EP3236074B1 - Pompe rotative comprenant une rainure de graissage dans une nervure d'étanchéité - Google Patents

Pompe rotative comprenant une rainure de graissage dans une nervure d'étanchéité Download PDF

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Publication number
EP3236074B1
EP3236074B1 EP17167286.8A EP17167286A EP3236074B1 EP 3236074 B1 EP3236074 B1 EP 3236074B1 EP 17167286 A EP17167286 A EP 17167286A EP 3236074 B1 EP3236074 B1 EP 3236074B1
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EP
European Patent Office
Prior art keywords
pump
rotor
bearing
rotary
rotary 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.)
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Application number
EP17167286.8A
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German (de)
English (en)
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EP3236074A1 (fr
Inventor
Michael Ehringer
Sven Peters
Gerd Jäggle
Thomas Wahl
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
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Schwaebische Huettenwerke Automotive GmbH
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Publication of EP3236074A1 publication Critical patent/EP3236074A1/fr
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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
    • 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
    • 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
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members

Definitions

  • the invention relates to a rotary pump with a housing that has a pump chamber with an inlet for a medium to be pumped into a low-pressure region of the pump chamber and an outlet for the medium to be pumped from a high-pressure region of the pump chamber.
  • the pump further includes at least one rotor and a bearing for the rotor.
  • the pump comprises a sealing web which faces the rotor axially and which separates the low-pressure region from the high-pressure region in the direction of rotation of the rotor, and a lubricant supply which supplies a lubricant from the pump chamber to the bearing.
  • the lubricant supply is formed in the sealing web, in particular in an area of greatest tooth engagement of the rotor.
  • the bearing of a pump is supplied with lubricant via the high pressure area or an external pressure reservoir.
  • the bearing lubrication is generally dependent on the direction of rotation of the pump, so that when the direction of rotation is reversed, the bearing is connected to the low-pressure area of the pump and is therefore no longer supplied with lubricant.
  • US 2005/064976 A1 a rotary pump in which a bearing of the driven rotor is supplied with lubricating fluid via a channel directly from the high-pressure side of the pump outside the delivery chamber.
  • Supplying a rotor bearing of a rotary pump via a supply line outside the delivery chamber is also possible CN 203 570 583 U known.
  • they show US 3,904,333 and the US 4,927,343 A Rotary pumps that use pressurized fluid to press pressure plates axially against the end faces of the rotor to seal the delivery chamber.
  • a rotary pump with a direction-independent and targeted lubricant supply for a bearing of the rotor should be provided.
  • One aspect of the invention relates to a rotary pump with a switchable direction of rotation, with a housing that has a pump chamber with an inlet for a medium to be pumped into a low-pressure region of the pump chamber and an outlet for the medium to be pumped from a high-pressure region of the pump chamber, at least one rotor, at least one plain bearing, for the at least one rotor, at least one sealing web facing the rotor axially, which separates the low-pressure region from the high-pressure region in the direction of rotation of the rotor, and a lubricant supply which is independent of the direction of rotation and which supplies a lubricant from the pump chamber to at least the bearing, the lubricant supply being in the sealing web , in particular in an area of greatest tooth engagement of the rotor.
  • the rotary pump is an internal axis pump, such as a rotary piston pump, a vane pump, an internal gear pump or another internal axis pump known in the art.
  • the housing may include one or more parts, for example one or more lids, to close openings. Parts of the housing can form part of the pump chamber, for example an axial cover for the pump chamber or a peripheral wall or a cup-shaped structure for receiving the at least one rotor.
  • the rotor may be connected or coupled to a drive, such as an electric motor or a shaft driven by an internal combustion engine, which generates the driving energy for the rotor.
  • the rotor is preferably connected to an electric motor and is intended in particular for use in a motor vehicle. If the motor vehicle has an internal combustion engine as a drive, the rotary pump can be driven by the electric motor, preferably independently of the internal combustion engine, for example when the internal combustion engine is at a standstill.
  • the rotary pump advantageously has the electric motor.
  • the rotary pump is preferably designed as an electric rotary pump.
