EP4259375A1 - Procédé, dispositif et unité de commande pour établir un ajustement serré - Google Patents

Procédé, dispositif et unité de commande pour établir un ajustement serré

Info

Publication number
EP4259375A1
EP4259375A1 EP22703616.7A EP22703616A EP4259375A1 EP 4259375 A1 EP4259375 A1 EP 4259375A1 EP 22703616 A EP22703616 A EP 22703616A EP 4259375 A1 EP4259375 A1 EP 4259375A1
Authority
EP
European Patent Office
Prior art keywords
wedge sleeve
pressure
component
actuating force
press fit
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.)
Pending
Application number
EP22703616.7A
Other languages
German (de)
English (en)
Inventor
Nicola ACCIALINI
Matti Meissner
Christos Kallianteris
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.)
Aerospace Transmission Technologies GmbH
Original Assignee
Aerospace Transmission 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 Aerospace Transmission Technologies GmbH filed Critical Aerospace Transmission Technologies GmbH
Publication of EP4259375A1 publication Critical patent/EP4259375A1/fr
Pending legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P19/00—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes
    • B23P19/02—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes for connecting objects by press fit or for detaching same
    • B23P19/027—Machines for simply fitting together or separating metal parts or objects, or metal and non-metal parts, whether or not involving some deformation; Tools or devices therefor so far as not provided for in other classes for connecting objects by press fit or for detaching same using hydraulic or pneumatic means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P11/00—Connecting or disconnecting metal parts or objects by metal-working techniques not otherwise provided for 
    • B23P11/02—Connecting or disconnecting metal parts or objects by metal-working techniques not otherwise provided for  by first expanding and then shrinking or vice versa, e.g. by using pressure fluids; by making force fits
    • B23P11/022—Connecting or disconnecting metal parts or objects by metal-working techniques not otherwise provided for  by first expanding and then shrinking or vice versa, e.g. by using pressure fluids; by making force fits by using pressure fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/09—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces
    • F16D1/093—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping due to axial loading of at least one pair of conical surfaces using one or more elastic segmented conical rings forming at least one of the conical surfaces, the rings being expanded or contracted to effect clamping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers

Definitions

  • the present disclosure relates to a method and an apparatus for producing an interference fit between at least a first component and at least a second component and at least one wedge sleeve arranged therebetween. Furthermore, the present disclosure relates to a control device for carrying out the method and a corresponding computer program product.
  • first component is designed, for example, as a bearing pin of a planet gear of a planetary gear
  • second component is a planet carrier.
  • wedge sleeves designed as clamping sleeves are inserted or pressed in between the end areas of the bearing pin and bearing areas of the planet carrier, which radially encompass the end areas of the bearing pin.
  • a wedge sleeve is applied with its one end face to the two components and, starting from its other end face, is acted upon by the actuator or the actuating element with the axial actuating force required for insertion and thereby inserted between the bearing bolt and the planetary carrier.
  • the splined sleeves are inserted between the bearing pin and the splined sleeve and between the splined sleeve and the planet carrier by using liquid nitrogen and/or injecting high pressure oil.
  • the devices described before for making press fits are also suitable for resolving the press fits.
  • the devices are used for producing and releasing press fits in various areas of application. In particular, the devices are used in the manufacture of ship propellors, steering units, gears, flywheels, clutch hubs, roller bearings, hydraulic pumps and the like.
  • the devices used are either manually or automatically operated during the production of press fits or the release of press fits.
  • the press fit is made or released by manual operation of such a device, it is the task of the operator operating the device to apply oil or hydraulic fluid at high pressure between the facing inner and outer surfaces of the components to be joined and of the wedge sleeve arranged in between. This is to ensure that the mutually facing surfaces of the components and the wedge sleeve are expanded or shrunk during the joining process and the friction is reduced.
  • the wedge sleeve is adjusted by the press to its desired end position.
  • Joining and loosening processes for press fittings can be carried out reproducibly to the desired extent using automatically operable devices.
  • known systems are not able to adapt to different starting conditions of the joining and detaching process in the required manner.
  • both manually operated and automatically operated devices are based on the disadvantage that the process parameters for carrying out joining and detaching processes for press assemblies usually have to be determined using complex and cost-intensive test series.
  • the initial conditions can vary greatly. If, for example, the wedge sleeve is not pre-installed to the required extent relative to the components, the axial setting force to be applied to create the interference fit can increase significantly compared to proper pre-installation of the wedge sleeve. In addition, higher joining forces are required to produce an interference fit if the components to be joined or their contact surfaces are not sufficiently cleaned before the start of the process. Hard particles that are already present in the area of the facing mating surfaces of the components and the wedge sleeve increase the axial force immediately and cause irreversible damage in the area of the components and the wedge sleeve during the joining process, which is undesirable.
