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EP2249039A2 - Pompe à engranage externe dotée d'une lubrification de palier améliorée - Google Patents

Pompe à engranage externe dotée d'une lubrification de palier améliorée Download PDF

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Publication number
EP2249039A2
EP2249039A2 EP10161304A EP10161304A EP2249039A2 EP 2249039 A2 EP2249039 A2 EP 2249039A2 EP 10161304 A EP10161304 A EP 10161304A EP 10161304 A EP10161304 A EP 10161304A EP 2249039 A2 EP2249039 A2 EP 2249039A2
Authority
EP
European Patent Office
Prior art keywords
bearing
fluid
chamber
lubricant
profile
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.)
Withdrawn
Application number
EP10161304A
Other languages
German (de)
English (en)
Other versions
EP2249039A3 (fr
Inventor
Hilmar Gärtner Dr.
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive 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 Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP2249039A2 publication Critical patent/EP2249039A2/fr
Publication of EP2249039A3 publication Critical patent/EP2249039A3/fr
Withdrawn legal-status Critical Current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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0088—Lubrication
    • 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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/185—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by varying the useful pumping length of the cooperating members in the axial direction
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps 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
    • 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
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • 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
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the invention relates to the lubrication of a rotary bearing of a rotary displacement pump, preferably an external gear pump.
  • Recirculating displacement pumps include a rotatably supported impeller or a plurality of rotatably mounted impellers that form or form circulating conveyor cells around one or more axes of rotation in which fluid is conveyed from an inlet to an outlet of a pumping chamber.
  • rotary bearing fluid from the pump chamber is used, which is pressed by a high pressure side of the pump chamber through the rotary bearing to be lubricated back to a low pressure side.
  • the rotary bearing or with several conveyor wheels, the respective pivot bearing is subject to considerable wear, which often limits the life of the pump.
  • the invention is based on a circulation displacement pump which comprises a housing with a chamber and at least one delivery wheel received in the chamber.
  • the chamber has an inlet on a low pressure side of the pump and an outlet on a high pressure side of the pump for a fluid to be delivered by the pump.
  • the delivery wheel is rotatably mounted about an axis of rotation for delivery of the fluid. It forms with walls of the chamber and preferably in a conveying engagement with a further conveying wheel conveyor cells, which run in the case of a rotary drive of the conveying wheel or the plurality of conveying wheels about the axis of rotation and in which the fluid is conveyed from the inlet to the outlet.
  • the pump further comprises at least one bearing structure, which is preferably arranged axially offset from the feed wheel, and a bearing profile which has a bearing surface for the rotary mounting of the feed wheel about the axis of rotation.
  • the bearing surface forms with a counter bearing surface a bearing gap of the pivot bearing, i. the bearing surface and the counter bearing surface limit the bearing gap in radial direction with respect to the axis of rotation.
  • the bearing surface is an outer peripheral surface of the bearing profile and the bearing surface surrounds the bearing surface. Alternatively, however, the bearing surface may surround the bearing surface.
  • the bearing counter surface is formed by the bearing structure or preferably by the feed wheel.
  • the bearing profile may be formed as an axis about which the conveying wheel is rotatable, or as a shaft rotating together with the conveying wheel. If the bearing structure forms the counter bearing surface, the conveying wheel and the bearing profile can be connected to one another in a rotationally secured manner or even formed in one piece. If, as preferred, the delivery wheel forms the bearing counter surface, the delivery wheel correspondingly rotates about the bearing profile to form the storage gap. In such cases, the bearing profile is preferably fixed, i. immovably connected to the bearing structure, for example in one piece or preferably by means of a positive or frictional connection.
  • the word "or” has the usual meaning of "and / or” here as well as otherwise in the sense of the invention, as far as nothing else can be deduced from the respective context.
  • bearing gap rolling elements can be arranged and the pivot bearing be formed as a rolling bearing.
  • the pivot bearing is designed as a sliding bearing.
  • the pump For the lubrication of the rotary bearing, the pump comprises a lubricant channel, through which a lubricant can be conveyed into the bearing gap.
  • the lubricant used is the fluid to be delivered by the pump.
  • the lubricant passage extends from outside the chamber into the bearing gap to guide the lubricating fluid not from the chamber but from a high pressure side of the pump downstream of the chamber as a lubricant into the bearing gap. From the flow of the pump, a partial flow is diverted and led back for the purpose of bearing lubrication in the bearing gap.
