EP3212935A2 - Pompe à engrenage à denture intérieure et procédé de pompage - Google Patents

Pompe à engrenage à denture intérieure et procédé de pompage

Info

Publication number
EP3212935A2
EP3212935A2 EP15780903.9A EP15780903A EP3212935A2 EP 3212935 A2 EP3212935 A2 EP 3212935A2 EP 15780903 A EP15780903 A EP 15780903A EP 3212935 A2 EP3212935 A2 EP 3212935A2
Authority
EP
European Patent Office
Prior art keywords
rotor
ring element
fluid
housing
internal 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.)
Granted
Application number
EP15780903.9A
Other languages
German (de)
English (en)
Other versions
EP3212935B1 (fr
Inventor
Michael Kuehner
Sven Schuster
Andreas ELLER
Mark Schweiher
Harald Ihben
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.)
Magna PT BV and Co KG
Original Assignee
Getrag BV and Co KG
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 Getrag BV and Co KG filed Critical Getrag BV and Co KG
Publication of EP3212935A2 publication Critical patent/EP3212935A2/fr
Application granted granted Critical
Publication of EP3212935B1 publication Critical patent/EP3212935B1/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
    • F04C2/102—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

Definitions

  • the present invention relates to an internal gear pump, in particular for a hydraulic circuit of a motor vehicle drive train, having a housing, which preferably has a first fluid port and a second fluid port, with an inner rotor which is rotatably mounted in the housing about an inner rotor axis and has an outer toothing , and an outer rotor rotatable within the housing about an outer rotor axis and having internal teeth meshing with the outer teeth of the inner rotor for pumping action.
  • the present invention relates to a pump assembly having a pivotable ring member having a pump which promotes fluid in a first direction of rotation in a first flow direction, in particular an internal gear pump of the type described above.
  • the present invention relates to a method for operating an internal gear pump, in particular an internal gear pump of the above type, wherein the internal gear pump has a rotor set and a ring member, wherein the ring member is pivotally limited, wherein the rotor set a rotor element with a first rotor axis and a second rotor element having a second rotor axis, wherein the ring element is pivotable about the first rotor axis.
  • the present invention relates to a hydraulic circuit, in ⁇ particular for a motor vehicle drive train, with such an internal gear pump. 2015/073928
  • Gear pumps generally distinguish between external gear pumps, internal gear pumps and gerotor pumps.
  • the term of the internal gear pump is intended herein to include the term of the ring gear pump.
  • an inner rotor and an outer rotor are eccentric to each other.
  • the internal toothing usually has exactly one more tooth than the external toothing.
  • the number of teeth of the internal teeth is significantly larger than those of the external teeth, wherein the teeth are sealed by a sickle.
  • Such pumps are well known. In hydraulic circuits of motor vehicle drive trains, such pumps can be driven electrically, by means of an electric motor which, for example, drives the inner rotor. The pumps are used, for example, to generate a working pressure for a hydraulic actuator. Another use is the supply of clutch and transmission components with lubricating and / or cooling oil.
  • Such components can each be regarded as hydraulic consumers.
  • a hydraulic consumer for lubrication and / or cooling of a dual-clutch transmission can be used, whereas another hydraulic consumer is formed by a cooling circuit of a drive motor, which may be formed, for example in the form of an electric machine for providing drive power to the motor vehicle.
  • Another way to supply two hydraulic consumers by means of a pump is to design the pump bidirectional. Depending on the direction of rotation then one of the two fluid ports of the pump is a pressure port, and the other is then a suction port. Since, in this case too, fluid generally has to be delivered from a sump, it is then necessary via an elaborate non-return valve arrangement, which includes, for example, four non-return valves, to draw in fluid from the fluid sump in each rotational direction and release it via the respective pressure port ,
  • the pivoting of the ring element takes place when reversing the direction of rotation due to a friction effect.
  • the ring member is taken in reversing the drive direction of rotation by viscous fluid friction in the direction of rotation until the ring member has reached the opposite pivot position.
  • the pivoting of the ring element is thus effected by a drag torque, which is caused by viscous shear friction in the fluid between the outer rotor of the rotor set and a ring receiving the ring element. This can cause the ring element does not swing immediately or not completely.
  • the duration of the pivoting operation of the ring element can vary greatly, depending, inter alia, on the temperature and viscosity of the pumped fluid.
  • the document DE 27 42 821 A1 discloses as a friction device, a leaf spring and a coupling device acting on the outer rotor.
  • document DE 35 43 488 C2 discloses for this purpose a slotted eccentric with a slight clamping effect at low pump speeds. Furthermore, document DE 197 19 692 B4 discloses a friction device with a band spring placed around the outer rotor.
  • publication DE 10 2013 1 10 400 A1 discloses an internal gear pump in which at least one third fluid port is formed on the housing, wherein the third fluid port is arranged with respect to the ring element such that the third fluid port in the first position of the ring member is connected to the second fluid port and is separated in the second position of the ring member from the second fluid port.
  • this ring element 400 proposed to use this ring element as a kind of valve spool, which connects in one position another fluid port to the second fluid port, and in a second position of the ring member separates the third fluid port from the second fluid port.
  • a pump assembly having a pivotable ring member having a pump which promotes fluid in a first direction of rotation fluid in a first flow direction, in particular with an internal gear pump of the type according to the invention, and with a valve assembly which in a reversal of the direction Pump prevents reversal of the flow direction to promote pivoting of the ring member.
  • the above object is achieved in the aforementioned method for operating an internal gear pump, characterized in that a pivoting of the ring element between a first position and a second position in at least a direction is supported by the fact that the first and the second rotor element are blocked against each other at least for a part of the pivoting range.
  • an improved hydraulic circuit can be realized, in particular for a motor vehicle drive train.
  • a blocking of the rotor set is understood herein that the inner ring and the outer ring are not or only slightly against each other rotatable.