  • the object of the present disclosure is to provide a method and a device for producing or releasing an interference fit between at least one first component and at least one second component and at least one wedge sleeve arranged therebetween , by means of which the disadvantages described in more detail above are avoided.
  • a control unit designed to carry out the method and a computer program product to carry out the method are to be specified.
  • a method for producing or releasing a press fit between at least one first component and at least one second component and at least one wedge sleeve arranged in between is proposed. Hydraulic fluid under pressure is introduced between an outer surface of the wedge sleeve and an inner side of the second component and/or between an inner side of the wedge sleeve and an outer side of the first component during the creation or release of the interference fit. An axial positioning force is determined during the manufacture or release of the press fit.
  • the pressure with which the hydraulic fluid is introduced is automatically varied when there is an axial actuating force greater than or equal to a predefined upper limit value until the axial actuating force is less than the predefined upper limit value.
  • the pressure with which hydraulic fluid or oil is injected between the mating surfaces of the components and the wedge sleeve, around the mating surfaces or mating surfaces between, for example, a bore of the first component and an outer surface of the wedge sleeve and between them an inner surface of the wedge socket and an outer surface of the second component move away from each other and thus reduce or completely eliminate the existing friction, varies automatically depending on the operating state.
  • the next step is to move the wedge sleeve to the final position where the desired interference fit is present or to slide it out of that final position and release the interference fit.
  • the level of the pressure or the radial pressure of the hydraulic fluid is accordingly adjusted and changed during the implementation of the method according to the present disclosure.
  • This procedure avoids both plastic deformations in the area of the components and the wedge sleeve as well as the undesired generation of chips.
  • the generation of chips should be avoided as far as possible, especially during the production of the press fit.
  • the method according to the present disclosure ensures that process data on which the process of producing or releasing the press connection is based can be determined with significantly less effort than in the case of known solutions.
  • the method offers improved process control due to the adaptive control on which the method is based.
  • the procedure described is also characterized by a high level of process flexibility, since different initial conditions when joining or detaching the components and the wedge sleeve can be taken into account in a simple manner.
  • the proposed control strategy can be used to create or release press fits in various application areas. For example, there is the possibility of press fits in the area of bearings, clutches, gears, crankshafts, railway wheels, planetary gears and the like to produce or solve the proposed scope. It can be provided that by means of the method according to the present disclosure, so-called planet bolts, on which at least one planet gear is rotatably mounted, are connected in bores of a planet carrier via wedge sleeves to the planet carrier in a rotationally fixed manner.
  • the planetary carrier In such planetary gears, the planetary carrier usually rotates, subjecting the system to high centrifugal loads. In order to be able to ensure the non-rotatable connection between such planet bolts and a planet carrier despite the high centrifugal loads acting on them, wedge sleeves are used in order to produce correspondingly high press fits. It can be provided that methods for assembling and disassembling planetary gears that are used in the aerospace industry are used.
  • the radial pressure of the hydraulic fluid and the axial positioning force are correlated in real time and the radial pressure of the hydraulic fluid is corrected as needed.
  • the level of the axial actuating force is automatically defined by the system logic. This means that with little control and regulation effort it can be guaranteed that the axial force applied in each case does not exceed a predefined limit value, above which residual stresses in the area of the wedge sleeves, chip formation and, in addition, plastic deformation in the area of the components of the wedge sleeves, can be controlled or avoided are. This is achieved in that when an axial actuating force is determined which exceeds the predefined limit value, the control of the method automatically varies the radial pressure of the hydraulic fluid in order to reduce the friction between the mating surfaces of the components and the wedge sleeves.
  • interference fit is understood to mean interference fits in which the maximum dimension of the bore is always smaller than the minimum dimension of the shaft. In the case of application under consideration, this means that the oversize is present between the components in the assembled operating state of the wedge sleeve between the facing mating surfaces of the components and the wedge sleeve.
  • the joining process is ended if an axial actuating force that is less than a predefined lower limit value is determined during the production of the press fit. This avoids in a simple way that insufficient press fits are produced.
  • the joining process is ended if an axial actuating force greater than a further predefined upper limit value is determined during the production of the press fit.
  • the predefined upper limit value can be greater than the upper limit value of the actuating force and can have a value above which plastic deformations occur in the area of the components and/or the wedge sleeve. This in turn means that during the manufacture of the press fit, plastic deformations in the area of the components and/or in the area of the wedge sleeve are avoided with little control and regulation effort.
  • the joining process is ended if the pressure exceeds an upper limit value during the production of the press fit. This procedure in turn ensures in a simple manner that irreversible damage, such as plastic flow, in the area of the components and/or the wedge sleeve is avoided as a result of the pressure applied.
