WO2002048548A1 - Radial piston pump - Google Patents
Radial piston pump Download PDFInfo
- Publication number
- WO2002048548A1 WO2002048548A1 PCT/EP2001/014645 EP0114645W WO0248548A1 WO 2002048548 A1 WO2002048548 A1 WO 2002048548A1 EP 0114645 W EP0114645 W EP 0114645W WO 0248548 A1 WO0248548 A1 WO 0248548A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- control
- drive shaft
- pump according
- radial
- Prior art date
Links
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
- F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
- F04B1/0536—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units
- F04B1/0538—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units located side-by-side
-
- 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
- F04B1/06—Control
- F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
- F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
- F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
Definitions
- the present invention relates to a radial piston pump for displacing liquids with an axially mounted rotatable drive shaft in a pump housing, which has eccentric or cam-shaped actuators with respect to the axis and with several actuators mounted radially with respect to the drive shaft in a respective cylinder space and with the respective actuator interacting pistons, which can be moved back and forth in their cylinder space in the radial direction when the drive shaft is rotated, with liquid inlet and outlet openings arranged in the pump housing, the individual pistons being arranged in at least two separate axially separated piston groups and the radial stroke of the individual pistons being linear between a minimum value and a maximum value is adjustable.
- the invention particularly relates to a pump for
- Fuel supply to the engines of an aircraft is not limited to this preferred application, but can also be used in other fields for the transport or displacement of liquids.
- the conventional pumps for supplying fuel to an aircraft engine are driven directly by the engines. Since these engines, with the exception of the landing process, run at constant speed, the pumps are also operated at constant speed, so that the delivery volume of the fuel is constant over time and must be calculated so that it can meet the highest fuel consumption. However, this fuel consumption depends on the flight conditions and is essentially determined by the pilot using the control lever.
- This control lever acts on a control device downstream of the fuel pump, which determines the power and the fuel consumption. Except for the mechanical regulation by the control lever also experiences a sensor-controlled hydraulic control depending on various flight parameters such as altitude, pressure, etc., as well as an electrical control to refine the hydraulic control.
- the control device accordingly receives a constant in time
- the difference or excess amount of fuel is branched off by the control device and returned to the fuel tank.
- the present invention is therefore based on the object of providing a radial piston pump which only conveys as much fuel as is consumed by the associated engine and which can be operated at high speed.
- the radial piston pump according to the invention has the features provided in the main claim. Further embodiments of the invention result from the subclaims.
- the pump according to the invention is accordingly a volumetric, controllable construction.
- the required volume flow is brought to the required pressure level by radially arranged displacement pistons distributed on two levels.
- the pistons are driven in accordance with the two levels by two actuators with variable eccentricity arranged on a common drive shaft, these being positively guided by the device.
- the two actuators are offset by 180 ° to each other and can be moved against each other via an integrated mechanism arranged in the drive shaft, which means that the volume flow can be increased or decreased evenly.
- the load on the main drive shaft bearings is significantly minimized, which means less wear and thus a longer maintenance-free runtime.
- Due to the relatively large number of displacement pistons a significantly lower pulsation of the delivery medium is achieved, as a result of which a significantly lower mechanical load on all fuel-carrying parts, such as pipes and hoses, is achieved.
- the inlet and outlet control of the individual pistons is controlled by control devices which are firmly seated on the intake and pressure side and which rotate with the drive shaft. This positively driven control has the advantage over a simple control with spring-loaded check valves that the pump can be operated at a much higher speed.
- the entire pump housing is flowed through by the fuel, so that the lubrication and cooling are carried out by the transported fuel. This results in maintenance-free and low-wear operation.
- the aircraft pilot controls the output using the mechanical control lever, and electromechanical control is also possible.
- the further required control option i.e. e.g. Variable volume flow at constant pressure and constant speed is achieved by an actuator (e.g. piston) built into the pump, which adjusts the volume flow automatically and hydraulically by shifting the eccentric by means of the system pressure.
- an actuator e.g. piston
- FIG. 1 shows an axial section through a first embodiment of a radial piston pump according to the invention along the section line II-II in FIG. 2 for the left-hand piston group (based on FIG. 1) and along the section line Ir-Ir for the right-hand piston group.
