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
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
  • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
  • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
  • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
  • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
  • B60B27/00—Hubs
• • 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
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/72—Sealings
  • F16C33/76—Sealings of ball or roller bearings
  • F16C33/768—Sealings of ball or roller bearings between relatively stationary parts, i.e. static seals
• • 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
  • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
  • F16C35/07—Fixing them on the shaft or housing with interposition of an element
  • F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race ring
• • 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
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
  • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
  • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
  • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
  • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
• • 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
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
  • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
• • 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
  • F16C2326/00—Articles relating to transporting
  • F16C2326/01—Parts of vehicles in general
  • F16C2326/02—Wheel hubs or castors
• • 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
  • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
  • F16C35/063—Fixing them on the shaft
• • 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
  • F16C43/00—Assembling bearings
  • F16C43/04—Assembling rolling-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
  • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
  • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
  • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
  • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
  • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
  • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
  • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member

Definitions

• the wheel drive axle unit according to the present invention is a so-called fourth-generation hub unit in which a constant velocity joint and a hub unit are disassembled integrally, and the drive wheel (FF vehicle) supported by an independent suspension type suspension unit.
• All front wheels front-engine front-wheel-drive vehicles
• FR vehicles front-engine rear-wheel-drive vehicles
• RR vehicles rear-engine rear-wheel-drive vehicles
• 4WD vehicles four-wheel-drive vehicles
• the wheels are rotatably supported by the suspension device and are used to rotationally drive the driving wheels.
• axle units In order to rotatably support the wheels with respect to the suspension, various types of axle units are used in which an outer ring and an inner ring are rotatably combined via rolling elements.
• the drive wheels are supported by the independent suspension type suspension, and the wheel drive axle unit for rotating the drive wheels is combined with a constant velocity joint to reduce the relative displacement between the differential gear and the drive wheels. Regardless of the steering angle given to the wheels, the rotation of the drive shaft needs to be transmitted smoothly (with constant velocity) to the above wheels.
• a so-called fourth-generation wheel drive axle unit which can be configured to be relatively small and lightweight in combination with such a constant velocity joint, has been used in the past.
• FIG. 10 shows a first example of the conventional structure described in Japanese Patent Application Laid-Open No. 7-317754.
• the outer ring 1 which is mounted on the vehicle and does not rotate while being supported by the suspension device, has an outer flange-shaped mounting portion 2 on the outer peripheral surface for supporting the suspension device, and a double-row outer ring raceway on the inner peripheral surface. I have 3, 3 each.
• a hub 6 formed by combining the first element 4 and the second element 5 is arranged on the inner diameter side of the outer ring 1.
• the first element 4 is an outer end of an outer peripheral surface (in this specification, an outer end in the width direction when assembled to a vehicle; a left end in FIG. 10).
• the second element 5 has one end (the left end in FIG. 10) as a cylindrical portion 9 for externally fixing the first element 4 and the other end (the right end in FIG. 10).
• a housing 11 serving as an outer ring of a tweeper type or bar field type constant velocity joint 10
• an inner ring raceway 8 is provided on the outer peripheral surface of the intermediate portion.
• an outer locking groove 13 and an inner locking groove 14 are formed at positions where the inner peripheral surface of the first element 4 and the outer peripheral surface of the second element 5 are aligned with each other, respectively.
• the first element 4 is prevented from falling out of the second element 5.
• a weld 17 is formed between the outer edge of the second element 5 (left end face in FIG. 10) and the inner edge of the step 16 formed on the inner surface of the first element 4. And the first and second elements 4 and 5 are connected and fixed to each other.
• a substantially cylindrical cover 18, 18, made of metal such as stainless steel plate, and rubber or other elastomer are provided between the openings at both ends of the outer ring 1 and the outer peripheral surface of the intermediate portion of the hub 6, a substantially cylindrical cover 18, 18, made of metal such as stainless steel plate, and rubber or other elastomer are provided.
• An annular seal ring 19, 19 made of first-class elastic material is provided.
• the covers 18 and 18, the seal rings 19 and 19, and the partition plate 20 are provided outside the portion where the plurality of rolling elements 12 and 12 are installed or the constant velocity joint 10 portion. The grease existing in the relevant part is prevented from leaking out, and at the same time, foreign matters such as rainwater and dust are prevented from entering the part.
• the constant velocity joint 10 includes the housing portion 11, an inner ring 21, a retainer 22, and a plurality of balls 23.