  • the upper limit and/or the lower limit of the actuating force can be varied depending on a displacement path of the wedge sleeve relative to the components or depending on a displacement path of one of the components relative to the other component and relative to the wedge sleeve. This in turn makes it easy to take into account that the axial actuating force increases or decreases as a function of the adjustment path when producing or releasing the press fit and that the joining or dissolving process is carried out with the currently required axial actuating force.
  • a course of the axial force is determined as a function of an axial adjustment path of the wedge sleeve relative to the components or as a function of a displacement path of one of the components relative to the other component and ge compared to the wedge sleeve.
  • the course of the actuating force can be determined using a numerical model that is calibrated as a function of empirically determined data.
  • adaptive control is made available with which the radial pressure of the hydraulic fluid and the axial actuating force can be correlated in real time and the radial pressure of the hydraulic fluid can be corrected as required.
  • the numerical model calibrated using the empirically determined data, depicts the joining and loosening process between the components and the wedge sleeve.
  • varying initial conditions such as insufficiently cleaned components, an undesired inclination of the components to be joined to one another, any chips or the like that may be present can be easily taken into account by the adaptive control.
  • the pressure of the hydraulic fluid can be left at the pressure level of the upper limit value for a defined period of time. It can be provided that during the defined period of time a check is made as to whether the actuating force falls to values less than the upper limit value within the defined period of time. If the test result is positive, the pressure can be reduced again, whereas the joining process can be ended if the test result is negative. It can thus be guaranteed with little effort that a joining or a loosening process is only ended when it is determined that the actuating force is permanently greater than the upper limit value.
  • the pressure is reduced when the another upper limit of the pressure, which is smaller than the upper limit of the pressure, kept constant.
  • the first component can be a planetary bolt on which a planetary gear of a planetary gear unit is rotatably mounted.
  • the second component can be designed as a planetary carrier.
  • the planet pin can be arranged at the ends in bores of the planetary carrier.
  • the at least one wedge sleeve can be pressed in to produce the press fit between the planet pin and the planet carrier by applying the axial force and pushed out to loosen the press fit by means of the axial force.
  • a device for producing or releasing an interference fit of an interference fit between at least a first component and a second component and at least one wedge sleeve arranged between the components.
  • the device includes a pressing device for applying an axial actuating force to the components and to the wedge sleeve.
  • the device comprises at least one sensor for determining the axial actuating force.
  • the device according to the present disclosure is designed with a high-pressure hydraulic fluid injection device for introducing hydraulic fluid under pressure between an outer surface of the wedge sleeve and an inner side of the second component and/or between an inner side of the wedge sleeve and an outer side of the first component.
  • the device has at least one pressure measurement sensor for determining the pressure and a control device for carrying out the method described in more detail above.
  • a control unit which is designed to carry out the method according to the present disclosure.
  • the control unit includes, for example, means that are used to carry out the method. These means can be hardware-side means and software-side means.
  • the hardware-side means of the control device are, for example, data interfaces in order to communicate with the assemblies of the device involved in the implementation of the method exchange. Additional hardware means are, for example, a memory for data storage and a processor for data processing.
  • Software-side means can be, inter alia, program modules for carrying out the method.
  • the control device can be designed with at least one receiving interface which is designed to receive signals from signal generators.
  • the signal generators can, for example, be in the form of sensors that record measured variables and transmit them to the control unit.
  • a signal transmitter can also be referred to as a signal sensor.
  • the receiving interface can receive a signal from a signal generator, which signals that a press fit is to be produced or released.
  • the signal can be generated by an operator, for example, by actuating an operating element via which such a determination can be requested.
  • the signal can also be generated by a manufacturing strategy that is activated and implemented in the area of the control unit or in the area of another control unit of a machine tool or the like.
  • the control device can also have a data processing unit in order to evaluate and/or process the received input signals or the information of the received input signals.
  • the control unit can also be designed with a transmission interface that is designed to output control signals to actuators.
  • An actuator is understood to mean actuators that implement the commands of the control unit.
  • the actuators can, for example, be in the form of hydraulic, electrical or mechanical actuators which generate or make available the axial actuating force required to produce or release the press fit and the pressure of the hydraulic fluid.
  • the control unit If the control unit recognizes that a press fit between the components and the wedge sleeve is to be created or loosened, the control unit applies hydraulic fluid under pressure between an outer surface of the wedge sleeve and an inner surface of the wedge sleeve while the press fit is being created or loosened second component and / or introduced between an inside of the wedge sleeve and an outside of the first component. Furthermore, the control device is used to determine an axial actuating force during the production or the loosening of the press fit. The pressure with which the hydraulic fluid is introduced is automatically varied by means of the control device when an axial actuating force is greater than or equal to a predefined upper limit value until the axial actuating force is smaller than the predefined upper limit value.
