EP3169908A1 - Gebaute kurbelwelle mit in kurbelwangen eingepressten lagerzapfen - Google Patents
Gebaute kurbelwelle mit in kurbelwangen eingepressten lagerzapfenInfo
- Publication number
- EP3169908A1 EP3169908A1 EP15738614.5A EP15738614A EP3169908A1 EP 3169908 A1 EP3169908 A1 EP 3169908A1 EP 15738614 A EP15738614 A EP 15738614A EP 3169908 A1 EP3169908 A1 EP 3169908A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- profile
- receiving openings
- crankshaft
- receiving
- toothing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/06—Crankshafts
- F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/02—Rigid support of bearing units; Housings, e.g. caps, covers in the case of sliding-contact bearings
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
-
- 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
- F16D1/064—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 non-disconnectable
- F16D1/072—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 non-disconnectable involving plastic deformation
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2223/00—Surface treatments; Hardening; Coating
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/10—Force connections, e.g. 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/10—Force connections, e.g. clamping
- F16C2226/12—Force connections, e.g. clamping by press-fit, e.g. plug-in
Definitions
- crankshaft with pressed in crank arms bearing journals
- the present invention relates to a built crankshaft with bearing journals, which are designed for mounting the crankshaft in a bearing receptacle or for receiving a connecting rod to the crankshaft, and with crank webs, are introduced into the receiving openings, so that in the receiving openings end formed on the bearing journal connecting portions are, wherein the receiving openings have a toothing, which adjoin the inside and substantially parallel to the axis in the receiving openings on an input-side centering of the receiving openings, and wherein the connecting portions have a substantially circumferential rolling profile on which by joining the connecting portions in the receiving openings a through the teeth caused at least partially formed plastic deformation is generated.
- crankshaft with bearing pin, and the bearing pins are pressed via end formed connecting portions in receiving openings in a crank arm.
- the crank arm has on the inside a toothing, which passes through the receiving opening parallel to the joining axis and the front side has the receiving opening a centering shoulder, which is designed as a chamfer and is referred to as a support diameter.
- a roller burnishing profile is applied on the circumference, by which it is meant that circumferential profile peaks and profile valleys are formed on the connecting sections in the circumferential direction, so that a wavy shape results in the longitudinal section.
- the strength of the material for forming the connecting portion and thus of the bearing journal may differ from the strength of the material for forming the crank arm, so that the plastic deformation is generated at least at one of the joining partners.
- the strength of the crank arm should not be too high, however, as this will negatively affect other material characteristics such as fatigue life or ductility, and the cost of providing high strength crank webs increases significantly. In particular, no high-strength, brittle-hard material should be used for crank webs, as this negatively influences the mentioned further material properties.
- the material of the journals should be selected with a strength that is not too low, since in particular the bearing journals of a crankshaft are exposed to high mechanical, in particular dynamic alternating loads.
- the object of the invention is a further improvement in the strength of a built crankshaft, taking into account the lowest possible material costs and a light, also high-strength connection possibility of the bearing pin on the crank arm.
- the advantage should be achieved that the connection of the journals on the crank arm can be made easy to manufacture and high strength by a press fit.
- crankshaft according to the preamble of claim 1, according to the preamble of claim 6 and according to the preamble of claim 1 1 with the respective characterizing features.
- Advantageous developments of the invention are specified in the dependent claims.
- the invention includes the technical teaching that the material of the crank arm has a strength at least in the region of Zentrierabsatzes, which is at least 80 N / mm 2 higher than the strength of the material in the rolling profile of the connecting portions of the journals.
- the material of the crank webs can be case-hardened at least in the region of the centering shoulder, wherein case hardening can be produced, for example, and in particular by carburizing.
- case hardening can be produced, for example, and in particular by carburizing.
- Other hardening methods can also be used, in particular a micro-alloyed steel can be used as the material for the crank webs.
- a micro-alloyed steel can be used as the material for the crank webs.
- aluminum, niobium, vanadium and / or titanium may be added to this steel in order to achieve high strength via the formation of carbides, nitrides and / or grain refining.
- the centering shoulder undergoes a hardening zone, so that a molding of the teeth in the rolling profile is made possible in a particularly advantageous manner, whereby the profile mountains are plastically deformed and the material of the profile mountains is displaced into the adjacent profile valleys.
- a difference in strength of at least 80 N / mm 2 between the centering and the rolling profile is achieved in particular that the toothing undergoes substantially no plastic deformation, while the plastic deformation in the preparation of the press connection between the bearing pin and the crank arm substantially and in particular exclusively produced in Rollierprofil.
- the region of the centering of the crank arm can be performed with a higher strength, the strength of the entire crank arm does not necessarily have to be increased and also does not have to be fundamentally above the strength of the journal.