• the inner ring 21 depends on the engine It is fixed to the tip of a drive shaft (not shown) that is driven to rotate via a transmission.
• a plurality of inner engaging grooves 24 having a circular cross section when cut along a virtual plane perpendicular to the center axis of the inner ring 21 are formed. They are formed at equal intervals in the circumferential direction, and at right angles to the circumferential direction.
• a plurality of outer engaging grooves 25 also having an arc-shaped cross-sectional shape are provided at positions on the inner peripheral surface of the housing portion 11 facing the inner engaging grooves 24 in the circumferential direction. It is formed perpendicular to the direction.
• the retainer 22 has an arcuate cross section and is formed in an annular shape as a whole, and is held between the outer peripheral surface of the inner ring 21 and the inner peripheral surface of the housing portion 11.
• pockets 26 are formed at positions matching the inner and outer engagement grooves 24, 25, respectively, and the inside of each of these pockets 26 is formed. Each of them holds a total of 6 balls 23 above.
• Each of the balls 23 is rotatable along the inner and outer engagement grooves 24 and 25 while being held in the respective pockets 26.
• the outer ring 1 When assembling the wheel drive axle unit configured as described above to a vehicle, the outer ring 1 is supported on the suspension by the mounting portion 2, and the drive wheel is fixed to the first element 4 by the mounting flange 7. Further, a tip end of a drive shaft (not shown), which is rotationally driven by the engine via a transmission and a differential gear, is spline-engaged inside the inner race 21 constituting the constant velocity joint 10.
• a drive shaft (not shown), which is rotationally driven by the engine via a transmission and a differential gear, is spline-engaged inside the inner race 21 constituting the constant velocity joint 10.
• FIG. 11 shows a second example of the conventional structure described in the above-mentioned US Pat. No. 5,674,011.
• double-row outer ring raceways 3, 3 are provided on the inner peripheral surface of the outer ring 1 which is not fitted and fixed to the knuckle 27 constituting the suspension and which does not rotate during use.
• a mounting flange 7 for supporting the wheel is provided near the outer end (closer to the left end in Fig. 11) of the outer peripheral surface of the hub 6a, and a pair of mounting flanges is also provided near the inner end (closer to the right end in Fig. 11).
• Double-row inner raceways 8, 8 are provided through inner races 28, 28, respectively.
• These inner races 28, 28 are formed by crimping portions 29 formed by plastically deforming the other end of the haptic 6a so as to bend outward in the diameter direction. It is supported and fixed to the main body.
• a plurality of rolling elements 12 and 12 are provided between the outer raceways 3 and 3 and the inner raceways 8 and 8 and the hub 6 a is provided inside the outer race 1. Is rotatably supported.
• a spline hole 30 is provided in the center of the hub 6a. Further, the hub 6a and the drive shaft member 31 are combined to form a wheel drive axle unit. One end of the drive shaft member 31 is provided with a spline shaft 32 that engages with the spline hole 30. Further, the other end of the drive shaft member 31 is a housing portion 11 which becomes an outer ring of a constant velocity joint. Such a drive shaft member 31 and the hub 6a are combined with a state in which the spline shaft 32 is inserted into the spline hole 30, and an elastic material which is unevenly engaged with the two members 31 and 6a. Separation is prevented by the coupling member 33 made of aluminum.
• the transmission of the rotational force between the first and second elements 4 and 5 constituting the hub 6 is as follows.
• this welding 17 is a full circumference build-up welding
• the shape of the inner ring raceway 8 formed on the outer peripheral surface of the first element 4 is distorted due to the heat during welding, and the hardness of the inner ring raceway 8 is hardened. And the durability of the rolling bearing unit including the inner raceway 8 cannot be sufficiently ensured.
• Japanese Patent Application No. Hei 11-21624 describes, for example, a wheel drive axle unit having a structure as shown in FIG.
• the inner engagement defined in the claims is provided over the entire outer peripheral surface of the spline shaft 32 constituting the drive shaft member 31 near the outer end.
• An inner locking groove 14 corresponding to the portion is formed.
• a position corresponding to the inner engaging groove 14 on the inner peripheral surface of the intermediate portion near the outer end of the spline hole 30 provided at the center of the haptic 6a corresponds to the outer engaging portion described in the claims.
• the locking step 48 is formed over the entire circumference.