  • the rotary pump is preferably designed as an auxiliary pump and/or an additional pump to support and/or at least partially replace a main or primary pump in a lubricant and/or coolant system of the motor vehicle. “Provided” is intended to mean, in particular, specifically designed, designed, executed, arranged and/or programmed.
  • the direction of rotation of the rotary pump can be switched so that the pump can be used flexibly.
  • the outlet of the pump that rotates in the first direction of rotation becomes the inlet for the same pump that now rotates in the second direction of rotation.
  • the inlet of the pump which after a change in the direction of rotation of the pump outlet becomes.
  • the inlet opens into a low-pressure area and the outlet opens into a high-pressure area of the pump. Switching the direction of rotation of the pump thus changes the flow direction of the medium to be pumped through the pump, which in other words is a reversible rotary pump.
  • the medium to be pumped can in particular be a lubricant and/or coolant, such as a lubricating and/or cooling oil, which is supplied to one or more units from the high-pressure side of the pump via hoses, channels or lines to the units to lubricate and/or cool.
  • a lubricant and/or coolant such as a lubricating and/or cooling oil
  • it can also be a medium for another purpose, for example heating oil, heavy oil or diesel, which is also used to lubricate the rotor bearing.
  • the low-pressure side of the pump can be fluidly connected to a reservoir for the medium to be pumped.
  • the rotary pump preferably has at least two sealing webs facing axially towards the rotor, each of which separates the low-pressure region from the high-pressure region in the direction of rotation of the rotor.
  • the sealing webs are arranged between the inlet and the outlet, viewed along the direction of rotation.
  • the sealing webs are preferably arranged opposite each other.
  • One of the sealing webs is formed in the area of greatest tooth engagement of the rotor and is also referred to as the drive web.
  • the other sealing web is formed in an area of the smallest tooth meshing of the rotor or in an area of a missing tooth meshing of the rotor.
  • the lubricant supply is preferably formed in the so-called drive web and thus in the sealing web in the area of greatest tooth engagement of the rotor.
  • the lubricant supply is additionally or alternatively formed in the sealing web in the area of the smallest tooth meshing of the rotor or in the area of the missing tooth meshing of the rotor.
  • the sealing webs each have an extension directed in the direction of rotation, which are preferably different from one another.
  • the sealing web in the area of the greatest tooth engagement of the rotor has an extent directed in the direction of rotation, which is preferably smaller than the extent of the sealing web in the area of the smallest tooth engagement of the rotor or in the area of the missing tooth engagement of the rotor.
  • the lubricant supply is preferably suitable for reliably supplying the bearing of the rotor with lubricant regardless of the direction of rotation of the pump.
  • the lubricant supply feeds the medium to be pumped preferably from at least one closed working chamber, which is delimited in the direction of rotation by the at least one rotor, to the bearing.
  • the medium to be pumped is passed through the Rotation of the at least one rotor is transported from the low pressure area to the high pressure area.
  • the volume of the working chamber changes with the rotation of at least one rotor.
  • the working chambers are limited and/or closed in the direction of rotation by the teeth of the rotors.
  • the lubricant supply feeds a medium squeezed by the reduction in the size of the working chamber or a medium to be pumped under squeezing pressure from the closed working chamber to the bearing.
  • the lubricant supply in gear pumps is arranged in the area of tooth engagement in which squeezing pressures can occur that are independent of the direction of rotation. Squeezing pressures arise in particular because the closed working chambers for the medium on the pressure side formed by the rotating rotor are closed again before they are completely emptied through the outlet. The remaining medium is then further compacted.
  • the medium to be pumped under squeezing pressure can be diverted via the lubricant supply, so that the provision of the relief bores is no longer necessary.
  • the squeezing pressures occurring in the pump can advantageously be used to guide the lubricant under squeezing pressure specifically to the bearing and use it there to lubricate the bearing. Eliminating the need for holes to return the medium from the squeezing area can contribute to lower manufacturing costs.
  • the inlet and the outlet can be arranged symmetrically or asymmetrically to one another. Due to the symmetrical arrangement of the inlet and outlet, the geometry of the pump is identical in both directions of rotation in relation to the inlets and outlets.