  • the aforementioned signals are to be considered as exemplary only and are not intended to limit the present disclosure.
  • the detected input signals and the output control signals can be transmitted via a data bus.
  • the control device or the control unit can be designed, for example, as a central electronic control unit of a machine tool.
  • the solution proposed here can also be embodied as a computer program product which, when it runs on a processor of a control device, instructs the processor in terms of software to carry out the associated method steps in accordance with the present disclosure.
  • the subject matter of the present disclosure also includes a computer-readable medium on which a computer program product described above is stored in a retrievable manner.
  • 1 is a longitudinal sectional view of a gas turbine engine
  • Figure 2 is an enlarged partial longitudinal sectional view of an upstream portion of a gas turbine engine
  • FIG. 3 is an isolated view of a transmission for a gas turbine engine
  • FIG. 4 shows a highly schematized longitudinal view of a device for producing or releasing an interference fit between at least one first component and at least one second component and at least one wedge sleeve arranged between them;
  • FIG. 5 shows an enlarged view of an area V identified in more detail in FIG. 4;
  • FIG. 6 shows a schematic partial representation of a first component and a second component as well as a wedge sleeve arranged between them, which are to be connected to one another via a press fit;
  • FIG. 8 several curves of various process parameters of the device according to FIG. 4 during the production or release of a press fit between the planet bolt and the planet carrier of the planetary gear according to FIG. 3; and 9 shows a representation corresponding to FIG. 8 of further curves of various process parameters of the device according to FIG.
  • Fig. 1 depicts a gas turbine engine 10 having a main axis of rotation 9.
  • the engine 10 includes an air intake 12 and a thrust fan 23 that creates two airflows: a core airflow 111 and a bypass airflow 122.
  • the gas turbine engine 10 includes a core 11 that Core air flow 111 absorbs.
  • the engine core 11 includes, in axial flow order, a low pressure compressor 14, a high pressure compressor 15, a combustor 16, a high pressure turbine 17, a low pressure turbine 19, and a core exhaust nozzle 20.
  • An engine nacelle 21 surrounds the gas turbine engine 10 and defines a bypass duct 22 and a bypass exhaust nozzle 18.
  • the bypass air flow 122 flows through the bypass duct 22.
  • the fan 23 is attached via a shaft 26 and an epicycloidal gear 30 to the low-pressure turbine 19 and is driven thereby.
  • the shaft 26 is also referred to as the core shaft.
  • the core air stream 111 is accelerated and compressed by the low pressure compressor 14 and passed into the high pressure compressor 15 where further compression occurs.
  • the compressed air discharged from the high-pressure compressor 15 is fed into the combustor 16, where it is mixed with fuel and the mixture is burned.
  • the resultant hot combustion products then propagate through and thereby drive the high and low pressure turbines 17, 19 before being expelled through the nozzle 20 to provide some thrust.
  • the high pressure turbine 17 drives the high pressure compressor 15 through a suitable connecting shaft 27, also referred to as the core shaft.
  • the fan 23 generally provides the majority of the thrust.
  • the epicycloidal gear 30 is a reduction gear.
  • FIG. 1 An exemplary arrangement for a geared fan gas turbine engine 10 is shown in FIG.
  • the low pressure turbine 19 drives the shaft 26 which is coupled to a sun gear 28 of the epicycloidal gear assembly 30.
  • a plurality of planetary gears 32 which are coupled to one another by a planetary carrier 34, are located radially outwards from the sun gear 28 and mesh with it and are each arranged rotatably on components or carrier elements 42 which are non-rotatably connected to the planetary carrier 34.
  • the planetary carrier 34 constrains the planetary gears 32 to orbit synchronously about the sun gear 28 while allowing each planetary gear 32 on the carrier members 42 to rotate about its own axis.
  • the planetary carrier 34 is coupled to the fan 23 via linkage 36 in such a way as to drive its rotation about the engine axis 9 .
  • An Au DTrad or ring gear 38 which is coupled via linkage 40 to a stationary support structure 24, is located radially outward of the planetary gears 32 and meshes there with.
  • the terms “low-pressure turbine” and “low-pressure compressor” as used herein may be construed to mean the lowest-pressure turbine stage and the lowest-pressure compressor stage, respectively (i.e. not including the fan 23) and/or the turbine and compressor stages connected together by the connecting shaft 26 at the lowest speed in the engine (i.e. not including the transmission output shaft driving the fan 23).
  • the "low-pressure turbine” and “low-pressure compressor” referred to herein may alternatively be known as the "intermediate-pressure turbine” and “intermediate-pressure compressor.”
  • the fan 23 may be referred to as a first stage or lowest pressure stage.
  • the epicycloidal gear 30 is shown in more detail in FIG. 3 by way of example.
