EP0991863B1 - Radialkolbenpumpe mit dichtung am antriebswellenende zur fluiddichten kapselung des pumpenraumes - Google Patents
Radialkolbenpumpe mit dichtung am antriebswellenende zur fluiddichten kapselung des pumpenraumes Download PDFInfo
- Publication number
- EP0991863B1 EP0991863B1 EP98936190A EP98936190A EP0991863B1 EP 0991863 B1 EP0991863 B1 EP 0991863B1 EP 98936190 A EP98936190 A EP 98936190A EP 98936190 A EP98936190 A EP 98936190A EP 0991863 B1 EP0991863 B1 EP 0991863B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- eccentric
- piston pump
- radial piston
- housing
- pump according
- 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
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Classifications
-
- 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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
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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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0448—Sealing means, e.g. for shafts or housings
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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
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/045—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being eccentrics
Definitions
- the invention relates to a radial piston pump, in particular a High-pressure gasoline pump, according to the preamble of claim 1.
- Radial piston pumps of this type are used as fuel pumps used for internal combustion engines. Fuel delivery takes place via at least one radial piston, which is driven by a Eccentric of a shaft is operated. Usually three are Radial piston evenly provided on the outer circumference of the eccentric shaft. Each of the radial pistons lies over a slide shoe and one Eccentric ring on the eccentric shaft. The eccentric ring is over a plain bearing rotatably mounted on the eccentric shaft and guaranteed safe guidance of the slide shoe with minimal friction losses.
- the cylinders for receiving the radial pistons are in the pump housing arranged and each with a suction and pressure valve provided, through which the fuel is sucked out of the crankcase or the pressurized fuel to the internal combustion engine is.
- This known radial piston pump is lubricated via its own lubricant circuit, in which the lubricant through an axial bore of the eccentric shaft to the shaft bearings and the plain bearing of the eccentric ring is guided.
- a radial piston pump (DE 197 01 392 A1) is also known, where there is a cam on the drive shaft approximately in the middle of one Is located by an axially arranged Separator in a working fluid area and a lubricant area is divided. Because the flexible separating element is therefore a large one Has expansion in the axial direction, also results in this Pump a high manufacturing effort.
- the invention has for its object the generic To design radial piston pump so that leakage flows with minimal expenditure on device technology can be reduced.
- a radial piston pump thus has a separator with a housing side and a eccentric sealing element on, the fluid-tight with each other are connected, the separating device receiving spaces for conveyors or working fluid and lubricants separates from each other.
- An eccentric element takes one Rotational movement from a drive shaft to and transmits this so that on a conveyor element that is a sliding block can be a radial movement. It is eccentric sealing element in the circumferential direction of the eccentric element slidable and the housing-side sealing element arranged fluid-tight on the pump housing.
- the eccentric element is at an end portion of the drive shaft or eccentric shaft arranged and the drive shaft is supported by a shaft bearing in the pump housing.
- the eccentric element in the form of an axial projection on the drive shaft trained, whereby a small number of components is achieved becomes.
- the eccentric sealing element is cap-shaped trained so that the scope with only one component of the eccentric element is sealable.
- cap-shaped Sealing element is a thin-walled component in the form of a Plain bearing or as an outer ring of a rolling bearing. On in this way, the efficiency of the radial piston pump increase with good sealing at the same time.
- a pressure device on the bottom of the eccentric side Sealing element can be the eccentric Preload the sealing element against the eccentric element, whereby energy losses through a game of the eccentric Have the sealing element reduced.
- the eccentric element in the form of a Axial groove.
- the length can be reduce the drive shaft and can be annoying Noise in bearings and wear of the bearings limit.
- this is the eccentric side Sealing element preferably in the axial direction extending coupling element, the movements of the drive shaft transfers to the shoe and its end section is rotatably supported in the axial recess. Consequently is the funding through an elastic separating element and the lubricant is separable in line form this way the effects of axial forces better received.
- the eccentricity is greater than the stroke of the slide shoe.
- the stroke of the conveyor element is dependent of lever ratios of the coupling element adjustable.
- a sealing element between the eccentric and the housing-side sealing element takes in particularly good Way the relative movement between the sealing elements and Axial forces between the funding receiving space and the Lubricant receiving space.
- the elastic element can be tight on the coupling element concern what a corresponding profile design for requires elastic element, or attached to this be, in which case the influence of material fatigue is reduced as the cause of the error.
- the eccentric shaft unilaterally store and at the cantilevered free end of the eccentric shaft to form a cap-shaped eccentric ring that the covers the free end face of the eccentric shaft and its Ring end faces act on a shaft seal that between the shaft bearing and the eccentric is, the lubricant circuit can reliably from the Funding cycle, especially in the crankcase arranged funds are separated.
