WO2018114331A1 - Machine à roues dentées extérieures - Google Patents

Machine à roues dentées extérieures Download PDF

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Publication number
WO2018114331A1
WO2018114331A1 PCT/EP2017/081651 EP2017081651W WO2018114331A1 WO 2018114331 A1 WO2018114331 A1 WO 2018114331A1 EP 2017081651 W EP2017081651 W EP 2017081651W WO 2018114331 A1 WO2018114331 A1 WO 2018114331A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
external gear
rotation
filter
gear machine
Prior art date
Application number
PCT/EP2017/081651
Other languages
German (de)
English (en)
Inventor
Guido Bredenfeld
Jakob Branczeisz
Matthias RIEDLE
Original Assignee
Robert Bosch Gmbh
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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to US16/472,285 priority Critical patent/US20210131285A1/en
Publication of WO2018114331A1 publication Critical patent/WO2018114331A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/12—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type
    • F01C1/14—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F01C1/18—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/04—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/06—Heating; Cooling; Heat insulation
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for 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
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/56—Bearing bushings or details thereof
    • 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
    • F04C2240/80—Other components
    • F04C2240/802—Liners

Definitions

  • the invention relates to an external gear machine, in particular a
  • External gear pump or an external gear motor with at least two gears meshing with each other in outer engagement, wherein the gears are surrounded by a housing, wherein the one gear at least one journal and the other gear has a drive or driven pin, each in a bushing to each a rotation axis are rotatably mounted, wherein in the bearing bush a bearing sleeve with a
  • Anti-rotation is arranged.
  • External gear machine in particular a pump or a motor, with axially opposite a low pressure port and a
  • the object of the invention is an external gear machine, in particular an external gear pump or an external gear motor, with at least two gears which mesh with each other in external engagement, wherein the gears are surrounded by a housing, wherein the one gear at least one
  • Bearing journal and the other gear has a drive or driven pin, which are each rotatably mounted in a bearing bush about a respective axis of rotation, wherein in the bearing bush, a bearing sleeve with a
  • Anti-rotation is arranged, in particular with regard to the
  • the object is with an external gear machine, in particular one
  • External gear pump or an external gear motor with at least two gears meshing with each other in outer engagement, wherein the gears are surrounded by a housing, wherein the one gear at least one journal and the other gear has a drive or driven pin, each in a bearing bush to each a rotation axis are rotatably mounted, wherein in the bearing bush a bearing sleeve with a
  • Anti-rotation is arranged, achieved in that the rotation of the
  • Bearing sleeve disposed in a through hole of the bearing bush and combined with a filter and / or throttle device, through which a
  • bearing bushes in the bearing bushes with the pins rotatably mounted therein are plain bearings.
  • the bearing sleeves are also referred to as plain bearing sleeves.
  • the plain bearing sleeves are advantageously pressed into a bearing bush made of aluminum.
  • the external gear machine is preferably used as an external gear pump in a WHR system, wherein the
  • the WHR system is used to recover energy from an exhaust gas of a Internal combustion engine in a drive train of a motor vehicle.
  • a heat exchanger is arranged in an exhaust tract of the internal combustion engine, which transfers heat from the exhaust gas to a working medium flowing in a heating circuit.
  • the working medium in the heating circuit drives an expansion machine.
  • Heat cycle is a thermodynamic cycle or steam power process, also known as the Rankine process or Clausius-Rankine cycle.
  • Rankine process also known as the Rankine process or Clausius-Rankine cycle.
  • expansion machine is a thermodynamic cycle or steam power process, also known as the Rankine process or Clausius-Rankine cycle.
  • Turbomachine for example, a turbomachine, or a
  • Positive displacement machine for example a piston machine
  • Screw machine or a scroll machine used.
  • a condenser and an evaporator are arranged in the cycle.
  • External gear pump is arranged in the cyclic process between the condenser and the evaporator.
  • the working medium used in the cyclic process is preferably a low-viscosity medium, such as an ORC fluid.