  • the inlet and outlet are at least substantially the same shape.
  • the lubricant supply is arranged centrally in the sealing web. When arranged centrally, the lubricant supply is at least substantially the same distance from a nearest edge of the mutually facing ends of the outlet and the inlet. Due to the central or central arrangement, the geometry of the pump is identical in both directions of rotation in relation to the lubricant supply.
  • the inlet and the outlet are kidney-shaped.
  • the lubricant supply is arranged off-center in the sealing web. This can make sense if the rotary pump has a preferred first and a less preferred second direction of rotation.
  • the off-center lubricant supply is preferably arranged closer to the outlet for the medium to be pumped provided for the preferred direction of rotation.
  • the off-center arrangement of the lubricant supply is advantageous because, in main operation in the preferred direction of rotation, a distance between the lubricant supply and the outlet is smaller than in the central arrangement, which, with additional security, prevents the lubricant supply from being short-circuited with the inlet .
  • the lubricant supply is a groove in the sealing web.
  • the groove or channel can be rectangular, U- or V-shaped or of any design in a section transverse to its longitudinal axis.
  • a width and a length of the groove or channel can be adapted to the rotary pump.
  • the groove or channel can be funnel-shaped at its end facing the bearing and/or away from the bearing.
  • the long sides of the groove or channel can run parallel to one another or can be inclined towards or away from each other in the direction of the bearing, so that a width of the groove or channel changes continuously over the length.
  • the same can apply to the depth of the groove or channel.
  • the shape such as length, width and depth of the groove or channel is not fixed, but can be freely chosen by the expert.
  • the groove or channel advantageously has a width, i.e. an extension oriented in the direction of rotation, of at least 0.5 mm and particularly advantageously of at least 1 mm.
  • the groove or channel preferably has a width, i.e. an extent oriented in the direction of rotation, between 0.5 mm and 3 mm and particularly advantageously between 1 mm and 1.5 mm.
  • a groove or a channel can also divide in a delta manner, so that the groove or the channel comprises several arms at at least one of its ends.
  • the groove or channel does not have to form a straight line, but can be curved, for example.
  • the groove or channel can have at least one throttle path, in particular arranged centrally with respect to a main extent of the groove or channel, which is characterized in particular by a smaller flow cross section compared to the start and end of the groove or the start of the channel and the end of the channel.
  • the lubricant supply can comprise a pocket in the sealing web.
  • the pocket can end directly on the bearing or be connected to the bearing via a groove or channel.
  • the bag can be round, oval, rectangular, funnel-shaped or any shape in length, width and depth.
  • the lubricant supply cannot be short-circuited in any position of the rotor with the inlet into or the outlet from the pump room. This avoids that when the lubricant supply is directly connected to the outlet or high-pressure area of the pump, too much lubricant is pressed into the lubricant supply and that, despite the lubricant supply, squeezing pressures occur in the area of greatest tooth engagement of the pump.
  • a short circuit to the inlet or suction side of the pump can reduce, stop or even reverse flow of lubricant through the lubricant supply to the bearing, which could result in an undersupply of lubricant to the bearing. The result could be damage or even destruction of the rotary pump.
  • An imaginary extension of the groove or channel or an axial central axis (longitudinal axis) of the groove or channel can intersect a rotation axis of the rotor or a straight line that runs parallel to the rotation axis of the pump.
  • the imaginary extension of the groove or channel can impinge perpendicularly on a circumferential outer surface of the bearing at least at one point or at an angle that can be specified in the design.
  • the imaginary extension of the groove or channel viewed in a cross section of the rotary pump that is orthogonal to the axis of rotation of the at least one rotor, is oriented parallel to an eccentric line.
  • the imaginary extension or the central axis of the groove or channel in the cross section lies particularly advantageously on the eccentric line, in particular if the inlet and the outlet are arranged or designed asymmetrically to one another.
  • An “eccentric line” is to be understood in particular as a straight line which, viewed in the cross section of the rotary pump, connects a center point of the rotor and a center point of the pump chamber or which connects the axis of rotation of an inner rotor and the axis of rotation of an outer rotor of the rotary pump.