- the cap-shaped Eccentric ring works practically with this construction as part of the shaft seal and helps keep the free To enclose the end section of the eccentric shaft in a sealing manner.
- the assembly is due to the one-sided shaft bearing the eccentric shaft compared to conventional solutions split bearings, which are arranged on both sides of the eccentric are significantly simplified, so that the assembly costs are reduced compared to the previously known solution.
- the pressure of the cap-shaped eccentric ring on the Shaft seal can be due to the fluid pressure in the Crank chamber.
- the sealing effect can, however increase further if on the bottom of the eccentric ring Pressure device acts against the eccentric ring the seal is pressed.
- This pressure device advantageously has one angle-adjustable pressure ring, which has a biasing spring biased against the cap-shaped eccentric ring is.
- Shaft sealing device preferably has a slide ring, on the one sliding surface of which the pressure ring acts and through which a sealing ring against the shaft and the shaft bearing is pressed.
- the one-sided shaft bearing is preferably by realized a grease-filled roller bearing arrangement.
- the Area between the drive end portion of the Eccentric shaft and the shaft bearing another sealing device arranged.
- the assembly of the radial piston pump is particularly simple, if the shaft bearing in the pump bowl of the housing is arranged.
- the radial piston pump 1 shown in Fig. 1 has a Pump housing with a housing pot 4 through a Housing cover, hereinafter referred to as housing flange 6, closed is.
- housing flange 6 In the pump housing there are a large number, for example three cylinder receiving spaces 8 formed in which each one of the conveyor units 2 is included.
- a circumferential, gas-tight seal 9 In the parting line between housing pot 4 and housing flange 6 a circumferential, gas-tight seal 9 is arranged, which is similar to a cylinder head gasket is.
- the two housing parts are by means of clamping screws 11 screwed together.
- the conveyor units 2 are driven by a Eccentric shaft 10, which is mounted in the housing pot 4.
- the Lubrication / cooling of the shaft bearings is done with a dashed line Lubricant circuit 7 shown.
- the subsidy, in this case petrol, is via an input connection, not shown, into a formed between the housing pot 4 and the housing flange 6 Crank chamber 16 with a predetermined form (1 to 3 bar) supplied and after pressurization via a also not shown output connection to the internal combustion engine directed.
- the present invention is not limited to that Limited separation of funds and lubricants, any fluids can be separated, whereby also two fluids of the same fluid type with, for example different pressure and / or different temperature can be present.
- the eccentric shaft 10 has an eccentric element 20, the Center around the eccentricity measure e compared to the Axis of rotation 22 of the eccentric shaft 10 is offset.
- the drive shaft 10 in the exemplary embodiments according to the invention only mounted on one side, a grease-filled one designed as a roller bearing Shaft bearing 18 in an axial bore 24 of the housing pot 4 is attached.
- the axial bore 24 is provided with a radial shoulder 26, at which the left end section of the shaft bearing 18 in FIG. 1 is supported.
- the rotational movement of the drive shaft 10 is determined by a further below described transmission device in an orbital movement of a Eccentric sealing element 36 designed as an eccentric ring trained eccentric sealing element converted.
- Under Orbital movement is the movement on a circle without change understand the alignment when looking at the top of the circle.
- the Sealing element 36 is flattened at its upper end section in the figure, the flattening somewhat perpendicular to the plane of the drawing in the figure runs. Retains during rotation of the drive shaft 10 the flattening their orientation to the conveyor unit 2, so that a defined investment area is created. Because of the wobble of the eccentric element 20 performs the sealing element 36 a compensating movement so that between conveyor unit 2 and flattening a relative shift approximately perpendicular to the plane of the drawing he follows. With regard to further details of the conveyor unit 3, see the refer to the following explanations.
- the housing pot 4 and the housing flange 6 delimit the crank chamber 16, from which the receiving spaces 8 for the conveyor units 2 extend in the axial direction.
- Each of these conveyor units 2 has a stationary, cylindrical piston 52, which is fixed radially in the parting plane between the housing pot 4 and the housing flange 6 and on which an oscillating cylinder 54 is guided.
- the piston 52 is fastened by means of a clamping device with a clamping piece 56, which can be fixed by a clamping screw 58.
- the latter passes through a flange 60 of the housing pot 4.
- the cylinder 54 guided on the piston 52 has on its circumference an annular end face 62 on which a compression spring 64 engages, the other end of which is supported by a spring plate mounted on the housing.
- the cylinder 54 is biased by the compression spring 36 toward the outer periphery of the eccentric ring 36.
