GB2270127A - Split-type bearing assembly eg for a crankshaft. - Google Patents

Split-type bearing assembly eg for a crankshaft. Download PDF

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Publication number
GB2270127A
GB2270127A GB9313853A GB9313853A GB2270127A GB 2270127 A GB2270127 A GB 2270127A GB 9313853 A GB9313853 A GB 9313853A GB 9313853 A GB9313853 A GB 9313853A GB 2270127 A GB2270127 A GB 2270127A
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GB
United Kingdom
Prior art keywords
outer race
split
segments
bearing assembly
type bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
GB9313853A
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GB9313853D0 (en
GB2270127B (en
Inventor
Kazuyoshi Harimoto
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NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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Publication date
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of GB9313853D0 publication Critical patent/GB9313853D0/en
Publication of GB2270127A publication Critical patent/GB2270127A/en
Application granted granted Critical
Publication of GB2270127B publication Critical patent/GB2270127B/en
Anticipated expiration legal-status Critical
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16BDEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B5/00Joining sheets or plates, e.g. panels, to one another or to strips or bars parallel to them
    • F16B5/0004Joining sheets, plates or panels in abutting relationship
    • F16B5/0056Joining sheets, plates or panels in abutting relationship by moving the sheets, plates or panels or the interlocking key perpendicular to the main plane
    • F16B5/006Joining sheets, plates or panels in abutting relationship by moving the sheets, plates or panels or the interlocking key perpendicular to the main plane and using ring-shaped clamps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30Parts of ball or roller bearings
    • F16C33/58Raceways; Race rings
    • F16C33/60Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/02Crankshaft bearings
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05CINDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2201/00Metals
    • F05C2201/04Heavy metals
    • F05C2201/0433Iron group; Ferrous alloys, e.g. steel
    • F05C2201/0436Iron
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/44Needle bearings
    • F16C19/46Needle bearings with one row or needles
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50Positive connections
    • F16C2226/70Positive connections with complementary interlocking parts
    • F16C2226/74Positive connections with complementary interlocking parts with snap-fit, e.g. by clips

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

The bearing assembly comprises a an outer race (1) with a plurality of outer race segments (1A, 1B) separated circumferentially from each other by joints (A) which extend generally longitudinally. To connect the segments (1A, 1B) together to provide the complete bearing outer race (1), mounting grooves (2) are provided, one for each joint (A), in an outer peripheral surface of the outer race (1) so as to form a loop which straddles the respective joint (A), and a connecting member (3) which is press-fitted into the associated mounting groove (2). The connecting member may be a snap ring (3), a circlip, a plate washer or a garter spring. <IMAGE>