  • the lubricant supply extends from the bearing to between the inlet and the outlet.
  • the lubricant supply preferably extends radially from the bearing at least up to a root circle diameter of one of the gears, for example at least up to a root circle diameter furthest radially from the bearing.
  • the lubricant supply preferably extends radially from the bearing at least to a root diameter of an external gear and thus at least to the root diameter furthest radially from the bearing.
  • the end of the lubricant supply facing the bearing can be open, the end of the groove-shaped lubricant supply without a pocket facing away from the bearing can be closed.
  • the lubricant supply can open into the bearing at its end facing the bearing, so that lubricant from the lubricant supply reaches the bearing directly.
  • the bearing can in particular be an annular gap extending around a drive shaft of the at least one rotor.
  • the lubricant supply can extend from the bearing to close to the point of deepest tooth engagement, whereby the medium to be pumped under squeezing pressure can be supplied to the bearing essentially completely via the lubricant supply.
  • the sealing web can be wider than in comparable rotary pumps in the prior art, which can increase the lubricating pressure and/or improve the seal compared to the inlet into and/or outlet from the pump chamber.
  • the pump chamber is usually delimited at its axial ends by a cover and a base.
  • the inlet, the outlet, the sealing web and the lubricant supply can optionally be formed in the cover or in the bottom of the pump room or both in the cover and in the bottom of the pump room.
  • the rotary pump can have two inlets into the low-pressure area of the pump room, two outlets from the high-pressure area of the pump room, two sealing webs facing the rotor axially, in particular drive webs, which separate the low-pressure area from the high-pressure area in the direction of rotation of the rotor, and one in each of the two sealing webs Lubricant supply, especially in the area of greatest tooth engagement of the rotor.
  • the two axially opposite lubricant feeds and thus the lubricant feed introduced in the base and the lubricant feed introduced in the cover can differ in shape, depth, length, width and / or the like. Furthermore, the two axially opposite lubricant feeds can be oriented offset and/or twisted relative to one another with respect to the direction of rotation. In principle, it is conceivable that one of the lubricant feeds is arranged off-center and closer to the outlet for the medium to be pumped, which is provided for the preferred direction of rotation, and the axially opposite lubricant feed is arranged off-center and closer to the inlet for the medium to be pumped, which is provided for the preferred direction of rotation is arranged.
  • the axially opposite lubricant feeds can differ from one another, for example in the size of their groove or channel.
  • the rotary pump or the lubricant and/or coolant system having the rotary pump has at least one check valve which is located between the pump chamber and a lubricant and/or coolant reservoir from which the rotary pump sucks in a lubricant and/or coolant in at least one operating state. is arranged.
  • the check valve advantageously blocks a flow from the pump room into the lubricant and/or coolant reservoir and allows a flow from the lubricant and/or coolant reservoir into the pump room.
  • the rotary pump or the lubricant and/or coolant system has at least one branch which is arranged between the pump chamber and the lubricant and/or coolant reservoir. It is advantageous if the check valve is arranged between the branch and the lubricant and/or coolant reservoir.
  • the rotary pump is advantageously at least partially immersed in the lubricant and/or coolant in the lubricant and/or coolant reservoir and/or is at least partially arranged below a lubricant and/or coolant level.
  • the rotary pump can be arranged above the lubricant and/or coolant level and is not immersed in the lubricant and/or coolant.
  • the rotary pump or the lubricant and/or coolant system having the rotary pump has the check valve in order to prevent the pump chamber from running empty.
  • the check valve can ensure that the pump chamber is always filled with the lubricant and/or coolant and that the lubricant supply is ensured via the lubricant supply, especially when the rotary pump is arranged above the lubricant and/or coolant level.
  • the check valve is preferably designed as a check valve.
  • the rotary pump additionally has a lubricant drain that drains a lubricant from the bearing.
  • the lubricant drain can connect the bearing to the inlet or outlet.
  • the lubricant discharge has at least one groove or channel which runs from the bearing to the inlet or outlet.
  • the lubricant discharge is advantageously formed in the base and/or the lid.