  • the invention sets upon the recognition that the fluid delivered by the chamber contains dirt particles, in particular wear particles, which increase the abrasion in the rotary bearing and therefore increase the wear of the rotary bearing, which can lead to seizure. Due to the lubricant channel according to the invention, the fluid for lubrication can be freed of dirt particles before being introduced into the bearing gap.
  • the recirculation displacement pump according to the invention is therefore not lubricated with the raw fluid as it is conveyed through the chamber, but with purified clean fluid.
  • the crude fluid is passed in preferred embodiments through a purifier located in a fluid circuit of the pump downstream of the pump.
  • the fluid purified by the purifier i. the clean fluid is recycled in a return to the pump.
  • the return is connected via a connection formed on the housing of the pump to the lubricant channel.
  • the cleaning device or an additional cleaning device can also be arranged in the return.
  • the cleaning device or the additional cleaning device can also be arranged in the housing of the pump or directly on the housing.
  • the fluid displaced through the outlet of the chamber is branched into a first partial flow and a second partial flow, wherein the first partial flow, which preferably forms a main flow, is supplied in full or in part to an aggregate to be supplied to the fluid and the second partial flow is supplied completely or to one Part is passed over the cleaning device back into the lubricant channel.
  • the cleaning device is arranged in or directly on the housing of the pump, it is advantageously arranged interchangeably.
  • the cleaning device may be in all arrangement variants in particular a fluid filter with a single or multiple screens.
  • Pure fluid lubrication also has the advantage that cooler pure fluid can be used to remove heat from the rotary bearing as compared to the crude fluid in the chamber.
  • the crude fluid delivered by the pump is cooled on the high pressure side in the flow path to or preferably before the purifier by means of a cooler and returned to the pump as a lubricant in the cooled state. Therefore, if the cooling device is located downstream of the cleaning device, the return preferably branches off behind the Cooling device off.
  • a cooling device can also be provided exclusively for the branched lubricant or additionally in the return, as also applies with respect to the cleaning device.
  • the specific delivery volume of the pump is adjustable in order to adapt the delivery rate or the absolute delivery volume of the pump to the needs of the unit to be supplied.
  • the pump has an adjustment unit, which comprises the delivery wheel, the bearing profile and a piston, which are connected to one another in such a way that together they perform an adjustment movement.
  • the bearing structure forms the piston.
  • the adjustment unit is preferably adjusted as a function of a fluid pressure of the high pressure side of the pump.
  • the adjustment unit is mounted so that it can move back and forth, wherein a movement of the adjustment unit in a first direction causes a reduction and a movement in the other direction causes an increase in the specific delivery volume.
  • the adjustment unit is axial, i. along the axis of rotation or parallel to the axis of rotation of the feed wheel, movable back and forth. Alternatively, however, it can also be movable transversely to the axis of rotation, linearly or pivotably.
  • Axial mobility is preferred for off-axis pumps, while for internal-axis pumps, both axial mobility and transverse mobility are possible.
  • the adjustment unit is preferably acted upon in dependence on a fluid pressure of the high pressure side in the first direction of its mobility, so that the specific delivery volume is reduced with increasing pressure.
  • the fluid pressure counteracts a restoring force.
  • the adjusting unit is acted upon counteracting the fluid pressure with a spring force.
  • the position of the adjusting unit adjusts itself to the current equilibrium of the adjusting force generated by means of the fluid pressure and the restoring force.
  • the piston can be an axial stroke piston, in particular in the case of external-axis pumps, but also in the case of internal-axis pumps.
  • the piston is directly facing an end face of the impeller so as to form with the impeller an axial sealing gap which fluidly separates the high pressure side of the chamber from the low pressure side of the chamber from unavoidable leakage.
  • the piston is preferred for the piston to be exposed to the clean fluid.
  • Such an embodiment allows the supply of the clean fluid through the piston into the bearing gap of the pivot bearing.
  • the lubricant passage extends in such embodiments through the piston.
  • Such an arrangement of the lubricant channel is structurally simple and guarantees a bearing lubrication with always sufficient pressure.
  • the centrifugal force is preferably used for the discharge by the lubricant is discharged from the bearing gap radially outward to the low pressure side.