Description

2270127 Split-type Bearing Assembly The present invention generally
relates to a bearing assembly of two-piece construction and, for example to a split-type bearing assembly suited for use in rotatably supporting a crankshaft of an internal combustion engine within a crankcase.
In the marine outboard engine, one or more split-type bearing assemblies are generally employed for the support of a crankshaft, one example of which is fragmentarily shown in Fig. 8 in a longitudinal sectional representation. This prior art split type bearing assembly will now be discussed with reference.to Fig.
9.
The marine outboard engine includes a crankshaft 10 of one-piece construction including axially aligned shaft portions 10a, a pair of webs 10b interposed between each neighboring shaft portions 10a and a crank pin 10c connecting the webs 10b together, and a connecting rod 11 rotatably connected with the respective crank pin 10c. This crankshaft 10 is encased in a crankcase 12 while some of the shaft portions 10a are rotatably supported by associated split-type bearing assemblies 14 each interposed between the respective shaft portion 10a and a bearing seat 13 integral with the crankcase 12. Each of the split-type bearing assemblies 14 is in the form of a roller bearing with no inner race.
More specifically, the split-type bearing assembly 14 includes a bearing outer race 15 that is circumferentially separat ed, i.e-, split in a plane containing a longitudinal axis of the < 1 > bearing outer race 12, into two outer race halves, a Plurality of rolling elements 16, for example, needle rollers,and a roller retainer or cage 17 for rotatably retaining the rolling elements 16, said roller retainer 17 being also separated circumferentially into two retainer halves. The bearing outer race 15 has an outer peripheral surface formed with a circumferentially extending lock groove 20 adapted to accommodate therein a snap ring 18 that is used to keep the outer race halves connected together during assemblage of the crankshaft 10 into the crankcase 12. Opposite split faces of each of the outer race halves forming the bearing outer race 15 are generally not ground and represent a naturally fractured face by which, when the outer race halves are mated together, no substan tial displacement occurs between them.
The associated bearing seat 13 integral with the crank case 12 includes a bearing body 13a integral with the crankcase 12 and a cover member 13b and has a cylindrical inner peripheral surface defined between the bearing body 13a and the cover member 13b. The corresponding bearing outer race 15 is accommodated within the hollow delimited by the cylindrical inner peripheral surface of the bearing seat 13 with the outer race halves tightly mated together by the cover member 13b. In this prior art split type bearing assembly 14 shown in Fig. 9, the bearing outer race 15 has such an axial length as to allow at least one end thereof to protrude a distance outwardly from adjacent ends of the rolling elements 16, and a sealing ring 19 is interposed between that one end of the bearing outer race 15 and the shaft portion 10a- The sealing ring 19 may be a ring-shaped contact seal made of rubber or any other suitable sealing member.
< 2 > During assemblage, the split-type bearing assembly 14 is set in position on the crankshaft 10, followed by a mounting of the snap ring 18:to retain the split-type bearing assembly 14 in a temporarily assembled condition. In other words, the split-type bearing assembly 14 is retained in the temporarily assembled condition before the assembly of the crankshaft 10 with the split type bearing assembly 14 is accommodated within the crankcase 12, thereby to prevent a undesirable separation of the outer race halves of the bearing outer race 15 from each other from taking place during assemblage.
In assembling the split-type bearing assembly 14, it is extremely important for the outer race halves of the bearing outer race 15 to be accurately positioned relative to each other with a pair of opposite split faces of one outer race half exactly aligned with another pair of opposite split faces of the other outer race half, so that a precisely tailored raceway can eventually be obtained in the assembled split-type bearing assembly 14. However, since the snap ring 18 is used for mounting on the outer periphery of the split-type bearing assembly 14, the snap ring 18 generally has a small thickness and a large diameter and is therefore less capable of providing a sufficiently required clamping force necessary to firmly retain the outer race halves together during assemblage.
Because of the problem of the snap ring 18 discussed above, it often occurs that, before the assembly of the crankshaft with the split-type bearing assembly 14 is mounted in the crank case 12, the.opposite split faces of one of the outer race halves may be displaced from the mating opposite split faces of the other of the outer race halves under the influence of the weight of the < 3 > bearing outer race 15 and/or impacts induced during the assemblage If the split-type bearing assembly 14 is assembled while the outer race halves of. the bearing outer race 15 displaced relative to each other, obnoxious noises will be easily generated during an operation of the split-type bearing assembly 14, requiring a re assemblage of the split-type bearing assembly 14 to rectify them.
Specifically in this type of split-type bearing assembly 14 utilizing the sealing ring 19, utmost care is required for the split-type bearing assembly 14 to be accurately assembled with the opposite split faces of one outer race half exactly aligned with the mating opposite split faces of the other outer race to secure a high sealability.
