EP1827760B1 - Burnishing roller head - Google Patents

Description

The invention relates to a deep rolling roller head for deep rolling of radii or punctures, which laterally limit the bearing seats of main and crank pins of crankshafts for engines of motor vehicles.

The deep rolling roller head is provided in particular for deep rolling of so-called split pin crank pins of crankshafts. The difficulty with split-pin crank pin is the deep rolling of the gusset section, which connects the two adjacent crank pin such a crankshaft with each other. When rolling the deep rolling tool over the circumference of such a split pin crank pin, the deep rolling tool is supported over only a portion of the circumference on one side and on the subsequent section, namely the gusset portion, on both sides. The deep rolling roller head is not limited to the deep rolling of split-pin crankpin, but is also intended to standard roll and crankpins of crankshafts, which are bounded on either side by radii or punctures.

For example, from the US 5,445,003 is known a deep rolling machine for deep rolling of crankshafts, which is suitable to roll split-pin crank pin. In this case, two counter-supported deep rolling roller heads are provided, each having only on their sides facing away from each other deep rolling rollers. But with the known deep rolling machine can always only the outer radii or recesses of the journal be rolled. The gusset area can not be edited with it.

It follows that the object of the present invention to provide a deep rolling head, which is suitable for deep rolling of radii or punctures of the main or crank pin of all types of crankshafts. In particular, the deep rolling of the gusset areas of split-pin crank pins should be possible, which can not be processed with conventional deep-rolling tools so far.

The problem is solved by a deep rolling head, in which two disc or annular disc-shaped and cylindrical fixed rollers of the same outer diameter and approximately the same axial width are provided, which are arranged parallel and at a mutual distance from each other in the housing of the deep rolling roller head to a common horizontal axis of rotation in the Housing of the deep rolling roller head are rotatably mounted, and each have on their outer, mutually remote peripheral edges a circumferential, rounded and the outer diameter of the respective deep rolling roller by a predetermined amount magnifying projection, which also extends over a portion near the edge of the axial width of the deep rolling.

Accordingly, the peripheral edges are intended to intervene in the deepening of punctures in the already existing recess of the groove, or einwalzen the deep rolling of radii of transitions in the radii a recess, wherein the deep rolling during each engagement or rolling with the one section of their axial width supported on the bearing seat. This is the deep rolling head in itself itself stabilized by the solid rolling of split-pin crank pin engages over the peripheral portion of the not adjacent to the gusset portion of the bearing seat of the deep rolling roller either in a recess on the opposite edge of the bearing seat or when deep rolling of radii there creates a recess in which he at the same time guided sideways. A mutual support of two deep rolling roller heads, as is known from the cited document, is not provided in the present case. Due to the geometric conditions, two deep rolling roller heads can not work side by side for the adjacent and only connected via the gusset crank pin a split-pin crankshaft. For this purpose, an arrangement is advantageous in which two deep rolling roller heads are at an axial distance from each other. The deep rolling forces are absorbed in a known manner by support rollers, which lie opposite the deep rolling roller heads each. The deep rolling head plus the supporting roller head each form a deep rolling tool.

The axial width of the deep rolling roller head with its two disc-shaped deep rolling rolls corresponds at most to the width of a bearing seat from oil collar to oil collar. A limited axial compliance of the two fixed rollers is advantageous for adapting to the manufacturing tolerances of the bearing seats.

An advantageous embodiment of the deep rolling roller head is obtained when one of two forming the deep rolling pulleys on one side has a projecting annular flange, while the other disc has on one side a projecting cylindrical pin and the annular flange of a disc and the pin of the other disc are each arranged concentrically to the common axis of rotation of the two fixed rollers. In particular, it is provided that engages in the assembled deep rolling roller head of the cylindrical pin of a deep rolling roller in the annular flange of the other deep rolling roller almost free of play. The two fixed rollers can then be releasably connected to each other via screws or bolts or else permanently connected by rivets.

By connecting the two fixed rollers together in the region of their respective hubs creates a solid construction that can be stored in a fairly simple manner in the housing of the deep rolling head. The bearing is provided between the outer circumference of the annular flange and the housing of the deep rolling roller head. This gives a kind of tandem arrangement, as it is known from the double roles that are used in buggy (stroller). As a type of storage are both sliding and rolling bearings into consideration.

An alternative embodiment of a deep rolling head provides to form the two fixed rollers as annular discs, which are mounted on pins which project from the web of the housing of the deep rolling roller head. Here, the annular discs can be rotatably mounted on bearings and held by simple means known per se on the journal.