- Fig. 1 b is an axial view of the control disc of the left
- Piston group. 1c shows an axial section through the control disk of FIG. 1b.
- FIG. 2 shows a diagonal section through the left-hand piston group of FIG. 1
- Fig. 3 is an axial plan view of the adjustable cam.
- Fig. 5 is an axial plan view of the eccentric ring.
- FIG. 6 shows a part of the drive shaft in axial section along the section line II-II in FIG. 2.
- FIG. 8 shows an axial section through a second embodiment of a radial piston pump according to the invention along section line II-II in FIG. 2 for the left-hand piston group (referring to FIG. 8) and along section line Ia-Ir for the right-hand piston group.
- Figures 1 and 2 show a first embodiment of a radial piston pump according to the invention for supplying an aircraft engine with fuel.
- the pump comprises a drive shaft 14 which is rotatably mounted in a pump housing 10 in roller or ball bearings 12.
- the shaft 14 is driven by the engine at a constant speed of e.g. 8000 rpm or more driven.
- the pump housing comprises at least one fuel inlet opening 16 and one fuel outlet opening 18, which is connected to the associated engine.
- the radial piston pump comprises at least two piston groups 20I and 20r in two axially separated parallel planes.
- the left piston group 20I consists of the individual pistons 22I which move in the respective cylinder spaces 24I and the right piston group 20r consists of the individual pistons 22r which move in the respective cylinder spaces 24r.
- each piston group 201, 20r consists of five pistons 221 and 22r.
- the number of pistons can also be larger, for example seven, nine, etc., or smaller. The pump runs more smoothly the larger the number of pistons.
- pistons of one group are angularly offset from the pistons of the other group.
- the pistons 22r are offset by 36 ° with respect to the pistons 221, ie that if a piston 221 of the group 201 is oriented to the north, as shown in FIG 20r facing south.
- Each piston 221, 22r is sealed in its cylinder space 241 or 24r. This seal is shown in FIG. 1, for example, by a simple O-ring seal 26.
- Each cylinder chamber 24I, 24r is connected on the intake side to the inlet opening 16 via a suction opening 28 and on the pressure side to the outlet opening 18 via an ejection opening 30.
- positive control devices described below are provided to control these openings 28, 30, positive control devices described below are provided. The back and forth movement of the individual pistons accordingly draws fuel out of the inlet opening 16 in a manner known per se and displaces it through the outlet opening 18.
- the stroke of the individual pistons can be adjusted linearly between a maximum value and a minimum value.
- the individual pistons 22I, 22r are actuated via the cam disk 32 shown in FIGS. 3 and 4, one cam disk 321 or 32r being provided for each piston group 20I, 20r.
- the cam disk 32 is horseshoe-shaped with a circular outer circumference and parallel inner sides 34, 36 between the two legs.
- the drive shaft 14 has corresponding flats 38, 40 on two opposite sides in the middle of each piston group 20I, 20r, the spacing of which is the distance between the inner side surfaces 34, 36 of the cam disk 32 corresponds so that it can be stuck onto the drive shaft in a rotationally fixed manner.
- each cam disk 32 has in the opening bottom between the two inner side surfaces 34, 36 a cylindrical connecting piece 42 which penetrates through a corresponding opening 44I or 44r in the drive shaft 14 when the cam disk 32 is pushed onto the shaft 14.
- the top surface of the connecting piece 42 is designed as an inclined ramp 46, which has a certain inclination with respect to the drive shaft 14.
- the drive shaft 14 comprises an axial bore 48 in which a control shaft 50 is axially movable. In the bore 48, the control shaft 50 is exposed to the force of a compression spring 52.
- control shaft 50 each comprises an inclined ramp 541, 54r with an inclination corresponding to the inclination of the ramps 46 of the cam disks 321, 32r such that the ramps 461, 541 or 46r, 54r belonging to one another can interact.
- Each cam disk 32 is seated in a circular eccentric ring 56 shown in FIG. 5, which is screwed to the cam disk 32 in a rotationally locking manner at 59.
