EP1230481A1 - Radialkolbenpumpe - Google Patents
RadialkolbenpumpeInfo
- Publication number
- EP1230481A1 EP1230481A1 EP00975952A EP00975952A EP1230481A1 EP 1230481 A1 EP1230481 A1 EP 1230481A1 EP 00975952 A EP00975952 A EP 00975952A EP 00975952 A EP00975952 A EP 00975952A EP 1230481 A1 EP1230481 A1 EP 1230481A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston pump
- radial piston
- eccentric
- compensation element
- 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.)
- Granted
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
- F04B1/0404—Details or component parts
-
- 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
- F04B49/22—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 means of valves
- F04B49/225—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 means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
Definitions
- the invention relates to a radial piston pump according to the preamble of claim 1.
- Radial piston pumps of this type which are also referred to as radial piston pumps, have a suction chamber in which a rotatably drivable eccentric for driving at least one piston is arranged. Furthermore, this radial piston pump has an inlet control element which, depending on the piston position, releases or closes a connection between the suction chamber and the cylinder bore.
- a disk influencing the intake flow is arranged concentrically. The diameter of the disk is selected so that there is a relatively small gap between the wall radially delimiting the suction space and the disk, so that a throttle gap is formed over the entire circumference of the disk.
- a radial piston pump is known from US Pat. No. 5,207,771 A, which has imbalance compensation elements which are intended to compensate for or compensate for the imbalance caused by the eccentric.
- this known pump is not bottom suction, which means that the eccentric and the balance weight are not are arranged in the space that also forms the suction space.
- a radial piston pump which has the features of claim 1. It has a suction chamber with a suction connection and a rotationally drivable eccentric arranged in the suction chamber for driving at least one piston of the radial piston pump. In addition, it has a cylinder bore guiding the piston and an inlet control element which, depending on the piston position, releases or closes a connection between the suction chamber and the cylinder bore.
- the radial piston pump is characterized by an imbalance compensation element for the eccentric, which rotates synchronously with the eccentric in the suction chamber, the imbalance compensation element being arranged in the suction chamber and / or its contour being such that a hydraulic between the suction connection and the inlet control element - Formed resistance or the medium flow reaching the inlet control element is unaffected.
- Contour of the unbalance compensation element of the medium flow reaching the inlet control element can be influenced.
- the unbalance compensation element tapers in the radial direction in order to be at a greater distance from it in the area of the inlet control element and / or the suction connection, so that the medium flow is not influenced thereby.
- the radial piston pump is designed to be suction throttled.
- Suction-throttled radial piston pumps have the advantage that they drive up to a certain speed of the drive shaft or the eccentric. ne increasing flow rate characteristic and from this certain speed, also known as limit speed, have a horizontal flow characteristic.
- the imbalance compensation element is arranged in the suction space and / or its contour is designed such that the medium flow reaching the inlet control element is essentially unaffected.
- the unbalance compensation element according to the invention it is therefore possible to use the unbalance compensation element according to the invention to provide a suction-throttled radial piston pump which draws in at the bottom and which has very little or no vibrations and yet has an unaffected delivery flow characteristic, that is to say essentially has a horizontal delivery flow characteristic from the predeterminable limit speed.
- This radial piston pump is used in particular to supply a hydraulic system which actively influences the chassis of a motor vehicle.
- a preferred exemplary embodiment is characterized in that the unbalance compensation element has a bevel on its side facing the inlet control element, so that the thickness of the unbalance compensation element decreases radially outward. It has been shown that an imbalance compensation element designed in this way essentially does not influence the intake medium flow to the inlet control element.
- the imbalance compensation element comprises a disk segment.
- a Washer is provided, which is arranged offset with its central axis to the eccentric.
- the unbalance compensation element thus has a mass element which is assigned to the eccentric in such a way that the unbalance caused by the eccentric is compensated for.