For this reason, various improvements have hitherto been made in design, shape and/or physical strength of any of the lock groove 20 and the snap ring 18. However, in view of limitations of dimension, no decisive solution has yet been made available. In other words, the snap ring 18 must have a diameter sufficient to encompass the outer periphery of the bearing outer race 15 and, in order to provide the bearing outer race 15 with a required clamping force, the snap ring 18 must have an increased thickness, that is, an increased cross-section- This in turn necessitates the lock groove 20 to have both a depth and a width increased enough to accommoda te the increased thickness of the snap ring 18. For a given size of the bearing outer race 15, the use of the lock groove 20 having the increased depth and width constitutes a cause of reduction in physical strength of the bearing outer race 15 as a whole. This incompatibility has hitherto made it difficult to increase the clamping f orce available from the snap ring 18.
< 4 > In addition, since the lock groove 20 is formed so as to extend over the entire circumference of the bearing outer race 15, reduction in physical strength of the bearing outer race 15 would be pronounced if the lock groove 20 is formed at a portion of the bearing outer race 15 intermediate of the axial length thereof where the bearing outer race 15 is apt to receive a considerable load from the rolling elements 16- The current practice is there fore to form the lock groove 20 at a location adjacent one end of the bearing outer race 15. This leads to a problem in that the clamping force exerted by the snap ring 18 so as to clamp the outer race halves together is not uniformly distributed over the length of the bearing outer race 15 and a gap tends to be formed between the outer race halves at a location adjacent the opposite end of the bearing outer race 15 remote from the snap ring 18 In view of the foregoing, the present invention has been devised to provide an improved split-type bearing assembly wherein the outer race segments forming the bearing outer race are claimed together with the clamping force distributed uniformly over the length thereof and can, if required, be easily detached from each other To this end, the present invention provides a split-type bearing assembly for use in rotatably supporting a shaft such as, for example, a crankshaft, within a casing such as, for example, a crankcase. This split-type bearing assembly comprises a bearing outer race including a plurality of race segments separated circumferentially from each other and fitted to the casing- The outer race has circumferentially spaced joints defined between each neighboring race segments. The outer race may be of two-piece type.
A plurality of rolling elements are disposed in a circumferentially extendin.9 row and held in rolling contact with an inner surface of the bearing outer race To connect the outer race segments together to provide the complete bearing outer race, mounting grooves are employed one for each joint, each of said mounting grooves being defined on an outer peripheral surface of the bearing outer race so as to form a loop encompassing at least a portion of the associated joint by straddling the respective joint, and a connecting member is employed for each mounting groove. This connecting member is so shaped as to be press-f itted into said associated mounting groove to connect the associated neighboring race segments together thereby to complete the bearing outer race.
With two-piece type, diametrically opposite portions of the outer peripheral surface of the bearing outer race are formed with mounting grooves, respectively - Each of the mounting grooves is so shaped as to extend from one side portion of the first outer race segment to the adjacent side portion of the second outer race segment across the respective joint and then from such adjacent side portion of the second outer race segment to such one side portion of the first outer race segment across such respective joint. A connecting member employed for each of the first and second mounting grooves is press-fitted into said associated mounting groove to connect the first and second outer race segments together thereby to complete the bearing outer race.
According to the present invention, the outer race segments are firmly mated together by means of the connecting members that are press-f itted into the respective mounting grooves defined on the outer peripheral surface of the bearing outer race < 6 > so as to straddle the associated joints between the outer race segments.. Since the present invention dispenses with the necessity to form any groove around the outer periphery of the bearing outer race such as necessitated in the bearing outer race used in the prior art split-type bearing assembly and allows each mounting groove to be formed at a respective localized portion of the outer peripheral surface of the bearing outer race, each connecting member of a reduced circumferential length can be advantageously employed and, therefore, the required clamping force can be secured notwithstanding a small sectional dimension. Consequently, each mounting groove may have a small depth and, hence, dimensional limitations imposed by the thickness of the wall of the bearing outer race should pose no problem in designing the connecting members and/or the mounting grooves.
Moreover, since, unlike the circumferentially extending groove employed in the prior art assembly, the mounting grooves are formed in the vicinity of the associated joints between the outer race segments, the formation of these mounting grooves does not result in a substantial reduction in physical strength of the resultant bearing outer race. Accordingly, the present invention makes it possible to form each mounting groove so as to occupy a position intermediate of the axial length of the bearing outer race where a load tends to be centered on from the rolling elements during the operation of the bearing assembly and, since the con necting members pressfitted into the respective mounting grooves exerts respective clamping forces acting uniformly over the axial length of the bearing outer race, the first and second outer race segments can be firmly connected together to complete the bearing outer race.
< 7 > Furthermore, since each connecting member is small in size as compared with the snap ring used in the prior art bearing assembly so as-to extend over the circumference of the bearing outer race, each connecting member can be easily mounted in and removed from the associated mounting groove and this feature is advantage ous particularly when the bearing outer race is desired to be dismounted and subsequently mounted at the time of overhauling of the engine.
