EP0927305B1 - Piston pump - Google Patents

Piston pump Download PDF

Info

Publication number
EP0927305B1
EP0927305B1 EP98924218A EP98924218A EP0927305B1 EP 0927305 B1 EP0927305 B1 EP 0927305B1 EP 98924218 A EP98924218 A EP 98924218A EP 98924218 A EP98924218 A EP 98924218A EP 0927305 B1 EP0927305 B1 EP 0927305B1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
valve
pressure delivery
low
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP98924218A
Other languages
German (de)
French (fr)
Other versions
EP0927305A1 (en
Inventor
Egbert Frenken
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gustav Klauke GmbH
Original Assignee
Gustav Klauke GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE19743747A external-priority patent/DE19743747B4/en
Application filed by Gustav Klauke GmbH filed Critical Gustav Klauke GmbH
Publication of EP0927305A1 publication Critical patent/EP0927305A1/en
Application granted granted Critical
Publication of EP0927305B1 publication Critical patent/EP0927305B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01R—ELECTRICALLY-CONDUCTIVE CONNECTIONS; STRUCTURAL ASSOCIATIONS OF A PLURALITY OF MUTUALLY-INSULATED ELECTRICAL CONNECTING ELEMENTS; COUPLING DEVICES; CURRENT COLLECTORS
    • H01R43/00—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors
    • H01R43/04—Apparatus or processes specially adapted for manufacturing, assembling, maintaining, or repairing of line connectors or current collectors or for joining electric conductors for forming connections by deformation, e.g. crimping tool
    • H01R43/042—Hand tools for crimping
    • H01R43/0427—Hand tools for crimping fluid actuated hand crimping tools
    • 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
    • F04B3/00—Machines or pumps with pistons coacting within one cylinder, e.g. multi-stage
    • 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
    • F04B5/00—Machines or pumps with differential-surface pistons

Definitions

  • the invention relates to a piston pump for delivery a fluid at low pressure and at higher pressure, being higher at low pressure in one pump cycle Delivery rate is given than at higher pressure, with one moved in a pump cylinder, under tension acted upon in its delivery end position of a pressure chamber Low pressure delivery piston, a high pressure delivery piston and an inlet and an outlet valve, further between the intake and exhaust valves a fluid delivery path is formed and the low pressure delivery piston against its bias into one The initial position of the conveyor must be moved back.
  • Piston pumps of this type are used, for example, by hand or motor-driven hand tools. This is about to a state of the art according to the US patents 5,575,627, 5,195,354 and 2,688,231. This prior art relates to motor-driven hand tools for crimping cable lugs or cable connectors. Furthermore, the subject of the invention but also meaning with regard to scissors, about cable shears. This is about the German Utility model 94 16 535 and the unpublished to refer to German patent application 196 49 932. In addition, such pumps also used in other areas of technology. It For example, U.S. Patents 2,845,033 and 674,381.
  • Two-stage pumps Numerous types of two-stage pumps are known. It is e.g. possible two different pump types to combine with each other and at the same time to drive, e.g. a gear pump for the low Pressure range and a piston pump for the high Print area. As soon as the required outlet pressure reaches the Working pressure of the low pressure pump exceeds their flow through a pressure relief valve in the tank returned.
  • Two-stage piston pumps are common, both for the low as well as for the high pressure sub-piston pumps be used.
  • One type is widespread the two pistons in the form of a pump tappet with two different diameters are united.
  • the hydraulic effective area is at the low pressure part the circular area between the two diameters and for the high pressure piston it is the entire cross sectional area of the small diameter.
  • Both Niederals even high pressure pumps each have one with the Tank connected inlet and one connected to pressure side Exhaust valve.
  • the US-PS 4,492,106 relates to a lever-operated hand tool in an embodiment for pressing Cable shoes.
  • a pump device which have a high pressure delivery piston and one Has low-pressure delivery piston.
  • the low pressure delivery piston consists of a spring-supported pipe section with a tube plate, which is the piston crown forms.
  • the low pressure delivery piston is replaced by a Continuation of the high pressure delivery piston against the spring force relocated, with hydraulic fluid from a reservoir is sucked in. Then moves the extension of the high pressure delivery piston back and the Low-pressure delivery piston delivers due to the pressure on it Spring the sucked hydraulic fluid in the work room.
  • the funding ends as soon as the Pressure in the delivery chamber no longer from the spring force is to be overcome. Then works at the well-known Pump only the high pressure piston.
  • the invention deals with the technical Problem, a piston pump to deliver a fluid to indicate at low pressure and at higher pressure, effective support with the simplest possible structure allows.
  • the fluid delivery path is also passed through the low-pressure delivery piston, with a valve blocking the movement of the low-pressure delivery piston in the delivery direction.
  • the valve in the low-pressure delivery piston is open, the pressure on both sides of the low-pressure delivery piston is practically the same.
  • the embodiment advantageously has a few individual parts.
  • valve in the low-pressure delivery piston In addition to the inlet and outlet valves, only the valve in the low-pressure delivery piston is required. The design is also simplified. There is only one pressure chamber for both the low pressure stage and the high pressure stage. Furthermore, it is provided that the movement of the low-pressure delivery piston takes place against its preload by the high-pressure delivery piston.
  • the high-pressure delivery piston can in particular act directly on the low-pressure delivery piston.
  • the high-pressure delivery piston preferably has a smaller cross-sectional area effective in terms of pumping than the low-pressure delivery piston.
  • the ratio can be, for example, 4: 1 with respect to the area of the low-pressure delivery piston to the area of the high-pressure delivery piston. Practically good values are also achieved with ratios of 6 to 7: 1.
  • the high-pressure delivery piston actuates the valve which is arranged in the low-pressure delivery piston and which blocks when the low-pressure delivery piston moves in the direction of delivery. Because the high-pressure delivery piston does not have to rest against the low-pressure delivery piston when the low-pressure delivery piston moves in the conveying direction, a valve which is very simple in construction, namely a plate valve, can be arranged in the low-pressure delivery piston in continuation of this idea.
  • the valve in the low-pressure delivery piston further preferably has a style-like extension or an actuating end passing through the piston head of the low-pressure delivery piston. Via this actuation end, the valve can be actuated in the manner described by the high-pressure delivery piston.
  • the preload of the low-pressure delivery piston in its delivery end position is advantageously achieved by a spring, more preferably by a helical spring (compression spring).
  • a spring more preferably by a helical spring (compression spring).
  • the spring acting on the low-pressure delivery piston biases the valve into the closed position.
  • the fluid volume in the piston pump, ie on the inlet side of the low-pressure delivery piston and in the pressure chamber is as small as possible.
  • the low-pressure delivery piston has a stylish extension on the back, for reducing the fluid volume between the inlet valve and the low-pressure delivery piston.
  • a projection on the rear wall can also be provided in the cylinder receiving the low-pressure delivery piston or a combination of these measures.
  • the pump cylinder has an operationally openable base. Due to the fact that the pump cylinder base can be opened operationally, it is possible, for example, to exchange or maintain the spring and / or the low-pressure delivery piston with the valve arranged therein in a simple manner.
  • the pump cylinder base can be screw-fastened in the pump housing in further detail.
  • the bottom of the pump cylinder is of a pot-like design with a screw-in thread on an outer edge of the pot. It is also possible, alternatively or alternatively, for the guide of the high-pressure delivery piston and possibly part of the adjoining piston crown to be screwed on and exchanged in this way.
  • a piston pump 1 for delivering a fluid at low pressure and at higher pressure.
  • the piston pump 1 can be used in a very wide variety of ways Find. With simple, manually operated pumps, the High pressure delivery piston operated by a hand lever and the ones already mentioned above motor-driven handheld devices just by a motor, like an electric motor. It is essential that first, without Load, an overdrive is desired, accordingly a high flow rate per stroke, and then under load higher pressures must be applied (at lower Delivery per stroke).
  • the piston pump 1 has a pump cylinder 2, in which against the bias exerted by a spring 3 a low-pressure delivery piston 4 is movable.
  • the Low-pressure delivery piston 4 also has a passage 5 for the hydraulic fluid, which is here is pumped.
  • the fluid passageway 5 is through a valve 6 designed as a check valve is closed. The valve 6 locks when the low pressure delivery piston 4 moves in the conveying direction and can open when the low-pressure delivery piston 4 opposes each other its direction of conveyance moves.
  • the low-pressure delivery piston 4 works in a pressure chamber 7.
  • the valve 6 opens accordingly only when if the pressure in the pressure chamber 7 is less than the inlet side in an inflow space 8 of the low-pressure delivery piston 4th
  • the piston pump 1 also has an inlet valve 9 and an outlet valve 10.
  • the inlet valve 9 is in a line connection to a fluid storage room arranged.
  • the outlet valve 10 is in a line connection to a work space not shown in FIG. 1 arranged (see also fluid storage space 26 and work space 27 in Fig. 5).
  • a high-pressure delivery piston continues to operate in the pressure chamber 7 11, which is basically based on different, in Fig. 1 ways not shown be driven can. For example, one with an electric motor connected eccentric drive, by a manual drive or any other that generates reciprocating motions Drive.
  • the freedom of movement of the high-pressure delivery piston 11 is by the broken line indicated.
  • the high-pressure delivery piston 11 has a lower one effective cross section than the low pressure delivery piston 4.
  • the ratio here is approximately 4: 1 (low-pressure delivery piston to high-pressure delivery pistons).
  • Fig. 2 a is at low pressure operation, i.e. at low pressure, in the work area, the delivery end position of the low-pressure delivery piston 4 shown.
  • the spring 3 is still practicing a bias, which is about in the embodiment corresponds to a value of 10 bar.
  • the high pressure delivery piston 11 is at its farthest retracted position, in the embodiment it closes approximately flush with a (lower) Cylinder wall 12 (from the pressure chamber 7).
  • 2c is the delivery stroke of the low-pressure delivery piston 4 shown. Because of the effect of the coil spring 3, the low-pressure delivery piston 4 after the high-pressure delivery piston 11 started its return movement has in the direction of its end-of-conveyance position Fig. 2a moves. The valve 6 is closed and on the inflow side due to resulting Negative pressure via the opening inlet valve 9 Fluid is sucked from the reservoir into the inflow space. At the same time, fluid from the pressure chamber 7 via the open exhaust valve 10 displaced in the work space. It can be seen that the amount of fluid displaced here depends on the cross-sectional ratio of the Low-pressure delivery piston 4 to the high-pressure delivery piston 11. It becomes all the more fluid in the low pressure stage conveyed into the work space via the outlet valve 10, the greater the - effective - cross-sectional ratio of the two pistons.
  • 3a to 3c is a corresponding one Shown funding cycle, in which it is assumed that the pressure in the work space is greater than that Biasing the low-pressure delivery piston 4 in its Conveyor-end position.
  • the pressure is said to be much greater than the initially mentioned pressure of approx. 10 bar. It is important that the pressure in the work area is greater than that by the coil spring (compression spring 3) in the upper, maximum preloaded position of the low-pressure delivery piston 4 is.
  • Fig. 3a is the delivery end position of the high pressure piston 11 shown.
  • the high-pressure delivery piston 11 is maximally moved into the pressure chamber 7.
  • FIG. 3b shows a state in which the high-pressure delivery piston 11 on the return stroke located.
  • the outlet valve 10 is closed because of Pressure in the pressure chamber 7 only by the spring 3rd is determined. For example, this can be a pressure between 10 and 20 bar. This pressure is essential smaller than the one to be assumed as high in this state Pressure in the work space.
  • the falling pressure or the compensation caused by the high-pressure delivery piston moving out 11 resulting volume increase leads to a wake of the low-pressure delivery piston 4. This is at the same time through the opening inlet valve 9 fluid from the reservoir sucked into the inflow 8.
  • the low pressure delivery piston 4 does not reach the end of delivery position 2a, but one for this in the conveying direction upstream position until an equalization of the volume share the moving out part of the high pressure delivery piston 11 is reached.
  • 3c is a point in time in the delivery stroke of the high-pressure delivery piston 11 shown.
  • the high pressure delivery piston 11 is not (yet) in contact with the low-pressure delivery piston 4. Due to the given Pressure increase, the inlet valve 9 is closed. On the other hand the outlet valve 10 is open because the pressure in the pressure chamber 7 due to the retracted high-pressure delivery piston 11 has increased so that the pressure in the work room.
  • FIG. 4 is another embodiment the piston pump 1 shown.
  • the position shown corresponds to Fig. 3a, this position itself here, however, on both a low-pressure and one High pressure cycle can relate.
  • the low-pressure delivery piston 4 faces the rear here a stylish extension 13. In any case functionally.
  • the stylish extension 13 is on one Plate 14, which is part of the valve 6 here, is formed.
  • the valve 6 or in the specific embodiment the plate 14 also has a front Actuation extension 15 on.
  • the stylish extension 13 leads to a minimal Fluid volume in inflow space 8. This is desirable to to achieve certain flow velocities there. Furthermore, in order to enter the (high pressure) delivery stroke as little recoil as possible due to the hydraulic fluid to given elasticity to reach. In general, however, it is essential that for the pump uses a fluid that is essentially is incompressible. There are common - oily ones - hydraulic fluids.
  • the coil spring 3 is in the Embodiment of FIG. 4 surrounding the cylindrical Extension 13 arranged.
  • the 4 the piston crown 31 as a screw-in part is trained. It has a side wall an external thread 33 with a corresponding Internal thread of the pump housing 32 cooperates. hereby is a simple exchange possible Ease of maintenance given.
  • both the piston guide for the high pressure delivery piston 11 like the piston crown for the low-pressure delivery piston 4 are designed to be screwed in. It is preferred only the piston guide for the high-pressure delivery piston 11 trained to be screw-in.
  • a flow path is formed is in which a usual check valve is arranged. This makes it possible, on the one hand still in the compressed position of the spring 3 keep the given volume as small as possible, on the other hand, in particular, such a flow path train that always relatively high flow rates are ensured. Is essential also that the construction is such that there are little or no dead spaces.
  • FIG. 5 is a hand-held power tool with a piston pump according to the above illustrated embodiment Fig. 4 shown.
  • the reduction gear 22 acts via a Shaft 23 on an eccentric 24, which in turn over a roller bearing 25 on the high-pressure delivery piston 11 acts.
  • the Fluid storage space 26 fluid pumped into the working space 27 and thereby a working piston 28 against the Effect of a return spring 29 in its working end position emotional.
  • the return movement of the working piston 28 takes place via the return spring 29 if - what here is not shown in detail - a drain valve of the work space 27 is open, through which the Fluid can then flow back into the storage space 26.
  • the electric motor 21 is driven further Detail about a battery or an accumulator 30.
  • Fig. 7 is the high pressure delivery piston 11 directly by a hand lever 34 actuated.
  • the high-pressure piston 11 is for this in detail with a coaxially aligned connector 35 connected, which by means of a hook formation 36 a driving pin 37 of the hand lever 34 coupled is.
  • the hand lever is independent of this Pivot pin 38 mounted on the housing 39.
  • piston pump 1 behaves in the embodiment of Figure 7 in the same way as that Piston pump 1 of the previously described embodiments, so that reference is made to this.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Steroid Compounds (AREA)

