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
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
  • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
  • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
  • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
  • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
  • B60T8/4031—Pump units characterised by their construction or mounting
• • 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
  • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
  • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
• • 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
  • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
• • 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
  • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
  • F04C2/086—Carter

Definitions

• the invention is based on a pump assembly for the synchronous pressurization of two fluid circuits according to the preamble of independent claim 1.
• Such a pump assembly is z. B. from DE 10053991 Al as so-called
• Pump insert for a hydraulic, wheel slip-controlled vehicle brake system known, being supplied by the two internal gear pumps of the pump insert different brake circuits of the brake system with diagonal brake circuit distribution.
• the two internal gear pumps are separated from each other by a separately formed partition wall of the multi-part housing and are traversed transversely by a common drive shaft.
• the pinion of the two gear pumps are pushed and rotatably connected via a driver connection with her.
• two shaft seals are inserted into matched annular spaces of the partition bore at a distance from each other.
• each internal gear pump are further associated with a suction channel and a pressure channel, which are seen in the axial direction at opposite end portions of the pump assembly, extending substantially radially and bending their end portion in the suction or pressure side of the associated pump room open. Due to their lateral arrangement, the pairs of channels belonging to the internal gear pumps have, in addition to the front ends of the pump assembly, an NEN considerable distance from each other, which must also be considered in the design and dimensioning of the pump housing.
• the pump assembly according to the invention with the features of independent claim 1 has the advantage that the axial distance of the pairs with suction and pressure channel of the internal gear pumps can be significantly reduced from each other. This allows a more compact design of the pump assembly can be realized and possibly accompanied by a simplified design of the line system for the two FIu- id Vietnamesee.
• the suction channel and the pressure channel can also be arranged in a technically simpler manner positionally accurate in the partition, since the partition serves as an axial thrust washer for the wheelsets of the pump. So the partition is accessible from all sides before installation in the pump housing, which z. B. a spa- nende processing for generating or editing the hollow channels significantly easier.
• the enclosing housing parts no longer at a distance of their faces from each other at the periphery of the partition by means of rolled-up areas or the like. Be joined, but the dividing plane can extend next to the partition wall and the annular end faces of the housing parts to be joined together can be added to shock.
• the connection intensity of the hollow cylindrical housing parts can be substantially improved so that the pump assembly does not require the insertion into a pump housing that stabilizes it.
• the suction channels and the pressure channels of both internal gear pumps are integrated into the partition.
• the pressure channels and the suction channels of both internal gear pump are very close to each other, which is a correspondingly compact
• the dividing wall can have a relatively small thickness if the four fluid channels are arranged substantially in the same cross-sectional area of the dividing wall.
• the fluid channels in the dividing wall can be arranged offset from each other by 90 degrees by arranging the internal gear pumps of the pump assembly rotated 180 degrees counter to one another. This has the positive side effect that largely cancel out the acting in the opposite direction compressive forces in the internal gear pumps.
• valve arrangement is provided in the line system of one of the fluid circuits to be supplied, this arrangement can be arranged directly in the associated fluid channel
• This valve arrangement may comprise one or two valves in one or both fluid circuits to be charged.
• a technically particularly useful equipment of the fluid circuits or fluid circuits, each with two valves is present when a pressure relief valve in the suction channel or the suction channels of the partition and a pressure relief valve in the pressure channel of the partition wall are arranged.
• a pressure relief valve in the suction channel or the suction channels of the partition and a pressure relief valve in the pressure channel of the partition wall are arranged.
• an already existing space is used within the partition, so that it can be dispensed with an external arrangement of the valves in the system of the associated fluid circuit. This results in a corresponding space savings outside the pump assembly and possibly a simplification of the connected line system.