Each mounting groove for accommodating the associated connecting member is preferably of a round shape as viewed in a radial direction of the bearing outer race because of an ease of machining or grinding.
Also, each mounting groove may be of a substantially U shaped cross-section delimited by a bottom face and a pair c-if side faces lying perpendicular to the bottom face. This U-shaped cross section of each mounting groove permits the associated connecting member to be easily removed therefrom when the dismounting is desired. However, where it is important to ensure a f irm retention of each connecting member within the associated mounting groove rather than the ease to remove, each mounting groove may be so shaped as to have a generally dovetail cross-section delimited by a bottom face and a pair of side faces lying at an acute angle relative to the bottom f ace.
Preferably, each connecting member is of a type capable of exerting a radially inwardly acting elastic compressive force which provides the clamping force necessary to clamp firmly together islands left in the first and second outer races by the formation of the associated mounting groove, thereby to connect the < 8 > f irst and second outer race segments together to complete the bearing outer race.
In any event, the present invention will become more clearly understood from the following description of a preferred embodiment thereof, when taken in conjunction with the accompanying drawings. However, the embodiment and the drawings are given only for the purpose of illustration and explanation, and are not to be taken as limiting the scope of the present invention in any way whatsoever, which scope is to be determined by the appended claims.
In the accompanying drawings, like reference numerals are used to denote like parts throughout the several views, and:
Fig. 1 is a schematic perspective view showing an bearing outer race used in a split-type bearing assembly according to one preferred embodiment of the present invention; Fig. 2 is a fragmentary side view of the bearing outer race shown in Fig. 1, showing one joint between outer race halves forming the bearing outer race; Fig. 3 is a fragmentary end view, with a portion shown in section, of the bearing outer race shown in Fig. 1, showing the joint between the outer race halves forming the bearing outer race; Fig. 4 is a plan view of a connecting member used on the bearing outer race shown in Fig- 1-, Fig. 5 is a side view of a modif ied f orm of the connecting member; Figs. 6(a) and 6(b) are front elevational and side sectional views of a further modified form of the connecting member, respectively; < 9 > Figs. 7(a) and 7(b) are front elevational and side sectional views of a still further modified form of the connecting member, respectively; Fig- 8 is a view similar to Fig. 3, showing a modified form of a lock groove formed on an outer peripheral surface of the bearing outer race; and Fig. 9 is a fragmentary longitudinal sectional view of a crankshaft having the prior art split-type bearing assembly mounted thereon.
The present invention is directed to a split-type bearing assembly which may be similar to that shown in and described with reference to Fig- 9, except for the details of a bearing outer race employed therein. The bearing outer race designed according to the present invention is shown by 1 in Figs. 1 to 3.
With reference to Figs. 1 to 3, the bearing outer race 1 shown therein is of a collarless type having an inner peripheral surface serving as a raceway for rolling elements which may be needle rollers. This bearing outer race 1 in the illustrated embodiment is of a two-piece construction including outer race segments 1A and 1B which are obtained by splitting the bearing outer race 1 along a plane containing a longitudinal axis thereof. Each of these outer race segments is therefore of a generally semicircu lar configuration and has split faces Sa and Sb opposite to each other. As a matter of design, when the outer race segments 1A and 1B are mated together to provide the complete bearing outer race 1, diametrically opposite joints A are formed between the opposite split faces Sa of one of the outer race segments 1A and 1B and the < 10 > mating opposite split faces Sb of the other of the outer race segments 1Aand 1B.
The illustrated bearing outer race 1 has its outer peripheral surface formed with a pair of annular mounting grooves 2 recessed inwardly of the outer surface of the bearing outer race 1 and straddling the respective joints A. More specifically, in an assembled condition of the bearing outer race 1, each mounting groove 2 represents an annular configuration extending from one side portion of the outer race segment 1A adjacent the respective joint A to the adjacent side portion of the outer race segment 1B across such joint A following a semicircular path and then f rom such adjacent side portion of the outer race segment 1B to such one side portion of the outer race segment 1A across such respective joint A similarly following a semicircular path. Thus, it will readily be understood that each mounting groove 2 is divided into two generally semicircular groove segments positioned respectively on the outer race segments 1A and 1B.
With each mounting groove 2 so formed in part on the outer race segment 1A and in part on the outer race segment IB as described above, islands 5A and 5B of a semicircular configuration are left on the outer race segments 1A and 1B, respectively, and surrounded by the associated semicircular groove segments forming the respective mounting groove 2.
As best shown in Fig. 2, each mounting groove 2 is positioned at a portion of the complete bearing outer race 1 intermediate of the axial length thereof. Each mounting groove 2 is utilized to accommodate therein a correspondingly annular connecting member 3 which will now be described.
