Saturday, 3 August 2013

Rear Wheel Bearing Change

Rear Wheel Bearing Change


I purchased a new rear wheel bearing kit which also included the axle bolt. For the B5 S4 ('00-'02), there are two different sets of possible front uprights. The early '00s had aluminum and after that they were changed to cast iron. The cast iron ones have press in bearings as seen below, while the aluminum ones come in a housing which bolts to the upright. I don't know if the rear uprights also differ like the front ones.
For the iron uprights, the P/Ns I used are:
Front Kit: 8D0598625A
Rear Kit: 4B0498625A
Note: always confirm P/Ns for your car.

In this photo, the front kit has the green bearing with the larger M16 bolt, while the rear kit is orange with the M14 bolt.



For the rear wheel axle bolt, you will need a 14mm allen / hex-bit socket. (FYI - the front requires a 17mm)



An 18" breaker bar is the minimum needed to remove/replace this bolt:



I've added a 38" black steel pipe to my breaker bar for more leverage in order to achieve the tightening torque spec (85ft-lbs +180deg for the rear, 105(?)ft-lbs +180deg for the front)



1.) Break the axle bolt free while the wheel is still on the ground:



1.) As said above, do this while the wheel is on the ground - this photo is just for illustration of bolt:



2.) Jack up car, put on jack stand, remove wheel

3.) Using a 15mm open end, hold the support nut in place while removing the 13mm bolt at the top of the brake caliper:



4.) Do the same for the bottom bolt:



5.) Remove the brake caliper and move out of the way:



6.) Remove the two 8mm allen bolts that hold the brake caliper bracket to the upright (note you can perform step #11 now if you need room due to that suspension link):



6.) Extra photo of this step:



7.) With the top bolt out and the bottom one loose, the rotor can be removed. Continue and remove the bottom bolt completely and remove bracket:



8.) Remove three 10mm bolts holding in splash guard, & also remove splash guard:



9.) Use 4mm(?) allen / hex-bit to remove retaining bolt holding in ABS sensor, then remove sensor as well.



10.) Using 19mm wrench, remove nut on control arm connection. Just remove the nut, you likely won't be able to separate the arms:



11.) Use two 17mm wrenches to remove the bolt through this suspension link:



12.) Use two 19mm wrenches to remove this bolt at the top control arm:



13.) At this point, you can remove the drive shaft from the upright. I supported it with a bungee cord so it was up and out of my way:



14.) Take note of how the brake lines run around the suspension arms. Be sure to put this back this way when you reassemble, otherwise you'll have to disassemble again. Also note that by raising the drive shaft, I now have room to bang on that lower right control arm which is a pain to separate. We're not doing that yet though, as it will be easier later...



15.) Using two 19mm wrenches, remove this camber alignment bolt. Note that the washers are aligned to the bolt and do not spin freely, so don't try. It would be a good idea to mark the washer it's orientation so that you can put it back at the same rotation. You'll likely need an alignment after
removing this, but you can at least try to get it back as close to how it was before.:



16.) After removing the above bolt, you can now remove the upright as well. It will still be connected by the lower right control arm, but now there won't be as much pressure on that connection. A whack or two with a mallet will free that connection which is held together by a tapered friction connection.

Success!



Now let's work on the bearing...



In this photo you can see in the center is the spline section which is part of the hub. Along the outer edge of the bearing you can see the cast iron lip - the bearing is pressed in from the other side (outside) and stops at this lip. So when we press out the bearing, we'll press from this side:



A zoomed-out shot of above:



17.) First we will press out the hub from the bearing. There's less friction here than between the bearing and the upright, so we can just support the upright when pressing out the hub:



Close up:



Photo just to show progress of hub being pressed out:



You'll most definitely end up with the bearing separating when complete:



Here you can notice that there's a wide outer rim of shiny bearing housing which further illustrates the lip which is on the other side - thus the bearing comes out in this direction. Also note that the bearing is recessed about 1/4 inch from this outside edge:



18.) Since there is that 1/4" of space where the bearing can move, we'll first place the upright on a flat surface. We're going to need to exert the most effort to initially break the bearing free, so thus the flat surface will give us the most stability:



Once it breaks free, we look and see that sure enough it moved downwards about 1/4", now revealing a space below the lip:



19.) Now we change our support to the outer sides, so we can press the bearing through:



Success!



Old vs New:



20.) We still need to remove the part of the bearing that was stuck to the hub, so we place the hub in a vice and separate the two by hitting the joint with a chisel:



Starting to come apart:



Apart!



