WO2008047472A1 - Dispositif de palier pour roue - Google Patents

Dispositif de palier pour roue Download PDF

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Publication number
WO2008047472A1
WO2008047472A1 PCT/JP2007/001121 JP2007001121W WO2008047472A1 WO 2008047472 A1 WO2008047472 A1 WO 2008047472A1 JP 2007001121 W JP2007001121 W JP 2007001121W WO 2008047472 A1 WO2008047472 A1 WO 2008047472A1
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WO
WIPO (PCT)
Prior art keywords
row
wheel
bearing device
rolling
wheel bearing
Prior art date
Application number
PCT/JP2007/001121
Other languages
English (en)
Japanese (ja)
Inventor
Takayuki Norimatsu
Original Assignee
Ntn Corporation
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from JP2006282761A external-priority patent/JP2008101651A/ja
Priority claimed from JP2006282760A external-priority patent/JP2008101650A/ja
Application filed by Ntn Corporation filed Critical Ntn Corporation
Publication of WO2008047472A1 publication Critical patent/WO2008047472A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/49—Bearings with both balls and rollers
    • F16C19/492—Bearings with both balls and rollers with two or more rows with angular contact
    • F16C19/495—Bearings with both balls and rollers with two or more rows with angular contact with two rows
    • F16C19/497—Bearings with both balls and rollers with two or more rows with angular contact with two rows 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • 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

Definitions

  • the present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like, and more particularly to a wheel bearing device that is reduced in weight and increased in rigidity.
  • wheel bearing devices for supporting wheels of automobiles and the like support a hub wheel for mounting a wheel rotatably via a rolling bearing, and there are a drive wheel and a driven wheel.
  • the inner ring rotation method is generally used for driving wheels, and both the inner ring rotation method and outer ring rotation method are used for driven wheels.
  • a double-row angular contact ball bearing that has a desired bearing rigidity, exhibits durability against misalignment, and has a low rotational torque from the viewpoint of improving fuel efficiency is often used.
  • double row tapered roller bearings are used in vehicles with heavy vehicle body weight such as off-road force and trucks.
  • the wheel bearing device has a structure called a first generation in which a wheel bearing composed of a double-row anguilla ball bearing or the like is fitted between a knuckle and a hub wheel constituting a suspension device.
  • Second generation structure with body mounting flange or wheel mounting flange formed directly on the outer periphery of the outer member, or third generation structure with one inner raceway formed directly on the outer periphery of the hub wheel, or hub It is roughly divided into the 4th generation structure in which the inner rolling surface is directly formed on the outer circumference of the outer joint member of the wheel and constant velocity universal joint.
  • the wheel bearing device shown in Fig. 17 has a lightweight fourth-generation structure that is compact and has a hub wheel 50, a double row rolling bearing 51, and a constant velocity universal joint 52. It is configured as a unit.
  • the double row rolling bearing 51 includes an outer member 53, an inner member 54, and a plurality of poles 55 and tapered rollers 56 accommodated between the two members.
  • the side closer to the outside of the vehicle in the state assembled to the vehicle is the outer side (left side of the drawing), and the side closer to the center is the inner side (right side of the drawing). Side).
  • the outer member 53 is integrally provided with a vehicle body mounting flange 53c attached to a knuckle constituting a suspension device (not shown) on the outer periphery, and a double row outer rolling surface 53a on the inner periphery. 5 3 b is formed.
  • the diameter of the outer rolling surface 53a on the outer side is set to be smaller than the diameter of the outer rolling surface 53b on the inner side.
  • the inner member 5 4 includes a hub wheel 50, an outer joint member 5 8, which will be described later, integrally formed with the hub wheel 50, and a separate inner ring 5 press-fitted into the outer joint member 5 8. 7 and.
  • the hub wheel 50 has integrally a wheel mounting flange 50b for mounting a wheel (not shown) at one end, and double row outer rolling surfaces 5 3a, 5 3 on the outer periphery.
  • the inner side rolling surface 50 0a opposite to the outer side outer rolling surface 5 3 a is directly formed, and the outer race of the inner ring 5 7 has double row outer rolling surfaces 5 3 a, 5 3
  • An inner rolling surface 5 7 a opposite to the outer rolling surface 5 3 b on the inner side of b is formed.
  • the constant velocity universal joint 52 has an outer joint member 58 comprising a cup-shaped mouth portion 59 and a shoulder portion 60 forming the bottom of the mouth portion 59.
  • the outer joint member A curved track groove 5 8 a is formed on the inner periphery of 58.
  • the inner ring 5 7 is press-fitted into the outer diameter of the mouse part 59 and is fixed in the axial direction by a retaining ring 61.
  • Such a wheel bearing device has a structure in which the inner ring 5 7 is fixed to the mouse part 59 of the outer joint member 58, so that it is certainly compact in the axial direction.
  • the outer diameter itself of the outer member 53 is increased, which not only hinders weight reduction, but is also undesirable due to a design change of peripheral parts such as a knuckle.
  • a wheel bearing device as shown in Fig. 18 is known as a solution to these problems.
  • This wheel bearing device has a vehicle body mounting flange 6 2 c integrally attached to a knuckle (not shown) on the outer periphery, and a double row outer rolling surface 6 2 a on the inner periphery. 6 2 b
  • the outer member 6 2 is formed on one end and the wheel mounting flange 6 3 for attaching the wheel (not shown) at one end is integrated into the outer periphery.
