WO2021005151A1 - Dispositif d'alimentation en pression comprenant une pompe à engrenages - Google Patents

Dispositif d'alimentation en pression comprenant une pompe à engrenages Download PDF

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Publication number
WO2021005151A1
WO2021005151A1 PCT/EP2020/069357 EP2020069357W WO2021005151A1 WO 2021005151 A1 WO2021005151 A1 WO 2021005151A1 EP 2020069357 W EP2020069357 W EP 2020069357W WO 2021005151 A1 WO2021005151 A1 WO 2021005151A1
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WO
WIPO (PCT)
Prior art keywords
supply device
pressure supply
gear
housing
pump
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.)
Ceased
Application number
PCT/EP2020/069357
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German (de)
English (en)
Inventor
Heinz Leiber
Norbert Alaze
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ipgate AG
Original Assignee
Ipgate AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ipgate AG filed Critical Ipgate AG
Priority to DE112020003258.2T priority Critical patent/DE112020003258A5/de
Publication of WO2021005151A1 publication Critical patent/WO2021005151A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps
    • 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
    • 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
    • F04C15/008—Prime movers
    • 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
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil
    • 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
    • F04C2240/00—Components
    • F04C2240/40—Electric motor

Definitions

  • Gear pumps or gerotor pumps are widely used for medium to high flow rates. In the pressure range, the gear pump is limited due to the large number of gap seals; in some cases, multi-stage pumps are used in which the pressure load per pump is lower. Gear pumps are mostly used for applications with a pressure of up to 300 bar.
  • Gear pumps are mostly driven by electric motors. It is widespread here to provide a series connection, i. H. To design the electric motor and pump separately, using a common drive shaft, as disclosed in DE 102017106927 A with a coupling. This requires a lot of installation space, which is particularly disadvantageous when used in a unit with limited space, such as an integrated brake system or a transmission control.
  • a small motor-pump unit is known in which the pump is essentially arranged within the rotor or the rotor. In this arrangement, however, the size of the pump is limited to the rotor size and the motor mounting and the arrangement of the motor angle sensor is complex.
  • a fuel pump for low pressure levels less than 10 bar is known, with mounting of the pump in a kind of flange, but without a connection to a hydraulic block with control valves. In addition, the suction and pressure connections are not located together in the bearing flange. The medium to be pumped flows around the motor, which prevents the pump from being used as a high-pressure pump.
  • the pressure range and also the degree of efficiency depend on the number of sealing surfaces to be sealed, which are dependent, among other things, on the play between the teeth of the intermeshing gears and the play or distance between the inner wall of the housing and the tooth tips that guide along it. It also depends on the tightness between tween the gears and the axially adjacent housing walls. The larger the axial gap between the housing and the gear, the lower the performance and the maximum possible pressure that can be achieved.
  • the object of the present invention is to provide a pressure supply device with a gear pump and an integrated electric motor with small dimensions and high efficiency.
  • the object of the invention is advantageously achieved with a pressure supply device according to claim 1.
  • Advantageous further training of Pressure supply device according to claim 1 result from the features of the subclaims.
  • the pressure supply device is characterized in that it has a motor housing with an electric motor drive arranged in it, which drives a gear pump.
  • the drive has a stator and a rotor for this.
  • An internal gear wheel of the gear pump is moved via the rotor of the drive.
  • the drive is designed according to the invention by means of at least one seal, which is arranged between the rotor and the inner gear wheel, as a dry runner or has a dry running rotor, ie the rotor of the drive is not surrounded by the medium conveyed by the gear pump and / or is not surrounded by the medium. Due to the design as a dry runner, the rotor turns oh ne greater frictional and flow resistances, whereby higher speeds and a better efficiency can be achieved.
  • a particularly compact and simple pressure supply device is obtained when the motor housing has a side wall on which the gear pump is arranged, in particular this has a recess in which the gear pump is at least partially or completely inserted.
  • the Sowan extension of the motor housing can be penetrated by a rotatably connected ver with the rotor shaft, wherein the gear is either rotatably connected to the shaft or is coupled to the shaft via an interposed gear and / or a coupling.
  • the drive with its housing rests against a hydraulic housing with at least one valve and / or hydraulic lines or channels arranged therein or forms a unit with it.
  • the side wall of the drive housing can abut or abut the side wall of the hydraulic housing, in particular be attached to it, the particularly cup-shaped recess accommodating the gear pump at least partially or completely and being open to the hydraulic housing.