  • the centrifugal force can thus be at least partially compensated for a pressure loss, the pure fluid compared to the raw fluid of conventional lubrication concepts.
  • the lubricant channel extends through the bearing profile and the bearing gap is preferably supplied from the inside radially with the lubricant.
  • the bearing profile has, at least in sections, a hollow cross section which forms a section of the lubricant channel.
  • a connecting channel is formed in the bearing profile, which leads from the hollow cross section through the bearing profile out to the outside of the bearing surface.
  • the connecting channel may in particular be a simple radial bore in the bearing profile.
  • the lubricant channel thus leads through the piston of the adjustment in the hollow cross section of the bearing profile. If the conveyor wheel is not adjustable, a fixed chamber wall to replace the piston by the lubricant channel leads through this chamber wall in the hollow cross section of the bearing profile.
  • the lubricant channel opens into an axially middle section of the bearing gap.
  • the lubricant is distributed from the mouth region axially to both sides and therefore on a short path to the axial ends of the bearing gap.
  • the removal is preferably carried out by discharge channels, which are formed in sealing surfaces facing the two axial end faces of the feed wheel and each form an axial sealing gap with one of these sealing surfaces.
  • the discharge channels are each formed in the sealing surfaces as a recess leading from the inside to the outside radially.
  • the discharge channels are so narrow that they do not appreciably affect the sealing effect of the respective sealing gap.
  • the lubricant would be introduced in such an embodiment conveniently at the opposite end of the discharge axial end of the bearing gap.
  • the guided through the bearing profile lubricant channel opens in a recess which is formed in the bearing surface or the bearing counter surface and extending in the circumferential direction about the axis of rotation of the feed wheel.
  • the recess extends circumferentially about the axis of rotation, ie over 360 °.
  • the bearing profile is a hollow axis around which rotates the feed wheel, or a hollow shaft which is rigidly connected to the feed wheel, it is advantageous if the recess is formed in the bearing counter-surface to the shell of the hollow shaft or hollow shaft not to weaken.
  • the recess may instead or optionally additionally a recess in the hollow axle or shaft may be formed.
  • the recess serves as a distribution channel for the lubricant. Without such a distribution channel would have the lubricant channel at non-rotatable bearing profile in the bearing gap in a rotational angle position open in the operating load a sufficiently wide gap for the distribution of the lubricant remains. Viewed over the circumference of the bearing surface, the forces in the operation of the pump are distributed nonuniformly.
  • a distribution channel which extends in the circumferential direction over a sufficiently large rotation angle range, preferably over 370 °, allows the positioning of the mouth of the lubricant channel in the region of the recess at an arbitrary rotational angular position.
  • a bearing profile which is at least partially hollow, contributes to weight reduction.
  • a weight reduction is particularly advantageous if the bearing profile is part of a movable adjustment or optionally rotates with the feed wheel. The reduction of the moment of inertia associated with the weight reduction improves the response time of such an adjustment unit.
  • the lubricant channel can also run on the bearing profile outside by the bearing profile in the region of its bearing surface has an axial or spiral circumferential recess or flattening, in which the lubricant is guided in the bearing gap and distributed in the axial direction.
  • the lubricant channel would initially run on its feed side through said piston or non-adjustable impeller through a stationary chamber wall and axially the sealing gap on the respective end face of the feed wheel bridging lead in the formed as a recess or flattening lubricant channel.
  • the lubrication would still be done essentially with pure fluid, but the pure fluid would be mixed because of the bridging of the sealing gap, a certain proportion of funded through the chamber raw fluid. Furthermore, the lubricant would have to flow through the entire axial length of the bearing gap from the feed side to the discharge side.
  • the bearing profile can have circumferentially stepped recesses over its axial length for connection to the delivery wheel and the bearing structure or the bearing structures.
  • the outer peripheral surface of the bearing profile is in the longitudinal direction over at least the most of the axial length of the bearing profile stepless continuously smooth, preferably circular cylindrical.
  • An over the entire axial length of the bearing profile continuously smooth outer peripheral surface is particularly preferred.
  • the bearing profile can have a single or a plurality of form-fitting elements, for example a flattening, in order to connect the bearing profile with either the bearing structure or the feed wheel so as to be secured against rotation.
  • a non-rotating and also for an axially fixed connection with the relevant part however, a purely frictional-acting connection is preferred.