  • Inner rolling surface 6 4 a opposite to the outer rolling surface 6 4 a and small diameter step portion 6 4 b extending axially from this inner rolling surface 6 4 a Is formed on the hub wheel 6 4 formed with the outer ring 6 and the small-diameter step portion 6 4 b of the hub wheel 6 4.
  • An inner member 6 6 composed of an inner ring 6 5 formed with an inner rolling surface 6 5 a facing the running surface 6 2 b, and double-row poles 6 7, 6 accommodated between these rolling surfaces 8 and these double-row poles 6 7 and 6 8 It is composed of double-row anguillar ball bearings with cages 69, 70 that can be moved freely.
  • the inner ring 65 is fixed in the axial direction by a caulking portion 6 4 c formed by plastic deformation of the small-diameter stepped portion 6 4 b of the hub wheel 6 4 radially outward.
  • the seals 7 1 and 7 2 are attached to the opening of the annular space formed between the outer member 62 and the inner member 66, and leakage of the lubricating grease sealed inside the bearing Prevents rainwater and dust from entering the bearing.
  • the pitch circle diameter D1 of the pole 67 on the one side of the counter is set to be larger than the pitch circle diameter D2 of the pole 68 on the side of the inner side.
  • the inner raceway surface 6 4 a of the hub wheel 6 4 has a larger diameter than the inner raceway surface 65 5 a of the inner race 65
  • the outer raceway surface on the outer side of the outer member 62 is also adjusted 6 2 a has a larger diameter than the outer rolling surface 6 2 b on the inner side.
  • the outer side pole 6 7 is accommodated more than the inner side pole 6 8. In this way, by setting each pitch circle diameter D 1 and D 2 to D 1> D 2, the vehicle is stationary. In addition to improving the rigidity even during turning, it is possible to extend the life of the wheel bearing device (for example, see Patent Document 2).
  • Patent Document 1 Japanese Patent Laid-Open No. 1-9-9 30 8
  • Patent Document 2 Japanese Patent Laid-Open No. 2 0 0 4 _ 1 0 8 4 4 9
  • the pitch circle diameter D1 of the outer-side pole 6 7 rows is set larger than the pitch circle diameter D2 of the inner-side pole 68 rows, Accordingly, the inner raceway surface 6 4 a of the hub wheel 6 4 has a larger diameter than the inner raceway surface 6 5 a of the inner race 65.
  • the rigidity of the bearing row on the one side of the tower can be improved while avoiding an increase in the size of the device, and the service life of the wheel bearing device can be extended.
  • the load applied to each bearing row on the inner _ side and the outer side is different from each other, and the load applied to the bearing row on the inner side is generally larger than the load applied to the bearing row on the outer side. is there.
  • the basic load rating of the inner side bearing row becomes smaller than the basic load rating of the outer side bearing row, resulting in a short life.
  • the present invention has been made in view of such circumstances, and simultaneously solves the conflicting problems of light weight and compactness and high rigidity of the device, and at the same time, has improved strength and durability.
  • An object of the present invention is to provide a bearing device for a vehicle.
  • the present invention includes an outer member integrally having a vehicle body mounting flange to be attached to a knuckle on the outer periphery, and a double row outer rolling surface formed on the inner periphery.
  • a hub wheel having a wheel mounting flange for mounting a wheel at one end is integrally formed, a hub wheel having a small-diameter step portion formed on the outer periphery, and press-fitted into the small-diameter step portion of the hub wheel, and the double row outer rolling on the outer periphery.
  • An inner member composed of at least one inner ring formed with an inner rolling surface facing the surface, and a double row accommodated in a freely rolling manner between both rolling surfaces of the inner member and the outer member.
  • one of the double row rolling element rows is constituted by a pole, and the other.
  • the number of poles in the pole row is set to be larger than the number of rollers in the tapered roller row.
  • the row is composed of poles
  • the other rolling element row is composed of tapered rollers
  • the number of poles in the pole row is set larger than the number of rollers in the tapered roller row, so that the rotational torque of the bearing is increased. It is possible to solve the conflicting issues of compactness and high rigidity at the same time.
  • the pitch circle diameter of the outer rolling element row of the double row rolling element rows is set larger than the pitch circle diameter of the inner rolling element row. May be. Claim 2
  • the pitch circle diameter of the inner one rolling element row of the double row rolling element rows is set larger than the pitch circle diameter of the outer rolling element row. May be. Claim 3
  • an outer-side inner rolling surface is formed directly on the outer periphery of the hub wheel, and the small-diameter step portion extending in the axial direction from the inner-rolling surface is formed. If the inner ring on the inner side is press-fitted into the small diameter step portion through a predetermined shim opening, the device can be made lighter and more compact. ⁇ ⁇ ⁇ Claim 5
  • the small-diameter step portion of the hub ring is connected to the Can be formed in any shape, and processability can be improved.
  • the wheel bearing device has a vehicle body mounting flange for being attached to the knuckle on the outer periphery, and an outer side in which a double row outer rolling surface is formed on the inner periphery.
  • a hub wheel having a wheel mounting flange for mounting a wheel at one end, a small-diameter step portion formed on the outer periphery, and a press fit into the small-diameter step portion of the hub wheel, and the double row on the outer periphery.
  • one of the double row rolling element rows is constituted by a pole, and the other rolling element row is constituted by a tapered roller.
  • the number of poles in the pole row is set to be larger than the number of rollers in the tapered roller row, the conflicting problems of light weight and compactness and high rigidity of the device can be solved at the same time.