  • the gear pump can either be completely in the recess of the wall of the Drive housing, completely in a recess of the hydraulic housing or both in a recess in the side wall of the drive housing and in a recess in the side wall of the hydraulic housing. In the latter case, the openings of the two recesses then face one another. Additional seals can be provided in order to seal the two housings to one another and to the outside.
  • the above-described recess in the side wall of the drive housing is advantageous to the outside, and if there is a hydraulic housing, open to this.
  • the recess can itself advantageously be designed to be pot-shaped. It can also have a cylindrical section with a circular cross-section in which the gear pump rests with its Zahnrä countries.
  • the side wall of the drive housing can also advantageously be designed as a flange with which the drive can be attached to another part or unit.
  • the gear pump used in the pressure supply device according to the invention can be an internal gear pump with a sickle, an external gear pump or a toothed ring pump.
  • the gear pump can also advantageously be arranged axially next to the stator and / or the rotor of the drive, its structure and size is not disadvantageously limited by the gear pump. The size and structure of the gear pump is then not dependent on the dimensions of the stator and the rotor.
  • the drive housing can be designed in at least two parts, the side wall being part of a first housing part or forming this.
  • the second housing part can, for example, be cup-shaped and accommodate the stator and the rotor of the drive.
  • the rotor is connected to the gearwheel by means of a drive shaft directly or via a transmission and / or a clutch.
  • the gear can either be by means of a non-positive connection or be non-rotatably connected to the drive shaft by means of a form fit, which is formed in particular by means of a pin or serration.
  • the inner gear is arranged eccentrically on a part connected to the drive shaft, in particular in the form of a disk or a cam disk.
  • an external internal ring gear is also necessary for the internal gear.
  • the internal gear is rotated in the internal gear pump by means of the driven by the drive shaft inner gear about its axis of rotation, the inner gear being arranged eccentrically to the internal gear.
  • the inner ring gear rotates in an outer ring or cylinder surrounding it.
  • a sickle must be provided, which must be arranged in the space between the inner ring gear and the inner gear wheel resulting from the eccentricity.
  • the internal gear ring of the gerotor pump In contrast to the internal gear pump, the internal gear ring of the gerotor pump is fixed, the inner gear rolling due to its eccentric mounting on the disc rotated by the drive shaft in the internal gear rim. A sickle as with the internal gear pump is not required.
  • the drive shaft can either be a) in the motor housing on the one hand and in the gear pump and / or in the hydraulic housing on the other hand or b) only in the gear pump or c) in the hydraulic housing and in the motor housing or d) in the gear pump and in the hydraulic housing or supported by means of suitable Bearings, especially radial bearings, in the form of ball or roller bearings and / or axial bearings.
  • the drive shaft can extend up to extend into the hydraulic housing, in particular up to its side opposite the drive.
  • a target for a sensor can be arranged on the drive shaft, the sensor being arranged in the control and regulating unit (ECU). Additional seals can prevent the conveyed medium from entering the control and regulation unit.
  • the drive shaft extends right through the hydraulic housing and ends in the housing adjoining it, for example a control and regulating unit.
  • the gear pump as an internal gear pump can be designed differently.
  • the inner gear, the inner ring gear, the sickle and the outer ring can be arranged between two disks, with the disks being firmly connected to the outer ring after appropriate centering and adjustment of the parts to one another. Since the material connection can stretch all around the circumference, so that a stable and compact embodiment results in which the individual moving parts only have small games and gaps zueinan of, whereby a good efficiency is achieved and a high one Pressure is achievable.
  • the one lateral disk and the outer ring are grouped together to form a cup-shaped part, so that only a material connection between the cup-shaped part and the one disk needs to be established.
  • the moving parts can be arranged between two disks, which are firmly connected to an outer ring or the inner ring gear. It is also possible to design the outer ring or the inner ring gear with a disk as a component, which in turn is firmly connected to the remaining disk after the remaining parts have been inserted into the cup-shaped part.
  • a bearing in particular a ball or roller bearing, can advantageously be placed between the radial outer wall of the internal gear rim and the one encompassing the internal gear rim outer ring or the cylindrical inner wall of the cup-shaped part can be provided in order to keep the friction as small as possible.
  • the previously described embodiments of the internal gear pumps and gerotor pumps can advantageously be set in a recess in a wall. So that the gear pump rotates in the recess, either a form fit by means of a non-circular shape of the recess and the corresponding contour of the gear pump can be provided or an anti-twist device, e.g. in the form of a bolt, etc. can be provided.
