DE102007015422A1 - Roller, in particular for gripper shaft control on sheet-fed offset printing machines - Google Patents

Abstract

The invention relates to a roller (1) suitable for gripper shaft control on sheet-fed offset printing machines, in which a multiplicity of rolling elements (6, 7) arranged side by side in a plurality of rows (2, 3, 4, 5) are arranged in a plurality of outer raceways (8, 9, 10, 11) on the outer circumferential surface (12) of an inner ring (13) and in a plurality of inner raceways (14, 15, 16, 17) on the inner circumferential surface (18) of a thick-walled outer ring (19) roll, whose outer lateral surface (20) in the Cross-section convex contour and is intended for direct rolling on a cylindrical mating track. According to all rolling elements (6, 7) of the roller (1) are formed as ball rollers, each having two axial side symmetrically flattened from its basic spherical shape, parallel to each other arranged faces and thus distinguished from conventional bearing balls with the same load capacity by such a narrow design that despite the in four rows (2, 3, 4, 5) juxtaposed rolling elements (6, 7) no changes in the axial and radial dimensions of the roller 1 are necessary.

Description

Field of the invention

The The invention relates to a roller according to the preamble forming Features of claim 1, and in particular advantageous for rollers for gripper shaft control on sheet-fed offset printing machines or for control rollers in the folding unit of web offset printing presses applicable.

Background of the invention

castors are proven, highly sustainable and versatile usable machine elements used in a wide variety of applications be used. The most common embodiments provide support rollers, cam rollers and standard rollers which is mostly due to different Wälzkörperätze differ and either a conventional inner ring or have a roller pin. All embodiments However, they are mainly characterized by their thick-walled outer rings out, making them especially good for direct unrolling on cams or other flat or cylindrical mating tracks are suitable. The outer lateral surface This outer ring usually has a cross section convex contour on, in order to tilt the roller its edge load and to reduce the wear of the mating track. There Casters for receiving high radial loads and axial Forces in both directions are typical Application of rollers, for example, the gripper shaft control on sheetfed offset presses or as control rollers in the folder roll offset printing machines or their use in cam gears, Conveying systems or linear guidance systems.

Such rollers are, inter alia, by the published by the applicant catalog "Rolling Bearings" from January 2006 are known and described on pages 822 to 892 in the embodiments mentioned as support rollers, cam rollers and standard rollers and described.

The shown support rollers are doing by ready to install Needle or cylindrical roller bearings with a particularly thick-walled outer ring formed, whose rolling elements by vollnadelige or cage-guided needle rims or through full complement or cage-guided single or double row Cylinder wheel rings are formed. The support rollers can do this with or without axial guidance of the outer ring as well as open or through lip, split or labyrinth seals be formed sealed and are with or without inner ring Axles mounted.

The In contrast, the cam rollers shown correspond essentially to the Support rollers with axial guidance, but have instead of the inner ring a massive roller pin with mounting thread and a thrust washer on. Even with cam rollers are the rolling elements either by full needle or cage guided Needle rings or by full or cage-guided one or two-row cylindrical roller rings formed, the outwards by lip, split or labyrinth seals sealed against dirt and spray.

When Standard rollers are finally shown rollers, the same in their construction single or multi-row groove or angular contact ball bearings and essentially from an outer ring to an inner ring as well a variety in mostly two ball rings next to each other arranged bearing balls consist in two outer raceways on the outer surface of the inner ring or a roller pin and in two inner raceways on the inner Unroll the lateral surface of the thick-walled outer ring. The ball rings are doing in plastic cages guided and are outward by lip or Gap seals sealed against dirt and spray water.

A disadvantage of the said support and cam rollers, it has been found that the trained as a bearing needles or cylindrical rollers have a line contact with their careers, the cause of a relatively high friction torque and along with the high flexing of the filled lubricant for increased heat is in the caster. In continuous operation, the increased heat development in the roller can lead to a thermal expansion of their individual parts, through which the friction torque in the roller even higher and their life is severely limited. Likewise, results from the line contact trained as bearing needles or cylindrical rollers rolling elements to their careers in connection with high operating speeds and the centrifugal forces acting an unfavorable distribution of lubricant in the roller through which there is deficient lubrication between the rolling elements and their raceways and a further increase of Reibmomentes can come. In addition, the previous sealing concepts both support and cam rollers and standard rollers have not yet been sufficient to centrifugal force occurring at high operating speeds accumulation of the lubricant within the rollers on the inside of its outer ring and the consequent leakage of the lubricant to effectively avoid the seals passing out of the roller. It has also been shown on standard castors that they quickly reach the limits of their load carrying capacity under high radial and axial loads and at high operating speeds lubricant shortage and bearing overheating have an extremely shortened service life. An obvious measure to avoid such premature caster failures would be to increase their carrying capacity by larger-sized rolling elements or by arranging additional rows of rolling stock, however, such measures usually always at the expense of the radial and axial dimensions of the roller and usually require extensive changes in the adjacent construction ,