- the entire region of the toothing or even the entire crank arm can have a material whose strength is at least 80 N / mm 2 above the strength of the material of the bearing journal.
- the material of the bearing journal with the connecting portions and / or the material of the crank webs may be in a tempered state.
- the bearing pins and / or the crank webs can be made of a tempered steel.
- a tempered steel is a steel that has been treated by a tempering process followed by a tempering process, and this has a high strength, in which a tempered steel is already characterized in principle by a high basic strength.
- the strength of the material of the connecting portions of the journals may have a value of 900 N / mm 2 to 1300 N / mm 2 and preferably of 1 100 N / mm 2 , wherein the strength of the material of the crank webs at least in the region of the centering paragraph a value of 1 100 N / mm 2 to 1500 N / mm 2 and preferably 1300 N / mm 2 .
- the bearing journal and in particular the end-side connecting portion can be provided with a strength of, for example 950 N / mm 2 , wherein only by rolling a work hardening is generated, so that the strength of the Material of the connecting portions in the region of the rolling profile on values of, for example, 900 N / mm 2 to 1 100 N / mm 2 and preferably from 1000 N / mm 2 may increase.
- the strength of the material in the region of the roller burnishing profile at the connecting portion should not exceed values of, for example, 1300 N / mm 2 , as this causes the distortions occurring in the press fit between the bearing journal and the crank web to become too large, in particular notch effects occur in the toothing of the receiving opening of the crank web, to further increase the occurring stress peaks in the material of the crank web, in particular if the pressing of the bearing journal with the crank webs takes place under excessive force.
- the input-side centering of the receiving opening having a Ein Industriesfase with a chamfer angle formed to a joining axis of 5 ° to 25 ° and preferably of 10 °.
- the centering paragraph may have an outside diameter diameter, which is greater than the profile mountains of the roller burnishing profile and have an inside diameter diameter, which is smaller than the profile valleys of the roller burnishing profile. If the connecting portion is pressed into the receiving opening, the elevations in the toothing form into the profile peaks of the rolling, and by an axially parallel structure in the toothing and by a circumferentially encircling structure of the rolling profile results in a positive-non-positive joint connection with intersecting structures ,
- crankshaft with crankpins which are designed for mounting the crankshaft in a bearing receptacle or for receiving a connecting rod to the crankshaft, and with crank webs, are introduced into the receiving openings, so that in the receiving openings end to the Bearing journals formed connecting portions are pressed, wherein the receiving openings have a toothing, the inside and substantially parallel to the axis in the receiving openings to an input side Connecting centering of the receiving openings, and wherein the connecting portions have a substantially circumferential rolling profile on which is generated by the joining of the connecting portions in the receiving openings caused by the toothing at least partially formed plastic deformation.
- the roller burnishing profile can be formed over a rolling length on the connecting portion, which is shorter than a contact length of the joint connection between the connecting portion and the crank arm. Due to the fact that no profile valleys lying outside the contact length are present in the outer peripheral surface of the connecting section, there is the advantage that no disadvantageous notch effect is formed in the connecting section of the bearing journal by the profile valleys of the roller burnishing profile.
- the roller burnishing profile is designed as a mountain-valley profile and may preferably have a circumferential structure or the roller burnishing profile is formed as a threaded structure.
- the rolling profile is defined by the axial spacing, that is, by the slope of the Rollierprofils with the Rollierbergen and Rolliertälern, the number of spacings from mountain to mountain, the angle of the flanks of adjacent mountains to each other and the rounding with a radius of curvature define the burnishing profile , Since only the profile mountains undergo plastic deformation during the design of the roller-set joint connection, the notch effect-relevant profile valleys, ie the notches, are present in the area within the joint connection, that is, limited to the contact length of the joint connection.
- the rolling profile can have a sequence of profile peaks and profile valleys, wherein the rolling profile is formed so that it terminates laterally with a profile mountain on the contact length at least in the direction of the transition from the connecting portion in the journal.
- the contact length of the joint connection between the connecting portion and the crank arm can be made shorter than the length of the connecting portion.
- the contact length can protrude as far as the free end of the connecting portion, wherein between the end of the contact length in the direction of the journal an open area can be maintained, and the free area can have an undercut in the transition to the bearing portion of the journal, which is contoured so that a notch effect is minimized.
- the plastic deformation caused by the teeth of the roller burnishing profile can be done by a predominantly lateral impressions of the material of the profile mountains in adjacent profile valleys, resulting in an enlarged contact area of the roller burnishing profile forms with the teeth.
- the contact length between the profile mountain of the roller and the toothing is extended in the receiving opening, whereby the load capacity and thus the load capacity of the connection between the bearing pin and the crank arm is improved.