- the eccentric and the imbalance compensation element are arranged on a drive shaft which rotates or rotates in the suction space. It can be provided that the eccentric is formed in one piece with the drive shaft. The center axis of the balancing element does not coincide with the longitudinal axis of the drive shaft.
- a second unbalance compensation element rotates synchronously with the eccentric.
- the two unbalance compensation elements are oriented with respect to the eccentric so that when the
- At least one of the two unbalance compensation elements can be applied to the drive shaft.
- at least one of the two unbalance compensation elements is pushed onto the drive shaft, the Imbalance compensation element has a breakthrough, the inner diameter of which is selected such that the unbalance compensation element is held on the drive shaft.
- one of the two unbalance compensation elements is formed in one piece with the drive shaft and that the other unbalance compensation element can be applied to the drive shaft.
- the eccentric has a DU bushing and a steel bushing which are pushed onto the eccentric contour.
- the steel bush interacts with the piston crown of the at least one piston. Because an imbalance compensation element can be attached to the drive shaft, this, preferably hardened, steel bushing and the internal DU bushing can first be pushed onto the eccentric so that the imbalance compensation element can then be applied to the drive shaft.
- the unbalance compensation elements are attached to the drive shaft in such a way that the steel bushing and the DU bushing cannot slip off the eccentric.
- the first imbalance compensation element has a hub through which the drive shaft passes, the disk segment originating from the hub.
- a circular disk can also be provided instead of the disk segment. This disk or the disk segment serve as a balance weight, which has an offset with respect to the central axis of the hub.
- the axial length of the unbalance compensation element is particularly preferably dimensioned such that it rests with one end on the side surface of the eccentric and with its other end against a wall delimiting the suction space. This axially fixes the drive shaft. A separate thrust washer can therefore be omitted.
- the drive shaft penetrates this wall delimiting the suction space and interacts with its free end with a rotor of a second pump, in particular a vane pump.
- the drive shaft drives both the radial piston pump and the second pump.
- An embodiment is characterized in that the unbalance compensation element has on its side facing the wall of the suction chamber a radially outwardly directed recess, the one
- the imbalance compensation element thus also serves as a so-called thrust washer, a lubricating film being formed between the imbalance compensation element and the wall delimiting the suction space.
- the inlet control element comprises a control edge lying in the mouth region of the cylinder bore and at least one opening lying in the piston wall.
- the inlet control is therefore preferably in the suction chamber. Depending on the piston position, this breakthrough is covered or released by the control edge, so that through this breakthrough the medium can be sucked in and thus enters the cylinder in order to be pushed out of the cylinder again when the piston moves again.
- Figures each a perspective view of a 2 and 3 nes balancing element.
- FIG. 1 shows a pump housing 1 in which at least one radial piston pump 2 is arranged.
- a second pump 3 is arranged in the pump housing 1 and can be designed as a vane pump 4.
- the radial piston pump 2 has a drive element 5.
- the vane pump also has a drive element 6. It is preferably provided that both drive elements 5 and 6 are formed by a common drive shaft 7, into which a drive torque can be introduced.
- Each pump 2, 3 has a suction connection 8 or 8 'and a pressure connection 9 or 9'.
- the two suction connections 8 and 8 ' can be in the pump housing 1 be brought together in a common connection channel 8 ′′. Both pumps 2 and 3 can then deliver from a common reservoir.
- the radial piston pump 2 has a cylinder block 10 in which one or more pistons 11 are guided in a cylinder bore 12.
- the pressure connection 9 ′ can open, to which an outlet control element 14 can also be assigned.
- a spring element 16 is supported with one end. With its other end, the spring element 16 bears against the stopper 13, so that the piston 11 is pushed in the direction of the drive shaft 7.
- An eccentric 17 acts on the outside of the piston crown 15, which is driven in rotation via the drive shaft 7 and thus displaces the piston 11 in the cylinder bore.
- the eccentric 17 can be formed in one piece with the drive shaft 7 or can be attached in a rotationally fixed manner.