  • the rotation of the ring element takes place in the said part of the pivoting area forcibly, so not only supportive.
  • the activation of the blocking preferably takes place when the direction of rotation is reversed. Preferably, the activation of this blockage of the rotor set takes place automatically.
  • the pivoting of the ring element can be effected substantially due to viscous fluid friction, in particular shear friction in the region between a rotor receptacle of the ring element and the outer rotor.
  • the pivoting of the ring element can be realized in reversing the direction of rotation with a higher security.
  • gerotor pumps the internal gear pump
  • the present application relates to gerotor pumps.
  • the inner rotor axis and the outer rotor axis are offset eccentrically.
  • the inner rotor (or the outer rotor) is driven, preferably by means of an electric motor, which is directly associated with the pump and therefore does not serve to provide drive power for a motor vehicle.
  • a first fluid port of the housing may, for example, be connected to a tank or a reservoir for hydraulic fluid.
  • a second fluid connection can be designed, for example, as a pressure connection.
  • the ring element is pivoted within the housing about an axis eccentric to the inner rotor axis.
  • the ring member is rotatably mounted in the housing about a ring element axis between a first rotational position and a second rotational position and has a rotor receptacle for rotatably receiving the outer rotor, wherein the rotor receptacle is formed eccentrically to the ring element axis.
  • the ring element axis is preferably equal to the inner rotor ⁇ axis. Further, it is particularly advantageous if a first fluid port of the housing is formed independently of the direction of rotation of the inner rotor as a suction port and when a second fluid port is formed independently of the direction of rotation of the inner rotor as a pressure port.
  • the ring member in particular serves to maintain the pumping direction independently of the drive rotational direction, but can also be used to reverse the pumping direction.
  • the ring element is in particular designed as an eccentric ring, in which the outer rotor is mounted eccentrically with respect to the inner rotor axis.
  • an outer rotor receptacle of the ring element is preferably offset eccentrically to the inner rotor axis.
  • the Ringele ⁇ ment but is preferably rotatable about the same axis as the inner rotor.
  • the outer rotor preferably has one more tooth than the inner rotor.
  • a fluidic blocking is understood to mean that at least one fluid space between the inner rotor and the outer rotor essentially maintains a constant volume over at least part of the pivoting region of the annular element, ie essentially has no outflow and no inflow.
  • a fluidic blocking or hydraulic blocking or blocking is preferably self-locking.
  • the fluidic blocking therefore takes place through the valve arrangement.
  • a mechanical locking device may be provided. This can be designed in the manner of a coupling which is actuated electrically, magnetically, fluidically or in any other way.
  • a first and a second volume variable fluid space are formed, wherein the housing has a first fluid passage for connection to the first variable volume fluid chamber and a second fluid channel for connection having the second variable volume fluid space.
  • One of the two fluid spaces is a displacement volume which is connectable to a pressure port of the pump, wherein the other fluid space is formed as an expansion volume, which is connected to a suction port of the fluid pump.
  • the fluid spaces are not fixed spaces, but are formed again and again due to the meshing between the inner rotor and outer rotor, in particular, since the outer rotor preferably has one more tooth than the inner rotor.
  • the fluid spaces Depending on the direction of rotation, each can be designed as a displacement volume or as an expansion volume.
  • the fluid spaces may be formed by means of a sickle, but are preferably formed directly between the inner rotor and the outer rotor.
  • first volume-variable fluid space and the first Fiuidkanal and / or the second volume-variable fluid space and the second Fiuidkanal be shut off against each other.
  • the pump has at least one transfer channel, which connects a volume-variable fluid space between the inner rotor and the outer rotor and a fluid passage connected to a fluid port in the housing in a pump pivot position of the ring element and in FIG a shut-pivot position is at least partially locked.
  • the pump pivoting position may be the first or the second position of the ring element, in particular one of the end positions of the ring element.
  • the shut-off pivot position is preferably between the first and the second position and may be formed by a pivoting range which is smaller than 180 °, preferably smaller than 150 °, in particular smaller than 120 °.
  • the transfer channel can be shut off in the shut-off pivot position by a separate slide, or by the ring member or a 8th
  • Section of the housing or the like It is preferred if the shut-off of the transfer channel takes place by a twisting operation of such an element.
  • the shut-off is preferably complete in the shut-off pivot position, except for any leakage losses.
  • the pump has a first and a second transfer channel, one of which is associated with a pressure port and the other a suction port of the pump.
  • the ring element has a ring bottom extending in the radial direction.
  • While ring members such as eccentric rings are generally formed in the prior art as pure ring members extending around the outer rotor, in this aspect, the ring member has a ring bottom extending in the radial direction.
  • the ring member preferably has an axially extending ring gear disposed about the outer rotor.
  • Ring bottom and annular ring are preferably connected to one another at an axial end of the annular ring.
  • the compound preferably extends over at least 180 °, in particular at least 270 °.
  • the ring bottom is preferably arranged in the axial direction between the rotor set of the outer rotor and the inner rotor and a bottom of a housing portion.
  • the ring bottom can be used for a variety of purposes and can improve the variability of the pump.
  • the transfer channel is formed in the ring bottom and extends substantially in the axial direction.
  • the transfer channel is aligned in the first and the second position of the ring member with a fluid channel in the housing to establish the connection between the fluid chamber and the Fluidka ⁇ signal.
  • the fluid channel is preferably connected to a terminal of the housin ⁇ ses.
  • the transfer channel is in a position in which it is no longer aligned with the fluid channel and consequently to the housing is shut off.
  • the ring element forms for this case itself a kind of valve spool to align the transfer channel either with a fluid channel and connect, or shut off from the fluid channel.