Abstract

The invention relates to a piston pump (1) for delivering a fluid at low pressure and at a higher pressure, a higher delivery volume being provided in one pumping cycle at low pressure than at a higher pressure, having a low-pressure delivery piston (4), which is moved inside a pump cylinder (2) and acts upon a pressure chamber (7) under prestress into its delivery end position, a high-pressure delivery piston (11), an inlet valve (9) and an outlet valve (9, 10), a fluid delivery path (5) furthermore being provided between the inlet valve (9) and the outlet valve (10), and the low-pressure delivery piston (4) being able to be moved back counter to its prestress into a delivery starting position, and proposes, to achieve effective delivery at low pressure and at a higher pressure with the simplest possible construction, that the fluid delivery path (5) passes through the low-pressure delivery piston (4), that a valve (6) is provided in the low-pressure delivery piston (4), which valve shuts in the case of movement into the delivery starting position, that the high-pressure delivery piston (11) and the low-pressure delivery piston (4) operate in a common pressure chamber (7), and that the high-pressure delivery piston (11) moves the low-pressure delivery piston (4) counter to its prestress.

Description

Die Erfindung betrifft eine Kolbenpumpe zur Förderung eines Fluids bei niederem Druck und bei höherem Druck, wobei bei niederem Druck in einem Pumpzyklus eine höhere Fördermenge gegeben ist als bei höherem Druck, mit einem in einem Pumpzylinder bewegten, unter Vorspannung in seine Förder-Endstellung eines Druckraums beaufschlagten Niederdruck-Förderkolben, einem Hochdruck-Förderkolben und einem Einlaß- und einem Auslaßventil, wobei weiter zwischen dem Einlaß- und dem Auslaßventil ein Fluid-Förderweg ausgebildet ist und der Niederdruck-Förderkolben gegen seine Vorspannung in eine Förder-Anfangsstellung zurückzubewegen ist.The invention relates to a piston pump for delivery a fluid at low pressure and at higher pressure, being higher at low pressure in one pump cycle Delivery rate is given than at higher pressure, with one moved in a pump cylinder, under tension acted upon in its delivery end position of a pressure chamber Low pressure delivery piston, a high pressure delivery piston and an inlet and an outlet valve, further between the intake and exhaust valves a fluid delivery path is formed and the low pressure delivery piston against its bias into one The initial position of the conveyor must be moved back.

Derartige Kolbenpumpen finden bspw. Einsatz bei handoder motorgetriebenen Handwerkzeugen. Hierzu ist etwa auf einen Stand der Technik gemäß den US-Patentschriften 5,575,627, 5,195,354 und 2,688,231 zu verweisen. Dieser Stand der Technik betrifft motorgetriebene Handwerkzeuge zur Verpressung von Kabelschuhen oder Kabelverbindern. Weiter hat der Gegenstand der Erfindung aber beispielsweise auch Bedeutung hinsichtlich Scheren, etwa Kabelscheren. Hierzu ist etwa auf das deutsche Gebrauchsmuster 94 16 535 und die nicht vorveröffentlichte deutsche Patentanmeldung 196 49 932 zu verweisen. Darüber hinaus werden derartige Pumpen aber auch in sonstigen Gebieten der Technik eingesetzt. Es wird bspw. auf die US-Patentschriften 2,845,033 und 674,381 verwiesen.Piston pumps of this type are used, for example, by hand or motor-driven hand tools. This is about to a state of the art according to the US patents 5,575,627, 5,195,354 and 2,688,231. This prior art relates to motor-driven hand tools for crimping cable lugs or cable connectors. Furthermore, the subject of the invention but also meaning with regard to scissors, about cable shears. This is about the German Utility model 94 16 535 and the unpublished to refer to German patent application 196 49 932. In addition, such pumps also used in other areas of technology. It For example, U.S. Patents 2,845,033 and 674,381.