  • the hydraulic connections for the gear pump can advantageously be provided directly in the wall or recess and / or the at least one disk or the cup-shaped part. This results in a compact design of the pressure supply device according to the invention.
  • Seals can be provided to seal the connections to the channels. This can, for example, lie in the mouth opening of the channel, a groove in a wall running around the channel opening, etc.
  • the internal gear can be arranged tiltably on the shaft. This can be done via a narrow contact surface of the internal gear on the shaft or an elastic connection between the shaft and the internal gear. This allows tolerances to be well balanced, which leads to a smoother running of the gear pump and which advantageously increases the efficiency.
  • the electrical connection lines of the electric drive can advantageously be passed through the hydraulic housing through to the housing of the control unit, in particular in at least one channel.
  • the gear pump can also advantageously be arranged wholly or partly next to the rotor and / or the stator in the axial direction, whereby the stator and / or rotor and also the gear pump can be formed independently of one another.
  • the pressure supply device according to the invention can advantageously serve as a pressure source for a brake system and / or a transmission.
  • the integration of the gear pump into the side wall of the drive housing or the bearing flange of the drive creates a compact structural unit in which a larger structural volume is available for both a single-stage and a two-stage pump.
  • the mounting can be simplified in that the rotor of the electric motor is mounted only with one bearing arranged in the drive housing and with a second bearing arranged in the gear pump. As described above, however, it is also possible to provide the entire bearing of the rotor in the gear pump.
  • the arrangement can be used for both a brushless motor and a motor with brushes.
  • the pressure supply device can advantageously be used in all systems in which a hydraulic pressure is provided with a pressure supply source and this also has to be regulated, such as in integrated brake systems, transmission controls, robotics, special machines, etc.
  • only one electric motor is provided in the drive housing, only one hydraulic circuit can be supplied with the pressure supply devices described above.
  • several electric motors are arranged in the drive housing, which drive several gear pumps, the gear pumps being designed as described above, such a pressure supply device being suitable for supplying several hydraulic circuits.
  • several single-circuit pressure supply devices according to the invention can be combined can be combined in a module, the module then also being used to supply several hydraulic circuits or units.
  • the gear pumps can be designed both as single-stage and as multi-stage gear pumps, so-called pumps.
  • This adjustment mechanism may be necessary because when assembling the one-piece and the two-piece sickle variant, special measures are taken into account, as neither the sickle nor the gear wheel may have an insertion bevel, as this bevel creates a bypass to the suction side of the pump would. This means that the sickle would have to be positioned very precisely over the narrow gap, which makes automatic assembly of the pump very difficult.
  • the sickle can first be introduced into an area where there is still a relatively large clearance between Sickle and inner gear and outer internal gear consists, after which it can then be pushed into the tapered gap by means of the adjustment mechanism, whereby a sufficiently small game between sickle's rule and gears is adjustable.
  • the adjusting mechanism for example in the form of the eccentric described above, can be set after the necessary play has been set, which can be done, for example, by means of a locking screw, gluing or welding.
  • the pump can then be further assembled.
  • Fig. 1 a first possible embodiment of a gear pump of a pressure supply device according to the invention, wherein the gear pump is designed as a 1-stage gear pump, and the drive shaft is inter alia via the inner gear of the gear pump Gela Gert;
  • FIG. La a section through the internal gear pump according to FIG. 1;
  • FIG. 1b a section through the area of the gear pump according to FIG. 1, in which the fixed outer parts of the gear pump are welded together;
  • Fig. Lc a slightly modified embodiment of the gear pump ge compared to the embodiment shown in Figure la with Schllitz ter sickle and its mounting via a bolt;
  • Fig. Id Cross-sectional view through a gear pump with internal
  • FIG. 1e enlarged detail from FIG. 1d;
  • Fig. 2 an embodiment of the gear pump with a ball bearing between the inner ring gear and the outer ring, the drive shaft in the gear pump is also superimposed on the inner gear GE;
  • Fig. 3 an embodiment in which the drive shaft is mounted in the gear pump by means of roller bearings;
  • Fig. 4 a 2-stage gear pump with partial storage of the drive shaft to in the gear pump;
  • Fig. 5 a 2-stage gear pump, the drive shaft being supported completely, i.e. exclusively in the gear pump;
  • Fig. 6 an engine mounting both in the drive housing and in the
  • Gear pump wherein the first bearing is formed with magnetic Verspan voltage and the second bearing is arranged in the gear pump;
  • Fig. 8 a mounting device for a gear pump according to the invention pe.
