WO2004061303A1 - Radialkolbenpumpe - Google Patents
Radialkolbenpumpe Download PDFInfo
- Publication number
- WO2004061303A1 WO2004061303A1 PCT/DE2003/003795 DE0303795W WO2004061303A1 WO 2004061303 A1 WO2004061303 A1 WO 2004061303A1 DE 0303795 W DE0303795 W DE 0303795W WO 2004061303 A1 WO2004061303 A1 WO 2004061303A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- sliding block
- pump
- support
- slide shoe
- 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
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
Definitions
- the present invention relates to a radial piston pump with a plurality of pump units, according to the preamble of patent claim 1.
- Such a radial piston pump is already known from DE 100 39 210 AI.
- the radial piston pump has one
- each pump unit has a pump piston which is guided radially longitudinally in the pump housing.
- the pump piston rests on a sliding block that is supported on the cam ring.
- the cam ring has a number of flats corresponding to the number of pump pistons.
- each pump unit has a slide shoe arrangement with a return spring and a support piston. The return spring is supported with one end on the pump cylinder and the other end on the support piston. Preloading the support spring ensures that the slide shoe remains in constant contact with the cam ring.
- FIG. 6 A sliding shoe arrangement known from DE 100 39 210 AI is shown in FIG. 6.
- the support piston is designed as a stepped sleeve 6.
- the sleeve 6 lies against the cylinder 4 and is thus guided during the up and down movement of the cylinder.
- the widening of the diameter of the sleeve in the lower area serves to receive the slide shoe 8.
- the slide shoe 8 is essentially cylindrical, with a narrow collar 17 on its side upper end. The diameter of the collar 17 corresponds approximately to the inner diameter of the sleeve in the area of the slide shoe holder.
- the sliding shoe is pushed into the receptacle of the sleeve and then secured with the snap ring 12, so that both components are firmly connected to one another.
- the diameter of the slide shoe is always smaller than the snap ring or the inner diameter of the sleeve 6 in the area of the slide shoe receptacle. This limits the contact area of the slide shoe on the lifting ring. Due to the ever increasing requirements regarding maximum pressure generation, the surface pressure between the slide shoe and the cam ring continues to increase, which leads to increased wear of the two components. In addition, when fastening with a snap ring, an additional check must always be carried out to ensure that the snap ring is correctly installed.
- the object of the invention is therefore to enable safe and simple assembly of the slide shoe arrangement and to reduce the surface pressure on the contact area between the slide shoe and the cam ring.
- the invention is characterized in that the connection between the sliding shoe and the support piston is directly positive, the positive connection being effected by a snap-in connection.
- the form-fit by means of a snap-in connection ensures particularly easy installation. An additional securing with a snap ring is not necessary. By eliminating an additional component, the material costs are also reduced. After they have snapped into place, the two components have a play to one another, as a result of which an axial offset between the sliding shoe and the support piston is compensated for can and a full-surface contact between the shoe and the cam ring is guaranteed.
- a particularly advantageous embodiment of the invention provides for the slide shoe to be in the form of a stamp, the end face with the larger cross-sectional area resting on the cam ring. In this way, a particularly large contact surface on the cam ring can be achieved, whereby the surface pressure can be significantly reduced compared to the prior art.
- FIG. 1 shows a longitudinal section through the radial piston pump
- Figure 2 shows a simplified cross section through the, in Figure
- Figure 3 is a detailed view of a pump unit of the figure
- Figure 4a is a detailed view of the support piston with mounted slide shoe
- Figure 4b shows a detail section of the locking connection between
- Support piston and slide shoe and Figure 5 shows another embodiment of a slide shoe.
- FIG. 1 shows a longitudinal section through the radial piston pump 1.
- the radial piston pump 1 has a pump housing in which an eccentric shaft 2 is mounted.
- a movable cam ring 9 is arranged, in which a slide ring 10 is secured against rotation.