  • the transfer channel preferably extends in the axial direction through the ring bottom.
  • a kidney-shaped recess is formed in the annular bottom of the Ringeiementes, which is connected in a pump pivot position of the ring member with a variable volume fluid space between the inner rotor and the outer rotor.
  • the kidney-shaped recess preferably does not extend in the axial direction through the ring bottom, but is formed as a shallow recess on the rotor set facing side of the ring bottom. Its cardioid From ⁇ perception here forms the suction or the pressure kidney of the pump. It is particularly preferred if the kidney-shaped recess is connected to a transfer channel extending axially through the ring bottom.
  • the transfer channel preferably extends from a bottom of the kidney-shaped recess to an opposite axial end of the ring bottom of the ring member.
  • the pump preferably has two transfer channels in the annular bottom, and two kidney-shaped recesses which are associated with the respective transfer channels, to form in this way a pressure kidney and a suction kidney of the pump.
  • the suction kidney and the pressure kidney are not fixed to the housing in the pump according to the invention, but are formed on the annular bottom of the ring member, but in the end positions of the ring member each fulfill the function of Saugniere and Druckniere.
  • the kidney-shaped recesses are preferably designed symmetrically for this purpose, so that each of the kidney-shaped recesses, depending on the position of the ring element, can act either as Saugniere or as Druckniere.
  • the housing has a housing base and a housing pot, wherein the housing base has an axial recess into which the housing pot is inserted, wherein the housing pot has a ring element receptacle for rotatably receiving the ring element.
  • the ring element is arranged directly in an axial recess of the housing base to be stored twisted within such a ring element receptacle. Due to the rotatable mounting of the ring element in a ring element receiving a housing pot, which is inserted into an axial recess of the housing base, however, a variety of other functions can be realized inexpensively, such as other fluid connections, bypass and diaphragm functions, valve functions, etc. 15 073928
  • the housing pot is preferably arranged concentrically to the inner rotor axis, so that the ring element receptacle is aligned concentrically to the inner rotor axis.
  • the housing pot is preferably rotatably received within the housing base.
  • the fluid channels in the housing are formed by bores or the like in the housing base and by axially aligned pot channels extending through the housing pot bottom.
  • these pot channels can be connected with distribution kidney or the like, for example, to be able to connect several fluid channels to such an axial channel.
  • the housing base is connected to an eccentric pin, such that the housing pot is fixed rotationally relative to the housing base via the eccentric pin and / or the eccentric pin forms a rotational stop for the annular element.
  • the eccentric pin which can fulfill both functions mentioned (although for this purpose, however, two separate pins can be provided) preferably extends from a recess bottom of the axial recess of the housing base in the axial direction.
  • the housing pot has at its bottom and / or in the region of its outer periphery an opening which is penetrated by the eccentric pin.
  • the ring element has on its outer circumference preferably two circumferentially offset radial shoulders which abut on the eccentric pin depending on the rotational position (in the end positions of the ring element). Between the radial shoulders, a radial recess is preferably formed, which is preferably aligned concentrically with the inner rotor axis.
  • the ring element has on its outer circumference at least one circumferential groove portion, by means of which, depending on a rotational position of the ring element, a hydraulic bypass and / or a diaphragm function can be set up.
  • the ring element can fulfill further functions of such a pump.
  • an outer circumferential opening is formed on a housing pot, within which the ring element is rotatably mounted.
  • This may be formed, for example, for fluid communication with such a circumferential groove portion of the ring member.
  • the aperture may also be formed for fluid communication with fluid channels in the housing base or the like.
  • blockage of the rotor set is achieved by shutting off at least one fluid chamber of the rotor set, it is also possible in an alternative embodiment that a pressure in the variable volume fluid space during at least a part of a pivoting operation of the ring element by an external or separate pressure source is applied.
  • Such a pressure source can in particular be formed by a pressure accumulator.
  • the internal gear pump according to the invention and the associated method for its operation preferably includes at least one of the following measures.
  • the rotor set (consisting of inner and outer rotor) preferably runs in a ring element with an eccentric outer rotor receptacle, wherein the ring element at least on one side has a bottom and has there transfer channels to the fixed housing of the pump.
  • the ring element is pivoted, whereby the pivoting process is initially achieved in a comparable manner as in the prior art by viscous shear friction of the fluid.
  • the thus locked rotor set acts as a pivoting cam for the ring member, which is taken in this pivotal movement until the ring member reaches the other end position in the housing.
  • the transfer channels are reconnected to fluid channels in the housing, so that the fluid of the fluid cushion can flow away and the blockage of the rotor set is released. This can be set up shortly before reaching the end position, so that the last area of the pivoting process up to the end position again takes place via viscous shear forces (fluid friction).
  • the goal of secure switching can be achieved.
  • the transfer channels can be replaced by radial transfer channels
  • the ring bottom of the ring element could also be designed separately from the ring element, so that the ring bottom, which is embodied separately from the ring element, acts as a type of valve slide.
  • the ring element could also be designed as a closed sub-housing, with ring floors attached on both sides.
  • the transfer ducts can be designed in many different forms and in several parts, wherein the transfer cross section can be designed to be pivotally dependent on specific angles by using a plurality of bores.
  • the application of the closable transfer points or channels to improve the switching behavior can be used in all internal gear pumps for changing directions of rotation with ring element.
  • fluid connections of the internal gear pump when the ring element is used as a valve spool or rotary valve, can be set up for further functions by means of the internal gear pump, for example as a switching element for a mechanical changeover valve.