- the clamping screw 58 other suitable devices for clamping the piston 52 can also be used, for example leaf spring and elastomer elements can be used. Highly precise receptacles are provided in the parting plane, which enable the piston 52 to be easily positioned.
- the cylindrical piston can be very easily machined, for example by centerless grinding.
- the sliding block 50 has an axially extending one Guide pin 66, which in the the fixed Plunger 52 engages cylinder bore 68. On the guide pin 66 closes a guide flange 70 of the slide shoe 50, the opposite in the radial direction the guide pin 66 is expanded.
- the cylinder 54 lies on the ring end face facing away from the eccentric ring 36 of the guide flange 70.
- the sliding shoe 50 has a central through hole 72 which is in a tangential slot 74 of the eccentric ring 36 opens.
- a suction valve is attached, which in the embodiment shown is designed as a plate valve 76 via that the connection to the cylinder space can be opened or closed is.
- the plate of the plate valve 76 has through holes 78 (only one shown), which at dated Valve seat lifted plate a fluid connection of the Cylinder space with the through hole 72 allows.
- the plate of the plate valve 76 is in the Illustration indicated compression spring in its closed position biased.
- the axial movement of the plate away from that Valve seat is on the end face of the guide pin 66 limited by a stop ring 80 in the cylinder bore 68.
- the contact surfaces for the plate on the front of the guide pin 66 and on the stop ring 80 designed as valve seat surfaces.
- a separate fastening screw can also be used used to fix the plate which in turn have a through hole is executed.
- a corresponding embodiment is in the parallel application 197 ... (our sign: MA7214) by the applicant, the disclosure of which that of the present application is to be counted.
- the Piston 52 provided with an axial bore 82, in the in Figure 1 upper end portion screwed a pressure valve 84 is.
- this is Pressure valve 84 designed as a ball check valve, the spherical valve body 86 resilient against one Valve seat is biased in the axial bore 82.
- at lifted valve body 86 can be the pressurized Gasoline (approx. 100 bar) via a connecting channel 88 a manifold (not shown). Of there the pressurized gasoline flows to the outlet connection.
- the construction of the conveyor unit shown in the figure has the advantage that the unit consists of a pressure valve 84, piston 52, cylinder 54 and suction valve 76 pre-assembled can be and then as a pre-tested cartridge or cartridge is screwed into the pump housing, so that the manufacturing and assembly costs a minimum is reduced.
- the part of the connecting channel adjacent to the pressure valve 84 88 is approximately in the axial direction in Housing flange 6 formed and opens into a radial bore of the housing flange 6 through to the outside Sealing plug 89 is sealed.
- the compensating movement of the eccentric ring 36 causes a swirling of the in the crank chamber 16th located gasoline, so that possibly occurring in the crankcase Gas bubbles are swirled and do not adhere can accumulate in one place.
- Eccentric element 20 as a radially projecting eccentric executed.
- the end face of the roller bearing 18 is a shaft sealing device 28 provided via which the crank chamber 16 and the other flow paths of the funding the lubricant circuit 7 is sealed.
- the shaft sealing device 28 has one on the inner circumference of the axial bore 24 and adjacent to the roller bearing assembly 18 Sealing ring 30, the sliding ring 32 in its sealing position is pressed. The latter lies with his Sliding surface 34 on the ring end face 40 of a cap-shaped trained eccentric rings 36 on a Slide bearing 38 on the eccentric 20 of the eccentric shaft 10 is stored.
- the eccentric ring 36 a cap or cup-shaped cross section and encompasses in the illustration shown the eccentric 20, the forms the freely projecting end of the eccentric shaft 10.
- the ring end face 40 of the eccentric ring 36 lies on the Sealing surface 34 of the sliding ring 32.
- a friction reducing Insert 42 are provided, for example made of Teflon consists of an O-ring resilient against the ring face 40 is pressed.
- the Biasing of the eccentric ring 36 in the axial direction on the Slip ring 32 to by a pressure device that by a pressure ring 44 is formed by means of a bias spring 46 against the end face of a bottom 48 of the Eccentric rings 36 is pressed.
- the pressure ring 44 is adjustable in angle, so that it exactly matches the geometry of the floor 48 is customizable.
- the eccentric ring is thus 36 Part of the shaft sealing device 28, since this is the slide ring 32 presses against the sealing ring 30.
- the relative speed is between the slide ring 32 and the eccentric ring 36 comparatively low, so that the heat input in the gasoline due to the friction and also the wear the sealing surfaces is minimal.
- the pressure of the eccentric ring 36 against the slide ring 32 is carried out in addition to the pressure device by the Fluid pressure in the crank chamber 16, which is about that at the input port corresponding form of the fuel corresponds.
