EP1025360B1 - Innenzahnradmaschine - Google Patents
Innenzahnradmaschine Download PDFInfo
- Publication number
- EP1025360B1 EP1025360B1 EP98952712A EP98952712A EP1025360B1 EP 1025360 B1 EP1025360 B1 EP 1025360B1 EP 98952712 A EP98952712 A EP 98952712A EP 98952712 A EP98952712 A EP 98952712A EP 1025360 B1 EP1025360 B1 EP 1025360B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- sealing
- segment
- sectional area
- cross
- sealing strip
- 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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Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members
Definitions
- the invention relates to an internal gear machine (pump or Motor) with an externally toothed pinion and one with the Pinion with internal toothed ring gear, with a semi-crescent-shaped, in the space between the pinion and the ring gear arranged filler, which consists of a segment carrier and a sealing segment, and with at least a spring-loaded cylindrical sealing element between the segment carrier and the sealing segment.
- an internal gear machine pump or Motor
- pinion externally toothed pinion and one with the Pinion with internal toothed ring gear
- a semi-crescent-shaped in the space between the pinion and the ring gear arranged filler, which consists of a segment carrier and a sealing segment, and with at least a spring-loaded cylindrical sealing element between the segment carrier and the sealing segment.
- Such an internal gear machine is from DE 43 22 239 A1 known.
- a semi-crescent Filler arranged, which consists of a segment carrier and there is a sealing segment. Between the segment carrier and there is a gap in the sealing segment. That gap is characterized by two sealing elements that extend across the width of the Extend filler, sealed.
- the sealing elements are designed as sealing rollers with a circular cross-section. The sealing rollers are each against the leaf spring Segment carrier and pressed against the sealing segment. The Sealing rollers touch the segment carrier and the sealing segment each linear.
- segment carrier In practice, however, there is one elastic deformation of segment carrier, sealing segment and Sealing roll instead, which is the greater the greater the force with which the sealing rollers against the segment carrier and be pressed against the sealing segment.
- This power is in the Operation of the internal gear machine depending on the pressure with which the internal gear machine is operated. From the line-shaped In practice, touch becomes a flat one Contact. The larger the touching areas are, the lower the mechanical stress of the Segment carrier, the sealing segment and the sealing rollers.
- the diameter of the sealing rollers as large as possible to choose so that the contact surfaces between the sealing roller and the segment carrier on the one hand and between the Sealing roller and the sealing segment on the other hand as large as possible are.
- increasing the diameter of the sealing rollers is basically an increase in the maximum permissible Operating pressure of the internal gear machine possible.
- increasing the diameter of the sealing rollers is a limit set.
- the segment carrier is with recesses for the Mount the sealing rollers and the leaf springs.
- the Size of these recesses is due to the diameter of the Sealing rollers and the thickness of the leaf springs determined. Since the Recesses weaken the segment carrier, they limit the maximum allowable pressure with which the internal gear machine may be operated, the larger the larger they are. To the Recesses for the sealing rollers and the leaf springs Keep it as small as possible for the different Sizes of internal gear machines sealing rollers with different large diameters used in fine gradation. The individual diameters only differ by a few tenths of a millimeter.
- the invention has for its object an internal gear machine of the type mentioned at the beginning, which it allows the internal gear machine with the same external dimensions operate at a higher pressure.
- the sealing element as Sealing strip
- the cross-sectional area of one in itself closed polygon formed like a triangle there is a large contact area between the Sealing strip and the segment carrier and between the sealing strip and the sealing segment.
- the one for the sealing strips receiving recesses space is reduced because the radius of the circumference of the cross-sectional area of the sealing strip can be chosen smaller than the radius of the circular Cross-sectional area of a corresponding sealing roller.
- the weakening of the segment carrier is therefore less so that the segment carrier can be loaded with a greater force is. Since the force acting on the segment carrier is from the Pressure in the internal gear machine is dependent an increase in the maximum permissible on the segment carrier acting force also a corresponding increase in pressure, with which the internal gear machine can be operated.