< 11 > As best shown in Fig- 3, when the outer race segments 1A and 1B are mated together to provide the complete bearing outer race 1, the annular connecting members 3 are pressfitted into the respective mounting grooves 2 thereby to clamp the outer race segments 1A and 1B firmly together. For this purpose, each annular connecting member 3 has an inner diameter slightly undersized relative to the circle depicted by the semicircular islands SA and 5B such that, when the annular connecting member 3 is press-f itted into the respective mounting groove 2, the associated islands SA and 5B can be brought close to each other thereby to clamp the outer race segments 1A and 1B f irmly together. At this time, the inner periphery of each annular connecting member 3 is held in tight contact with the composite peripheral surface of the islands SA and 5B positioned radially inwardly of the associated mounting groove 2_ Each annular connectin"g member 3 employed in the illust rated embodiment is in the form of what is generally referred to as a circlip, i.e., a flat clip ring having a radial slit 3a as best shown in Fig. 4 and made of metal such as, for example, iron. This circlip, when circumferentially expanded, accumulates an elastic force tending itself to restore to the original shape and, there fore, when the circlips 3 are press-fitted into the respective mounting grooves 2 so as to encircle the islands SA and 5B, the elastic forces exerted by the circlips 3 act as clamping forces necessary to firmly clamp the outer race segments 1A and 1B together The bearing outer race 1 embodying the present invention may be manufactured in the following manner. An outer race member having a predetermined length, which eventually forms the bearing < 12 > outer race 1, is cut from a rigid member. Before this outer race member is split into two outer race segments to provide the outer race segments 1A and 1B, the mounting grooves 2 are formed over intended lines of split by machining or grinding at diametrically opposite portions of the outer peripheral surface of the outer race member. The outer race member having the mounting grooves 2 formed on the outer peripheral surface thereof is then heat-treated and ground and is, thereafter, split into two outer race segments, that is, the outer race segments 1A and 1B. In splitting the outer race member into the outer race segments 1A and 1B, a natural fracture method is preferably employed to allow the outer race member to undergo a natural fracture along the intended lines of split to provide the outer race segments 1A and 1B.
The natural fracture method referred to above is a method of dividing the outer race member into two segments without utilizing any cutter and is disclosed in, for example, the Japanese Patent Publication 63-29129 published June 3, 1988. According to the natural fracture technique, in order to facilitate a natural fracture of the outer race member, the outer race member is formed either with shallow line grooves on an outer peripheral surface thereof along diametrically opposite split lines or with a pair of crack- initiating notches at opposite end faces thereof in alignment with diametrically opposite split lines. The outer race member is then applied a load acting radially inward of the outer race member enough to allow the outer race member to crack along the split lines to provide the outer race segments 1A and 1B. As a matter of course, in accordance with the present invention, the outer race segments 1A and 1B are mated f irmly together by means of the annular < 13 > connecting members 3 in the manner hereinbefore described to complete the bearing outer race 1.
In completing the split-type bearing assembly, rolling elements and a two-piece retainer or cage are positioned radially inside the bearing outer race 1 as is the case with those in the prior art split-type bearing assembly shown in Fig- 9_ Also, the split-type bearing assembly embodying the present invention may be employed as an equivalent substitute for the prior art split-type bearing assembly 14 of Fig. 9 and may therefore be mounted on the crankshaft 10 and encased within the crankcase 12 as shown in Fig.
9.
Thus, according to the present invention, the outer race segments 1A and 1B are firmly mated together by means of the connecting members 3 each press-f itted into the respective mounting groove 2 defined on the outer peripheral surface of the bearing outer race 1 so as to straddle the associated joint A between the outer race segments 1A and 1B. The present invention dispenses with the necessity to form any groove around the outer periphery of the bearing outer race such as necessitated in the bearing outer race used in the prior art split-type bearing assembly and allows each mounting groove 2 to be formed at a respective localized portion of the outer peripheral surface of the bearing outer race 1. Even though each mounting groove 2 so formed at the respective localized portion of the outer peripheral surface of the bearing outer race 1 has a circumference smaller than that of the groove 20 formed around the bearing outer race 13 in the prior art split-type bearing assembly, each connecting member 3 employable in the practice of the present invention can have a reduced circumferential length and, therefore, the required clamping force can be secured notwith < 14 > standing a small sectional dimension. Consequently, since each mounting groove 2 may have a small depth, dimensional limitations imposed by the thickness of the outer surface of the bearing outer race 1 should pose no problem in designing the connecting members 3 and/or the mounting grooves 2.
Thus, since the connecting members 3 are of a type providing an increased clamping force and the increased clamping force of each connecting member 3 is utilized to connect the outer race segments 1A and 1B together to complete the bearing outer race 1, any possible displacement between the outer race segments 1A and 1B can advantageously be eliminated, allowing the resultant bearing outer race 1 to provide a precisely tailored raceway for the contact with the rolling elements. Also, a high sealability can be secured if a sealing member is employed in a manner similar to the sealing ring 19 employed in the prior art split-type bearing assembly shown in Fig. 9.