• a snap ring 35 formed between the inner locking groove 14 and the locking step portion 48 by forming an elastic metal wire such as spring steel or stainless steel spring into a substantially C-shaped cutout annular shape. Is hanging over.
• the end face of the caulking portion 29 for fixing the pair of inner rings 28, 28 to the hub 6a is brought into contact with the outer end surface of the housing portion 11 constituting the drive shaft member 31. Or close together.
• the O-ring 37 held in the holding groove 36 formed on the outer end face of the housing part 11 is elastically brought into contact with the end face of the caulking part 29, and the end face of the caulking part 29 is A seal is formed between the outer end surface of the housing 11 and the spline engagement portion between the spline hole 30 and the spline shaft 32, or foreign matter such as rainwater or dust enters the spline engagement portion.
• Lubricant such as grease injected into the part is prevented from leaking to the outside.
• the end surface of the caulking portion 29 facing the outer end surface of the housing portion 11 remains curved as the caulking portion 29 is formed.
• the cross-section had an arc-shaped convex surface. For this reason, the contact area between the end face of the caulking portion 29 and the outer end face of the housing portion 11 or the O-ring 37 is reduced, and as a result, the following problem occurs.
• the width of the annular contact portion (in the diametrical direction) becomes narrow, and it becomes difficult to secure the sealing performance.
• the caulking portion 29 is made to face a flat sealing material such as a sheet, the portion opposing the caulking portion 29, the surface pressure acting on the sealing material is excessive, and It tends to be uneven.
• the swaged portion 29 is simply designed to fix the inner rings 28, 28 to the hub 6a. No consideration is given to restricting the axial dimension in order to properly set the material interference. For this reason, it is difficult to ensure the durability of the sealing material and the sealing performance of the sealing material.
• the wheel drive axle unit of the present invention was invented in view of such circumstances. Disclosure of the invention
• the wheel drive axle unit of the present invention has an outer ring raceway on the inner peripheral surface, which does not rotate during use, and an outer end of the outer peripheral surface, similarly to the conventionally known wheel drive bearing unit described above.
• a mounting flange for supporting the wheel is provided on the near side, a first inner ring raceway is also provided on the middle part directly or via the inner ring, a second inner ring raceway is also provided on the inner end side, and a spline hole is provided on the center.
• a drive shaft member having a spline shaft engaging with the spline hole at an outer end thereof, and a drive shaft member having an inner end serving as a housing part serving as an outer ring of a constant velocity joint;
• a plurality of rolling elements provided rotatably between the inner raceway and the inner raceway.
• an inner engaging portion formed over the entire outer peripheral surface of the spline shaft, and the inside of the hub at a position aligned with the inner engaging portion.
• An outer engaging portion formed over the entire peripheral surface and a stopper formed of an elastic material And a ring.
• the retaining ring is bridged between the inner engaging portion and the outer engaging portion to prevent the spline shaft from coming out of the spline hole.
• the inner race having the second inner raceway formed on the outer peripheral surface thereof is formed by caulking a portion protruding from the inner end surface of the inner race at the inner end of the hapto outward in the diameter direction. By holding down the inner end surface, the hub is fixed to the hub. Further, a flat surface parallel to the outer end surface is formed in a portion of the caulking portion facing the outer end surface of the housing portion, and these flat surfaces and the outer end surface are directly or sealed. Butts through.
• the contact area between the end surface of the caulked portion and the outer end surface of the housing portion or the sealing material can be increased. Therefore, it is possible to prevent the hub from being largely displaced in the axial direction with respect to the drive shaft member as the vehicle travels, thereby preventing generation of unpleasant noise and vibration.
• the contact area between the caulked portion and the seal material can be ensured, and the sealing property of the seal material and the durability of the seal material can be ensured.
• the axial dimension can be regulated to make the interference of the sealing material appropriate.
• FIG. 1 is a half sectional view showing a first example of an embodiment of the present invention.
• FIG. 2 and (A) are enlarged views of part a of FIG. 1, and (B) is a view similar to (A) showing a structure different from that of the present invention for comparison.
• FIG. 3 is a half sectional view showing a second example of the embodiment of the present invention.
• FIG. 5 is a half sectional view showing a third example of the embodiment of the present invention.
• FIG. 6 and (A) are enlarged views of part c in FIG. 5, and (B) is a view similar to (A) showing a structure different from that of the present invention for comparison.
• FIG. 7 is a view similar to FIG. 6, illustrating a fourth example of the embodiment of the present invention.