Häufig werden vor allem für den Antrieb von Hydraulikwerkzeugen Pumpen eingesetzt, die über zwei Druckstufen verfügen. Diese liefern bis zu einem bestimmten Grenzdruck, der z.B. 5 % des Maximaldrucks beträgt, eine wesentlich höhere Ölmenge als bei Maximaldruck. Damit läßt sich die Arbeitsgeschwindigkeit der Hydraulikgeräte beträchtlich erhöhen, weil bei vielen Werkzeugen, wie z.B. Preßwerkzeugen für das Verpressen von Kabelschuhen, zunächst ein bestimmter Leerhub zurückgelegt werden muß, bevor das Werkstück berührt wird und der eigentliche Arbeitsvorgang mit hohem Kraftbedarf erfolgt. Beim Leerhub muß in der Regel nur die Kraft der Kolbenrückholfeder des Werkzeug-Hydraulikzylinders überbrückt werden. Dafür reicht ein geringer Öldruck aus.Frequently used mainly for driving hydraulic tools Pumps used that have two pressure levels feature. These deliver up to a certain limit pressure, e.g. 5% of the maximum pressure is one much higher oil volume than at maximum pressure. In order to can the working speed of the hydraulic equipment increase significantly because with many tools, such as. Crimping tools for crimping cable lugs, first a certain idle stroke must be before the workpiece is touched and the actual work with high power requirements. At idle stroke only the force of the Piston return spring of the tool hydraulic cylinder be bridged. A low oil pressure is sufficient for this out.

Es sind zahlreiche Bauarten von Zweistufen-Pumpen bekannt. Es ist z.B. möglich, zwei unterschiedliche Pumpenbauarten miteinander zu kombinieren und gleichzeitig anzutreiben, also z.B. eine Zahnradpumpe für den niedrigen Druckbereich und eine Kolbenpumpe für den hohen Druckbereich. Sobald der geforderte Ausgangsdruck den Arbeitsdruck der Niederdruckpumpe übersteigt, wird deren Förderstrom über ein Überdruckventil in den Tank zurückgeleitet.Numerous types of two-stage pumps are known. It is e.g. possible two different pump types to combine with each other and at the same time to drive, e.g. a gear pump for the low Pressure range and a piston pump for the high Print area. As soon as the required outlet pressure reaches the Working pressure of the low pressure pump exceeds their flow through a pressure relief valve in the tank returned.

Insbesondere für handbetätigte Hydraulikwerkzeuge sind Zweistufen-Kolbenpumpen üblich, bei denen sowohl für den Nieder- als auch für den Hochdruck Teilkolbenpumpen verwendet werden. Weitverbreitet ist eine Bauart, bei der beide Kolben in Form eines Pumpstößels mit zwei unterschiedlichen Durchmessern vereinigt sind. Die hydraulisch wirksame Fläche ist bei dem Niederdruckteil die Kreisringfläche zwischen den beiden Durchmessern und bei dem Hochdruckkolben ist es die gesamte Querschnittsfläche des kleinen Durchmessers. Sowohl Niederals auch Hochdruckpumpe besitzen jeweils ein mit dem Tank verbundenes Einlaß- und ein mit Druckseite verbundenes Auslaßventil. Zusätzlich ist ein Überdruckventil für die Niederdruckstufe erforderlich, durch welches das Öl nach Überschreiten des Druckes der Niederdruckstufe in den Tank zurückfließt.Especially for hand-operated hydraulic tools Two-stage piston pumps are common, both for the low as well as for the high pressure sub-piston pumps be used. One type is widespread the two pistons in the form of a pump tappet with two different diameters are united. The hydraulic effective area is at the low pressure part the circular area between the two diameters and for the high pressure piston it is the entire cross sectional area of the small diameter. Both Niederals even high pressure pumps each have one with the Tank connected inlet and one connected to pressure side Exhaust valve. There is also a pressure relief valve required for the low pressure stage, through which the oil after the pressure of the low pressure stage has been exceeded flows back into the tank.

Die US-PS 4,492,106 betrifft ein hebelbetätigtes Handwerkzeug in einer Ausgestaltung zur Verpressung von Kabel-Schuhen. Hierbei ist eine Pumpeinrichtung vorgeschlagen, die einen Hochdruck-Förderkolben und einen Niederdruck-Förderkolben aufweist. Der Niederdruck-Förderkolben besteht aus einem federabgestützten Rohrabschnitt mit einem Rohrboden, welcher den Kolbenboden bildet. Der Niederdruck-Förderkolben wird durch eine Fortsetzung des Hochdruck-Förderkolbens gegen die Federkraft verlagert, wobei aus einem Vorratsbehältnis Hydraulikflüssigkeit eingesaugt wird. Sodann bewegt sich der Fortsatz des Hochdruck-Förderkolbens zurück und der Niederdruck-Förderkolben fördert aufgrund der ihn beaufschlagenden Feder die eingesaugte Hydraulikflüssigkeit in den Arbeitsraum. Die Förderung hört auf, sobald der Druck in dem Förderraum von der Federkraft nicht mehr zu überwinden ist. Sodann arbeitet bei der bekannten Pumpe nur noch der Hochdruckkolben.The US-PS 4,492,106 relates to a lever-operated hand tool in an embodiment for pressing Cable shoes. Here, a pump device is proposed which have a high pressure delivery piston and one Has low-pressure delivery piston. The low pressure delivery piston consists of a spring-supported pipe section with a tube plate, which is the piston crown forms. The low pressure delivery piston is replaced by a Continuation of the high pressure delivery piston against the spring force relocated, with hydraulic fluid from a reservoir is sucked in. Then moves the extension of the high pressure delivery piston back and the Low-pressure delivery piston delivers due to the pressure on it Spring the sucked hydraulic fluid in the work room. The funding ends as soon as the Pressure in the delivery chamber no longer from the spring force is to be overcome. Then works at the well-known Pump only the high pressure piston.

Ausgehend von dem vorstehend genannten Stand der Technik, beschäftigt sich die Erfindung mit der technischen Problematik, eine Kolbenpumpe zur Förderung eines Fluids bei niederem Druck und bei höherem Druck anzugeben, die bei möglichst einfachem Aufbau eine wirksame Förderung ermöglicht.Based on the prior art mentioned above, the invention deals with the technical Problem, a piston pump to deliver a fluid to indicate at low pressure and at higher pressure, effective support with the simplest possible structure allows.