  • ORC stands for the English terms Organic Rankine Cycle.
  • ORC fluids are ethanol or cyclopentane.
  • the refrigerant has sufficiently good thermodynamic properties and is also non-flammable.
  • a disadvantage is that the low-viscosity or low-viscosity fluid or medium, for example ethanol, has little or no lubricity. Therefore, in the experiments and examinations carried out in the context of the present invention, adjustments were made to reduce the bearing load. It was for example the
  • Anti-rotation of the bearing sleeve with the filter and / or throttle device is a double-function part created.
  • the compression of the bearing sleeve in the bearing bush can be reduced by the double-function part, since undesired rotation of the bearing sleeve, for example as a result of temperature conditions in the bearing and the mechanical bearing load, is mechanically blocked.
  • About the working fluid occurring during operation of the sliding bearing friction heat can be removed.
  • the structure of a hydrodynamic lubricating wedge in the sliding bearing can be improved with the working medium additionally supplied by the throttling and / or filter device. This prevents combined with the anti-rotation filter and / or
  • Throttling device of the dual-function part an undesirable penetration of particles, in particular chips, in the sliding bearing.
  • a preferred embodiment of the external gear machine is characterized in that the combined with the anti-rotation filter and / or throttle device comprises a slit filter for the working medium.
  • Particulate filtration on the one hand holds particles of a hazardous size
  • Throttling passages in particular throttle bores, the bearing sleeve fern.
  • the gap filtration allows a self-cleaning effect, since the particles are kept outside the bearing bush in the flowing working medium. That is, the particles can be washed away in a flow around specifically with the funded by the external gear machine working fluid.
  • a further preferred embodiment of the external gear machine is characterized in that the combined with the anti-rotation filter and / or throttle device comprises a base body with at least one flat which is arranged in the through hole of the bearing bush.
  • the main body of the anti-twist device is designed as a bore, for example.
  • the flattening is then advantageously formed as a surface on the screw thread of the body.
  • Another preferred embodiment of the external gear machine is characterized in that the base body on one of the bearing sleeve facing end has a Vermos Anlagensspitze and on one of the bearing sleeve end facing away a spacer with a filter head.
  • the anti-rotation tip is a mandrel that can be screwed into the bearing sleeve to mechanically secure it against rotation in the bearing bush.
  • the anti-rotation tip is advantageous in one piece with the
  • the spacer is connected via a shoulder with the filter head.
  • the combined with the anti-rotation filter and / or throttle device is tightened to the spacer body.
  • a desired slit filtering can be adjusted.
  • the spacer body for example, has a height that is less than 0.8 millimeters.
  • the spacer and the filter head are used to represent a gap for the gap filter.
  • the filter head is advantageously integrally connected via the spacer body with the base body.
  • Bearing bushes are connected to a bearing glasses with each other, wherein the combined with the anti-rotation filter and / or throttle device a
  • connecting body which connects two anti-rotation elements together and used to attach the combined with the anti-rotation filter and / or throttle device on the bearing glasses.
  • the through-hole is preferably a recess or two recesses, which is or are combined to form supply channels with a receiving slot described below.
  • the connection of two radially adjacent bearing bushes to a bearing glasses is known per se.
  • the term radial refers to the axes of rotation of the associated plain bearings. Radial means transverse to the axes of rotation.
  • the anti-rotation elements which are preferably integrally connected to the connecting body, are advantageously carried out at their free ends as tips, which during the pressing of the Connecting body are pressed into the receiving slot as rotation in the two bearing sleeves.
  • a further preferred embodiment of the external gear machine is characterized in that the bearing glasses has a receiving slot which extends between two supply channels for the working medium through the bearing bushes to the respective bearing sleeve and serves to receive the connecting body with the anti-rotation elements.
  • Receiving slot is designed for example as a milling slot.
  • a receiving gap or milling gap has, at least over part of the length of the receiving slot or Frässchlitzes, a fitting for pressing in the connecting body.
