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
• • 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
  • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
  • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
  • F04C15/0007—Radial sealings for working fluid
  • F04C15/0019—Radial sealing elements specially adapted for intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

• the invention is based on an internal gear pump for a brake system according to the preamble of independent claim 1, as used in particular in the hydraulic system of the brake systems of vehicles.
• Fluid pressure is supported on the pressure side to a stop surface.
• the filler lies with its curved inner or outer peripheral surface under radial sealing to a plurality of tooth tips of pinion and ring gear. Since the entrained by the sealed tooth gaps of the rotating in the same direction sense gears fluid volumes at the tapered end of the filler, resulting in this area of the pump, the desired high pressure level.
• the filler is composed of a base part forming the segment carrier and a movably supported on the segment carrier sealing segment, wherein the peripheral surface of the segment carrier to the overlapped tooth tips of the pinion and the opposite peripheral surface of the sealing segment the overlapped tooth tips of the ring gear rests.
• a leaf spring assembly is further supported with three leaf springs, are pressed apart by which segment carrier and sealing segment and thus rest under a spring load on the overlapped tooth heads.
• segment carrier and sealing segment are available under appropriate operating conditions is pressed apart via a corresponding approximately half the operating pressure fluid pressure, as a divided by elastic sealing rollers made of an elastomer or polymer material gap between the segment carrier and sealing element is connected by recesses fluidly with a pressure build-up area of the ring gear.
• the sealing rollers engage in an associated groove and must be held in their sealing position during the displacement of the sealing element by means of one of the three leaf springs.
• the seal between the overlapped tooth tips and cooperating with them peripheral side of the segment carrier and sealing element automatically increases with increasing pressure level of the pump by increasing the contact pressure.
• the individual parts of the filler must be made very precisely in order to ensure proper operation of the internal gear pump with a reasonable life.
• the internal gear pump according to the invention according to the features of independent claim 1 has the advantage that it can be designed structurally much easier and thereby produce less expensive and easier to assemble. Small tolerances in the radial direction are automatically compensated by resilient adaptation of the peripheral wall. A structural simplification by
• both circumferential sides of the filler are formed by a radially resilient peripheral wall.
• both circumferential walls can create under adapted bending deformation sealingly to the overlapped by her teeth heads of the associated teeth.
• a particularly compact design of the filler in its longitudinal direction is possible by extending each radially resilient peripheral wall of the filler over the entire length of the associated peripheral side.
• the filler piece comprises a hollow chamber, which is delimited by one or both radially resilient peripheral walls of the filler piece and fluidly connected to a pressure region of the internal gear pump.
• the radially resilient peripheral walls of the filler over the radial spring load also pushed apart by the hydraulic operating pressure and placed in a the head circle diameter of pinion or ring gear corresponding to the tooth heads.
• the radial contact force of the circumferential wall or the peripheral walls is automatically adjusted proportionally to the rising operating pressure of the internal gear pump and thus compensated accordingly.
• the radial spring preload of the peripheral wall or peripheral walls can be chosen to be moderate in order to avoid excessive friction losses of the internal gear pump.
• a particularly simple and lightweight construction of the filler results when both radially resilient peripheral walls are connected to each other at the supported end of the filler over a support wall, from which they cantilever freely as a leg.
• the filler thus comprises only three adjoining wall portions, wherein the ends of the cantilevered leg limit the overflow to the pressure side of the internal gear pump.
• the support wall can preferably be formed in one piece with the two peripheral walls and consist of pre-bent lengths of a leaf spring made of spring steel.
• a clearance may advantageously be present between the free ends of the peripheral walls, so that the clear cross section between the free ends of the peripheral walls forms the overflow opening for the fluid from the pressure region of the pump housing.
• the support wall of the filler can be provided with a central recess, the knee lever-like wall course is stretched as the reduction of the recess on the fluid pressure inside the filler, resulting in a corresponding spreading apart of the peripheral walls taking advantage of the - A -
• the support wall is supported by means of a round stop surface, which with a
• Partial cross section protrudes into the recess.
• the round stop surface may expediently be the cylindrical peripheral surface of a bolt passing transversely through the pump housing.
• the stop surface may, however, be a flat surface, which may in particular be formed by a flattened peripheral side of a round bolt passing through the pump housing.
• the planar abutment surface results in an enlarged support distance, since the support wall rests only with their hump-shaped curved transition regions of the central recess of the support wall to the peripheral walls of the filler.
• the support wall is thus already bent back at lower operating pressure of the fluid in its stretched expanded position.
• a larger radial extension feed can be generated, since the possible deformation path of the support wall is greater than in a support which engages in the hollow cross-section of the indentation.
• a housing-fixed holding device can advantageously be provided, by means of which the filler piece is supported on the inner side opposite the stop surface.
• Fig. 1 shows the interior of an internal gear pump with a Greetrachlorosemiconductor
• Fig. 2 shows the filler of the internal gear pump separately in the side view.
• Fig. 3 shows the filler of the internal gear pump separately in the circumferential view.
• Fig. 4 shows the filler of the internal gear pump separately in perspective oblique view.
