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
  • F04C2/102—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 the two members rotating simultaneously around their respective axes
• • 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
  • B60T8/36—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 including a pilot valve responding to an electromagnetic force
  • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
  • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
  • B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master cylinders
• • 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
• • 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
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
• • 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

• Motor-pump unit especially for slip-controlled braking systems
• the invention relates to a motor-pump unit, in particular for slip-controlled motor vehicle brake systems, with the features of the preamble of claim 1.
• a piston pump of the eccentric type requires at least two bores arranged at an angle to one another for receiving a drive shaft and at least one pump piston. At least one pressure valve and one sucking valve are necessary for the charge change.
• This type of pump is associated with the general and constructive disadvantage that unavoidable and audible pressure pulsations occur in the pumping operation. Because the pump is only rarely switched on by conventional, slip-controlled brake systems during average driving, for example when a brake slip limit or a drive slip limit is exceeded, the running noise is generally tolerated.
• EMS electro-hydraulic brake systems
• An increase in the pump running time can also be connected if the pump - without using a pressure accumulator - is used to directly increase the pressure in wheel brakes.
• Measures to improve noise behavior are known - for example, pumps with three or are known more pistons - which cause lower pulsations overall. Nevertheless, the comfort behavior is seen as in need of improvement.
• DE 199 18 390 AI discloses a vehicle brake device with a two-circuit internal gear pump.
• the internal gear pump can be used as a unit in a receiving body.
• the internal gear pump has, in addition to pinion / ring gear arrangements, a plurality of axially abutting as well as disk-shaped housing parts with a matching diameter, which are aligned with one another and welded together at the circumference before the pump is inserted into an essentially cylindrical bore in the receiving body.
• the high-precision alignment and fixation of the housing parts is complex.
• DE 100 04 518 AI shows an internal gear pump designed as a cartridge with an essentially cup-shaped first housing part, which receives a pinion shaft, a ring gear and a second housing part.
• the second housing part is arranged centered in the first housing part, which in turn is inserted and fastened in a bore of the receiving body provided with diameter steps. This arrangement allows the cartridge to be checked separately. Nevertheless, the construction effort is considered too high.
• the object is achieved according to the invention in that the housing parts can be provisionally arranged to one another by means of at least one securing element in such a way that the final alignment of the housing parts to one another takes place when the unit is inserted into the receiving body.
• the alignment of the pump components combined as a unit takes place, as it were, automatically when they are inserted into the receiving body.
• the work steps regarding alignment or adjustment are omitted.
• the at least one securing element connects the housing parts to one another with relative play, a bore being provided in the receiving body for the final alignment of the housing parts in the radial direction. This ensures that the internal gear pump can be integrated into the receiving body while avoiding double fits, tolerance chains or the like.
• a first one of the housing parts is fixed immovably in the axial direction and in the radial direction on the receiving body, and moreover serves to lock the pump components in the receiving body. Consequently, the first housing part additionally fulfills a locking function for at least one other pump component, which limits the construction effort.
• a pin with a first end can be provided as a securing element, which pin is pressed into a bore in the first housing part, the pin having a second end with a stop for securing the second housing part. The reverse arrangement is also possible.
• the pin is arranged parallel to a pump shaft.
