WO2016076027A1 - Rolling wheel for crawler type traveling vehicle - Google Patents

Rolling wheel for crawler type traveling vehicle Download PDF

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Publication number
WO2016076027A1
WO2016076027A1 PCT/JP2015/077911 JP2015077911W WO2016076027A1 WO 2016076027 A1 WO2016076027 A1 WO 2016076027A1 JP 2015077911 W JP2015077911 W JP 2015077911W WO 2016076027 A1 WO2016076027 A1 WO 2016076027A1
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WO
WIPO (PCT)
Prior art keywords
shaft
tapered roller
pressing member
collar
traveling vehicle
Prior art date
Application number
PCT/JP2015/077911
Other languages
French (fr)
Japanese (ja)
Inventor
大須賀忠男
駒井盛生
Original Assignee
太平洋精機ホールディング株式会社
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
Application filed by 太平洋精機ホールディング株式会社 filed Critical 太平洋精機ホールディング株式会社
Priority to CN201580002174.4A priority Critical patent/CN105793147A/en
Publication of WO2016076027A1 publication Critical patent/WO2016076027A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/14—Arrangement, location, or adaptation of rollers
    • B62D55/15—Mounting devices, e.g. bushings, axles, bearings, sealings

Definitions

  • the present invention relates to a wheel of a crawler type traveling vehicle.
  • Rollers used in crawler type traveling vehicles are rotated by friction with moving crawler belts (not shown).
  • the bearing means of the rolling wheels are changed from bushes to tapered roller bearings.
  • axial clearance management in the case where tapered roller bearings are incorporated into the rolling wheels is very important, and if the clearance management is not properly managed, the inherent performance of the bearings can not be exhibited, and the reliability as rolling wheels can not be achieved. There was a risk of losing sex.
  • Patent Document 1 As a method of managing the clearance in the axial direction, shim adjustment at the shaft end of the shaft of the rotating wheel (Patent Document 1), installation of a disc spring between the tapered roller bearing and the collar (Patent Document 2), tapered roller bearing There has been an installation of a regulating member between the two (Patent Document 3) and the like.
  • FIG. 6 shows FIG. 4 of Patent Document 2, but between the tapered roller bearing 4 and the collar 7 A disc spring 28 is mounted. If the spring constant of the disc spring 28 is reduced, excessive preload on the tapered roller bearings can be prevented during assembly, but the rollers are attached to the vehicle body, and from the outside when actually used The large axial load causes the disc spring 28 to be largely bent, and the axial gap of the tapered roller bearing on the opposite side of the loaded tapered roller bearing is increased.
  • the present invention has been made to solve the above-mentioned drawback of the difficulty in managing the axial clearance of the conventional tapered roller bearing, and the purpose thereof is to use the tapered roller bearing for the rotating wheel corresponding to high speed traveling. Moreover, it is an object of the present invention to provide a wheel of a crawler type traveling vehicle which is easy to assemble and is excellent in durability and reliability.
  • the turning wheels of the crawler type traveling vehicle are rolling wheels that constitute a part of the crawler type traveling vehicle, and include a roller, a shaft, sealing means installed at both ends, and a collar
  • a structure including a pair of tapered roller bearings including the left and right disposed bearing means externally fitted to the shaft, the tapered roller bearing and the sealing means being mounted, the axial direction of the tapered roller bearing
  • a preloading means for adjusting the gap is installed at the shaft end of the shaft, and the preloading means applies a preload by pressing the collar in the direction of the inner race end face of the tapered roller bearing by the force of deflection of the pressing member. It is characterized by being a structure.
  • the tapered roller bearing is provided with a necessary sufficient and not excessive preload without using a shim, it is possible to simplify the assembly simultaneously The axial clearance management of the roller bearings can be properly realized, and high-quality rolling wheels can be obtained.
  • the roller of the crawler belt traveling vehicle is a pressing member in which the preloading means presses the collar in the central direction of the shaft, and a fixing member for pressing the pressing member against the shaft end of the shaft And the pressing member is pressed against the shaft end of the shaft in a structure in which the collar is pushed in the central direction of the shaft by a force due to the pressing member bending, and a preload is applied to the tapered roller bearing. It is characterized in that the stress due to the deflection of the pressing member reaches the yield stress or the proof stress in the vicinity where the necessary preload is generated.
  • the same effect as the roller of the crawler type traveling vehicle according to the first aspect of the present invention can be achieved. Even if the pressing member is caused to yield and the pressing member is further pressed after a predetermined preload pressure is released, the change in the preload pressure can be reduced. This prevents the occurrence of excessive preload, thereby facilitating assembly and at the same time improving assembly quality. In addition, when reassembling in after service, it is possible to reuse by surrendering in the reverse direction by reversing and using the above-mentioned pressing member that has yielded at the time of assembly.
  • the rolling wheels of the crawler type traveling vehicle are a pressing member in which the preloading means presses the collar in the central direction of the shaft, and a fixing member for pressing the pressing member against the shaft end of the shaft
  • the pressing member pushes the collar toward the center of the shaft by the force of the pressing member to bend, thereby applying a pre-load to the tapered roller bearing
  • the pressing member is a disc spring-like hollow disc It is characterized in that the stress due to the bending at the time of bending is within the elastic limit.
  • the same effect as the wheel of the crawler type traveling vehicle according to the first aspect of the present invention can be achieved. Since the spring constant of the pressing member can be weakened even after a heavy preload is applied, the rate of increase in preload can be kept low, excessive preload can be prevented, and assembly becomes easy as well. improves.
  • the wheel of the crawler type traveling vehicle comprises installing means for preventing deviation between the collar and the shaft on the collar on the side where the preloading means is installed. It is characterized.
  • the means for preventing the shift between the collar and the shaft is installed, so the wheel is attached to the vehicle body,
  • the above-mentioned shaft acts as a reinforcement for the vehicle body and contributes to the prevention of lateral deformation of the wheel mounting portion of the vehicle body even when the lateral rigidity of the mounting portion of the vehicle body is weak, The durability of rolling wheels can be secured.
  • roller according to the present invention will be described in detail with reference to the drawings.
  • the rolling wheels of the crawler type traveling vehicle of the present invention are not limited to the preferred embodiments of the present invention specifically described below.
  • FIG. 1 is a schematic cross-sectional view of a rotating wheel of a crawler type traveling vehicle according to a first embodiment of the present invention.
  • the wheel of the crawler type traveling vehicle according to the first embodiment of the present invention is used, for example, as a wheel of a crawler type traveling vehicle in a construction machine such as a bulldozer or an agricultural machine such as a rice harvester or a forest machine.
  • the crawler type traveling vehicle generally includes an idler (not shown), a sprocket (not shown) and a crawler belt (not shown) outside of the rolling wheels, and the crawler belt is disposed around the idler, the rolling wheel and the sprockets. It is wounded.
  • the wheels of the crawler type traveling vehicle include a shaft 1, a roller 2, floating seals 41 and 42 as sealing means at both ends, and collars 3 and 4 at both ends.
  • Tapered roller bearings 11 and 12 which are bearing means disposed on the left and right, two inner cylinders 81 and 82, a snap ring 6 for holding the collar 3 on the shaft 1, and a pressing member constituting the preloading means 80
  • a bolt 62 for pressing the pressing member 85 against the end face of the shaft 1.
  • the right side of FIG. 1 is the one on the main body side (inner side) when mounted on a crawler type traveling vehicle.
  • the shaft 1 has an intermediate large diameter portion whose diameter is larger than that of the end portion in the central portion, but it may be a cylinder whose diameter does not change either at the end portion or the central portion.
  • the roller 2 is supported by the shaft 1 in a state where it can be externally fitted to and rotated by the shaft 1.
  • the tapered roller bearings 11 and 12 are fitted between the outer peripheral surface of the shaft 1 and the inner peripheral surface of the roller 2 to make the roller 2 rotatable relative to the shaft 1. That is, the roller 2 is rotatably supported by the shaft 1 via tapered roller bearings 11 and 12.
  • the inner cylinders 81 and 82 are ring-shaped, and are installed so as to be in contact with the inner peripheral surface of the roller 2 on the end side of the tapered roller bearings 11 and 12 and held inside the roller 2 by O-rings 83 and 84.
  • the collars 3 and 4 are externally fitted to the respective end portions of the shaft 1 and inserted into the roller 2 and fitted into the ring-shaped inner cylinders 81 and 82 to hold the central portion of the shaft 1 inside the roller 2.
  • Sealing means (floating seals 41, 42 and seals 45, 46, 49, 50 outside the floating seals, O-rings 43, 44, 47, 48) are provided on the roller 2 side when the collars 3, 4 are attached to the shaft 1. Fit to the end (tip) of the one to become.
  • the sealing means is in contact with the inside of the ring of the inner cylinder 81, 82 when the collar 3, 4 is mounted in the roller 2, and the tip of the collar 3, 4 is fitted into the end of the roller 2 and mounted Play a
  • the shaft 1 supports the inner races 14 and 16 of the tapered roller bearings 11 and 12, and the collars 3 and 4 are inserted on both sides thereof.
  • the collar 3 is held on the shaft 1 by a snap ring 6, and the collar 4 is pressed in the central direction of the shaft 1 by a pressing member 85 and a bolt 62.
  • O-rings 51 and 52 are attached to the left and right of the shaft 1 respectively to prevent oil from leaking from the oil reservoir 90 from the gap between the shaft 1 and the collars 3 and 4.
  • a hole 92 from one end of the shaft 1 and a hole 93 communicating therewith form an oil supply path to the oil reservoir 90.
  • a plug 91 is inserted.
  • the collars 3 and 4 are fixed to a crawler type traveling vehicle main body (not shown) by bolts (not shown).
  • the roller 2 is hollow, and the outer races 13 and 15 of the tapered roller bearings 11 and 12 and the inner cylinders 81 and 82 are mounted. Further, O-rings 83 and 84 are attached to the inner cylinders 81 and 82, respectively, and oil leakage of the oil reservoir 90 from the gap between the roller 2 and the inner cylinders 81 and 82 is prevented.
  • the floating seal 41 is disposed between the collar 3 and the inner cylinder 81, and the floating seal 42 is disposed between the collar 4 and the inner cylinder 82. The floating seals 41, 42 prevent lubricating oil from leaking out of the oil reservoir 90 and prevent mud and other foreign matter from entering the oil reservoir 90.
  • the end face 31 of the collar 3 positioned on the shaft 1 by the snap ring 6 is in contact with the end face 21 of the inner race 14 of the tapered roller bearing 11.
  • the end face 19 of the outer race 13 of the tapered roller bearing 11 is in contact with the hollow end face 33 of the roller 2.
