EP4185773B1 - Machine à fluide à engrenage interne - Google Patents

Machine à fluide à engrenage interne

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Publication number
EP4185773B1
EP4185773B1 EP21746687.9A EP21746687A EP4185773B1 EP 4185773 B1 EP4185773 B1 EP 4185773B1 EP 21746687 A EP21746687 A EP 21746687A EP 4185773 B1 EP4185773 B1 EP 4185773B1
Authority
EP
European Patent Office
Prior art keywords
fluid
internal gear
connection
flow
gear
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.)
Active
Application number
EP21746687.9A
Other languages
German (de)
English (en)
Other versions
EP4185773A1 (fr
Inventor
Alexander Goss
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.)
Eckerle Technologies GmbH
Original Assignee
Eckerle Technologies 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 Eckerle Technologies GmbH filed Critical Eckerle Technologies GmbH
Publication of EP4185773A1 publication Critical patent/EP4185773A1/fr
Application granted granted Critical
Publication of EP4185773B1 publication Critical patent/EP4185773B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/54—Hydrostatic or hydrodynamic bearing assemblies specially adapted for rotary positive displacement pumps or compressors

Definitions

  • the invention relates to an internal gear fluid machine with a first gear having external teeth and mounted for rotation about a first axis of rotation, and a second gear having internal teeth that mesh with the external teeth in an engagement region and that are mounted for rotation about a second axis of rotation different from the first axis of rotation, wherein a filler piece is arranged between the first gear and the second gear, away from the engagement region, which filler piece bears on the one hand against the external teeth and on the other hand against the internal teeth in order to divide a fluid space present between the first gear and the second gear into a first fluid chamber and a second fluid chamber, and wherein housing walls of a machine housing of the internal gear fluid machine are arranged on both sides of the first gear and the second gear in the axial direction with respect to the first axis of rotation.
  • the state of the art includes, for example, the publication DE 199 30 911 C1
  • the filling comprises two identical filling pieces; a stop pin is provided, which is mounted in the housing and against which the filling pieces are supported with their end faces.
  • Axial disks are provided on both sides of the pinion.
  • An axial pressure field is provided between the outer side of each axial disk and the corresponding housing wall, and a control field is provided between the inner side of each axial disk and the pinion. At least one control slot is connected to each control field, which tapers towards its free end.
  • a reversibly operable gear machine comprising a housing in which two gears are arranged.
  • a first bearing chamber and a second bearing chamber are provided, wherein in a first operating direction of the gear machine the first bearing chamber and in an opposite second operating direction
  • the second bearing chamber is pressurized with hydraulic fluid and forms a hydrostatic bearing for a gear.
  • a vehicle steering system comprising a hydraulic circuit, a hydraulic cylinder, and a gear machine that operates as a pump and pressurizes a first working chamber of the hydraulic cylinder in its first operating direction and a second working chamber of the hydraulic cylinder in its second operating direction.
  • the printed matter DE 10 2009 024216 A1 discloses an internal gear fluid machine with plain bearings.
  • the object of the invention is to propose an internal gear fluid machine which has advantages over known internal gear fluid machines, in particular enabling higher efficiency due to a particularly effective bearing of the gears in the machine housing with, at the same time, low fluid loss.
  • the second gear is at least partially encompassed in the circumferential direction by at least one bearing recess formed in the machine housing to form a hydrostatic bearing, which only partially overlaps the second gear in the axial direction and is fluidly connected to a fluid connection of the internal gear fluid machine via a fluid line having a flow resistance.
  • the internal gear fluid machine is a fluid conveying device and is used to convey a fluid, for example a liquid or a gas.
  • the internal gear fluid machine has two gears, namely the first gear and the second gear.
  • the first gear can also be referred to as a pinion and the second gear as a ring gear.
  • the pinion has the external toothing and the ring gear has the internal toothing. Viewed in the circumferential direction, the external toothing and the internal toothing engage with each other in some areas, i.e. they mesh with each other in some areas, namely in the engagement region.
  • the two gears are intended for fluid conveyance and are therefore designed such that they interact during a rotary movement to convey the fluid and in doing so engage or mesh with each other.
  • the first gear is preferably coupled to an input shaft or drive shaft of the internal gear fluid machine, preferably rigidly and/or detachably or permanently.
  • detachable coupling for example, there is a pinion that is plugged onto the drive shaft and can be removed from it without damage.
  • the plug-in pinion has internal teeth that interact with external teeth on the input shaft to drive the plug-in pinion to the input shaft.
  • the first gear is rotatably mounted in a machine housing of the internal gear fluid machine by means of the input shaft.
  • the first gear is arranged on the input shaft so that it always has the same speed as the input shaft during operation of the internal gear fluid machine.
  • Both the first gear and the second gear are arranged in the machine housing and are rotatably mounted therein.
  • the first gear is rotatably mounted about the first axis of rotation
  • the second gear is rotatably mounted about the second axis of rotation.
  • the first axis of rotation can also be referred to as the pinion axis of rotation and the second axis of rotation as the ring gear axis of rotation.
  • the first gear is arranged in the second gear in such a way that the external teeth of the first gear mesh with or are in engagement with the internal teeth of the second gear in the engagement region. This means that a rotational movement of the first gear is transmitted directly to the second gear and conversely a rotational movement of the second gear is transmitted directly to the first gear.
  • the engagement region is, for example, fixed to the housing, meaning it does not rotate with the first gear or the second gear.
  • a tooth of one of the gears engages with a tooth space of the other of the gears.
  • the tooth space is circumferentially delimited by teeth of the respective gear.
  • a tooth of the internal gear engages with a tooth space of the external gear, or conversely, a tooth of the external gear engages with a tooth space of the internal gear.
  • the internal and external gears interact to form a seal.
  • the filler piece is arranged on the other side of the engagement region, i.e., preferably on the side diametrically opposite the engagement region with respect to the first axis of rotation and/or the second axis of rotation.
  • the filler piece is located between the first gear and the second gear, or in other words, between the external toothing of the first gear and the internal toothing of the second gear.
  • the filler piece is thus arranged in a fluid space that is bounded radially inward by the first gear and radially outward by the second gear, respectively with respect to the first axis of rotation and the second axis of rotation.
  • the filler piece rests on the outer toothing on one side and the inner toothing on the other. More precisely, the filler piece rests sealingly on the tooth tips of the outer toothing and sealingly on the tooth tips of the inner toothing to divide the fluid space into the first fluid chamber and the second fluid chamber.
  • each of the two fluid chambers is bounded on the one hand by the filler piece and on the other hand by the tight meshing of the outer toothing and the inner toothing in the engagement area.
  • one of the fluid chambers serves as the suction chamber and the other of the fluid chambers as the pressure chamber.
  • the suction chamber can accordingly also be referred to as the inlet chamber and the pressure chamber as the outlet chamber; what is crucial is that the fluid is always pumped from the inlet chamber towards the outlet chamber during operation of the internal gear fluid machine.
  • the pressure in the inlet chamber is always lower than the pressure in the outlet chamber when operated as a pump.
  • the pressure in the inlet chamber can already be (significantly) greater than ambient pressure.
  • pressurized fluid is pumped from the inlet chamber towards the outlet chamber.
  • the internal gear fluid machine is designed as a motor or is operated as a motor, fluid is supplied to the pressure chamber, which enters the suction chamber, causing the gears to rotate.
  • the pressure chamber acts as the inlet chamber and the suction chamber as the outlet chamber; the pressure in the inlet chamber is higher than the pressure in the outlet chamber.
  • This description does not explicitly address the operation of the internal gear fluid machine as a motor; instead, the internal gear fluid machine and its function are explained for operation as a pump. Of course, use as a motor is also possible, and the explanations are analogously applicable to such a design of the internal gear fluid machine or such a use.
  • the suction chamber can also be referred to as a low-pressure chamber and the pressure chamber as a high-pressure chamber.
  • the suction side of the internal gear machine corresponds to a low-pressure side.
  • the pressure side of a high-pressure side The terms "low pressure” and "high pressure” do not imply a restriction to a specific pressure level; rather, the pressure in the high-pressure chamber or on the high-pressure side is simply relatively higher than the pressure in the low-pressure chamber or on the low-pressure side.
  • the filler piece is designed in several parts and thus has several segments.
  • the segments of the filler piece are arranged next to one another in the radial direction, so that a first segment is arranged on the side of a second segment facing the first gear, and conversely, the second segment is arranged on the side of the first segment facing the second gear.
  • the first segment bears sealingly against the first gear or its external toothing
  • the second segment bears sealingly against the second gear or the internal toothing of the second gear.
  • the two segments are preferably radially displaceable relative to one another.
  • a gap existing between them is subjected to fluid pressure during operation of the internal gear fluid machine in such a way that the first segment is forced towards the first gear and the second segment towards the second gear, so that the segments bear sealingly against the respective gear or the tooth tips of the corresponding gearing.
  • the internal gear fluid machine is thus radially compensated or gap-compensated in the radial direction.
  • Each of the segments can be further subdivided into segments.
  • the first segment is one-piece or consists of at least two segments and/or the second segment is one-piece or consists of at least two segments.
  • These segments of the filler piece are also preferably mounted so that they can be displaced relative to one another, i.e., can be displaced independently of one another. This achieves particularly effective gap compensation.
  • the internal gear fluid machine has the machine housing.