• the pin has a cylindrical section which passes through a bore in the stop-side housing part, and the bore in this housing part has a larger diameter in comparison with the cylindrical section, and the diameter is smaller in comparison with the stop , This enables the unit to be pre-assembled in a form-fitting manner without causing tension when it is inserted into the receiving body.
• Up to three pins are provided for secure and statically determined pre-assembly, the pins being regularly distributed around the circumference, that is to say arranged at a regular angle to one another.
• the ring gear is mounted in a ring, the ring being arranged in the axial direction between the housing parts, and the ring being pivotable relative to the housing parts about a pivot axis which is parallel to the Pump shaft is arranged.
• a housing part receives one end of a spring element, where at another free end of the spring element engages in a bore of the ring under elastic deformation, in particular under bending.
• the Fe ⁇ derelement causes a resilient bias between the ring gear and pinion.
• Figure 1 is a sectional view of an internal gear pump on a larger scale and obliquely from above.
• FIG. 2 shows the internal gear pump according to FIG. 1 in an oblique section from below
• Fig. 3 shows a motor-pump unit in section
• Fig. 4 details of an internal gear pump as in Fig. 3 on a larger scale.
• the invention relates to a motor-pump unit 1, as shown in Fig. 3, which comprises an electric motor 2, which on a receiving body 3 for hydraulically active components, such as in particular electromagnetically actuated Valves, storage chambers and channels connecting these components to one another is fastened.
• the motor 2 has a pot-shaped motor housing which is covered at the end by a bearing plate 4, which is preferably made of plastic material, and which serves to temporarily accommodate a bearing 5.
• This recording is not used to derive bearing forces during the operation of the motor-pump unit 1, but only a subassembly-like assembly, so that the motor 2 can be tested as a separate unit together with a provisionally mounted drive shaft 6.
• the drive shaft 6 With the bearing 5, the drive shaft 6 is supported in a bore 7 on the receiving body side for receiving a pump 8.
• the pump 8 is designed as an internal gear pump and has an inlet channel 9 for connecting a pressure medium reservoir such as, in particular, a brake fluid reservoir, a master cylinder or a simulator with a separable displacement space 10, and one - from the displacement space 10 in the direction of at least one pressure medium consumer, such as for example a pressure medium accumulator and / or wheel brakes - leading drain channel 11.
• a pinion 13 is arranged on a pump shaft 12 in a rotationally fixed manner. The connection is made by pressing or shrinking.
• the pump shaft 12 is coupled to the drive shaft 6 in the area of freely projecting pins 14, 15 by means of a separate shaft coupling - however, it is possible to connect the two shaft ends directly, that is to say without a separate shaft coupling, to one another.
• the pinion 13 meshes with a ring gear 16, which is encompassed by a ring 17 (compensation ring) for storage.
• the pinion 13 has a smaller number of teeth than the ring gear 16. For example, a difference of one tooth is provided.
• the ring gear 16 is arranged eccentrically in relation to the pinion 13.
• tooth-side interstices on the outlet side are filled with the medium to be pumped, in particular with brake fluid.
• a sealing effect between adjacent tooth flanks there is a sealing effect between adjacent tooth heads, so that a suction area is separated from a pressure area, and displacement takes place in such a way that the medium for increasing the pressure is printed out on the outlet side.
• a bearing 18 - preferably a slide bearing or alternatively a roller bearing, in particular a needle ring as illustrated in FIGS. 1 and 2 - serves to support the ring gear 16 in the ring 17.
• the ring 17 is mounted within certain limits so as to be pivotable about a pivot axis A in the form of a pin 46, so that during pump operation a section of the ring 17 lying in an engagement-free ring gear area lies on the ring gear through the displacement space (pressure chamber) 16 acting pressure forces (force resultant) moved essentially radially to a pinion axis 19 hm, so that toothed heads on the low pressure side seal against one another as a result of mutual contact.
• the pin 46 is arranged in bores 47, 48 of the housing parts 20, 21.
• At least one separate pin 38 serves as the securing element, which is pressed with a first end 39 into a bore 40 in the housing part 21 and has a stop 42 at a second end 41 for securing the housing part 20.
• pin 38 extends parallel to of the pump shaft 12.
• the pin 38 also has a cylindrical section 43 which extends through a bore 44 in the stop-side housing part 20.