Object of the invention

outgoing from the stated disadvantages of the solutions of the known The prior art is therefore the object of the invention, a Roller, in particular for gripper shaft control on sheet-fed offset printing machines to design, which at the same or approximately the same axial and radial dimensions like known rollers a higher Load capacity, a lower friction torque, a cheaper Lubricant distribution and a longer service life has and at the centrifugal force due to leakage of the lubricant whose seals are effectively avoided.

Description of the invention

According to the invention This object with a roller with the features of the preamble of Patent claim 1 solved such that all rolling elements the roller are designed as ball rollers, each two axially symmetrical flattened from its basic spherical shape, parallel have mutually arranged end faces.

Of the The invention is therefore based on the finding that it is solely by the replacement of the previously as bearing balls or needles or as cylindrical rollers trained rolling elements against as ball rollers trained rolling elements and by an adapted thereto Career training in the caster is already possible while simultaneously reducing the friction torque, the number of rolling elements and thus to increase the carrying capacity of a roller in such a way that they are synonymous for higher radial loads at high Operating speeds is suitable, being flattened by the axial side and thus narrow training of the rolling elements no changes the axial and radial dimensions for such a roller necessary.

preferred Embodiments and advantageous developments of the invention formed Roller are described in the subclaims.

After that It is according to claims 2 and 3 at provided the inventively designed roller, that they preferably four rows of ball rollers trained rolling elements of which the two inner rows have an identical pitch circle diameter are formed, which is smaller than the also identical pitch circle diameter the two outer rows is. additionally is the diameter of the ball basic shape of the rolling elements of two outer rows opposite the diameter the rolling elements of the two inner rows larger formed, so that in each case an outer row and the adjacent inner row of rolling elements a first and a second row pair, each with different ones Wälzkörper- and pitch circle diameters form. Alternatively, it would also be possible for different Pitch circle diameters between the inner and outer rows of rolling elements the ball rollers of all rows with the same diameter of the ball basic shape train. It would also be possible to depend on the caster from the respective required load capacities with less or also more than four rows formed as ball rollers rolling elements equip with the same or different ball basic diameters. Regardless, however, it is an advantage, the ball rollers on the edges of their treads or the marginal parts their raceways in the inner and outer ring in addition with an expiring logarithmic profile to form with it Edge stresses between the ball rollers and their raceways contrary to act.

Based on the above-described embodiment, the inventively designed roller according to claims 4 and 5 further characterized by the fact that the adjacent rolling elements of both pairs of rows are each arranged on a common axis of rotation and parallel to each other inclined Druckwinkelachsen and both pairs of rows of rolling elements in O Arrangement against each other are hired. The rolling elements of each row pair are preferably guided in each case in a common, designed as a plastic cage cage bearing cage such that each arranged on a common axis of rotation rolling elements are arranged adjacent to each other in a common cage window with their mutually facing side surfaces and thus lead one another in an advantageous manner , In addition, it has proven to be particularly advantageous kinematically, if the diameter and widths of the adjacent rolling elements of both rows are each dimensioned such that all the rolling elements tangent to their outer contours Hüllkegel with their conical tips exactly at the intersection of the common axis of rotation of these rolling elements with the Rotation axis of the axial angular contact bearings are arranged. This Hüllkegel bearing kinematics known per se from tapered roller bearings provides an optimum for skew bearings of all kinds with regard to bearings load capacity, reduction in wear and service life and also causes in the specific case that each abutting ball rollers of two adjacent rows roll synchronously to each other or that at different relative speeds between these ball rollers, the friction occurring is reduced.