  • the lubricant discharge has, at least in a partial section, a compared to the Lubricant supply has a smaller flow cross section and/or includes a throttle point, for example in the form of a constriction.
  • the Figure 1 shows a rotary pump 1 of a motor vehicle.
  • the rotary pump 1 is designed as an internal gear, internal gear ring or gerotor pump.
  • the rotary pump 1 can be switched in its conveying direction or direction of rotation D during operation.
  • the rotary pump 1 has a rotor set which has a rotor 10 designed as an external gear and a rotor 11 designed as an internal gear, which are arranged eccentrically to one another.
  • the rotor 10 can serve as a stator in which the rotor 11 is arranged eccentrically.
  • the rotor 10 can also rotate, for example be rotated by the rotor 11.
  • the designations rotor 10 and rotor 11 are therefore retained for the description.
  • the two rotors 10 and 11 together form a pump chamber 7, which is filled with a medium to be pumped and in which the medium is compressed on the way from the inlet to the outlet.
  • the rotors 10, 11 delimit or form, viewed in the direction of rotation D, several working chambers in which the medium to be pumped is transported.
  • the rotors 10, 11 divide the pump chamber 7 into several working chambers, the volume of which changes when the rotors 10, 11 rotate.
  • the rotary pump 1 For driving, the rotary pump 1 has an electric motor, not shown, which is connected to the rotor 11 in terms of drive technology.
  • the electric motor is intended to drive the rotor 11 in both directions of rotation D.
  • the rotary pump is designed as an auxiliary pump and/or an additional pump to support and/or at least partially replace a main or primary pump of the motor vehicle.
  • the rotary pump 1 is arranged in a lubricant and/or coolant system of the motor vehicle.
  • the rotary pump 1 has one in the Figure 1 housing 2, not shown, which can form a bottom of the pump room 7, with an inlet or outlet 4, an outlet or inlet 3, a bearing 5 for the rotor 11 and two between the inlet or outlet 4 and sealing webs 8 and 9 formed at the outlet and inlet 3 (see also Fig. 2 ).
  • the inlets and outlets 3, 4 change their function.
  • the inlet or outlet 4 is designed as an inlet and the outlet or inlet 3 is designed as an outlet.
  • the inlet or outlet 4 is designed as an outlet and the outlet or inlet 3 is designed as an inlet.
  • the inlet or outlet 4 is referred to below as inlet 4 and the outlet or inlet 3 as outlet 3.
  • the inlet 4 and the outlet 3 are designed symmetrically to one another.
  • a lubricating groove is introduced in the sealing web 9, which forms a lubricant supply 6 with which squeeze oil is passed as lubricant from the pump chamber 7 to the bearing 5 of the rotor 11.
  • the lubricant supply 6 supplies squeeze oil from one of the working chambers to the bearing 5 of the rotor 11.
  • the lubricant supply 6 and thus the lubricating groove is formed in the area of greatest tooth engagement of the rotors 10, 11, that is to say in the area in which a tooth of the rotor 11 essentially completely engages in an area between two teeth of the rotor 10.
  • the lubricant supply 6 is fed with a residual medium that has not been displaced through the outlet 3 and is subjected to a squeezing pressure as the rotor 11 continues to rotate. Since the medium under squeezing pressure can negatively influence the performance of the rotary pump 1 and accelerate wear of the rotary pump 1, an attempt is made to avoid the occurrence of such squeezing pressures by draining the remaining medium in pumps from the prior art, for example via bores in the rotor 10, 11 is displaced back into the pump room 7 or the inlet 4. In the exemplary embodiment of the invention, this advantageous discharge of the medium under squeezing pressure takes place via the lubricant supply 6 and the medium is used to lubricate the bearing 5 of the rotor 11.
  • the lubricant supply 6 is arranged centrally in the sealing web 9, that is, a distance from the lubricant supply 6 to the outlet 3, which connects a high-pressure side of the rotary pump 1 with, for example, lines, and a distance from the inlet 4, which is the low-pressure side of the rotary pump 1 is assigned are identical or essentially identical.