  • the switching behavior can be significantly improved over prior art solutions, especially at low fluid viscosities (e.g., transmission oil at higher operating temperatures). Switching safety does not have to be bought with an increased frictional torque (efficiency deterioration) during operation of the pump.
  • the internal gear pump can be designed with a small number of components and can be mounted inexpensively.
  • a risk of sticking of the ring element in a central position is extremely reduced by the proposed solution.
  • the pivoting of the ring element can be extremely fast in the proposed solution, with complete hydraulic blockage by entrapped fluid preferably within half a turn at the drive of the pump.
  • waiting times for the pivoting of the ring element are minimized, since the pivoting moment does not have to be generated solely by the drag torque (caused by the viscous shear friction in the fluid between the outer rotor and the ring element), but is provided by a drive torque of the drive of the internal gear pump itself can.
  • a constant speed difference is required to establish this shearing friction.
  • a third fluid connection and / or a fourth fluid connection of the housing is connected to a consumer section of the hydraulic circuit.
  • a hydraulic consumer section can always be under Be supplied pressurized hydraulic fluid.
  • a hydraulic consumer connected to the third fluid connection can be supplied with pressurized hydraulic fluid as a function of the direction of rotation of the driven ring element.
  • a further hydraulic consumer portion in depen ⁇ dependence may be powered by the rotational direction about the fourth fluid connection.
  • the hydraulic circuit includes a hydraulically pilot operated valve which is connected to the first or the second fluid port of the internal gear pump, wherein the valve is actuated in dependence on the position of the ring member or in dependence on a direction of rotation of the inner rotor.
  • such a valve can be arranged in spatial proximity to the pump and / or within a drive train housing, and that the valve is preferably not to be operated via a control line from a central control device. Consequently, a demand-based switching of a volume flow of hydraulic fluid with a minimum number of components can be realized, and this with a small footprint and low component and assembly costs.
  • valve is actuated by means of a directly or indirectly acting actuator, wherein the actuating device is connected to the third fluid port and / or to the fourth fluid port.
  • valve is biased into an actuating position by means of a spring, it is sufficient if the actuating device is connected to one of the third and fourth fluid connection.
  • the valve may be provided with actuators acting in opposite directions, one actuator connected to the third fluid port and the other actuated to the fourth fluid port. 2015/073928
  • the valve is operable by means of an electric actuator, wherein the internal gear pump is associated with a rotational position sensor arrangement which detects the rotational position of the ring member and outputs a rotational position signal, and wherein the electrical actuator is driven based on the rotational position signal ,
  • valve can be actuated by means disposed in close proximity to the internal gear pump.
  • the rotational position sensor arrangement can be connected to a switch, for example a switch relay.
  • the rotational position sensor assembly includes an amplifier to drive the electrical actuator based on such amplified signal.
  • the valve can be actuated by means of an electric actuating device, wherein the hydraulic circuit has an electric motor which drives the inner rotor, wherein the motor is associated with a direction of rotation sensor arrangement which detects the direction of rotation of the motor and a Output direction signal, and wherein the electrical actuator is driven on the basis of the direction of rotation signal.
  • the switching of the flow rate can be achieved via means which are arranged in close spatial association with the internal gear pump.
  • the direction of rotation sensor arrangement is adapted to detect the direction of rotation of the motor on the basis of a Kommut ists Herbertn ⁇ sequence of electrical connection phases of the motor. In a further preferred embodiment, the direction of rotation sensor arrangement is adapted to detect the direction of rotation of the motor on the basis of signals of a position encoder system of the motor.
  • the internal gear pump can promote a conveyed volume flow into two different branches of a hydraulic circuit, depending on the direction of rotation of the pump or of the pump driving the motor (in particular electric motor). In order to switch over the delivery flow, no separate element and / or separate activation (current output at a central control device) is preferably required in this case.
  • a demand-based switching of the volume flow is preferably realized with a minimum number of components, thereby reduced space requirements and low component and assembly costs.
  • an electrical circuit used for this purpose may be part of a transmission control unit, part of the electric motor, part of the switching valve or part of the electrical wiring harness, for example, the electric motor supplied with drive signals and energy.
  • At least one fourth fluid port is formed on the housing, the fourth fluid port being arranged with respect to the ring element such that the fourth fluid port is connected to the second fluid port in the second position of the ring element is and is separated from the second fluid port in the first position of the ring member.
  • the pump has two pressure ports and a suction port, wherein the valve assembly comprises at least one check valve which is connected to one of the pressure ports.
  • the pump to ⁇ next attempts to reverse the direction of flow (pumping direction).
  • the use of a check valve on the pressure port can prevent such a flow direction reversal. Consequently, in the pump core or in the fluid space no fluid flow between the inner rotor and the outer rotor, so that the rotor set (inner rotor and outer rotor) is hydraulically blocked because the volume can not change.
  • the inner rotor and outer rotor of the rotor set can no longer move relative to each other, so that the pump drive tries to rotate the eccentrically mounted rotor set as a unit, which is geometrically possible only if the pump core (rotor set) together with the ring element (envelope ring ) twisted.
  • the forces acting in this case on the ring element in the direction of rotation are significantly higher than those torques resulting from the torques of frictional forces.
  • the start of the rotational movement of the ring element can thereby be done reliably and quickly.
  • the rotation of the ring element can be supported only at a reversal of direction.
  • the turn of the ring element can be assisted in both directions.
  • the pump has two pressure ports and a suction port and if the valve assembly comprises at least one check ⁇ valve, which is connected to the suction port.