Diese technische Problematik ist zunächst und im wesentlichen beim Gegenstand des Anspruches 1 gelöst, wobei darauf abgestellt ist, daß der Fluid-Förderweg den Niederdruck-Förderkolben durchsetzt, daß in dem Niederdruck-Förderkolben ein bei Bewegung in Förderrichtung sperrendes Ventil angeordnet ist und daß der Hochdruck-Förderkolben in den Druckraum des Niederdruck-Förderkolbens arbeitet. Es ist nur ein gemeinsamer Druckraum für den Niederdruck-Förderkolben und für den Hochdruck-Förderkolben vorhanden. Der Niederdruck-Förderkolben wird zwangsweise zurückgeschoben, nämlich durch den Hochdruck-Förderkolben. Erfindungsgemäß ist eine vereinfachte Ausführung der Kolbenpumpe zunächst dadurch erreicht, daß der Niederdruck-Förderkolben und der Hochdruck-Förderkolben auf denselben Druckraum arbeiten. Es ist nur noch ein Druckraum bzw. Pumpraum gegeben. Die Verluste durch Drosselvorgänge sind minimiert bzw. nicht mehr gegeben. Weiter ist der Fluid-Förderweg durch den Niederdruck-Förderkolben hindurch geführt, mit einem bei Bewegung des Niederdruck-Förderkolbens in Förderrichtung sperrenden Ventil. Dies bedeutet zugleich, daß bei einer Bewegung des Niederdruck-Förderkolbens entgegen der Förderrichtung Fluid in den Druckraum strömt, wobei der Druck in dem Druckraum nicht größer ist als in Zuströmrichtung vor dem Niederdruck-Förderkolben. Es herrscht vielmehr in der Regel gleicher Druck wie in Zuströmrichtung vor dem Niederdruck-Förderkolben, vermindert um die Kraft einer auf den Niederdruck-Förderkoben wirkenden Feder. Bei geöffnetem Ventil in dem Niederdruck-Förderkolben ist der Druck auf beiden Seiten des Niederdruck-Förderkolbens praktisch gleich. Die Ausführungsform weist vorteilhaft wenige Einzelteile auf. Außer dem Zulauf- und dem Ablaufventil ist nur noch das Ventil in dem Niederdruck-Förderkolben erforderlich. Außerdem ist die Bauform vereinfacht. Es ist nur noch ein Druckraum sowohl für die Niederdruckstufe wie die Hochdruckstufe gegeben. Im weiteren ist vorgesehen, daß die Bewegung des Niederdruck-Förderkolbens entgegen seiner Vorspannung durch den Hochdruck-Förderkolben erfolgt. Der Hochdruck-Förderkolben kann insbesondere unmittelbar flächig auf den Niederdruck-Förderkolben einwirken. Der Hochdruck-Förderkolben besitzt bevorzugt eine kleinere hinsichtlich des Pumpens wirksame Querschnittsfläche als der Niederdruck-Förderkolben. Das Verhältnis kann bspw. hinsichtlich der Fläche des Niederdruck-Förderkolbens zu der Fläche des Hochdruck-Förderkolbens 4:1 sein. Praktisch gute Werte werden auch mit Verhältnissen von 6 bis 7:1 erreicht. In weiterer bevorzugter Ausführungsform ist auch vorgesehen, daß der Hochdruck-Förderkolben das in dem Niederdruck-Förderkolben angeordnete Ventil, das bei Bewegung des Niederdruck-Förderkolbens in Förderrichtung sperrt, betätigt. Dadurch, daß der Hochdruck-Förderkolben bei Bewegung des Niederdruck-Förderkolbens in Förderrichtung nicht an den Niederdruck-Förderkolben anliegen muß, kann in Fortführung dieses Gedankens ein in der Bauweise sehr einfaches Ventil, nämlich ein Plattenventil, in dem Niederdruck-Förderkolben angeordnet sein. Das Ventil in dem Niederdruck-Förderkolben besitzt weiter bevorzugt einen stilartigen Fortsatz bzw. ein den Kolbenboden des Niederdruck-Förderkolbens durchsetzendes Betätigungsende. Über dieses Betätigungsende kann eine Betätigung des Ventils in der beschriebenen Weise durch den Hochdruck-Förderkolben erfolgen.
Die Vorspannung des Niederdruck-Förderkolbens in seine Förder-Endstellung ist vorteilhafterweise durch eine Feder, weiter bevorzugt durch eine Schraubenfeder (Druckfeder), erreicht. Im Hinblick auf das in dem Niederdruck-Förderkolben enthaltene Ventil kann insbesondere auch vorgesehen sein, daß die den Niederdruck-Förderkolben beaufschlagende Feder das Ventil in die Verschlußstellung vorspannt. Im weiteren ist es bevorzugt, daß das Fluidvolumen in der Kolbenpumpe, d.h. auf der Zulaufseite des Niederdruck-Förderkolbens und im Druckraum, möglichst gering ist. In einer Ausgestaltung ist hierfür vorgesehen, daß der Niederdruck-Förderkolben rückseitig einen stilartigen Fortsatz aufweist, zur Verkleinerung des Fluid-Volumens zwischen dem Einlaßventil und dem Niederdruck-Förderkolben. In gleicher Weise kann auch etwa ein rückwandseitiger Vorsprung in dem den Niederdruck-Förderkolben aufnehmenden Zylinder vorgesehen sein oder eine Kombinaton dieser Maßnahmen. In weiterer Ausgestaltung, zur Erreichung einer hohen Wartungsfreundlichkeit, ist auch vorgesehen, daß der Pumpzylinder einen betrieblich öffenbaren Boden aufweist. Dadurch, daß der Pumpzylinder-Boden betrieblich öffenbar ist, ist es bspw. in einfacher Weise möglich, die Feder und/oder den Niederdruck-Förderkolben mit darin angeordnetem Ventil auszutauschen oder zu warten. Hierzu kann in weiterer Einzelheit der Pumpzylinder-Boden in dem Pumpgehäuse schraubbefestigt sein. Es empfiehlt sich hierzu auch, daß der Pumpzylinder-Boden insgesamt topfartig ausgebildet ist, mit einem Einschraub-Gewinde an einer Topfrand-Außenwand. Es ist kombinativ oder alternativ hierzu auch möglich, daß die Führung des Hochdruck-Förderkolbens und ggf. ein Teil des angerenzenden Kolbenbodens in dieser Weise engeschraubt und austauschbar ist.This technical problem is solved first and for the most part in the subject matter of claim 1, the focus being on the fact that the fluid delivery path passes through the low-pressure delivery piston, that a valve blocking movement in the direction of delivery is arranged in the low-pressure delivery piston and that the high pressure -Delivery piston works in the pressure chamber of the low-pressure delivery piston. There is only one common pressure chamber for the low-pressure delivery piston and for the high-pressure delivery piston. The low-pressure delivery piston is forcibly pushed back, namely by the high-pressure delivery piston. According to the invention, a simplified design of the piston pump is first achieved in that the low-pressure delivery piston and the high-pressure delivery piston operate on the same pressure chamber. There is only one pressure chamber or pump room. The losses caused by throttling are minimized or no longer exist. The fluid delivery path is also passed through the low-pressure delivery piston, with a valve blocking the movement of the low-pressure delivery piston in the delivery direction. At the same time, this means that when the low-pressure delivery piston moves against the direction of delivery, fluid flows into the pressure chamber, the pressure in the pressure room not being greater than in the inflow direction upstream of the low-pressure delivery piston. Rather, there is generally the same pressure as in the inflow direction in front of the low-pressure delivery piston, less the force of a spring acting on the low-pressure delivery piston. When the valve in the low-pressure delivery piston is open, the pressure on both sides of the low-pressure delivery piston is practically the same. The embodiment advantageously has a few individual parts. In addition to the inlet and outlet valves, only the valve in the low-pressure delivery piston is required. The design is also simplified. There is only one pressure chamber for both the low pressure stage and the high pressure stage. Furthermore, it is provided that the movement of the low-pressure delivery piston takes place against its preload by the high-pressure delivery piston. The high-pressure delivery piston can in particular act directly on the low-pressure delivery piston. The high-pressure delivery piston preferably has a smaller cross-sectional area effective in terms of pumping than the low-pressure delivery piston. The ratio can be, for example, 4: 1 with respect to the area of the low-pressure delivery piston to the area of the high-pressure delivery piston. Practically good values are also achieved with ratios of 6 to 7: 1. In a further preferred embodiment it is also provided that the high-pressure delivery piston actuates the valve which is arranged in the low-pressure delivery piston and which blocks when the low-pressure delivery piston moves in the direction of delivery. Because the high-pressure delivery piston does not have to rest against the low-pressure delivery piston when the low-pressure delivery piston moves in the conveying direction, a valve which is very simple in construction, namely a plate valve, can be arranged in the low-pressure delivery piston in continuation of this idea. The valve in the low-pressure delivery piston further preferably has a style-like extension or an actuating end passing through the piston head of the low-pressure delivery piston. Via this actuation end, the valve can be actuated in the manner described by the high-pressure delivery piston.
The preload of the low-pressure delivery piston in its delivery end position is advantageously achieved by a spring, more preferably by a helical spring (compression spring). With regard to the valve contained in the low-pressure delivery piston, it can in particular also be provided that the spring acting on the low-pressure delivery piston biases the valve into the closed position. Furthermore, it is preferred that the fluid volume in the piston pump, ie on the inlet side of the low-pressure delivery piston and in the pressure chamber, is as small as possible. In one embodiment, it is provided for this that the low-pressure delivery piston has a stylish extension on the back, for reducing the fluid volume between the inlet valve and the low-pressure delivery piston. In the same way, a projection on the rear wall can also be provided in the cylinder receiving the low-pressure delivery piston or a combination of these measures. In a further embodiment, in order to achieve a high degree of ease of maintenance, it is also provided that the pump cylinder has an operationally openable base. Due to the fact that the pump cylinder base can be opened operationally, it is possible, for example, to exchange or maintain the spring and / or the low-pressure delivery piston with the valve arranged therein in a simple manner. For this purpose, the pump cylinder base can be screw-fastened in the pump housing in further detail. It is also recommended that the bottom of the pump cylinder is of a pot-like design with a screw-in thread on an outer edge of the pot. It is also possible, alternatively or alternatively, for the guide of the high-pressure delivery piston and possibly part of the adjoining piston crown to be screwed on and exchanged in this way.

Nachstehend ist die Erfindung desweiteren anhand der beigefügten Zeichnung, die jedoch lediglich ein Ausführungsbeispiel darstellt, erläutert. Hierbei zeigt:

Fig. 1
eine schematische Querschnittsansicht einer Kolbenpumpe;
Fig. 2
in den Darstellung a, b und c den Ablauf eines Förderzyklus bei Niederdruck;
Fig. 3
in den Darstellung a, b und c den Ablauf eines Förderzyklus bei Hochdruck;
Fig. 4
die schematische Ansicht einer Kolbenpumpe einer zweiten Ausführungsform;
Fig. 5
eine schematische Querschnittsansicht eines motorbetriebenen Handgerätes mit einer Kolbenpumpe gemäß Fig. 4;
Fig. 6
eine gegenüber Fig. 4 abgewandelte Ausführungsform; und
Fig. 7
eine weitere Ausführungsform, bei welcher die Betätigung mit einem Handhebel erfolgt.
The invention is further explained below with reference to the accompanying drawing, which, however, only represents an exemplary embodiment. Here shows:
Fig. 1
a schematic cross-sectional view of a piston pump;
Fig. 2
in representations a, b and c the course of a delivery cycle at low pressure;
Fig. 3
in the representations a, b and c the course of a delivery cycle at high pressure;
Fig. 4
the schematic view of a piston pump of a second embodiment;
Fig. 5
a schematic cross-sectional view of a motor-operated hand-held device with a piston pump according to FIG. 4;
Fig. 6
an embodiment modified from FIG. 4; and
Fig. 7
a further embodiment in which the operation is carried out with a hand lever.

Dargestellt und beschrieben ist, zunächst mit Bezug zu Fig. 1, eine Kolbenpumpe 1 zur Förderung eines Fluids bei niederem Druck und bei höherem Druck. Die Kolbenpumpe 1 kann in einer sehr vielfachen Hinsicht Verwendung finden. Bei einfachen, handbetätigten Pumpen kann der Hochdruck-Förderkolben durch einen Handhebel betätigt werden und bei den weiter vorstehend bereits erwähnten motorbetriebenen Handgeräten eben durch einen Motor, wie ein Elektromotor. Wesentlich ist, daß zuerst, ohne Belastung, ein Schnellgang erwünscht ist, entsprechend einer hohen Fördermenge pro Hub, und dann unter Belastung höhere Drücke aufgebracht werden müssen (bei geringerer Fördermenge pro Hub).Is shown and described, initially with reference to Fig. 1, a piston pump 1 for delivering a fluid at low pressure and at higher pressure. The piston pump 1 can be used in a very wide variety of ways Find. With simple, manually operated pumps, the High pressure delivery piston operated by a hand lever and the ones already mentioned above motor-driven handheld devices just by a motor, like an electric motor. It is essential that first, without Load, an overdrive is desired, accordingly a high flow rate per stroke, and then under load higher pressures must be applied (at lower Delivery per stroke).