  • the connecting body advantageously constitutes a type of wedge, which is driven into the receiving slot or milling slot.
  • the receiving slot is advantageously made slightly wider to the
  • the supply channels preferably run along the anti-rotation elements. Via the supply channels, a preferably filtered inflow in the direction of the two bearing sleeves is made possible in a simple manner.
  • a further preferred embodiment of the external gear machine is characterized in that an edge region is angled from the connecting body, which, at least in the region of the supply channels, exerts a gap filter function for the working medium.
  • the connecting body preferably has substantially the shape of an elongated cuboid, which is pressed in a wedge-like manner into the receiving slot of the bearing goggles. From an underside of the connecting body, which faces the bearing glasses, the anti-rotation elements extend to the bearing sleeves in the bearing glasses. At the top of the connecting body, which faces away from the bearing glasses, the edge region is angled. The edge area is angled, for example, by crimping. An angle between the angled edge region and the
  • Connecting body is preferably substantially ninety degrees.
  • the angled edge region is to represent the gap filter function, at least in the region of the supply channels, so far away from the bearing glasses that results in a filter gap for the working medium. This is a simple way an undesirable influx of particles, for example Chips, to the bearing sleeves prevented. About to press in the
  • a further preferred embodiment of the external gear machine is characterized in that the angled edge portion of the connecting body between the supply channels constitutes a stop for the combined with the anti-rotation filter and / or throttle device.
  • the angled edge region for example the flange, is pre-bent deeper in a middle region.
  • pre-bent curl can be set in a simple manner, the height of the split filter.
  • the angled edge region to retain the gap filter function is not pre-bent more.
  • a further preferred embodiment of the external gear machine is characterized in that at least one cooling channel is provided between the bearing sleeve and the bearing bush, which extends from the through hole or from the supply channels in the bearing bush to at least one throttle passage in the bearing sleeve.
  • Throttling passage in the bearing sleeve is designed for example as a throttle bore.
  • About the bearing bush or the bearing bushes is in
  • Heat dissipation at least one cooling channel, which is designed for example as a flushing groove, in the plain bearing, preferably in the bearing bush integrated.
  • the cooling channel in particular the flushing groove, has at its outlet into the bearing sleeve, ie at the throttle passage, a very small throttle diameter.
  • Throttle diameter is for example 0.8 millimeters.
  • the invention further relates to a combined with an anti-rotation filter and / or throttle device, a bearing bush and / or a bearing glasses for a previously described external gear machine.
  • the parts mentioned are separately tradable.
  • the bearing bush or bearing glasses is advantageously made of a good heat conducting material, such as aluminum. As a result, the removal of the frictional heat occurring during operation of the external gear machine is improved and an undesirable overloading of the plain bearing or plain bearing is avoided.
  • the bearing bush or bearing glasses is advantageously made of a lightweight material, such as aluminum. This makes the external gear lighter.
  • the aluminum material also provides the advantage that it is easy to work, especially easy machinable.
  • the bearing bush or bearing glasses is advantageously produced as a blank in a die-casting process. This provides the advantage that some processing steps are omitted or directly into the
  • the invention also relates to a method for operating and / or producing or mounting a previously described one
  • External gear can, for example, by a material removal on gear heads of the gears of the external gear a
  • Figure 1 is a schematic representation of the external gear machine with a bearing assembly comprising four sliding bearings
  • Figure 2 is a plain bearing of Figure 1 in section through a bearing bush with an anti-rotation device for the bearing sleeve, wherein the rotation is combined with a filter and / or throttle device;
  • FIG. 3 shows the enlarged illustration of a detail III from FIG. 2;
  • Figure 4 is a perspective view of the combined with the anti-rotation filter and / or throttle device of Figures 1 and 2;