- a convex rounding of the sides the cross-sectional area of the sealing strips gives one Radius of curvature of the cross-sectional area of the sealing strip in the on the segment carrier and in the area on the Sealing segment adjacent area of the sealing strip, each larger than the radius of the circumference of the cross-sectional area the sealing strip is.
- a convex rounding of the corners too the cross-sectional area of the sealing strip reduces the circumference the cross-sectional area of the sealing strip. Also reduced there is a risk that the sealing strip is in the gap canted between the segment carrier and the sealing segment.
- the cross-sectional area of the sealing strip Due to the different radius of curvature of the circumferential line the cross-sectional area of the sealing strip, which is from a small value in the area of the corners to a maximum Value enlarged in the middle of the pages is enough for the different sizes of the internal gear machine a coarser Gradation of the dimensions of the sealing strip. Hereby reduce the effort and costs for warehousing. In addition, there is a rough gradation of the dimensions the sealing strip the risk of confusion is less than with fine gradations, as different sizes can be distinguished without special measuring equipment. Due to the symmetrical design of the cross-sectional area of the Sealing strip needs the angular position of the when installing Sealing strip not to be considered.
- Figure 1 shows a section through the housing of a Pump trained internal gear machine 1.
- the ring gear 4 is in the Center part 2 of the housing of the internal gear machine 1 out.
- the pinion 3 is held on a drive shaft 5 in a rotationally fixed manner.
- the drive shaft 5 is not one of the in Figure 1 shown motor driven.
- the direction of rotation of the Drive shaft 5 driven pinion 3 is by an arrow 6 specified.
- the filler 8 consists of a segment carrier 9 and a sealing segment 10.
- the segment carrier 9 and the sealing segment 10 are supported from a flat 11 of a stop pin 12. Between the Segment carrier 9 and the sealing segment 10 is located Gap 13. Two sealing strips 14 and 15, both on the Segment carrier 9 as well as on the sealing segment 10, seal the gap 13. Provide two leaf springs 16 and 17 for a defined position of the sealing strips 14 and 15. The Sealing strips 14 and 15 and the leaf springs 16 and 17 are arranged in recesses of the segment carrier 9. details of the filler 8 are in Figure 2 on an enlarged scale shown. Via a suction channel 18 and via in FIG. 1 invisible channels that pass the ring gear 4 laterally, 7 hydraulic fluid is supplied to the free space.
- FIG. 2 shows a section through the filler 8 in compared to Figure 1 enlarged view.
- the segment carrier 9 and the sealing segment 10 are supported on the Flattening 11 of the stop pin 12. Between the Segment carrier 9 and the sealing segment 10 extends Gap 13.
- the recesses for the sealing strips 14 and 15 and the leaf springs 16 and 17 are in the segment carrier 9 provided with the reference numerals 21 and 22.
- the cross-sectional area the sealing strips 14 and 15 is not circular like in the state of the art but from a self-contained Polygon in the manner of a triangle, preferably one simultaneous triangle, formed, its sides and corners are convexly rounded.
- FIG. 3 shows a state of the art technology as a sealing roller with a circular cross-sectional area formed sealing element and in Figure 4 a according to the invention as a sealing strip with a triangular cross-sectional area trained sealing element compared.
- FIG. 3 shows a state of the art technology as a sealing roller with a circular cross-sectional area formed sealing element and in Figure 4 a according to the invention as a sealing strip with a triangular cross-sectional area trained sealing element compared.
- FIG. 3 shows a section from FIG. 2, namely the area of FIG Recess 21, shown in an enlarged view.
- the corresponding area is also shown in FIG. 3.
- the parts of FIG. 3 corresponding to FIG. 4 are marked with the provided reference numerals used in Figure 4, where the reference symbol is added to distinguish between "*" is.
- FIG. 3 shows a sealing roller 14 * used in the prior art.
- the sealing roller 14 * is arranged in a recess 21 * of a segment carrier 9 *. It is pressed by a leaf spring 16 * against a side wall of the recess 21 * of the segment carrier 9 * and against the sealing segment 10 *.