Die Kolbenpumpe 1 weist einen Pumpzylinder 2 auf, in welchem gegen die durch eine Feder 3 ausgeübte Vorspannung ein Niederdruck-Förderkolben 4 bewegbar ist. Der Niederdruck-Förderkolben 4 weist weiter einen Durchgangsweg 5 für das hydraulische Fluid aus, welches hier gepumpt wird. Der Fluid-Durchgangsweg 5 ist durch ein als Rückschlagventil ausgebildetes Ventil 6 verschlossen. Das Ventil 6 sperrt, wenn sich der Niederdruck-Förderkolben 4 in Förderrichtung bewegt und kann sich öffnen, wenn sich der Niederdruck-Förderkolben 4 entgegen seiner Förderrichtung bewegt.The piston pump 1 has a pump cylinder 2, in which against the bias exerted by a spring 3 a low-pressure delivery piston 4 is movable. The Low-pressure delivery piston 4 also has a passage 5 for the hydraulic fluid, which is here is pumped. The fluid passageway 5 is through a valve 6 designed as a check valve is closed. The valve 6 locks when the low pressure delivery piston 4 moves in the conveying direction and can open when the low-pressure delivery piston 4 opposes each other its direction of conveyance moves.

Der Niederdruck-Förderkolben 4 arbeitet auf einen Druckraum 7. Das Ventil 6 öffnet sich entsprechend nur dann, wenn der Druck in dem Druckraum 7 geringer ist als auf der Zulaufseite in einem Zuflußraum 8 des Niederdruck-Förderkolbens 4.The low-pressure delivery piston 4 works in a pressure chamber 7. The valve 6 opens accordingly only when if the pressure in the pressure chamber 7 is less than the inlet side in an inflow space 8 of the low-pressure delivery piston 4th

Weiter weist die Kolbenpumpe 1 ein Einlaßventil 9 und ein Auslaßventil 10 auf. Das Einlaßventil 9 ist in einer Leitungsverbindung zu einem Fluid-Vorratsraum angeordnet. Das Auslaßventil 10 ist in einer Leitungsverbindung zu einem in Fig. 1 nicht dargestellten Arbeitsraum angeordnet (vgl. auch Fluid-Vorratsraum 26 und Arbeitsraum 27 in Fig. 5).The piston pump 1 also has an inlet valve 9 and an outlet valve 10. The inlet valve 9 is in a line connection to a fluid storage room arranged. The outlet valve 10 is in a line connection to a work space not shown in FIG. 1 arranged (see also fluid storage space 26 and work space 27 in Fig. 5).

In den Druckraum 7 arbeitet weiter ein Hochdruck-Förderkolben 11, der grundsätzlich auf verschiedene, in Fig. 1 nicht weiter dargestellte Weisen angetrieben sein kann. Beispielsweise durch einen mit einem Elektromotor verbundenen Exzenterantrieb, durch einen Handantrieb oder einen sonstigen, Hin- und Herbewegungen erzeugenden Antrieb. Der Bewegungsspielraum des Hochdruck-Förderkolbens 11 ist durch die strichlinierte Darstellung angedeutet.A high-pressure delivery piston continues to operate in the pressure chamber 7 11, which is basically based on different, in Fig. 1 ways not shown be driven can. For example, one with an electric motor connected eccentric drive, by a manual drive or any other that generates reciprocating motions Drive. The freedom of movement of the high-pressure delivery piston 11 is by the broken line indicated.

Der Hochdruck-Förderkolben 11 besitzt einen geringeren wirksamen Querschnitt als der Niederdruck-Förderkolben 4. Das Verhältnis beträgt hier etwa 4:1 (Niederdruck-Förderkolben zu Hochdruck-Förderkolben). The high-pressure delivery piston 11 has a lower one effective cross section than the low pressure delivery piston 4. The ratio here is approximately 4: 1 (low-pressure delivery piston to high-pressure delivery pistons).

Die Funktion der Kolbenpumpe 1 ist unter Bezug auf die Fig. 2 und 3 in weiterer Einzelheit erläutert. In Fig. 2 a ist bei Niederdruckbetrieb, d.h. bei niederem Druck , in dem Arbeitsraum, die Förder-Endstellung des Niederdruck-Förderkolbens 4 dargestellt. Die Feder 3 übt noch eine Vorspannung aus, welche etwa beim Ausführungsbeispiel einem Wert von 10 Bar entspricht. Der Hochdruck-Förderkolben 11 befindet sich in seiner am weitesten zurückgezogenen Stellung, beim Ausführungsbeispiel schließt er stirnseitig etwa bündig mit einer (unteren) Zylinderwandung 12 (des Druckraumes 7) ab.The function of the piston pump 1 is with reference to the 2 and 3 explained in further detail. In Fig. 2 a is at low pressure operation, i.e. at low pressure, in the work area, the delivery end position of the low-pressure delivery piston 4 shown. The spring 3 is still practicing a bias, which is about in the embodiment corresponds to a value of 10 bar. The high pressure delivery piston 11 is at its farthest retracted position, in the embodiment it closes approximately flush with a (lower) Cylinder wall 12 (from the pressure chamber 7).

In der Fig. 2b ist dargestellt, daß der Hochdruck-Förderkolben 11 in - stirnseitiger - Anlage an dem Niederdruck-Förderkolben 4 ist und diesen entgegen der Wirkung der Schraubenfeder 3 zurückbewegt. Bei dieser Zurückbewegung ist das Ventil 6 geöffnet. Aus dem bezüglich des Niederdruck-Förderkolbens 4 rückseitigen Zuflußraum 8 strömt Fluid durch den Fluid-Förderweg 5 in den Druckraum 7. Da zugleich das Volumen der Pumpe (Zuflußraum 8 und Druckraum 7) durch den einfahrenden Hochdruck-Förderkolben 11 stetig verkleinert wird,ist auch das Auslaßventil 10 geöffnet und strömt Fluid in den Arbeitsraum.2b shows that the high-pressure delivery piston 11 in - frontal - system on the low-pressure delivery piston 4 is and this against the effect the coil spring 3 moved back. At this Backward movement, the valve 6 is open. From the regarding of the low-pressure delivery piston 4 rear inflow space 8 flows fluid through the fluid delivery path 5 in the pressure chamber 7. At the same time the volume of the pump (Inflow space 8 and pressure space 7) by the incoming High-pressure delivery piston 11 is steadily reduced the outlet valve 10 also opens and fluid flows in the workspace.

In Fig. 2c ist der Förderhub des Niederdruck-Förderkolbens 4 dargestellt. Aufgrund der Wirkung der Schraubenfeder 3 wird der Niederdruck-Förderkolben 4, nachdem der Hochdruck-Förderkolben 11 seine Rückbewegung begonnen hat, in Richtung seiner Förder-Endstellung gemäß Fig. 2a bewegt. Hierbei ist das Ventil 6 geschlossen und auf der Zuflußseite wird aufgrund sich ergebenden Unterdruckes über das sich öffnende Einlaßventil 9 Fluid aus dem Vorratsbehältnis in den Zuflußraum angesaugt. Zugleich wird aus dem Druckraum 7 Fluid über das geöffnete Auslaßventil 10 in dem Arbeitsraum verdrängt. Es ist ersichtlich, daß die hierbei verdrängte Fluidmenge abhängig ist von dem Querschnittsverhältnis des Niederdruck-Förderkolbens 4 zu dem Hochdruck-Förderkolben 11. Es wird um so mehr Fluid in der Niederdruckstufe über das Auslaßventil 10 in den Arbeitsraum gefördert, je größer das - wirksame - Querschnittsverhältnis der beiden Kolben ist.2c is the delivery stroke of the low-pressure delivery piston 4 shown. Because of the effect of the coil spring 3, the low-pressure delivery piston 4 after the high-pressure delivery piston 11 started its return movement has in the direction of its end-of-conveyance position Fig. 2a moves. The valve 6 is closed and on the inflow side due to resulting Negative pressure via the opening inlet valve 9 Fluid is sucked from the reservoir into the inflow space. At the same time, fluid from the pressure chamber 7 via the open exhaust valve 10 displaced in the work space. It can be seen that the amount of fluid displaced here depends on the cross-sectional ratio of the Low-pressure delivery piston 4 to the high-pressure delivery piston 11. It becomes all the more fluid in the low pressure stage conveyed into the work space via the outlet valve 10, the greater the - effective - cross-sectional ratio of the two pistons.

Mit Bezug zu den Fig. 3a bis 3c ist ein entsprechender Förderzyklus dargestellt, bei welchem angenommen ist, daß der Druck in dem Arbeitsraum größer ist als die Vorspannung des Niederdrucks-Förderkolbens 4 in seiner Förder-Endstellung. Der Druck soll wesentlich größer sein als der zunächst genannte Druck von ca. 10 Bar. Maßgebend ist, daß der Druck im Arbeitsraum größer ist als der durch die Schraubenfeder (Druckfeder 3) in der oberen, maximal vorgespannten Stellung des Niederdruck-Förderkolbens 4 ist.3a to 3c is a corresponding one Shown funding cycle, in which it is assumed that the pressure in the work space is greater than that Biasing the low-pressure delivery piston 4 in its Conveyor-end position. The pressure is said to be much greater than the initially mentioned pressure of approx. 10 bar. It is important that the pressure in the work area is greater than that by the coil spring (compression spring 3) in the upper, maximum preloaded position of the low-pressure delivery piston 4 is.