- the pressure of the eccentric ring 36 could also done solely by this form, so that under certain circumstances on the pressure device (pressure ring 44, preload spring 46) could be dispensed with.
- the construction according to the invention first embodiment is characterized in that the shaft bearing is very simple, so that the number of gaps in which leakage flow occurs can, compared to the state described above technology is reduced to a minimum.
- the seal between the conveyor circuit and the lubricant circuit is essentially done by a central Shaft sealing device, which by the eccentric ring 36 in their sealing position is biased. The latter thus comes a double function - the guidance of the slide shoe 50 and the pressurization of the shaft sealing device - too. Due to the cap-shaped design of the eccentric ring 36 the gasoline cannot come from the freely projecting end the eccentric shaft 10 forth in the lubricant circuit reach.
- FIG. 2 second embodiment of the present invention described.
- the components of the radial piston pump of the second Embodiment correspond with the exception of Transmission device essentially those of the radial piston pump according to the first embodiment.
- the structural modifications to the housing pot 4 and housing flange 6, in particular the reduced outer diameter of the housing flange 6, do not affect the Operation of the components essential to the invention and are therefore not explained in detail
- the radial piston pump according to the second embodiment points in place of the shaft sealing device 28, the sealing ring 30 and the insert for reducing friction 42 of the first embodiment Sealing ring 33 and an elastic element 35.
- the sealing ring 35 is located in the inner circumference of the housing pot adjacent to the shaft bearing 18 and is related this inner peripheral surface is designed to be fluid-tight, for example by means of an interference fit.
- the elastic element 35 is preferably a deformable membrane which connected to the inner circumference of the sealing ring 35 in a fluid-tight manner is.
- the inner peripheral portion of the elastic member 35 stands with the outer circumference of a plain bearing 138 in fluid-tight connection. This is either elastic element 35 on the plain bearing 138 in a fluid-tight manner or is attached to this in a fluid-tight manner.
- the plain bearing 138 is a deep-drawn bush formed with plain bearing function, is cap-shaped as well thin-walled and is located on the eccentric element 20, which as in the first embodiment as a protruding Eccentric is formed.
- the eccentric ring 136 is formed as a hollow cylinder in the second embodiment and applied to the plain bearing 138.
- one to the pressure device 44, 46 of the first embodiment be designed analog device, the ensures the constant position of the plain bearing 138.
- An embodiment is instead of the plain bearing 138 cap-shaped outer ring 238 of a rolling bearing with rolling elements 139 provided. That way you can Sliding behavior between the eccentric element 20 and the Eccentric ring 136 improve, resulting in less wear of the components.
- a radial piston pump shown in FIG. 4 correspondingly the third embodiment differs of the radial piston pump according to the second embodiment in the construction of the transmission facility.
- the radial piston pump points accordingly the third embodiment as an eccentric element an eccentric recess 120 on the eccentric shaft 10
- Rolling bodies 139 of a rolling bearing are provided on the inner circumference thereof are.
- These rolling elements 139 preferably take one massive, cylindrical end portion 91a one Coupling element 91.
- the coupling element 91 extends in the longitudinal direction the eccentric shaft 10 and has one with respect to the center line 22 of the eccentric shaft 10 offset center line 25.
- the opposite to the end portion 91a in the axial direction lying end portion 91b has a larger outer diameter than the end portion 91a and is located with the Eccentric ring in contact.
- a device 142 for reducing friction On the circular surface between the end sections 91a and 91b can be a device 142 for reducing friction be provided.
- the eccentric shaft 10 and the coupling element 91 with respect to vibrations decouples what is also the noise during operation the radial piston pump according to the invention reduced. Further is compared to the first embodiment Assembling the radial piston pump is easier because the exact Positioning of the shaft sealing device 28 is omitted.
- the eccentric shaft 10 in one piece with the inner ring of the shaft bearing 18 be formed, whereby the number of components and the space requirement can be further reduced.
- the eccentric recess 120 is hemispherical and takes a hemispherical end portion 92a of the Coupling element 92 slidably.
- the structure of this radial piston pump corresponds to the transmission device that of the second embodiment.
- the coupling element 92 extends with respect to the eccentric shaft 10 essentially in the axial direction.
- the for End portion 92a oppositely arranged in the axial direction End section 92b is in a housing-fixed hemispherical guide 94 forming the end section 92b holds firmly and during an orbital movement of the end section 92a in the eccentric recess 120, the coupling element 92 leads on a conical surface.
- a plate-like one Protrusion 92c formed on which an inner portion of the elastic element 35 is attached.
- the outer portion of the elastic member 35 is the same as in the second and third embodiment on the sealing ring 33 attached.