- the invention is directed to further aspects of the above-listed built crankshaft with bearing journals, which are designed for mounting the crankshaft in a bearing receptacle or for receiving a connecting rod on the crank arm, and with crank webs, are introduced into the receiving openings, so in the receiving openings at the end the bearing journal formed connecting portions are pressed, wherein the receiving openings have a toothing, which adjoin the inside and substantially parallel to the axis in the receiving openings on an input-side centering of the receiving openings, and wherein the connecting portions have a substantially circumferential rolling profile on which by joining the connecting portions in the receiving openings caused by the toothing at least partially formed plastic deformation is generated.
- the toothing is limited on the inside in at least one of the receiving openings to at least a partial circumference of the receiving opening.
- the durability of the built crankshaft is increased.
- the toothing remains on a circumference within the receiving opening, which is exposed to particularly high material stresses.
- occurring notch effects are avoided by the teeth in the receiving opening in the stress critical areas of the crank arm, whereby the durability of the built crankshaft is increased. Cracks due to stress exaggeration, which can occur in the region of the notches of the toothing on the stress-critical regions over the circumference of the receiving opening in the crank web, can be avoided.
- the at least one region in the receiving opening which is formed free of a toothing, may have a cylindrical inner peripheral surface.
- the diameter of this cylindrical inner peripheral portion can be selected so that, for example, this diameter coincides with the effective diameter of the rolling profile, that is, with the diameter of the profile peaks on the connecting portion of the journal.
- the at least one region in the receiving opening which is formed free from a toothing, can extend over an angular range of the receiving opening with a value of 0 ° to 45 °, and preferably of 30 ° to 45 °.
- the crank arm may have two receiving openings, wherein the at least one region is introduced in the semicircle of the respective receiving opening, which points to the adjacent receiving opening in the crank arm.
- two receiving openings in the crank arm can form a plane of symmetry in the crank web, in which the two center axes of the receiving openings run, wherein the areas can be introduced simultaneously in the receiving opening laterally to the plane of symmetry in the inner peripheral surface.
- Figure 1 is a schematic view of the joint connection of a
- FIG. 2 shows a partial view of a joint connection with a bearing journal and a crank web
- Figure 3 is a cross-sectional view through a rolling profile with profile mountains
- Figure 4 is a side view of a crank arm with a first
- Figure 1 shows a schematic view of a journal 10 in a separate arrangement of a crank arm 1 1 to form a built crankshaft, bearing journal 10 and crank arm 1 1 are each only partially represented.
- a receiving opening 12 is introduced, and the half-side bearing pin 10 with the connecting portion 13 also shown half side can be connected to form a Llvespress saides with the crank arm 1 1.
- the receiving opening 12 has on the inside a toothing 14, which extends through the receiving opening 12 substantially parallel to the axis.
- the axis forms the joining axis 17, which also forms the axis of rotation of the bearing journal 10 and of the connecting section 13 integrally formed on the bearing journal 10, and with a movement along the joining axis 17, the connecting element 13 can be pressed into the receiving opening 12.
- roller burnishing profile 16 is introduced, and the roller burnishing profile 16 has a sequence of profile peaks 16a and profile valleys 16b.
- the centering shoulder 15 On the insertion side of the receiving opening 12, a centering shoulder 15 is provided.
- the centering shoulder 15 has an outside diameter paragraph D, which is greater than the diameter of the profile peaks 16a of the roller shutter 16.
- the centering 15 tapers into the teeth 14 in transition and the transition between the centering 15 and the teeth 14 is limited to the inside an inside diameter d.
- the inside diameter paragraph d is smaller than the diameter of the profile peaks 16a.
- the toothing 14 forms into the roller burnishing profile 16.
- this invention is formed with a hardness zone 19, and so that the material of the crank arm 1 1 in the region of the centering 15 has a strength that is at least 80 N / mm 2 higher than the strength of the material in the rolling profile 16 of the connecting portion 13 of the journal 10. This ensures that a plastic deformation in the region of the profile peaks 16a of the roller shutter 16 is generated, whereas in the toothing 14 substantially no plastic deformation is generated.
- Figure 2 shows a partial view of the journal 10 and a partial view of the crank arm 1 1, wherein the connecting portion 13 of the journal 10 in the Receiving opening 12 of the crank arm 1 1 is pressed. It can be seen that the profile mountains 16a are flattened and the profile valleys 16b are shown reduced in size. The reduction of the profile valleys 16b has its cause in that during the plastic deformation of the profile peaks 16a material of the material of the roller burnishing profile 16 was displaced into the profile valleys 16b.
- the length of the roller burnishing profile 16 has a burnishing length r, which is smaller than the contact length I of the joint between the connecting portion 13 and the crank arm 1 1.
- the contact length I of the joint connection is again smaller than the total length L of the connecting portion 13 on the journal 10.