  • the two gears of the internal gear fluid machine are arranged between the housing walls of the machine housing.
  • One of the housing walls is located on a first side of the gears, and a second of the housing walls is located on a side of the gears opposite the first side in the axial direction, so that the housing walls accommodate the gears between them in the axial direction.
  • the gap remaining between the housing walls and the gears is dimensioned so small that the housing walls ensure sufficient sealing of the fluid chamber. or the fluid chambers.
  • the gears are mounted on and/or in the machine housing.
  • the second gear is partially encompassed in the circumferential direction by at least one bearing recess formed in the machine housing.
  • the bearing recess is designed such that it only partially overlaps the second gear in the axial direction and is arranged so as to completely overlap with the second gear.
  • the bearing recess not only has a smaller extension in the axial direction than the second gear, but is also arranged such that the ends delimiting the bearing recess in the axial direction are arranged so as to overlap with the second gear. The bearing recess therefore does not protrude beyond the second gear in the axial direction.
  • the bearing recess is formed as a groove in the machine housing that runs in the circumferential direction.
  • the bearing recess surrounds the second gear in the circumferential direction by at least 30°, at least 60°, at least 90°, at least 120°, or at least 150°.
  • the bearing recess can also be significantly smaller in the circumferential direction and surround the second gear in this direction by less than 30°, in particular by at most 15°, at most 10°, or at most 5°.
  • the bearing recess is formed, for example, as a round bore.
  • the bearing recess serves to form the hydrostatic bearing or a hydrostatic bearing for the second gear.
  • the bearing recess is at least temporarily pressurized with fluid under pressure, so that the second gear is pushed radially away from the machine housing. This creates a fluid film between the second gear and the machine housing, which ensures particularly loss-free support of the second gear.
  • the pressure present in the bearing recess counteracts the pressure present in the pressure chamber.
  • the bearing recess is arranged and/or designed accordingly for this purpose.
  • a force exerted on the second gear by the fluid present in the bearing recess is at least as strong as as large as a force exerted on the second gear by the fluid present in the pressure chamber.
  • the former force is at least 50%, at least 60%, at least 70%, at least 80%, or at least 90% of the latter force.
  • the flow resistance exists between the fluid connection and the bearing recess, which causes a reduction in pressure.
  • the flow resistance is preferably in the form of a cross-sectional constriction.
  • a flow cross-sectional area is preferably identical before and after the flow resistance or the cross-sectional constriction. This means that the cross-sectional constriction is only present in sections and, in particular, does not extend directly to the bearing recess. Rather, the flow cross-sectional area decreases in the area of the cross-sectional constriction and then increases again, in particular also in the area of the cross-sectional constriction.
  • a ratio between a length and a width or a diameter of the cross-sectional constriction is at most 25, at most 20 or at most 15. However, the ratio is preferably at most 10 or at most 5.
  • the width or diameter is to be understood as the smallest dimension of the cross-sectional constriction over its extent.
  • the flow resistance reduces fluid loss from the bearing recess toward the return line.
  • the flow resistance can be readily provided, as the fluid pressure available on the pressure side of the internal gear fluid machine is usually more than sufficient to achieve adequate bearing support. It is therefore possible to reduce the pressure without compromising the quality of the bearing. Reducing the pressure, in turn, reduces the flow, so that a smaller amount of fluid is discharged via the bearing recesses toward the return line or into the return line.
  • the flow resistance is designed such that the amount of fluid discharged from the bearing recess into the return line per unit of time corresponds to at most 50%, at most 40%, at most 30%, or at most 25% of the total amount of fluid accumulating in the return line per unit of time.
  • Such dimensioning of the flow resistance is in any case suitable for achieving adequate support of the second gear in the machine housing.
  • the amount of fluid per unit of time can also be higher and For example, a maximum of 75%, a maximum of 70%, a maximum of 75%, a maximum of 60%, or a maximum of 55% of the specified value.
  • the smaller values are preferred because they can significantly limit fluid loss with sufficient storage quality.
  • dimensions of the flow resistance depend on a diameter of the second gear or a root circle diameter of the internal toothing. It can be provided that the dimensions are selected as a function of an extension of the bearing recess in the circumferential direction and/or in the axial direction. Additionally or alternatively, a dependence on the bearing clearance and/or on an extension of the bearing webs in the axial direction can be provided. For example, a relationship with a displacement volume of the internal gear fluid machine is also provided.
  • a ratio of the dimensions of the flow resistance, in particular a smallest diameter of the flow resistance over its extension, to the displacement volume of at least 15 1/m 2 and at most 75 1/m 2 , at least 30 1/m 2 and at most 60 1/m 2 or at least 30 1/m 2 and at most 45 1/m 2 is provided.
  • the bearing recess is fluidically connected to both fluid connections, in particular via a flow resistance.
  • a flow resistance is designed identically for both fluid connections.
  • an asymmetric design can also be implemented, in which different flow resistances exist between the fluid connections and the bearing recesses.
  • the bearing recess only partially encompasses the second gear in the circumferential direction.
  • there are two bearing recesses spaced apart from one another in the circumferential direction i.e., the two bearing recesses are spaced apart from one another on both sides in the circumferential direction.
  • the bearing recesses viewed in cross-section, are arranged symmetrically with respect to an imaginary plane that includes the rotational axis of the second gear and/or the rotational axis of the second gear.
  • the bearing recesses are fluidically connected to different fluid connections, preferably each via a flow resistance.
  • a first of the bearing recesses is fluidly connected to a first fluid connection via a first flow resistance
  • a second of the bearing recesses is fluidly connected to a second fluid connection of the internal gear fluid machine via a second flow resistance.
  • each of the bearing recesses is directly connected to the corresponding fluid connection via the respective flow resistance and is only indirectly fluidically connected to the other fluid connection, in particular via the fluid space or one or more of the fluid chambers.
  • Such a flow connection can, of course, also exist outside the internal gear fluid machine.
  • one of the bearing recesses is always fluidly connected to the pressure side and another of the bearing recesses is fluidly connected to the suction side of the internal gear fluid machine. This balances the forces within the internal gear fluid machine, resulting in particularly high efficiency.
  • the flow resistance is arranged in the fluid line, via which the respective bearing recesses are in fluid communication with the corresponding fluid connection.
  • the bearing recesses are each connected to the corresponding fluid connection via a fluid line, with a flow resistance being arranged in each of the fluid lines. All statements regarding the bearing recess within the scope of this description are preferably optionally applicable to each of the multiple bearing recesses, if present.
  • a single bearing recess is formed in the machine housing, which only partially or completely surrounds the second gear in the circumferential direction.
  • This bearing recess is fluidically connected to the fluid connection of the internal gear fluid machine.
  • the single bearing recess is fluidically connected to several fluid connections, in particular to a fluid connection on the pressure side and a fluid connection on the suction side of the internal gear fluid machine.
  • valves in particular check valves, are fluidically connected between the bearing recess on the one hand and the fluid connections on the other. These are preferably designed and/or adjusted in such a way that they allow a flow of the fluid only from the direction of the respective fluid connection towards the bearing recess, i.e. a flow from the bearing recesses towards of the fluid connections. This ensures optimal fluid supply to the bearing recess, while largely preventing fluid loss or overflow from the pressure side to the suction side via the bearing recess.
  • the bearing recess In the axial direction, the bearing recess only partially overlaps the second gear, so that conversely the second gear completely overlaps the bearing recess in the axial direction.
  • the bearing recess is delimited on both sides in the axial direction by bearing webs which are formed in circumferential overlap with the bearing recess and have at least the same extension as the bearing recess. In the case of multiple bearing recesses, each of the bearing recesses has such bearing webs.
  • the second gear rests sealingly on the bearing webs, in particular continuously in the circumferential direction in overlap with the bearing recess, or the second gear is at a smaller distance from the bearing webs than from a base of the bearing recess, which delimits the bearing recess in the direction facing away from the second gear, i.e. in particular in the radial direction outwards. This reliably prevents undesired outflow of fluid from the bearing recess.
  • the second gear has a bearing clearance, i.e., a radial distance from the bearing lands, of at most 0.25 mm, at most 0.2 mm, at most 0.15 mm, at most 0.1 mm, at most 0.075 mm, or at most 0.05 mm. Distances of at most 0.1 mm or less are preferred.
  • the described internal gear fluid machine enables particularly effective and loss-free mounting of the second gear in the machine housing.
  • excessive fluid losses which can occur due to the use of the fluid to implement the hydrostatic bearing, are effectively avoided by the flow resistance.
  • the flow resistance does cause a pressure loss between the fluid connection and the bearing recesses, so that the fluid pressure present in the bearing recesses is lower than the fluid pressure at the fluid connection.
  • the fluid pressure remaining in the bearing recesses is sufficient for mounting the second gear.
  • the flow resistance is preferably designed or dimensioned accordingly.
  • the internal gear fluid machine is in fluid communication with a first chamber of a working cylinder and with a second chamber of the working cylinder.
  • the first chamber of the working cylinder is connected to a first of the fluid chambers.
  • the second chamber of the working cylinder is fluidly connected to a second of the fluid chambers.
  • the working cylinder is preferably designed as a hydraulic cylinder; in this case, a liquid, in particular oil, is used as the fluid.
  • the arrangement comprising the internal gear fluid machine and the working cylinder is, for example, a component of an industrial truck, in particular a forklift truck, or of a construction machine or piece of construction equipment, in particular an excavator.