  • the hollow end surface 34 of the roller 2 is in contact with the end surface 20 of the outer race 15 of the tapered roller bearing 12.
  • the end face 22 of the inner race 16 of the tapered roller bearing 12 is in contact with the end face 32 of the collar 4.
  • the end face 32 of the collar 4 is on the root side of the collar 4 (the side inserted into the roller 2).
  • the end surface 22 of the inner race 16 of the tapered roller bearing 12 is a surface on the side that can be seen from the hole at the end of the roller 2 when the tapered roller bearing 12 is attached to the roller 2.
  • FIG. 2 is a right side view of the wheel of the crawler type traveling vehicle according to the first embodiment of the present invention.
  • FIG. 2 shows an embodiment of the preloading means, and includes a pressing member 85 for pressing the collar 4 in the central direction of the shaft 1 and a bolt 62 for pressing the pressing member 85 against the shaft 1.
  • a preload force is generated by the force due to the bending, and the close contact of each of the end surfaces described above is enabled.
  • the preloading means 80 appropriately realizes clearance management in the axial direction of the tapered roller bearings 11 and 12 with the collars 3 and 4 attached to the roller 2, and the preloaded roller 80 is necessary and sufficient for tapered roller bearings.
  • the preloading means 80 is the body side (inner side) when the roller according to the first embodiment of the present invention is mounted on a crawler type traveling vehicle, that is, the shaft end side of the shaft 1. It is comprised including.
  • the bolt 62 is a fixing member that presses and fixes the pressing member 85 against the end face of the shaft end of the shaft 1.
  • the pressing member 85 presses the collar 4 toward the center of the shaft 1 by tightening the bolt 62.
  • the pressing member 85 is a component that is disposed at the center of the end face on the side closer to the main body side when the shaft 1 is mounted on the crawler type traveling vehicle, and has one arm extending to both diametrical ends.
  • At the center of the end of the collar 4 there is a hole into which the shaft 1 is inserted, and at the end of the hole there is provided a step portion which is concaved in the center.
  • the end face of the shaft 1 is inside the stepped portion at the end of the collar 4 (in FIG. 2, the distance between the end face of the shaft 1 and the stepped portion of the collar 4 is L).
  • the length of the arm of the pressing member 85 is longer than the diameter of the shaft end, and the rear surface of the arm of the pressing member 85 contacts the inner peripheral end of the step portion of the collar 4 when mounted on the shaft 1.
  • the bolt 62 passes through the center hole of the pressing member 85 and then fits around the end of the shaft 1.
  • both ends of the arm portion which is a part of the peripheral portion of the pressing member 85 press the end portion of the collar 4 in the direction of the central portion of the shaft 1 while pressing the pressing member A part or all of the peripheral part of 85 may be pressed in a state where the end of the collar 4 is pressed in the direction of the central part of the shaft 1.
  • the pressing member 85 bends against the inner peripheral angle of the step portion of the collar 4 and bends.
  • the collar 4 is pushed by the pressing member 85 from the end side of the shaft 1 toward the central side.
  • the pressing member 85 begins to yield, and even if the bolt 62 is tightened and the deflection is increased, the pressure does not increase so much, thereby preventing the generation of the excess preload. be able to.
  • FIG. 7A shows the characteristics of the pressing load W and the deflection L of the pressing member 85, where Wy is a required preload.
  • Wy is a load for zeroing the axial gap of the tapered roller bearing at the time of assembly, and the repulsive force of the elastic ring bodies 43, 44, 47, 48 contained in the floating seals 41, 42, and other sliding resistances. It is a value obtained by adding a margin to the added value, and is not an excessive value.
  • the deflection L is Lo as a reference value, it fluctuates from L1 to L2 due to the accumulation of the dimensional tolerance of each component. When the pressing member 85 is bent, the pressing load increases in proportion to the bending, but by causing the pressing member 85 to yield halfway, generation of excessive pressing load is suppressed, and generation of excessive preload is prevented. I can do it.
  • the pressing member 85 For the pressing member 85, a material whose yield stress falls within a predetermined range is selected.
  • the pressure applied to the collar 4 by tightening the bolt 62 and bending the pressing member 85 pushes the collar 4 toward the center of the shaft 1 to apply a preload to the tapered roller bearings 11 and 12.
  • the yield stress or the load resistance is reached, even if the bolt 62 is further tightened and the deflection becomes large, the preload does not increase almost at all, so that the generation of the excess preload can be prevented.
  • the pressing member 85 is a thin plate having a rectangular solid shape, and can be made to yield with an appropriate preload by changing the plate thickness and the dimension of the short side.
  • the bearing manufacturer's recommendation for using tapered roller bearings 11 and 12 effectively is "The fatigue life is longest when the bearing clearance is slightly negative, but the fatigue life is increased when the negative clearance amount is large. Decrease in heat and heat buildup. ” That is, the excessive pre-load rapidly reduces the fatigue life of the tapered roller bearing and makes the heat generation large.
  • FIG. 6 of FIG. 6 of FIG. 6 shows Tapered Roller Bearing 4 and Collar 7
  • the disc spring 28 is mounted between them. If the spring constant of this disc spring 28 is reduced, excessive preload on the tapered roller bearings can be prevented during assembly, but the rollers are attached to the vehicle body and from the outside when actually used The large axial load causes the disc spring 28 to be largely bent, and the axial gap of the tapered roller bearing on the opposite side of the loaded tapered roller bearing is increased.
  • the axial gap is a cumulative tolerance of the component parts, and the actual axial gap has a tolerance width of There is a risk of growing up.
  • the tolerances of the components are tightened, there is a risk of cost increase, and if the tolerances are not tightened, there is a risk that the clearance management may cause the life of the bearings to fall away from the bearing manufacturer's recommendation.
  • the rolling wheels of the crawler type traveling vehicle of the first embodiment of the present invention in the clearance management of tapered roller bearings, a high level assembly technique such as shim adjustment is not necessary, and the dimensional tolerance of components needs to be tightened.
  • the axial clearance of the tapered roller bearing can be set to zero with no simple assembly procedure, and moreover, since the preload does not become excessive, the fatigue life of the tapered roller bearing can be reduced without increasing the amount of negative clearance. You can expect to prevent the decline.
  • it is possible to reuse by surrendering in the reverse direction by reversing and using the pressing member that has yielded at the time of assembly.
  • the durability and the reliability are excellent.
  • FIG. 6 shows FIG. 4 of Patent Document 2.
  • the disc spring 28 between the tapered roller bearing 4 and the collar 7 is weakened, excessive preload on the tapered roller bearing is prevented.
  • the disc spring 28 is disposed closer to the central portion of the shaft 1 than the collar 7, the disc spring 28 is bent by a large axial load from the outside of the actual work when the wheel is actually used. I'm sorry. (The code used in this paragraph is the code in Figure 6 and has nothing to do with the code in the other figures.)
  • FIG. 3 is a schematic cross-sectional view of the wheels of the crawler type traveling vehicle of the second embodiment of the present invention.
  • FIG. 3 shows the wheels of the crawler type traveling vehicle according to the second embodiment of the present invention, but both ends of the shaft 1 have no notch over the entire circumference, therefore the cylindrical parts of the collars 3 and 4 are both ends of the shaft 1
  • the wall thickness is maintained over the entire circumference.
  • the pressing member 61 has a disk shape.
  • FIG. 4 is a right side detail view of the wheel of the crawler type traveling vehicle of the second embodiment of the present invention.
  • FIG. 4 is a detailed view of the periphery of the pressing member 61 of the rotating wheel of the crawler traveling vehicle according to the second embodiment of the present invention shown in FIG.
  • the pressing member 61 in FIG. 4 functions the same as the pressing member 85 in FIG.
  • the preloading means 80 of the rotating wheels of the crawler belt type traveling vehicle according to the second embodiment of the present invention is constituted by the pressing member 61 and the bolt 62, and the pressing member 61 has a portion longer than the diameter of the end face of the shaft 1 A preload is applied to the bearings 11 and 12 to adjust the axial clearance by the action of deflection.
  • the pressing member 61 yields in the middle of tightening the bolt 62. Even if the bolt 62 is completely tightened, the generation of an excessive pressing load is suppressed and the generation of an excessive preload is prevented. It can.
  • the durability and the reliability are excellent.
  • FIG. 5 is a right side detail view of the wheels of the crawler type traveling vehicle of the third embodiment of the present invention.
  • the wheel of the crawler type traveling vehicle according to the third embodiment of the present invention has its center expanded at the end (shaft end) on the side which becomes the main body side when the shaft 1 is mounted on the crawler type traveling vehicle (convex And the wheel of the crawler type traveling vehicle according to the second embodiment of the present invention described above except that a stepped portion is provided and a washer 72 and a disc spring-like hollow disc 71 are used instead of the pressing member 61. It is the same composition.
  • the disc spring-like hollow disc 71 may be in the form of a donut having an inner diameter larger than the diameter of the end of the shaft 1 and an outer diameter larger than the diameter of the main body of the shaft 1. it can.
  • a material having a spring constant smaller than a predetermined value is selected.
  • a washer 72 is fixed to the shaft 1 by a bolt 73.
  • a disc spring-like hollow disc 71 having a weak spring constant and a large displacement is incorporated.
  • the initial state of the disc spring-like hollow disc 71 is shown by a broken line, but in a state where the washer 72 is fixed to the shaft 1 by the bolt 73, the deflection becomes L ′.
  • the wheel of the crawler type traveling vehicle according to the third aspect of the present invention is a roller of the crawler type traveling vehicle according to the third embodiment of the present invention, and has the configuration shown in FIG.
  • the spring constant is weak, and the L 'dimension in FIG. 5 varies from L'1 to L'o to L'2 in cumulative tolerance of components.
  • excessive preload can be prevented.
  • the characteristic diagram is shown in (B) of FIG. 7, but since the spring constant of the disc spring-like hollow disc 71 is weak, the excessive pressing load is not obtained even if the deflection fluctuates from L'1 to L'2 shown in FIG. It does not occur.
  • the durability and the reliability are excellent. According to this embodiment, since the spring constant of the disc spring-like hollow disc 71 is low, the excessive pressing load due to the deflection does not occur.
  • the preloading means 80 of the rotating wheel of the crawler belt type traveling vehicle of the third embodiment of the present invention is constituted by a washer 72, a disc-shaped hollow disc 71 and a bolt 73.
  • the washer 72 and the disc spring-like hollow disc 71 have a diameter which is longer than the diameter of the end face of the shaft 1 and shorter than the diameter of the main body of the shaft. It is provided to be in contact with the surface of a disc spring-like hollow disc 71. Therefore, the preloading means 80 composed of the washer 72, the disc-shaped hollow disc 71 and the bolt 73 is used to deflect the preload for adjusting the axial clearance of the tapered roller bearings 11 and 12 by the action of deflection. Since the spring constant is small even when the bolt 73 is tightened, generation of excessive pressing load can be suppressed and generation of excessive preload can be prevented. This bolt may be tightened.