  • low torque can be achieved and the inner shaft Even summer greater than the load which the load applied to the column is applied to the bearing column of the outer side can be a child life equal to or higher. Therefore, it is possible to provide a wheel bearing device that can realize a design without waste and has improved strength-durability.
  • a body mounting flange that can be attached to the knuckle on the outer periphery is integrated, an outer member with a double row outer raceway formed on the inner periphery, and a wheel mounting flange for mounting a wheel on one end.
  • a hub ring formed on the outer periphery and formed with an inner rolling surface opposed to one of the outer rolling surfaces of the double row, and a small-diameter step portion extending in an axial direction from the inner rolling surface, and the hub ring
  • An inner member comprising an inner ring that is press-fitted into a small-diameter step portion and has an inner ring surface that is opposed to the other of the outer rows of the double row on the outer periphery, and both the inner member and the outer member.
  • the inner ring is a hub ring by a crimping portion formed by plastically deforming the end of the small diameter step portion radially outward.
  • Wheel bearing device fixed in the axial direction with respect to the double row of rolling element rows
  • the pitch circle diameter of the rolling element row on the outer side is set to be larger than the pitch circle diameter of the rolling element row on the inner side
  • the rolling element row on the outer side is constituted by a pole
  • the moving body row is composed of tapered rollers, and the number of the poles is set larger than the number of the tapered rollers.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1, A wheel bearing 2 fixed to the hub wheel 1 is provided.
  • the hub wheel 1 integrally has a wheel mounting flange 3 for mounting a wheel (not shown) at one end on the outer side, and has a small diameter extending in the axial direction from the wheel mounting flange 3 via a shoulder 1a.
  • a step 1b is formed.
  • Hub ports 3 a are planted on the wheel mounting flange 3 at equal intervals in the circumferential direction.
  • the wheel bearing 2 is press-fitted into the small-diameter step portion 1b through a predetermined shimiro while being in contact with the shoulder portion 1a of the hub wheel 1, and the end portion of the small-diameter step portion 1b is It is fixed in the axial direction by a caulking portion 1 c formed by plastic deformation.
  • the hub ring 1 is formed of medium and high carbon steel containing carbon 0.40 to 0.8 O wt% such as S 53 C, and is hardened by induction hardening from the shoulder 1a to the small diameter step 1b. Has been cured to a range of 5 8 to 6 4 HRC. Note that the caulking portion 1c remains the surface hardness after forging.
  • the wheel bearing 2 is integrally provided with a vehicle body mounting flange 4c to be attached to a knuckle (not shown) constituting a suspension device on the outer periphery, and a double row outer rolling surface 4 on the inner periphery.
  • Two outer rings with outer members 4 with a and 4 b and inner rolling surfaces 5 a and 6 a facing the outer circumferential surfaces 4 a and 4 b of the double row on the outer circumference. 5, 6 and a plurality of rolling surfaces 4 a, 5 a and 4 b, 6 a are provided with a plurality of poles 9 and tapered rollers 10 accommodated in a freely rolling manner via cages 7 and 8 .
  • Seals 1 1 and 1 2 are installed in the opening of the annular space formed between the outer member 4 and the two inner rings 5 and 6, and the grease sealed inside the bearing leaks to the outside. This prevents rainwater and dust from entering the bearing from the outside.
  • Each rolling surface 4a, 5a on the outer side is formed in an arc shape that contacts the pole 9 in an annulus
  • each rolling surface 4b, 6a on the inner side is a tapered roller 1 0 It is formed in a taper shape that makes line contact.
  • the inner ring 6 on the inner side 6 has a large flange 6 b for guiding the tapered roller 10 to the large diameter side of the inner rolling surface 6 a and a small diameter for preventing the tapered roller 10 from dropping off on the small diameter side. ⁇ 6 c is formed.
  • the outer member 4 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the double row outer rolling surfaces 4 a and 4 b are induction-hardened.
  • the surface hardness is hardened in the range of 58 to 64 HRC.
  • Inner rings 5 and 6 and pole 9 and tapered roller 10 are made of high carbon chrome steel such as SU J 2 and hardened in the range of 58 to 64 HRC up to the core part by quenching.
  • the pitch circle diameter PCDo of the 9 rows of outer poles is larger than the pitch circle diameter PCDi of the 10 rows of tapered rollers on the inner side (PCDo> PCDi)
  • the 9 poles on the outer side are arranged closely spaced, and the number of poles is set to be larger than the number of tapered rollers 10 in the 10 row of inner ones.
  • the basic load rating of the inner side bearing row is larger than the basic load rating of the outer side bearing row and is applied to the inner side bearing row. Even if the load is larger than the load applied to the outer bearing row, the service life can be the same or longer. That is, it is possible to provide a wheel bearing device that can realize a design without waste and has improved strength and durability.
  • FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-described embodiment only in the configuration of the hub wheel, and other parts having the same parts or the same functions are denoted by the same reference numerals for detailed description. Omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4, the hub wheel 1 3 and the small-diameter step portion 1 3 b of the hub wheel 13. And an inner member 14 composed of an inner ring 6.
  • the hub wheel 1 3 has an outer outer rolling surface 4 a that faces the outer outer rolling surface 4 a on the outer periphery, and a small-diameter step portion 1 3 that extends in the axial direction from the inner rolling surface 1 3 a. b is formed.
  • the inner ring 6 is press-fitted into the small-diameter step portion 13 b through a predetermined shim opening and is fixed in the axial direction by the crimping portion 1 c.
