EP1025360A1 - Innenzahnradmaschine - Google Patents
InnenzahnradmaschineInfo
- Publication number
- EP1025360A1 EP1025360A1 EP98952712A EP98952712A EP1025360A1 EP 1025360 A1 EP1025360 A1 EP 1025360A1 EP 98952712 A EP98952712 A EP 98952712A EP 98952712 A EP98952712 A EP 98952712A EP 1025360 A1 EP1025360 A1 EP 1025360A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- sealing
- segment
- internal gear
- cross
- sectional area
- 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
- 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 an internally toothed ring gear which rotates with the pinion, with a semi-crescent shaped filler which is arranged in the space between the pinion and the ring gear and consists of a segment carrier and a sealing segment, and with at least one spring-loaded cylindrical sealing element between the segment carrier and the sealing segment.
- a semi-crescent shaped filler which is arranged in the space between the pinion and the ring gear and consists of a segment carrier and a sealing segment, and with at least one spring-loaded cylindrical sealing element between the segment carrier and the sealing segment.
- Such an internal gear machine is known from DE 43 22 239 AI.
- a semi-crescent-shaped filler is arranged, which consists of a segment carrier and a sealing segment. There is a gap between the segment carrier and the sealing segment. This gap is sealed by two sealing elements that extend across the width of the filler.
- the sealing elements are designed as sealing rollers with a circular cross section. The sealing rollers are pressed against the segment carrier and against the sealing segment by a leaf spring. The sealing rollers each touch the segment carrier and the sealing segment in a line.
- a sealing roller the diameter of which is of the order of magnitude of the gap between the segment carrier and the sealing segment, could get jammed in the gap between the segment carrier and the sealing segment
- the segment carrier is provided with recesses for receiving the sealing rollers and the leaf springs.
- the size of these recesses is determined by the diameter of the sealing rollers and the thickness of the leaf springs. Since the recesses weaken the segment carrier, they limit the maximum permissible pressure with which the internal gear machine can be operated, the greater the larger they are. In order to keep the recesses for the sealing rollers and the leaf springs as small as possible, sealing rollers with different sizes of diameters are used in fine increments for the different sizes of internal gear machines. The individual diameters only differ by a few tenths of a millimeter.
- the invention has for its object to provide an internal gear machine of the type mentioned, which allows the internal gear machine to be operated at a higher pressure with the same external dimensions.
- the sealing element as a sealing strip, the cross-sectional area of which is formed by a self-contained polygon in the manner of 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 space required for the recesses receiving the sealing strips is reduced since the radius of the circumference of the cross-sectional area of the sealing strip can be selected to be 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. Since the force acting on the segment carrier is dependent on the pressure in the internal gear machine, an increase in the maximum permissible force acting on the segment carrier also enables a corresponding increase in the pressure with which the internal gear machine may be operated.
- a convex rounding of the sides of the cross-sectional area of the sealing strips results in a radius of curvature of the cross-sectional area of the sealing strip in the area lying against the segment carrier and in the area of the sealing strip lying against the sealing segment, which radius is in each case larger than the radius of the circumference of the cross-sectional area of the sealing strip.
- a convex rounding of the corners of the cross-sectional area of the sealing strip also reduces the circumference of the cross-sectional area of the sealing strip. In addition, the risk of the sealing strip jamming in the gap between the segment carrier and the sealing segment is reduced.
- FIG. 1 shows a section through an internal gear machine designed as a pump
- FIG. 2 shows a section through the filler piece of the internal gear machine shown in FIG. 1 in an enlarged view
- Figure 3 shows a section through one of the prior art, designed as a sealing roller
- Figure 4 shows a section through a sealing element designed according to the invention as a sealing strip
- Figure 5 shows the cross-sectional area of the sealing strip shown in Figure 4.
- FIG. 1 shows a section through the housing of an internal gear machine 1 designed as a pump.
- an externally toothed pinion 3 and an internally toothed ring gear 4 are arranged in the central part 2 of the housing of the internal gear machine 1.
- the ring gear 4 is in the
- the pinion 3 is held on a drive shaft 5 in a rotationally fixed manner.
- the drive shaft 5 is driven by a motor, not shown in FIG. 1.
- the direction of rotation of the Drive shaft 5 driven pinion 3 is indicated by an arrow 6.
- a filler 8 is arranged in a free space 7 between the ring gear 4 and the pinion 3.
- 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 on a flattened portion 11 of a stop pin 12.
- Two leaf springs 16 and 17 ensure a defined position of the sealing strips 14 and 15, respectively.
- the sealing strips 14 and 15 and the leaf springs 16 and 17 are arranged in recesses in the segment carrier 9. Details of the filler 8 are shown in Figure 2 on an enlarged scale. Hydraulic fluid is supplied to the free space 7 via a suction channel 18 and via channels which are not visible in FIG. 1 and which pass the ring gear 4 laterally. Hydraulic fluid located in the tooth gaps travels along the filler 8 and reaches the tooth engagement area of the pinion 3 and the ring gear 4, which is provided with the reference numeral 19. From there, the hydraulic fluid is passed laterally to the gearwheels 3 and via channels not visible in FIG 4 displaced past in a pressure channel 20.
- the gap 13 extends between the segment carrier 9 and the sealing segment 10.
- the recesses for the sealing strips 14 and 15 and the leaf springs 16 and 17 in the segment carrier 9 are provided with the reference numerals 21 and 22.
- the cross-sectional area of the sealing strips 14 and 15 is not circular, as in the prior art, but is formed by a self-contained polygon shape in the manner of a triangle, preferably a simultaneous triangle, the sides and corners of which are convexly rounded.
- FIG. 4 For comparison, a sealing element designed according to the prior art as a sealing roller with a circular cross-sectional area and in FIG. 4 a sealing element designed according to the invention as a sealing strip with a triangular cross-sectional area are compared.
- a detail from FIG. 2, namely the area of the recess 21, is shown in an enlarged representation in FIG.
- the corresponding area is also shown in FIG. 3.
- the parts of FIG. 3 corresponding to FIG. 4 are provided with the reference symbols used in FIG. 4, a “*” being added to the reference symbol to differentiate them.
- 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 surface of the sealing roller 14 * is marked r. In view of the largest possible contact surfaces between the sealing roller 14 * and the segment carrier 9 * and between the sealing roller 14 * and the sealing segment 10 * when the sealing roller 14 * is pressurized by the hydraulic fluid, the largest possible radius r.
- the radius r. the sealing roller 14 * in FIG. 3 should be optimized so that the internal gear machine can be operated with the greatest possible pressure.
- FIG. 4 instead of the sealing roller 14 * used in FIG. 3, a sealing strip 14 designed according to the invention is used.
- the circumference of the cross-sectional area of the sealing strip 14 is provided with the reference number 23, the radius ru of the circumference is denoted by ru.
- the radius is the same size as the circular cross-sectional area of the sealing roller 14 choose the cross-sectional area of the sealing strip 14 * 23rd 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 carrier 9 and in the
- 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 middle 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 center points 34, 35 and 36 and the radius r. Pages 28, 29 and 30 consist of
- a circular section with the radius r is connected to a circular section with the radius rs 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)
Abstract
Description
Claims
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 true EP1025360A1 (de) | 2000-08-09 |
EP1025360B1 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
Non-Patent Citations (1)
Title |
---|
See references of WO9922142A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE19746983A1 (de) | 1999-04-29 |
DE59802272D1 (de) | 2002-01-10 |
WO1999022142A1 (de) | 1999-05-06 |
EP1025360B1 (de) | 2001-11-28 |
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