Considering that each mounting groove 2 on the outer peripheral surface of the bearing outer race 1 is positioned intermediate of the axial length of the bearing outer race 1, the clamping force exerted by the respective annular connecting member 3 can advantageously be distributed substantially uniformly over the axial length of the bearing outer race 1, permitting the outer race segments 1A and 1B to be firmly mated together to complete the bearing outer race 1. Since, unlike the circumferentially extend ing groove employed in the prior art assembly, the mounting grooves
2 are formed in the vicinity of the associated -joints A between the outer race segments 1A and 1B, the formation of these mounting grooves 2 in accordance with the teachings of the present invention does not result in a substantial reduction in physical strength of < 15 > the resultant bearing outer race 1. Accordingly, even though each mounting groove 2 is formed so as to occupy a position intermediate of the axial length of the bearing outer race 1 where a load tends to be centered on f rom the rolling elements during the operation of the bearing assembly, no substantial reduction in physical strength of the bearing outer race 1 occur.
Furthermore, since each mounting groove is of a round shape as viewed in a radial direction of the bearing outer race 1, machining or grinding of the mounting groove on the outer race 1 is easy to perform.
As compared with the snap ring employed in the prior art bearing assembly, the annular connecting member 3 employed for each mounting groove 2 is considerably small in size and can therefore be easily mounted in and removed from the associated mounting groove 2 when the bearing is desired to be dismounted at the time of overhauling of the engine. Although each annular connecting member 3 has been shown and described as employed in the form of a circlip, that is, a flat clip ring having a radial slit 3a as best shown in Fig. 4, the annular connecting member 3 which can be employed in the practice of the present invention may take any shape, form and design other than the circlip depending on the magnitude of the clamping force desired to be exerted thereby.
For example, each annular connecting member 3 may be in the form of a circlip of a type having opposite ends 3a and 3b and a generally intermediate angular portion 3c all adapted to be held in contact with the islands 5A and 5B when mounted in the corres ponding mounting groove 2 such as shown in Fig. 5_ Alternatively.
it may be in the form of a connecting ring of a shape having a plurality of circumferentially spaced, radially inwardly extending < 16 > spokes 3d which are, when mounted in the corresponding mounting groove 2, held in contact under pressure with the islands 5A and 5B, such as shown in Figs. 6(a) and 6(b). Again alternatively, as shown in Figs. 7(a) and 7(b), each annular connecting member 3 may be a generally ring-shaped push nut of a design having an elastically deformable plate region 3e situated radially inwardly thereof, said deformable plate region 3e being capable of functioning in a similar manner to a plate washer. A garter spring may also be employed for the connecting member 3.
Each annular connecting member 3 employed in the practice of the present invention may be made of any suitable material such as, for example, aluminum, synthetic resin, wire, press material, spring steel, other than iron referred to hereinbefore.
Also, each mounting groove 2 is of a substantially U shaped cross-sectiondelimited by a bottom face and a pair of side faces lying perpendicular to the bottom face. This U-shaped cross section of each mounting groove 2 permits the associated connecting member 3 to be easily removed therefrom when the dismounting is desired. However, where it is important to ensure a firm retention of each connecting member 3 within the associated mounting groove 2 rather than the ease to remove, each mounting groove 2 may be so shaped as to have a generally dovetail cross-section delimited by a bottom face and a pair of side faces lying at an acute angle relative to the bottom face as shown in Fig. 7.
In describing the preferred embodiment of the present invention, although each mounting groove 2 has been shown as being of a round shape as viewed in a radial direction of the bearing outer race, it may be of a generally rectangular shape or of a generally oval shape if desired.
< 17 > Although the present invention has been fully described in connection with the preferred embodiment thereof with reference to the accompanying drawings which are used only for the purpose of illustration, those skilled in the art will readily conceive numerous changes and modifications within the framework of obvious ness upon the reading of the specification herein presented of the present invention - For example, although the present invention has been described and shown as applied to the collarless bearing outer race of the splittype bearing assembly, the present invention can be equally applied to the bearing outer race of a type having collars at opposite ends thereof for avoiding axial displacement of the rolling elements.
Also, while in describing the preferred embodiment of the present invention, reference has been made to the split-type bear.Ing assembly of the type having no inner race, the present invention can be equally applicable to the split-type bearing assembly of a type utilizing an inner race in combination with the two-piece outer race.
Also, the present invention is not always limited to the split-type bearing assembly for the support of the crankshaft within the crankcase such as shown and described with reference to the accompanying drawings, but may equally be applied to any other split-type bearing assembly used for the support of a shaft within any suitable casing.
Furthermore, although the bearing outer race has been shown and described as comprised of the two outer race segments, the number of the outer race segments forming the bearing outer race may not be always limited to two, but may be three or more. Where three or more outer race segments are employed, they can readily be < 18 > prepared by the use of a cutting technique rather than the natural fracture technique.
Accordingly, such changes and modifications are, unless they depart from the scope of the present invention to be construed as included therein.
< 19 >