  • Seals 15 and 1 2 are attached to the openings of the annular space formed between the outer member 4 and the hub ring 13 and the inner ring 6, and the grease sealed inside the bearing is exposed to the outside. It prevents leakage and rainwater and dust from entering the bearing.
  • the hub wheel 13 is made of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and the inner rolling surface from the seal land portion 3 b in which the seal 15 is in sliding contact.
  • the surface hardness is hardened to a range of 58 to 64 HRC by induction hardening over 1 3 a and small diameter step 1 3 b.
  • the pitch circle diameter PCD o of the outer pole 9 rows is larger than the pitch circle diameter PCD i of the 10 inner tapered rollers 10D, as in the above-described embodiment.
  • PCD o> PCD i the number of poles in the 9 outer rows of poles is set to be larger than the number of tapered rollers 10 in the 10 rows of inner ones.
  • FIG. 3 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically the same as the first embodiment (FIG. 1) described above except that the configuration of the wheel bearing is different, and other parts are the same or the same. Parts having functions ⁇ Parts are denoted by the same reference numerals, and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 16 fixed to the hub wheel 1.
  • the wheel bearing 16 is press-fitted into the small-diameter step portion 1b through a predetermined shim opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this manner.
  • the wheel bearing 16 has an outer member 17 integrally formed with a vehicle body mounting flange 4c on the outer periphery and formed with a plurality of outer rolling surfaces 17a and 17b on the inner periphery.
  • Two inner rings 1 8, 1 9 formed on the outer circumference with inner rolling surfaces 1 8 a, 1 9 a facing the double row outer rolling surfaces 17 a, 17 b, respectively,
  • a plurality of tapered rollers 10 and poles 9 are provided between the rolling surfaces 17 a, 18 a and 17 b, 19 a so as to be freely rollable via cages 20, 21.
  • the rolling surfaces 17a and 18a on the outer side are formed in a taper shape, and the rolling surfaces 17b and 19a on the inner side are formed in an arc shape. ing. Then, the large roller 1 8 b for setting the tapered roller 10 on the large-diameter side of the inner raceway 18 a in the inner ring 18 on the one side of the outer ring and the tapered roller 10 on the small-diameter side are dropped off. A small claw 1 8 c is formed for prevention.
  • the outer member 1 7 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double row outer rolling surfaces 1 7 a and 17 b are high frequency. Hardened by quenching to a surface hardness of 58-64 H RC. Inner rings 18 and 19 are made of high carbon chrome steel such as SU J 2 and hardened to the core by a quenching process in the range of 58 to 64 HRC.
  • the outer side tapered roller 10 row pitch circle diameter PC D o is the inner one side pole 9 row pitch circle diameter PCD i larger than the diameter (PC Do> PCD i) and the number of poles in the 9 rows of inner ones is set to be larger than the number of rollers in the 10 rows of outer tapered rollers.
  • the outer diameter D on the inner side of the outer member 17 can be set to a small diameter, and the knuckle can be kneaded without reducing the basic load rating of the inner side bearing row. The size can be reduced and the device can be made lighter and more compact.
  • the outer diameter of the inner ring 18 on the outer side is increased in response to the amount of expansion of the pitch circle diameter PCD o in the outer row of tapered rollers 10 row, so that the difference between the pitch circle diameters PCD o and PCD i Even if there is, the small-diameter step portion 1b of the hub wheel 1 can be formed into a straight shaft, and the workability can be improved.
  • FIG. 4 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention.
  • This embodiment is basically the same as the third embodiment described above (Fig. 3) except that the configuration of the wheel is different, and the other parts are the same or have the same function. Reference numerals are assigned and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called a third generation, and is an outer member.
  • the hub wheel 2 2 has an outer tapered inner rolling surface 2 2 a facing the outer outer rolling surface 17 a of the outer member 17 on the outer periphery, and the inner rolling surface 2 2 a.
  • a small-diameter step portion 2 2 b extending in the axial direction is formed.
  • a large collar 18 b for guiding the tapered roller 10 is formed on the large diameter side of the inner rolling surface 22 a on the one side of the outer.
  • the inner ring 19 is press-fitted into the small-diameter step portion 2 2 b through a predetermined shim opening and is fixed in the axial direction by the crimping portion 1 c.
  • the hub wheel 2 2 is formed of medium and high carbon steel containing carbon 0.40 to 0.80 wt% such as S 53 C, and rolls inward from the seal land portion 3 b where the seal 15 is in sliding contact.
  • the surface 22 2 a and the small diameter step 2 2 b are hardened by induction hardening in the range of 58 to 64 HRC.
  • the pitch circle diameter PCD o of the outer tapered roller 10 row is larger than the pitch circle diameter PCD i of the pole 9 row on the inner side.
  • the number of poles in the 9 rows of inner side poles is set to be greater than the number of rollers in the 10 rows of outer tapered rollers.
  • the outer diameter D on the inner side of the outer member 17 can be reduced.
  • the knuckle size can be reduced without reducing the basic load rating of the inner bearing row. Therefore, while making the device lighter and more compact, the overall bearing rigidity can be increased and the torque can be reduced.
  • the basic load rating is larger than the basic load rating of the outer bearing row. Even if the load applied to the bearing row is larger than the load applied to the outer bearing portion, the service life can be the same or longer.
  • FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the invention.
  • This embodiment is basically the same as the first embodiment described above (FIG. 1) except that the left and right rows have the same pitch circle diameter, and has the same components and the same functions as the previously described embodiments. Parts ⁇ Parts are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 24 fixed to the hub wheel 1.