Each of the deep rolling rollers consists of a high-strength, in particular hardened material, as is known per se Use of conventional deep-rolling rollers is known. In the case of the execution of the storage of the deep rolling rollers as plain bearings, the housing of the deep rolling roller head or the part of the housing in which the deep rolling rollers are mounted, made of bronze.

The two deep rolling rollers of a deep rolling roller head are hereinafter referred to as outer roller when they point to the main journal and as an inner deep rolling when they are located adjacent to the journal of a split-pin crankshaft.

• 1. Fall: Es sind am Split-Pin-Hubzapfen einer Split-Pin-Kurbelwelle zwei äußere und ein innerer Einstich vorgesehen, welche die beiden angrenzenden Lagersitze des Split-Pin-Hubzapfens jeweils seitlich begrenzen. Die äußeren Einstiche werden vorab von zwei sich aufeinander abstützenden Festwalzrollenköpfen festgewalzt, wie sie aus der eingangs zitierten US 5,445,003 bekannt sind. Die mit den bekannten Festwalzrollenköpfen mögliche Festwalzrichtung von z.B. 35° schräg zur Kurbelwellenachse besitzt den Vorteil, dass eine vorgegebenen Dauerfestigkeit erreicht werden kann. Im vorliegenden Fall hat die äußere Festwalzrolle des erfindungsgemäßen Festwalzrollenkopfes nur Führungseigenschaften und führt keinen Festwalzvorgang im Zwickelabschnitt aus. Der äußere Abrundungsradius der äußeren Festwalzrolle berührt den Einstich im Zwickelabschnitt des Lagersitzes nicht. Dazu wird der Außendurchmesser der äußeren Festwalzrolle mindestens um die Eindringtiefe der inneren Festwalzrolle beim Festwalzen des Zwickels und um die entsprechenden Toleranzen des inneren Einstichs bei der Vorfertigung der Kurbelwelle kleiner ausgeführt. Im übrigen Umfangsabschnitt des Split-Pin-Hubzapfens liegt die äußere Festwalzrolle in dem äußeren Einstich auf und gewährleistet, dass der Festwalzrollenkopf seine korrekte axiale Position einhält. In diesem Umfangsabschnitt des Eingriffs der äußeren Festwalzrolle wird die auf den Festwalzrollenkopf einwirkende Festwalzkraft verringert, während im Zwickelabschnitt eine zum Festwalzen geeignete Festwalzkraft von z.B. 10 kN aufgebracht wird.
• 2. Fall: Am Split-Pin-Hubzapfen der Kurbelwelle sind innere und äußere Einstiche vorgesehen, welche den jeweiligen Lagersitz seitlich begrenzen. Diese Einstiche werden mit dem Festwalzrollenkopf gleichzeitig festgewalzt. Dazu wird die Festwalzkraft über den Umfangsabschnitt des Lagersitzes, wo der Zwickel ist, erhöht, z.B. verdoppelt. Da ein Festwalzgerät nur in geringem Maße unterschiedliche Tiefen zwischen den Einstichen ausgleichen kann, ist hier eine hohe Genauigkeit bei der Vorfertigung der Split-Pin-Kurbelwelle erforderlich.

Die Außendurchmesser der beiden Festwalzrollen sind in diesem Fall gleich groß.When deep-rolling split pin crank pins, the deep rolling head can be used as follows:

• Case 1: Two outer and one inner recess are provided on the split pin crankpin of a split pin crankshaft, which laterally delimit the two adjoining bearing seats of the split pin crank pin. The outer punctures are solidly rolled in advance by two mutually supporting deep rolling roller heads, as they are cited from the above US 5,445,003 are known. The possible deep-rolling direction of the known deep-rolling roller heads of eg 35 ° oblique to the crankshaft axis has the advantage that a predetermined fatigue strength can be achieved. In the present case, the outer deep rolling roller of the deep rolling roller head according to the invention only guide properties and performs no hard rolling in the gusset section. The outer radius of curvature of the outer deep rolling roller does not touch the puncture in the gusset portion of the bearing seat. For this purpose, the outer diameter of the outer deep rolling roller at least by the penetration depth of the inner deep rolling roller during deep rolling of the gusset and the corresponding Tolerances of the inner groove in the prefabrication of the crankshaft made smaller. In the remaining peripheral portion of the split-pin crank pin, the outer deep-rolling roller lies in the outer recess and ensures that the deep-rolling roller head maintains its correct axial position. In this peripheral portion of the engagement of the outer deep rolling roller acting on the deep rolling roller head deep rolling force is reduced, while in the gusset section suitable for deep rolling deep rolling force of eg 10 kN is applied.
• 2nd case: At the split-pin crankpin of the crankshaft inner and outer recesses are provided, which limit the respective bearing seat laterally. These punctures are simultaneously rolled down with the deep rolling head. For this purpose, the deep rolling force over the peripheral portion of the bearing seat, where the gusset is increased, eg doubled. Since a deep rolling machine can compensate for different depths between the punctures only to a small extent, a high accuracy in the prefabrication of the split-pin crankshaft is required here.