  • the invention therefore also relates to such an arrangement comprising an internal gear fluid machine and a working cylinder, as well as to a method for operating such an arrangement. Reference is made to the further explanations within the scope of this description.
  • the flow resistance is in the form of a fluidic orifice, a fluidic throttle, or a fluidic nozzle.
  • An orifice is understood to be a sudden cross-sectional constriction; at the beginning of the orifice, the flow cross-sectional area decreases suddenly and widens again just as suddenly at the end of the orifice, in particular to the same flow cross-sectional area as before the orifice.
  • the orifice has a ratio of the length of the cross-sectional constriction in the flow direction to the width or diameter of at most 2, at most 1.5, or at most 1.
  • the ratio is at least 2 or greater than 2.
  • a ratio of at least 3, at least 4, or at least 5 is used.
  • the nozzle is a cross-sectional constriction where the flow cross-sectional area continuously decreases until it reaches a minimum. Downstream of the minimum flow cross-sectional area, the flow cross-sectional area widens again. This can occur abruptly or continuously.
  • the flow resistance comprises a diffuser in addition to the nozzle.
  • the nozzle and the diffuser are designed symmetrically or as mirror images, i.e., they have the same longitudinal extent. and the same gradient of the flow cross-sectional area over the longitudinal extent. The use of the nozzle and diffuser enables effective reduction of pressure and flow rate without excessive losses.
  • a further development of the invention provides that the fluid line runs radially outwards from the bearing recess and/or is continuously straight.
  • the fluid line opens directly into the bearing recess.
  • the fluid line can also open directly into the fluid connection or, alternatively, can be fluidically connected to it only indirectly via another line.
  • the fluid line runs radially outwards from the bearing recess, preferably exactly in the radial direction. This means that a longitudinal center axis of the fluid line is perpendicular to an imaginary plane containing the axis of rotation of the first gear and the axis of rotation of the second gear. This achieves low-loss introduction of the fluid into the bearing recess.
  • the fluid line is continuously straight. This is to be understood in particular that the longitudinal center axis of the fluid line is continuously straight. The straight course ensures a low pressure loss across the fluid line, so that this design also serves to introduce the fluid into the bearing recess with high efficiency.
  • a further development of the invention provides that the fluid line opens radially inward into the bearing recess by passing through a base of the bearing recesses to form an opening.
  • the base delimits the bearing recess in the direction away from the second gear.
  • the base is formed by the machine housing.
  • the bearing recess is thus delimited radially outward by the base and is open radially inward and correspondingly in the direction of the second gear.
  • the bearing recess is preferably delimited on opposite sides by walls which run at an angle to the base. The walls delimiting the bearing recess preferably run parallel to one another.
  • the bearing recess can alternatively also be angled to one another, so that, for example, the bearing recess has an axial extent which increases or decreases in the direction of the second gear or in the direction away from the base.
  • the bearing recess is, for example, trapezoidal in shape when viewed in section.
  • the fluid line passes through the base of the bearing recess. In this case, it forms the orifice. In other words, the fluid line flows into the bearing recess via the orifice, with the orifice being in the The bottom is formed. This design also serves to efficiently introduce the fluid into the bearing recess and prevent excessive pressure losses.
  • a further development of the invention provides that the fluid line, on its side facing away from the bearing recess, opens into a larger connecting channel, via which it is fluidically connected to the fluid connection.
  • the fluid line can be fluidically connected to the fluid connection either directly or only indirectly. If the fluid line is only indirectly connected to the fluid connection, the fluid line is in fluid communication with the fluid connection via the connecting channel.
  • the fluid line opens directly into the connecting channel, namely in particular in the radial direction.
  • a longitudinal center axis of the fluid line is preferably angled with respect to a longitudinal center axis of the connecting channel, i.e. the two longitudinal center axes enclose an angle with each other that is greater than 0° and less than 180°. The angle is preferably at least 45° and at most 135°, at least 60° and at most 120°, at least 75° and at most 105°, or approximately or exactly 90°.
  • the connecting channel can be continuously straight, i.e., it can run continuously straight between the point at which the fluid line flows into it and the fluid connection.
  • the connecting channel can also have at least one bend or curve.
  • the fluid line flows into a straight region of the connecting channel.
  • the connecting channel flows into the fluid connection on its side facing away from the fluid line, i.e., it is directly fluidically connected to it.
  • the connecting channel flows into the fluid connection in a radial direction, so that the longitudinal center axis of the connecting channel is angled relative to a longitudinal center axis of the fluid connection.
  • the angle is made to the above explanations regarding the angle.
  • the connecting channel has larger dimensions than the fluid line; in particular, its flow cross-section is larger than the flow cross-section of the fluid line. This results in a particularly low pressure loss, so that the fluid line is fluidically connected to the fluid connection particularly effectively.
  • the largest flow cross-sectional area of the connecting channel over its entire length is larger by a factor of at least 2, at least 3, at least 4, or at least 5 than the largest flow cross-sectional area of the fluid channel over its entire length.
  • a further development of the invention provides that the cross-sectional constriction is formed only locally in the fluid line, so that a flow cross-section of the fluid line on both sides of the cross-sectional constriction is larger than a flow cross-section in the region of the cross-sectional constriction.
  • the cross-sectional constriction is present in the fluid line and temporarily reduces its flow cross-sectional area. This means that the fluid line as a whole cannot be regarded as a cross-sectional constriction, even if its flow cross-sectional area is possibly smaller than the flow cross-sectional area of elements that are fluidically connected to the fluid line. For example, the flow cross-sectional area of the connecting channel may be larger than that of the fluid line.
  • the flow resistance is not caused by the fluid line itself; rather, the cross-sectional constriction occurs in the fluid line.
  • the fluid line On both sides of the cross-sectional constriction, the fluid line has a flow cross-sectional area that is larger than the flow cross-sectional area of the cross-sectional constriction or the flow resistance.
  • the flow cross-sectional area of the fluid line on both sides of the cross-sectional constriction is larger than the flow cross-sectional area of the cross-sectional constriction by a factor of at least 5, at least 7.5, at least 10, at least 12.5, at least 15, or at least 20.
  • the flow cross-sectional area of the cross-sectional constriction is understood to be the smallest flow cross-sectional area of the cross-sectional constriction across its entire length. The described design achieves effective flow limitation for the fluid.
  • a further development of the invention provides that the bearing recess, on its side fluidically remote from the fluid line, is fluidically connected via a leakage gap to a return recess of the internal gear fluid machine, which is in direct fluid communication with a suction side of the internal gear fluid machine and/or a fluid tank.
  • the bearing recess is fluidically connected to a return line of the internal gear fluid machine, via which fluid is discharged, namely in the direction of the suction side of the internal gear fluid machine and/or in the direction of the fluid tank.
  • Leakage fluid i.e., fluid that accrues due to leaks in the internal gear fluid machine, is collected in the return line.
  • the fluid is discharged in the direction of the suction side and/or the fluid tank, preferably in such a way that it is again conveyed by the internal gear fluid machine in the direction of the pressure side.
  • the fluid tank is fluidically connected to the suction side of the internal gear fluid machine for this purpose.
  • the fluid tank can be a component of the internal gear fluid machine. or be present separately.
  • the internal gear fluid machine and the fluid tank are part of a corresponding arrangement.
  • the return has the return recess, which is formed in the machine housing.
  • the return recess is, for example, a recess formed in the machine housing and open in the direction of the gears.
  • the return recess can have at least the same dimensions in the axial direction as the at least one bearing recess or the bearing recesses, or can project beyond them in the axial direction, in particular only on one side or on both sides.
  • the bearing recess or the bearing recesses are each designed to be spaced apart from the return recess in the circumferential direction. If there are multiple bearing recesses, the return or the return recess is preferably arranged between the bearing recesses in the circumferential direction. In particular, the bearing recesses are arranged to be equidistant from the return recess in the circumferential direction.
  • the return line is preferably configured such that the fluid present therein is either fed to the fluid tank and/or directly returned to the internal gear fluid machine and conveyed by it toward its pressure side.
  • the fluid discharged from the return line into the fluid tank can also be returned to the internal gear machine. In other words, the fluid is first discharged from the return line into the fluid tank and then removed from the fluid tank by the internal gear fluid machine and conveyed toward its pressure side.
  • the bearing recess is preferably spaced apart from the return recess in the circumferential direction.
  • the bearing recess is connected to the return or the return recess at exactly one point in the circumferential direction, in particular, it opens into the return recess.
  • the leakage gap in the area of which the second gearwheel has, at least in some areas, only a small distance from the machine housing in the radial direction, for example a distance of at most 10 ⁇ m, at most 5 ⁇ m, at most 2.5 ⁇ m or at most 1 ⁇ m.
  • this distance in the circumferential direction is only at one point or across a specific part of the second gear. Away from this point or this part, the distance is greater.
  • the small distance, seen in cross-section is on a side of the internal gear machine on which there is higher pressure.
  • the distance away from the point or part of the second gear, in particular on the side with lower pressure is more than 10 ⁇ m, in particular at least 25 ⁇ m, at least 50 ⁇ m, at least 75 ⁇ m or at least 100 ⁇ m.