  • the wheel bearing 24 has an outer member 25 having a body mounting flange 4c integrally formed on the outer periphery and double row outer rolling surfaces 4a, 25a formed on the inner periphery, and these on the outer periphery.
  • Two inner races 5, 2 6 formed with inner rolling surfaces 5a, 2 6a opposite to double row outer rolling surfaces 4a, 2 5a, and both rolling surfaces 4a, 5a and
  • a plurality of poles 9 and tapered rollers 10 are provided between 2 5 a and 2 6 a so as to be freely rollable via cages 7 and 2 7.
  • Seals 1 1 and 2 8 are installed in the opening of the annular space formed between the outer member 2 5 and the two inner rings 5 and 2 6, and the grease sealed inside the bearing is exposed to the outside. This prevents leakage and prevents rainwater and dust from entering the bearing.
  • the outer rolling surface 4a, 5a is formed in an arc shape that contacts the pole 9 in an annulus
  • the inner rolling surface 25a, 26a is a tapered roller 1 0 It is formed in a taper shape that makes line contact.
  • the inner ring 26 on the inner side 26 is provided with a large flange 6 b for guiding the tapered roller 10 to the large diameter side of the inner rolling surface 26 a, and the tapered roller 10 is prevented from falling off on the small diameter side.
  • Gavel for 6c Each is formed.
  • the outer member 25 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double-row outer rolling surfaces 4 a and 25 a are represented by induction hardening. Hardened to a surface hardness of 58 to 64 H RC.
  • the inner ring 26 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 H RC up to the core part by quenching.
  • 9 rows of poles on the outer side are arranged at close intervals, and the number of poles is set to be larger than the number of rollers in the 10 rows of tapered rollers on the inner side. Therefore, the overall bearing rigidity can be secured, and the basic load rating of the inner bearing row is larger than the basic load rating of the outer side bearing row, so that the load applied to the inner side bearing row is the outer bearing. Even if it is larger than the load applied to the row, the service life can be the same or longer. That is, it is possible to provide a wheel bearing device that can realize a design without waste and has improved strength and durability.
  • FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the present invention.
  • This embodiment basically differs from the above-described fifth embodiment (FIG. 5) only in the configuration of the hub wheel, and other parts having the same parts and the same functions as the above-described embodiments. Parts are denoted by the same reference numerals and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 25, the hub wheel 1 3 and the small diameter step portion 1 3 b of the hub wheel 13. And an inner member 29 composed of an inner ring 26.
  • the pitch circle diameter PCDo of the 9 rows of outer poles and the pitch circle diameter PCDi of the 10 rows of tapered rollers 10 on the inner side are the same as in the embodiment described above.
  • PCDo PCD i) and the outer side —
  • the number of poles in the 9th row is set to be greater than the number of tapered rollers on the 10th row of the inner one. Therefore, while making the device lighter and more compact, the overall bearing rigidity is increased, and the basic load rating is larger than the basic load rating of the outer bearing row, which is applied to the inner bearing row portion. Even if the load becomes larger than the load applied to the outer bearing section, the life can be made the same or more.
  • FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the present invention.
  • This embodiment is basically the same as the above-described third embodiment (FIG. 3) except that both the left and right rows have the same pitch circle diameter, and has the same parts and the same functions as the above-described embodiments.
  • Parts ⁇ Parts are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 and a wheel bearing 30 fixed to the hub wheel 1.
  • the wheel bearing 30 is press-fitted into the small-diameter step portion 1b through a predetermined shim opening while being abutted against the shoulder portion 1a of the hub wheel 1, and the end of the small-diameter step portion 1b is plastically deformed. It is fixed in the axial direction by a caulking portion 1 c formed in this manner.
  • the wheel bearing 30 has an outer member 3 1 integrally formed with a vehicle body mounting flange 4c on the outer periphery, and formed with a plurality of outer rolling surfaces 17a, 31a on the inner periphery.
  • Two inner rings 1 8 and 3 2 formed on the outer periphery with inner rolling surfaces 1 8 a and 3 2 a facing the double row outer rolling surfaces 1 7 a and 3 1 a, respectively,
  • a plurality of tapered rollers 10 and poles 9 which are rotatably accommodated through cages 20, 3 3 between both rolling surfaces 1 7 a, 1 8 a and 3 1 a, 3 2 a Yes.
  • Each rolling surface 17a, 18a on the outer side is formed in a taper shape, and each rolling surface 3 1a, 3 2a on the inner side is formed in an arc shape. ing. Then, the large roller 1 8 b for setting the tapered roller 10 on the large-diameter side of the inner raceway 18 a in the inner ring 18 on the one side of the outer ring and the tapered roller 10 on the small-diameter side are dropped off. A small claw 1 8 c is formed for prevention.
  • the outer member 3 1 is formed of medium-high carbon steel containing carbon 0.40-0.80 wt% such as S 5 3 C, and double row outer rolling surfaces 1 7 a, 3 1 a is hardened by induction hardening to a surface hardness in the range of 58 to 64 HRC.
  • the inner ring 3 2 is made of high carbon chrome steel such as SUJ 2 and hardened in the range of 58 to 64 HRC up to the core part by quenching.
  • the number of poles in the nine rows of inner side poles is set to be greater than the number of tapered rollers in the outer row of 10 rows.
  • FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention.
  • This embodiment basically differs from the above-described seventh embodiment (FIG. 7) only in the configuration of the hub wheel, and other parts having the same parts and the same functions as the above-described embodiments. Parts are denoted by the same reference numerals and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 3 1, the hub wheel 2 2, and the small-diameter step portion 2 2 b of the hub wheel 2 2. And an inner member 3 4 composed of the inner ring 3 2.