  • the son gear 28, the planet gears 32 and the ring gear 38 each include teeth around their periphery for meshing with the other gears. However, for the sake of clarity, only exemplary portions of the teeth are shown in FIG. Although four planetary gears 32 are illustrated, those skilled in the art will recognize that more or fewer planetary gears 32 may be provided within the scope of the claimed invention.
  • Practical applications of an epicycloidal gear 30 generally include at least three planetary gears 32.
  • the exemplified in Fig. 2 and 3 epicycloidal gear 30 is a planetary gear, in which the planet carrier 34 is coupled via linkage 36 to an output shaft, wherein the ring gear 38 is fixed.
  • epicycloidal gear 30 may be any other suitable type.
  • the epicycloidal gear 30 may be a star arrangement in which the planetary carrier 34 is held fixed while allowing the ring gear (or ring gear) 38 to rotate. With such an arrangement, the fan 23 is driven by the ring gear 38 .
  • the gear 30 may be a differential gear in which both the ring gear 38 and the planet carrier 34 are allowed to rotate.
  • the present disclosure extends to a gas turbine engine having any arrangement of gear types (e.g., radial or planetary), support structures, input and output shaft layout and bearing positioning.
  • gear types e.g., radial or planetary
  • support structures e.g., support structures, input and output shaft layout and bearing positioning.
  • the transmission can drive secondary and/or alternative components (e.g., the intermediate pressure compressor and/or a booster).
  • secondary and/or alternative components e.g., the intermediate pressure compressor and/or a booster.
  • gas turbine engines to which the present disclosure may have application may have alternative configurations.
  • such engines may have an alternative number of compressors and/or turbines and/or an alternative number of connecting shafts.
  • the gas turbine engine shown in Figure 1 has a split flow nozzle 20, 22, meaning that the flow through the bypass duct 22 has its own nozzle which is separate from the engine core nozzle 20 and radially outward therefrom.
  • this is not limiting and any aspect of the present disclosure may also apply to engines where flow through bypass duct 22 and flow through core 11 occur before (or upstream of) a single nozzle, referred to as a mixed flow nozzle can be mixed or combined. Either or both nozzles (whether mixed or split flow) may have a fixed or variable area.
  • turbofan engine any type of gas turbine engine, such as a turbofan engine.
  • a turbofan engine an open rotor (where the blower stage is not surrounded by an engine nacelle) or a turboprop engine.
  • the geometry of the gas turbine engine 10 and components thereof is or are defined by a conventional axis system having an axial direction (which is aligned with the axis of rotation 9), a radial direction (in the direction from bottom to top in Fig. 1) and a Circumferential (perpendicular to the view in Fig. 1) includes.
  • the axial, radial and circumferential directions are perpendicular to one another.
  • FIG. 4 shows a longitudinal sectional view of a device 40 which includes a pressing device 41 . Furthermore, the planetary carrier 34 and that to be connected to it Component or the planetary pin 42 for a planetary wheel 32 of the transmission 30 rotatably mounted thereon. 4 also shows clamping elements or wedge sleeves 43, 44, an axially adjustable actuator 45 and an actuating element 46 of the pressing device 41 that can be moved axially via the actuator 45, via which the wedge sleeves 43, 44 can be moved radially in the axial direction A or B between areas of the planet carrier 34 and areas of the planet pin 42 can be inserted. The actuating element 46 reaches through the actuator 45, the planetary carrier 34 and the planetary pin 42 in the axial direction A or B.
  • the actuating element 46 interacts with the actuator 45 at one end and is designed with a cover element 47 at the other end.
  • the actuator 46 with the planet carrier 34 and the planet pin 42 in operative connection.
  • the wedge sleeve 44 is positioned axially between the cover element 47 and the planet carrier 34 and the planet pin 42 po, while the wedge sleeve 43 is arranged between the planet carrier 34 and the tarpaulin pin 42 and a housing area 48 of the actuator 45 .
  • the actuating element 46 and the actuator 45 for inserting the wedge sleeves 43 and
  • the actuator 45 is designed as a hydraulic actuator, by means of which the actuating element 46 can be displaced in the axial direction A. Furthermore, the actuator 45 is designed in such a way that the actuator 45 is also moved in the axial direction B towards the planetary carrier 34 and the planetary pin 42 during the axial adjustment of the actuating element 46 .
  • the adjustment paths of the adjustment element 46 and the actuator are
  • the wedge sleeves 43 and 44 are displaced by the axial displacement of the actuating element 46 on the actuator side and the associated adjustment of the actuator 45 starting from in the axial direction of the planetary carrier 34 and the planetary pin 42 from each other facing pages 53, 54 are inserted.