- a compression spring 58 which is supported on the outside of the drive shaft 14 and the inside of the eccentric ring 56. This spring accordingly ensures that the cooperating ramps 46I, 54I and 46r, 54r are in contact with each other.
- each cylinder space 24I, 24r is provided with a suction opening 28 and with an ejection opening 30 which are connected to the inlet opening 16 and to the outlet opening 18 by control devices.
- this connection takes place through two groups of five axially parallel channels which run between the individual cylinder spaces 24 and are partially visible at 72 in FIG. 1.
- the connection of these channels to the inlet and outlet openings is controlled in the embodiment of FIG. 1 by two control disks 74 arranged on the suction side and pressure side and shown in more detail in FIGS. 1 b and 1 c.
- These two control disks 74 are identical to one another and are fixed connected to the drive shaft 14 to rotate with it.
- Each control disk 74 comprises a first kidney-shaped slot 76 which extends over approximately 160 ° (with five pistons and depending on the opening diameter) and a second kidney-shaped slot 78 which also extends about 160 °, wherein, as FIG. 1b shows, the radius of curvature of the first slot 76 is larger than that of the second slot 78.
- the first slot 76 of the intake-side control disk 74 is assigned to the intake openings 28 of the left cylinder spaces 24I, while the second slot 78 of the same intake-side disk 74 is assigned to the intake openings and the corresponding connecting channels 72 of the right cylinder spaces 24r.
- the second "slot 78 is 74 to the discharge ports of the right cylinder chambers 24r associated with the pressure-side control disc while the first slot 76 of the control disk 74 to the discharge ports and, connecting channels 72 of the left cylinder chambers associated 241 in this regard.
- each revolution of the control disks 74 corresponds to a full working cycle of the individual pistons 24 and vice versa.
- the slot 76 opens the suction openings 28 of the left cylinder spaces 24I in succession when the individual pistons 22I are in the suction phase and move axially inward.
- the full part of the disk 74 opposite the slot 76 simultaneously closes the suction openings of the cylinder spaces 24I on the other side of the pump, in which the pistons 24! are in the displacement phase.
- the left upper piston 22 I and the right lower piston 22r are at the dead center between the displacement phase and the suction phase.
- the suction-side control disk 74 is here in the position of FIG. 1b in which the full upper and lower regions between the slots 76 and 78 close the accesses to the upper left cylinder space 241 and to the lower right cylinder space 24r.
- the control disk 74 is turned, starting from this position and the pistons 221 and 22r move inwards at the same time, the accesses to these cylinder spaces 241 and 24r, which are now entering the suction phase, are released by the slots 76 and 78, respectively, and with the inlet opening 16 and the associated ring-shaped one Channel connected.
- the pressure-side control disk 74 is offset by 180 ° from the suction-side control disk, but the method of operation is exactly the same.
- the connecting channel to the cylinder space 24I and the ejection opening 30 of the cylinder space 24r are closed by the pressure-side control disk 74 so that these cylinder spaces 24I and 24r can suck.
- each cam disk 32I, 32r sits with its ramp 46I, 46r under the action of the spring 58 on the base of the associated ramp 541, 54r of the control shaft 50.
- the drive shaft 14, the cam disks 32 and the eccentric rings 56 are coaxial, ie that when the drive shaft 14 rotates, the individual pistons 22 do not move in their cylinder spaces 24, ie the pump is not working.
- each eccentric ring 56 accordingly experiences an eccentric circular movement through the cam disk 32 and presses the individual pistons 22 outwards one after the other, so that the fuel located in the cylinder spaces is displaced into the outlet opening 18 and continues to do so by approximately 180 ° rotary movement is sucked in about 180 ° new fuel.
- the inward movement of the individual pistons ie the suction of the fuel, can take place in various ways. Two possibilities are shown in FIGS. 1 and 2, but either one or the other is used.
- the simplest possibility consists in a compression spring 60, which is arranged in each cylinder chamber 24 (for simplicity's sake, only two springs are shown in FIG. 2) on the head side and the pistons come into contact with the inside Eccentric ring 56 presses.