• FIG. 8 is a half sectional view showing the fifth example.
• FIG. 9 is a sectional view showing the sixth example.
• FIG. 10 is a partial cross-sectional view showing a first example of a conventional structure.
• FIG. 11 is a half sectional view showing the second example.
• FIG. 12 is a half sectional view showing an example of the structure of the invention.
• 1 is an outer ring
• 2 is a mounting part
• 3 is an outer ring raceway
• 4 is a 1st element
• 5 is a 2nd element
• 6, 6a, 6b is a hap
• 7 is a mounting flange
• 8 is Inner ring raceway
• 9, cylindrical part, 10 is constant velocity joint
• 11 is housing part
• 12 is rolling element
• 13 is outer locking groove
• 14 is inner locking groove
• 15 is retaining ring
• 15 16 is a step
• 17 is a weld
• 18 is a force bar
• 19 is a seal ring
• 20 is a diaphragm
• 21 is an inner ring
• 22 is a cage
• 23 is a ball
• 24 is an inside.
• Engagement groove, 25 is outer engagement groove
• 26 is pocket
• 27 is knuckle
• 28 is the inner ring
• 29 and 29 a are the caulked parts
• 3 ⁇ is the spline hole
• 31 is the drive shaft member
• 3 2 is a spline shaft
• 33 is a coupling member
• 35 and 35 a are retaining rings
• 36 is a retaining groove
• 37 is a 0 ring
• 38 is a flat surface
• 39 is a flat end surface
• 40 is an encoder.
• 41 is a core
• 42 is a cylinder
• 43 is a through hole
• 44 is a sensor
• 45 is a ring
• 46, 46a is an elastic plate
• 47 is a seal lip
• 48 Is a locking step
• 49 is a step surface
• 50 is an inclined surface
• 51 is a shoulder
• 52 is a seal ring
• 53 is a seal lip.
• FIGS. 1-2 show a first example of an embodiment of the present invention.
• the features of this example are the swaged portion 29a provided at the inner end of the hub 6a and the outer end surface of the housing 11 constituting the drive shaft member 31 (left end surface in FIGS. 1-2). The point is to secure the contact area with and prevent rattling at this contact portion.
• the basic structure of the wheel drive axle unit is the same as that of the second example of the conventional structure shown in FIG.
• the structure for preventing separation from 1 is the same as the structure of the prior invention shown in FIG. Therefore, the same reference numerals are given to the same parts as those of the above-described conventional structure and the structure of the previous invention, and the overlapping description will be omitted.
• the end face of the caulked portion 29 a is present in a direction perpendicular to the center axis of the hub 6 a.
• a flat surface 38 is formed. After forming the caulked portion 29 whose end face is convexly curved as shown in FIG. 12 or FIG. 2 (B), the flat surface 38 is pressed against the end face of the caulked portion 29. It is formed by processing or cutting. Then, with the wheel drive axle unit assembled, the flat surface 38 directly abuts the outer end surface 39 of the housing portion 11.
• the contact area between the flat surface 38 provided on the end surface of the caulking portion 29 a and the outer end surface 39 of the housing portion 11 is reduced.
• the contact pressure between these two surfaces 38 and 39 can be reduced. Therefore, even when a thrust load is applied between the hub 6a and the drive shaft member 31 as the vehicle travels, the respective surfaces 38, 39 become slack (recessed due to plastic deformation). Can be prevented. That is, in the case of the structure of the prior invention shown in FIG. 12 described above, as shown in FIG. 2 (B), the end face of the caulking portion 29 was convexly curved.
• the contact area between the outer end surface 39 of the housing portion 11 and the outer end surface 39 was small, and both surfaces were easily set, whereas in the structure of this example, the above both surfaces 38, 39 were as shown in Fig. 2 (A).
• the contact between the two surfaces 38, 39 can be prevented because of the large contact area.
• the hub 6a is prevented from being displaced in the axial direction with respect to the drive shaft member 31, and unpleasant noise and vibration can be prevented from being generated.
• the length L in the radial direction of the flat surface 38 of the caulking portion 29a shown in FIG. 2A is 1 to 4 mm, preferably about 2.5 to 3.5 thighs.
• At least a portion of the flat surface 38 closer to the outer diameter is present on a radially outer side of the diameter D 2 of the radial edge.
• FIGS. 3 and 4 show a second example of the embodiment of the present invention.
