts (20) and from there to the control (22) by means of bolts (21) is transferred.
- suction water (30) is sucked 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 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 is 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).
- 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). If 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.
- 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 because the ball (62) can move freely to the left.
- 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 jacket).
- 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)
Abstract
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, z.B. zum Zwecke von Hochdruckreinigung.The invention relates to a hydraulically driven high-pressure cleaner with at least three pistons, on one side of which hydraulic oil is applied, which on the other side act on a second liquid to be displaced in a continuous manner, e.g. for the purpose of high pressure cleaning.
Hochdruckreiniger der gesammten Gattung sind bekannt. Diese beinhalten eine Mehrzahl von Hydraulikkolben, 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 Kolbenfäche 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 Kompressionsöles 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 Gerate in Serie produziert, sondern nur "konventionelle Bauarten", d .h. Gerate mit Hydraulikmotor, hydraulischen Steuerungselementen, Kupplungen, Wasserpumpe, wasserseitigen Steuerungseinrichtungen, Montagerahmen, Abdeckhaube etc., denn die technischen Schwierigkeiten mit bisherigen, gattungsgemäßen Geräten waren zu groß.Pressure washers of the entire genus are known. These include a plurality of hydraulic pistons that drive a control in the middle and from there a plurality of water pistons that are connected to the hydraulic pistons. Since the use of external rubber seals to seal the pistons is required, a large installation diameter is required. Since in such cases the control system must be arranged between the piston surface acted on by the oil hydraulics and the water side, the radially required installation space is very large, especially since it increases quadratically 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 synchronization forces are determined, for example from piston friction, Sealing friction and other friction such as from bearings and hydraulic forces, which are necessary 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 event of alternating loads. Overall, no generic devices have yet been produced in series, but only "conventional designs", i.e. Devices with hydraulic motor, hydraulic control elements, couplings, water pump, water-side control devices, mounting frame, cover, etc., because the technical difficulties with previous, generic devices were too great.
Die Erfindung zielt darauf, ein gattungsgemäßes Reinigungsgerät in äußerst leichter, kompakter und trotzdem betriebssicherer Weise zu gestalten, um einen einfachen Einsatz mit Gabelstaplern, Ackerschleppern, Baumaschinen, Lkw mit Bordhydraulik, Betonmischern usw. zu ermöglichen.The invention aims to design a generic cleaning device in an extremely light, compact and yet reliable manner in order to enable simple use with forklifts, agricultural tractors, construction machinery, trucks with on-board hydraulics, concrete mixers, etc.
Dieses Ziel wird erfindungsgemäß dadurch erreicht, daß auf jeder Ölseite eines axial beweglichen und ölhydraulisch angetriebenen Kolbens (2) eine Synchronisierstange (6) angeordnet wird, die mit einer Dreheinrichtung (9-12) diese antreibend so verbunden ist, daß die Axialbewegung der Kolben (2) in eine Drehbewegung des Taumelringes (12) umgesetzt wird, wobei die Dreheinrichtung (9-12) eine Steuerung (22) antreibt, welche das Hydrauliköl so zu und von den Kolben (2) weg steuert, daß deren Axialbewegung erzeugt wird.This aim is achieved according to the invention in that a synchronizing rod (6) is arranged on each oil side of an axially movable and oil-hydraulically driven piston (2), which is connected to a rotating device (9-12) driving it so that the axial movement of the pistons ( 2) is converted into a rotary movement of the swash ring (12), the rotary device (9-12) driving a controller (22) which controls the hydraulic oil to and from the piston (2) in such a way that their axial movement is generated.
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, in turn, you can 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 internal parts so close together that all oil-hydraulic and water-side control elements can be housed so close together in the cylinder block (1) or valve block (50) that external piping, connecting pieces, assembly arrangements etc. can be 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
- 1 shows a longitudinal section through a high-pressure cleaner according to the invention.
- Fig. 2 is a section along the line II-II of Fig. 1;
- 3 shows a longitudinal section of an alternative embodiment of the inventive concept;
- Fig. 4 shows a weight and volume comparison of a conventional machine in comparison with a realized, hydraulically driven high-pressure cleaner according to the invention
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 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), i.e. Via the circumferential channel (26), a connecting bore (27) to the pressure kidney (28) and from there to a control bore (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 is on the drive shaft (19) by means of bolts (20) and from there to the control (22) by means of bolts (21) is transferred.
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 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), tumble 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 Zylinderräume 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 sucked 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 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 tumbling 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 disk (9) in order to compensate for a slight radial path due to the wobble angle of the perforated disk (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 which result 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 is 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). If 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
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 explicitly 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 in general 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 jacket).