- the projection 92c is connected a spherical bearing section 92d, which is in a Bearing 95 is located on the inner circumference of the eccentric ring 136 and thereby during an orbital movement of the end section 92a a tilting movement in the eccentric recess 120 the eccentric ring 136 and the coupling elements 92.
- Fig. 6 shows an alternative for the fourth embodiment in the form of a fifth embodiment.
- 5 is the housing-fixed guide 94 from FIG an end portion of the coupling member 92 stands by a sealing and bearing portion 96 on one middle spherical section 93c of a coupling element 93 replaced.
- the outer circumference of the sealing and bearing section 96 is via a sealing ring on the inner circumference of the housing pot 4 fixedly arranged.
- One end portion 93a of the axially extending coupling element 93 is via an eccentric bearing 121, preferably a plain bearing, in the eccentric recess 120 of the eccentric shaft 10 added.
- the one to the end section 93a opposite in the axial direction End portion 93b of the coupling element 93 is via a bearing 95 added in eccentric ring 136.
- the elastic element 35 Adjacent to the middle spherical portion 93c the elastic element 35 extends to the sealing and Bearing section 96, on which a radially outer section of the elastic element 35 is attached.
- the elastic element 35 is a variant of this Embodiment in the upper section of Fig. 6 shown metal diaphragm bellows 35p, which causes signs of wear occur only to a very small extent.
- the Sealing and bearing section 96p can due to the good Elasticity of the metal membrane bellows 35p in the axial direction be designed short and over the sealing ring on the outer circumference of the sealing and bearing section 96p in the housing pot 4 be attached.
- elastic element 35 as a massive deformable membrane 35r formed by the sealing and bearing section 96r pressed against a projection 4m in the housing pot 4 becomes.
- the elastic element thus extends 35r also a certain distance in the axial direction what smooth movement of the elastic member 35r enables with low material stress.
- the present invention can thus Problems with sealing systems in petrol pumps, such as with regard to wear and leaks, while at the same time with hermetically separated Lubricant and working fluid areas of the Pump drive in the lubricant area the displacer in Working fluid area can operate.
- a radial piston pump in which an eccentric shaft for driving a conveyor unit on one side is stored in the pump housing and on the freely projecting End section of the shaft as a mechanical seal trained shaft seal is arranged.
- the slide ring lies on an eccentric ring of the eccentric shaft on by a pressure device and / or the form of the conveyor is pressed against the slide ring.
- the eccentric ring is cap-shaped and encompasses the freely projecting end section of the eccentric shaft.
- a membrane between one provided on the housing Sealing ring and an eccentric sealing section, the as a cap-shaped socket, optionally with Plain bearings, on an eccentric element or as a coupling element can be provided in an eccentric recess of the eccentric shaft is.
- a middle section or an end section of the coupling element can be supported by the housing. An end portion or a middle portion thereof can be a lifting movement on a conveyor element Cause radial piston pump.
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Description
das durch eine Spannschraube 58 festlegbar ist. Letztere durchsetzt einen Flansch 60 des Gehäusetopfs 4. Der auf dem Kolben 52 geführte Zylinder 54 hat an seinem Umfang eine Ringstirnfläche 62, an der eine Druckfeder 64 angreift, deren anderes Ende über einen am Gehäuse gelagerten Federteller abgestützt ist. Der Zylinder 54 wird mittels der Druckfeder 36 in Richtung auf den Außenumfang des Exzenterrings 36 vorgespannt. Anstelle der Spannschraube 58 können auch andere geeignete Einrichtungen zur Klemmung des Kolbens 52 verwendet werden, beispielsweise können Blattfeder- und Elastomerelemente eingesetzt werden. In der Trennebene sind hochgenau ausgebildete Aufnahmen vorgesehen, die eine einfache Lagepositionierung des Kolbens 52 ermöglichen. Der zylinderförmige Kolben kann sehr einfach, beispielsweise durch spitzenloses Schleifen feinstbearbeitet werden. Anstelle des zylinderförmigen Kolbens 52 kann auch eine andere Kolbenform, beispielsweise ein Kolben mit Kolbenfuß verwendet werden, wie er in der parallelen Anmeldung P ..., (unser Zeichen: MA7214) (Radialkolbenpumpe) der Anmelderin dargestellt ist.