• Fig. 5 shows the interior of a variant of the internal gear pump in side view with modified Gundanaku.
• An internal gear pump 10 for a hydraulic system of a brake system shown in FIG. 1 comprises as main components a ring gear 12 rotatably mounted in a sliding bearing of a pump housing 11 with internal teeth, in which a corresponding counter-toothing of a pinion rotatably mounted eccentrically to the ring gear 12 in the pump housing 11 11 meshes.
• the internal toothing of the ring gear 12 has, for example, 19 teeth and the external toothing of the pinion 13 13 teeth.
• the top circles of ring gear 12 and pinion 13 define a crescent-shaped pumping space in which a crescent-shaped filling piece 14, which is essentially adapted to the peripheral contour of this space, is arranged.
• the filling piece 14 has the task of covering the tooth gaps covered by it, which are sealed axially on both sides by the end faces of the pump housing 11 or printing plates arranged thereon, by means of flat surfaces
• the ring gear 12 is rotated about the meshing engagement in the same direction.
• the hydraulic fluid in the internal gear pump 10 in the tooth spaces of ring gear 12 and pinion 13 is conveyed from the low-pressure region to the high-pressure region of the internal gear pump 10.
• the low pressure area is located in the left half of the pump housing 11, in which a large inflow opening 15 is arranged, and the high pressure area in the right half of the pump housing 11, in which the corresponding smaller discharge opening 16 can be seen.
• the increase in pressure in the hydraulic fluid is created by combining the entrained by the teeth in the tooth gaps fluid volumes at the tapered end of the filler 14 in conjunction with the overflow between low pressure and high pressure region of the réelle leopard- wheel pump 10 by means of the filler 14.
• the filling piece 14 consists of a one-piece, divided into three sections leaf spring made of spring steel with a constant, parallelepiped parallel section.
• the filling piece 14 is pre-bent with a sickle-like peripheral contour and thus comprises a support wall 14a as a base part, an inner peripheral wall 14b and an outer peripheral wall 14c.
• the curvature of the inner peripheral wall 14b over the length thereof is approximately matched to the tip circle of the pinion 13 and the curvature of the outer peripheral wall 14c over its length approximately to the tip circle of the internal toothing of the ring gear 12, wherein the filler 14 is shorter on the inner circumference than on the outer circumference.
• the filler piece 14 In the exemplary embodiment shown, three tooth heads of the external toothing of the pinion 13 and five tooth heads of the internal toothing of the ring gear 12 are simultaneously covered by the filler piece 14.
• the radially resilient peripheral walls 14b and 14c connected via the support wall 14a project into the support wall 14a at a bend of approximately 90 degrees and protrude freely from the support wall 14a, resulting in two longitudinal sections of the support wall 14a enclosing an obtuse angle, which are interconnected via an oppositely curved middle length region of the support wall 14a.
• the support wall 14 a is provided in its central region with a recess 17.
• the two peripheral walls 14b and 14c Prior to installation, the two peripheral walls 14b and 14c are further spread apart so that they are compressed when inserting between the teeth of ring gear 12 and pinion 13. By this Verzwfitung it is ensured that the circumferential walls 14b and 14c snugly nestle under their resilient restoring forces to the associated tooth heads.
• the filler 14 is pre-bent so that its resilient peripheral walls 14b and 14c rest after insertion between the ring gear 12 and pinion 13 with sufficient radial biasing force to the tooth tips of their associated teeth. Between the free ends of the peripheral walls 14b and 14c there remains a gap which represents an overflow opening to the pressure side or to the high-pressure region of the internal gear pump 10.
• the entire hollow chamber of the filling piece 14 outlined by the support wall 14a, the peripheral wall 14b and the peripheral wall 14c and bounded axially by housing walls or their pressure plates fills with the hydraulic fluid and is under the pressure prevailing in the high-pressure region.
• the peripheral walls 14a and 14b are pushed apart, so that their decisive for the sealing effect on the tooth tips pressure force is automatically increased pressure-dependent.
• the support wall 14a is additionally deformed, wherein the curved central region of the support wall 14a bent and thereby moved to the flat stop surface 18a and the support wall 14a is flattened accordingly.
• the angle between the longitudinal regions of the support wall delimiting the indentation 17 becomes blunt, which leads to an extension of the support wall 14a.
• the stretching forces transmitted thereby also additionally divide the circumferential walls 14b and 14c apart and ensure an improved sealing to the low-pressure region of the internal gear pump 10 in the case of the tooth heads lying close to the support wall 14a.
• the embodiment of the internal gear pump 10 shown in Fig. 5 differs from that described only by the type of support of the filler 14 in the region of the support wall 14a.
• a stop pin 20 is provided with a cylindrical cross section, which engages with a partial cross section in the recess 17 of the support wall 14a. This results in addition to the axial support and a certain radial support of the support wall 14a on the stop pin 20.
• the extended position of the support wall 14a in which this almost the entire surface of the stop pin 20th is present and maximum spreading forces in the supporting wall near peripheral portions of the peripheral walls 14a and 14b initiates.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Rotary Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)

Applications Claiming Priority (2)

Publications (1)

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Country Status (6)

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• 2007
  • 2007-10-17 DE DE102007049704.2A patent/DE102007049704B4/de not_active Expired - Fee Related
• 2008
  • 2008-09-19 US US12/738,459 patent/US8475150B2/en not_active Expired - Fee Related
  • 2008-09-19 EP EP08838841A patent/EP2212559A1/de not_active Withdrawn
  • 2008-09-19 WO PCT/EP2008/062563 patent/WO2009049991A1/de active Application Filing
  • 2008-09-19 CN CN2008801117316A patent/CN101828037B/zh not_active Expired - Fee Related
  • 2008-09-19 JP JP2010529322A patent/JP5186005B2/ja active Active

Non-Patent Citations (1)

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