  • the flow resistance is on the suction side. Possibly. As a result, the Kavitationsne Trent the pump may worsen, but it is preferably only one valve for both reversals required.
  • the check valves can be classified ⁇ be outside the pump housing.
  • At least one check valve is integrated in a housing of the pump or in the ring element itself.
  • the ring member can be rotated quickly and safely, so that after a reversal of the direction of rotation of the pump drive a dead time is minimized, in which the pump promotes little or no fluid.
  • Fig. 1 is a schematic representation of an internal gear pump with a
  • FIG. 2 shows the internal gear pump of FIG. 1 with the ring element in a second rotational position
  • FIG. 3 shows a longitudinal section through an internal gear pump according to an embodiment of the invention
  • Fig. 4 is an exploded view of the internal gear pump of Fig. 3;
  • FIG. 5 is a perspective view of a housing pot of the internal gear ⁇ pump of Figures 3 and 4.
  • Fig. 6 is another perspective view of the housing pot of Fig. 5; 3928
  • FIG. 7 shows a perspective view of a ring element of the internal gear pump of FIGS. 3 and 4;
  • Fig. 8 is another perspective view of the ring member of Fig. 7;
  • Fig. 9 is a sectional view taken along the line IX-IX of Fig. 3;
  • Fig. 10 is a partial sectional view of the internal gear pump of Figs. 3 to 9, with the ring member in a first position;
  • FIG. 11 is a view similar to FIG. 10, with the ring element in an intermediate position;
  • FIG. 12 is a view similar to FIG. 10, wherein the ring element is in a second position (second end position); FIG.
  • FIG. 13 shows a motor vehicle drive train with a hydraulic circuit in schematic form
  • FIG. 14 shows a further embodiment of a hydraulic circuit for a motor vehicle drive train in schematic form.
  • an internal gear pump 10 is shown schematically.
  • the internal gear pump 10 includes a housing 12, a schematically indicated inner rotor 14 and a schematically indicated outer rotor 16, wherein the inner rotor 14 and the outer rotor 16 form a rotor set 18.
  • the internal gear pump 10 is preferably designed as a toothed ring pump or gerotor pump so that an internal toothing, not shown, of the outer rotor 16 has one more tooth than the outer toothing of the inner rotor 14.
  • a pumping effect is achieved by the transport of the fluid in the gaps of the rotor toothings realized.
  • the inner rotor 14 is driven, in particular by means of an electric motor.
  • a ring member 20 is mounted in the manner of a reversing ring.
  • the 25 element 20 is pivotable concentrically to an axis of the inner rotor 14 between two rotational positions, one of which is shown in Fig. 1 at A.
  • the ring member 20 further includes an unspecified outer rotor receptacle formed eccentrically with respect to the inner rotor axis.
  • a first fluid port 22 is formed, which is preferably formed as a suction port and connected to a tank. Furthermore, the housing 12 has a second fluid connection 24, which is preferably designed as a pressure connection.
  • the internal gear pump 10 is driven with a first rotational direction.
  • the pressure level at the first fluid port 22 is designated P L.
  • the pressure level at the second fluid port 24 is designated P H , where P H > P
  • a third fluid port 26 of the housing 12 is connected to the second fluid port 24, so that there is also a pressure level P H there.
  • the housing 12 has a fourth fluid connection 28, which is not connected to the second fluid connection 24 in the illustrated rotational position A of the ring element 20, so that there prevails a pressure level P L , but not necessarily equal to the pressure level P L in the first Fluid connection 22 must be.
  • Fig. 2 shows the internal gear pump 10 of Fig. 1, wherein the ring member 20 is in a second rotational position B. Further, the inner rotor 14 is driven in an opposite direction of rotation. In this case, there is still a pressure level P L at the first fluid connection 22 and a pressure level P H at the second fluid connection 24.
  • the third fluid connection 26 is preferably separated from the second fluid connection 24 via the ring element 20, so that there prevails a pressure level P L.
  • a fourth fluid connection 28 is provided, it is preferably connected to the second fluid connection 24 in the second rotational position B of the ring element 20, so that there prevails a pressure level P H.
  • the ring element 20 has a rotor receptacle 34, which is formed eccentrically with respect to the inner rotor axis 32.
  • the outer rotor 16 is received within the rotor seat 34 and rotatably supported therein.
  • the outer rotor axis 36 is arranged eccentrically with respect to the inner rotor axis 32 due to the eccentricity of the rotor receptacle 34.
  • this forms between an outer peripheral portion of the ring element 20 and an inner peripheral portion of the housing 12 within which the ring element 20 is rotatably mounted, an annular space 38, which in the present case over an angular range of extends about 180 °.
  • FIG. 1 further shows that the internal gear pump 10 has a suction kidney 40 which is connected to the first fluid port 22. Furthermore, the fluid pump 10 has a pressure kidney 42, which is connected to the second fluid port 24. These compounds are not shown in each case.
  • a schematically illustrated first connection 44 between the pressure kidney 42 and shown in Fig. 1 annular space 38 is further shown, wherein the annular space 38 is connected in the rotational position A with the third fluid port 26.
  • the internal gear pump 10 further includes a second connection 46 between the pressure kidney 42 and another inner peripheral portion of the housing 12, which is covered in the rotational position A by the ring member 20.
  • the ring element 20 consequently acts as a control slide which connects the second fluid connection 24 to the third fluid connection 26 in the first rotational position A shown in FIG.
  • connections 44, 46 shown are only of a schematic nature and are intended to indicate that, depending on the rotational position of the ring element 20, either the third fluid port 26 or the fourth fluid port 28 is connected to the second fluid port 24, so that the functionality is achieved , which is shown in Figs. 1 and 2.
  • the fluid ports 26, 28 and the connections 44, 46 are optional.
  • the direction of rotation of the inner rotor 14 shown in Fig. 1 is denoted by 48, the opposite direction of rotation with 49.
  • the housing 12 of the internal gear pump 10 has a stop 50, by means of which the ring element 20 can be held in the respective rotational positions A, B.
  • the stop 50 is presently formed for the sake of simplicity by a pin 52 which passes through a wall of the housing 12 and depending on the rotational position on a first shoulder 54 or on a second shoulder 56 of the ring member 20 engages.
  • the shoulders 54, 56 enclose the annular space 38 in the circumferential direction between them.
  • a first fluid chamber 58 is arranged, and a second fluid chamber 60.