  • the return line or return recess for example, is centered in the circumferential direction relative to the filler piece. This places it centrally between the pressure side and the suction side of the internal gear fluid machine, resulting in a symmetrical design.
  • the implementation of the return recess enables effective recirculation of the leakage fluid occurring in the internal gear fluid machine.
  • the invention provides that the return line has return pockets on both sides of the gears in the axial direction, which are in flow communication with the return recess.
  • the return pockets are also provided as recesses formed in the machine housing. Viewed in the axial direction, such a return pocket is present or formed on each side of the gears.
  • the return pockets also serve to return leakage fluid accumulating in the internal gear fluid machine toward the suction side of the internal gear fluid machine and/or toward the fluid tank. This ensures efficient operation of the internal gear fluid machine.
  • connection channel is formed in each of the two housing walls, and via both connection channels, the same of the fluid chambers is in flow connection with the fluid connection of the internal gear fluid machine.
  • connection channel in each of the housing walls. This means that each of the housing walls has such a connection channel.
  • one of the fluid chambers is fluidically connected to a fluid connection of the internal gear fluid machine, preferably permanently.
  • Each of the connection channels is therefore fluidically located between this fluid chamber and this fluid connection, so that the flow connection between the fluid chamber and the fluid connection runs via both connection channels.
  • the connection channels are therefore fluidically parallel between the fluid chamber and the fluid connection, so that fluid can flow via both connection channels simultaneously from the fluid connection to the fluid chamber or vice versa.
  • connection channels serve to establish the flow connection between exactly one of the fluid chambers and exactly one of the fluid connections. Accordingly, during operation of the internal gear fluid machine, the fluid flows either out or in through the connection channels at the same time. This makes it possible to achieve a particularly high fluid throughput of the internal gear fluid machine.
  • the flow connection is to be understood as a flow connection that runs exclusively via the internal gear fluid machine, i.e. not via an external connection. In particular, the flow connection runs only via the connection channels and - optionally - via one or more axial openings in one or more optionally provided sealing disks.
  • the fluid chamber fluidically connected to the fluid connection via the connecting channels can be the first fluid chamber or the second fluid chamber.
  • the fluid chamber can be either the suction chamber or the pressure chamber, so that during operation of the internal gear fluid machine, the connecting channels serve either to supply fluid to the suction chamber or to discharge the fluid from the pressure chamber. In either case, a particularly low flow resistance is achieved during the inflow or outflow of the fluid.
  • a further development of the invention provides that, in the axial direction relative to the first rotational axis, a sealing disk is arranged next to the first gear and the second gear, which sealing disk rests sealingly against the first gear and the second gear during operation of the internal gear fluid machine, wherein an axial opening is formed in the sealing disk, via which one of the fluid chambers is in flow connection with one of the fluid connections of the internal gear fluid machine.
  • the sealing disk is only present on one side of the first gear and the second gear.
  • - again viewed in the axial direction such a sealing disk is arranged on both sides of the two gears.
  • the particularly advantageous case of multiple sealing disks is frequently explained. It goes without saying, however, that the corresponding embodiments also apply to a configuration the internal gear fluid machine, in which only a sealing disc is part of the internal gear fluid machine.
  • the sealing disc is located on one side of the gears, viewed in the axial direction.
  • the sealing disc lies in sealing contact with the gears.
  • it is preferably forced in the axial direction towards the gears, for example by applying pressure, i.e. by being subjected to a pressurized fluid.
  • pressure i.e. by being subjected to a pressurized fluid.
  • it are arranged on both sides of the gears in the axial direction.
  • One of the sealing discs is therefore located on a first side of the gears and a second of the sealing discs is located on a second side of the gears, opposite the first side in the axial direction, so that the sealing discs hold the gears between them, viewed in the axial direction.
  • the sealing discs lie in sealing contact with the gears.
  • they are preferably forced in the axial direction towards the gears, for example by applying pressure, i.e. by being subjected to a pressurized fluid.
  • the internal gear fluid machine is therefore axially compensated or gap-compensated in the axial direction. This results in a particularly high efficiency of the internal gear fluid machine.
  • each of the sealing discs has an axial opening.
  • each of the sealing discs has such an axial opening, so that a total of several axial openings are formed in the multiple sealing discs.
  • One of the fluid chambers is fluidically connected, preferably permanently, to a fluid connection of the internal gear fluid machine via the axial opening(s). From a fluidic perspective, the axial opening or each of the axial openings is therefore located between this fluid chamber and this fluid connection, so that the flow connection between the fluid chamber and the fluid connection runs via the axial opening or openings.
  • the axial opening(s) serve to establish the flow connection between exactly one of the fluid chambers and exactly one of the fluid connections. Accordingly, during operation of the internal gear fluid machine, the fluid flows through the axial opening(s) simultaneously either in or out through the axial openings. This allows a particularly high fluid throughput of the internal gear fluid machine to be achieved.
  • the fluid chamber fluidically connected to the fluid connection via the axial opening(s) can be the first fluid chamber or the second fluid chamber.
  • the fluid chamber can be either the suction chamber or the pressure chamber, so that the axial opening(s) serve either to supply fluid to the suction chamber or to discharge the fluid from the pressure chamber during operation of the internal gear fluid machine. In either case, a particularly low flow resistance is achieved during the inflow or outflow of the fluid.
  • connection channels is fluidically connected to the fluid chamber via the axial opening.
  • the axial opening is fluidically located between the connection channel and the fluid chamber.
  • the fluid chamber is fluidically connected to the fluid connection via the axial opening and the corresponding connection channel.
  • both connection channels are fluidically connected to the fluid chamber via the axial openings.
  • a first of the connection channels is fluidically connected to the fluid chamber via a first of the axial openings.
  • a second of the connection channels is fluidically connected to the same fluid chamber via a second of the axial openings.
  • a further development of the invention provides that the axial opening widens in the direction of the first gear and the second gear.
  • a flow cross-sectional area of the axial opening does not remain constant over its respective extent, but rather changes.
  • the flow cross-sectional area of the axial opening increases in the direction of the gears, i.e., becomes larger.
  • the widening occurs continuously, at least in sections or throughout, so that discontinuities in the flow cross-sectional area are avoided.
  • the widening can also occur abruptly, so that a dimensional jump is formed in each axial opening.
  • the axial opening is round, i.e., circular, in cross-section relative to its respective longitudinal extent.
  • the widening of the axial opening enables particularly efficient inflow and outflow of the fluid.
  • the widening occurs for both axial openings.
  • the axial openings widen in the direction of the first gear and the second gear.
  • the embodiments for widening the axial opening can be used in addition to each other.
  • the fluid connection is a first fluid connection of a plurality of fluid connections, and that the first fluid chamber is in flow order with the fluid connection present as the first fluid connection via the connection channels present as first connection channels, and that a second connection channel is formed in each of the housing walls, and that the second fluid chamber is in flow connection with a second fluid connection of the internal gear fluid machine via the second connection channels.
  • the internal gear fluid machine therefore has a plurality of fluid connections, a plurality of first connection channels, and a plurality of second connection channels.
  • the fluid connection already mentioned above forms the first fluid connection
  • the connection channels mentioned form the first connection channels.
  • first fluid connection there is now a second fluid connection, and in addition to the first connection channels, there are second connection channels in the machine housing.
  • the second fluid chamber is fluidly connected to the second fluid connection via the second connection channels, preferably permanently.
  • first connection channels apply analogously to the second connection channels.
  • the filler piece extends circumferentially from the first connection channels to the second connection channels, thus engaging both the imaginary extension of the first connection channels and the imaginary extension of the second connection channels.
  • the described taper is particularly preferably provided and formed on both the side of the filler piece facing the first connection channels and the side facing the second connection channels. The described configuration enables, in particular, direction-independent operation of the internal gear fluid machine.
  • the fluid connection is a first fluid connection of a plurality of fluid connections and that the first fluid chamber is in flow order with the fluid connection present as the first fluid connection via the axial opening designed as the first axial opening, and that a second axial opening is formed in the sealing disc and that the second fluid chamber is in flow connection with a second fluid connection of the internal gear fluid machine via the second axial opening.
  • a plurality of sealing discs with a corresponding plurality of axial openings, wherein the axial openings are designed as first axial openings.
  • a second axial opening is formed in each of the sealing discs, wherein the second fluid chamber is in flow order with the second fluid connection via the second axial openings.
  • a further development of the invention provides that the filler piece projects in the circumferential direction up to the axial opening and/or ends in overlap with the axial opening when viewed in the circumferential direction.
  • the filler piece therefore projects in the circumferential direction up to an imaginary extension of the axial opening. It at least engages with this imaginary extension, but it can also penetrate it completely in the circumferential direction.
  • the filler piece particularly preferably ends in overlap with the axial opening when viewed in the circumferential direction, i.e. in the imaginary extension of the axial opening. This achieves reliable and effective sealing of the fluid chambers from one another by means of the filler piece.