  • PCD o PCD i
  • FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention.
  • This embodiment is basically the same as the above-described fifth embodiment (FIG. 5) except that the pitch circle diameters of both bearing rows are the same.
  • Parts ⁇ Parts are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 and a wheel bearing 35 fixed to the hub wheel 1.
  • the wheel bearing 35 has an outer member 3 6 having a body mounting flange 4 c integrally formed on the outer periphery and double row outer rolling surfaces 4 a, 3 6 a formed on the inner periphery, and these on the outer periphery.
  • a plurality of poles 9 and tapered rollers 10 that are rotatably accommodated via cages 7 and 3 8 are provided between 3 6 a and 3 7 a.
  • Seals 1 1 and 3 9 are installed in the opening of the annular space formed between the outer member 3 6 and the inner rings 5 and 7, and leakage of grease sealed inside the bearing This prevents rainwater and dust from entering the bearing.
  • the outer member 3 6 is formed of medium-high carbon steel containing carbon 0.40-0.80 wt% such as S 5 3 C, and double row outer rolling surfaces 4 a, 3 6 a However, it has been hardened by induction hardening to a surface hardness of 58-64 HRC.
  • the inner ring 37 is made of high carbon chrome steel such as SUJ2, and is hardened in the range of 58 to 64 HR C to the core part by quenching.
  • the pitch circle diameter PCD i of the inner one side tapered roller 10 row is larger than the pitch circle diameter PCD o of the ninth row pole 9 row (PCD i> PCD o )
  • the number of poles in the 9 outer rows of poles is set to be greater than the number of tapered rollers in the 10 inner rows.
  • the inner ring 37 has a thicker wall and the rigidity is increased corresponding to the diameter expansion of the pitch circle diameter PCD i in the row of tapered rollers 10 on the inner side, the inner ring The hoop stress generated in 37 can be suppressed, and the durability of the inner ring 37 can be improved.
  • FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention.
  • This embodiment basically differs from the above-described ninth embodiment (FIG. 9) only in the configuration of the hub wheel, and other parts having the same parts, the same parts, and the same functions as the above-described embodiments.
  • the parts are denoted by the same reference numerals and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 36, the hub wheel 13 and the small-diameter step portion 13b of the hub wheel 13 And an inner member 40 composed of an inner ring 37.
  • the tapered roller on the inner side is the same as the above-described embodiment.
  • Pitch circle diameter PCD i is set to a larger diameter than the 9th pitch circle diameter PCD o of the outer pole (PCD i> PCD o), and the number of poles in the outer pole 9 rows is The number of tapered rollers on the inner side is set more than the number of rollers in the 10th row.
  • This increases the basic load rating of the inner-side bearing row, and makes the service life the same or longer even if the load applied to the inner-side bearing row is greater than the load applied to the outer-side bearing row.
  • the device can be made lighter and more compact.
  • the inner ring 37 on the inner side is thickened, and the oop stress generated in the inner ring 37 due to the caulking process can be suppressed, and the durability of the inner ring 37 can be improved.
  • FIG. 11 is a longitudinal sectional view showing a first embodiment of the wheel bearing device according to the present invention. This embodiment is the same as the ninth embodiment (FIG. 9) described above. In fact, the configuration of the hub wheel and the wheel bearing is only partially different, and other parts that have the same parts or the same functions as the above-described embodiment .
  • This wheel bearing device is for a driven wheel referred to as a second generation, and includes a hub wheel 1 'and a wheel bearing 35' fixed to the hub wheel 1 '.
  • the wheel bearing 35 ' has a body mounting flange 4c integrally formed on the outer periphery, an outer member 36 having double rows of outer rolling surfaces 4a and 36a formed on the inner periphery, and these double rows on the outer periphery.
  • Two inner rings 5 'and 37' formed with inner rolling surfaces 5a and 37a opposite to the outer rolling surfaces 4a and 36a, and both rolling surfaces 4a, 5a and 36a,
  • a plurality of poles 9 and tapered rollers 10 accommodated in a freely rolling manner via cages 7 and 38 are provided between 37a.
  • the outer diameter of the small-diameter step portion 1 b ′ is larger than that of the hub wheel 1 in the ninth embodiment described above.
  • the inner rings 5 'and 37' are made thinner as the small-diameter step portion 1b 'expands.
  • the diameter of the small-diameter step 1 b 'of the hub wheel 1 ′ is increased without increasing the outer diameter of the wheel bearing 35 ′, thereby reducing the weight of the device and making the hub wheel 1 ′ compact.
  • ⁇ Strength can be increased.
  • FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • This embodiment is basically the same as the above-described 10th embodiment (FIG. 10) except that the configuration of the hub ring and the inner ring is partially different, and the same parts and functions as described above are the same. Parts to have ⁇ Same parts are given the same reference numerals and detailed explanations are omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and includes an outer member 36, a hub wheel 1 3 ', and a small-diameter step portion 1 3 b' of the hub wheel 1 3 '. And an inner member 40 'composed of an inner ring 37' press-fitted into the inner ring.
  • the outer diameter of the small diameter step portion 13 b ′ is formed larger than the hub wheel 13 in the tenth embodiment described above.
  • This small diameter step 1 As the diameter of 3 'increases, the inner ring 37' becomes thinner. As a result, the diameter of the small diameter step portion 1 3 b 'of the hub wheel 1 3' is increased without increasing the outer diameter of the outer member 36, thereby reducing the weight of the device and reducing the size of the hub. Strength of wheel 1 3 ' ⁇ Rigidity can be increased.