- an undercut 20 is provided in the transition between the connecting portion 13 and the bearing pin 10, and the area of the undercut 20 merges into a profile peak 16a of the roller shutter 16, so that the contact length I of the joint connection begins with the profile peak 16a.
- FIG. 3 shows, in a detail view in cross-section, the roller burnishing profile 16 with the profile peaks 16a and the profile valleys 16b.
- the flanks of the profile peaks 16a have a flank angle ⁇ of 20 ° to 60 °, preferably 25 ° to 55 °, and more preferably of 30 ° to 50 °.
- a further reduction of notch effects and thus an increase in the durability of the built crankshaft is generated by transition radii R, which are both provided on the tip side of the profile mountains 16a and the valley side in the profile valleys 16b.
- FIG. 4 shows a side view of a crank web 11 with a first receiving opening 12, shown on the upper side, for receiving a bearing journal 10, on which a connecting rod can be arranged.
- the underside shown receiving opening 12 serves to receive a Bearing 10, via which the crankshaft can be stored for example in a crankcase of an internal combustion engine.
- a plane of symmetry S is defined, wherein the crank arm 1 1 extends in a horizontal lateral direction symmetrical to the plane of symmetry S.
- the toothing 14 on the inside in the receiving openings 12 according to the invention is not fully formed and extends only to partial circumferences.
- the areas which have no teeth 14 in the receiving openings 12 are marked with X.
- the regions X in adjacent receiving openings 12 towards each other, so that in relation to the central axes 18, the regions X are introduced in the semicircles of the opening contour of the receiving openings 12, which assign each other.
- the areas X shown form the areas in the body of the crank arm 1 1, in which the material is exposed to high voltages, so that the material areas of the crank arm 1 1 form stress-critical areas in or near the areas X. Due to the absence of the teeth 14 in the areas X a notch effect is avoided by the teeth 14, so that a material failure of the crank arm 1 1 is effectively avoided. In the operation of the built crankshaft voltages are added in the material of the crank arm 1 1, which are generated by the interference fit with the bearing pins 10 and with voltages by the operating forces of the crankshaft.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014109818.8A DE102014109818A1 (de) | 2014-07-14 | 2014-07-14 | Gebaute Kurbelwelle mit in Kurbelwangen eingepressten Lagerzapfen |
PCT/EP2015/065955 WO2016008838A1 (de) | 2014-07-14 | 2015-07-13 | Gebaute kurbelwelle mit in kurbelwangen eingepressten lagerzapfen |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3169908A1 true EP3169908A1 (de) | 2017-05-24 |
Family
ID=53673070
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15738614.5A Withdrawn EP3169908A1 (de) | 2014-07-14 | 2015-07-13 | Gebaute kurbelwelle mit in kurbelwangen eingepressten lagerzapfen |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3169908A1 (de) |
DE (1) | DE102014109818A1 (de) |
WO (1) | WO2016008838A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102016206643A1 (de) * | 2016-04-20 | 2017-10-26 | Thyssenkrupp Ag | Wellensegment mit Rohr und Endstück sowie Nockenwelle |
EP3925434B1 (de) | 2020-06-15 | 2024-02-21 | CNH Industrial Belgium N.V. | Kurbelbetätigter packermechanismus für eine landwirtschaftliche ballenpresse |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1270893B (de) * | 1961-04-28 | 1968-06-20 | Sueddeutsche Praecisions G M B | Verpressungsverbindung an Kurbelwellen zwischen Kurbelwangen einerseits und Kurbel- bzw. Hauptlagerzapfen andererseits |
DE10027517A1 (de) * | 2000-06-06 | 2001-12-13 | Thyssen Krupp Automotive Ag | Einrichtung mit einer Welle und mit zumindest einer auf dieser Welle angebrachten Nabe und Verfahren für die Herstellung dieser Einrichtung |
JP5001803B2 (ja) * | 2007-11-28 | 2012-08-15 | トヨタ自動車株式会社 | 組立式クランクシャフト |
JP2009257512A (ja) * | 2008-04-18 | 2009-11-05 | Toyota Motor Corp | 組立式クランクシャフト及びその製造方法 |
DE102012111124B3 (de) | 2012-11-19 | 2013-12-05 | Thyssenkrupp Presta Teccenter Ag | Gebaute Kurbelwelle sowie Verfahren zur Herstellung einer gebauten Kurbelwelle |
-
2014
- 2014-07-14 DE DE102014109818.8A patent/DE102014109818A1/de not_active Ceased
-
2015
- 2015-07-13 EP EP15738614.5A patent/EP3169908A1/de not_active Withdrawn
- 2015-07-13 WO PCT/EP2015/065955 patent/WO2016008838A1/de active Application Filing
Non-Patent Citations (2)
Title |
---|
None * |
See also references of WO2016008838A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2016008838A1 (de) | 2016-01-21 |
DE102014109818A1 (de) | 2016-01-14 |
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