A alternative embodiment of an inventively designed It is roller according to claim 6 beyond, the roller form rolling elements formed only with three rows as ball rollers, all have an identical diameter of the ball base as well have the same pitch circle diameter. The thus formed rolling elements are on perpendicular to each other perpendicular pressure angle axes arranged and are in rows in individual, preferably as Kunststoffschnappkäfige trained camp cages led. Such Embodiment has been particularly advantageous for Applications proven in which the roller at higher operating speeds higher Radial loads but lower axial forces, such as in conveyor systems or linear guidance systems, is exposed. Depending on the required Load capacities, however, it is also possible with such trained rollers, these with less or more than three rows as ball rollers trained rolling elements with the same ball basic diameters train.

Independently from its embodiment it is according to the Claims 7 and 8 still a functional Development of the invention trained Roller that is axially next to the two outer Rows of rolling elements each one as armored Lip seal trained seal is arranged, with which trained as a lubricant depot space between the Outer ring and the inner ring or the roller journal of the roller sealed is. These lip seals are each in a hard-turned Ring groove in the inner circumferential surface of the outer ring fixed in position and supported by one or more elastic sealing lips grinding in each case a circumferential groove or on another surface in / on the outside Lateral surface of the inner ring or the roller journal of Roller off. Such, known per se lip seals are here by the use of ball rollers as rolling elements for the roller and the associated reduced axial space requirement of Wälzkörpersatzes especially advantageous applicable and wear in comparison to the previous mostly used gap or labyrinth seals essential for optimization the sealing action against in the space between the inner ring and the outer ring of the roller penetrating impurities and moisture. In addition, hard turning causes the Ring grooves for the seal fixing an increase the accuracy of the seal seat, by a centrifugal force Leakage of the lubricant through the seals out of the Roller is effectively avoided at high operating speeds.

Finally, it is proposed as an advantageous embodiment of the inventively embodied rolling bearing by claim 9 that both the outer surface of the outer ring and the running surfaces of the rolling elements or their outer and inner races in the outer ring or inner ring or roller journal have a wear-reducing coating. Particularly suitable in this case has a wear protection layer of Triondur ^® or Balinit ^® or a thin layer chromium plating proved, since each of these Be coatings a dry friction coefficient up to 80% compared to a pair steel steel dry, so that both the service life of the roller with respect on the mating track and the service life of the rolling element of the roller can be significantly increased.

In summary has the inventively designed roller thus compared to those known from the prior art Rollers have the advantage of having them through the use of multiple Rows of ball rollers as rolling elements at the same or approximately the same axial and radial dimensions as known Casters have a higher load capacity and a lower one Having friction torque. In addition, the Ball rollers have a more favorable distribution of lubricant due to their point contact with the raceways in the roller and by their reduced Axialbauraum the formation an enlarged lubricant depot and the Use of optimized seals, through which a centrifugal force Leakage of the lubricant from the roller effectively avoided becomes. This and additional wear protection layers on the outer surface of the outer ring and at the running surfaces of the rolling elements or on the outer and inner races in the outer ring or inner ring or Rolienzapfen the service life of the roller be increased significantly.

Brief description of the drawings

The According trained according to the invention roller is below in two preferred embodiments with reference explained in more detail in the accompanying drawings. Showing:

1 an enlarged cross-section through a first embodiment of an inventively designed roller;

2 an enlarged cross section through a second embodiment of an inventively designed roller.

Detailed description the drawings

Out 1 is clearly suitable for the gripper shaft control of a sheet-fed offset printing machine suitable roller 1 in which a variety in four rows 2 . 3 . 4 . 5 juxtaposed rolling elements 6 . 7 in four outer races 8th . 9 . 10 . 11 on the outer lateral surface 12 an inner ring 13 as well as in four inner raceways 14 . 15 . 16 . 17 on the inner lateral surface 18 a thick-walled outer ring 19 unroll, whose outer surface 20 has a convex contour in cross-section and is intended for direct rolling on a cylindrical mating track. All rolling elements 6 . 7 this roller 1 According to the invention are formed as ball rollers, each having two axial side symmetrically flattened from its basic spherical shape, arranged parallel to each other end faces and thus characterized over conventional bearing balls with the same load capacity by such a narrow design that despite the four rows 2 . 3 . 4 . 5 juxtaposed rolling elements 6 . 7 no changes in the axial and radial dimensions of the roller 1 necessary.