  • the spacer elements 55A or 55B or 56A or 56B prevent a reduction in the distance between the cover element 47 and the side 54 or between the housing area 48 and the side 53 and only the wedge sleeve 43 or the wedge sleeve 43 between the planet carrier 34 and the planet pin 42 is inserted to the desired extent.
  • FIG. 5 shows an enlarged sectional view of region V, which is identified in more detail in FIG. 5 shows that the wedge sleeve 43, which in principle has the same structure as the wedge sleeve 44, is a clamping sleeve which is cylindrical in the area of its outer circumference 57 and conical in the area of its inner diameter 58 .
  • the inner diameter 58 of the wedge sleeve 43 decreases starting from the side 59 facing the components or the planet carrier 34 and the planet pin 42 in the direction of the side 60 facing away from the components or the planet carrier 34 and the planet pin 42 .
  • the planet pin 42 in the joining area with the wedge sleeve 43 has a we at least approximately adapted to the wedge sleeve 43 conical outer contour 61, while the planet carrier 34 is designed in the joining area with the wedge sleeve 43 with a zy-cylindrical inner contour.
  • Both the planetary carrier 34 and the planetary pin 42 are formed in the joining area with the wedge sleeve 44 as described in more detail above, as in the joining area with the wedge sleeve 43 .
  • the planetary pin 42 is provided with lines 62 which are in overlap with a line 63 of the actuating element 46 when the actuating element 46 reaches a defined position Po.
  • Lines 64 are provided in the wedge sleeve 43 via which hydraulic fluid can be guided from the joining area between the wedge sleeve 43 and the planet pin 42 into the joining area between the wedge sleeve 43 and the planet carrier 34 .
  • the planetary pin is located between the planetary pin 42 and the planetary carrier 34 while the wedge sleeve 43 is being pushed in 42 can be reversibly constricted on the circumference and the wedge sleeve 43 and the planet carrier 34 can be reversibly widened, while the wedge sleeve 43 is reversibly compressed in the outer circumference 57 .
  • the wedge sleeve 43 can thus be inserted between the planet bolt 42 and the planet carrier 34 with low axial joining forces.
  • the hydraulic pressure applied is reduced or switched off, whereby the previously reversible expansion of the planetary carrier 34 and the reversible constriction of the planetary pin 42 decrease and the wedge sleeve 43 provides the desired non-rotatable connection between the planetary carrier 34 and the planetary pin 42 in the form of a creates a press fit.
  • the line 63 of the adjusting element 46 extends in the axial direction of the adjusting element 46 into the joining area between the wedge sleeve 44 with the planetary bolt zen 42 and the planetary carrier 34.
  • the wedge sleeve 44 and the planetary bolt 42 are in the end region facing the page 54 in the same way Scope formed with lines to during the joining process of the wedge sleeve 44 hydraulic fluid via the actuating element 46 in the joining areas between the wedge sleeve 44 and the Planet pin 42 and between the wedge sleeve 44 to initiate the planet carrier 34 can.
  • Fig. 6 shows a schematic partial representation of the planet carrier 34, the planet bolt 42 and the wedge sleeve 43.
  • there is an inner diameter 66 of a bore 67 of the Planet carrier 34 and an outer diameter 68 of the planet pin 42 is specified.
  • a maximum oversize in the area between the outer circumference 57 of the wedge sleeve 43 and the inner diameter 66 of the bore 67 of the planet carrier 34 is determined from the sum of the difference between the outer diameter 57 of the wedge sleeve 43 and the inner diameter 66 of the bore 67 and the Sum of the tolerance fields of the outer diameter 57 and the inner diameter 66.
  • the maximum internal oversize between the inner diameter 58 of the wedge sleeve 43 and the outer diameter 68 of the planetary pin 42 corresponds to the sum of the difference between the outer diameter 68 of the planetary pin 42 and the inner diameter 58 of the wedge sleeve 43 and the sum of the tolerance fields of the inner diameter 58 and the outer diameter 68.
  • the total maximum oversize results from the tolerance stack, which corresponds to the sum of the maximum outer oversize and the maximum inner oversize and has a significant influence on the joining process or the loosening process of the press fit between the planet carrier 34 and the planet pin 42 as well as the interposed wedge sleeve 43 has.
  • This assumption applies to small cone angles in the area of the conical surfaces of the wedge sleeve 43 and the planetary pin 42. This means that if only the diameters of the components involved in the press fit are taken into account, the total scatter is equal to the sum of the four tolerances of the diameters 57, 58, 66 and 68 is.
  • the planetary carrier 34, the planetary pin 42 and the wedge sleeve 43 are positioned in the device 40 in the manner shown in more detail in FIG.
  • the wedge sleeve 43 is then inserted between the planet carrier 34 and the planet pin 42 by applying an axial actuating force Fa.