  • FIGS 1 and la show a possible embodiment of an internal gear pump with drive shaft 1, internal gear 2, internal ring gear 3, guide part in the form of a sickle 5, the latter being connected via the bolt 6 to the outer disks 7.1 and 7.2 and thus fixed.
  • the aforementioned parts are embedded in the two outer disks 7.1 and 7.2 together with the outer ring 4, the outer ring 4 being connected to the two outer disks 7.1 and 7.2 by welding LS, which is shown enlarged in FIG.
  • the two outer disks 7.1 and 7.2 together with the outer ring 4 form the pump housing ZG of the gear pump Z, which is mounted in the recess 18b of the wall 18.
  • the wall 18 forms a flange on or with which the drive housing can be fastened to the hydraulic housing.
  • Fig. Lb it is shown that the outer diameter of the areas 7.1a, 7.2a and 4a of the outer disks 7.1, 7.2 and the outer ring 4 provided for the welding LS is smaller than the largest outer diameter D A of the parts, so that the assembly in the recess 18b, which can be formed by means of a hole, is not hindered by the weld LS.
  • the Monta ge and adjustment of these parts is described in FIG.
  • the disks 7.1, 7.2 and the outer ring 4 can be manufactured very precisely by flat grinding, so that small gaps or clearances are possible.
  • the inner gear 2 is guided on the drive shaft 1 through the short collar 11. This has the advantage that small angular tolerances between gear 2 and shaft 1 do not lead to gear 2 jamming in the housing ZG.
  • the torque to gear 2 is transmitted via a driver 10. This torque is also transmitted by the locking bolt 9 to the wall application or the flange 18 transferred.
  • both suction and pressure connections act with seals, which are connected to the hydraulic housing HCU.
  • the outer disk 7.2 is provided with a seal 14 to the hydraulic housing HCU.
  • the shaft seals 13.1 and 13.2 also act.
  • the drive shaft 1 also has a shaft journal 8, which is required for mounting the pump housing ZG, see FIG. 8.
  • a roller bearing, needle or ball bearing 17a can be installed between the latter and the outer ring 4.
  • Fig. La shows the gear pump Z in section.
  • the sickle 5 is here centrally mounted on a pin 6, as is known from the prior art.
  • the connections for suction S and the pressure outlet with pressure P with direction of rotation are also shown in FIG. Of course, the currents will change direction as soon as the gear 2 rotates in the other direction, whereby the suction side S becomes the pressure output P and vice versa.
  • a gerotor pump can also be used, which does not have a sickle and a fixed internal gear rim.
  • the inner gear is mounted eccentrically on an eccentric being driven by the drive shaft and rolls in the stationary internal gear rim.
  • a trochoidal tooth system is preferred as the tooth system.
  • the leakage oil must be diverted to S via the leakage flow channel in order to relieve the seals.
  • Figures ld and le show a further possible embodiment of a gear pump with an inner gear 2 and an outer inner toothed ring 3 as well as a sickle 5, which lies in a gap 52 formed by the inner gear 2 and the outer inner toothed ring 3, the gap 52 in Tapered clockwise.
  • the sickle 5 has a first circular arc-shaped bearing surface 54, with which it rests on the radially outer end faces 2b of the teeth 2a of the inner gear 2.
  • the sickle 5 has a further second circular arc-shaped contact surface 55, with which it rests on the radially inwardly facing end faces 3b of the teeth 3a of the outer inner tooth ring 3.
  • the sickle has a particularly elongated recess 51 through which an eccentric bolt 5c extends, the cam of the eccentric 5c with the inner wall 50 of the elongated hole 51 together men acts or is applied to this area by area.
  • the eccentric 5c itself is, for example, in or on at least one or both outer disks 7.1, 7.2 rotatably Gela Gert and can be locked, fixed or attached to at least one outer disk 7.1, 7.2 by a locking mechanism, not shown in Figures ld and le, so that after setting the necessary Game the sickle 5 can no longer move relative to the inner gear 2 and the outer ring gear 3 during operation of the pump and the game is permanently maintained.
  • the radii of the circular arc-shaped contact surfaces 54 and 55 are matched to those of the tip circles of the inner gear 2 and the outer inner toothed ring 3, so that as many teeth as possible fit sufficiently sealingly 2a, 3a to the contact surfaces 54, 55.
  • At least one channel 5k which is designed, for example, as a radial bore 5kb or channel or groove 5kr, can be provided so that a pressure-equalizing exchange of the conveying medium between the contact surfaces 54 and 55 or the chambers Rpi or Rp 2 can take place.
  • FIG. 1e shows an enlarged detail from FIG. 1d in the area of sickle 5.
  • FIG. 2 shows the same construction of the gear pump Z according to FIG. 1, with the difference being a sliding bearing 16 on both sides of the drive shaft 1 in the two outer disks 7.1 and 7.2. This eliminates the need for a separate engine mount, as shown in Figures 6 and 6a.
  • the leakage oil channels 15 are modified here.
  • FIG. 3 also shows the similar structure of the pressure supply device according to FIGS. 1 and 2, with the difference in the use of roller bearings 17 to minimize bearing friction.
  • the outer disk 7.1 and the outer ring 4 are replaced by the part 7.1b, which is pot-shaped and accommodates the inner gear 2 and the inner ring gear 3.
  • only one weld LS is required, which connects the part 7.1b and the outer pane 7.2 materially.
  • Fig. 4 shows a 2-stage internal gear pump.