  • the first fluid chamber 58 is via the suction kidney 40 and a schematically indicated first fluid channel 62 in the housing 12 connected to the first fluid port 22.
  • the second fluid space 60 is connected via the pressure kidney 42 to a second fluid channel 64 in the housing 12, wherein the second fluid channel 64 is connected to the second fluid port 24.
  • FIGS. 3 to 9 show a further embodiment of an internal gear pump 10 ', which corresponds in terms of structure and mode of operation of the internal gear pump of FIGS. 1 and 2.
  • the same elements are therefore identified by the same reference numerals.
  • the following section essentially explains the differences. 15 073928
  • the housing 12 has a housing base 70 and a housing cover 72.
  • an axial recess 74 is formed, which is closed by the housing cover 72 in the axial direction.
  • the housing 12 further includes a housing pot 76 which is inserted into the axial recess.
  • the housing pot 76 has a ring element receptacle 78 (see also FIG. 5), within which the ring element 20 is accommodated coaxially with the inner rotor axis 32.
  • the axial recess 74 has a recess bottom 80.
  • the housing pot 76 is arranged in the axial direction between the recess bottom 80 and the housing cover 72.
  • the internal gear pump 10 'by means of a drive motor 82 can be driven, for example in the form of an electric motor.
  • the inner rotor 14 is rotatably supported by a bearing pin 84 with respect to the ring member 20.
  • the housing pot 76 has a pot ring or -kränz 88 which extends substantially in the axial direction, and a pot bottom 90.
  • the pot bottom 90 is disposed in the axial recess 74 adjacent to the recess bottom 80.
  • the pot ring 88 extends from this in the axial direction up to the housing cover 72.
  • the housing pot has a first pot channel 92 and a second pot channel 94.
  • the first pot channel 92 forms part of the first fluid channel 62.
  • the second pot channel 94 forms part of the second fluid channel 64.
  • a manifold portion 98 is formed, which is formed in the manner of a bag recess in the pot bottom 90.
  • the first cup channel 92 extends from one axial end toward the opposite axial end of the cup bottom 90.
  • the second cup channel 94 extends from a bottom of the manifold portion 98 in the axial direction toward the opposite axial end of the cup bottom 90.
  • a radial recess 100 is further formed, which extends over a 15 073928
  • the housing pot 76 also has a pin receptacle 102, along which the eccentric pin 52 is guided, as best seen in FIGS. 3 and 4.
  • a pin receptacle 102 On a peripheral wall of the axial recess 74 an axially extending, unspecified radial recess is provided which serves together with the pin receptacle 102 for receiving the pin 52.
  • the housing pot is fixed in the direction of rotation with respect to the housing base 70.
  • the pin 52 can serve as a stop for the ring member 20 due to the radial recess 100, which is located within the ring member receptacle 78 of the housing pot 76.
  • first outer circumferential opening 104 and / or a second outer circumferential opening 106 may be formed on the pot ring 88.
  • the openings 104, 106 may each be parts of the connections 44 and 46, respectively.
  • the radial recess 100 is connected to the distributor region 98 in the radial direction such that fluid can pass from the distributor region 98 into a circumferential region between the inner circumference of the annular element receiver 78 and the outer circumference of the annular element 20.
  • the ring element 20 is shown in Figures 4 and 7 and 8 closer Darge ⁇ represents.
  • the ring element 20 includes an annular ring 1 12 extending in the axial direction and a ring base 14. On the ring bottom, a first transfer channel 1 16 is formed and a second transfer channel 1 18. The over ⁇ gabekanäle 1 16, 1 18 extend in the axial direction through the ring bottom 1 14 therethrough. The transfer channels 1 16, 1 18 are associated with the pot channels 92, 94. In the two end positions of the ring member 20 (first rotational position A and second Drehpositi ⁇ on B of Fig. 1 and 2) are the transfer channels 1 16, 1 18 is aligned with the respective plug channel 92, 94, so that the fluid chambers 58, 60 (see Also Fig. 4) over the EP2015 / 073928
  • Transfer channels 1 16, 1 18 and the pot channels 92, 94 may be connected to respective fluid channels 62, 64 in the housing (and / or with other channels).
  • the ring member 20 has at its outer periphery between the first shoulder 54 and the second shoulder 56 has a pivoting recess 120, within which the pin 52 is guided during a pivoting operation.
  • the ring bottom 1 14 on its side facing the rotor set 18, a first kidney-shaped recess 122 and a second kidney-shaped recess 124 which do not extend through the ring bottom 1 14 therethrough.
  • the transfer channels 1 16, 1 18 connect respective bottoms of the kidney-shaped recesses 122, 124 with the axially opposite side.
  • the kidney-shaped recesses 122, 124 in the rotational positions A, B each form a suction or pressure kidney.
  • the ring member 20 On the outer periphery in the region between the first shoulder 54 and the second shoulder 56, in the circumferential direction subsequent to the Verschwenkaus Principleung 120, the ring member 20 has a first torquenutabrough 126 and a second torquenutabrough 128.
  • the groove sections 126, 128 can be of different widths and depths in the axial and in the radial direction and can realize bypass functions and / or diaphragm functions, for example for a partial flow of the pumped fluid passed through them.
  • Figures 10 to 12 show the internal gear pump 10 'of Figures 3 to 9, respectively in an assembled state.
  • Fig. 10 shows the pump while in a state in which the ring member 20 is in a first rotational position A.
  • Fig. 12 shows the ring member 20 in a second rotational position B.
  • the rotational positions A, B correspond to end positions of the ring element.
  • Fig. 1 1 shows an intermediate position C of the ring member, wherein the ring member between the positions A and B is located. 8th
  • FIG. 10 shows a state in which the inner rotor 4 is driven in the first rotational direction 48.
  • the shoulder 54 is in abutment with the eccentric pin 52.
  • the outer rotor 16 rotates in the same direction.
  • the pot channels 92, 94 and the transfer channels 1 16, 1 18 are aligned with each other.
  • fluid is drawn in from the first fluid space 58 and discharged via the second fluid space 60 under pressure.
  • Fig. 12 shows the opposite direction of rotation 49 of the inner rotor, wherein the ring member 20 is in the second rotational position and the shoulder 56 abuts the pin 52.
  • FIG. 11 shows an intermediate position C of the ring element 20.
  • the direction of rotation 48 is reversed, the following happens.
  • the outer rotor is also driven in the opposite direction of rotation by the inner rotor 14. Due to viscous shear friction between the outer rotor and the ring member 20, the ring member is then taken in this new direction of rotation 49.