• the partition consists in a preferred embodiment of a cylindrical disc with plane-parallel end faces which are perpendicular to the central longitudinal axis of the disc and parallel to each other, and is pressed into a cylindrical hollow cross-section of the associated housing part. If the flat faces are ground, which is possible due to the disc shape cost-effective with high surface quality, they can serve directly as contact surfaces for the gear sets.
• a press fit By pressing the disc in a cylindrical hollow section, z. B. with a press fit, can ensure a position-securing mounting position of the disc in the housing without additional fasteners.
• the press-in process must be carried out so that the radial ends the fluid channels of the disc are aligned after the pressing process to corresponding fluid channels in the housing. By choosing a suitable interference fit, if necessary, a liquid-tight connection between the outer circumference of the disk and the inner circumference of the housing can be created without additional sealing means.
• the pressed-in dividing wall can advantageously be supported axially between opposite annular end faces of two housing parts, the outer diameter of one of the housing parts largely corresponding to the outer diameter of the dividing wall.
• the adapted in the diameter of the partition tubular end portion can then, similar to the dividing wall, be pressed or inserted into the larger tubular end portion of the other housing part, after which there is a telescopic length overlap of the pipe ends.
• a pressure piece from a usual for plungers plastic material may be arranged on the one hand and on the front sides of the associated wheelset on the other hand, axially supported on the opposite bore wall of the pump chamber.
• the plungers are each structurally associated with an associated bearing sleeve for the drive shaft, resulting in a desirable reduction in the number of parts in the pump assembly.
• the bearing sleeve itself can be formed integrally with the pressure piece and even form a plain bearing. Alternatively, however, the bearing sleeve can accommodate or enclose a roller bearing or bearing shells of a sliding bearing.
• Fig. 1 shows a schematic central longitudinal section through a pump assembly according to the invention.
• Fig. 2 shows a pump chamber of the pump assembly of Fig. 1 in side view.
• 3 shows a vertical section through a partition wall of the pump assembly according to the section line III-III in FIG. 1.
• a pump assembly 10 comprises two internal gear pumps 11 and 11 ', which lie laterally next to one another and are arranged in a common pump housing 12.
• the pump assembly 10 is part of a not shown pressure control device for a vehicle brake system with diagonally split brake circuits, the internal gear pumps 11 and 11 'are each responsible for the pressure supply of the brake circuits in the course of known as such brake interventions for ABS or ESP applications.
• the common pump housing 12 is composed on the outside of two pot-like hollow housing parts 13 and 14, which each define a pump space of the internal gear pump 11 or 11 'on three sides and are joined under length coverage of their end regions.
• a partition wall 15 is inserted as an inner housing part, which limits the pump chambers of the two internal gear pumps 11 and 11 'with its end faces on the fourth side.
• the partition wall 15 consists of a cylindrical disc with plane-parallel end faces, which is pressed into a cylindrical hollow cross-section of the associated housing part 13.
• Housing 12 is inserted and passes through coaxial bearing bores, which are recessed from the end faces of the housing parts 13 and 14 and from the partition wall 15.
• the drive shaft 16 is rotatably mounted to slide directly in the bore of the partition wall 15, while the drive shaft 16 is rotatably mounted rotatably on the lateral bearings via a bearing sleeve 17 and a bearing sleeve 17 'made of plastic.
• the bearing sleeves 17 and 17 ' are each formed as a hollow cylinder and lie positively between the circumference of the drive shaft 16 and the associated bore wall of the housing part 13 and 14 respectively.
• the drive shaft 16 passes through the bearing sleeve 17 or 17 'in each case a pressure piece 18 or 18', which is formed integrally with the associated bearing sleeve 17 or 17 ', then a central insertion opening in the associated pinion 19 and 19 'of the internal gear pumps 11 and 11' and finally an associated shaft seal 20 or 20 ', in an associated, stepped extension of
• Bearing bore for the drive shaft 16 is pressed in the partition wall 15.
• the drive shaft 16 z. B. by means of an electric gear motor rotated in the clockwise direction, the pinion 19 rotates synchronously with and also the ring gear 21 is rotated due to the meshing engagement with the pinion 19 in the same direction. Since the tooth gaps covered by the filling piece 22 are sealed on one end face by the pressure piece 18 acted upon by a corresponding axial force and by running on the dividing wall 15 on the opposite end face, the hollow volumes of brake fluid received by the tooth spaces can be filled sufficiently. Seal the tooth tips relative to the filler 22 are transported under appropriate pressure increase from the suction channel 24 to the pressure channel 25 of the internal gear pump 11. The sealing between the tooth tips and filling piece 22 required for this purpose comes about solely on the basis of a defined circumferential clearance of the filling piece 22, through which a pressure distribution over the circumferential extension of the filling ring 22 during operation is achieved
• the internal gear pump 11 ' is driven by the drive shaft 16, as well as the pinion 19' penetrated by the drive shaft 16 and rotatably connected thereto via one of the pinion 19 corresponding driver connection.