  • FIG. 13 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • This embodiment is basically the same as the above-described seventh embodiment (FIG. 7) except that the pitch circle diameters of both bearing rows are different, and has the same parts and the same functions as the above-described embodiments. Parts ⁇ Parts are denoted by the same reference numerals and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called a second generation, and includes a hub wheel 1 and a wheel bearing 41 fixed to the hub wheel 1.
  • the wheel bearing 41 has a vehicle body mounting flange 4 c integrally formed on the outer periphery, an outer member 42 formed with double row outer rolling surfaces 17 a and 42 a on the inner periphery, and these double rows on the outer periphery.
  • Outer rolling surfaces 1 7 a, 42 a opposite inner rolling surfaces 1 8 a, 43 a formed two inner rings 1 8, 43, and both rolling surfaces 1 7 a, 1 8 a
  • a plurality of tapered rollers 10 and poles 9 which are rotatably accommodated through cages 20 and 44 between 42a and 43a.
  • the outer member 42 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S 53 C, and the double row outer rolling surfaces 1 7 a and 42 a are obtained by induction hardening. Hardened to a surface hardness of 58-64 H RC.
  • the inner ring 43 is made of high carbon chrome steel such as SU J 2 and is hardened in the range of 58 to 64 H RC up to the core part by quenching.
  • the pitch circle diameter PCD i of the nine poles on the inner side is larger than the pitch circle diameter PCDo of the outer tapered roller 10 rows (PCD i> PCDo).
  • the number of poles in the 9 rows of inner inner poles is set to be greater than the number of rollers in the 10 outer rows of tapered rollers.
  • the overall weight of the bearing is increased while making the device lighter and more compact.
  • increase the basic load rating of the inner-side bearing row so that the service life will be the same or longer even if the load applied to the inner-side bearing row is greater than the load applied to the outer-side bearing row. Can do.
  • the inner ring 4 3 on the inner side 4 3 is thickened to increase the rigidity corresponding to the amount of expansion of the pitch circle diameter PCD i in the 9 rows of poles on the inner side.
  • the hoop stress generated in the inner ring 43 can be suppressed, and the durability of the inner ring 43 can be improved.
  • FIG. 14 is a longitudinal sectional view showing a 14th embodiment of a wheel bearing device according to the present invention. Note that this embodiment is basically different from the above-mentioned first to third embodiments (Fig. 13) except that the configuration of the hub wheel is basically the same. Are denoted by the same reference numerals, and detailed description is omitted.
  • This wheel bearing device is for a driven wheel called the third generation, and is press-fitted into the outer member 4 2, the hub wheel 2 2, and the small-diameter step portion 2 2 b of the hub wheel 2 2. And an inner member 4 5 composed of the inner ring 4 3.
  • the pitch circle diameter PCD i of the nine rows of poles on the inner side is larger than the pitch circle diameter PCD o of the ten rows of tapered rollers on the one side, as in the embodiment described above.
  • the diameter (PCD i> PCD o) is set, and the number of poles in the inner row of 9 rows of poles is set to be larger than the number of rollers in the outer row of tapered rollers of 10 rows.
  • the strength, rigidity, and weight of the device can be increased without compromising the basic load rating of the bearing row on the inner side and without increasing the rotational torque of the bearing. Can do.
  • the inner ring 43 on the inner side is thicker, and the hoop stress generated in the inner ring 43 due to the caulking process can be suppressed to improve the durability.
  • FIG. 15 is a longitudinal sectional view showing a fifteenth embodiment of the wheel bearing device according to the present invention.
  • This embodiment is the same as the above-described first embodiment (FIG. 13). Basically, only the configuration of the hub wheel and wheel bearing is partially different. Other parts that have the same parts or the same function as the above-mentioned embodiment ⁇ Parts are assigned the same reference numerals and detailed description is omitted. To do.
  • This wheel bearing device is for a driven wheel called the second generation, and includes a hub wheel 1 ′ and a wheel bearing 4 1 ′ fixed to the hub wheel 1 ′.
  • the wheel bearing 4 1 ′ has a body mounting flange 4 c integrally formed on the outer periphery, an outer member 42 having double row outer rolling surfaces 17 a and 42 a formed on the inner periphery, and these on the outer periphery.
  • a plurality of poles 9 and tapered rollers 10 which are rotatably accommodated via cages 20 and 44 are provided between a, 18 a and 42 a, 43 a.
  • the outer diameter of the small-diameter step portion 1 b ′ is larger than that of the hub wheel 1 in the first to third embodiments described above. Further, the inner rings 18 ′ and 43 ′ are made thinner with the increase in diameter of the small diameter step 1b ′. As a result, the small diameter step 1 b ′ of the hub wheel 1 ′ is expanded without increasing the outer diameter of the wheel bearing 4 1 ′. The strength of the wheel 1 ' ⁇ The rigidity can be increased.
  • FIG. 16 is a longitudinal sectional view showing a sixteenth embodiment of the wheel bearing device according to the present invention. Note that this embodiment is basically the same as the above-described 14th embodiment (Fig. 14) except that the configuration of the hub ring and the inner ring is partially different. Parts having the same function ⁇ Parts are denoted by the same reference numerals and detailed description thereof is omitted.
  • This wheel bearing device is for a driven wheel called the second generation, and is press-fitted into the outer member 42, the hub wheel 22 ', and the small-diameter step portion 22b' of the hub wheel 22 '. And an inner member 45 'composed of an inner ring 43'.