Claims (15)
- Radialkolbenpumpe mit zumindest einer Fördereinrichtung (2) und mit einer Trenneinrichtung, die einen ersten Aufnahmeraum für ein erstes Fluid, insbesondere ein Fördermittel, und einen zweiten Aufnahmeraum für ein zweites Fluid, insbesondere ein Schmiermittel, voneinander trennt und ein gehäuseseitiges Dichtelement (28; 33; 96) sowie ein exzenterseitiges Dichtelement (36; 38; 138; 238; 91; 92; 93) aufweist, die fluiddicht miteinander verbunden sind, wobei eine Drehbewegung einer Antriebswelle (10) über ein Exzenterelement (20; 120; 220) in eine Radialbewegung eines Förderelementes (50) der Fördereinheit (2) umsetzbar ist und bei der das gehäuseseitige Dichtelement (28; 33; 96) am Pumpengehäuse (4) fluiddicht angeordnet ist und die Antriebswelle (10) durch eine Wellenlagerung (18) im Pumpengehäuse (4) gelagert ist,
dadurch gekennzeichnet, daß das exzenterseitige Dichtelement (36; 38; 138; 238; 91; 92; 93) in Umfangsrichtung des Exzenterelementes (20; 120; 220) gleitfähig angeordnet ist, und daß das Exzenterelement (20; 120; 220) an einem Endabschnitt der Antriebswelle (10) vorgesehen ist. - Radialkolbenpumpe nach Anspruch 1,
dadurch gekennzeichnet, daß die Trenneinrichtung so ausgebildet ist, daß eine Orbitalbewegung zwischen dem gehäuseseitigen Dichtelement (28; 33; 96) und dem exzenterseitigen Dichtelement (36; 38; 138; 238; 91; 92; 93) vorsehbar ist. - Radialkolbenpumpe nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß das Exzenterelement (20) an der Axialwelle (10) als Axialvorsprung ausgebildet ist. - Radialkolbenpumpe nach Anspruch 3,
dadurch gekennzeichnet, daß das gehäuseseitige Dichtelement (28) und das exzenterseitige Dichtelement (36) stirnseitig aufeinandergleitend ausgebildet sind. - Radialkolbenpumpe nach Anspruch 3,
dadurch gekennzeichnet, daß das exzenterseitige Dichtelement (36; 38; 138; 238) kappenförmig ausgebildet ist. - Radialkolbenpumpe nach Anspruch 5,
dadurch gekennzeichnet, daß das exzenterseitige Dichtelement (38; 138; 238) ein dünnwandiges Bauteil ist, das als Gleitlager oder Außenring eines Wälzlagers vorgesehen ist. - Radialkolbenpumpe nach Anspruch 5 oder 6,
dadurch gekennzeichnet, daß an einem Boden (48) des exzenterseitigen Dichtelementes (36) eine Andruckeinrichtung (44, 46) angreift, die das exzenterseitige Dichtelement (36) gegen das Exzenterelement (20) vorspannt. - Radialkolbenpumpe nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß das Exzenterelement (120; 220) als Axialvertiefung der Antriebswelle (10) ausgebildet ist. - Radialkolbenpumpe nach Anspruch 8,
dadurch gekennzeichnet, daß das exzenterseitige Dichtelement (91; 92; 93) ein sich im wesentlichen in Axialrichtung erstrekkendes Element aufweist, durch das die Bewegung von der Antriebswelle (10) auf das Förderlement (50) übertragbar ist und dessen einer Endabschnitt in der Axialvertiefung (120; 220) drehbar angeordnet ist. - Radialkolbenpumpe nach Anspruch 9,
dadurch gekennzeichnet, daß das Koppelelement (92; 93) durch das Pumpengehäuse (4) geführt ist. - Radialkolbenpumpe nach Anspruch 10,
dadurch gekennzeichnet, daß der Endabschnitt (92b) des Koppelelementes (92), der bezüglich dem in der Axialvertiefung (120) angeordneten Endabschnitt (92a) des Koppelelementes (92) entgegengesetzt liegt, am Pumpengehäuse (4) schwenkbar angeordnet ist. - Radialkolbenpumpe nach Anspruch 10,
dadurch gekennzeichnet, daß ein zwischen den beiden Endabschnitten (93a, 93b) des Koppelelementes (93) angeordneter Abschnitt (93c) des Koppelelementes (93) am gehäuseseitigen Dichtelement (96) schwenkbar angeordnet ist. - Radialkolbenpumpe nach einem der Ansprüche 1 bis 3 und 5 bis 12,