  • the wheel of the crawler type traveling vehicle according to the fourth aspect of the present invention is an example shown in FIG. 3, and the collar 4 is a stopper as a means for preventing deviation between the collar 4 and the shaft 1 A screw 63 is provided.
  • the collars 3 and 4 are fixed to a crawler type traveling vehicle main body (not shown) by bolts (not shown).
  • the shaft 1 can be used individually even if the lateral rigidity of the mounting portion is weak. Connection by is effective in strengthening the entire rigidity.
  • Such a vehicle body contributes to the prevention of lateral deformation of the wheel mounting portion of the vehicle body, and the durability of the wheel can be secured.
  • FIG. 6 is a view showing a prior art, not an embodiment of the present invention, which is FIG. 4 of US Pat. No. 4,640,559.
  • the symbols shown in FIG. 6 are independent of the symbols used in the other figures of the present application.
  • the description of the reference numerals shown below is the description of the reference numerals used other than FIG.
  • FIG. 7 is a pressure load-gap diagram.
  • FIG. 7A is a pressing load-gap diagram in Example 1 and Example 2 of the present invention
  • FIG. 7B is a pressing load-gap diagram in Example 3 of the present invention.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)

Abstract

Provided is a rolling wheel for a crawler type traveling vehicle which facilitates easy assembly while utilizing a tapered roller bearing for a rolling wheel adaptable to high speed traveling, and which has excellent durability and reliability. A rolling wheel which constitutes a part of a crawler type traveling vehicle comprises a roller (2), a shaft (1), sealing means (41, 42) provided at both ends, and collars (3, 4), and has bearing means which are arranged on the left and right and configured with a pair of tapered roller bearings (11, 12) fitted to the outside of the shaft (1). With the tapered roller bearings (11, 12) and the sealing means (41, 42) being attached, a pre-loading means (80) that adjusts the gap of the tapered roller bearings (11, 12) in the axial direction is provided at the axial end of the shaft (1), a pushing member (85) of the pre-loading means (80) applies a pre-load due to force of deformation by a bolt (62), and a change in the pre-load is reduced after the pre-load has reached a necessary level. Accordingly, a simple and excellent gap managing means for the tapered roller bearings is attained.

Description

履帯式走行車両の転輪Wheels of track type traveling vehicle
　本発明は、履帯式走行車両の転輪に関するものである。 The present invention relates to a wheel of a crawler type traveling vehicle.
　履帯式走行車両に使われている転輪は移動する履帯（図示せず）との摩擦により回転する。一方、履帯式走行車両の高速化に伴い、転輪の軸受手段がブッシュから円すいころ軸受に変わるものが現れた。ところが、転輪に円すいころ軸受を組み込んだ場合の軸方向のすきま管理は非常に重要であり、すきま管理が適切に管理されていないと、軸受本来の性能が発揮できなくなり、転輪としての信頼性を損なう恐れがあった。 Rollers used in crawler type traveling vehicles are rotated by friction with moving crawler belts (not shown). On the other hand, with the increase in speed of track-type traveling vehicles, there have appeared those in which the bearing means of the rolling wheels are changed from bushes to tapered roller bearings. However, axial clearance management in the case where tapered roller bearings are incorporated into the rolling wheels is very important, and if the clearance management is not properly managed, the inherent performance of the bearings can not be exhibited, and the reliability as rolling wheels can not be achieved. There was a risk of losing sex.
　この軸方向の隙間管理をおこなう方法としては、転輪のシャフトの軸端でのシム調整（特許文献１）、円すいころ軸受とカラーの間への皿ばね設置（特許文献２）、円すいころ軸受間への規制部材の設置（特許文献３）等があった。 As a method of managing the clearance in the axial direction, shim adjustment at the shaft end of the shaft of the rotating wheel (Patent Document 1), installation of a disc spring between the tapered roller bearing and the collar (Patent Document 2), tapered roller bearing There has been an installation of a regulating member between the two (Patent Document 3) and the like.
特開昭４９－７２８３７ 号公報JP-A-49-72837 米国特許４，６４０，５５９号公報（Fig４）U.S. Pat. No. 4,640,559 (FIG. 4) 特開２００４－８２８１９ 号公報Japanese Patent Application Publication No. 2004-82819
　特許文献１記載の転輪では、転輪での円すいころ軸受のアキシャル隙間管理をシム調整で行った場合、組立時に熟練した技術が必要であり、アキシャル隙間管理が十分に行われていないと、組立品質の低下の恐れがあった。 In the rolling wheel described in Patent Document 1, when axial clearance management of tapered roller bearings in the rolling wheel is performed by shim adjustment, skillful technology is required at the time of assembly, and axial clearance management is not sufficiently performed, There was a risk of deterioration in assembly quality.
　また、特許文献２記載の転輪では、円すいころ軸受とカラーの間へ皿ばねを設置する方法の場合、図６に特許文献２のFig４を示すが、円すいころ軸受４とカラー７の間に皿ばね２８が装着されている。この皿ばね２８のばね定数を弱くすれば、組立時の円すいころ軸受への過大な予圧力を防ぐことはできるが、転輪が車両本体に取り付けられて、実際に使われた時の外部からの大きなアキシャル負荷により、皿ばね２８は大きく撓んでしまい、負荷を受けた円すいころ軸受の反対側の円すいころ軸受のアキシャル隙間が大きくなってしまう。逆に、皿ばね２８のばね定数を強くすれば、外部からの大きなアキシャル負荷に対する撓みを押さえることができるが、組立時に円すいころ軸受に過大な予圧力がかかることとなり、実際に使われた時に、軸受の発熱や、低寿命化を招く恐れがあった。（本段落において用いた符号は、図６における符号であり、他の図の符号とは無関係である。） Further, in the case of the method of installing a disc spring between the tapered roller bearing and the collar in the rolling wheel described in Patent Document 2, FIG. 6 shows FIG. 4 of Patent Document 2, but between the tapered roller bearing 4 and the collar 7 A disc spring 28 is mounted. If the spring constant of the disc spring 28 is reduced, excessive preload on the tapered roller bearings can be prevented during assembly, but the rollers are attached to the vehicle body, and from the outside when actually used The large axial load causes the disc spring 28 to be largely bent, and the axial gap of the tapered roller bearing on the opposite side of the loaded tapered roller bearing is increased. Conversely, if the spring constant of the disc spring 28 is increased, deflection against a large axial load from the outside can be suppressed, but an excessive preload is applied to the tapered roller bearing at the time of assembly, which makes it possible to actually use it. There is a possibility that the heat generation of the bearing and the life shortening may be caused. (The code used in this paragraph is the code in Figure 6 and has nothing to do with the code in the other figures.)
　また、特許文献３記載の転輪では、円すいころ軸受間へ規制部材を設置した場合は、アキシャル隙間は構成部品の公差の累積となり、実際のアキシャル隙間の公差の巾が大きくなり、上記同様、円すいころ軸受の低寿命化を招く恐れがあった。 Further, in the rolling wheel described in Patent Document 3, when the restricting member is installed between the tapered roller bearings, the axial gap is a cumulative tolerance of the component parts, and the tolerance width of the actual axial gap is increased. There is a risk that the service life of tapered roller bearings may be shortened.
　本発明は、上記従来の円すいころ軸受のアキシャル隙間管理の困難さの欠点を解決するためになされたものであって、その目的は、高速走行に対応する転輪に円すいころ軸受を使いながら、しかも組立の容易化を図ると共に、耐久性及び信頼性に優れる履帯式走行車両の転輪を提供することである。 The present invention has been made to solve the above-mentioned drawback of the difficulty in managing the axial clearance of the conventional tapered roller bearing, and the purpose thereof is to use the tapered roller bearing for the rotating wheel corresponding to high speed traveling. Moreover, it is an object of the present invention to provide a wheel of a crawler type traveling vehicle which is easy to assemble and is excellent in durability and reliability.
　本発明の第１の態様の履帯式走行車両の転輪は、履帯式走行車両の一部を構成する転輪であって、ローラと、シャフトと、両端に設置されたシール手段と、カラーを備え、左右に配置された軸受手段がシャフトに外嵌される一対の円すいころ軸受により構成される構造において、上記円すいころ軸受及び上記シール手段が装着された状態で、上記円すいころ軸受の軸方向すきまを調整する予圧手段が上記シャフトの軸端に設置され、かつ、上記予圧手段が押し付け部材の撓みによる力で上記カラーを上記円すいころ軸受のインナーレース端面方向に押し付けることより、予圧力を与える構造であることを特徴としている。 The turning wheels of the crawler type traveling vehicle according to the first aspect of the present invention are rolling wheels that constitute a part of the crawler type traveling vehicle, and include a roller, a shaft, sealing means installed at both ends, and a collar In a structure including a pair of tapered roller bearings including the left and right disposed bearing means externally fitted to the shaft, the tapered roller bearing and the sealing means being mounted, the axial direction of the tapered roller bearing A preloading means for adjusting the gap is installed at the shaft end of the shaft, and the preloading means applies a preload by pressing the collar in the direction of the inner race end face of the tapered roller bearing by the force of deflection of the pressing member. It is characterized by being a structure.
　上記本発明の第１の態様の履帯式走行車両の転輪では、シムを用いることなく、円すいころ軸受に必要充分で、且つ、過大でない予圧力を与えるので、組立の容易化と同時に、円すいころ軸受の軸方向のすきま管理が適切に実現でき、高い品質の転輪が得られる。 In the rolling wheels of the crawler type traveling vehicle according to the first aspect of the present invention, since the tapered roller bearing is provided with a necessary sufficient and not excessive preload without using a shim, it is possible to simplify the assembly simultaneously The axial clearance management of the roller bearings can be properly realized, and high-quality rolling wheels can be obtained.
　本発明の第２の態様の履帯式走行車両の転輪は、上記予圧手段が上記カラーを上記シャフトの中央方向に押し付ける押し付け部材と、上記押し付け部材を上記シャフトの軸端に押し付ける為の固定部材とからなり、上記押し付け部材が撓むことによる力で上記カラーを上記シャフトの中央方向に押して、上記円すいころ軸受に予圧力を与える構造において、上記押し付け部材が上記シャフトの軸端に押し付けられて、必要な予圧力が発生する近傍において、上記押し付け部材の撓みによる応力が降伏応力、または耐力に達することを特徴としている。 The roller of the crawler belt traveling vehicle according to the second aspect of the present invention is a pressing member in which the preloading means presses the collar in the central direction of the shaft, and a fixing member for pressing the pressing member against the shaft end of the shaft And the pressing member is pressed against the shaft end of the shaft in a structure in which the collar is pushed in the central direction of the shaft by a force due to the pressing member bending, and a preload is applied to the tapered roller bearing. It is characterized in that the stress due to the deflection of the pressing member reaches the yield stress or the proof stress in the vicinity where the necessary preload is generated.