  • the axial actuating force Fa is determined by means of a sensor of the device 40 during the joining process of the wedge sleeve 43 or during the production of the press fit.
  • hydraulic fluid or oil is introduced via a high-pressure hydraulic fluid injection device of the device 40 between the wedge sleeve 43 and the planet carrier 34 and between the wedge sleeve 43 and the tarpaulin tenbolt 42 under pressure.
  • the pressure with which the hydraulic fluid is introduced is determined by means of at least one pressure measuring sensor of device 40 .
  • the pressure with which the hydraulic fluid is introduced is automatically varied when an axial actuating force Fa is greater than or equal to a predefined upper limit value until the axial actuating force is smaller than the predefined upper limit Limit.
  • the procedure is based on an adaptive control, which uses the profiles of the axial actuating force Fa, which are carried out in FIG.
  • the discrete travel value S1 corresponds to a position of the wedge sleeve 43 in which the wedge sleeve 43 is in contact with one end face of the bore 67 of the planetary carrier 34 and in which there is still no overlap between the wedge sleeve 43 and the planetary carrier 34 or the planetary pin 42 .
  • the further discrete adjustment path value S2 corresponds to an axial position of the wedge sleeve 43 in which the press fit between the planetary carrier 34, the planetary pin 42 and the wedge sleeve 43 is fully established.
  • the illustration according to FIG. 7 shows that the axial actuating force Fa to be used to produce the press fit increases progressively from the actuating travel value S1 in the direction of the further actuating travel value S2.
  • the lower curve Fau of the axial actuating force Fa corresponds to a curve of the actuating force Fa, which is determined using a numerical model for a lower maximum overall oversize between the planet carrier 34, the planet bolt 42 and the wedge sleeve 43 and for lower coefficients of friction between these components as a middle course Farn or an upper course Fao of the axial adjusting force Fa.
  • the numerical model is calibrated depending on empirically determined data. To calibrate the numerical model, a sufficient number of joining processes are carried out and the axial actuating forces to be applied are determined by measurement. In addition, the respectively corresponding pressure values with which the hydraulic fluid is introduced between the planetary carrier 34, the planetary pin 42 and the wedge sleeve 43 are determined by measurement and used to calibrate the numerical model. Furthermore, when specifying the process parameters of the joining process, the entire maximum and the entire minimum oversize are taken into account. In addition, the final dimensions of the components 34, 42 and 43 are taken into account so that the joining process can be carried out as soon as the process parameters have been determined as a function of the maximum permissible oversize. If the word-case scenario is present, the maximum total oversize is present in combination with other circumstances that increase the axial actuating force, which can be compensated for by the adaptive control described in more detail below, without having to stop the joining process or change the process parameters manually have to.
  • the adaptive control described in more detail below offers the possibility of expanding narrow manufacturing tolerances and thus improving manufacturing productivity and reducing manufacturing rejects. Normally, such a high level of variability is only possible by specifying different process parameters, which, however, is not necessary due to the proposed adaptive control.
  • the numerical model is also able to determine upper and lower limit values for individual curves in the family of curves in order to avoid damage to the Components 34, 42 and 43 to avoid.
  • the determined values of the axial setting force Fa are used to check whether the axial setting force Fa currently applied to the wedge sleeve 43 is less than an upper limit value.
  • FIG. 8 shows several curves of different process parameters of the device 40 according to FIG. 4 .
  • Different curves of the axial actuating force Fa and the radial pressure p of the hydraulic fluid over the operating time t are shown in each case.
  • a curve Fath corresponds to a theoretical curve of the axial positioning force Fa during the production of the press fit between the components 34, 42 and 43. Since the axial adjustment path S increases steadily over the operating time t, starting from the adjustment path value S1 in the direction of the adjustment path value S2, it also increases the theoretical curve Fath of the axial positioning force Fa to the extent shown.
  • An upper theoretical curve Fatho is indicated above the theoretical curve Fath, which runs at least approximately parallel to the theoretical curve Fath of the axial actuating force Fa.
  • a theoretical lower curve Fatu which also runs parallel to the theoretical curve Fath, is shown, which represents a lower limit of the axial actuating force Fa.
  • an actual curve Faactual of the axial actuating force Fa is given, which graphically reproduces the actuating force Fa actually applied to the wedge sleeve 43 .
  • an axial adjusting force Faactual (T 1 ) is applied to the wedge sleeve 43 , as a result of which the wedge sleeve 43 is pushed in between the planetary carrier 34 and the planetary pin 42 .
  • the radial pressure p of the hydraulic fluid has a constant pressure level p(T1) from the point in time T1.