  • FIG. 5 shows the illustration of a section along the line V-V in FIG. 6 through a pair of bearing glasses with an anti-rotation lock for two bearing sleeves, wherein the anti-twist device is combined with a filter and / or throttle device;
  • Figure 6 shows the bearing glasses of Figure 5 is shown in a view from above;
  • Figure 7 is a sectional view taken along the line VII-VII in Figure 5;
  • FIG. 8 shows a detail VIII from FIG. 7;
  • FIG. 9 is a perspective view of the filter and / or throttle device of FIG. 5 combined with the anti-twist device;
  • Throttle device represents a stop. Description of the embodiments
  • FIG. 1 shows a schematic diagram of an external gear machine 1 with a first gear 3 and a second gear 4 simplified in longitudinal section.
  • the externally toothed gears 3, 4 mesh with each other in external engagement.
  • the first gear 3 is rotatably connected in Figure 1 on its left side with a pin 5.
  • the first gear 3 can be driven via the pin 5, which is then also referred to as a drive pin 5.
  • the first or driving gear 3 is rotatably connected to a bearing pin 6.
  • the second gear 4 has in Figure 1 laterally two bearing pins 7, 8, with which the second gear 4 is rotatably connected.
  • the two gears 3, 4 are rotatably mounted in a housing 10 by means of the pins 5, 6 and 7, 8.
  • the first gear 3 is rotatable about a first axis of rotation 13 with the aid of the drive pin 5 and the journal 6.
  • the second or driven gear 4 is rotatable by means of the bearing pins 7, 8 about a second axis of rotation 14 which is parallel to the first axis of rotation 13.
  • the housing 10 is on its left in Figure 1 side of a first
  • Housing cover 11 and limited on its right in Figure 1 side of a second housing cover 12.
  • a housing base 15 of the housing 10 is arranged between the housing covers 11, 12.
  • the first housing cover 11 is by means of fixing means 16, 17 on the first housing cover 11
  • the second housing cover 12 is fixed to the housing base body 15 with the aid of fixing means 18, 19.
  • the fixing means 16 to 19 are, for example, dowel pins.
  • the connection of the housing cover 11, 12 takes place with the aid of bolts 81 and 82 documents.
  • Housing body 15 a first housing seal 21 is arranged.
  • Figure 1 is disposed between the second housing cover 12 and the housing base 15, a second housing seal 22.
  • a radial shaft seal 24 is used to seal a
  • the radial shaft seal 24 is installed in a known manner from the outside into an annular space which extends around the drive pin 5 around.
  • a bearing arrangement 25 serves to mount the two gearwheels 3, 4 in the housing 10.
  • the bearing arrangement 25 comprises two bearings 26, 27 for mounting the first gearwheel 3.
  • the bearing 25 comprises two further bearings 28 , 29.
  • the bearings 26 and 27 are associated with two Axialfelddichtonne 31, 32, which serve to seal between the bearings 26, 27 and the housing covers 11, 12.
  • the bearings 28, 29 are associated with two Axialfelddichtonne 33, 34, which serve to seal between the bearings 28, 29 and the housing covers 11, 12.
  • the Axialfelddichtitch 31 and 33 are advantageous in a component
  • the Axialfelddichtitch 32 and 34 are also advantageously combined in one component. Then, the bearings 26 and 28 are sealed with the combined axial field seal 31, 33. The bearings 27 and 29 are then sealed with the combined axial field seal 32, 34.
  • the bearings 26 to 29 of the external gear machine 1 are designed as sliding bearings, each with a bearing bush.
  • a bearing sleeve is arranged in the bearing bush.
  • Two radially adjacent bearing bushes can be advantageously connected to one another to a bearing glasses.
  • FIG. 2 shows a slide bearing 36 with a single bearing bush 38 in cross section.
  • the bushing 38 comprises a through-hole 39 in FIG. 2 at the top.
  • the through-hole 39 is designed, for example, as a radial bore.
  • a bearing sleeve 40 is pressed into the bearing bush 38.
  • a throttle passage is indicated in Figure 2, which is designed as a throttle bore.
  • the working medium, with which the external gear machine (1 in Figure 1) is operated to the bearing sleeve 40 passes over at least one cooling channel 54 that
  • High-pressure channel shortened also referred to as pump
  • the working fluid enters the interior of the bearing sleeve 40, where it advantageously the structure of a hydrodynamic
  • Lubricant wedge of the plain bearing improved.
  • the throttle bore 41, 42 is also referred to as Spülbohrung.
  • the necessary flushing quantity can be determined by the size of the
  • Throttle bore 41, 42 are determined.
  • the throttle bore 41, 42 has, for example, a diameter of 0.8 millimeters.
  • a double-function part 43 is arranged in the through hole 39 of the bearing bush 38.
  • the combined with the anti-rotation filter and / or throttle device comprises a main body 46, which has substantially the shape of a straight circular cylinder with an external thread. From the main body 46, a mandrel extends with a