　本発明の第２の態様の履帯式走行車両の転輪では、上記本発明の第１の態様の履帯式走行車両の転輪と同様の効果を図ることが出来ると共に、特に上記押し付け部材によって適切な予圧力が出た後は、上記押し付け部材を降伏させて、更に押し付け部材を押し付けても、その予圧力の変化を少なくできる。これにより、過剰な予圧力の発生を防ぐことができるので、組立が容易になると同時に組立品質も向上する。なお、アフターサービスにおいて再組立をする場合には、組立時に降伏した上記押し付け部材を反転して使えば、逆方向に降伏することにより再利用も可能である。 In the wheel of the crawler type traveling vehicle according to the second aspect of the present invention, the same effect as the roller of the crawler type traveling vehicle according to the first aspect of the present invention can be achieved. Even if the pressing member is caused to yield and the pressing member is further pressed after a predetermined preload pressure is released, the change in the preload pressure can be reduced. This prevents the occurrence of excessive preload, thereby facilitating assembly and at the same time improving assembly quality. In addition, when reassembling in after service, it is possible to reuse by surrendering in the reverse direction by reversing and using the above-mentioned pressing member that has yielded at the time of assembly.
　本発明の第３の態様の履帯式走行車両の転輪は、上記予圧手段が上記カラーを上記シャフトの中央方向に押し付ける押し付け部材と、上記押し付け部材を上記シャフトの軸端に押し付ける為の固定部材とからなり、上記押し付け部材が撓むことによる力で上記カラーを上記シャフトの中央方向に押して、上記円すいころ軸受に予圧力を与える構造において、上記押し付け部材が、皿ばね状の中空円板からなり、撓んだ時の撓みによる応力が弾性限度内にあることを特徴としている。 The rolling wheels of the crawler type traveling vehicle according to the third aspect of the present invention are a pressing member in which the preloading means presses the collar in the central direction of the shaft, and a fixing member for pressing the pressing member against the shaft end of the shaft The pressing member pushes the collar toward the center of the shaft by the force of the pressing member to bend, thereby applying a pre-load to the tapered roller bearing, wherein the pressing member is a disc spring-like hollow disc It is characterized in that the stress due to the bending at the time of bending is within the elastic limit.
　本発明の第３の態様の履帯式走行車両の転輪では、上記本発明の第１の態様の履帯式走行車両の転輪と同様の効果を図ることが出来ると共に、特に上記押し付け部材によって必要な予圧力が出た後も、上記押し付け部材のばね定数を弱くできるので予圧力の増加率を低く抑え、過剰な予圧力が出るのを防ぐことが出来、組立が容易になると同時に組立品質も向上する。 In the wheel of the crawler type traveling vehicle according to the third aspect of the present invention, the same effect as the wheel of the crawler type traveling vehicle according to the first aspect of the present invention can be achieved. Since the spring constant of the pressing member can be weakened even after a heavy preload is applied, the rate of increase in preload can be kept low, excessive preload can be prevented, and assembly becomes easy as well. improves.
　本発明の第４の態様の履帯式走行車両の転輪は、上記予圧手段が設置されている側の上記カラーに、上記カラーと上記シャフトとの間のずれを防止する手段を設置することを特徴としている。 The wheel of the crawler type traveling vehicle according to the fourth aspect of the present invention comprises installing means for preventing deviation between the collar and the shaft on the collar on the side where the preloading means is installed. It is characterized.
　本発明の第４の態様の履帯式走行車両の転輪では、上記カラーと上記シャフトとの間のずれを防止する手段が設置されているため、転輪が車両本体に取り付けられて、実際に使われた時に上記シャフトが車両本体の補強材の役割を果たし、車両本体の取付け部の横方向の剛性が弱い場合でも、車両本体の転輪取付け部の横方向の変形の防止に貢献し、転輪の耐久性を確保できる。 In the wheel of the crawler type traveling vehicle according to the fourth aspect of the present invention, the means for preventing the shift between the collar and the shaft is installed, so the wheel is attached to the vehicle body, When used, the above-mentioned shaft acts as a reinforcement for the vehicle body and contributes to the prevention of lateral deformation of the wheel mounting portion of the vehicle body even when the lateral rigidity of the mounting portion of the vehicle body is weak, The durability of rolling wheels can be secured.
　本発明によれば、高速走行に対応する転輪に円すいころ軸受を使いながら、しかも組立の容易化を図ると共に、耐久性及び信頼性に優れる。 ADVANTAGE OF THE INVENTION According to this invention, while achieving simplification of an assembly while using a tapered roller bearing for the wheel which respond | corresponds to high speed driving | running | working, it is excellent in durability and reliability.
本発明の実施例１の履帯式走行車両の転輪の断面概略図である。BRIEF DESCRIPTION OF THE DRAWINGS It is the cross-sectional schematic of the rolling wheel of the crawler type traveling vehicle of Example 1 of this invention. 本発明の実施例１の履帯式走行車両の転輪の右側側面図である。It is a right side view of the turning wheel of the crawler type traveling vehicle of Example 1 of the present invention. 本発明の実施例２の履帯式走行車両の転輪の断面概略図である。It is the cross-sectional schematic of the rolling wheel of the crawler type traveling vehicle of Example 2 of this invention. 本発明の実施例２の履帯式走行車両の転輪の右側詳細図である。It is a right-hand side detail view of the turning wheel of the crawler type traveling vehicle of Example 2 of this invention. 本発明の実施例３の履帯式走行車両の転輪の右側詳細図である。It is a right-hand side detail view of the turning wheel of the crawler type traveling vehicle of Example 3 of this invention. 米国特許４６４０５５９号公報のFig４である。It is FIG. 4 of U.S. Pat. No. 4,640,559. 押付荷重―隙間線図である。It is a pressing load-clearance diagram.
　次に、この発明の転輪の具体的な実施の形態について、図面を参照しつつ詳細に説明する。本発明の履帯式走行車両の転輪は、下記において具体的に説明する本発明の好適な実施の形態に限定されるものではない。 Next, specific embodiments of the roller according to the present invention will be described in detail with reference to the drawings. The rolling wheels of the crawler type traveling vehicle of the present invention are not limited to the preferred embodiments of the present invention specifically described below.
｛実施例１｝
　図１は、本発明の実施例１の履帯式走行車両の転輪の断面概略図である。本発明の実施例１の履帯式走行車両の転輪は、例えばブルドーザ等の建設機械や稲刈り機等の農業機械や森林機械等における履帯式走行車両の転輪に使用される。この履帯式走行車両は、転輪の外に通常、アイドラ（図示せず）とスプロケット（図示せず）と履帯（図示せず）とを含み、アイドラ、転輪、及びスプロケットの周囲に履帯を巻装したものである。 {Example 1}
FIG. 1 is a schematic cross-sectional view of a rotating wheel of a crawler type traveling vehicle according to a first embodiment of the present invention. The wheel of the crawler type traveling vehicle according to the first embodiment of the present invention is used, for example, as a wheel of a crawler type traveling vehicle in a construction machine such as a bulldozer or an agricultural machine such as a rice harvester or a forest machine. The crawler type traveling vehicle generally includes an idler (not shown), a sprocket (not shown) and a crawler belt (not shown) outside of the rolling wheels, and the crawler belt is disposed around the idler, the rolling wheel and the sprockets. It is wounded.
　本発明の実施例１の履帯式走行車両の転輪は、図１に示すように、シャフト１と、ローラ２と、両端のシール手段であるフローティングシール４１，４２と、両端のカラー３，４と、左右に配置された軸受手段である円すいころ軸受１１，１２と、２個の内筒８１，８２と、カラー３をシャフト１に保持する止め輪６と、予圧手段８０を構成する押し付け部材８５と、押付部材８５をシャフト1の端面に押し付けるボルト６２とを含んでいる。 As shown in FIG. 1, the wheels of the crawler type traveling vehicle according to the first embodiment of the present invention include a shaft 1, a roller 2, floating seals 41 and 42 as sealing means at both ends, and collars 3 and 4 at both ends. , Tapered roller bearings 11 and 12 which are bearing means disposed on the left and right, two inner cylinders 81 and 82, a snap ring 6 for holding the collar 3 on the shaft 1, and a pressing member constituting the preloading means 80 And a bolt 62 for pressing the pressing member 85 against the end face of the shaft 1.
　図１の右側が、履帯式走行車両に装着したときに本体側（内側）になる方である。シャフト１は、実施例１では、中央部分に端部よりも径が大きい中間大径部分を有するが、端部も中央部も径が変わらない円柱であってもよい。ローラ２は、シャフト１に外嵌し回転可能な状態でシャフト１に支持される。円すいころ軸受１１，１２は、シャフト１の外周面とローラ２の内周面との間に嵌装され、シャフト１に対しローラ２を回転可能にさせる。すなわち、ローラ２は、シャフト１に、円すいころ軸受１１，１２を介して回転可能に支持される。内筒８１，８２は、リング状で、円すいころ軸受１１，１２より端側でローラ２の内周面に接して内装されＯリング８３，８４でローラ２内に保持される。カラー３，４は、シャフト１の端部それぞれに外嵌してローラ２内に差し込んでリング状の内筒８１，８２に嵌め込んでシャフト１中央部をローラ２内に保持する。シール手段（フローティングシール４１，４２及びフローティングシールの外側のシール４５，４６，４９，５０、Ｏリング４３，４４，４７，４８）は、カラー３，４をシャフト１に装着した際にローラ２側となる方の端部（先端）に外嵌する。シール手段は、カラー３，４をローラ２内に装着した際に、内筒８１，８２のリング内側に接して、カラー３，４の当該先端をローラ２の端部内側に嵌めて装着した状態で保持する役割を果たす。 The right side of FIG. 1 is the one on the main body side (inner side) when mounted on a crawler type traveling vehicle. In Example 1, the shaft 1 has an intermediate large diameter portion whose diameter is larger than that of the end portion in the central portion, but it may be a cylinder whose diameter does not change either at the end portion or the central portion. The roller 2 is supported by the shaft 1 in a state where it can be externally fitted to and rotated by the shaft 1. The tapered roller bearings 11 and 12 are fitted between the outer peripheral surface of the shaft 1 and the inner peripheral surface of the roller 2 to make the roller 2 rotatable relative to the shaft 1. That is, the roller 2 is rotatably supported by the shaft 1 via tapered roller bearings 11 and 12. The inner cylinders 81 and 82 are ring-shaped, and are installed so as to be in contact with the inner peripheral surface of the roller 2 on the end side of the tapered roller bearings 11 and 12 and held inside the roller 2 by O- rings 83 and 84. The collars 3 and 4 are externally fitted to the respective end portions of the shaft 1 and inserted into the roller 2 and fitted into the ring-shaped inner cylinders 81 and 82 to hold the central portion of the shaft 1 inside the roller 2. Sealing means (floating seals 41, 42 and seals 45, 46, 49, 50 outside the floating seals, O- rings 43, 44, 47, 48) are provided on the roller 2 side when the collars 3, 4 are attached to the shaft 1. Fit to the end (tip) of the one to become. The sealing means is in contact with the inside of the ring of the inner cylinder 81, 82 when the collar 3, 4 is mounted in the roller 2, and the tip of the collar 3, 4 is fitted into the end of the roller 2 and mounted Play a role in
　シャフト１は円すいころ軸受１１，１２のインナーレース１４，１６を支持し、その両側にはカラー３，４が挿入されている。カラー３は止め輪６により、シャフト１に保持され、カラー４は押付部材８５とボルト６２によりシャフト１の中央方向に押し付けられている。また、シャフト１の左右にはそれぞれOリング５１、５２が装着されており、シャフト１とカラー３，４との隙間からの油溜り９０の油の漏れを防止している。 The shaft 1 supports the inner races 14 and 16 of the tapered roller bearings 11 and 12, and the collars 3 and 4 are inserted on both sides thereof. The collar 3 is held on the shaft 1 by a snap ring 6, and the collar 4 is pressed in the central direction of the shaft 1 by a pressing member 85 and a bolt 62. In addition, O- rings 51 and 52 are attached to the left and right of the shaft 1 respectively to prevent oil from leaking from the oil reservoir 90 from the gap between the shaft 1 and the collars 3 and 4.