  • This pump uses the same elements, such as drive shaft 1, inner gear 2, inner ring gear 3, guide part (sickle) 5, fixings 6 and 6a., Driver 10, outer ring 4, all of which are provided twice.
  • the additional difference lies in the suction channel S and in the overall length and the central disk 19, which also contains a channel from the P output of the 1st stage to the suction channel of the 2nd stage.
  • Fig. 6 shows a representation of the entire structural unit consisting of motor 22, pump Z, HCU and ECU, which is able to exercise the pressure regulation and control for systems such as brakes, gears, etc.
  • the main focus here is on the combination of motor and pump.
  • the pump is arranged in the bearing flange 18, as shown in FIGS. 1 to 5, or is attached to the HCU or ECU in a separate pump housing 40, as shown in the upper half of the figure.
  • the simplest version according to Fig. 1 is shown, which requires an additional motor bearing 20 in which the shaft 1 is mounted.
  • the motor is composed of rotor 21, which is connected to shaft 1 via driver 10a.
  • the rotor 21 is axially preloaded by its force via a permanent magnet 30a in the housing 30.
  • This is a solution for the motor manufacturer who manufactures and tests the motor with housing 22 and stator and winding 23 and delivers it to the system supplier.
  • the motor is tested without a pump with an auxiliary shaft. Thereafter, when the shaft is removed, the rotor is centered by the axial magnetic force, so that the shaft 1 can then be assembled with the rotor during final assembly.
  • the permanent magnet 30a can, with its force acting axially on the rotor 21, if it is large enough, compensate for tilting forces of the rotor, so that no further mounting of the rotor 21 in addition to the bearing 20 is necessary. A sufficiently large clearance can or should be provided in the gear pump.
  • the drive housing must also be joined and fastened here with the flange 18 at 25a - shown in the lower half of the figure, e.g. B. with springs, which are attached in segments over three connections the.
  • a housing seal 31 is also necessary here. It can be fastened by caulking, at 25 from the engine flange with HCU or ECU, see upper half of the figure 28.
  • the pump version with pump housing is shown here.
  • the motor is shown here as a brushless motor that needs a Mo torsensor for commutation and control of the volume delivery of the pump.
  • This motor sensor is arranged at a distance from the drive housing 22, with a sensor shaft 26 which is net or attached to the drive shaft 1 and carries a sensor target 27. This target 27 acts on the sensor element 28, which is arranged on the circuit board of the ECU.
  • the winding is connected to the ECU via contact bars 24.
  • the motor with bearing flange 18 can be connected directly to the hydraulic housing HCU, which valves or other hydr. Includes components to be connected to the pump. If this is not the case, a connection of the drive housing 22, 18 directly to the housing of the ECU is possible.
  • gear pump Z in a pump housing 40 which is connected directly to the hydraulic housing HCU, as shown in FIG. 6 in the upper half of the drive shaft 1.
  • the gear pump Z is first integrated or mounted in the pump housing 40, the rotor 21 then being pressed onto the shaft 1 and then assembled with the bearing 20.
  • the tensile force of the magnet 30 can also act on the rotor 21 and the bearing 20, so that the bearing acts like a four-point bearing.
  • the motor housing 22 is thus connected to the gear pump Z and its pump housing 40 and, in the next step, can be connected to the hydraulic housing HCU or the electronics housing ECU.
  • the fastening screw 41 is used.
  • the shaft 1 is previously centered in the outer disks 7.1 and 7.2 so that the pump housing 40 is centered with the shaft 1 before the screw connection to the hydraulic housing HCU or the electronics housing ECU.
  • the pressure supply device uses a 2-stage pump with long sliding or roller bearings according to Fig. 2, 3 and 5, wel- does not require separate motor storage.
  • the motor structure with the housing is accordingly simplified.
  • the rotor 21 sits with driver 10a on the motor shaft and is axially connected to the locking ring.
  • the pump housing protrudes slightly into the HCU here.
  • Fig. 7 shows a 1-stage gear pump with a brush direct current motor, which is taken from DE 102013217257.
  • the gear pump according to the invention is now used. This can correspond to the embodiments according to FIGS. 1, 2 and 3. 1 is shown with drive shaft 1, inner gear 2, inner ring gear 3 and the welded disks 7.1, 7.2 with outer ring 4.
  • a motor bearing can also be dispensed with.
  • Fig. 7a shows the delivery condition from the engine manufacturer without gear pump, only with drive shaft 1.
  • the shaft 1 is mounted in the bearing flange 18.
  • FIG. 8 shows the assembly device for welding the disks 7.1 and 7.2 together with the outer ring 4.
  • a sleeve 37 is pushed over the drive shaft and axially fixed with the locking ring.
  • the disks 7.1, 7.2 and the outer ring are then centered via the centering sleeve 35.
  • the washers 7.1, 7.2 are axially clamped together with the outer ring with the nut 34 via the mounting disk 33.
  • LS can then preferably be laser welded.
  • the sleeve is clamped in a rotatable manner. As Fig. Lb shows, the diameter of the weld is smaller, so that the later assembly in the flange is not hindered.
  • Motor housing in particular as a bearing flange or side wall, is formed