dadurch gekennzeichnet, daß sich zwischen dem gehäuseseitigen Dichtelement (33; 96) und dem exzenterseitigen Dichtelement (38; 138; 238; 91; 92; 93) ein elastisches Element (35) erstreckt. - Radialkolbenpumpe nach Anspruch 13,
dadurch gekennzeichnet, daß das elastische Element (35) am Koppelelement (91; 92; 93) dicht anliegt oder an diesem befestigt ist. - Radialkolbenpumpe nach Anspruch 13 oder 14,
dadurch gekennzeichnet, daß das Koppelelement (91; 92; 93) mechanisch gegen Verdrehen gesichert ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19725565 | 1997-06-17 | ||
DE19725565 | 1997-06-17 | ||
PCT/DE1998/001646 WO1998058171A1 (de) | 1997-06-17 | 1998-06-17 | Radialkolbenpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0991863A1 EP0991863A1 (de) | 2000-04-12 |
EP0991863B1 true EP0991863B1 (de) | 2002-11-20 |
Family
ID=7832727
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98936190A Expired - Lifetime EP0991863B1 (de) | 1997-06-17 | 1998-06-17 | Radialkolbenpumpe mit dichtung am antriebswellenende zur fluiddichten kapselung des pumpenraumes |
Country Status (7)
Country | Link |
---|---|
US (1) | US6328537B1 (de) |
EP (1) | EP0991863B1 (de) |
JP (1) | JP2002508821A (de) |
KR (1) | KR20010013938A (de) |
BR (1) | BR9810179A (de) |
DE (2) | DE19826961A1 (de) |
WO (2) | WO1998058172A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2012059298A1 (de) * | 2010-11-04 | 2012-05-10 | Robert Bosch Gmbh | Kraftstoff-fördereinrichtung für eine brennkraftmaschine |
Families Citing this family (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19637646A1 (de) * | 1996-09-16 | 1998-03-19 | Bosch Gmbh Robert | Hydropumpenaggregat |
DE19913070A1 (de) * | 1999-03-23 | 2000-09-28 | Hydraulik Ring Gmbh | Radialkolbenpumpe |
DE19920996A1 (de) * | 1999-05-06 | 2000-11-09 | Hydraulik Ring Gmbh | Pumpeinheit |
DE10241306A1 (de) | 2002-09-04 | 2004-03-18 | Continental Teves Ag & Co. Ohg | Motor-Pumpen-Aggregat insbesondere für schlupfgeregelte Bremssysteme |
DE10253189A1 (de) * | 2002-11-15 | 2004-05-27 | Robert Bosch Gmbh | Radialkolbenpumpe mit flächiger Dichtung zwischen Flansch und Gehäuse |
WO2006037674A1 (de) * | 2004-10-06 | 2006-04-13 | Siemens Aktiengesellschaft | Radialkolbenpumpe mit verbesserter schmierung des exzentertriebs |
DE102006041480B4 (de) * | 2006-09-05 | 2016-06-16 | Robert Bosch Gmbh | Motor-Pumpen-Aggregat mit einer Pumpen-Antriebswelle hoher Elastizität und einem Exzenter am Antriebswellenende |
JP4983593B2 (ja) * | 2007-04-10 | 2012-07-25 | 日産自動車株式会社 | 燃料ポンプの駆動装置 |
DE102008042073A1 (de) * | 2008-09-15 | 2010-03-18 | Robert Bosch Gmbh | Radialkolbenpumpe |
DE102009027272A1 (de) | 2009-06-29 | 2010-12-30 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102009054635A1 (de) * | 2009-12-15 | 2011-06-16 | Robert Bosch Gmbh | Radialkolbenpumpe mit Exzenterlager, insbesondere für Fahrzeugbremssysteme |
DE102011076076A1 (de) * | 2011-05-18 | 2012-09-20 | Continental Automotive Gmbh | Pumpe |
WO2013001035A2 (de) | 2011-06-30 | 2013-01-03 | Arens Gmbh Metallbau & Bauschlosserei | Kraftstoffverteilerblock |
DE112012002676A5 (de) | 2011-06-30 | 2014-03-13 | Arens GmbH Metallbau- und Bauschlosserei | Kraftstoffpumpe |
DE102011119519A1 (de) * | 2011-06-30 | 2013-01-03 | Arens GmbH Metallbau- und Bauschlosserei | Motorensystem |
DE102011078466A1 (de) * | 2011-06-30 | 2013-01-03 | Arens GmbH Metallbau- und Bauschlosserei | Motorensystem |
DE102011119520A1 (de) * | 2011-06-30 | 2013-01-03 | Arens GmbH Metallbau- und Bauschlosserei | Motorensystem |