　更に、シャフト１の一端からの穴９２、それに連通した穴９３により、油溜り９０への給油路が形成されている。穴９２の入り口には栓９１が挿入されている。 Further, a hole 92 from one end of the shaft 1 and a hole 93 communicating therewith form an oil supply path to the oil reservoir 90. At the entrance of the hole 92, a plug 91 is inserted.
　カラー３，４は履帯式走行車両本体（図示せず）に、ボルト（図示せず）によって各々固定されている。 The collars 3 and 4 are fixed to a crawler type traveling vehicle main body (not shown) by bolts (not shown).
　ローラ２は中空になっており、円すいころ軸受１１，１２のアウターレース１３，１５と、内筒８１，８２が装着されている。また、内筒８１，８２にはそれぞれＯリング８３、８４が装着されており、ローラ２と内筒８１、８２との隙間からの油溜り９０の油の漏れを防止している。フローティングシール４１はカラー３と内筒８１の間に、フローティングシール４２はカラー４と内筒８２の間にそれぞれ配置されている。フローティングシール４１，４２は油溜り９０からの潤滑油の漏れを防止し、泥及び他の異物が油溜り９０に入るのを防止する。 The roller 2 is hollow, and the outer races 13 and 15 of the tapered roller bearings 11 and 12 and the inner cylinders 81 and 82 are mounted. Further, O- rings 83 and 84 are attached to the inner cylinders 81 and 82, respectively, and oil leakage of the oil reservoir 90 from the gap between the roller 2 and the inner cylinders 81 and 82 is prevented. The floating seal 41 is disposed between the collar 3 and the inner cylinder 81, and the floating seal 42 is disposed between the collar 4 and the inner cylinder 82. The floating seals 41, 42 prevent lubricating oil from leaking out of the oil reservoir 90 and prevent mud and other foreign matter from entering the oil reservoir 90.
　次に、シャフト１に止め輪６で位置決めされたカラー３の端面３１は円すいころ軸受１１のインナーレース１４の端面２１に接触している。円すいころ軸受１１のアウターレース１３の端面１９はローラ２の中空内の端面３３に接触している。ローラ２の中空内の端面３４は円すいころ軸受１２のアウターレース１５の端面２０に接触している。円すいころ軸受１２のインナーレース１６の端面２２はカラー４の端面３２に接触している。カラー４の端面３２は、カラー４の根元側（ローラ２内に挿入した側）である。円すいころ軸受１２のインナーレース１６の端面２２は、ローラ２に円すいころ軸受１２を装着した際にローラ２の端部の穴から見える側の面である。 Next, the end face 31 of the collar 3 positioned on the shaft 1 by the snap ring 6 is in contact with the end face 21 of the inner race 14 of the tapered roller bearing 11. The end face 19 of the outer race 13 of the tapered roller bearing 11 is in contact with the hollow end face 33 of the roller 2. The hollow end surface 34 of the roller 2 is in contact with the end surface 20 of the outer race 15 of the tapered roller bearing 12. The end face 22 of the inner race 16 of the tapered roller bearing 12 is in contact with the end face 32 of the collar 4. The end face 32 of the collar 4 is on the root side of the collar 4 (the side inserted into the roller 2). The end surface 22 of the inner race 16 of the tapered roller bearing 12 is a surface on the side that can be seen from the hole at the end of the roller 2 when the tapered roller bearing 12 is attached to the roller 2.
　図２は、本発明の実施例１の履帯式走行車両の転輪の右側側面図である。図２は、予圧手段の一実施例を示すものであるが、カラー４をシャフト１の中央方向に押しつける押し付け部材８５と、押し付け部材８５をシャフト１に押し付けるボルト６２を含んでいる。押し付け部材８５が、図示の寸法Lだけ撓むことにより、その撓みによる力で予圧力が発生し、上記の各々の端面の密着を可能としている。 FIG. 2 is a right side view of the wheel of the crawler type traveling vehicle according to the first embodiment of the present invention. FIG. 2 shows an embodiment of the preloading means, and includes a pressing member 85 for pressing the collar 4 in the central direction of the shaft 1 and a bolt 62 for pressing the pressing member 85 against the shaft 1. When the pressing member 85 is bent by the dimension L shown in the drawing, a preload force is generated by the force due to the bending, and the close contact of each of the end surfaces described above is enabled.
　予圧手段８０は、カラー３，４を、ローラ２に装着した状態で、円すいころ軸受け１１，１２の軸方向に、すきま管理を適切に実現でき、円すいころ軸受に必要十分で、かつ過大でない予圧力を与える。予圧手段８０は、本発明の実施例１の転輪を履帯式走行車両に装着したときに本体側（内側）になる方、すなわちシャフト１の軸端側にあって、押し付け部材８５とボルト６２を含んで構成される。ボルト６２は、押し付け部材８５をシャフト１の軸端の端面に押し付けて固定する固定部材である。押し付け部材８５は、ボルト６２を締めることによって、カラー４をシャフト１の中央方向に押し付ける。 The preloading means 80 appropriately realizes clearance management in the axial direction of the tapered roller bearings 11 and 12 with the collars 3 and 4 attached to the roller 2, and the preloaded roller 80 is necessary and sufficient for tapered roller bearings. Give pressure. The preloading means 80 is the body side (inner side) when the roller according to the first embodiment of the present invention is mounted on a crawler type traveling vehicle, that is, the shaft end side of the shaft 1. It is comprised including. The bolt 62 is a fixing member that presses and fixes the pressing member 85 against the end face of the shaft end of the shaft 1. The pressing member 85 presses the collar 4 toward the center of the shaft 1 by tightening the bolt 62.
　押し付け部材８５は、シャフト１の、履帯式走行車両に装着したときに本体側になる側の端面の中央に配置され、直径方向両端に延びる１本の腕部を有する部品である。カラー４の端部中央にはシャフト１を挿入する穴があり、穴の端部には中央がへこんだ（凹状の）段差部分が設けてある。シャフト１の端面は、カラー４の端部の段差部分より内側にある（図２では、シャフト１の端面とカラー４の段差部分との距離はＬ）。押し付け部材８５の腕部の長さはシャフト端部の直径より長く、シャフト１への装着時、押し付け部材８５の腕部の裏面は、カラー４の段差部分の内周端に接する。ボルト６２は、押し付け部材８５の中央の穴に通したうえでシャフト１の端部中心に嵌める。本実施例では、押し付け部材８５の周縁部の一部である腕部両端がカラー４の端部をシャフト１中央部方向に押し付けた状態で押圧するが、腕部以外であっても、押し付け部材８５の周縁部の一部又は全部がカラー４の端部をシャフト１中央部方向に押し付けた状態で押圧するものであればよい。 The pressing member 85 is a component that is disposed at the center of the end face on the side closer to the main body side when the shaft 1 is mounted on the crawler type traveling vehicle, and has one arm extending to both diametrical ends. At the center of the end of the collar 4 there is a hole into which the shaft 1 is inserted, and at the end of the hole there is provided a step portion which is concaved in the center. The end face of the shaft 1 is inside the stepped portion at the end of the collar 4 (in FIG. 2, the distance between the end face of the shaft 1 and the stepped portion of the collar 4 is L). The length of the arm of the pressing member 85 is longer than the diameter of the shaft end, and the rear surface of the arm of the pressing member 85 contacts the inner peripheral end of the step portion of the collar 4 when mounted on the shaft 1. The bolt 62 passes through the center hole of the pressing member 85 and then fits around the end of the shaft 1. In this embodiment, both ends of the arm portion which is a part of the peripheral portion of the pressing member 85 press the end portion of the collar 4 in the direction of the central portion of the shaft 1 while pressing the pressing member A part or all of the peripheral part of 85 may be pressed in a state where the end of the collar 4 is pressed in the direction of the central part of the shaft 1.
　ボルト６２を締めると、押し付け部材８５は、カラー４の段差部分の内周角に当たって撓む。ボルト６２を締めると、カラー４は、押し付け部材８５によって、シャフト１の端部側から中央部側の方向に向けて押される。 When the bolt 62 is tightened, the pressing member 85 bends against the inner peripheral angle of the step portion of the collar 4 and bends. When the bolt 62 is tightened, the collar 4 is pushed by the pressing member 85 from the end side of the shaft 1 toward the central side.