• the bore 44 has a diameter which is larger in comparison with the section 43, but is smaller in comparison with the stop 42, so that a positive locking takes place.
• the pump shaft 12 passes through aligned bores in the housing parts 20, 21, which are lined with slide bearing elements 22, 23.
• the slide bearing elements 22, 23 are preferably pressed into the bores, the first slide bearing element 22 being provided within the first housing part 20, while the second slide bearing element 23 is arranged within the bore of the second housing part 21.
• the bearing forces of the slide bearing element 22 are introduced into the receiving body 3 in all embodiments via the housing part 20.
• the housing part 20 according to FIGS. 3 and 4 is essentially pot-shaped and has an essentially flat bottom 24 with a through hole 25 into which the slide bearing element 22 is inserted, which has one end of the pump shaft 12 directly next to the pinion 13 supports.
• the housing part 20 lies against a step 28 with a tubular connecting piece 49, which surrounds the pump components on the outside.
• the Bore 7 is multi-stage and has a first stage 27 which merges into a second diameter section with the second stage 28.
• the housing part 21 is also supported in a liquid-tight manner by means of a sealing element 29.
• a third diameter section with a third step 30 receives the slide bearing element 23 so that the bearing forces are introduced into the blind hole-like end of the bore 7.
• the housing part 21 is not involved in the introduction of force into the receiving body.
• This design enables the bore 7 of the receiving body 3 to be designed with comparatively coarse tolerances, while the fine tolerances are concentrated on the pump components.
• Another special feature of the embodiment according to FIG. 4 is that the pin 46 is designed like a pin 38 according to FIG. 1, so that two functions (securing function, compensation function) are fulfilled by a single component (pin 38).
• the embodiment according to FIGS. 1 and 2 differs as follows from the embodiment described above according to FIGS. 3 and 4.
• the housing parts 20, 21 have a disk shape and are each supported with an outer circumference on an inner wall of the bore 7 in order to introduce the bearing forces.
• the bore 7 is made in one operation with a single tool with great accuracy.
• pivot axis A also serves to position the second housing part 21 in the circumferential direction relative to the first housing part 20.
• a component namely the axis A (pin 38, 46)
• the housing parts 20, 21 prevents the housing parts 20, 21 from rotating relative to one another.
• the compensation effect is even achieved with the pin 46 without having to provide a bore on the receiving body side for receiving the axis A.
• the relevant components are already positioned relative to one another as a pre-assembled unit.
• the first housing part 20 is fixed with respect to the receiving body 3, preferably by axial contact with a step (27 in FIGS. 1 and 2; 28 in FIGS. 3 and 4).
• the housing part 21 is only received in the stepped bore 7 and is placed in the sliding seat (transition fit) on the step 28. An independent attachment does not take place.
• FIGS. 1 and 2 show an elastically prestressed, needle-shaped spring element 32, which is inserted with a first end 33 into a bore 34 of the first housing part 20 advantageously in the press fit, and with a second end 35 with elastic deformation (bending) engages in a bore 36 of the ring 17 to keep it in a defined rest position.
• the embodiment according to FIGS. 1 and 2 can be equipped with such a spring element, even if this is not shown.
• a sealing element 37 is provided in an intermediate space 45 between the housing part 20 and the pump shaft 12, which is pressed into an inner wall of the collar 26 and bears against the pump shaft 12 with one or more sealing lips.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Physics & Mathematics (AREA)
• General Engineering & Computer Science (AREA)
• Fluid Mechanics (AREA)
• Electromagnetism (AREA)
• Transportation (AREA)
• Details And Applications Of Rotary Liquid Pumps (AREA)
• Rotary Pumps (AREA)
• Valves And Accessory Devices For Braking Systems (AREA)

Applications Claiming Priority (5)

Publications (1)

Family

ID=29737602

Family Applications (1)

Country Status (3)

Families Citing this family (4)

Family Cites Families (4)

• 2003
  • 2003-05-23 WO PCT/EP2003/005403 patent/WO2003106237A1/de not_active Application Discontinuation
  • 2003-05-23 JP JP2004513091A patent/JP2005529279A/ja active Pending
  • 2003-05-23 EP EP03759896A patent/EP1515883A1/de not_active Withdrawn

Non-Patent Citations (1)

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