Claims (1)

  1. CLAIMS split-type bearing assembly for use in rotatably supporting a shaft
    within a casing, which comprises:
    a bearing outer race including a plurality of race segments separated circumferentially from each other and fitted to the casing, said outer race having circumferentially spaced joints defined between each neighboring race segments; a plurality of rolling elements disposed in a circumferential ly extending row and held in rolling contact with an inner surface of the bearing outer race; mounting grooves employed one for each joint, each of said mounting grooves being defined on an outer peripheral surface of the bearing outer race so as to form a loop encompassing at least a portion of the associated joint by straddling the respective joint; and a connecting member employed for each mounting groove, said connecting member being so shaped as to be press-fitted into said associatecl mounting groove to connect the associated neighboring race segments together thereby to complete the bearing outer race 2_ The split-type bearing assembly as claimed in Claim 1, wherein the number of said race segments is two 3_ The split-type bearing assembly as claimed in Claim 1, wherein each of said mounting grooves represents a generally round shape when viewed radially of the bearing outer race 4_ The split-type bearing assembly as claimed in Claim 1, wherein each of said mounting grooves is comprised of first and second groove segments, said f irst and second groove segments being formed in the neighboring outer race segments adjacent the <.20 > associated joint, respectively, the neighboring side Portions of the outer race segments having respective islands encompassed by the associated first and second groove segments, and wherein said connecting member for each mounting groove, when press-f itted into the respective mounting groove, clamping the islands firmly together thereby to connect the neighboring outer race segments together.
    5. The split-type bearing assembly as claimed in Claim 1, wherein each of said mounting grooves is defined on the bearing outer race at a position intermediate of the axial length of the bearing outer race.
    6. The split-type bearing assembly as claimed in Claim 1, wherein each of said mounting grooves has a generally U-shaped cross-section.
    7. The split-type bearing assembly as claimed in Claim 1, wherein each of said mounting grooves has a generally dovetail shaped cross-section.
    8. The split-type bearing assembly as claimed in Claim 4, wherein said connecting member exerts an elastic clamping force necessary to bring the islands close to each other thereby to f i rmly connect them together.
    9. A split-type bearing assembly substantially as herein described with reference to and as illustrated in Figs. 1 to 7 of the accompanying drawings.
    < 21 >
GB9313853A 1992-08-31 1993-07-05 Bearing assembly Expired - Fee Related GB2270127B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP25713492A JPH0681846A (en) 1992-08-31 1992-08-31 Split type bearing