The outer diameter of the two fixed rollers are the same size in this case.

The invention will be described in more detail with reference to an exemplary embodiment.

• Fig. 1 einen Abschnitt einer Split-Pin-Kurbelwelle in perspektivischer Darstellung,
• Fig. 2 einen Festwalzrollenkopf in der Seitenansicht,
• Fig. 3 einen Schnitt durch den Festwalzrollenkopf der Fig. 2 entlang der Linie III - III,
• Fig. 4 einige Einzelteile des Festwalzrollenkopfes,
• Fig. 5 die Situation vor dem Festwalzen von Radien an einem Split-Pin-Hubzapfens und
• Fig. 6 die Situation wie in der Fig. 5 mit zwei eingebauten Festwalzrollenköpfen,
• Fig. 7 Einzelheiten des Festwalzens.

In each case in a schematic and not to scale representation of the

• Fig. 1 a section of a split-pin crankshaft in perspective,
• Fig. 2 a deep rolling head in side view,
• Fig. 3 a section through the deep rolling head of the Fig. 2 along the line III - III,
• Fig. 4 some individual parts of the deep rolling roller head,
• Fig. 5 the situation before the rolling of radii on a split pin crank pin and
• Fig. 6 the situation like in the Fig. 5 with two built-in deep-rolling rollers,
• Fig. 7 Details of deep rolling.

The split pin crankshaft 1 of Fig. 1 has a split-pin crank pin 2 with the two individual crank pins 3 and 4 which are interconnected via a gusset 5, represented by the curved arrow. Laterally, the two crank pins 3 and 4 are each bounded by cheeks 7 and 8, wherein the transition between the crank pin 4 and the cheek 8 is formed as a recess 6. The Fig. 1 serves to represent the conditions on a split-pin crankshaft. 1

In the housing 9 of a deep rolling roller head 10, two disc-shaped deep rolling rollers 11 and 12 are rotatably mounted about a common axis of rotation 13. On the one side 14 carries the cylindrical disc of the deep rolling roller 12 has a projecting annular flange 15 which is concentric with the axis of rotation 13. The annular flange 15 corresponds to the corresponding side 16 of the cylindrical disc of the deep rolling roller 11 a projecting cylindrical pin 17, which is also arranged concentrically to the common axis of rotation 13. In the assembled deep rolling head 10, as in the section of the Fig. 3 is shown, engages the cylindrical pin 17 from the inside into the cylindrical flange 15 a. The intervention takes place with very little play. The assembled in this way Deep-rolling rollers 11 and 12 are finally connected by screws 18 firmly together.

In the present embodiment, a sliding bearing is provided between the fixed rollers 11 and 12 and the housing 9 of the deep rolling roller head 10. In this case, the housing 9 is made of bronze and has a bore 19. In the bore 19 of the annular flange 15 engages with its outer side 35 a.

When deep rolling the crank pin 4, as in the FIGS. 2 and 3 is shown, the crank pin 4 is supported by support rollers 20, as is known per se. Two support rollers 20 are combined in a support roller head. The deep rolling roller head 10 and the support roller head together form a deep rolling device.

The projection 21 in the Fig. 4 indicates the configuration of the peripheral edges 22 of the two fixed rollers 11 and 12 at. The peripheral edges 22 of the two fixed rollers 11 and 12 are identical in their configuration.

The Fig. 5 shows the situation of the deep rolling of two crank pins 3 and 4 by two deep rolling roller heads 10 and 23, which are identical in their construction in each case. The outer peripheral edge 22 of the deep rolling roller 12 is rounded and increases the outer diameter of each disc of the respective deep rolling roller 11, 12 by a predetermined amount 24. The peripheral edge 22 also extends over an edge portion 25 of the axial width of each deep rolling roller 11 and 12. Im present embodiment, it is provided that the two fixed rollers 11 and 12 each have the same axial width. But that is not absolutely necessary but different widths are also possible. The total width of a deep rolling roller head 10 or 23 extends from the oil collar 26 of each crank pin 3 or 4 to the oil collar 31 of the gusset 5. As transitions between the crank pins 3 or 4 to the respective cheeks 27 on the oil collar 26 are each the outer recesses 29th intended. During the deep rolling penetrate the peripheral edges 22 of the fixed rollers 11 and 12 respectively in the outer recesses 29 of the crank pins 3 and 4 a. The dimension 24 is reduced to the value 0, ie on the predominant portion of its axial width, the deep rolling rollers 11 and 12 are based on the bearing seats 36 of the respective crank pin 3 or 4, as in the Fig. 5 can be seen. The penetrating into the outer recesses 29 peripheral edges 22 of the outer fixed rollers 12 leave Einwalzungen 32 in the outer recesses 29 to the respective cheeks 27 out. Rolling 30 in the region of the gusset 5 are caused by the inner peripheral edges 33 and 34, corresponding to the peripheral edges 22.