  • Anti-rotation tip 47 in Figure 3 down.
  • the main body 46 is screwed into the through hole 39 of the bearing bush 38 so that the
  • Anti-rotation tip 47 is pressed externally into the bearing sleeve 40.
  • the spacer body 48 has substantially the shape of a circular disk with a flattening unspecified, which merges into a flattening 50 of the base body 46.
  • the spacer 48 serves in combination with the filter head 49 for the representation of a filter gap 51, 52.
  • 53 particles are indicated, which collect in front of the filter gap 51, 52.
  • the working medium passes without the particles 53 through the filter gap 51, 52 along the flattening 50 into the cooling channel 54.
  • FIGS. 5 to 14 show two exemplary embodiments of two plain bearings 56, 57, in which two bearing bushes 58, 59 are combined in a pair of bearing glasses 60.
  • the bearing bush 58 is a bearing sleeve 61st
  • a bearing sleeve 62 is arranged in the bearing bush 59.
  • the two bushings 58, 59 are integrally connected by the bearing glasses 60 together.
  • the bearing glasses 60 is associated with a double-function part 63, in which an anti-rotation device is combined with a filter and / or throttle device 86.
  • the anti-rotation 63 is installed in the high pressure region of the shortened referred to as a pump external gear to supply the bearings with fresh medium from the high pressure.
  • the anti-rotation comprises two anti-rotation elements 66, 67, which by a
  • Connecting body 65 are integrally connected to each other.
  • Anti-rotation element 66 has at a free, in Figure 5 lower end a tip 68 which is pressed to prevent rotation in the bearing sleeve 61.
  • the anti-rotation element 67 at a free, in Figure 5 lower end a tip 69 which is pressed to prevent rotation in the bearing sleeve 62.
  • the double-function part 63 is connected to the connecting body 65 in a
  • Receiving slot 70 pressed or clamped.
  • Receiving slot 70 is designed for example as a Frässchlitz and extends between two supply channels 71, 72.
  • the supply channel 71 extends along the anti-rotation element 66 to the bearing sleeve 61.
  • Supply channel 72 extends along the anti-rotation element 67 to the bearing sleeve 62.
  • the supply channels 71, 72 open into cooling channels 73, 74.
  • the cooling channel 73 connects the supply channel 71 with a
  • Throttle passage 75 The cooling channel 74 connects the supply channel 72 with an indicated by arrows 76, 77 throttle passage.
  • the cooling channels 73, 74 are, as can be seen in particular in Figures 5 and 6, designed as a spiral Spülnuten 79, 80.
  • the spiral flushing grooves 79, 80 are radially inwardly inserted into the bearing bushes 58, 59 and serve to perform the working medium of the external gear pump (1 in Figure 1).
  • An edge region 85 facing away from the bearing gland 60 in FIG. 5 is angled away from the connecting body 65 in order to depict a gap filter of the filter and / or throttle device 86.
  • a gap height for the gap filtering is indicated in Figure 8.
  • the undesired penetration into the spiral Spülnuten 79, 80 is prevented by the filter and / or throttle device 86.
  • the connecting body 65 is pressed into the receiving slot 70.
  • the receiving slot 70 has over its length a fitting for pressing the connecting body 65. In the vicinity of its two ends of the receiving slot 70 is made slightly wider to represent the supply channels 71, 72.
  • Connecting body 65 in one piece with the angled edge portion 85th are connected.
  • To illustrate the angled edge region 85 of the connecting body 65 is crimped at its upper edge.
  • the gap height (87, 88 in FIG. 8) can be adjusted by means of the pressing force used for pressing in the cross-sectionally wedge-shaped connecting body 65.
  • FIGS. 10 to 14 largely corresponds to the exemplary embodiment illustrated in FIGS. 5 to 9. Therefore, the same reference numerals are used to designate the same or similar parts. To avoid repetition, reference is made to the preceding description of Figures 5 to 9. In the following, only the differences between the two embodiments will be discussed.
  • the angled edge region 85 of the connecting body 65 designed as a flange is bent deeper to represent a stop when the double-functional part 63 is mounted. This eliminates the previously described dependence of the gap height of the pressing force during pressing of the connecting body 65 in the receiving slot 70. On the height of the center portion 100 more pre-bent curl the gap height (87, 88 in Figure 13) can be set or determined. In two end sections 101, 102, the edge region 85 is spaced from the bearing gland 67 by the gap height (87, 88 in FIG. 13) in order to represent the gap filter function.