  • such a configuration preferably applies to multiple axial openings.
  • the filler piece projects in the circumferential direction up to the axial openings and/or ends in overlap with the axial openings when viewed in the circumferential direction.
  • the filler piece is tapered in the axial direction in overlap with the axial opening, in particular only on one side or both sides. It is particularly preferred that the taper of the filler piece, viewed in the circumferential direction, ends in overlap with the axial openings.
  • the taper of the filler piece causes the filler piece to move away from the axial opening or at least one of the axial openings in the axial direction, i.e., to be continuous therefrom. In other words, the distance between the filler piece and the axial opening or at least one of the axial openings increases. in the circumferential direction. This facilitates the inflow and outflow of the fluid.
  • the taper of the filler piece can be designed such that the fluid is efficiently deflected in the circumferential direction, so that it can flow into or out of the respective fluid chamber particularly efficiently.
  • the filler piece tapers only on one side, i.e. on the side facing the axial opening or one of the axial openings.
  • it is particularly preferably tapered on both sides, so that the inflow or outflow through the axial opening or both axial openings can take place efficiently.
  • the filler piece is particularly preferably designed symmetrically when viewed in longitudinal section, i.e. in the axial direction, so that the taper is identical on both sides, albeit a mirror image.
  • a further development of the invention provides that the taper of the filler piece, viewed in the circumferential direction, ends in overlap with the axial opening or openings.
  • the filler piece extends at least partially up to the axial opening or openings and preferably has constant dimensions in the axial direction up to the taper, viewed in the circumferential direction.
  • the filler piece has an extension in the axial direction up to the imaginary extension of the axial opening or openings, which corresponds to the distance between the sealing discs, so that it rests against the sealing discs away from the axial opening or openings, in particular continuously in the circumferential direction. Only then, i.e.
  • the filler piece taper in overlap with the axial opening or openings, does the filler piece taper, so that its extension in the axial direction decreases in the circumferential direction, namely up to a free end of the filler piece.
  • the taper begins only when the axial opening(s) overlap and preferably extends to the free end of the filler piece. This ensures a reliable sealing effect of the filler piece.
  • connection channels are fluidically connected to the fluid connection directly, and another of the connection channels is fluidically connected to the fluid connection via the connecting channel that axially extends over the first gear and the second gear.
  • the connection channels have the same flow cross-sectional area.
  • at least one of the connection channels opens into the axial opening, if present.
  • both connection channels open into the optionally provided, multiple axial openings.
  • the flow cross-sectional area of the connecting channel on its side facing the gears and/or the respective axial opening is smaller than the flow cross-sectional area of the axial opening on its side facing the gears and/or the respective connecting channel. From the direction of the connecting channel toward the gears and/or the axial opening, there is thus a widening of the flow cross-section and a corresponding increase in the flow cross-sectional area.
  • the connecting channels have the same axial length with respect to their respective longitudinal center axes.
  • One of the connecting channels is fluidically connected directly to the fluid connection, for example, it opens directly into the fluid connection.
  • the other of the connecting channels is fluidically connected to the fluid connection only indirectly via the connecting channel.
  • the connecting channel completely overlaps the two gears in the axial direction.
  • the connecting channel overlaps at least one of the sealing discs or both sealing discs, if present.
  • the connecting channel opens into the connection channel on a side of a first sealing disc facing away from the gears, and into the fluid connection on a side of another sealing disc facing away from the gears.
  • one connection channel opens into the fluid connection in the axial direction, and the other connection channel opens into the radial direction.
  • the fluid connection has a flow cross-sectional area that is larger than the flow cross-sectional area of the connecting channels.
  • the flow cross-sectional area of the fluid connection is larger than the flow cross-sectional area of the connecting channels by a factor of at least 2.5, at least 3, at least 4, or at least 5.
  • the flow cross-sectional area of the connecting channel is larger than the flow cross-sectional area of the connecting channels, for example, by a factor of at least 1.25, at least 1.5, at least 1.75, or at least 2.0. This ensures particularly effective operation of the internal gear fluid machine.
  • a further development of the invention provides that the axial opening is encompassed by a seal which seals on the one hand on the sealing disc and on the other hand on the machine housing. Outside of an area encompassed by the seal, a pressure field is fluidly connected to a pressure side of the internal gear fluid machine, so that the sealing disc is at least temporarily forced toward the gears.
  • the seal ensures a fluid-tight connection between the axial opening or the respective axial opening and the respective connection channel.
  • the pressure field which is at least temporarily pressurised with pressurised fluid.
  • the pressure field is fluidically connected to the pressure side of the internal gear fluid machine.
  • the pressurised fluid pushes the sealing disc towards the gears so that the fluid chambers are reliably sealed in the axial direction by the axial disc. This particularly preferably applies to the multiple sealing discs, if present.
  • the axial openings are each encompassed by a seal which bears sealingly on the one hand against the respective sealing disc and on the other hand against the machine housing, wherein outside an area encompassed by the seal, a pressure field is fluidically connected to a pressure side of the internal gear fluid machine so that the sealing disc is at least temporarily urged towards the gears.
  • a further development of the invention provides that the filler piece is designed symmetrically in the circumferential direction, so that the internal gear fluid machine is reversible.
  • the filler piece is divided into several segments in the circumferential direction.
  • the filler piece has a total of four segments, since it is divided into individual segments both in the radial direction and in the circumferential direction. This realizes the radial compensation of the internal gear fluid machine regardless of its direction of rotation.
  • Such an internal gear fluid machine can also be referred to as a four-quadrant internal gear fluid machine or a reversible internal gear fluid machine.
  • the bearing recess is a first bearing recess of a plurality of bearing recesses and the flow resistance is a first flow resistance of a plurality of flow resistances and a second of the bearing recesses is formed in the machine housing at a distance from the first bearing recess in the circumferential direction, which second bearing recess at least partially overlaps the second gear in the axial direction, wherein the first bearing recess is connected to the first fluid connection via the first flow resistance and the second Bearing recess is fluidically connected to the second fluid connection via a second of the flow resistances.
  • the bearing recess is referred to as the first bearing recess and the further bearing recess as the second bearing recess.
  • the two bearing recesses i.e. the first bearing recess and the second bearing recess, are arranged spaced apart from one another in the circumferential direction in the machine housing.
  • the explanations regarding the bearing recess and the first bearing recess are preferably fully applicable to the second bearing recess. Reference is therefore made to the corresponding explanations.
  • Both bearing recesses are each fluidically connected to one of several fluid connections, namely the first bearing recess to the first fluid connection and the second bearing recess to the second fluid connection, which is different from the first fluid connection.
  • the first fluid connection is located, for example, on a pressure side and the second fluid connection on a suction side of the internal gear fluid machine, or vice versa.
  • the first flow resistance corresponds to the flow resistance already explained, while the second flow resistance is additional to this.
  • the explanations regarding the first flow resistance apply, so reference is made to them.
  • the two bearing recesses are arranged symmetrically to each other and to the filler piece of the internal gear fluid machine. Accordingly, the internal gear fluid machine can be operated efficiently in different directions of rotation.
  • a further development of the invention provides for the flow resistances to be arranged symmetrically to one another.
  • the flow resistances are located symmetrically within the machine housing and are symmetrically aligned.
  • the flow resistances are arranged symmetrically with respect to an imaginary plane that includes both the first and second rotational axes. This results in a simple and compact design of the internal gear fluid machine, which is also characterized by low flow losses and high efficiency.
  • the Figure 1 shows a schematic cross-sectional view of an internal gear fluid machine 1, which has a machine housing 2, in which a first gear 3 and a second gear 4 are rotatably mounted.
  • the first gear 3 can also be referred to as a pinion and the second gear 4 as a ring gear.
  • the first gear 3 is rotatably mounted in the machine housing 2 about a first axis of rotation 5 and the second gear 4 about a second axis of rotation 6. It can be seen that the first axis of rotation 5 and the second axis of rotation 6 are arranged parallel and spaced from one another, so that the first gear 3 and the second gear 4 have different axes of rotation.
  • the first gear 3 has an external toothing 7 and the second gear 4 has an internal toothing 8, which mesh with one another in an engagement region 9, i.e. are in engagement with one another.
  • the first gear 3 and the second gear 4 jointly define a fluid chamber 10.
  • the first gear 3 defines the fluid chamber 10 radially inward
  • the second gear 4 defines the fluid chamber 10 radially outward.
  • the fluid chamber 10 is circumferentially divided into a first fluid chamber 12 and a second fluid chamber 13 by the meshing of the gears 3 and 4 on the one hand and a filler piece 11 on the other.
  • one of the fluid chambers 12 and 13 serves as a suction chamber and another of the fluid chambers 12 and 13 serves as a pressure chamber.
  • the filler piece 11 is designed symmetrically to enable reversing operation of the internal gear fluid machine 1.
  • the internal gear fluid machine 1 can therefore be operated in both directions of rotation.
  • the filler piece 11 is designed in several parts and has several segments 14 and 15, or 16 and 17.
  • the segments 14 and 15, or 16 and 17, are divided radially. Accordingly, the first segment 14 or 16 rests against the first gear 3, and the second segment 15 or 17 rests against the second gear 4.