　カラー４がシャフト１の中央部方向へ押されることにより、カラー３の端面３１は、接触している円すいころ軸受１１のインナーレース１４の端面２１を、シャフト１の端部側から中央部側の方向に向けて押し付けることになる。円すいころ軸受１１がシャフト１の端部側から中央部側の方向に向けて押し付けられることにより、円すいころ軸受け１１，１２の軸方向のすきまは狭くなる。したがって、さらに、ボルト６２を締め付けていくと、押し付け部材８５の撓みによって、カラー４から円すいころ軸受１１，１２の軸方向のすきまはなくなる。さらに締め付けていくと必要予圧荷重を超えたところで、押し付け部材８５が降伏し始め、ボルト６２を締めきって撓みが大きくなった状態でも、押圧はそれほど増加しないので、過剰な予圧力の発生を防ぐことができる。 When the collar 4 is pushed toward the central portion of the shaft 1, the end surface 31 of the collar 3 is in contact with the end surface 21 of the inner race 14 of the tapered roller bearing 11 from the end of the shaft 1 to the central portion It will be pushed in the direction. When the tapered roller bearing 11 is pressed from the end side of the shaft 1 toward the central side, the axial clearance of the tapered roller bearings 11 and 12 becomes narrow. Therefore, when the bolt 62 is further tightened, the axial clearance of the tapered roller bearings 11 and 12 from the collar 4 is eliminated by the deflection of the pressing member 85. When the tightening load further exceeds the necessary preload, the pressing member 85 begins to yield, and even if the bolt 62 is tightened and the deflection is increased, the pressure does not increase so much, thereby preventing the generation of the excess preload. be able to.
　図７（Ａ）は押し付け部材８５の押付荷重Wと撓みLの特性を示すものであるが、ここで、Wyは必要予圧荷重である。Wyは組立時に、円すいころ軸受のアキシャル隙間を零にする為の荷重で有り、フローティングシール４１、４２に含まれる弾性リング体４３，４４、４７，４８の反発力と、その他の摺動抵抗を加算した値に余裕代を加えた値であり、且つ過大でない値である。一方、撓みLはＬｏが基準値であるが、各構成部品の寸法公差の累積によりL１～L2と変動する。押し付け部材８５を撓ませて行くと、撓みに比例して押付荷重が増加するが、途中で押し付け部材８５を降伏させることにより、過剰な押付荷重の発生を抑え、過大な予圧力の発生を防ぐことが出来る。 FIG. 7A shows the characteristics of the pressing load W and the deflection L of the pressing member 85, where Wy is a required preload. Wy is a load for zeroing the axial gap of the tapered roller bearing at the time of assembly, and the repulsive force of the elastic ring bodies 43, 44, 47, 48 contained in the floating seals 41, 42, and other sliding resistances. It is a value obtained by adding a margin to the added value, and is not an excessive value. On the other hand, although the deflection L is Lo as a reference value, it fluctuates from L1 to L2 due to the accumulation of the dimensional tolerance of each component. When the pressing member 85 is bent, the pressing load increases in proportion to the bending, but by causing the pressing member 85 to yield halfway, generation of excessive pressing load is suppressed, and generation of excessive preload is prevented. I can do it.
　押し付け部材８５には、降伏応力が所定の範囲となる材料を選択する。ボルト６２を締めて押し付け部材８５が撓むことによりカラー４に与えられる押圧で、カラー４をシャフト１の中央方向に押して、円すいころ軸受１１，１２に予圧力を与える。押し付け部材８５がシャフト１の軸端に押し付けられてカラー４を介して円すいころ軸受け１１に与えられる予圧力、すなわち、押し付け部材８５の撓みによる応力が、必要な予圧荷重を越えて、押し付け部材８５の降伏応力、または耐力に達すると、それ以上にボルト６２を締めて撓みが大きくなっても、予圧力はほとんど増加しないので、過剰な予圧力の発生を防ぐことが出来る。 For the pressing member 85, a material whose yield stress falls within a predetermined range is selected. The pressure applied to the collar 4 by tightening the bolt 62 and bending the pressing member 85 pushes the collar 4 toward the center of the shaft 1 to apply a preload to the tapered roller bearings 11 and 12. The preload force applied to the tapered roller bearing 11 through the collar 4 by the pressing member 85 being pressed against the axial end of the shaft 1, that is, the stress due to the deflection of the pressing member 85 exceeds the necessary preload load. When the yield stress or the load resistance is reached, even if the bolt 62 is further tightened and the deflection becomes large, the preload does not increase almost at all, so that the generation of the excess preload can be prevented.
　押し付け部材８５は、直方体形状の薄板で板厚や短辺の寸法を変えることで適正な予圧力で降伏させることができる。 The pressing member 85 is a thin plate having a rectangular solid shape, and can be made to yield with an appropriate preload by changing the plate thickness and the dimension of the short side.
　なお、円すいころ軸受１１，１２を効果的に使うためのベアリングメーカの推奨は「軸受のすきまがわずかに負であるとき、疲れ寿命が最も長くなるが、負のすきま量が大きくなると、疲れ寿命が急激に低下することと、発熱も大きくなる。」としている。即ち、過大な予圧力は、円すいころ軸受の疲れ寿命を急激に低下させ、発熱も大きなものにする。 In addition, the bearing manufacturer's recommendation for using tapered roller bearings 11 and 12 effectively is "The fatigue life is longest when the bearing clearance is slightly negative, but the fatigue life is increased when the negative clearance amount is large. Decrease in heat and heat buildup. ” That is, the excessive pre-load rapidly reduces the fatigue life of the tapered roller bearing and makes the heat generation large.
　一方、特許文献１に記載の様な従来技術では、円すいころ軸受のアキシャル隙間管理をシム調整で行っており、このシム調整は組立時に熟練した技術が必要であり、アキシャル隙間管理が十分に行われていないと、組立品質の低下を引き起こす恐れがあった。即ち使用するシムの最少厚みが厚いと、すきま管理がベアリングメーカの推奨から遠のいてベアリングの寿命低下を起こす恐れがあり、逆に、シムの最少厚みを薄くすると、製作の難易度が上がることによるコストアップとなり、組立技術もより高度化し、組立品質の低下を引き起こす恐れがあった。 On the other hand, in the prior art as described in Patent Document 1, axial clearance management of tapered roller bearings is performed by shim adjustment, and this shim adjustment requires skilled techniques at the time of assembly, and axial clearance management is sufficiently performed. If not, there was a risk of causing deterioration in assembly quality. That is, if the minimum thickness of the shim used is large, the clearance management may cause the bearing life to fall away from the bearing manufacturer's recommendation, and conversely, if the minimum thickness of the shim is reduced, the manufacturing difficulty increases. The cost is increased, the assembly technology is more advanced, and the assembly quality may be degraded.
　また、特許文献２に記載の転輪のように、円すいころ軸受とカラーの間へ皿ばねを設置する方法の場合、図６に特許文献２のFig４を示すが、円すいころ軸受４とカラー７の間に皿ばね２８が装着されている。この皿ばね２８のばね定数を弱くすれば、組立時の円すいころ軸受への過大な予圧力を防ぐことは出来るが、転輪が車両本体に取り付けられて、実際に使われた時の外部からの大きなアキシャル負荷により、皿ばね２８は大きく撓んでしまい、負荷を受けた円すいころ軸受の反対側の円すいころ軸受のアキシャル隙間が大きくなってしまう。逆に、皿ばね２８のばね定数を強くすれば、外部からの大きなアキシャル負荷に対する撓みを押さえることができるが、組立時に円すいころ軸受に過大な予圧力がかかることとなり、実際に使われた時に、軸受の発熱、低寿命化を招く恐れがあった。（本段落において用いた符号は、図６における符号であり、他の図の符号とは無関係である。） In the case of the method of installing the disc spring between the tapered roller bearing and the collar as in the rolling wheel described in Patent Document 2, FIG. 6 of FIG. 6 of FIG. 6 shows Tapered Roller Bearing 4 and Collar 7 The disc spring 28 is mounted between them. If the spring constant of this disc spring 28 is reduced, excessive preload on the tapered roller bearings can be prevented during assembly, but the rollers are attached to the vehicle body and from the outside when actually used The large axial load causes the disc spring 28 to be largely bent, and the axial gap of the tapered roller bearing on the opposite side of the loaded tapered roller bearing is increased. Conversely, if the spring constant of the disc spring 28 is increased, deflection against a large axial load from the outside can be suppressed, but an excessive preload is applied to the tapered roller bearing at the time of assembly, which makes it possible to actually use it. There was a risk that the bearing could generate heat and shorten its life. (The code used in this paragraph is the code in Figure 6 and has nothing to do with the code in the other figures.)
　また、特許文献３に記載の転輪のように、円すいころ軸受間へ規制部材を設置した従来技術の場合は、アキシャル隙間は構成部品の公差の累積となり、実際のアキシャル隙間の公差の巾が大きくなる恐れがある。一方、構成部品の公差を厳しくするとコストアップの恐れがあり、また公差を厳しくしない場合は、すきま管理が、ベアリングメーカの推奨から遠のいてベアリングの寿命低下を起こす恐れがあった。 Further, in the case of the prior art in which the restricting member is installed between the tapered roller bearings as in the rolling wheel described in Patent Document 3, the axial gap is a cumulative tolerance of the component parts, and the actual axial gap has a tolerance width of There is a risk of growing up. On the other hand, if the tolerances of the components are tightened, there is a risk of cost increase, and if the tolerances are not tightened, there is a risk that the clearance management may cause the life of the bearings to fall away from the bearing manufacturer's recommendation.
　本発明の実施例１の履帯式走行車両の転輪に依れば、円すいころ軸受のすきま管理において、シム調整のような高度の組立技術も不要であり、構成部品の寸法公差を厳しくする必要もなく、簡単な組立要領で、円すいころ軸受のアキシャル隙間を零に設定でき、しかも、その予圧力が過大にならないので、負のすきま量が大きくなることもなく、円すいころ軸受の疲れ寿命の低下を防ぐことを期待できる。また、アフターサービスにおいて再組立をする場合には、組立時に降伏した押し付け部材を反転して使えば、逆方向に降伏することにより再利用も可能である。本発明の実施例１の履帯式走行車両の転輪によれば、高速走行に対応する転輪に円すいころ軸受を使いながら、しかも組立の容易化を図ると共に、耐久性及び信頼性に優れる。本発明の実施例１の履帯式走行車両の転輪によれば、高度な調整なしに、ボルトを締めるだけで押し付け部材の撓み特性により、カラーから押圧である予圧力を必要十分に得ることが出来る。このボルトは締め付けても構わない。 According to the rolling wheels of the crawler type traveling vehicle of the first embodiment of the present invention, in the clearance management of tapered roller bearings, a high level assembly technique such as shim adjustment is not necessary, and the dimensional tolerance of components needs to be tightened. The axial clearance of the tapered roller bearing can be set to zero with no simple assembly procedure, and moreover, since the preload does not become excessive, the fatigue life of the tapered roller bearing can be reduced without increasing the amount of negative clearance. You can expect to prevent the decline. In addition, when reassembling in after service, it is possible to reuse by surrendering in the reverse direction by reversing and using the pressing member that has yielded at the time of assembly. According to the rolling wheels of the crawler type traveling vehicle of the first embodiment of the present invention, while facilitating assembly while using tapered roller bearings for the rolling wheels corresponding to high speed traveling, the durability and the reliability are excellent. According to the rolling wheels of the crawler type traveling vehicle of the first embodiment of the present invention, it is necessary to obtain the necessary and sufficient preload force from the collar by the deflection characteristics of the pressing member only by tightening the bolt without advanced adjustment. It can. This bolt may be tightened.