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

Dispositif d'alimentation en pression comprenant un entraînement (21, 23) par moteur électrique disposé dans un boîtier d'entraînement (18, 22) et une pompe à engrenages (Z) entraînée par celui-ci, l'entraînement (21, 23) présentant un stator (23) et un rotor (21) et la pompe à engrenages (Z) présentant une roue dentée (2) couplée au rotor (21), une paroi (18, 40) étant disposée entre le rotor (21) et la roue dentée (2), et au moins un joint d'étanchéité (13.1) étant disposé entre le rotor (21) et la roue dentée (2), de façon que le rotor (21) est un rotor fonctionnant à sec, qui n'est pas entouré par le milieu refoulé par la roue dentée (2) et/ou autour duquel ledit milieu ne s'écoule pas.
PCT/EP2020/069357 2019-07-10 2020-07-09 Dispositif d'alimentation en pression comprenant une pompe à engrenages Ceased WO2021005151A1 (fr)

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DE112020003258.2T DE112020003258A5 (de) 2019-07-10 2020-07-09 Druckversorgungseinrichtung mit einer Zahnradpumpe

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DE102019118708.7 2019-07-10
DE102019118708.7A DE102019118708A1 (de) 2019-07-10 2019-07-10 Druckversorgungseinrichtung mit einer Zahnradpumpe

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DE102022208186A1 (de) * 2022-08-05 2024-02-08 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Zahnradpumpe, insbesondere Gerotorpumpe
DE102024122296A1 (de) 2024-08-05 2026-02-05 Schwäbische Hüttenwerke Automotive GmbH Zahnradpumpe mit mehreren innenachsigen Zahnradsätzen

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Publication number Priority date Publication date Assignee Title
WO2023213955A2 (fr) 2022-05-05 2023-11-09 Thomas Leiber Système de dynamique de conduite, véhicule et procédé pour faire fonctionner un système de dynamique de conduite
EP4631807A2 (fr) 2022-05-05 2025-10-15 Ipgate Ag Système de dynamique de conduite, véhicule ainsi que procédé de fonctionnement d'un système de dynamique de conduite
EP4631806A2 (fr) 2022-05-05 2025-10-15 Ipgate Ag Système de dynamique de conduite, véhicule ainsi que procédé de fonctionnement d'un système de dynamique de conduite
EP4631805A2 (fr) 2022-05-05 2025-10-15 Ipgate Ag Système de dynamique de conduite, véhicule ainsi que procédé de fonctionnement d'un système de dynamique de conduite

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