- the lifting ring 9 has, as can be seen in particular in FIG. 2, three flattenings, on each of which a sliding block 8 of an associated pump unit 13 is supported.
- the sliding block 8 is pressed against the lifting ring 9 by a support piston 6, so that the lifting ring 9 is fixed in such a way that it cannot freely follow the rotational movement of the eccentric shaft 2, but merely performs a wobble movement.
- the individual pistons of the radial piston pump are loaded by this wobble movement. moved.
- the slide shoe 8 is connected to the support piston 6 by a snap connection.
- the snap-in connection forms a positive connection between the two components and, on the other hand, it ensures a certain amount of play between the support piston 6 and the slide shoe 8. Through the play, it is possible to compensate for a possible axial misalignment between the support piston 6 and the slide shoe 8 and thus to Ensure that the sliding block 8 is always in full contact with the cam ring 9.
- FIG. 3 shows a detailed view of a pump unit as used in the radial piston pump 1 according to FIGS. 1 and 2.
- the pump unit 13 consists of a piston 3, a cylinder 4, a return spring 5, a support piston 6, a return element 7 and a sliding block 8.
- the piston 3 is guided in the cylinder 4 in an axially freely movable manner.
- the sliding block 8 in turn is supported on the cam ring 9.
- the pump unit 13 has a support piston 6, a return element 7 and a return spring 5.
- the support piston 6 is guided in the area of the outer circumference of the cylinder 4.
- the return spring 5 is supported with one end on the cylinder 4 and on the other end on the support piston 6.
- the sliding block 8 and the support piston 6 are designed in such a way that an outer circumferential region of the sliding block 8 is engaged in the assembled state in the inner circumferential region of the support piston 6 and thus produces a positive connection between the two components.
- a reset element 7 is additionally fastened to the piston 3, which is supported on a shoulder region of the support piston 6 and ensures that the piston 3 is returned from its upper end point position to its lower end point position and is constantly in contact with the sliding block 8.
- FIGS. 4a and 4b show a detailed view of the slide shoe arrangement.
- the slide shoe 8 and the support piston ⁇ are positively connected to one another by a snap connection.
- An outer area of the sliding block 8 snaps into an inner area of the support piston 6.
- the support piston 6 is essentially designed as a step-shaped, cylindrical sleeve.
- the sliding block 8 is pushed into the widened end of the support piston 6 and lies against a first collar 15, which forms the transition from the larger to the smaller inside diameter of the support piston 6.
- the snap-in connection is made by a narrow second collar 14 in the edge region of the widened end of the support piston 6.
- the support piston 6 has an inner diameter D1 which is slightly smaller than the outer region of the sliding block 8 provided for positive locking. which has the diameter D3.
- the widened end of the support piston 6 has an inner diameter D2 which is somewhat larger than the diameter D3 of the sliding block 8.
- the sliding block 8 must first be through the second collar 14 overcome the narrowed area of the support piston 6.
- the sliding block 8 must be pressed into the supporting piston 6 with a corresponding force. Pressing can be done with a hammer or a small press, for example. Once the sliding block 8 has overcome the second collar 14, it snaps into the supporting piston 6 and thereby forms a positive connection with the supporting piston 6.
- FIG. 5 shows a further, particularly advantageous, exemplary embodiment of the sliding shoe connection.
- the latching connection is identical to that shown in Figure 4.
- the slide shoe 8 is designed in the shape of a stem, the end face with the larger cross-sectional area abutting the cam ring 9. Due to the latching connection, by means of which the securing by means of a snap ring is omitted, it is possible to design the sliding block 8 in such a way that the end face of the sliding block 8, which rests on the lifting ring 9, has a larger circumference than the maximum circumference of the support piston 6. This reduces the same load on the piston, the surface pressure between the sliding block 8 and the cam ring 9, which leads to an increased service life of the components.
- the invention is not limited to the snap-in connection shown in the exemplary embodiments, but includes all snap-in connections known to the person skilled in the art.