The FIG. 6 shows the situation of a deep rolling machine (not shown) where two deep rolling roller heads 10 and 23, the outer recesses 29 of two adjacent crank pins 3 and 4 of a crankshaft 1 edit. The deep rolling rollers 11 and 12 are in relation to the main axis of rotation 35 of the crankshaft 1 in each case by 180 ° opposite each other. Each deep rolling roller 11 and 12 are two support rollers 20 opposite, which are each arranged in a support roller head 37. The peripheral portion 38 of the cross-hatched, because cut, shown gusset 5 is machined by the peripheral edge 33 of the inner deep rolling roller 11, while the peripheral portion 39 from the peripheral edge 34 of the inner Deep rolling roller 11 on the left part of Fig. 6 is processed.

The presentation of the Fig. 7 corresponds to a situation which arises when only one deep rolling roller head 10 or 23 is considered. In its axial width 37 of the deep rolling roller head 23 projects beyond the axial width 38 of the bearing seat 36 and its groove 28 of the split-pin crank pins 3 and 4. The groove 39 of the gusset 5 is 3 and 4 every time during deep rolling of the split-pin crank pins mitgewalzt.

LIST OF REFERENCE NUMBERS

1

Split pin crankshaft

2

Split pin crankpins

3

crank pins

4

crank pins

5

gore

6

puncture

7

cheek

8th

cheek

9

casing

10

Rolling roller head

11

Fixed roller

12

Fixed roller

13

common axis of rotation

14

Side of the deep rolling roller 11

15

cylindrical ring flange

16

Side of the deep rolling roller 12

17

cylindrical pin

18

screw

19

drilling

20

support rollers

21

head Start

22

circumferential edge

23

Rolling roller head

24

extensive enlargement

25

marginal section

26

oil collar

27

cheek

28

Transition radius

29

outer puncture

30

Rolled-in

31

Waistband of the gusset

32

Rolled-in

33, 34

inner peripheral edges

35

Main axis of rotation

36

bearing seat

37

Support roller head

38

peripheral portion

39

peripheral portion

Claims (5)

1. Deep rolling head (10, 23) for deep rolling radii (28) or recesses that limit the bearing seat (36) - on the side - for main pins and crankpins (3, 4) on crankshafts (1) in motors in vehicles wherein two disc- or ring-shaped and cylindrical work rollers (11, 12) with the same external diameter and almost similar axial width are provided
   characterised by

   - the work rollers (11, 12) being arranged parallel and at a mutual distance from one another in the housing (9) of the deep rolling head (10)

   - being mounted so that they can rotate around a common, horizontal rotational axis (13) in the housing (9) of the deep rolling head (10) and

   - having a protrusion (21) on their opposite, exterior borders (22) that is peripheral, rounded off, and increases the external diameter of each work roller (11, 12) by a specified size, which also simultaneously extends beyond the section - near to the edge - of the axial width of the work roller (11, 12).
2. Deep rolling head according to Claim 1 is characterised by

   - one of the work rollers (11, 12) having a protruding ring flange (15) on one side (14)

   - the other work roller (11, 12) having a protruding, cylindrical pin (17) on one side

   - the ring flange (15) of one work roller (11, 12) as well as a pin (17) of the other work roller being concentrically aligned to the common rotational axis of both work rollers (11, 12).
3. Deep rolling head according to Claim 2
   is characterised by the cylindrical pin (17) of one work roller (11, 12) engaging almost free of play into the ring flange of the other work roller (11, 12) in the assembled deep rolling head.
4. Deep rolling head according to Claim 3 is characterised by both work rollers (11, 12) being connected by screws (18) or pins allowing for detachment, or being permanently adjoined with riveting.
5. Deep rolling head according to Claims 1 through 4 is characterised by the work rollers (11, 12) on the exterior circumference (40) of the ring flange (15) of one of the two work rollers (11, 12) in the housing (9) of the deep rolling head (10) being mounted so that they can rotate.

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