  • the bearing profile is preferably, as already mentioned, inside at least partially hollow.
  • the hollow cross section preferably extends over the major part of the axial length of the bearing profile, advantageously over almost the entire axial length.
  • the hollow cross section is preferably circular cylindrical inside.
  • the cavity of the bearing profile preferably corresponds to at least half of the total volume of the bearing profile.
  • the bearing profile may in particular be sleeve-shaped. It may have a bottom at one axial end.
  • the hollow cross-section may extend continuously from the bottom to the other axial end of the bearing profile.
  • the lubricant channel expediently leads through the bottom into the hollow cross section.
  • the bearing profile may be a simple sleeve with an axially constant throughout the same hollow cross-section.
  • the circulation displacement pump is preferably an external gear pump. In principle, it can also be another external-axis pump or an internal-axis pump, for example an internal gear pump or a vane pump. If it is a vane pump, the impeller may be the only impeller of the pump. In the case of a gear pump, a further delivery wheel is provided, which is in a conveying engagement, ie tooth engagement with the above-described delivery wheel. It can also be provided more than two conveyor wheels, for example, three conveyor wheels in an external gear pump, wherein a middle of these conveyor wheels with two outer each in a conveying engagement. In a vane pump may in principle also be provided several conveyor wheels.
  • the pump can be used in particular as a lubricating oil pump for supplying an engine of a motor vehicle.
  • vehicle construction is at all a preferred field of application of the invention.
  • the pump can also serve as a supply pump for another unit of a vehicle with a working fluid, for example for supplying an automatic transmission with hydraulic fluid. In principle, however, it can also serve to supply other units, for example a hydraulic press, with working fluid.
  • the supply of lubricant from radially inward or at least at the same radial height with the bearing gap is not only advantageous in embodiments in which the rotary bearing is lubricated with clean fluid, but also for a lubrication concept that uses not yet purified crude oil for the bearing lubrication, the Crude oil is preferably branched off within the housing of the pump and returned to the bearing gap.
  • the Applicant therefore reserves the right to pursue this aspect of the invention by means of a separate application, a main claim of such an application, for example, only the preamble features of claim 1 or optionally only a part of these features in combination with a supply of the lubricant having internal feature, for example according to claim 10.
  • FIG. 1 shows as an example of a rotary displacement pump, an external gear pump in a cross section.
  • a chamber is formed, are rotatably mounted in the two conveyor wheels 1 and 2 in the form of externally toothed gears about parallel axes of rotation R 1 and R 2 .
  • the feed wheel 1 is rotationally driven via a drive member, for example, from the crankshaft of an internal combustion engine of a motor vehicle.
  • the conveyor wheels 1 and 2 are meshed with each other in a conveying engagement, in the exemplary embodiment, so that in a rotary drive of the feed wheel 1, the thus meshing conveyor wheel 2 is also rotationally driven.
  • An inlet 4 opens into the chamber on a low-pressure side and an outlet 5 on a high-pressure side for a fluid to be delivered, preferably lubricating oil for the internal combustion engine mentioned by way of example.
  • the housing 3 forms the conveying wheels 1 and 2 facing in the radial direction in each case a radial sealing surface, which wraps around the respective conveying wheel 1 or 2 over part of its circumference to form a radial sealing gap.
  • the housing 3 further forms on each end face of the feed wheel 1 axially facing this an axial sealing surface 3b.
  • the pump delivers the fluid on the high pressure side via the outlet 5 and a connected in FIG. 2 schematically shown supply line 13, a cooling device 14 and further via a cleaning device 15 to be supplied to the unit 17 and from there into a sump 18. From the pressure-relieved sump 18, the fluid is sucked in on the low-pressure side via the inlet 4 and thus in a closed fluid circuit circulated by increasing the pressure and subsequent discharge.
  • the delivery rate of the pump increases proportionally with the speed of the conveyor wheels 1 and 2. Since an example assumed as a consumer engine from a certain limit speed less lubricating oil absorbs as the pump according to their proportionally with the speed increasing characteristic would promote the delivery rate of the pump from the Limiting speed limited.
  • the feed wheel 2 is axially movable to and fro relative to the feed wheel 1, so that the measured parallel to the rotation axes R 1 and R 2 engagement length of the feed wheels, the feed rate or the volume of the pump can be changed in accordance with 1 and 2 and ,
  • FIG. 2 takes the feed wheel 2 relative to the feed wheel 1 an axial position with a maximum axial overlap, ie maximum engagement length.