• the geometry of the internal gear pump 11 'as such is largely consistent with that of internal gear pump 11, wherein the wheel set of pinion 19' and ring gear 21 'are arranged rotated by 180 degrees relative to the wheel set of pinion 19 and ring gear 21. Because of this by 180 degrees against each other rotated Radsatzan whatsoever in the internal gear pumps 11 and 11 ', ie an oppositely eccentric arrangement, the resultant of the pressure forces on the pressure side of the internal gear pump 11 and 11' act in opposite radial directions, as shown in FIG Arrows is indicated. Thus, these resulting radial forces largely cancel, which allows a more favorable dimensioning of the pump housing 12, as in the dimensioning of the same essentially only the forces acting through the axial displacement of the resultant moments must be considered constructive.
• the suction channel 24 opening into the pump chamber of the internal gear pump 11 and the associated pressure channel 25 lie essentially in the same cross-sectional plane as the opening into the pump chamber of the internal gear pump 11 ' Suction channel 24 'and the associated pressure channel 25'.
• they are arranged radially so far in the direction of the outer circumference that they can stand without detriment to the function under axial cover to the pressed-in shaft sealing rings 20 and 20 '.
• the partition 15 must have a total of only a slightly greater thickness than is required to integrate the axial and radial channel portion of the suction channel 24 and 24 'anyway.
• a leakage channel 26 is additionally arranged for removing brake fluid which has penetrated into the bearing bore of the dividing wall 15, which extends from the bearing bore of the dividing wall 15 between the shaft sealing rings 20 and 20 ', extends diagonally through the dividing wall 15 and into which two suction channels 24 and 24 'opens. Furthermore, it can be seen that in the suction channels 24 and 24 'are each a pressure reducing valve 27 and 27' and in the pressure channels 25 and 25 'are each a pressure relief valve 28 and 28' is arranged, wherein the arrangement is made so that all Valves 27, 27 ', 28 and 28' received within the partition wall 15 are located within partition wall cavities in each switching state.
• the pressure relief valves 28 and 28 ' are identical, oppositely arranged pressure relief valves of conventional design, in which a ball is in the flow path of the pressure channel and is pressed by the force of a return spring to its sealing seat. As soon as the fluid pressure at the sealing seat is greater than the spring force, the ball is displaced and the flow path of the pressure channel is thus released.
• the pressure channels 25 and 25 ' which are integrated with their radial length portion diametrically opposite each other near the periphery in the partition wall 15 are thus moved at a corresponding pressure against the spring load radially outward and thereby with the associated
• the pressure reducing valves 27 and 27 ' are formed as linear slide valves, which transversely through the radial flow path of the suction channel 24 and 24' with a tapered control section and are also used in the opposite direction.
• the sliding directions of the pressure reducing valves 27 and 27 ' run parallel to one another and to the radial length sections of the pressure channels 25 and 25'.
• the slides of the pressure reducing valves 27 and 27 ' are each held by the spring force of an associated helical compression spring in an axial starting position, which, however, the passage position of the pressure reducing valve 27 and 27' corresponds.
• the helical compression spring is in each case supported on the annular end face of a piston section adjoining the control section, which is slidably guided under sealing in its bore of the partition wall 15, and the control section engages with an end region having a central bore in an associated blind hole bore of the partition wall 15 one.
• the components of the pressure reducing valves 27 and 27' are coordinated so that a pressure limit of about 10 bar on the suction side of the internal gear pumps 11 and 11 'can not be exceeded.
• unnecessary frictional forces in the internal gear pumps 11 and 11 'can be avoided, which would be detrimental both in terms of the efficiency of the pump assembly 10 and in terms of their wear. If fluid from the suction channel 24 or 24 'at the sealing plane of the pressure reducing valve 27 or 27' over into the guide bore, so it can flow together with fluid from the leakage channel 26, since the guide bore to the periphery of the partition wall 15 is open and thus additionally serves as a drain opening.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Transportation (AREA)
• Rotary Pumps (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)

Applications Claiming Priority (2)

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• 2007
  • 2007-11-16 DE DE102007054808A patent/DE102007054808A1/de not_active Withdrawn
• 2008
  • 2008-09-26 US US12/743,291 patent/US20100322810A1/en not_active Abandoned
  • 2008-09-26 CN CN2008801159889A patent/CN101855452B/zh not_active Expired - Fee Related
  • 2008-09-26 EP EP08804797A patent/EP2220373A1/de not_active Withdrawn
  • 2008-09-26 WO PCT/EP2008/062919 patent/WO2009062783A1/de active Application Filing
  • 2008-09-26 JP JP2010533521A patent/JP5323080B2/ja not_active Expired - Fee Related

Non-Patent Citations (1)

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