In Fig. 3a ist die Förder-Endstellung des Hochdruckkolbens 11 dargestellt. Der Hochdruck-Förderkolben 11 ist maximal in den Druckraum 7 eingefahren.In Fig. 3a is the delivery end position of the high pressure piston 11 shown. The high-pressure delivery piston 11 is maximally moved into the pressure chamber 7.

In Fig. 3b ist ein Zustand dargestellt, bei welchem sich der Hochdruck-Förderkolben 11 auf dem Rückhubweg befindet. Das Auslaßventil 10 ist geschlossen, da der Druck in dem Druckraum 7 nur noch durch die Feder 3 bestimmt ist. Beispielsweise kann dies ein Druck zwischen 10 und 20 Bar sein. Dieser Druck ist damit wesentlich kleiner als der in diesem Zustand als hoch anzunehmende Druck in dem Arbeitsraum. Der abfallende Druck bzw. der Ausgleich, der durch den herausfahrenden Hochdruck-Förderkolben 11 sich ergebenden Volumenvergrößerung führt zu einer Nachlaufbewegung des Niederdruck-Förderkolbens 4. Hierdurch wird zugleich durch das sich öffnende Zulaufventil 9 Fluid aus dem Vorratsbehältnis in den Zufluß 8 eingesogen. Der Niederdruck-Förderkolben 4 erreicht hierbei nicht die Förder-Endstellung gemäß Fig. 2a, sondern eine hierzu in Förderrichtung vorgelagerte Stellung, bis ein Ausgleich des Volumenanteils des sich herausbewegenden Teils des Hochdruck-Förderkolbens 11 erreicht ist.3b shows a state in which the high-pressure delivery piston 11 on the return stroke located. The outlet valve 10 is closed because of Pressure in the pressure chamber 7 only by the spring 3rd is determined. For example, this can be a pressure between 10 and 20 bar. This pressure is essential smaller than the one to be assumed as high in this state Pressure in the work space. The falling pressure or the compensation caused by the high-pressure delivery piston moving out 11 resulting volume increase leads to a wake of the low-pressure delivery piston 4. This is at the same time through the opening inlet valve 9 fluid from the reservoir sucked into the inflow 8. The low pressure delivery piston 4 does not reach the end of delivery position 2a, but one for this in the conveying direction upstream position until an equalization of the volume share the moving out part of the high pressure delivery piston 11 is reached.

In Fig. 3c ist ein Zeitpunkt Im Förderhub des Hochdruck-Förderkolbens 11 dargestellt. Der Hochdruck-Förderkolben 11 ist (noch) nicht in Anlage an dem Niederdruck-Förderkolben 4. Aufgrund der jedoch gegebenen Druckerhöhung ist das Einlaßventil 9 geschlossen. Dagegen ist das Auslaßventil 10 geöffnet, da der Druck in dem Druckraum 7 sich aufgrund des eingefahrenen Hochdruck-Förderkolbens 11 so erhöht hat, daß er den Druck in dem Arbeitsraum übersteigt.3c is a point in time in the delivery stroke of the high-pressure delivery piston 11 shown. The high pressure delivery piston 11 is not (yet) in contact with the low-pressure delivery piston 4. Due to the given Pressure increase, the inlet valve 9 is closed. On the other hand the outlet valve 10 is open because the pressure in the pressure chamber 7 due to the retracted high-pressure delivery piston 11 has increased so that the pressure in the work room.

Mit Bezug zu Fig. 4 ist eine weitere Ausführungsform der Kolbenpumpe 1 dargestellt. Die wiedergegebene Stellung entspricht der Fig. 3a, wobei diese Stellung sich hier jedoch sowohl auf einen Niederdruck- wie einen Hochdruckzyklus beziehen kann.4 is another embodiment the piston pump 1 shown. The position shown corresponds to Fig. 3a, this position itself here, however, on both a low-pressure and one High pressure cycle can relate.

Das Einlaßventil 9, das Auslaßventil 10 und der Hochdruck-Förderkolben 11 sind im wesentlichen unverändert.The inlet valve 9, the outlet valve 10 and the high-pressure delivery piston 11 are essentially unchanged.

Der Niederdruck-Förderkolben 4 weist hier jedoch rückseitig einen stilartigen Fortsatz 13 auf. Dies jedenfalls funktionsmäßig.However, the low-pressure delivery piston 4 faces the rear here a stylish extension 13. In any case functionally.

Tatsächlich ist der stilartige Fortsatz 13 an einem Teller 14, welcher hier Teil des Ventils 6 ist, ausgebildet. Das Ventil 6 bzw. bei der konkreten Ausführungsform der Teller 14 weist weiter einen vorderseitigen Betätigungsfortsatz 15 auf.In fact, the stylish extension 13 is on one Plate 14, which is part of the valve 6 here, is formed. The valve 6 or in the specific embodiment the plate 14 also has a front Actuation extension 15 on.

Der stilartige Fortsatz 13 führt zu einem minimalen Fluid-Volumen in Zuflußraum 8. Dieses ist erwünscht, um dort gewisse Strömungsgeschwindigkeiten zu erreichen. Im weiteren auch, um beim (Hochdruck-) Förderhub ein möglichst geringes Zurückweichen aufgrund einer durch die Hydraulikflüssigkeit gegebenen Federbarkeit zu erreichen. Allgemein ist es jedoch wesentlich, daß für die Pumpe ein Fluid verwendet wird, das im wesentlichen inkompressibel ist. Es bieten sich hier übliche - ölartige - Hydraulikflüssigkeiten an.The stylish extension 13 leads to a minimal Fluid volume in inflow space 8. This is desirable to to achieve certain flow velocities there. Furthermore, in order to enter the (high pressure) delivery stroke as little recoil as possible due to the hydraulic fluid to given elasticity to reach. In general, however, it is essential that for the pump uses a fluid that is essentially is incompressible. There are common - oily ones - hydraulic fluids.

In weiterer Einzelheit ist die Schraubenfeder 3 bei der Ausführungsform der Fig. 4 umgebend zu dem zylinderartigen Fortsatz 13 angeordnet.In further detail, the coil spring 3 is in the Embodiment of FIG. 4 surrounding the cylindrical Extension 13 arranged.

In dem Kolbenboden 17 des Niederdruck-Förderkolbens 4 sind Durchströmöffnungen 18 ausgebildet, welche bei dieser Ausführungsform den Fluid-Förderweg 5 bilden. Wie ersichtlich ist durch Anlage-Kontakt zwischen einer Stirnfläche 19 des Hochdruck-Förderkolbens 11 und dem Betätigungsfortsatz 15 des Ventils 6 eine Öffnung des Ventils 6 erreicht, so daß durch die Öffnungen 18 in dem Kolbenboden 17 des Niederdruck-Förderkolbens 4 Fluid aus dem Zuflußraum 8 in den Druckraum 11 strömt. Das Ventil 6 der Ausführungsform gemäß Fig.4 ist somit nicht druckbetätigt, sondern zwangsgesteuert.In the piston crown 17 of the low-pressure delivery piston 4 Flow openings 18 are formed, which at this embodiment form the fluid delivery path 5. As can be seen through plant contact between one End face 19 of the high pressure delivery piston 11 and the Actuation extension 15 of the valve 6 an opening of the Valve 6 reached so that through the openings 18 in the piston crown 17 of the low-pressure delivery piston 4 Fluid flows from the inflow space 8 into the pressure space 11. The valve 6 of the embodiment according to FIG. 4 is thus not pressure operated, but positively controlled.

In weiterer Einzelheit ist von Bedeutung, daß bei der Ausführungsform der Fig. 4 der Kolbenboden 31 als Einschraubteil ausgebildet ist. Es besitzt seitenwandseitig ein Außengewinde 33, das mit einem entsprechenden Innengewinde des Pumpgehäuses 32 zusammenwirkt. Hierdurch ist ein einfacher Austausch ermöglicht bzw. eine Wartungsfreundlichkeit gegeben.In more detail, it is important that the 4 the piston crown 31 as a screw-in part is trained. It has a side wall an external thread 33 with a corresponding Internal thread of the pump housing 32 cooperates. hereby is a simple exchange possible Ease of maintenance given.

In der Ausführungsform der Fig. 6 ist dargestellt, daß sowohl die Kolbenführung für den Hochdruck-Förderkolben 11 wie der Kolbenboden für den Niederdruck-Förderkolben 4 einschraubbar ausgebildet sind. Bevorzugt ist es, nur die Kolbenführung für den Hochdruck-Förderkolben 11 einschraubbar auszubilden.In the embodiment of Fig. 6 it is shown that both the piston guide for the high pressure delivery piston 11 like the piston crown for the low-pressure delivery piston 4 are designed to be screwed in. It is preferred only the piston guide for the high-pressure delivery piston 11 trained to be screw-in.