CN103470491B (zh) * | 2013-10-11 | 2016-03-23 | 湖州三井低温设备有限公司 | 一种低温高压往复泵用轴承偏心轮结构 |
TWI553228B (zh) * | 2014-12-05 | 2016-10-11 | Liquid pressurized pump output shaft lubrication structure | |
JP6096255B2 (ja) * | 2015-08-31 | 2017-03-15 | 中禾亞股▲ふん▼有限公司 | 液体加圧ポンプの出力軸潤滑構造 |
JP6741199B2 (ja) * | 2016-10-12 | 2020-08-19 | 日立オートモティブシステムズ株式会社 | ポンプ装置及びブレーキ装置 |
TWI624327B (zh) * | 2017-01-18 | 2018-05-21 | Integrated processing machine axial system adaptive lubrication control device and method | |
DE102021204715A1 (de) * | 2021-05-10 | 2022-11-10 | Thyssenkrupp Ag | Radialkolbenpumpe, sowie Verfahren zur Herstellung einer Radialkolbenpumpe |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2253022C2 (de) * | 1972-10-28 | 1974-12-12 | G.L. Rexroth Gmbh, 8770 Lohr | Radialkolbenmaschine |
DE2616435A1 (de) * | 1976-04-14 | 1977-10-27 | Fichtel & Sachs Ag | Radialkolbenpumpe |
DE2651885A1 (de) * | 1976-11-13 | 1978-05-18 | Kaercher Fa Alfred | Tragbares hochdruckreinigungsgeraet |
DE3721698A1 (de) * | 1987-07-01 | 1989-01-19 | Hauhinco Maschf | Radialkolbenpumpe fuer die foerderung von wasser |
GB8818912D0 (en) * | 1988-08-09 | 1988-09-14 | Lucas Ind Plc | Hydraulic pump & motor assemblies for vehicle hydraulic systems |
DE3840691C2 (de) * | 1988-12-02 | 1997-02-13 | Teves Gmbh Alfred | Radialkolbenpumpe |
DE4213798C2 (de) * | 1992-04-27 | 2002-10-24 | Bosch Gmbh Robert | Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren |
US5354183A (en) * | 1993-02-11 | 1994-10-11 | Elasis Sistema Ricerca Fiat Nel Mezzogiorno Societa Consortile Per Azioni | Pumping device with a main pumping stage and a supply pump |
DE4305791C2 (de) | 1993-02-25 | 2001-12-13 | Hydraulik Ring Gmbh | Radialkolbenpumpe, insbesondere Kraftstoffpumpe für Verbrennungsmotoren |
JPH06337072A (ja) * | 1993-05-28 | 1994-12-06 | Toyoda Gosei Co Ltd | 液圧ポンプ用メカニカルシール |
DE4419927A1 (de) | 1994-06-08 | 1995-12-14 | Bosch Gmbh Robert | Kolbenpumpe |
JPH08282471A (ja) * | 1995-04-14 | 1996-10-29 | Sumitomo Electric Ind Ltd | 電動ポンプ |
JPH09195926A (ja) | 1996-01-17 | 1997-07-29 | Unisia Jecs Corp | ラジアルプランジャポンプ |
DE19627757A1 (de) * | 1996-07-10 | 1998-01-15 | Bosch Gmbh Robert | Kraftstoffpumpe |
DE19637646A1 (de) | 1996-09-16 | 1998-03-19 | Bosch Gmbh Robert | Hydropumpenaggregat |
-
1998
- 1998-02-19 WO PCT/DE1998/000499 patent/WO1998058172A1/de active Application Filing
- 1998-06-17 JP JP50357099A patent/JP2002508821A/ja active Pending
- 1998-06-17 EP EP98936190A patent/EP0991863B1/de not_active Expired - Lifetime
- 1998-06-17 WO PCT/DE1998/001646 patent/WO1998058171A1/de active IP Right Grant
- 1998-06-17 DE DE19826961A patent/DE19826961A1/de not_active Withdrawn
- 1998-06-17 BR BR9810179-0A patent/BR9810179A/pt not_active Application Discontinuation
- 1998-06-17 KR KR1019997011960A patent/KR20010013938A/ko active Search and Examination
- 1998-06-17 DE DE59806362T patent/DE59806362D1/de not_active Expired - Fee Related
- 1998-06-17 US US09/446,493 patent/US6328537B1/en not_active Expired - Fee Related
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2012059298A1 (de) * | 2010-11-04 | 2012-05-10 | Robert Bosch Gmbh | Kraftstoff-fördereinrichtung für eine brennkraftmaschine |
Also Published As
Publication number | Publication date |
---|---|
KR20010013938A (ko) | 2001-02-26 |
DE59806362D1 (de) | 2003-01-02 |
US6328537B1 (en) | 2001-12-11 |
BR9810179A (pt) | 2001-11-27 |
WO1998058171A1 (de) | 1998-12-23 |
EP0991863A1 (de) | 2000-04-12 |
JP2002508821A (ja) | 2002-03-19 |
WO1998058172A1 (de) | 1998-12-23 |
DE19826961A1 (de) | 1998-12-24 |
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