- the springs 60 can also be replaced by a positive guidance of the individual pistons 22.
- This positive guidance can consist, for example, of two non-rotatable radially movable circular rings 62 with an inner diameter corresponding to the outer diameter of the eccentric ring 56, so that the eccentric ring 56 can rotate in this positive guidance 62 and can take it outwards and inwards.
- the individual pistons 22 then only need to be attached to the outside of the ring 62. As shown, this can be done, for example, by designing the outside of the rings 62 in a rail shape with a T-shaped cross section and engaging in corresponding side grooves in the individual pistons. To enable assembly, the ring 62 can consist of two separate parts which are held together by an expansion ring.
- Figure 1 also shows an embodiment for operating the
- a control ring 64 is positioned by a suitable thrust bearing.
- 66 schematically denotes a control lever which can be pivoted about an axis 68 and can be actuated by the pilot.
- the control lever 66 is tilted to the right, the control shaft 50 is axially displaced to the left against the force of the spring 52, so that the displaced fuel volume can be increased according to the above-described process.
- This mechanical control is supplemented by an automatic sensor-controlled hydraulic drive, which is indicated schematically at 70.
- FIG. 8 shows a second embodiment of a radial piston pump according to the invention, which differs from the embodiment according to FIG. 1 only in the flow control.
- the regulation of the pump is precise the same as in Figure 1 and the corresponding components are designated by the same reference numerals.
- the two control disks 74 of FIG. 1 are replaced by two plate-shaped control elements 174 which also rotate with the drive shaft 14.
- the control elements 174 rotate in annular chambers connected to the inlet opening 16 and the outlet opening 18 and consist of a radial disk 174a connected to the drive shaft and an adjoining outer cylindrical jacket 174b which extends axially outwards.
- the kidney-shaped slots 76, 78 which are provided in the embodiment of FIG. 1 and are open in the axial direction are replaced here by corresponding arcuate slots 176, 178. These diametrically open slots 176, 178 are provided in the cylindrical jacket region 174b of the control elements 174 and likewise extend over an arc angle of approximately 160 °.
- slots 176 and 178 in Figure 8 can control independently, they are axially offset from each other rather than radially as in the Figure 1 embodiment.
- Each slot 176 and 178 in each control element 174 is corresponding through the pump block to the individual cylinder spaces 24I and 24r associated with leading holes.
- the mode of operation of the control elements 174 is accordingly exactly the same as that of the control disks 74 of FIG. 1, so that a more detailed description is unnecessary.
- the embodiment according to FIG. 8 has the advantage of a better balance of forces and moments compared to that of FIG.
- a piston for example the upper piston 22I
- the transversely opposed piston 24r which operates in a clocked manner, exerts a corresponding, opposite, reaction force on the drive shaft 14. This naturally results in a corresponding tipping moment in the trigonometric sense around the center O on the drive shaft 14.
- the pressure of the liquid is transferred to the two closed suction-side openings opposite the outer surface of the control element 174 and the force thus created also causes the drive shaft 14 to tilt about the center O.
- the distance is from the center O to the slot 178 but larger than that to the slot 176. This results in a differential tilting moment acting on the drive shaft 14, which is opposite to the tilting moment generated by the piston movement. This means that with an optimally calculated axial distance between the slots 176, 178 and a corresponding adjustment of the flow cross-sections, the tilting moments generated by the displacement can be compensated.
- the control device which was necessary in the case of conventional pumps, is not required in order to throttle the fuel volume delivered by the pump by mechanical, hydraulic and electrical controls.