- An intermediate bushing 18, for example a DU bushing, is applied to the eccentric 17 and is surrounded by a hardened steel bushing 19, so that the outside of the piston crown 15 interacts with the outside of the steel bushing 19.
- a Teflon coating is preferably provided on the inside of the intermediate bushing 18 facing the eccentric 17. If the intermediate bushing 18 is designed as a DU bushing, it slides on the eccentric 17 during operation of the radial piston pump 2 while the steel bushing 19 is stationary.
- the eccentric 17 is arranged in a suction chamber 20, which is preferably triple-stepped here, which can be designed as an annular space and is delimited radially by a peripheral wall 21 and axially by side walls 22 and 23.
- the peripheral wall 21 is formed by a plurality of partial walls 21a, 21b, 21c.
- first and second unbalance compensation elements 24 and 25 which are intended to compensate for the unbalance caused by the eccentric rotation.
- the two unbalance compensation elements 24 and 25 run synchronously with the eccentric 17 and can be designed as a compensation eccentric, the two cams 24 'and 25' of the compensation eccentric, ie the unbalance compensation elements, and the cam of the eccentric 17 being oriented so that they extend substantially in opposite directions.
- the second is
- Imbalance compensation element 25 is formed in one piece with the drive shaft 7.
- the first imbalance compensation element 24 is pressed onto the drive shaft 7. It can be seen that the unbalance compensation elements 24 and 25 bear against the side surfaces 17 'of the eccentric 17 such that the intermediate bush 18 and the steel bush 19 cannot slide off the eccentric 17.
- the unbalance compensation elements 24 and 25 have an axial length such that their outer side is supported at least in regions on the side walls 22 and 23 of the suction chamber 20.
- the drive shaft 7 is fixed in the axial direction, the rest is slidably mounted and is surrounded on its housing passage 26 by a shaft seal 27 which is connected to the suction chamber 20 via a channel 28.
- the first imbalance compensation element 24 is described in more detail below with reference to FIGS. 1 and 2: It has a hub 29, the inside diameter di of which is preferably selected such that it can be pressed onto the drive shaft 7.
- the unbalance compensation element 24 further comprises a disk segment 30, which serves as a balance weight and forms the cam 24 '.
- the unbalance compensation element 24 can also be formed by the hub 29, which is connected to an essentially circular disk 34 or has the disk 34, the central axes of the hub 29 and the disk 34 not coinciding and thereby the cam 24 'is formed, which preferably projects beyond the peripheral wall of the hub 29.
- the unbalance compensation element 24 thus has an eccentric shape which comprises the cam 24 ', which serves as a balance weight.
- the medium flow leading from the suction connection 8 ′ to the inlet element 31 is influenced more or less. If a very large distance is selected, as can be seen in FIG. 1, the medium flow from the suction connection 8 ′ can reach the inlet control element 31 essentially unhindered. The unbalance compensation element 24 therefore essentially does not form any hydraulic resistance in the suction area between the suction opening 8 'and the inlet control element 31. This effect is further supported by the bevel 33.
- the bevel 33 is provided on the imbalance compensation element 24 and the axial distance between the cam 24 'and the inlet control element 31 or the suction connection 8' is chosen to be relatively small.
- the thickness D of the disk 34 or the disk segment 30 can also be varied.
- a hydraulic resistance can be formed between the suction connection 8 ′ and the inlet control element 31.
- the flow characteristic curve of the radial piston pump 2 can be changed.
- the hub 29 on the eccentric 17 lies and the balance weight, that is, the cam 24 ', is arranged at a distance from the eccentric 17.
- the balance weight is adjacent to the eccentric 17 would also be conceivable.
- the inlet control element 31 is formed by a control edge 36 ′ which is present on the cylinder block 10 and surrounds the cylinder bore 12 in its mouth region 35 to the suction space 20. At least one opening 36 made in the piston wall of the piston 11 is also assigned to the inlet control element 31. It is therefore clear that, depending on the piston position, a connection can be opened or closed from the suction port 8 'via the suction chamber 20 into the piston chamber 37. Depending on the opening width of the opening 36 and the distance between it and the piston crown 15, a corresponding opening cross section is formed with the control edge 36 ', so that the radial piston pump 2 can also be designed with suction restriction.