  • the lubricant supply 6 has no fluidic connection to either the outlet 3 or the inlet 4.
  • the central arrangement of the lubricant supply 6 in the sealing web 9 has the advantage that regardless of the direction of rotation of the rotary pump 1 and thus the rotors 10, 11, the lubricant supply 6 is reliably supplied with lubricant from the pump chamber 7.
  • sealing web 9 is wider than in pumps of the prior art, that is, a distance between the edges of the inlet 4 and the outlet 3 that face one another and define a minimum width of the sealing web 9 is chosen to be larger than in comparable pumps without the lubricant supply 6.
  • the lubricant supply 6 is open at its ends assigned to the bearing 5 and opens on an outer surface of the bearing 5. From there it extends radially outwards into the sealing web 9 and ends in an area of the sealing web 9 which is between the inlet 4 and the Outlet 3 is located.
  • the lubricant supply 6 is formed as a depression in the bottom of the pump chamber 7.
  • the further sealing web 8 also has the same function, namely to prevent a direct fluidic connection between the inlet 4 and outlet 3, whereby in the area of the sealing web 8, in contrast to the sealing web 9, there is no or minimal tooth engagement between the internal gear 11 and the external gear 10 is.
  • the medium to be pumped can be, for example, an oil, a heavy oil, diesel or another medium that has sufficient lubricating properties to reliably lubricate the bearing 5 of the rotor 10.
  • This exemplary embodiment is lubricating oil for lubricating and/or cooling motor vehicle components.
  • the rotor 11 can be rotationally driven and can only be rotated relative to the housing 2 and optionally adjusted linearly along the axis of rotation R. That means, the axis of rotation R of the rotary pump 1 of the exemplary embodiment does not change its position relative to the housing 2.
  • the rotary pump 1 also has a bearing for supporting the rotor 10.
  • the lubricant supply 6 can supply the bearing of the rotor 10 with the squeeze oil for lubrication as an alternative or in addition to supplying the bearing 5 with lubricating oil.
  • the lubrication groove can be extended radially outwards and supply both bearings with squeeze oil.
  • an additional, in particular parallel, lubrication groove can be introduced, which supplies the bearing of the rotor 10 with squeeze oil.
  • the lubrication grooves can remove the squeeze oil from the same working chamber or from two different working chambers.
  • FIG. 3 a rotary pump 1 of a second exemplary embodiment is shown, wherein the Figure 3 a look into a housing 2 of the rotary pump 1 shows.
  • the housing 2 has an inner side wall which can form a bottom of a pump chamber 7, with an inlet 4, an outlet 3, a bearing 5 for a rotor 11 and two sealing webs 8 and 9 formed between the inlet 4 and the outlet 3.
  • a lubricating groove is introduced into the sealing web 9, which forms a lubricant supply 6 with which squeeze oil is passed as lubricant from the pump chamber 7 to the bearing 5 of the rotor 11.
  • the inlet 4 and the outlet 3 are designed asymmetrically.
  • the lubricant supply 6 is arranged off-center in the sealing web 9, that is, a distance between the lubricant supply 6 and the outlet 3 provided for a preferred direction of rotation D bev , which connects a high-pressure side of the rotary pump 1 with, for example, lines, is smaller than a distance to the inlet 4 provided for the preferred direction of rotation D bev , which is assigned to the low-pressure side of the rotary pump 1.
  • the off-center arrangement of the lubricant supply 6 in the sealing web 9 is particularly advantageous if the rotary pump 1 has a preferred direction of rotation D bev .
  • the arrangement of the lubricant supply 6 increases the area of the sealing web 9, which seals the lubricant supply 6 from the low-pressure side or the inlet 4, so that it is reliably avoided that the lubricant flows out through a fluidic connection between the lubricant supply 6 and the inlet 4 the lubricant guide 6 is sucked out again.
  • the axial longitudinal axis L of the lubricant supply 6 lies on a straight eccentric line, which connects a rotation axis of the rotor 10 and a rotation axis of the rotor 11 to one another in a cross section of the rotary pump 1.