  • the first transfer channel 1 16 is no longer aligned with the first pot channel 92 (and the second transfer channel 1 18 is therefore no longer aligned with the second pot channel 94), that is between the inner rotor and the Outer rotor caught fluid present and the inner rotor 14 and the outer rotor 16 are fluidly blocked.
  • the blocked fluid space is shown schematically at 130 in FIG. 11. 3928
  • a drive train for a motor vehicle is shown in schematic form and generally designated 140.
  • the powertrain 140 includes a drive motor 142.
  • the drive motor 142 may be an internal combustion engine, but may also be an electric drive motor to provide drive power.
  • the powertrain 140 further includes a clutch assembly 144, which may be a single clutch or a dual clutch assembly.
  • the powertrain 140 includes a transmission assembly 146, which may include a single stage or multi-stage transmission, and a non-shiftable or shiftable transmission. In the case of a shiftable transmission, the transmission assembly 146 may be a dual clutch transmission.
  • the powertrain may further include an electric prime mover 147.
  • the drive train 140 includes a differential 148, by means of which drive power can be distributed to two driven wheels 150L, 150R of the motor vehicle.
  • the drive train 140 further includes a hydraulic circuit 160.
  • an internal gear pump 10 is provided, which is preferably formed in terms of functionality as one of the internal gear pumps 10, 10 'of Fig. 1 to 12.
  • the internal gear pump 10 is an electric motor 82 driven, wherein the electric motor 82 can be driven in both directions of rotation, as is schematically indicated in Fig. 13 by a double arrow.
  • the second fluid port 24 and the third fluid port 26 and optionally a fourth fluid port 28 of the internal gear pump 10 may be directly connected to hydraulic consumer sections, as will be discussed below.
  • the first fluid connection 22 is connected to a low-pressure region or a tank 162.
  • the hydraulic circuit 160 includes a valve 164, which in the present case is designed as a 3/2-way valve.
  • the valve 164 includes a first hydrau ⁇ lic actuator 166 to bring the valve 164 in a first switching position.
  • the valve 164 may include a return spring 170, which counteracts the first hydraulic actuator 166.
  • the first hydraulic actuator For example, the supply device 166 can be connected to the third fluid connection 26.
  • valve 164 has a second hydraulic actuator 168.
  • the second hydraulic actuator 168 is preferably connected to the fourth fluid port 28.
  • An input of the valve 164 is connected to the second fluid port 24.
  • a first output of the valve 164 is connected to a first hydraulic consumer section 172, which may be associated with the clutch assembly 144, for example.
  • a second output of the valve 164 is presently connected to a second hydraulic consumer section 174, which may be associated, for example, with the gear arrangement 146 or the drive motor 142.
  • a central control device 176 (transmission control device) is provided, which controls the consumer sections 172, 174.
  • the third fluid port 26 may also be directly connected to a consumer section, as shown here by a third hydraulic consumer section 178.
  • the third hydraulic consumer section 178 can be used, for example, to supply fluid to an electric drive motor 147 of the drive train 140, for example to cool it.
  • the electric drive motor 147 may be formed as the only drive motor of the drive train, but may also be a drive motor in the form of an electric machine of a hybrid drive train.
  • second and / or fourth fluid connection 24, 28 can also be connected directly to such a hydraulic consumer section.
  • the consumer sections are generally configured to supply certain components of the drive train 140 with fluid.
  • the consumer sections 3928 are generally configured to supply certain components of the drive train 140 with fluid.
  • Each of the actuators may include actuator means to actuate certain components of the powertrain 140, such as clutches of the clutch assembly 144 and / or clutches of the transmission assembly 146. Further, the consumer portions may each alternatively or additionally be formed as pure lubricating and / or cooling portions. Shown at 180 in schematic form is a pressure source that may act on the internal gear pump 10 to fluidly block the inner rotor and the outer rotor.
  • the pressure source 180 may include a separate pump or accumulator or the like.
  • FIG. 14 shows another embodiment of a hydraulic circuit 160 '. In terms of structure and mode of operation, this corresponds generally to the hydraulic circuit 160 of FIG. 13. The differences will be explained below essentially.
  • the pump 10 is, as in the previous embodiments, preferably an internal gear pump with ring element or envelope ring 20.
  • the turning or twisting of the ring member 20 can be effected by fluid friction, which is caused by the drive of the drive motor 82, as it in Fig. 14 is indicated schematically by a dashed line.
  • a suction port 22 of the pump 10 is connected via a fluid filter unspecified with a tank 62.
  • the pump 10 has a first pressure port 24 and a second pressure port 26.
  • the first pressure port 24 serves to supply a clutch assembly 144 'with cooling or lubricating fluid, as indicated by a consumer section 172'.
  • the second pressure port 26 serves to cool an electric drive machine 147 ', whose cooling jacket is designated as a further hydraulic consumer section 178'.
  • a first check valve 182a is arranged in the connection between the pump 10 and the first hydraulic consumer section 172 '.
  • a second check valve 182b is arranged in the connection between the second pressure port 26 and the further hydraulic consumer section 178 '.
  • the check valves are arranged so that with a promotion of fluid from the respective Pressure port 24, 26 out the respective check valve 182 a, 182 b opens.
  • fluid flow in the opposite direction from one of the consumer sections 172 ', 178' into the pump 10 is prevented by the check valves.
  • This embodiment leads to the following operation.
  • the pump 10 attempts to reverse the flow direction (pumping direction).
  • the check valves 182a, 182b such a flow direction reversal (starting from both basic directions of rotation) is prevented. Consequently, no fluid can flow into the rotor set of the pump 10.
  • the rotor set is thereby hydraulically blocked.
  • the now driven in the opposite direction of rotation rotor set is thus rotated as a unit, which is geometrically possible only when the rotor set is rotated together with the ring element (cam action).
  • the resulting moments on the envelope ring are significantly higher than those moments that could result from frictional forces due to fluid friction.
  • the start of such a rotational movement in a rotation ⁇ direction reversal of the drive motor 82 can thereby be done reliably and quickly.
  • check valves may possibly be integrated into the pump housing or in the ring member 20th