Note that the hub has a stepped diameter, wider at the outside (towards wheel) and narrower at the inside. The bearing has corresponding diameters. It is very important to note this now so that when inserting the bearing you press it in, in the correct orientation:



And thus, the bearing presses in with the wider diameter facing out as shown here:



21.) The rear uprights are an awkward shape, so you may have to be creative to how you support the bottom when pressing in the bearing. The round disk I am using here directly supports that face of the upright. Be sure to use a flat surface when pressing the bearing - do not apply force directly to the center of the bearing as you will likely damage it.
Note: Some have suggested putting your new bearing in a freezer for a day and/or heat the upright - this should make insertion easier. Also, you may desire to lube the bearing/upright mating surface as well.



22.) Once the bearing is almost all of the way in, you'll need to press it in that extra 1/4" and you can't do that with a big flat plate on top. Instead, use the old bearing and stack that on the new one and then press on the old one. You'll end up pressing the old one in as well, for that 1/4" distance. Once you've done that, you can bang off the old one with a hammer as it's only partially inserted:



Confirming from the other side (inside), we see that the bearing was pressed all the way to the lip:



23.) Now we will press in the hub into the bearing. This time, it is vital to support the center of the bottom of the bearing (inner section). If we only support the upright, when we press in the hub it will blow apart the bearing similar to when we pressed out the hub. It's hard to distinguish in this photo, but my round disks underneath are only touching the bearing center, not any part of the upright.



That's it, now go put everything back together. Take your time to note the order you took things apart, so you don't have to do things twice. ie, don't forget the splash guard goes on before the rotor, be sure to put the brake caliper lines around the suspension links appropriately, etc.

Before putting on the wheel, I put in the axle bolt and tightened it just slightly snug with a wrench so the drive shaft was fully seated. I then put on the wheel, lowered the car to the ground, and tightened the axle bolt to the insane spec. With the 3' bar, I was able to achieve the 180deg.

HONDA CAM BEARING CONVERSION

HONDA CAM BEARING CONVERSION

Inspired by drturnip’s article on his low-cost alternative to the Honda single cylinder cam bearing problem, here http://www.thumperta...ad.php?t=819229, this is the story of my solution to the same problem, done before reading drt’s excellent article.

I acquired an early CB125 motor which would run ok at lower revs but was stuttering once the revs got up.  As opposed to the usual problem of the head bearings being burnt out, these were measured using manufactured go/no go plug gauges at 20.01 / 30.01.

The problem was traced to wear on the camshaft journals, 19.82 at the small end, 29.88 at the bigger end as opposed to 19.93/29.93 measured as new.  This was causing an end float of 0.3mm at the points cam, hence the running problems.

As NOS camshafts were coming in at about £75 / $120, I set about re-engineering the camshaft bearings.

Judging by the bearings that I saw on other camshafts, not knowing the loadings, and being a marine engineer where overkill is good, I didn't think that a thin bearing would be able to take the load.  Thus, I made an outrigger bearing holder with circlip for a 6004 bearing (20/42/12) to go between the head and points housing. 

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Once the alloy bearing holder was turned up (0.04mm undersize to allow for expansion) and fitted to check the axial clearance to the cam sprocket bolts, I turned up spigoted bushes for either side of the bearing to take the load onto the 15mm spigot and the 10mm camshaft points extension.  The outer of these 2 bushes was grooved on the internal bore for an O-ring to stop oil creeping along the shaft into the points housing (groove in yellow part). 

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The outer face of this bush acts as the running face for the points housing seal.  The bearing holder spigot into the head and points housing to bearing holder are sealed with the normal O-ring. The camshaft small end was left ‘as found’ as I didn’t want to machine a good head.

An extension was then made and turned concentric to the camshaft to take the advance retard unit, then drilled to take the ‘knock pin’ which locates it.

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A lot of work was involved measuring up to get the whole lot as narrow as possible (it's about 23mm wide), to seal the shaft where it comes through the bearing and to get the correct axial location of the camshaft once all tightened up. The whole lot is secured from moving by the circlip in one direction and the advance retard securing bolt in the other direction.

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Causes of Bearing Failures

Causes of Bearing Failures

There are many possible causes of bearing failures, and most times factories do produce bad bearings without much warning. Companies that observe the highest level of quality control for their facilities have a greater chance of eliminating such failures than those that lack proper maintenance practices.
Manufacturing defects are the most common cause of bearing failures this is because all bearings actually have some kinds of defects. But when they are graded accordingly, these defects can be remedied. The highest quality bearings are easily distinguished from the lowest quality ones through their degree of defects.
Further research and analysis have resulted in the conclusion that these defects do not cause too much harm that may lead to major bearing failures. Other major causes of failures in bearings include: contamination, which may be due to moisture; lack of lubrication; and over stress.