• the center of the hub 6a is directly connected to the end face of the caulking portion 29a provided at the inner end of the hub 6a. It forms a flat surface 38 existing in the intersecting direction.
• the O-ring 37 held in the holding groove 36 formed on the outer end surface of the housing portion 11 is elastically brought into contact with the flat surface 38. In this state, the O-ring 37 is elastically compressed and comes into contact with the flat surface 38 over a large area as shown in FIG. 4 (A). For this reason, the seal width (radial dimension of the contact portion) by the O-ring 37 is widened, and sufficient sealing performance can be ensured.
• FIGS. 5 and 6 show a third example of the embodiment of the present invention.
• a cored bar 41 having an encoder unit 40 is externally fitted and fixed to the outer end of the housing unit 11 so that the rotation speed of the drive shaft member 31 can be detected.
• the core metal 41 is formed by bending a corrosion-resistant magnetic metal plate such as a stainless steel plate such as SUS430, etc., so as to have an L-shaped cross section as a whole.
• Such a cored bar 41 is fixed to the drive shaft member 31 by tightly fitting a cylindrical portion 42 formed on the outer peripheral edge of the core bar 41 to an outer end of the housing portion 11. I have.
• the cylindrical portion 42 has a large number of slit-shaped through holes 43 which are long in the axial direction (left and right directions in FIGS. 5 and 6) at equal intervals in the circumferential direction. Therefore, the magnetic characteristics of the outer peripheral surface of the cylindrical portion 42 change alternately at regular intervals in the circumferential direction.
• the encoder section 40 which is the outer peripheral surface of the cylindrical section 42, has the detection section of the sensor 44 supported by a fixed portion such as a suspension device closely opposed thereto, and rotates in synchronization with the wheels. The rotational speed of the drive shaft member 31 can be detected.
• annular portion 45 of the cored bar 41 is in contact with the outer end surface 39 of the housing 11. Then, it is attached to the outer surface of the circular ring portion 45 by bonding, baking, or the like.
• annular elastic plate 46 as a seal member is provided together with the annular portion 45 on the outer end surface 39 of the housing portion 11 and the inner end portion of the haptic 6a, and the swaging portion 29a is provided. In a state where it is elastically compressed between the flat surface 38 formed on the end face of the slab, it is sandwiched as shown in FIG. 6 (A).
• the surface pressure acting on the elastic plate 46 is kept within an appropriate range, but almost completely. Can be uniform. For this reason, it is easy to ensure the durability of the elastic plate 46 and the sealing performance of the elastic plate 46. That is, as shown in FIG. 6 (B), when the end face of the caulked portion 29 is convexly curved, the radial dimension of the contact portion between the end face of the caulked portion 29 and the elastic plate 46 is obtained. Although the seal width is reduced, it is difficult to ensure the durability of the elastic plate 46 and the sealing performance of the elastic plate 46. In the case of this example, however, the seal width is increased, The durability of the elastic plate 46 and the sealing performance of the elastic plate 46 can be ensured.
• FIG. 7A shows a fourth example of the embodiment of the present invention.
• a seal lip 47 that is relatively thin, has low rigidity, and is easy to bend is provided on the outer peripheral edge of the elastic plate 46a. Then, the leading edge of the seal lip 47 is brought into contact with the outer periphery of the end surface of the caulking portion 29 a over the entire circumference, and the ring portion 45 of the mandrel 41 and the caulking portion 29 a are joined together. The space between them is sealed.
• the flat surface 38 is formed on the end face of the caulked portion 29a, the caulked portion 29 having no flat surface as shown in FIG. Compared with the structure, the durability of the elastic plate 46a and the sealing performance of the seal plate 46a can be secured.
• FIG. 8 shows a fifth example of the embodiment of the present invention.
• a retaining ring 35a is bridged between the inner locking groove 14 as the inner engaging portion and the step surface 49 as the outer engaging portion.
• the retaining ring 35a has a partially annular shape, has elasticity in a direction to reduce a diameter dimension, and is inclined in a direction in which a cross-sectional shape of a half portion on an inner diameter side becomes thinner toward an inner peripheral edge. , And have a wedge shape (triangle). Therefore, this retaining ring 3
• the contact portion between the inclined surface 50 formed on the outer surface of 5a and the axial outer edge of the inner locking groove 14 is formed on the inclined surface 5 based on the elasticity of the retaining ring 35a.