Weiter ist von Bedeutung, daß bei dieser Ausführungsform in dem Niederdruck-Förderkolben 4, nämlich dem zylinderartigen Fortsatz, ein Durchströmungsweg ausgebildet ist, in welchem ein übliches Rückschlagventil angeordnet ist. Hierdurch ist es möglich, einerseits das in der komprimierten Stellung der Feder 3 noch gegebene Volumen weiterhin möglichst klein zu halten, andererseits aber insbesondere auch einen solchen Strömungsweg auszubilden, daß immer relativ hohe Strömungsgeschwindigkeiten sichergestellt sind. Wesentlich ist auch, daß die Konstruktion so ausgebildet ist, daß wenig oder keine Todräume gegeben sind.It is also important that in this embodiment in the low-pressure delivery piston 4, namely the cylindrical extension, a flow path is formed is in which a usual check valve is arranged. This makes it possible, on the one hand still in the compressed position of the spring 3 keep the given volume as small as possible, on the other hand, in particular, such a flow path train that always relatively high flow rates are ensured. Is essential also that the construction is such that there are little or no dead spaces.

Unter Bezug auf Fig. 5 ist ein handbetriebenes Motorwerkzeug mit einer Kolbenpumpe gemäß der vorstehend erläuterten Ausführungsform Fig. 4 dargestellt.Referring to Fig. 5 is a hand-held power tool with a piston pump according to the above illustrated embodiment Fig. 4 shown.

In dem handbetriebenen Motorwerkzeug 20 ist ein Elektromotor 21 angeordnet, der ein Untersetzungsgetriebe 22 aufweist. Das Untersetzungsgetriebe 22 wirkt über eine Welle 23 auf einen Exzenter 24, der seinerseits über ein Wälzlager 25 auf den Hochdruck-Förderkolben 11 einwirkt. There is an electric motor in the hand-operated power tool 20 21 arranged, the reduction gear 22nd having. The reduction gear 22 acts via a Shaft 23 on an eccentric 24, which in turn over a roller bearing 25 on the high-pressure delivery piston 11 acts.

In der zuvor erläuterten Weise wird hierzu aus dem Fluid-Vorratsraum 26 Fluid in den Arbeitsraum 27 gepumpt und hierdurch ein Arbeitskolben 28 entgegen der Wirkung einer Rückstellfeder 29 in seine Arbeits-Endstellung bewegt. Die Zurückbewegung des Arbeitskolbens 28 erfolgt über die Rückstellfeder 29, wenn - was hier im einzelnen nicht dargestellt ist - ein Ablaufventil des Arbeitsraumes 27 geöffnet ist, über welches das Fluid sodann in den Vorratsraum 26 zurückströmen kann. Der Antrieb des Elektromotors 21 erfolgt in weiterer Einzelheit über eine Batterie oder einem Akkumulator 30.In the manner explained above, the Fluid storage space 26 fluid pumped into the working space 27 and thereby a working piston 28 against the Effect of a return spring 29 in its working end position emotional. The return movement of the working piston 28 takes place via the return spring 29 if - what here is not shown in detail - a drain valve of the work space 27 is open, through which the Fluid can then flow back into the storage space 26. The electric motor 21 is driven further Detail about a battery or an accumulator 30.

Bei der Ausführungsform der Fig. 7 ist der Hochdruck-Förderkolben 11 unmittelbar durch einen Handhebel 34 betätigt. Der Hochdruckkolben 11 ist hierzu im einzelnen mit einem koaxial ausgerichteten Anschlußstück 35 verbunden, das mittels einer Hakenausformung 36 mit einem Mitnahmebolzen 37 des Handhebels 34 gekuppelt ist. Der Handhebel ist über einen hiervon unabhängigen Drehbolzen 38 an dem Gehäuse 39 gelagert.In the embodiment of Fig. 7 is the high pressure delivery piston 11 directly by a hand lever 34 actuated. The high-pressure piston 11 is for this in detail with a coaxially aligned connector 35 connected, which by means of a hook formation 36 a driving pin 37 of the hand lever 34 coupled is. The hand lever is independent of this Pivot pin 38 mounted on the housing 39.

Im übrigen verhält sich die Kolbenpumpe 1 bei der Ausführungsform der Figur 7 in gleicher Weise wie die Kolbenpumpe 1 der zuvor beschriebenen Ausführungsformen, so daß hierauf Bezug genommen wird.Otherwise, the piston pump 1 behaves in the embodiment of Figure 7 in the same way as that Piston pump 1 of the previously described embodiments, so that reference is made to this.

Claims (13)

  1. A piston pump (1) for delivering a fluid at low pressure and at high pressure, there being a greater delivery rate in a pump cycle at low pressure than at high pressure, the piston pump comprising a low pressure delivery piston (4) which is moved in a pump cylinder (2) and which impinges on a pressure chamber (7) in its end delivery position under prestress, a high pressure delivery piston (11), an inlet valve and an outlet valve (9, 10), in addition, a fluid delivery channel (5) being provided between the inlet valve and the outlet valve (9, 10), and the low pressure delivery piston (4) being moved back into a delivery starting position against its prestress, characterised in that the fluid delivery channel (5) passes through the low pressure delivery piston (4), in that a valve (6) which locks on movement into the delivery starting position is located in the low pressure delivery piston (4), in that the high pressure delivery piston (11) and the low pressure delivery piston (4) work in a common pressure chamber (7), and in that the high pressure delivery piston (11) moves the low pressure delivery piston (4) against its prestress.
  2. Piston pump according to Claim 1, characterised in that the high pressure delivery piston (11) has a smaller cross-section than the low pressure delivery piston (4).
  3. Piston pump according to one or more of the preceding claims, characterised in that the valve (6) is a pressure-actuated non-return valve.
  4. Piston pump according to one or more of the preceding claims, characterised in that the valve (6) is a positively controlled valve.
  5. Piston pump according to one or more of the preceding claims, characterised in that the high pressure delivery piston (11) actuates the valve (6).
  6. Piston pump according to one or more of the preceding claims, characterised in that the valve (6) is formed as a disk valve.
  7. Piston pump according to one or more of the preceding claims, characterised in that the valve (6) has an actuation end (15) which passes through the piston base (17) of the low pressure delivery piston (4).
  8. Piston pump according to one or more of the preceding claims, characterised in that the prestress is achieved by a spring (3).
  9. Piston pump according to one or more of the preceding claims, characterised in that the spring (3) prestresses the valve (6) into the closed position.
  10. Piston pump according to one or more of the preceding claims, characterised in that the low pressure delivery piston (4) has at its rear side a column-type continuation (13), in order to reduce the fluid flow path between the inlet valve (9) and the low pressure delivery piston (4).
  11. Piston pump according to one or more of the preceding claims, characterised in that the pump cylinder (2) has a pump cylinder base (31) which is operationally openable.
  12. Piston pump according to one or more of the preceding claims, characterised in that the pump cylinder base (31) is secured by screw connection in a pump housing (32).
  13. Piston pump according to one or more of the preceding claims, characterised in that the pump cylinder base (31) is pot-shaped, there being a screw-in thread (33) on a peripheral outer wall of the pot.
EP98924218A 1997-07-19 1998-04-25 Piston pump Expired - Lifetime EP0927305B1 (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19731054 1997-07-19
DE19731054 1997-07-19
DE19743747 1997-10-02
DE19743747A DE19743747B4 (en) 1997-07-19 1997-10-02 piston pump
PCT/EP1998/002474 WO1999004165A1 (en) 1997-07-19 1998-04-25 Piston pump

Publications (2)

Publication Number Publication Date
EP0927305A1 EP0927305A1 (en) 1999-07-07
EP0927305B1 true EP0927305B1 (en) 2003-01-15

Family

ID=26038426

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98924218A Expired - Lifetime EP0927305B1 (en) 1997-07-19 1998-04-25 Piston pump

Country Status (9)

Country Link
US (1) US6206663B1 (en)
EP (1) EP0927305B1 (en)
JP (1) JP4138897B2 (en)
AT (1) ATE231217T1 (en)
AU (1) AU7649598A (en)
DK (1) DK0927305T3 (en)
ES (1) ES2187973T3 (en)
TW (1) TW401484B (en)
WO (1) WO1999004165A1 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008024018A1 (en) 2007-05-16 2008-11-20 Gustav Klauke Gmbh Method for operating a motor-operated hand crusher and hand crusher
WO2014049035A1 (en) 2012-09-28 2014-04-03 Gustav Klauke Gmbh Portable tool, portable expanding apparatus, hydraulic piston/cylinder arrangement and method for operating a portable tool
EP3091230A1 (en) * 2015-04-23 2016-11-09 Robert Bosch Gmbh Hydrostatic piston machine