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

Abstract

L'invention concerne une machine à roues dentées extérieures (1), en particulier une pompe à roues dentées extérieures ou un moteur à roues dentées extérieures comprenant au moins deux roues dentées (3, 4) qui s'engrènent l'une dans l'autre par engagement extérieur, les roues dentées (3, 4) étant entourées par un boîtier (10), l'une des roues dentées (4) présentant au moins un tourillon de palier (7, 8) et l'autre roue dentée (3) présentant un tourillon d'entraînement ou de prise de force (5), lesquels sont chacun supportés de manière à pouvoir tourner à chaque fois autour d'un axe de rotation (13, 14) dans un manchon de palier (38), une douille-palier (38) avec une fixation antirotation étant disposée dans le manchon de palier (38). Afin de perfectionner la machine à roues dentées extérieures, en particulier dans l'optique d'améliorer les matériaux pouvant être utilisés pour la fabrication des manchons de palier et/ou d'améliorer la durée de vie, la fixation antirotation de la douille-palier est disposée dans un trou traversant du manchon de palier et est combinée à un dispositif de filtre et/ou d'étranglement à travers lequel un fluide de travail parvient de la machine à roues dentées extérieures (1) jusqu'à la douille-palier.
PCT/EP2017/081651 2016-12-21 2017-12-06 Machine à roues dentées extérieures WO2018114331A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US16/472,285 US20210131285A1 (en) 2016-12-21 2017-12-06 External gear machine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016225826.5A DE102016225826A1 (de) 2016-12-21 2016-12-21 Außenzahnradmaschine
DE102016225826.5 2016-12-21

Publications (1)

Publication Number Publication Date
WO2018114331A1 true WO2018114331A1 (fr) 2018-06-28

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PCT/EP2017/081651 WO2018114331A1 (fr) 2016-12-21 2017-12-06 Machine à roues dentées extérieures

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US (1) US20210131285A1 (fr)
DE (1) DE102016225826A1 (fr)
WO (1) WO2018114331A1 (fr)

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US11060559B2 (en) * 2018-06-11 2021-07-13 Eaton Intelligent Power Limited Bi-metallic journal bearing with additive manufactured sleeve

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US20130259729A1 (en) * 2012-03-30 2013-10-03 Colfax Corporation Gear pump with asymmetrical dual bearing
DE102012209152A1 (de) * 2012-05-31 2013-12-05 Robert Bosch Gmbh Zahnradmaschine mit hydraulischer Verlagerung der Zahnränder
DE102012216254A1 (de) 2012-09-13 2014-03-13 Robert Bosch Gmbh Außenzahnradmaschine
DE102013202606A1 (de) * 2013-02-19 2014-08-21 Robert Bosch Gmbh Zahnradmaschine mit einer Lagerhülse, die mehrere Vorsprünge aufweist.

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