• a vertical force acts on zero. For this reason, a component force directed inward in the axial direction is applied to the hub 6a. This result As a result, the inner end surface of the caulking portion 29a is pressed against the outer end surface of the housing portion 11 constituting the drive shaft member 31.
• the retaining ring 35 a is reduced in diameter by widening the gap between the axial outer end edge of the inner locking groove 14 and the step surface 49 by its own elasticity, and the caulking portion 29 a Press the inner end face of the housing against the outer end face of the housing portion 11.
• the spline hole 30 provided in the center of the haptic 6a and the spline shaft 32 constituting the drive shaft member 31 are formed. It is possible to prevent the spline engaging portion from being displaced in the axial direction, and to prevent the spline engaging portion from being worn.
• the outside formed on the inner peripheral surface of the housing part 11 of the constant velocity joint is moved as far as possible toward the outer end, and the cross-sectional thickness T at the base of the spline shaft 32 shown in the figure is set to the minimum necessary size.c.
• the structure where the retaining ring 35a is fixed to 6a is different from the structure where the nut is fastened and fixed.Since a large shear stress is not generated at the root of the spline shaft 32, it is better than that of the nut fastening structure.
• the thickness of the cross section can be reduced.
• the value of T is set to about 2 to 7 wakefulness to realize a reduction in steering moment and weight. If the ratio (T / D) between the value of T and the outer diameter D of the root of the spline shaft 32 is about 0.09 to 0.3, the spline shaft 32 The strength is balanced with the base of the base, resulting in an optimal design without wasted meat.
• the bottom of the hole of the housing part 11 is protruded axially toward the outer end by 5 from the outer end face of the housing part 11, thereby realizing the weight reduction of the unit.
• FIG. 9 shows a sixth example of the embodiment of the present invention.
• the width of the male spline teeth formed on the outer peripheral surface of the spline shaft 32 in the circumferential direction is gradually increased toward the inner side in the axial direction (to the right in FIG. 9). It is changing.
• the width dimension in the circumferential direction of the female spline teeth formed on the inner peripheral surface of the spline hole 30 provided in the center of the hub 6b is directed outward in the axial direction (to the left in FIG. 9). It is changed so that it gradually becomes larger.
• Male and female spline teeth on circumferential side The inclination angles of the planes match each other.
• the retaining ring 35 is stretched between the inner locking groove 14 and the outer locking groove 13 so that the shafts of the male and female splines are connected to each other.
• the relative position in the direction is fixed.
• the outer engaging portion formed on the inner peripheral surface of the hub 6b cannot uniquely restrict the axial position of the retaining ring 35 as in the above-described respective examples (the retaining ring cannot be fixed in the axial direction).
• a concave groove-shaped outer locking groove 14 is provided, which can uniquely regulate the axial position of the retaining ring 35.
• a seal ring 52 is externally fitted to an outer peripheral surface of a shoulder portion 51 formed at a base end of a housing portion 11 serving as an outer ring of the constant velocity joint, and a seal loop 53 of the seal ring 52 is formed. Is brought into contact with a flat surface 38 formed on the inner end face of the caulking portion 29a, thereby closing a gap between the caulking portion 29a and the housing portion 11 described above.
• the radius of the seal rip 53 of the seal ring 52 is set to an appropriate value (for example, 0 (Approximately 2 to 1.2 mm).
• the present invention Since the present invention is constructed and operates as described above, the present invention realizes a wheel drive axle unit which is small and lightweight, and has excellent durability and reliability. Can be improved. In addition, it is possible to prevent the components from rattling during operation for a long period of time, and when a seal material is incorporated. Can secure the sealing property and durability of this sealing material. As a result, noise, vibration, and fretting wear are prevented from occurring, improving the comfort of the vehicle incorporating the wheel drive axle unit, and further improving the durability of the wheel drive axle unit itself. Can be achieved.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Rolling Contact Bearings (AREA)
• Mounting Of Bearings Or Others (AREA)

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• 2000
  • 2000-11-27 JP JP2000359075A patent/JP2001347805A/ja not_active Withdrawn
• 2001
  • 2001-04-03 WO PCT/JP2001/002891 patent/WO2001076891A1/ja not_active Ceased
  • 2001-04-03 AU AU2001248740A patent/AU2001248740A1/en not_active Abandoned
  • 2001-04-03 US US10/240,857 patent/US7118182B2/en not_active Expired - Lifetime

Patent Citations (7)

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