Publications (3)

Publication Number Publication Date
GB9313853D0 GB9313853D0 (en) 1993-08-18
GB2270127A true GB2270127A (en) 1994-03-02
GB2270127B GB2270127B (en) 1996-10-16

Family

ID=17302199

Family Applications (1)

Application Number Title Priority Date Filing Date
GB9313853A Expired - Fee Related GB2270127B (en) 1992-08-31 1993-07-05 Bearing assembly

Country Status (3)

Country Link
JP (1) JPH0681846A (en)
DE (1) DE4323278C2 (en)
GB (1) GB2270127B (en)

Cited By (1)

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GB2362435A (en) * 2000-04-19 2001-11-21 Dana Corp Semi-cylindrical bearing halves and housing with locking plate

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US6142923A (en) 1998-08-05 2000-11-07 Gbr Systems Corporation Roller ring
DE10230425A1 (en) * 2002-07-06 2004-01-22 Bayerische Motoren Werke Ag Bearing bush for IC engine crankshaft is made up of two halves which fit together with butt joints and have end flanges, halves being held together by clips across butt joints
DE10302002A1 (en) * 2003-01-21 2004-07-29 Fev Motorentechnik Gmbh Roller bearing, for a one-piece IC motor crankshaft, has two half-cages locked together by a swallowtail joint for centrifugal forces to be transmitted from the outer to the inner half-cage without rattling
DE10322248B4 (en) * 2003-05-13 2006-10-19 Federal-Mogul Wiesbaden Gmbh & Co. Kg System with shaft and at least two bearings and device for producing a system with shaft and at least two bearings
JP2007085447A (en) * 2005-09-21 2007-04-05 Ntn Corp Crankshaft support structure
JP4947959B2 (en) * 2005-11-22 2012-06-06 Ntn株式会社 Crankshaft support structure
DE102006035180A1 (en) * 2006-07-29 2008-01-31 Schaeffler Kg Four-point bearing e.g. radial roller bearing, has roller body formed as spherical rollers with two symmetrical side surfaces, which are leveled in spherical base shape and arranged parallel to each other
EP2019217A2 (en) 2007-07-25 2009-01-28 JTEKT Corporation Split bearing
JP5303240B2 (en) 2008-10-22 2013-10-02 Ntn株式会社 Rolling bearing and rotating shaft support structure
DE102011085647A1 (en) * 2011-11-03 2013-05-08 Bayerische Motoren Werke Aktiengesellschaft Divided bearing shell i.e. eccentric cam shell, for use in crank drive of piston-internal combustion engine, has mounting unit comprising tension rod with tension head, where cross-section of tension head is larger than that of tension rod
CN113503293B (en) * 2021-04-09 2023-04-07 温琴学 Two-in-one invisible fastener and working method thereof

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GB292108A (en) * 1927-06-13 1929-02-07 Cie Applic Mecaniques Improvements in or relating to anti-friction bearings
GB918646A (en) * 1960-01-04 1963-02-13 Schaeffler Wilhelm Improvements in or relating to roller bearings
GB1006415A (en) * 1962-11-16 1965-09-29 Schaeffler Wilhelm Spherical journal bearing
GB1104877A (en) * 1966-05-26 1968-03-06 Elges Helmut Self-aligning bearings

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
GB292108A (en) * 1927-06-13 1929-02-07 Cie Applic Mecaniques Improvements in or relating to anti-friction bearings
GB918646A (en) * 1960-01-04 1963-02-13 Schaeffler Wilhelm Improvements in or relating to roller bearings
GB1006415A (en) * 1962-11-16 1965-09-29 Schaeffler Wilhelm Spherical journal bearing
GB1104877A (en) * 1966-05-26 1968-03-06 Elges Helmut Self-aligning bearings

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2362435A (en) * 2000-04-19 2001-11-21 Dana Corp Semi-cylindrical bearing halves and housing with locking plate

Also Published As

Publication number Publication date
JPH0681846A (en) 1994-03-22
GB9313853D0 (en) 1993-08-18
DE4323278C2 (en) 2002-07-04
GB2270127B (en) 1996-10-16
DE4323278A1 (en) 1994-03-03

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Effective date: 20020705