- locking connections are also included in which the support piston is enclosed by the sliding shoe and engages in it.
Landscapes
- 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 |
---|---|---|---|
DE50308141T DE50308141D1 (de) | 2003-01-07 | 2003-11-17 | Radialkolbenpumpe |
EP03785522A EP1581744B8 (de) | 2003-01-07 | 2003-11-17 | Radialkolbenpumpe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10300144.1 | 2003-01-07 | ||
DE2003100144 DE10300144B3 (de) | 2003-01-07 | 2003-01-07 | Radialkolbenpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004061303A1 true WO2004061303A1 (de) | 2004-07-22 |
Family
ID=32115599
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2003/003795 WO2004061303A1 (de) | 2003-01-07 | 2003-11-17 | Radialkolbenpumpe |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1581744B8 (de) |
DE (2) | DE10300144B3 (de) |
WO (1) | WO2004061303A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004035251B4 (de) * | 2004-07-21 | 2006-06-14 | Siemens Ag | Radikalkolbenpumpe |
DE102004050886A1 (de) * | 2004-10-19 | 2006-04-20 | Siemens Ag | Radialkolbenpumpe mit Wellenabdichtung |
DE102005007839B3 (de) * | 2005-02-21 | 2006-05-18 | Siemens Ag | Radialkolbenpumpe mit Spülleitung |
DE112011104511A5 (de) * | 2010-12-23 | 2013-10-17 | Schaeffler Technologies AG & Co. KG | Radialkolbenpumpe |
CN103758721B (zh) * | 2013-10-18 | 2016-02-24 | 西安交通大学 | 一种轴配流式双列径向柱塞液压泵 |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4216877A1 (de) * | 1991-08-12 | 1993-02-18 | Rexroth Mannesmann Gmbh | Radialkolbenpumpe |
DE19727249A1 (de) * | 1996-07-01 | 1998-01-08 | Rexroth Mannesmann Gmbh | Vorrichtung zur Stabilisierung des Exzenterrings einer Radialkolbenpumpe |
DE19943160A1 (de) * | 1998-09-10 | 2000-03-16 | Denso Corp | Kraftstoffeinspritzpumpe |
EP1022461A2 (de) * | 1999-01-21 | 2000-07-26 | Siemens Aktiengesellschaft | Hochdruckpumpe |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10039210A1 (de) * | 2000-08-10 | 2002-02-28 | Siemens Ag | Radialkolbenpumpe mit zweiteiligem Federträger |
-
2003
- 2003-01-07 DE DE2003100144 patent/DE10300144B3/de not_active Expired - Fee Related
- 2003-11-17 DE DE50308141T patent/DE50308141D1/de not_active Expired - Lifetime
- 2003-11-17 WO PCT/DE2003/003795 patent/WO2004061303A1/de active IP Right Grant
- 2003-11-17 EP EP03785522A patent/EP1581744B8/de not_active Expired - Lifetime
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4216877A1 (de) * | 1991-08-12 | 1993-02-18 | Rexroth Mannesmann Gmbh | Radialkolbenpumpe |
DE19727249A1 (de) * | 1996-07-01 | 1998-01-08 | Rexroth Mannesmann Gmbh | Vorrichtung zur Stabilisierung des Exzenterrings einer Radialkolbenpumpe |
DE19943160A1 (de) * | 1998-09-10 | 2000-03-16 | Denso Corp | Kraftstoffeinspritzpumpe |
EP1022461A2 (de) * | 1999-01-21 | 2000-07-26 | Siemens Aktiengesellschaft | Hochdruckpumpe |
Also Published As
Publication number | Publication date |
---|---|
EP1581744A1 (de) | 2005-10-05 |
EP1581744B1 (de) | 2007-09-05 |
DE10300144B3 (de) | 2004-05-19 |
DE50308141D1 (de) | 2007-10-18 |
EP1581744B8 (de) | 2008-01-02 |
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