  • the second gear 4 is encompassed in the circumferential direction at least in regions, in particular only in regions, by one or more bearing recesses 20.
  • the bearing recesses 20 are fluidically connected to fluid connections 21 and 22 of the internal gear fluid machine 1 (not shown here), preferably each via a flow resistor 23.
  • the flow connections between the respective bearing recess 20 and the fluid connections 21 and 22 can be established via a respective connecting channel 24 or 25.
  • the bearing recesses 20 are designed such that they are at least temporarily supplied with pressurized fluid, for example from the fluid connections 21 and 22, so that they form a hydrostatic bearing for the second gear 4.
  • one of the bearing recesses 20 is fluidly connected only to that one of the fluid connections 21 and 22 that is assigned to a pressure side of the internal gear machine 1. This is particularly the case if the internal gear machine 1 is not designed to be reversible or is operated only in one preferred direction of rotation. However, if the internal gear machine 1 is intended for reversing operation and is operated with temporarily changing directions of rotation, the bearing recesses 20 are preferably fluidically connected to both fluid connections 21 and 22, namely one of the bearing recesses 20 to the fluid connection 21 and another of the bearing recesses 20 to the fluid connection 22.
  • one of the bearing recesses 20 is always subjected to the pressure present on the pressure side of the internal gear fluid machine 1, whereas the other of the bearing recesses 20 is subjected to any pressure, for example the pressure present on the suction side, which is lower.
  • the Figure 2 shows a longitudinal section of the internal gear fluid machine 1. It can be seen that the gears 3 and 4 are mounted in the axial direction by means of – purely optional – sealing disks 26 in the machine housing 3.
  • the sealing disks 26 are arranged on opposite sides of the gears 3 and 4 and bear against them in a sealing manner during operation of the internal gear fluid machine 1.
  • First axial openings 27 are provided in the sealing disks 26.
  • second axial openings 28 are formed. The axial openings 27 and 28 completely penetrate the respective sealing disc 26 in the axial direction.
  • the axial openings 27 and 28 each widen in the direction of the gears 2 and 4.
  • the axial openings 27 and 28, viewed in section on their side facing the gears 3 and 4, are aligned in the radial direction inside with a root circle of the external toothing 7 and/or in the radial direction outside with a root circle of the internal toothing 8, although only the former is shown here.
  • the axial openings 27 and 28 are located between the root circle of the external toothing 7 and the root circle of the internal toothing 8, thus not projecting beyond them in the radial direction. This ensures high efficiency of the internal gear fluid machine 1.
  • the axial openings 27 are arranged on both sides of the first fluid chamber 12, and the second axial openings 28 are arranged on both sides of the second fluid chamber 13.
  • the first fluid chamber 12 is fluidically connected to the first fluid connection 21 via the first axial openings 27.
  • the second fluid chamber 13 is fluidically connected to the second fluid connection 22 via the second axial openings 28.
  • connection channels 29 and 30 are formed in the machine housing 2.
  • the first axial openings 27 are connected to the respective fluid connection 21 and 22 via the connection channels 29, and the second axial openings 28 are connected to the respective fluid connection 21 and 22 via the second connection channels 30.
  • the sealing disks 26 and the axial openings 27 formed therein can be omitted. In this case, there is a direct flow connection between the connecting channels 29 and 30 and the fluid chambers 12 and 13. Of course, only one of the sealing discs 26 can also be implemented.
  • one of the connecting channels 29 opens directly into the corresponding fluid connection 21 or 22, whereas the other of the connecting channels 29 and 30 is connected to the corresponding fluid connection 22 via the respective connecting channel 24 or 25.
  • the connecting channels 24 and 25 completely overlap the gears 3 and 4 and the sealing discs 26 in the axial direction.
  • first connection channels 29 open in the axial direction and the connecting channels 24 and 25 open in the radial direction into the respective fluid connection 21 and 22, respectively.
  • the axial openings 27 and 28 are each formed by a Seal 31 or 32 is encompassed, which ensures a fluid-tight connection of the respective axial opening 27 or 28 to the respective connection channel 29 or 30.
  • the axial discs 26 have common dimensions in the axial direction that at least correspond to the dimensions of the gears 3 and 4 in the same direction. These large dimensions in the axial direction ensure particularly reliable mounting of the gears 3 and 4 in the machine housing 2. In particular, tilting of the axial discs 26 and the associated uneven sealing of the fluid chambers 12 and 13 are reliably prevented.
  • the Figure 3 shows another longitudinal section of the internal gear fluid machine 1. It is clear that the filler piece 11 extends in the circumferential direction up to the axial openings 28 and ends in the region of the axial openings 28. The same applies, of course, analogously to the first axial openings 27.
  • the filler piece 11 has a taper 34, through which it tapers in the axial direction, on both sides in the embodiment shown here.
  • the taper 34 is formed at the end of the filler piece 11 in the circumferential direction.
  • the taper 34 ends—also viewed in the circumferential direction—in overlap with the axial opening 28, so that the filler piece 11, in overlap with the axial opening 28, has dimensions in the axial direction that correspond to the distance between the two sealing discs 26. Only when it overlaps with the axial opening 28 does the filler piece 11 begin to taper toward its free end.
  • the taper 34 ensures optimized flow guidance, allowing the fluid to flow unhindered into or out of the respective fluid chamber 12 or 13.
  • a pressure field is preferably formed away from the seal 32, which can be subjected to pressurized fluid to apply a force directed toward the gears 3 and 4 to the sealing disks 26.
  • fluid is supplied to the pressure field from one of the fluid connections 21 and 22 or both fluid connections 21 and 22.
  • a corresponding fluid connection can be implemented for this purpose.
  • the described configuration ensures that the fluid chambers 12 and 13 are reliably sealed in the axial direction by the sealing disks 26.
  • the Figure 4 shows a first detailed representation of the filler piece 11. This is designed symmetrically in the circumferential direction, i.e., it has at least one axis of symmetry 35, with respect to which it is designed mirror-symmetrically.
  • a taper 34 is formed on each end of the filler piece in the circumferential direction.
  • the filler piece 11 has an extension of at least 180° in the circumferential direction, preferably more than 180°, in particular at least 190°, at least 200°, at least 210°, or at least 220°. In the exemplary embodiment shown here, the extension in the circumferential direction is at least 225°.
  • the described design of the filler piece 11 enables reversible operation of the internal gear fluid machine 1, i.e., operation in any direction of rotation.
  • the internal gear fluid machine 1 can also be operated optionally as a pump and/or as a motor, without the need for conversion. In addition, it ensures reliable sealing of the fluid chambers 12 and 13 from each other in the circumferential
  • the Figure 5 shows a further schematic representation of the filler piece 11, wherein the end-side, bilateral taper 34 can be seen again.
  • the filler piece has constant dimensions in the axial direction apart from the taper 34 or tapers 34.
  • a return line 36 can also be seen, via which fluid, in particular leakage fluid, can be discharged from the internal gear fluid machine 1 and/or fed back to the internal gear fluid machine 1 or the respective suction chamber.
  • the return line 36 is connected directly to the suction side or the suction chamber.
  • the return line 36 is fluidically connected to a fluid tank.
  • This fluid tank can be a component of the internal gear fluid machine 1, but can also be located separate from it.
  • it is fluidically connected to the suction side of the internal gear fluid machine 1.
  • the return line 36 is arranged approximately centrally with respect to the filler piece 11, preferably exactly centrally.
  • the return line 36 is arranged symmetrically with respect to an imaginary plane which accommodates both the first axis of rotation 5 and the second axis of rotation 6.
  • the return 36 has a return recess 37, which passes through an inner circumferential surface of the machine housing 2 facing the second gear 3, so that the return recess 37 is open in the direction of the gears 3 and 4.
  • the return 36 has via return pockets 38, which are preferably in flow communication with the return recess 37. While the return recess 37 overlaps the gears 3 and 4 in the axial direction, the return pockets 38 are located on both sides of the gears 3 and 4 in the axial direction; in particular, they are formed on the sides of the sealing discs 26 in the machine housing 2 facing away from the gears 3 and 4.
  • the fluid can be discharged via the return line 36, i.e., via the return recess 37 and the return pockets 38, and preferably fed back into the respective suction chamber.
  • the bearing recess 20 opens into the return recess 37.
  • the bearing webs that delimit the bearing recess 20 in the axial direction also delimit the return recess 37 in the axial direction.
  • the bearing recesses 20 are preferably arranged at a distance from the return recess 37 in the circumferential direction.
  • the bearing recesses are preferably designed symmetrically with respect to the return recess 37, in particular, they are at the same distance from it.
  • flow resistors 23 are provided. These are preferably designed identically and, for example, have a smallest diameter over their respective extent, which, based on a displacement volume of the internal gear fluid machine 1, is at least 15 l/m 2 and at most 75 l/m 2 . This allows effective mounting of the second gear 4 in the machine housing 2 and, at the same time, a significant reduction in the amount of leakage fluid.
  • One of the flow resistors 23 is fluidically arranged between one of the bearing recesses 20 and the pressure side, and another of the flow resistors is fluidically arranged between another of the bearing recesses 20 and the suction side of the internal gear fluid machine.
  • a fluidic connection between the bearing recesses 20 is preferably only present via unavoidable leaks and/or via the internal gear fluid machine 1 itself, i.e. via the fluid space 10 or at least one or both of the fluid chambers 12 and 13.
  • the described design of the internal gear fluid machine 1 enables particularly efficient fluid flow and a high fluid throughput. Furthermore, due to the symmetrical design of the filler piece 11, it can be operated reversibly and/or can be pressurized on both its pressure and suction sides. Since the filler piece 11 is designed in several parts, a four-segment internal gear fluid machine is realized, which any direction of rotation ensures effective sealing of the fluid chambers 12 and 13 from one another in the circumferential direction by means of the filler piece 11.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (9)