  • the longitudinal axis L of the lubricant supply 6 corresponds to the eccentric straight line
  • the longitudinal axis L of the lubricant supply 6 can, in modifications, also extend at a distance parallel to the eccentric straight line.
  • the longitudinal axis L can, in further modifications, be extended at an acute angle of preferably less than 20° to the eccentric straight line and intersect the axis of rotation of the rotor 10 and/or the axis of rotation of the rotor 11 or cross them at a distance.
  • the lubricant supply 6 can also be different than in the Figures 3, 4 , 5 shown, be arranged off-center and closer to the inlet 4 provided for the preferred direction of rotation D bev in the sealing web 9 in order to reliably prevent a fluidic connection of the outlet 3 provided for the preferred direction of rotation D bev with the lubricant supply 6.
  • This can be advantageous, for example, in rotary pumps 1 with a high outlet pressure, in order to reliably prevent the high-pressure medium from being pressed into the lubricant supply 6 before the outlet 3 of the rotary pump 1 is completely closed.
  • the area of the sealing web 9 is also shown in an enlarged view.
  • a rotary pump 1 is shown in a third exemplary embodiment.
  • the inlet 4 and the outlet 3 are designed asymmetrically.
  • the lubricant supply 6 is arranged centrally in the sealing web 9, so it has essentially identical distances from the inlet 4 and the outlet 3.
  • the rotary pump 1 therefore has inlets and outlets 3, 4 which are asymmetrically designed with respect to one another, but a centrally arranged lubricant supply 6.

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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)

Claims (14)

  1. Pompe rotative (1) à direction de rotation commutable, comprenant :
    a) un boîtier (2) comprenant un espace de pompe (7) comportant une entrée (4) dans une zone basse pression de l'espace de pompe (7) pour un milieu à pomper et une sortie (3) depuis une zone haute pression de l'espace de pompe (7) pour le milieu à pomper ;
    b) au moins un rotor (10, 11) ;
    c) au moins un palier (5) pour ledit au moins un rotor (10, 11) ;
    d) au moins un pont d'étanchéité (8, 9) faisant face axialement au rotor (10, 11) et séparant la zone basse pression de la zone haute pression en direction de rotation (D) du rotor (10, 11) ;
    e) et une alimentation en lubrifiant (6) alimentant un lubrifiant depuis l'espace de pompe (7) au moins vers le palier (5),
    f) l'alimentation en lubrifiant (6) étant formée dans le pont d'étanchéité (9),
    g) la pompe rotative (1) étant une pompe à axe intérieur, telle qu'une pompe à piston rotatif, une pompe à ailettes, une pompe à engrenage intérieur ou une autre pompe à axe intérieur,
    h) ledit au moins un palier (5) étant un palier de glissement,
    caractérisée en ce que
    i) l'alimentation en lubrifiant (6) est une rainure dans le pont d'étanchéité, et
    j) le pont d'étanchéité (9) est formé entre l'entrée (4) et la sortie (3) en direction de rotation (D) du rotor (10, 11), et l'alimentation en lubrifiant (6) s'étend depuis le palier (5) au moins jusqu'à entre l'entrée (4) et la sortie (3).
  2. Pompe rotative selon la revendication 1, dans laquelle l'alimentation en lubrifiant (6) alimente le milieu à pomper depuis au moins une chambre de travail fermée, qui est limitée en direction de rotation (D) par ledit au moins un rotor (10, 11), au moins vers le palier (5).
  3. Pompe rotative selon la revendication 1, dans laquelle en cas de pompes à engrenage l'alimentation en lubrifiant (6) dans le pont d'étanchéité (9) est formée dans une zone d'un engrènement maximal du rotor (10 ; 11).
  4. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle l'entrée (4) et la sortie (3) sont réalisées symétriquement l'une par rapport à l'autre.
  5. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle l'alimentation en lubrifiant (6) est disposée de manière centrique dans le pont d'étanchéité (9).
  6. Pompe rotative selon l'une quelconque des revendications 1 à 4, dans laquelle l'alimentation en lubrifiant (6) est disposée de manière excentrique dans le pont d'étanchéité (9), de préférence plus proche de la sortie (3) prévue pour une direction de rotation préférée (Dpréf) pour le milieu à pomper.