  • the feed wheel 2 is part of an adjustment with two axially offset to the feed wheel 2 arranged piston 8 and 9, a piston 8 and 9 connecting the bearing section 10 and the rotatably mounted between the piston 8 and 9 on the bearing section 10 conveyor wheel 2.
  • the bearing profile 10th connects the pistons 8 and 9 axially rigid and torsionally rigid with each other.
  • the pistons 8 and 9 form the conveying wheel 2 directly facing each one of the axial sealing surfaces 8b and 9b for the feed wheel 2.
  • the adjustment is axially displaceable in a sliding space of the housing 3 back and forth and mounted against rotation.
  • the displacement chamber comprises a fluid space 7 delimited by the adjustment unit on one axial side and a further space likewise delimited by the adjustment unit on the axially opposite side of the adjustment unit, in which a spring member 12 is arranged.
  • the fluid chamber 7 can be acted upon by pressure fluid of the high-pressure side of the pump.
  • the spring force of the spring member 12 counteracts the pressure force of the pressure fluid.
  • the spring member 12 is as exemplified in the DE 102 22 131 B4 described by the introduction of pressure fluid of the high-pressure side relieved when the pump is to promote the fluid with maximum specific flow.
  • the pivot bearing of the feed wheel 2 is formed as a sliding bearing between the feed wheel 2 and the bearing profile 10.
  • the bearing profile 10 forms an axis about which the conveyor wheel 2 rotates.
  • the sliding bearing is directly between a circular cylinder about the axis of rotation R 2 circumferential bearing surface 10a of the bearing profile 10 and a bearing surface 10a surrounding bearing surface 2a of the feed wheel 2 is formed.
  • the bearing surface 10a and the bearing counter surface 2a define between them a narrow bearing gap, is conveyed in the funded by the pump fluid of the high pressure side and serves as a lubricant in the bearing gap.
  • the clean fluid downstream of the cooling device 14 and the purifier 15 is branched off from the fluid flow conveyed through the chamber and then the supply line 13, i. the fluid pumped by the pump flows through the cooling device 14 and the cleaning device 15 and is returned downstream of these two devices via a return 16 for the purpose of lubricating the rotary bearing to the pump.
  • the feedback 16 is connected to a terminal 6 of the housing 3. From the port 6 leads within the housing 3, a lubricant channel into the bearing gap 2a, 10a.
  • the lubricant channel comprises the fluid space 7 and then extends directly to the fluid space 7 through the piston 8 and from there into the bearing profile 10.
  • the bearing profile 10 accordingly has a hollow cross-section 10b, which forms a portion of the lubricant channel.
  • the hollow cross section 10b is connected to the bearing gap via a connecting channel 10c, which is formed as a radial bore.
  • the connecting channel 10c leads into the bearing gap at an axially central location, i. it has at least substantially the same distance to the two axial ends of the bearing gap. In this way, the lubricant is distributed evenly and over the shortest path over the entire length of the bearing gap.
  • the lubricant flows through discharge channels formed in the sealing surfaces 8b and 9b of the pistons 8 and 9 toward the low-pressure side.
  • the flow path of the lubricant is indicated by a dotted line and an arrow pointing into the connecting channel 10c.
  • FIG. 3 shows the components of the adjustment along the axis of rotation R 2 lined up for assembly.
  • the fluid space 7 limiting piston 8 and the bearing profile 10 are already firmly connected to each other, preferably only by means of frictional engagement.
  • the bearing profile 10 can be shrunk or otherwise pressed into the piston 8 and 9, for example.
  • the functional distribution of the bearing profile is to be indicated in three axial sections, namely the central portion which forms the bearing surface 10 a, and the two outer end portions, each having a joint portion, preferably ReibBankab mustard for the solid Make connection with the respective piston 8 or 9.
  • the bearing profile 10 is a cylindrical sleeve with a with the exception of the mouth of the connecting channel 10c everywhere smooth, circular cylindrical outer periphery and over almost the entire axial length also smooth, circular cylindrical inner cross section.
  • the thickness of the corresponding circular cylindrical shell of this sleeve is smaller than the measured on the axis of rotation R 2 radius of the inner cross section.