  1. Machine à fluide à roue dentée interne (1), avec
    - une première roue dentée (3) comprenant une denture externe (7) et montée rotative autour d'un premier axe de rotation (5) et une deuxième roue dentée (4) comprenant une denture interne (8) s'engrenant par endroits avec la denture externe (7) dans une zone de mise en prise (9) et montée rotative autour d'un deuxième axe de rotation (6) différent du premier axe de rotation (5), dans laquelle
    - des parois de carter d'un carter de machine (2) de la machine à fluide à roue dentée interne (1) sont disposées dans la direction axiale par rapport au premier axe de rotation (5) des deux côtés de la première roue dentée (3) et de la deuxième roue dentée (4), et dans laquelle
    - la deuxième roue dentée (4) est enserrée dans la direction circonférentielle pour la constitution d'un palier hydrostatique au moins par endroits par au moins une cavité de palier (20) conçue sous la forme de rainure dans le carter de machine (2), laquelle cavité de palier (20) empiète uniquement en partie dans la direction axiale sur la deuxième roue dentée (4), ainsi que se trouve complètement en chevauchement avec la deuxième roue dentée (4), et est raccordée fluidiquement, par l'intermédiaire d'une conduite de fluide présentant une résistance à l'écoulement (23), à un raccord de fluide (21, 22) de la machine à fluide à roue dentée interne (1),
    caractérisée en ce que
    - une pièce de remplissage (11) est disposée entre la première roue dentée (3) et la deuxième roue dentée (4) à l'écart de la zone de mise en prise (9), laquelle pièce de remplissage (11) repose d'une part sur la denture externe (7) et d'autre part sur la denture interne (8), afin de subdiviser une chambre de fluide (10) située entre la première roue dentée (3) et la deuxième roue dentée (4) en une première chambre de fluide (12) et une deuxième chambre de fluide (13), et en ce que
    - la cavité de palier (20) est raccordée fluidiquement, sur son côté fluidiquement opposé à la conduite de fluide, par l'intermédiaire d'un interstice de fuite, à un évidement de retour (37) d'un retour (36) de la machine à fluide à roue dentée interne (1), lequel évidement de retour (37) se trouve en liaison fluidique directement avec un côté aspiration de la machine à fluide à roue dentée interne (1) et/ou avec un réservoir de fluide, dans laquelle le retour (36) comprend des poches de retour (38) dans la direction axiale des deux côtés des roues dentées (3, 4), lesquelles poches de retour (38) se trouvent en liaison fluidique avec l'évidement de retour (37) et sont prévues pour la recirculation de fluide de fuite s'accumulant dans la machine à fluide à roue dentée interne (1) dans la direction du côté aspiration de la machine à fluide à roue dentée interne (1) et/ou du réservoir de fluide.
  2. Machine à fluide à roue dentée interne selon la revendication 1, caractérisée en ce que la conduite de fluide s'étend dans la direction radiale vers l'extérieur à partir de la cavité de palier (20) et/ou est droite en continu.
  3. Machine à fluide à roue dentée interne selon l'une des revendications précédentes, caractérisée en ce que la conduite de fluide débouche dans la direction radiale vers l'intérieur dans la cavité de palier (20) du fait qu'elle traverse un fond de la cavité de palier (20) avec constitution d'ouvertures d'embouchure.
  4. Machine à fluide à roue dentée interne selon l'une des revendications précédentes, caractérisée en ce que la conduite de fluide débouche, sur son côté opposé à la cavité de palier (20), dans un canal de liaison (24, 25) de plus grande dimension par l'intermédiaire duquel elle est raccordée fluidiquement au raccord de fluide (21, 22).
  5. Machine à fluide à roue dentée interne selon l'une des revendications précédentes, caractérisée en ce que la résistance à l'écoulement (23) se présente sous la forme de rétrécissement de section transversale constitué uniquement localement dans la conduite de fluide de sorte qu'une section transversale d'écoulement de la conduite de fluide des deux côtés du rétrécissement de section transversale est plus grande qu'une section transversale d'écoulement dans la zone du rétrécissement de section transversale.
  6. Machine à fluide à roue dentée interne selon l'une des revendications précédentes, caractérisée en ce que respectivement un canal de raccordement (29) est constitué dans les deux parois de carter et une même chambre de fluide des chambres de fluide (12, 13) se trouve en liaison fluidique, par l'intermédiaire des deux canaux de raccordement (29), avec le raccord de fluide (21, 22) de la machine à fluide à roue dentée interne (1).
  7. Machine à fluide à roue dentée interne selon l'une des revendications précédentes, caractérisée en ce que le raccord de fluide (21, 22) est un premier raccord de fluide (21) parmi plusieurs raccords de fluide (21, 22) et la première chambre de fluide (12) se trouve en communication fluidique, par l'intermédiaire des canaux de raccordement (29) se présentant sous la forme de premiers canaux de raccordement (29), avec le raccord de fluide (21) se présentant sous la forme de premier raccord de fluide (21), et en ce que respectivement un deuxième canal de raccordement (30) est constitué dans les parois de carter et la deuxième chambre de fluide (13) se trouve en liaison fluidique, par l'intermédiaire des deuxièmes canaux de raccordement (30), avec un deuxième raccord de fluide (22) de la machine à fluide à roue dentée interne (1).
  8. Machine à fluide à roue dentée interne selon l'une des revendications précédentes, caractérisée en ce que l'un des canaux de raccordement (29, 30) est raccordé fluidiquement directement au raccord de fluide (21, 22) et un autre des canaux de raccordement (29, 30) est raccordé fluidiquement, par l'intermédiaire du canal de liaison (24, 25) empiétant sur la première roue dentée (3) et la deuxième roue dentée (4) dans la direction axiale, au raccord de fluide (21, 22).
  9. Machine à fluide à roue dentée interne selon l'une des revendications précédentes, caractérisée en ce que la cavité de palier (20) est une première cavité de palier (20) parmi plusieurs cavités de palier (20) et la résistance à l'écoulement (23) est une première résistance à l'écoulement (23) parmi plusieurs résistances à l'écoulement (23) et une deuxième des cavités de palier (20) est constituée dans la direction circonférentielle à distance de la première cavité de palier (20) dans le carter de machine (2), laquelle deuxième cavité de palier (20) empiète au moins en partie dans la direction axiale sur la deuxième roue dentée (4), dans laquelle la première cavité de palier (20) est raccordée fluidiquement, par l'intermédiaire de la première résistance à l'écoulement (23), au premier raccord de fluide (21) et la deuxième cavité de palier (20) est raccordée fluidiquement, par l'intermédiaire de la deuxième des résistances à l'écoulement (23), au deuxième raccord de fluide (22).
EP21746687.9A 2020-07-24 2021-07-19 Machine à fluide à engrenage interne Active EP4185773B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020209407.1A DE102020209407A1 (de) 2020-07-24 2020-07-24 Innenzahnradfluidmaschine
PCT/EP2021/070136 WO2022018022A1 (fr) 2020-07-24 2021-07-19 Machine à fluide à engrenage interne