  • the hub wheel 22 ' is formed such that the outer diameter of the small-diameter step portion 22b' is larger than the hub wheel 22 in the above-described 14th embodiment.
  • This small diameter step 2 As the diameter of 2 b ′ increases, the inner ring 4 3 ′ becomes thinner. As a result, the diameter of the small diameter step 2 2 b ′ of the hub wheel 2 2 ′ is increased without increasing the outer diameter of the outer member 4 2, thereby reducing the weight of the device and making it compact.
  • the strength of the hub wheel 2 2 ′ ⁇ The rigidity can be increased.
  • the wheel bearing device according to the present invention can be applied to a wheel bearing device having a second or third generation structure regardless of whether it is for a driving wheel or a driven wheel.
  • FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention.
  • FIG. 3 is a longitudinal sectional view showing a third embodiment of a wheel bearing device according to the present invention.
  • FIG. 4 is a longitudinal sectional view showing a fourth embodiment of a wheel bearing device according to the present invention.
  • FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the wheel bearing device according to the invention.
  • FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the wheel bearing device according to the invention.
  • FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the wheel bearing device according to the invention.
  • FIG. 8 is a longitudinal sectional view showing an eighth embodiment of the wheel bearing device according to the invention.
  • FIG. 9 is a longitudinal sectional view showing a ninth embodiment of the wheel bearing device according to the invention.
  • FIG. 10 is a longitudinal sectional view showing a tenth embodiment of the wheel bearing device according to the present invention.
  • FIG. 11 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • FIG. 12 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention.
  • FIG. 13 is a longitudinal sectional view showing a thirteenth embodiment of a wheel bearing device according to the present invention.
  • FIG. 14 is a longitudinal sectional view showing a 14th embodiment of a wheel bearing device according to the present invention.
  • FIG. 15 is a longitudinal sectional view showing a fifteenth embodiment of a wheel bearing device according to the present invention.
  • FIG. 16 is a longitudinal sectional view showing a sixteenth embodiment of a wheel bearing device according to the present invention.
  • FIG. 17 is a longitudinal sectional view showing a conventional wheel bearing device.
  • FIG. 18 is a longitudinal sectional view showing another conventional wheel bearing device.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un dispositif de palier pour une roue permettant de résoudre simultanément des problèmes contradictoires de réduction de poids et de taille et d'augmentation de rigidité et présentant une amélioration en termes de résistance et de durabilité. Le dispositif de palier pour une roue est une structure de troisième génération ayant des corps de roulement à deux rangées et ayant par ailleurs une bague intérieure (6) fixée en agrafant une extrémité d'une section à gradins de petit diamètre (13b) d'une bague de moyeu (13) par le biais d'une opération de rétreinte de matrice oscillante. En ce qui concerne les corps de roulement à deux rangées, la rangée de corps de roulement du côté extérieur a un diamètre du cercle primitif PCDo supérieur au diamètre du cercle primitif PCDi de la rangée de corps de roulement du côté intérieur. La rangée de corps de roulement du côté extérieur est réalisée à partir de billes (9), la rangée de corps de roulement du côté intérieur est réalisée à partir de rouleaux coniques (10), et le nombre de billes (9) est supérieur au nombre de rouleaux coniques (10). Ceci accroît la rigidité du palier, réalise un faible couple résistant en fonctionnement, et, même si une charge appliquée sur la rangée de palier du côté intérieur est supérieure à celle appliquée sur la rangée de palier du côté extérieur, maintient la durée de vie utile du dispositif de palier intacte ou même la prolonge.
PCT/JP2007/001121 2006-10-17 2007-10-16 Dispositif de palier pour roue WO2008047472A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2006282761A JP2008101651A (ja) 2006-10-17 2006-10-17 車輪用軸受装置
JP2006-282761 2006-10-17
JP2006-282760 2006-10-17
JP2006282760A JP2008101650A (ja) 2006-10-17 2006-10-17 車輪用軸受装置

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014109331A1 (fr) * 2013-01-09 2014-07-17 Ntn株式会社 Dispositif de palier pour roue

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004090732A (ja) * 2002-08-30 2004-03-25 Ntn Corp 駆動車輪用軸受装置
JP2004108449A (ja) * 2002-09-17 2004-04-08 Koyo Seiko Co Ltd 転がり軸受装置
JP2004345439A (ja) * 2003-05-21 2004-12-09 Honda Motor Co Ltd 車輪支持用ハブユニット
US20050111771A1 (en) * 2003-10-14 2005-05-26 Shevket Cengiz R. Asymmetric hub assembly

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004090732A (ja) * 2002-08-30 2004-03-25 Ntn Corp 駆動車輪用軸受装置
JP2004108449A (ja) * 2002-09-17 2004-04-08 Koyo Seiko Co Ltd 転がり軸受装置
JP2004345439A (ja) * 2003-05-21 2004-12-09 Honda Motor Co Ltd 車輪支持用ハブユニット
US20050111771A1 (en) * 2003-10-14 2005-05-26 Shevket Cengiz R. Asymmetric hub assembly

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014109331A1 (fr) * 2013-01-09 2014-07-17 Ntn株式会社 Dispositif de palier pour roue
JP2014134231A (ja) * 2013-01-09 2014-07-24 Ntn Corp 車輪用軸受装置
CN104903603A (zh) * 2013-01-09 2015-09-09 Ntn株式会社 车轮轴承装置

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