- the side of the recess 21 * facing away from the sealing segment 10 * is rounded in order to keep the notch effect of the recess 21 * as low as possible.
- the radius of the cross-sectional area of the sealing roller 14 * is denoted by r k .
- the largest possible radius r k is advantageous.
- the line of contact between the sealing roller 14 * and the segment carrier 9 * due to the elastic deformation of the sealing roller 14 * and the segment carrier 9 *, changes into a contact area which is larger the larger the radius r k Sealing roller 14 * is. The same applies to the line of contact between the sealing roller 14 * and the sealing segment 10 *.
- the smallest possible radius r k is advantageous since the recess 21 * weakens the segment carrier 9 *.
- the radius r k of the sealing roller 14 * in FIG. 3 is optimized so that the internal gear machine can be operated with the greatest possible pressure.
- a sealing strip 14 designed according to the invention is used instead of the sealing roller 14 * used in FIG.
- the circumference of the cross-sectional area of the sealing strip 14 is provided with the reference number 23, the radius r u of the circumference is denoted by r u .
- the circumference 23 of the cross-sectional area of the sealing strip 14 is chosen to be exactly as large as the circular cross-sectional area of the sealing roller 14 *. It can be clearly seen that the radius of the sealing strip 14, both in the area of contact between the sealing strip 14 and the segment support 9 and in the area of contact between the sealing strip 14 and the sealing segment 10, is greater than the radius r k in the corresponding contact areas in FIG.
- the circumferential line of the recess 21 * for comparison as a dashed line 24.
- the area 25 between the broken line 24 and the recess 21 shows the extent to which the recess 21 is smaller than the recess 21 *.
- the radius of the sealing strip 14 is larger both in the region of the contact surface of the sealing strip 14 with the segment carrier 9 and in the region of the contact surface of the sealing strip 14 with the sealing segment 10 than with a sealing roller 14 * with the same radius as the circumference 23 of the cross-sectional area of the sealing strip 14 is, the recess 21 required for receiving the sealing strip 14 and the leaf spring 16 is smaller than the corresponding recess 21 * in FIG. 3.
- the invention allows the internal gear machine to be operated at a higher pressure.
- FIG. 5 shows the cross-sectional area provided with the reference number 26 of the sealing strip 14 shown in FIG. 4.
- the circumferential line of the cross-sectional area 26 is provided with the reference number 27.
- the circumferential line 27 is a self-contained polygon that encloses the cross-sectional area 26 in the manner of an equilateral triangle, the sides 28, 29 and 30 and the corners 31, 32 and 33 of which are convexly rounded.
- the radius of curvature of the circumferential line 27 is smaller in the region of the corners 31, 32 and 33 than in the center of the sides 28, 29 and 30.
- the circumferential line 27 in the region of the corners 31, 32 and 33 consists of sections of circles with the centers 34, 35 and 36 and the radius r e .
- the pages 28, 29 and 30 consist of sections of circles with the center points 37, 38 and 39 and the radius r s .
- the radius r s is more than ten times larger than the radius r e .
- a circular section with the radius r e is connected to a circular section with the radius r s via a transition section.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Description
- Figur 1
- einen Schnitt durch eine als Pumpe ausgebildete Innenzahnradmaschine,
- Figur 2
- einen Schnitt durch das Füllstück der in der Figur 1 dargestellten Innenzahnradmaschine in vergrößerter Darstellung,
- Figur 3
- einen Schnitt durch ein zum Stand der Technik gehörendes, als Dichtrolle ausgebildetes Dichtelement,
- Figur 4
- einen Schnitt durch ein gemäß der Erfindung als Dichtleiste ausgebildetes Dichtelement und
- Figur 5
- die Querschnittsfläche der in der Figur 4 dargestellten Dichtleiste.