  7. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle l'alimentation en lubrifiant (6) comprend au moins une poche dans le pont d'étanchéité (9), la poche étant reliée au palier (5) directement ou via une rainure ou un canal.
  8. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle l'alimentation en lubrifiant (6) n'est en court-circuit dans aucune position du rotor (10, 11) avec l'entrée (4) dans l'espace de pompe (7) ou avec la sortie (3) depuis l'espace de pompe (7).
  9. Pompe rotative selon l'une quelconque des revendications 6 à 8, dans laquelle un prolongement imaginaire de la rainure ou du canal croise un axe de rotation (R) ou un axe parallèle à l'axe de rotation (R) de la pompe (1).
  10. Pompe rotative selon l'une quelconque des revendications 6 à 9, dans laquelle un prolongement imaginaire de la rainure ou du canal est disposé sur une ligne droite excentrique reliant un centre de l'espace de pompe (7) et l'axe de rotation (R) dudit au moins un rotor (11) l'un à l'autre.
  11. Pompe rotative selon l'une quelconque des revendications précédentes, caractérisée par une réalisation en tant que pompe à engrenage, l'alimentation en lubrifiant (6) s'étendant depuis le palier (5) au moins jusqu'à un diamètre de cercle de pied d'un des engrenages, de préférence au moins jusqu'à un diamètre de cercle de pied le plus éloigné radialement du palier (5).
  12. Pompe rotative selon l'une quelconque des revendications précédentes, dans laquelle l'espace de pompe (7) comprend un couvercle axial et une base axiale, et l'entrée (4), la sortie (3), le pont d'étanchéité (9) et l'alimentation en lubrifiant (6) sont formés dans le couvercle axial et / ou dans la base axiale de l'espace de pompe (7).
  13. Pompe rotative selon l'une quelconque des revendications précédentes, caractérisée par un moteur électrique prévu pour l'entraînement.
  14. Pompe rotative selon l'une quelconque des revendications précédentes, caractérisée par une réalisation en tant que pompe auxiliaire et / ou en pompe supplémentaire pour soutenir et / ou remplacer au moins partiellement une pompe principale dans un système de lubrifiant et / ou de réfrigérant d'un véhicule automobile.
EP17167286.8A 2016-04-21 2017-04-20 Pompe rotative comprenant une rainure de graissage dans une nervure d'étanchéité Active EP3236074B1 (fr)

Applications Claiming Priority (1)

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DE102016107447.0A DE102016107447A1 (de) 2016-04-21 2016-04-21 Rotationspumpe mit Schmiernut im Dichtsteg

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US (1) US10578101B2 (fr)
EP (1) EP3236074B1 (fr)
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MX2019002487A (es) 2016-09-02 2019-07-01 Stackpole Int Engineered Products Ltd Sistema de bomba de entrada dual.
DE102017126900A1 (de) 2017-11-15 2019-05-16 Schwäbische Hüttenwerke Automotive GmbH Rückschlagventil
US10895257B2 (en) * 2018-02-13 2021-01-19 GM Global Technology Operations LLC Lubrication strategy for dry run pump system
DE102018105121A1 (de) * 2018-03-06 2019-09-12 Schwäbische Hüttenwerke Automotive GmbH Unterstützungstaschen
DE102018107695A1 (de) * 2018-03-29 2019-10-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe
DE102018123909B4 (de) * 2018-09-27 2020-06-10 Nidec Gpm Gmbh Kompakt-Gleitlager mit Dichtungsanordnung und Wasserpumpe mit demselben
DE102018133680A1 (de) 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit

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CN203570583U (zh) * 2013-11-06 2014-04-30 宁波布赫懋鑫液压技术有限公司 直线共轭内啮合齿轮泵的回油装置

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DE102016107447A1 (de) 2017-11-09
EP3236074A1 (fr) 2017-10-25
CN107304765B (zh) 2020-09-22
CN107304765A (zh) 2017-10-31
US10578101B2 (en) 2020-03-03
US20170306950A1 (en) 2017-10-26

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