Furthermore, in 1 to see that of the four rows 2 . 3 . 4 . 5 designed as ball rollers rolling elements 6 . 7 the two inner rows 3 . 4 are formed with an identical pitch circle diameter, which is smaller than the also identical pitch circle diameter of the two outer rows 2 . 5 is and that at the same time the diameter of the ball basic shape of the rolling elements 6 the two outer rows 2 . 5 greater than the diameter of the rolling elements 7 the two inner rows 3 . 4 is trained.

A peculiarity of in 1 shown roller 1 it is that in each case an outer row 2 . 5 and the adjacent inner row 3 . 4 a first and a second row pair 21 . 22 form and the adjacent rolling elements 6 . 7 these two pairs of rows 21 . 22 each on a common axis of rotation 23 . 24 as well as on parallel to each other inclined pressure angle axes 25 . 26 . 27 . 28 are arranged. Both pairs of rows 21 . 22 the rolling elements 6 . 7 are employed in O-arrangement against each other and are each in a common, designed as a plastic cage cage bearing cage 29 . 30 guided such that each on a common axis of rotation 23 . 24 arranged rolling elements 6 . 7 are arranged in a common cage window and one another mutually lead or that the adjacent ball rollers of two adjacent rows 2 . 3 and 4 . 5 roll in sync with each other.

In 2 on the other hand is a roller which is particularly suitable for conveyor systems or linear guide systems 1' shown, in contrast to the previously described roller 1 a variety in three rows 2 . 3 . 4 juxtaposed rolling elements 6 in three outer races 8th . 9 . 10 on the outer lateral surface 12 an inner ring 13 as well as in three inner raceways 14 . 15 . 16 on the inner lateral surface 18 a thick-walled outer ring 19 unroll, whose outer surface 20 also has a convex contour in cross-section. The rolling elements 6 are also designed as ball rollers, each having two axial sides symmetrically flattened from its basic spherical shape, arranged parallel to each other end faces and rows in three in individual, designed as Kunststoffschnappkäfige bearing cages 29 . 30 . 31 be guided. Clearly visible are the rolling elements 6 In addition, formed with an identical diameter of the ball base shape and with the same pitch circle diameter and on parallel to each other perpendicular pressure angle axes 25 . 26 . 27 arranged so that they can be loaded at high operating speeds and lower axial forces with higher radial forces.

Finally, in the 1 and 2 to see that in both shown embodiments of the roller 1 . 1' axially next to the two outer rows 2 and 5 respectively. 2 and 4 the rolling elements 6 one each as a reinforced lip seal 32 . 33 trained seal is arranged, with which designed as a lubricant depot, unspecified gap between the outer ring 19 and the inner ring 13 the roller 1 . 1' is sealed. This, through the use of ball rollers as rolling elements 6 . 7 and the associated reduced axial space requirement of Wälzkörpersatzes space-optimized applicable lip seals 32 . 33 are clearly visible, each in a hard-turned annular groove 34 . 35 in the inner lateral surface 18 of the outer ring 19 Fixed in position and supported by an elastic sealing lip grinding in each case a circumferential groove 36 . 37 in the outer lateral surface 20 of the inner ring 13 the roller 1 . 1' from. In addition, both have the outer circumferential surface 20 of the outer ring 19 as well as the outer and inner races 8th . 9 . 10 . 11 and 14 . 15 . 16 . 17 in the outer ring 19 and in the inner ring 13 a wear-reducing coating of Triondur ^® on the service life of the roller 1 . 1' continue to increase.

1, 1'

caster

1

row of 6

2

row of 7 respectively. 6

3

row of 7 respectively. 6

4

row of 6

5

rolling elements

6

rolling elements

7

Outer raceway in 12

8th

Outer raceway in 12

9

Outer raceway in 12

10

Outer raceway in 12

11

outer surface of 13

12

Inner ring of 1 . 1'

13

Inner raceway in 18

14

Inner raceway in 18

15

Inner raceway in 18

16

Inner raceway in 18

17

inner lateral surface of 19

18

Outer ring of 1 . 1'

19

outer surface of 19

20

Row pair of 2 and 3

21

Row pair of 4 and 5

22

Rotation axis of 21

23

Rotation axis of 22

24

Pressure angle axis of 2

25

Pressure angle axis of 3

26

Pressure angle axis of 4

27

Pressure angle axis of 5

28

Bearing cage of 21 respectively. 2

29

Bearing cage of 22 respectively. 3

30

Bearing cage of 4

31

lip seal

32

lip seal

33

Ring groove for 32

34

Ring groove for 33

35

Circumferential groove for 32

36

Circumferential groove for 33

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited non-patent literature

• - "rolling bearings" of January 2006 [0003]