Families Citing this family (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6810236B2 (en) * 2001-05-14 2004-10-26 Interdigital Technology Corporation Dynamic channel quality measurement procedure for adaptive modulation and coding techniques
US6446482B1 (en) 2001-09-17 2002-09-10 Fci Americas Technology, Inc. Battery operated hydraulic compression tool with rapid ram advance
US6579079B2 (en) 2001-09-27 2003-06-17 Diamond Machine Werks, Inc. Rotary valve and piston pump assembly and tank dispenser therefor
KR100826799B1 (en) * 2002-03-20 2008-05-02 주식회사 만도 Pump of electronic control brake system
US6668613B2 (en) * 2002-04-09 2003-12-30 Fci Americas Technology, Inc. Hydraulic compression tool and hydraulic compression tool motor
US6666064B2 (en) 2002-04-19 2003-12-23 Fci Americas Technology, Inc. Portable hydraulic crimping tool
DE10329007A1 (en) * 2003-06-27 2005-01-13 Gustav Klauke Gmbh Locking bolt for attaching a tool to a hydraulic pressing device
EP2070660B1 (en) 2007-12-14 2012-09-26 Gustav Klauke GmbH Hydraulic pressing tool
DE102008023719A1 (en) 2007-12-14 2009-06-18 Gustav Klauke Gmbh Hydraulic pressing tool, has moving part whose return movement takes place by opening return valve based on predetermined, adjustable pressing pressure, where pressing pressure is gradually adjusted
DE102009020999A1 (en) * 2009-05-12 2010-11-18 Hydac System Gmbh lashing platform
EP2718067B1 (en) 2011-04-11 2023-10-11 Milwaukee Electric Tool Corporation Hydraulic hand-held knockout punch driver
DE102011052350A1 (en) 2011-08-02 2013-02-07 Gustav Klauke Gmbh Pair of jaws for punching out holes
CN103161725A (en) * 2011-12-16 2013-06-19 东台兴业股份有限公司 Piston-type pressure pump
CN102619739B (en) * 2012-04-09 2015-04-15 台州巨力工具有限公司 Variable plunger pump
CN204573232U (en) 2012-07-31 2015-08-19 米沃奇电动工具公司 Multifunction valve
DE102013100183A1 (en) 2013-01-09 2014-07-10 Gustav Klauke Gmbh Hydraulically actuated pressing device, method for carrying out a compression, method for producing an electrically conductive press connection, electrically pressed press sleeve, method for clamping a workpiece and hydraulic device
DE102013101978A1 (en) 2013-02-28 2014-08-28 Gustav Klauke Gmbh Hydraulic press tool e.g. hand-operated press tool, has piston retracted to initial position by moving return valve into open position, where return valve is displaced by mechanical effect by rotating portion of hand lever around axis
DE102016219220B4 (en) * 2016-10-04 2020-10-01 Hawe Hydraulik Se Hydraulic drive
DE102016122464B4 (en) * 2016-11-22 2020-11-12 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Liquid pump for conveying liquid
WO2018109521A1 (en) * 2016-12-12 2018-06-21 Arkling Limited Pressure transfer device for an inverse osmosis fluid treatment installation
DE102018103610B3 (en) * 2018-02-19 2019-02-14 Hanon Systems Apparatus for damping pressure pulsations for a gaseous fluid compressor
CN108412751B (en) * 2018-03-14 2024-02-06 宁波合力机泵股份有限公司 Hydraulic end of reverse suction and discharge self-balancing booster pump
ES2774427B2 (en) * 2019-01-21 2022-03-15 Samoa Ind S A LOW PRESSURE STARTING DEVICE FOR PNEUMATIC PUMPS
TWI717112B (en) * 2019-11-19 2021-01-21 科頡工業股份有限公司 Piston pump and clamping device with the piston pump
CN112901474B (en) * 2019-11-19 2023-03-31 科颉工业股份有限公司 Piston pump and clamping device with same

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US432107A (en) 1890-07-15 Roll-paper holder and cutter
US674381A (en) 1900-07-27 1901-05-21 Emil Frank Haenchen Guard attachment for cash-registers.
US2510150A (en) * 1945-02-01 1950-06-06 Hydraulic Equipment Company Variable capacity reciprocating pump
US2688231A (en) 1951-06-20 1954-09-07 Manco Mfg Co Piston actuated hydraulic pressure tool
US2938465A (en) * 1953-08-31 1960-05-31 Arthur E Mcfarland Combined high and low pressure pumping apparatus
US2845033A (en) 1954-07-08 1958-07-29 Tokheim Corp Diaphragm pump
US2820415A (en) * 1956-03-12 1958-01-21 Ray W Born Low pressure, high volume-high pressure, low volume pump
DE1283680B (en) * 1957-07-30 1968-11-21 Tecalemit Gmbh Deutsche Two-stage piston pump
US3016838A (en) * 1959-02-09 1962-01-16 Bessiere Pierre Etienne Reciprocating action pumps, in particular fuel injection pumps
GB1411978A (en) * 1972-08-31 1975-10-29 Lister Co Ltd R A Lubricating pump
IT1149409B (en) * 1982-01-07 1986-12-03 Cembre Srl MANUAL HYDRAULIC JACK FOR COMPRESSION OF ELECTRIC CONNECTORS ON ELECTRICAL CABLES AND CONDUCTORS IN GENERAL
JPS63131873A (en) * 1986-11-21 1988-06-03 Kosumetsuku:Kk Plunger pump of rapid pressure buildup type
US5195354A (en) 1989-03-31 1993-03-23 Japan Storage Battery Co., Ltd. Cam crank mechanism and motor driven hydraulic tool
DE9416535U1 (en) 1994-10-14 1994-12-01 Klauke Gmbh & Co Gustav Handheld device for punching holes
US5575627A (en) * 1995-01-12 1996-11-19 Hyvair Corporation High and low pressure two stage pump and pumping method
DE19649932A1 (en) 1996-12-02 1998-06-04 Klauke Gmbh Gustav Hydraulic hand tool

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008024018A1 (en) 2007-05-16 2008-11-20 Gustav Klauke Gmbh Method for operating a motor-operated hand crusher and hand crusher
EP2722133A2 (en) 2007-05-16 2014-04-23 Gustav Klauke GmbH Method for operating a motor-actuated manual injection device and manual injection device
EP3243604A1 (en) 2007-05-16 2017-11-15 Gustav Klauke GmbH Motor-driven manual pressing device and method for operating a motor-driven manual pressing device
DE102008024018B4 (en) 2007-05-16 2024-04-18 Gustav Klauke Gmbh Method for operating a motor-operated hand pressing device and hand pressing device
WO2014049035A1 (en) 2012-09-28 2014-04-03 Gustav Klauke Gmbh Portable tool, portable expanding apparatus, hydraulic piston/cylinder arrangement and method for operating a portable tool
DE102012109255A1 (en) 2012-09-28 2014-04-03 Gustav Klauke Gmbh Hand tool, hand widening device, hydraulic piston / cylinder assembly and method of operating a hand tool
EP3091230A1 (en) * 2015-04-23 2016-11-09 Robert Bosch Gmbh Hydrostatic piston machine

Also Published As

Publication number Publication date
ES2187973T3 (en) 2003-06-16
JP4138897B2 (en) 2008-08-27
US6206663B1 (en) 2001-03-27
JP2001504909A (en) 2001-04-10
ATE231217T1 (en) 2003-02-15
DK0927305T3 (en) 2003-05-05
EP0927305A1 (en) 1999-07-07
WO1999004165A1 (en) 1999-01-28
TW401484B (en) 2000-08-11
AU7649598A (en) 1999-02-10

Similar Documents

Publication Publication Date Title
EP0927305B1 (en) Piston pump
DE102004013307B4 (en) High-pressure fuel pump with a pressure relief valve
EP1411238A1 (en) Pressure regulating valve for an injection system
DE3248622C2 (en) High pressure cleaning device
DE3044363C2 (en)
DE102012219621A1 (en) piston pump
DE3934124A1 (en) COMPRESSED AIR PUMP ARRANGEMENT
EP2483560A1 (en) Pump for a high-pressure cleaning device
DE3447091A1 (en) OIL PUMP
EP1072796A2 (en) Screw-type compressor
DE60301312T2 (en) Fuel pump assembly
DE102012022997A1 (en) Adjustment device for a hydraulic machine and hydraulic axial piston machine
DE19743747B4 (en) piston pump
DE2736597A1 (en) ELECTROMAGNETIC PUMP
DE102004024126A1 (en) Hydraulic drive for a punch of forming machine has an active surface acting in the driving direction and delimiting an annular chamber which is connected to a switching valve
DE10139055A1 (en) Method, computer program, control and / or regulating device and fuel system for an internal combustion engine
EP1247983B1 (en) Piston pump for hydraulic systems
DE409075C (en) Press with transfer fluid between the punch and its drive member
EP0331958B1 (en) Hydraulic control device
DE4207764C2 (en) Hydraulic tool with a fully integrated hydraulic circuit
DE4315776A1 (en) Fuel injection pump
EP1160451A2 (en) Piston pump
DE2114044A1 (en) Control device for controlling fluid motors
DE102016223113B3 (en) transmission device
DE10249688A1 (en) High-pressure fuel pump for a fuel injection system, in particular a common rail fuel injection system, of internal combustion engines

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19990120

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: R. A. EGLI & CO. PATENTANWAELTE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

REF Corresponds to:

Ref document number: 59806928

Country of ref document: DE

Date of ref document: 20030220

Kind code of ref document: P

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CY

Payment date: 20030321

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: MC

Payment date: 20030403

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FI

Payment date: 20030404

Year of fee payment: 6

Ref country code: LU

Payment date: 20030404

Year of fee payment: 6

Ref country code: IE

Payment date: 20030404

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GR

Payment date: 20030422

Year of fee payment: 6

REG Reference to a national code

Ref country code: GR

Ref legal event code: EP

Ref document number: 20030401195

Country of ref document: GR

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20030519

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2187973

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20031016

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040425

Ref country code: FI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040425

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040426

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20041103

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20151126

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: PT

Payment date: 20160317

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20160419

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20160420

Year of fee payment: 19

Ref country code: CH

Payment date: 20160420

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20160419

Year of fee payment: 19

Ref country code: SE

Payment date: 20160421

Year of fee payment: 19

Ref country code: AT

Payment date: 20160419

Year of fee payment: 19

Ref country code: DK

Payment date: 20160421

Year of fee payment: 19

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20170518

Year of fee payment: 20

Ref country code: FR

Payment date: 20170424

Year of fee payment: 20

Ref country code: GB

Payment date: 20170412

Year of fee payment: 20

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20170430

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: NL

Ref legal event code: MM

Effective date: 20170501

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 231217

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170501

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171025

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170426

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20170430

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59806928

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20180510

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20180424

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170430

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20180424

Ref country code: PT

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20180508

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170426