- the suction throttling is therefore preferably implemented by means of the inlet control element 31. As can be seen in FIG. 1, several openings 36 can of course also be arranged in the piston wall.
- the drive shaft 7 penetrates the wall 23 delimiting the suction space 20 and is extended to the second pump 3.
- the drive shaft 7 is connected to a rotor of the vane pump 4, not shown here, so that this rotor can be rotated.
- vane pumps it is known that leakage oil flows out of the pressure area, which, for example, converges in the shaft channel 39. Since this medium is under pressure, it can migrate in the shaft channel 39 along the drive shaft 7 in the direction of the imbalance compensation element 24.
- a separate drain channel (not shown) can also be provided for this leakage oil, which opens into the side wall 23 of the suction chamber 20.
- the unbalance compensation element has a recess 40 on its side surface 41 facing the side wall 23, which preferably extends over the entire partial length T of this side surface 41.
- the delivery medium of the vane line pump 4 that has converged in the shaft channel 39 can migrate radially outward in this recess 40, which is designed as a groove, and thus reach the suction chamber 20 of the radial piston pump 2.
- lubricating oil is thus also provided between this side surface 41 and the side wall 23. If, as mentioned above, the counterweight lies adjacent to the eccentric 17, the recess 40 can be made in the base surface of the hub 29 designed as a hollow cylinder facing the side wall 23.
- the first imbalance compensation element 24, optionally with the second imbalance compensation element 25, serves as an imbalance compensation for the rotating eccentric 17.
- the delivery flow characteristic of the radial piston pump 2 to be influenced.
- the conveying flow line can be influenced by the special contouring, for example by the bevel 33 and the thickness D of the disk 34 or the disk segment 30, whereby “influencing” in the course of this application means that either a hydraulic resistance is formed between the suction port 8 'and the inlet control element 31, or the medium flow between the inlet control element 31 and the suction port 8' is unaffected.
- the unbalance compensation element 24 takes over the axial fixing of the drive shaft 7, so that a separate thrust washer can be dispensed with.
- the axial length of the hub 29 is match to the distance between the side surface 17 'of the eccentric 17 and the side wall 23 of the suction chamber 20.
- the axial length of the hub 29 and the thickness D of the disk 34 or the disk segment 30 can therefore be different.
- the recess 40 which serves as a lubrication groove, the lubricating oil that originates from the vane pump 4 can also be drained off.
- the unbalance compensation element 24 according to the invention thus has a multiple function.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19953248A DE19953248A1 (de) | 1999-11-04 | 1999-11-04 | Radialkolbenpumpe |
DE19953248 | 1999-11-04 | ||
PCT/EP2000/010640 WO2001033077A1 (de) | 1999-11-04 | 2000-10-28 | Radialkolbenpumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1230481A1 true EP1230481A1 (de) | 2002-08-14 |
EP1230481B1 EP1230481B1 (de) | 2004-12-22 |
Family
ID=7928003