  • the actual curve Faist reaches the upper curve Fatho, which also represents a curve of an upper limit value of the axial actuating force Fa. Since the actual curve Faactual of the axial actuating force Fa exceeds the upper curve Fatho at time T2, the radial pressure p of the hydraulic fluid is ramped from time T2 to the extent shown to a time T3 to a pressure level p(T3). When the pressure level p(T3) is reached, the actual curve Faact of the axial actuating force Fa falls below the upper curve Fatho of the axial actuating force Fa, which is why the pressure p is left at the pressure level p(T3) from the point in time T3.
  • the actual curve Faist of the axial actuating force again exceeds the upper curve Fatho, which is why the radial pressure p of the hydraulic fluid is increased in a ramped manner from point in time T4 to a point in time T5.
  • the radial pressure p has a pressure level p(T5) at which the actual curve Faist of the axial actuating force Fa falls below the upper curve Fatho again. For this reason, the radial pressure p is left at the pressure level p(T5) from the point in time T5.
  • the radial pressure p is preferred to an extent that is not shown in detail reduced in a ramp shape until the actual curve Faist again runs between the lower curve Fathu and the upper curve Fatho of the axial actuating force Fa.
  • a curve Faomax is stored in the adaptive control system, above which an axial actuating force Fa is applied to the wedge sleeve 43 undesired chip formation during the release position of the press fit.
  • the course Faomax has a constant value Famax from a point in time T6, above which plastic flow occurs in the area of wedge sleeve 43 and/or in the area of planet bolt 42 and/or in the area of planet carrier 34 if wedge sleeve 43 is subjected to greater axial forces than the Fmax value is applied.
  • the range of the axial setting force Fa in which chip formation is promoted is above the curve Faomax and below the value Famax of the axial setting force Fa.
  • the actual curve Faist exceeds the upper curve Fatho at a time T7.
  • the radial pressure p is again increased in a ramp-like manner from the point in time T7 up to a point in time T8. Since the pressure increase up to the time T8 does not bring about the desired reduction in the axial actuating force Fa and the actual course Faist at the time T8 exceeds another upper course Fathomax, the radial pressure p increases with a greater gradient in the direction of a maximum pressure value from the time T8 pmax that the radial pressure p reaches at a time T9.
  • the radial pressure p is left constant at the maximum pressure value pmax.
  • the maximum pressure value pmax has the effect that the actual curve Faactual falls below the upper maximum curve Fathomax at a point in time T10.
  • This event triggers a ramp-shaped reduction in the radial pressure p starting from the maximum pressure value pmax. Since the actual curve Faist falls below the upper curve Fatho at a point in time T11, the radial pressure p is left constant at the pressure level p(T11) from the point in time T11 and the wedge sleeve 43 further inserted between the planetary carrier 34 and the planetary pin 42 until the press fit is finally established.
  • Fathomax Maximum upper course of the theoretical course of the axial positioning force Faomax course of a maximum upper limit value of the axial actuating force

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • General Details Of Gearings (AREA)

Abstract

Un procédé, un dispositif et une unité de commande permettant d'établir ou de libérer un ajustement serré entre au moins un premier élément (42) et au moins un second élément (34) et au moins une gaine de calage (43) disposée entre eux. Lors de la création ou de la libération de l'ajustement serré, un fluide hydraulique est introduit à chaque fois sous pression entre une surface externe de la gaine de calage (43) et un côté interne du second élément (34) et/ou entre un côté interne de la gaine de calage (43) et un côté externe du premier élément (42). Une force d'actionnement axiale est déterminée lors de l'établissement ou de la libération de l'ajustement serré. La pression à laquelle est introduit le fluide hydraulique varie de manière automatiquement régulée, lorsqu'il y a présence d'une force d'actionnement axiale supérieure ou égale à une valeur limite supérieure prédéfinie, jusqu'à ce que la force d'actionnement axiale soit inférieure à la valeur limite supérieure prédéfinie.
EP22703616.7A 2021-02-16 2022-02-02 Procédé, dispositif et unité de commande pour établir un ajustement serré Pending EP4259375A1 (fr)

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DE102021103575 2021-02-16
PCT/EP2022/052457 WO2022175087A1 (fr) 2021-02-16 2022-02-02 Procédé, dispositif et unité de commande pour établir un ajustement serré

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Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4771654A (en) * 1983-09-17 1988-09-20 Kinichi Shinjo Gear system
CH701086B1 (de) * 2007-10-17 2010-11-30 Jan Wernecke Vorrichtung zur reibschlüssigen Kupplung zweier koaxialer Bauteile.
DE102017129359A1 (de) * 2017-12-08 2019-06-13 Rolls-Royce Deutschland Ltd & Co Kg Anordnung mit einer Presse, mit zwei Bauteilen und mit wenigstens einem Spannelement
US11358243B2 (en) * 2018-04-25 2022-06-14 Riverhawk Company High torque friction fit low moment hub joint assembly for a shaft

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