  • the sleeve is open at one axial end. At the other axial end, it has a bottom through which extends axially a slender channel section, which merges into the further axial channel section 8a, which extends through the piston 8 and opens into the fluid space 7.
  • connection between the fluid space 7 and the hollow cross-section 10b has a flow cross-section which is so small that the piston surface facing away from the delivery wheel 2, to which the pressure of the recycled pure oil acts, and thereby the force generated by the pressure is not appreciably reduced ,
  • the rapid and uniform distribution of the lubricant in the bearing gap is also a distribution channel 2b, which is formed in the bearing counter surface 2a as a recess which rotates about the axis of rotation R 2 .
  • the connecting channel 10c opens into the distribution channel 2b.
  • the feed wheel 1 is torsionally rigid and axially immovably connected to a bearing profile 11 which forms the drive shaft of the pump.
  • the bearing profile 11 is rotatably mounted about the rotation axis R 1 .
  • the pivot bearing for the feed wheel 1 comprises axially to the feed wheel 1 offset left and right of the feed wheel 1 arranged bearing structures, one of which forms the housing 3 and the other one firmly inserted in the housing 3 and therefore also designated 3 insert.
  • the bearing profile 11 extends through these two left and right of the impeller 1 arranged bearing structures 3.
  • the bearing profile 11 forms with each of these two bearing structures 3 a sliding bearing.
  • the bearing profile 11 has at its outer periphery per slide bearing a bearing surface 11 a.
  • the bearing structures 3 each form a bearing counter surface 3 a, which surrounds the respective associated bearing surface 11 a circumferentially to form a narrow bearing gap.
  • the two bearing gaps formed between the bearing profile 11 and the bearing structures 3 are supplied to lubricate the rotary bearing in a first embodiment with raw fluid of the high pressure side as a lubricant. In a further development, these two bearing gaps are also lubricated with the clean fluid.
  • the bearing profile 11 of the embodiment is formed as a full shaft, but may also be in a development instead also a hollow shaft with a hollow cross-section which extends over at least a major part of the axial length of the bearing profile 11.
  • the raw fluid or alternatively the pure fluid can be guided through the hollow shaft from the inside into the two bearing gaps.
  • the specific delivery volume of the pump is adjustable, wherein the pump automatically stops when reaching a limit speed, which is determined by the spring member 12 or a control of the pressure in the space containing the spring member 12, so that the delivery rate of the pump Actual demand of the unit to be supplied 17 or possibly sets several units accordingly.
  • the feed wheel 2 as the feed wheel 1 can be fixed in the axial direction.
  • the pistons 8 and 9 would be immobile in such embodiments relative to the housing 3 in the in FIG. 2 arranged axial position, so would be firmly connected to the housing 3 or preferably formed in one piece with the housing 3, namely each with one of a plurality of assembled housing parts, such as a main body and a lid.
  • the spring member 12 would be omitted, and the fluid space 7 could be used as a narrow portion of Be formed lubricant channel, similar to the channel section 8a.
  • the pistons 8 and 9 would in such an embodiment bearing structures comparable to the bearing structures 3, but with the difference that they would preferably each immovably connected to the bearing profile 10. Otherwise, the simplified pump would correspond to the embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Rotary Pumps (AREA)
EP10161304A 2009-04-29 2010-04-28 Pompe à engranage externe dotée d'une lubrification de palier améliorée Withdrawn EP2249039A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910019418 DE102009019418B4 (de) 2009-04-29 2009-04-29 Umlaufverdrängerpumpe mit verbesserter Lagerschmierung

Publications (2)

Publication Number Publication Date
EP2249039A2 true EP2249039A2 (fr) 2010-11-10
EP2249039A3 EP2249039A3 (fr) 2013-01-02

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Application Number Title Priority Date Filing Date
EP10161304A Withdrawn EP2249039A3 (fr) 2009-04-29 2010-04-28 Pompe à engranage externe dotée d'une lubrification de palier améliorée

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DE102013202917A1 (de) * 2013-02-22 2014-08-28 Robert Bosch Gmbh Zahnradmaschine mit erhöhter Partikelrobustheit
DE102016107447A1 (de) * 2016-04-21 2017-11-09 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit Schmiernut im Dichtsteg
CN110185609B (zh) * 2019-06-18 2024-04-16 江苏德华泵业有限公司 一种高压齿轮污水泵

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