　なお、特許文献２の場合は、図６に特許文献２のFig４を示すが、円すいころ軸受４とカラー７の間の皿ばね２８を弱くすれば、円すいころ軸受への過大な予圧力を防ぐことが出来るが、皿ばね２８がカラー７よりシャフト１の中央部よりに配置されているため、実際に転輪が使われた時の実作業の外部からの大きなアキシャル負荷により皿ばね２８が撓んでしまう。（本段落において用いた符号は、図６における符号であり、他の図の符号とは無関係である。） In the case of Patent Document 2, FIG. 6 shows FIG. 4 of Patent Document 2. However, if the disc spring 28 between the tapered roller bearing 4 and the collar 7 is weakened, excessive preload on the tapered roller bearing is prevented. However, since the disc spring 28 is disposed closer to the central portion of the shaft 1 than the collar 7, the disc spring 28 is bent by a large axial load from the outside of the actual work when the wheel is actually used. I'm sorry. (The code used in this paragraph is the code in Figure 6 and has nothing to do with the code in the other figures.)
　ところが本発明の実施例１の履帯式走行車両の転輪では、転輪が履帯式走行車両に固定されて、図１において右方向にアキシャル負荷が作用したとすると、押し付け部材８５がシャフト１の軸端にある為、実際に転輪が使われた時の実作業の外部からの大きなアキシャル負荷は、ローラ２から円すいころ軸受１２に伝わり、更にカラー４に伝わるが、カラー４は履帯式走行車両本体（図示せず）に、ボルト（図示せず）によって固定されているので、カラー４からの外部からの大きなアキシャル負荷は履帯式走行車両本体に直接伝わり、押し付け部材８５には伝わらない。これにより特許文献２に記載の転輪の様な不都合は発生しない。これにより、組立の容易化を図ると共に、耐久性及び信頼性に優れた履帯式走行車両の転輪を提供できる。 However, in the rolling wheels of the crawler type traveling vehicle according to the first embodiment of the present invention, assuming that the rotary wheels are fixed to the crawler type traveling vehicle and axial load acts in the right direction in FIG. Because it is at the shaft end, large axial load from the outside of the actual work when the wheel is actually used is transmitted from the roller 2 to the tapered roller bearing 12 and is further transmitted to the collar 4, but the collar 4 travels with a crawler belt Since it is fixed to the vehicle body (not shown) by bolts (not shown), a large axial load from the outside from the collar 4 is directly transmitted to the crawler type traveling vehicle body and is not transmitted to the pressing member 85. As a result, such inconveniences as the rolling wheels described in Patent Document 2 do not occur. As a result, it is possible to provide a wheel of a crawler type traveling vehicle which is easy to assemble and which is excellent in durability and reliability.
｛実施例２｝
　次に本発明の他の実施例を以下に述べる。図３は、本発明の実施例２の履帯式走行車両の転輪の断面概略図である。図３は、本発明の実施例２の履帯式走行車両の転輪を示すが、シャフト１の両端は全周にわたって切欠きが無く、それ故、カラー３，４の円筒部がシャフト１の両端で全周にわたって肉厚を保持している。押し付け部材６１は円板状である。 {Example 2}
Next, another embodiment of the present invention will be described below. FIG. 3 is a schematic cross-sectional view of the wheels of the crawler type traveling vehicle of the second embodiment of the present invention. FIG. 3 shows the wheels of the crawler type traveling vehicle according to the second embodiment of the present invention, but both ends of the shaft 1 have no notch over the entire circumference, therefore the cylindrical parts of the collars 3 and 4 are both ends of the shaft 1 The wall thickness is maintained over the entire circumference. The pressing member 61 has a disk shape.
　図４は、本発明の実施例２の履帯式走行車両の転輪の右側詳細図である。図４は、図３に示した本発明の実施例２の履帯式走行車両の転輪の押し付け部材６１周辺部の詳細図である。図４における押し付け部材６１は図２における押し付け部材８５と同じ働きをする。 FIG. 4 is a right side detail view of the wheel of the crawler type traveling vehicle of the second embodiment of the present invention. FIG. 4 is a detailed view of the periphery of the pressing member 61 of the rotating wheel of the crawler traveling vehicle according to the second embodiment of the present invention shown in FIG. The pressing member 61 in FIG. 4 functions the same as the pressing member 85 in FIG.
　本発明の実施例２の履帯式走行車両の転輪の予圧手段８０は、押し付け部材６１とボルト６２とで構成され、押し付け部材６１はシャフト１の端面の直径より長い部分を有するので、円すいころ軸受け１１，１２に対して、軸方向のすきまを調整する予圧を、撓みの作用によって与える。ボルト６２を締めていくと押し付け部材６１はボルト６２の締め付け途中で降伏しており、ボルト６２を完全に締め付けても、過剰な押付荷重の発生を抑え、過大な予圧力の発生を防ぐことが出来る。 The preloading means 80 of the rotating wheels of the crawler belt type traveling vehicle according to the second embodiment of the present invention is constituted by the pressing member 61 and the bolt 62, and the pressing member 61 has a portion longer than the diameter of the end face of the shaft 1 A preload is applied to the bearings 11 and 12 to adjust the axial clearance by the action of deflection. When the bolt 62 is tightened, the pressing member 61 yields in the middle of tightening the bolt 62. Even if the bolt 62 is completely tightened, the generation of an excessive pressing load is suppressed and the generation of an excessive preload is prevented. It can.
　本発明の実施例２の履帯式走行車両の転輪によれば、高速走行に対応する転輪に円すいころ軸受を使いながら、しかも組立の容易化を図ると共に、耐久性及び信頼性に優れる。 According to the rolling wheels of the crawler type traveling vehicle of the second embodiment of the present invention, while facilitating assembly while using tapered roller bearings for the rolling wheels corresponding to high speed traveling, the durability and the reliability are excellent.
｛実施例３｝
　図５は、本発明の実施例３の履帯式走行車両の転輪の右側詳細図である。本発明の実施例３の履帯式走行車両の転輪は、シャフト１の、履帯式走行車両に装着したときに本体側になる側の端部（軸端）において、中央が膨らんだ（凸状の）段差部分が設けてあり、押し付け部材６１の代わりに座金７２と皿ばね状の中空円板７１を用いている点以外は上述した本発明の実施例２の履帯式走行車両の転輪と同じ構成である。皿ばね状の中空円板７１は、シャフト１の端部の直径より大きい内径を有しシャフト１の本体部の直径より大きい外径を有するドーナツ形状で、シャフト１の段差部分に嵌め込むことができる。皿ばね状中空円板７１には、ばね定数が所定の値より小さい材料を選択する。本実施例では、シャフト１に座金７２がボルト７３によって固定されている。カラー４と座金７２の間に、ばね定数が弱く変位量の大きな皿ばね状中空円板７１が組み込まれている。皿ばね状中空円板７１の初期状態は破線で示されているが、シャフト１に座金７２がボルト７３によって固定された状態でその撓みはL’となる。 {Example 3}
FIG. 5 is a right side detail view of the wheels of the crawler type traveling vehicle of the third embodiment of the present invention. The wheel of the crawler type traveling vehicle according to the third embodiment of the present invention has its center expanded at the end (shaft end) on the side which becomes the main body side when the shaft 1 is mounted on the crawler type traveling vehicle (convex And the wheel of the crawler type traveling vehicle according to the second embodiment of the present invention described above except that a stepped portion is provided and a washer 72 and a disc spring-like hollow disc 71 are used instead of the pressing member 61. It is the same composition. The disc spring-like hollow disc 71 may be in the form of a donut having an inner diameter larger than the diameter of the end of the shaft 1 and an outer diameter larger than the diameter of the main body of the shaft 1. it can. For the disc spring-like hollow disc 71, a material having a spring constant smaller than a predetermined value is selected. In the present embodiment, a washer 72 is fixed to the shaft 1 by a bolt 73. Between the collar 4 and the washer 72, a disc spring-like hollow disc 71 having a weak spring constant and a large displacement is incorporated. The initial state of the disc spring-like hollow disc 71 is shown by a broken line, but in a state where the washer 72 is fixed to the shaft 1 by the bolt 73, the deflection becomes L ′.
　本発明の第３の態様の履帯式走行車両の転輪は、本発明の実施例３の履帯式走行車両の転輪であって、端部において図５に示す構成を有するものである。 The wheel of the crawler type traveling vehicle according to the third aspect of the present invention is a roller of the crawler type traveling vehicle according to the third embodiment of the present invention, and has the configuration shown in FIG.
　本発明の実施例３の履帯式走行車両の転輪によれば、ばね定数が弱く、図５のL’寸法が構成部品の累積公差でL’１～L’o～L’２と変動しても予圧力が過大になることを防ぐことが出来る。その特性図を図７の（B)に示すが皿ばね状中空円板７１のばね定数が弱いので、撓みが図７に示すL'１～L’２に変動しても過大な押付荷重は発生しない。これにより、円すいころ軸受を使った転輪の組立の容易化を図ると共に、耐久性及び信頼性に優れた履帯式走行車両の転輪を提供できる。本発明の実施例３の履帯式走行車両の転輪によれば、高速走行に対応する転輪に円すいころ軸受を使いながら、しかも組立の容易化を図ると共に、耐久性及び信頼性に優れる。本実施例によれば、皿ばね状中空円板７１のばね定数が低いため、撓みによる過大な押付荷重は発生しない。 According to the rolling wheels of the crawler type traveling vehicle of the third embodiment of the present invention, the spring constant is weak, and the L 'dimension in FIG. 5 varies from L'1 to L'o to L'2 in cumulative tolerance of components. However, excessive preload can be prevented. The characteristic diagram is shown in (B) of FIG. 7, but since the spring constant of the disc spring-like hollow disc 71 is weak, the excessive pressing load is not obtained even if the deflection fluctuates from L'1 to L'2 shown in FIG. It does not occur. As a result, it is possible to facilitate the assembly of the rotating wheel using the tapered roller bearing, and to provide the rotating wheel of a crawler type traveling vehicle excellent in durability and reliability. According to the rolling wheels of the crawler type traveling vehicle of the third embodiment of the present invention, while facilitating assembly while using tapered roller bearings for the rolling wheels corresponding to high speed traveling, the durability and the reliability are excellent. According to this embodiment, since the spring constant of the disc spring-like hollow disc 71 is low, the excessive pressing load due to the deflection does not occur.