Claims (6)
- Innenzahnradmaschine (Pumpe oder Motor) mit einem außenverzahnten Ritzel und einem mit dem Ritzel mitlaufenden innenverzahnten Hohlrad, mit einem halbsichelförmigen, in dem Freiraum zwischen dem Ritzel und dem Hohlrad angeordneten Füllstück, das aus einem Segmentträger und einem Dichtsegment besteht, und mit mindestens einem sich über die Breite des Segmentträgers erstreckenden federbelasteten zylinderförmigen Dichtelement zwischen dem Segmentträger und dem Dichtsegment, dadurch gekennzeichnet, daß das Dichtelement als Dichtleiste (14, 15) ausgebildet ist, deren Querschnittsfläche (26) von einem in sich geschlossenen Polygonzug in der Art eines Dreiecks gebildet ist.
- Innenzahnradmaschine nach Anspruch 1, dadurch gekennzeichnet, daß die Seiten (28, 29, 30) der Querschnittsfläche (26) der Dichtleiste (14, 15) konvex verrundet sind.
- Innenzahnradmaschine nach Anspruch 2, dadurch gekennzeichnet, daß die Ecken (31, 32, 33) der Querschnittsfläche (26) der Dichtleiste (14, 15) konvex verrundet sind.
- Innenzahnradmaschine nach Anspruch 3, dadurch gekennzeichnet, daß der Krümmungsradius der Umfangslinie (27) der Querschnittsfläche (26) der Dichtleiste (14, 15) im Bereich der Ecken (31, 32, 33) kleiner als in der Mitte der Seiten (28, 29, 30) ist.
- Innenzahnradmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Querschnittsfläche (26) der Dichtleiste (14, 15) von einem geschlossenen Polygonzug in der Art eines gleichschenkligen Dreiecks gebildet ist.
- Innenzahnradmaschine nach Anspruch 5, dadurch gekennzeichnet, daß die Querschnittsfläche (26) der Dichtleiste (14, 15) von einem geschlossenen Polygonzug in der Art eines gleichseitigen Dreiecks gebildet ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19746983 | 1997-10-24 | ||
DE19746983A DE19746983A1 (de) | 1997-10-24 | 1997-10-24 | Innenzahnradmaschine |
PCT/EP1998/006588 WO1999022142A1 (de) | 1997-10-24 | 1998-10-17 | Innenzahnradmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1025360A1 EP1025360A1 (de) | 2000-08-09 |
EP1025360B1 true EP1025360B1 (de) | 2001-11-28 |
Family
ID=7846480
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98952712A Expired - Lifetime EP1025360B1 (de) | 1997-10-24 | 1998-10-17 | Innenzahnradmaschine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1025360B1 (de) |
DE (2) | DE19746983A1 (de) |
WO (1) | WO1999022142A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012217225A1 (de) * | 2012-09-25 | 2014-03-27 | Robert Bosch Gmbh | Innenzahnradpumpe für eine hydraulische Fahrzeugbremsanlage |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE7607930L (sv) * | 1975-07-28 | 1977-01-29 | Otto Eckerle | Kugghjulspump eller- motor for hogtrycksmedium |
CH679879A5 (de) * | 1989-09-25 | 1992-04-30 | Bucher Maschf Gmbh | |
DE4322239C2 (de) * | 1993-07-03 | 1997-04-24 | Eckerle Rexroth Gmbh Co Kg | Innenzahnradmaschine (Pumpe oder Motor) |
-
1997
- 1997-10-24 DE DE19746983A patent/DE19746983A1/de not_active Withdrawn
-
1998
- 1998-10-17 DE DE59802272T patent/DE59802272D1/de not_active Expired - Fee Related
- 1998-10-17 EP EP98952712A patent/EP1025360B1/de not_active Expired - Lifetime
- 1998-10-17 WO PCT/EP1998/006588 patent/WO1999022142A1/de active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
DE19746983A1 (de) | 1999-04-29 |
EP1025360A1 (de) | 2000-08-09 |
DE59802272D1 (de) | 2002-01-10 |
WO1999022142A1 (de) | 1999-05-06 |
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