Claims (9)

Roller ( 1 ), in particular for gripper shaft control on sheet-fed offset printing machines, in which a plurality in a plurality of rows ( 2 . 3 . 4 . 5 ) juxtaposed rolling elements ( 6 . 7 ) in several outer races ( 8th . 9 . 10 . 11 ) on the outer lateral surface ( 12 ) of an inner ring ( 13 ) or roller pin and in several inner raceways ( 14 . 15 . 16 . 17 ) on the inner lateral surface ( 18 ) of a thick-walled outer ring ( 19 ), whose outer surface ( 20 ) has a cross-sectionally flat or convex contour and is provided for direct rolling on a flat or cylindrical mating track, characterized in that all rolling elements ( 6 . 7 ) of the roller ( 1 ) are formed as ball rollers, each having two axially symmetrically flattened from its basic spherical shape, arranged parallel to each other end faces. Roller ( 1 ) according to claim 1, characterized in that it preferably has four rows ( 2 . 3 . 4 . 5 ) designed as ball rollers rolling elements ( 6 . 7 ), of which the two inner rows ( 3 . 4 ) are formed with an identical pitch circle diameter, which is smaller than the also identical pitch circle diameter of the two outer rows ( 2 . 5 ). Roller ( 1 ) according to claim 2, characterized in that the diameter of the ball basic shape of the rolling elements ( 6 ) of the two outer rows ( 2 . 5 ) relative to the diameter of the rolling elements ( 7 ) of the two inner rows ( 3 . 4 ) is larger and each having an outer row ( 2 . 5 ) and the inner row ( 3 . 4 ) a first and a second row pair ( 21 . 22 ) form. Roller ( 1 ) according to claim 3, characterized in that the adjacent rolling elements ( 6 . 7 ) of both pairs of rows ( 21 . 22 ) each on a common axis of rotation ( 23 . 24 ) and parallel to each other oblique Druckwinkelachsen ( 25 . 26 . 27 . 28 ) are arranged and both pairs of rows ( 21 . 22 ) of the rolling elements ( 6 . 7 ) are employed in O arrangement against each other. Roller ( 1 ) according to claim 4, characterized in that the rolling bodies ( 6 . 7 ) of each row pair ( 21 . 22 ) preferably in a common, designed as a plastic cage cage bearing cage ( 29 . 30 ) and in each case on a common axis of rotation ( 23 . 24 ) arranged rolling elements ( 6 . 7 ) are arranged on one side mutually leader in a common cage window. Roller ( 1' ) according to claim 1, characterized in that it preferably three in individual bearing cages ( 29 . 30 . 31 ) guided rows ( 2 . 3 . 4 ) designed as ball rollers rolling elements ( 6 ), which are formed with an identical diameter of the ball basic shape and with the same pitch circle diameter and on mutually perpendicular perpendicular Druckwinkelachsen ( 25 . 26 . 27 ) are arranged. Roller ( 1 . 1' ) according to claim 5 and 6, characterized in that axially adjacent to the two outer rows ( 2 . 5 respectively. 4 ) of the rolling elements ( 6 ) one each as a reinforced lip seal ( 32 . 33 ) formed seal is arranged, with which the trained as a lubricant depot space between the outer ring ( 19 ) and the inner ring ( 13 ) or shaft journal of the roller ( 1 . 1' ) is sealed. Roller ( 1 . 1' ) according to claim 7, characterized in that the lip seals ( 32 . 33 ) each in a hard-turned annular groove ( 34 . 35 ) in the inner circumferential surface ( 18 ) of the outer ring ( 19 ) are fixed in position and sliding over one or more elastic sealing lips in each case a circumferential groove ( 36 . 37 ) in the outer lateral surface ( 20 ) of the inner ring ( 13 ) or roller pin of the roller ( 1 . 1' ) are arranged supporting. Roller ( 1 . 1' ) according to claim 8, characterized in that both the outer lateral surface ( 20 ) of the outer ring ( 19 ) as well as the running surfaces of the rolling elements ( 6 . 7 ) or their outer and inner races ( 8th . 9 . 10 . 11 and 14 . 15 . 16 . 17 ) in the outer ring ( 19 ) or in the inner ring ( 13 ) or in the roller journal a wear-reducing coating, for example made of Triondur or a thin-layer chrome plating, have.