- These controls now act directly on the radial piston pump according to the invention and are able to linearly increase or decrease the amount of fuel delivered. This not only results in significant energy savings, but also and in particular the elimination of a major risk factor.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU2002224928A AU2002224928A1 (en) | 2000-12-11 | 2001-12-10 | Radial piston pump |
EP01994781A EP1342010A1 (en) | 2000-12-11 | 2001-12-10 | Radial piston pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP00204414.7 | 2000-12-11 | ||
EP00204414A EP1213478A1 (en) | 2000-12-11 | 2000-12-11 | Radial piston pump |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002048548A1 true WO2002048548A1 (en) | 2002-06-20 |
Family
ID=8172404
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2001/014645 WO2002048548A1 (en) | 2000-12-11 | 2001-12-10 | Radial piston pump |
Country Status (3)
Country | Link |
---|---|
EP (2) | EP1213478A1 (en) |
AU (1) | AU2002224928A1 (en) |
WO (1) | WO2002048548A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015214837A1 (en) * | 2015-08-04 | 2017-02-09 | Zf Friedrichshafen Ag | Hydraulic radial piston machine |
US9751759B2 (en) | 2012-10-01 | 2017-09-05 | Oxford University Innovation Limited | Composition for hydrogen generation |
JP2021063447A (en) * | 2019-10-11 | 2021-04-22 | 株式会社トータレスキュージャパン | Radial piston pump |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE343886C (en) * | ||||
DE343686C (en) | ||||
BE484038A (en) | ||||
GB173264A (en) * | 1920-08-19 | 1921-12-19 | Luigi Cardini | Improvements connected with fluid pressure rotary motors |
FR1563223A (en) | 1968-03-01 | 1969-04-11 | ||
US3827831A (en) * | 1972-05-15 | 1974-08-06 | R Lines | Control for radial type pumps or the like |
FR2296778A1 (en) * | 1975-01-03 | 1976-07-30 | Rexroth Sigma | Radial-piston pump or motor - has cylinder heads of more than hemisphere section with centres held in fixed positions |
FR2321608A1 (en) * | 1975-08-20 | 1977-03-18 | Bechler Andre | Variable output radial piston hydraulic pump - has sliding rod inside drive spindle with sloping faces varying piston stroke |
DE4134184A1 (en) * | 1991-10-16 | 1993-04-22 | Bosch Gmbh Robert | Adjustable hydrostatic pump - has piston stroke adjusted dependent upon rpm, to limit feed flow |
-
2000
- 2000-12-11 EP EP00204414A patent/EP1213478A1/en not_active Withdrawn
-
2001
- 2001-12-10 AU AU2002224928A patent/AU2002224928A1/en not_active Abandoned
- 2001-12-10 EP EP01994781A patent/EP1342010A1/en not_active Withdrawn
- 2001-12-10 WO PCT/EP2001/014645 patent/WO2002048548A1/en not_active Application Discontinuation
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE343886C (en) * | ||||
DE343686C (en) | ||||
BE484038A (en) | ||||
GB173264A (en) * | 1920-08-19 | 1921-12-19 | Luigi Cardini | Improvements connected with fluid pressure rotary motors |
FR1563223A (en) | 1968-03-01 | 1969-04-11 | ||
US3827831A (en) * | 1972-05-15 | 1974-08-06 | R Lines | Control for radial type pumps or the like |
FR2296778A1 (en) * | 1975-01-03 | 1976-07-30 | Rexroth Sigma | Radial-piston pump or motor - has cylinder heads of more than hemisphere section with centres held in fixed positions |
FR2321608A1 (en) * | 1975-08-20 | 1977-03-18 | Bechler Andre | Variable output radial piston hydraulic pump - has sliding rod inside drive spindle with sloping faces varying piston stroke |
DE4134184A1 (en) * | 1991-10-16 | 1993-04-22 | Bosch Gmbh Robert | Adjustable hydrostatic pump - has piston stroke adjusted dependent upon rpm, to limit feed flow |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9751759B2 (en) | 2012-10-01 | 2017-09-05 | Oxford University Innovation Limited | Composition for hydrogen generation |
DE102015214837A1 (en) * | 2015-08-04 | 2017-02-09 | Zf Friedrichshafen Ag | Hydraulic radial piston machine |
JP2021063447A (en) * | 2019-10-11 | 2021-04-22 | 株式会社トータレスキュージャパン | Radial piston pump |
Also Published As
Publication number | Publication date |
---|---|
EP1213478A1 (en) | 2002-06-12 |
EP1342010A1 (en) | 2003-09-10 |
AU2002224928A1 (en) | 2002-06-24 |
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