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

Abstract

L'invention concerne une pompe à engrenage à denture intérieure (10), en particulier pour un circuit hydraulique (160) d'une chaîne cinématique de véhicule à moteur (140), comprenant un carter (12) ; un rotor intérieur (14), qui est monté rotatif autour d'un axe de rotor intérieur (32) dans le carter (12) et comporte une denture extérieure ; un rotor extérieur (16), qui est monté rotatif autour d'un axe de rotor extérieur (36) dans le carter (12) et comporte une denture intérieure qui engrène avec la denture extérieure du rotor intérieur (14) pour permettre l'obtention d'un effet de pompage ; et un élément couronne (20) apte à pivoter entre une première position (A) et une seconde position (B) dans le carter (12). Selon l'invention, un pivotement de l'élément couronne (20) entre la première position (A) et la seconde position (B) dans au moins un sens est favorisé par le fait que le rotor intérieur (14) et le rotor extérieur (16) peuvent être bloqués l'un par rapport à l'autre au moins dans une partie de la plage de pivotement totale.
EP15780903.9A 2014-10-27 2015-10-15 Pompe à engrenage interne et procédé de pompage Active EP3212935B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014115548.3A DE102014115548A1 (de) 2014-10-27 2014-10-27 Innenzahnradpumpe und Pumpverfahren
PCT/EP2015/073928 WO2016066440A2 (fr) 2014-10-27 2015-10-15 Pompe à engrenage à denture intérieure et procédé de pompage

Publications (2)

Publication Number Publication Date
EP3212935A2 true EP3212935A2 (fr) 2017-09-06
EP3212935B1 EP3212935B1 (fr) 2019-10-02

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Application Number Title Priority Date Filing Date
EP15780903.9A Active EP3212935B1 (fr) 2014-10-27 2015-10-15 Pompe à engrenage interne et procédé de pompage

Country Status (3)

Country Link
EP (1) EP3212935B1 (fr)
DE (1) DE102014115548A1 (fr)
WO (1) WO2016066440A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10895257B2 (en) * 2018-02-13 2021-01-19 GM Global Technology Operations LLC Lubrication strategy for dry run pump system
DE102018118100A1 (de) * 2018-07-26 2020-01-30 Ebm-Papst St. Georgen Gmbh & Co. Kg Pumpe mit absoluter Drehwinkel-Erfassung
CN111120297A (zh) * 2020-02-05 2020-05-08 富奥汽车零部件股份有限公司 一种机动车双向转动油泵
US11965509B2 (en) * 2022-02-28 2024-04-23 Genesis Advanced Technology Inc. Energy transfer machine for corrosive fluids

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Publication number Priority date Publication date Assignee Title
CH218968A (de) * 1940-10-05 1942-01-15 Safag A G Automatische Umsteuerung einer Druckpumpe ohne Ventil.
DE1145930B (de) * 1955-06-01 1963-03-21 Carrier Corp Umkehrbare Zahnradpumpe fuer gleichbleibende Foerderrichtung bei wechselnder Drehrichtung
DE2742821C2 (de) 1977-09-23 1982-11-25 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Zahnradpumpe mit bei wechselnder Antriebsrichtung gleichbleibender Förderrichtung
US4171192A (en) 1978-05-05 1979-10-16 Thermo King Corporation Eccentric positioning means for a reversible pump
DE2936066A1 (de) 1978-09-12 1980-03-20 Concentric Pumps Ltd Pumpe
US4492539A (en) * 1981-04-02 1985-01-08 Specht Victor J Variable displacement gerotor pump
DE3543488A1 (de) 1985-12-09 1987-06-11 Schwaebische Huettenwerke Gmbh Zahnradpumpe
GB2215401B (en) 1988-02-26 1992-04-15 Concentric Pumps Ltd Gerotor pumps
US5711408A (en) 1996-05-09 1998-01-27 Dana Corporation Reversible gerotor pump
DE10305585B3 (de) * 2002-12-19 2004-02-12 Joma-Hydromechanic Gmbh Rotorpumpe
DE102008006686B4 (de) 2008-01-21 2010-03-18 Prettl, Rolf Rückschlagventil
US8734140B2 (en) 2011-01-06 2014-05-27 Gm Global Technology Operations, Llc Reversible gerotor pump
DE102013110400A1 (de) 2013-09-20 2015-03-26 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Innenzahnradpumpe und Hydraulikkreis für Kraftfahrzeugantriebsstrang

Also Published As

Publication number Publication date
WO2016066440A2 (fr) 2016-05-06
EP3212935B1 (fr) 2019-10-02
WO2016066440A3 (fr) 2016-06-23
DE102014115548A1 (de) 2016-04-28

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