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00975952A Expired - Lifetime EP1230481B1 (de) | 1999-11-04 | 2000-10-28 | Radialkolbenpumpe |
Country Status (5)
Country | Link |
---|---|
US (1) | US6779986B1 (de) |
EP (1) | EP1230481B1 (de) |
JP (1) | JP4565792B2 (de) |
DE (3) | DE19953248A1 (de) |
WO (1) | WO2001033077A1 (de) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10228552B9 (de) * | 2002-06-26 | 2007-08-23 | Siemens Ag | Radialkolbenpumpeneinheit |
DE102004023195B4 (de) * | 2004-05-11 | 2006-06-14 | Siemens Ag | Radialkolbenpumpe mit Ausgleichsgewicht |
JP2008255985A (ja) | 2007-03-12 | 2008-10-23 | Toyota Industries Corp | 可変容量型圧縮機 |
DE102009003052B4 (de) | 2009-05-13 | 2018-05-03 | Robert Bosch Gmbh | Hochdruckpumpe, insbesondere Radialkolbenpumpe oder Reihenkolbenpumpe, mit einem Antriebs-Nocken dessen Seitenfläche mit einer Lagerscheibe verbunden ist |
WO2012069046A1 (de) * | 2010-11-24 | 2012-05-31 | Ixetic Bad Homburg Gmbh | Radialkolbenpumpe |
CN103133291A (zh) * | 2013-03-22 | 2013-06-05 | 四川盛堡机电科技有限责任公司 | 超高压径向柱塞泵 |
GB201504999D0 (en) * | 2015-03-25 | 2015-05-06 | Delphi International Operations Luxembourg S.�.R.L. | Pump assembly |
CN107676250B (zh) * | 2017-10-29 | 2024-03-15 | 南京润泽流体控制设备有限公司 | 往复式注射泵 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58160574A (ja) * | 1982-03-19 | 1983-09-24 | Nikkiso Co Ltd | ベロ−ズポンプ |
DE3231878C1 (de) * | 1982-08-27 | 1983-11-24 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Pumpe fuer hydraulische Anlagen |
US4915595A (en) * | 1988-06-15 | 1990-04-10 | Deere & Company | Valve/piston cartridge and rotor bearing pre-load for a radial piston pump |
JPH04219472A (ja) * | 1990-12-19 | 1992-08-10 | Aisin Seiki Co Ltd | ラジアルプランジャポンプ |
US5171135A (en) * | 1991-07-25 | 1992-12-15 | Tecumseh Products Company | Flexible suction valve retainer |
JPH078570U (ja) * | 1993-06-29 | 1995-02-07 | 株式会社ユニシアジェックス | ラジアルプランジャポンプ |
US5476371A (en) * | 1994-06-08 | 1995-12-19 | Tecumseh Products Company | Compressor suction valve of toroidal shape with a radial finger |
DE4419927A1 (de) * | 1994-06-08 | 1995-12-14 | Bosch Gmbh Robert | Kolbenpumpe |
DE4430909A1 (de) | 1994-08-31 | 1996-03-07 | Bosch Gmbh Robert | Einheit aus Antriebsmotor und Radialkolbenpumpe |
JPH09303252A (ja) * | 1996-05-13 | 1997-11-25 | Nissan Motor Co Ltd | 油圧ポンプ装置 |
US5951261A (en) * | 1998-06-17 | 1999-09-14 | Tecumseh Products Company | Reversible drive compressor |
-
1999
- 1999-11-04 DE DE19953248A patent/DE19953248A1/de not_active Withdrawn
-
2000
- 2000-10-28 WO PCT/EP2000/010640 patent/WO2001033077A1/de active IP Right Grant
- 2000-10-28 DE DE10083435T patent/DE10083435D2/de not_active Expired - Fee Related
- 2000-10-28 DE DE50009061T patent/DE50009061D1/de not_active Expired - Lifetime
- 2000-10-28 JP JP2001535735A patent/JP4565792B2/ja not_active Expired - Fee Related
- 2000-10-28 EP EP00975952A patent/EP1230481B1/de not_active Expired - Lifetime
- 2000-10-28 US US10/129,450 patent/US6779986B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO0133077A1 * |
Also Published As
Publication number | Publication date |
---|---|
US6779986B1 (en) | 2004-08-24 |
DE10083435D2 (de) | 2002-09-26 |
WO2001033077A1 (de) | 2001-05-10 |
DE19953248A1 (de) | 2001-05-23 |
EP1230481B1 (de) | 2004-12-22 |
JP4565792B2 (ja) | 2010-10-20 |
DE50009061D1 (de) | 2005-01-27 |
JP2003514173A (ja) | 2003-04-15 |
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