Publications (2)

Publication Number Publication Date
EP4185773A1 EP4185773A1 (fr) 2023-05-31
EP4185773B1 true EP4185773B1 (fr) 2025-09-03

Family

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Application Number Title Priority Date Filing Date
EP21746687.9A Active EP4185773B1 (fr) 2020-07-24 2021-07-19 Machine à fluide à engrenage interne

Country Status (5)

Country Link
US (1) US11971033B2 (fr)
EP (1) EP4185773B1 (fr)
CN (1) CN116917623A (fr)
DE (1) DE102020209407A1 (fr)
WO (1) WO2022018022A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020209406A1 (de) * 2020-07-24 2022-01-27 Eckerle Technologies GmbH Innenzahnradfluidmaschine
US12313068B2 (en) * 2021-08-05 2025-05-27 Hydraulik Nord Technologies GmbH Internal gear machine with helical toothing
DE102023202575A1 (de) * 2023-03-22 2024-09-26 Eckerle Technologies GmbH Innenzahnradfluidmaschine

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GB1269643A (en) 1968-07-19 1972-04-06 Lucas Industries Ltd Internally-meshing gear pumps and motors
US3824041A (en) 1972-08-01 1974-07-16 C Rystrom Positive displacement liquid pump
DE2547994C2 (de) 1975-10-27 1985-07-04 Sperry Corp., Troy, Mich. Zahnradpumpe oder -motor
DE7538960U (de) 1975-12-06 1977-06-08 Voith Getriebe Kg, 7920 Heidenheim Innenzahnradpumpe
JPS54152209A (en) 1978-05-20 1979-11-30 Tokico Ltd Gear pump
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DE4421255C1 (de) 1994-06-17 1995-06-29 Otto Eckerle Füllstücklose Innenzahnradpumpe
DE19930911C1 (de) 1999-07-06 2000-07-20 Voith Turbo Kg Axialkompensation einer Innenzahnradpumpe für den geschlossenen Kreislauf
DE102009024216A1 (de) 2008-06-26 2009-12-31 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Verdrängermaschine
DE102008053318A1 (de) 2008-10-27 2010-04-29 Trw Automotive Gmbh Reversibel betreibbare Zahnradmaschine, sowie Fahrzeuglenksystem und Verfahren zur Steuerung eines Fahrzeuglenksystems
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JP6633901B2 (ja) 2015-12-04 2020-01-22 株式会社Ｓｕｂａｒｕ オイルポンプシステム
DE102018008905A1 (de) 2018-11-13 2020-05-14 Bastian Voigt Hohlzapfenpumpe mit Fördermengenregelung

Also Published As

Publication number Publication date
DE102020209407A1 (de) 2022-01-27
CN116917623A (zh) 2023-10-20
US11971033B2 (en) 2024-04-30
WO2022018022A1 (fr) 2022-01-27
EP4185773A1 (fr) 2023-05-31
US20230296093A1 (en) 2023-09-21

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