　本発明の実施例３の履帯式走行車両の転輪の予圧手段８０は、座金７２と皿ばね状の中空円板７１とボルト７３とで構成される。座金７２と皿ばね状の中空円板７１とは、シャフト１の端面の直径より長くシャフトの本体部の直径より短い直径である座金７２の裏面が、シャフトの本体部の直径より長い外径の皿ばね状の中空円板７１の表面に接触するように設けてある。したがって、座金７２と皿ばね状の中空円板７１とボルト７３とで構成される予圧手段８０は、円すいころ軸受け１１，１２に対して、軸方向のすきまを調整する予圧を、撓みの作用によって与えると共に、ボルト７３を締めていく際でもばね定数が小さいため過剰な押付荷重の発生を抑え、過大な予圧力の発生を防ぐことが出来る。このボルトは締め付けても構わない。 The preloading means 80 of the rotating wheel of the crawler belt type traveling vehicle of the third embodiment of the present invention is constituted by a washer 72, a disc-shaped hollow disc 71 and a bolt 73. The washer 72 and the disc spring-like hollow disc 71 have a diameter which is longer than the diameter of the end face of the shaft 1 and shorter than the diameter of the main body of the shaft. It is provided to be in contact with the surface of a disc spring-like hollow disc 71. Therefore, the preloading means 80 composed of the washer 72, the disc-shaped hollow disc 71 and the bolt 73 is used to deflect the preload for adjusting the axial clearance of the tapered roller bearings 11 and 12 by the action of deflection. Since the spring constant is small even when the bolt 73 is tightened, generation of excessive pressing load can be suppressed and generation of excessive preload can be prevented. This bolt may be tightened.
　なお、本発明の第４の態様の履帯式走行車両の転輪は、図３に一例を示すものであり、カラー４に、カラー４とシャフト１との間のずれを防止する手段としての止めねじ６３を備えている。一方、カラー３，４は履帯式走行車両本体（図示せず）に、ボルト（図示せず）によって各々固定されている。通常、カラー３、４が固定されている車両本体の各々の取付け部の横方向の剛性は充分強いが、本例によれば、個別では取付け部の横方向の剛性が弱い場合でも、シャフト１による連結が全体の剛性強化に有効である。このような車両本体に対しては、車両本体の転輪取付け部の横方向の変形の防止に貢献し、転輪の耐久性を確保できる。 The wheel of the crawler type traveling vehicle according to the fourth aspect of the present invention is an example shown in FIG. 3, and the collar 4 is a stopper as a means for preventing deviation between the collar 4 and the shaft 1 A screw 63 is provided. On the other hand, the collars 3 and 4 are fixed to a crawler type traveling vehicle main body (not shown) by bolts (not shown). Normally, the lateral rigidity of the mounting portion of each of the vehicle bodies to which the collars 3 and 4 are fixed is sufficiently strong, but according to the present embodiment, the shaft 1 can be used individually even if the lateral rigidity of the mounting portion is weak. Connection by is effective in strengthening the entire rigidity. Such a vehicle body contributes to the prevention of lateral deformation of the wheel mounting portion of the vehicle body, and the durability of the wheel can be secured.
　なお、図６は、本発明の実施例ではなく従来技術を示す図であって、米国特許４６４０５５９号公報のFig４である。図６の中に示された符号は、本出願の他の図で用いた符号とは無関係である。下記に示す符号の説明は、図６以外で用いた符号についての説明である。また、図７は、押付荷重―隙間線図である。図７（Ａ）が本発明の実施例１及び実施例２における押付荷重―隙間線図、図７（Ｂ）が本発明の実施例３における押付荷重―隙間線図である。 FIG. 6 is a view showing a prior art, not an embodiment of the present invention, which is FIG. 4 of US Pat. No. 4,640,559. The symbols shown in FIG. 6 are independent of the symbols used in the other figures of the present application. The description of the reference numerals shown below is the description of the reference numerals used other than FIG. FIG. 7 is a pressure load-gap diagram. FIG. 7A is a pressing load-gap diagram in Example 1 and Example 2 of the present invention, and FIG. 7B is a pressing load-gap diagram in Example 3 of the present invention.
　なお、本発明は、上記実施の形態に限定されず、その発明の趣旨を逸脱しない範囲で種々と変形実施が可能である。また、上記各実施の形態の構成要素を発明の趣旨を逸脱しない範囲で任意に組み合わせることができる。 The present invention is not limited to the above embodiment, and various modifications can be made without departing from the scope of the invention. Further, the components of the above-described embodiments can be arbitrarily combined without departing from the spirit of the invention.
１　　　シャフト
２　　　ローラ
３　　　カラー
４　　　カラー
５　　　ピン
６　　　止め輪
１１　　円すいころ軸受
１２　　円すいころ軸受
１３　　アウターレース
１５　　アウターレース
１４　　インナーレース
１６　　インナーレース
１７　　ころ
１８　　ころ
１９　　アウターレースの端面
２０　　アウターレースの端面
２１　　インターレースの端面
２２　　インターレースの端面
３１　　カラーの端面
３２　　カラーの端面
３３　　ローラ内径部の端面
３４　　ローラ内径部の端面
４１　　フローティングシール
４２　　フローティングシール
４３　　Ｏリング
４４　　Ｏリング
４７　　Ｏリング
４８　　Ｏリング
４５　　シール
４６　　シール
４９　　シール
５０　　シール
５１　　Ｏリング
５２　　Ｏリング
６１　　押し付け部材
６２　　ボルト
６３　　止めねじ
７１　　皿ばね状中空円板
７２　　座金
７３　　ボルト
８０　　予圧手段
８１　　内筒
８２　　内筒
８３　　Ｏリング
８４　　Ｏリング
８５　　押し付け部材
９０　　油溜り
９１　　栓
９２　　穴
９３　　穴 Reference Signs List 1 shaft 2 roller 3 color 4 color 5 pin 6 snap ring 11 tapered roller bearing 12 tapered roller bearing 13 outer race 15 outer race 14 inner race 16 inner race 17 roller 18 roller 19 roller 19 outer race end face 20 outer race end face 21 interlaced End face 22 Interlaced end face 31 Collar end face 32 Collar end face 33 Roller inner diameter end face 34 Roller inner diameter end face 41 Floating seal 42 Floating seal 43 O ring 47 O ring 48 O ring 48 O ring 45 Seal 46 Seal 49 Seal 50 Seal 51 O-ring 52 O-ring 61 pressing member 62 bolt 63 set screw 71 disc spring shaped hollow disc 72 washer 73 bolt 80 preloading means 81 inner cylinder 82 Cylinder 83 O-ring 84 O-ring 85 pressing member 90 oil reservoir 91 plug 92 hole 93 hole

Claims (4)

  1. 履帯式走行車両の一部を構成する転輪であって、ローラと、シャフトと、両端に設置されたシール手段と、カラーを備え、左右に配置された軸受手段がシャフトに外嵌される一対の円すいころ軸受により構成される構造において、上記円すいころ軸受及び上記シール手段が装着された状態で、上記円すいころ軸受の軸方向すきまを調整する予圧手段が上記シャフトの軸端に設置され、かつ、上記予圧手段が押し付け部材の撓みによる力で上記カラーを上記円すいころ軸受のインナーレース端面方向に押し付けることより、予圧力を与える構造であることを特徴とする履帯式走行車両の転輪。 A pair of rolling wheels constituting a part of a crawler traveling vehicle, comprising a roller, a shaft, sealing means provided at both ends, and collars, and bearing means provided at the left and right are externally fitted to the shaft In the structure constituted by the tapered roller bearing, preloading means for adjusting the axial clearance of the tapered roller bearing is installed at the shaft end of the shaft in a state where the tapered roller bearing and the sealing means are mounted, and A roller wheel of a crawler belt type traveling vehicle, wherein the preloading means is configured to apply a preload pressure by pressing the collar toward the inner race end face of the tapered roller bearing by a force of deflection of a pressing member.
  2. 上記予圧手段が上記カラーを上記シャフトの中央方向に押し付ける押し付け部材と、上記押し付け部材を上記シャフトの軸端に押し付ける為の固定部材とからなり、上記押し付け部材が撓むことによる力で上記カラーを上記シャフトの中央方向に押して、上記円すいころ軸受に予圧力を与える構造において、上記押し付け部材が上記シャフトの軸端に押し付けられて、必要な予圧力が発生する近傍において、上記押し付け部材の撓みによる応力が降伏応力、または耐力に達することを特徴とする履帯式走行車両の転輪。 The preloading means comprises a pressing member for pressing the collar in the central direction of the shaft, and a fixing member for pressing the pressing member against the axial end of the shaft, and the collar is moved by the force of the pressing member being bent. In the structure for applying a pre-load to the tapered roller bearing by pushing in the central direction of the shaft, the pressing member is pressed against the shaft end of the shaft to generate a necessary pre-pressure due to the deflection of the pressing member. A rolling wheel of a track type traveling vehicle characterized in that a stress reaches a yield stress or a proof stress.
  3. 上記予圧手段が上記カラーを上記シャフトの中央方向に押し付ける押し付け部材と、上記押し付け部材を上記シャフトの軸端に押し付ける為の固定部材とからなり、上記押し付け部材が撓むことによる力で上記カラーを上記シャフトの中央方向に押して、上記円すいころ軸受に予圧力を与える構造において、上記押し付け部材が、皿ばね状の中空円板からなり、撓んだ時の撓みによる応力が弾性限度内にあることを特徴とする請求項１記載の履帯式走行車両の転輪。 The preloading means comprises a pressing member for pressing the collar in the central direction of the shaft, and a fixing member for pressing the pressing member against the axial end of the shaft, and the collar is moved by the force of the pressing member being bent. In the above-described tapered roller bearing, wherein the pressing member is formed of a disc-like hollow disk, and the stress due to bending when it is bent is within the elastic limit. The wheel of a crawler type traveling vehicle according to claim 1, characterized in that
  4. 上記予圧手段が設置されている側の上記カラーに、上記カラーと上記シャフトとの間のずれを防止する手段を設置することを特徴とする請求項１から請求項３のいずれかに記載の履帯式走行車両の転輪。 The crawler belt according to any one of claims 1 to 3, characterized in that means for preventing deviation between the collar and the shaft is installed in the collar on the side where the preloading means is installed. Wheels of a traveling vehicle.
PCT/JP2015/077911 2014-11-13 2015-10-01 Rolling wheel for crawler type traveling vehicle WO2016076027A1 (en)

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US10023251B2 (en) 2016-06-24 2018-07-17 Caterpillar Inc. Track roller assembly and method
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