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 relief 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.
Eine große Bandbreite weiterer Modifikationen und Verbesserungen der Erfindung ist gleichfalls möglich und offensichtlich in Anbetracht und unter Einbeziehung der obigen Beschreibung. Insoweit ist durch die obige Beschreibung keine Begrenzung der Erfindungsgedankens angestrebt, sondern lediglich dessen beispielhafte Erklärung mittels zwei Ausführungsbeispielen.A wide variety of other modifications and improvements to the invention are also possible and obvious in light of and incorporating the above description. In this respect, the above description is not intended to limit the inventive concept, but merely to explain it by way of example using two exemplary embodiments.
Claims (18)
dadurch gekennzeichnet,
daß auf jeder Ölseite eines hydraulisch angetriebenen Kolbens (2) eine Synchronisierstange (6) angeordnet ist, die mit einer Dreheinrichtung (9-12) diese antreibend so verbunden ist, daß die Axialbewegung der Kolben (2) in eine Drehbewegung des Taumelringes (12) umgesetzt wird, wobei die Dreheinrichtung (9-12) eine Steuerung (22 bzw. 51) antreibt, welche das Hydrauliköl so zu den Kolben (2) und von diesen wieder weg steuert, daß deren Axialbewegung erzeugt wird.1. Hydraulically driven high-pressure cleaner with at least three pistons, on one side of which hydraulic oil is applied, which on the other side act on a second liquid to be displaced in a continuous manner,
characterized by
that on each oil side of a hydraulically driven piston (2) a synchronizing rod (6) is arranged, which is drivingly connected to a rotating device (9-12) so that the axial movement of the pistons (2) into a rotary movement of the swash ring (12) is implemented, the rotating device (9-12) driving a control (22 or 51) which controls the hydraulic oil to the pistons (2) and away from them again so that their axial movement is generated.
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT12888 | 1988-01-25 | ||
AT128/88 | 1988-01-25 | ||
AT12988 | 1988-01-25 | ||
AT129/88 | 1988-01-25 |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0329208A2 true EP0329208A2 (en) | 1989-08-23 |
EP0329208A3 EP0329208A3 (en) | 1989-10-11 |
EP0329208B1 EP0329208B1 (en) | 1995-07-12 |
Family
ID=25591555
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP89200131A Expired - Lifetime EP0329208B1 (en) | 1988-01-25 | 1989-01-24 | Hydraulically driven high-pressure cleaner |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0329208B1 (en) |
DE (1) | DE58909333D1 (en) |
Cited By (3)
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 |
CN105179026A (en) * | 2015-10-10 | 2015-12-23 | 山东电力建设第一工程公司 | Flushing system and method for lubricating oil system of steam turbine generator unit |
CN111255651A (en) * | 2020-03-02 | 2020-06-09 | 韩国昊 | Air compressor |
Citations (9)
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 |
WO1985001336A1 (en) * | 1983-09-12 | 1985-03-28 | Beckman Instruments, Inc. | Floating piston coupling for plunger type pumps |
EP0149219A2 (en) * | 1983-12-28 | 1985-07-24 | Speck-Kolbenpumpen-Fabrik | Piston pump |
EP0214749A2 (en) * | 1985-08-09 | 1987-03-18 | Jse Corporation | Extra-high pressure water injector |
-
1989
- 1989-01-24 EP EP89200131A patent/EP0329208B1/en not_active Expired - Lifetime
- 1989-01-24 DE DE58909333T patent/DE58909333D1/en not_active Expired - Lifetime
Patent Citations (9)
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 |
WO1985001336A1 (en) * | 1983-09-12 | 1985-03-28 | Beckman Instruments, Inc. | Floating piston coupling for plunger type pumps |
EP0149219A2 (en) * | 1983-12-28 | 1985-07-24 | Speck-Kolbenpumpen-Fabrik | Piston pump |
EP0214749A2 (en) * | 1985-08-09 | 1987-03-18 | Jse Corporation | Extra-high pressure water injector |
Cited By (3)
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 |
CN105179026A (en) * | 2015-10-10 | 2015-12-23 | 山东电力建设第一工程公司 | Flushing system and method for lubricating oil system of steam turbine generator unit |
CN111255651A (en) * | 2020-03-02 | 2020-06-09 | 韩国昊 | Air compressor |
Also Published As
Publication number | Publication date |
---|---|
DE58909333D1 (en) | 1995-08-17 |
EP0329208A3 (en) | 1989-10-11 |
EP0329208B1 (en) | 1995-07-12 |
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