Benefits of Vibration Analysis

Pile-of-bearingsVibration analysis allows companies to effectively monitor and detect defects of bearings before more damage can occur. Thus, benefit of its use is being able to save a lot of money. When machine bearing failure is detected earlier, corrective maintenance to the machinery can be done prior to occurrence of possible disasters.
Therefore, purchase of vibration equipment to be used during routine plant maintenance is a very important factor to be considered by every manufacturing company.
Understanding and evaluation of machinery vibration is a complex process but it can be very beneficial for predictive maintenance practice.

How Vibration Analysis Works

Rotating equipment and machinery vibrate to some extent. Units with older bearings have higher chances of vibrating more dramatically and every vibration can be very distinct. Continuous equipment monitoring and evaluation allows the plant technicians to recognize and identify early wear and tear signs before further damage occurs.
Vibration Analysis is the technique used to identify early sign of machine failure, which allows machinery and equipment to be either repaired or replaced prior to expensive and destructive failure occurrence. Vibration analysis equipment uses sensors like tachometers and accelerometers in effectively monitoring of possible occurrence of bearing failures.

Traditional Maintenance Techniques versus Vibration Analysis

Tradition methods for machinery maintenance can be predictive wherein the components of equipment units are replaced regularly on a fixed schedule whether they are worn or still working.
Traditional maintenance can also be reactive, wherein equipment unit components are repaired after a break down.
In this modern time, these two types of traditional maintenance techniques are no longer ideal and acceptable. Although they are still used across many heavy industry businesses, some of the newly operational companies and manufacturing plants are now making use of modern techniques such as vibration analysis.
The reason the use of vibration analysis has become very popular is because is allows companies to prevent bearing failures long before they can happen. Bearing monitoring has become a significant part of manufacturing system maintenance and this is the main job of vibration analysis. As soon as abnormal vibrations have been detected, technicians and plant managers can start formulating the best possible solutions. The bearing can be repaired or replaced; either one will be a cost-effective alternative to complete unit repair or replacement.


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Lubrication grooves and holes

 

Lubrication grooves and holes

Spherical roller bearings are provided with a lubrication groove and holes in the outer ring, excepting those of series 213. Designation suffix W33 is used to identify this feature on bearings. The dimensions of the groove, bore diameter and their number depending on the dimension series are given in table 5.
 

Heat treatment

Spherical roller bearings with outside diameter D>240 mm of all series given in this catalogue are stress revealed. Therefore, they can be used up to an operating temperature of +200?C.The hardness of the rings should not be lower than 59 HRC. Small sized bearings operate normally at temperatures up to +120?C.
 

Axial load for bearings mounted on adapter sleeves

If the spherical roller bearings are mounted on a smooth shaft using an adapter sleeve, without side support, the axial load carrying capacity depends on the friction be-tween shaft and sleeve.
Considering that the mounting is correctly done, the permissible axial load can be accurately enough deter-mined using the following equation:
Fa max = 3 Bd, kN
where:
Fa max - maximum permissible axial load, kN,
B - bearing width, mm,
d - bearing bore diameter, mm.
 
 

Equivalent dynamic radial load

Pr = Fr + Y1Fa, kN,   for Fa/Fr <=e,
Pr = 0,67 Fr + Y2Fa, kN,  for Fa/Fr >e,
The values of the factors depending on the bearing type can be found in bearing tables
 

Equivalent static radial load

P0r = Fr + Y0Fa, kN
The value of the factor Yo depending on the bearing type can be found in bearing tables.
 

Abutment dimensions

For a proper location of bearing rings on the shaft and housing shoulder respectively, shaft (housing) maximum connection radius ru max should be less than bearing minimum mounting chamfer rs min.
Shoulder height should also be properly sized in case of bearing maximum mounting chamfer.
The values of the connection radii and support shoulder height are given in table 6.
 
 
The mounting dimensions for bearings with withdrawal sleeves are given in table 7.
 
 



Bearing Detals

 

Spherical roller bearings

Spherical roller bearings operate in arduous condi-tions. The spherical rollers can be symmetrical or unsym-metrical and are self-aligning in the outer ring sphered raceway. Thus, the possible coaxiality deviations of the supporting bearings as well as shaft bending can be compensated.
Spherical roller bearings are manufactured in the following constructive versions, depending on the bearing size and series:
 

Spherical roller bearings

d D B rs min Cr e Y1 Y2 Cor Y0 grease oil designation weight
25 52 18 1 43 0.35 1.9 2.9 43 1.8 7500 10000 22205 C 0.18
25 52 18 1 43 0.35 1.9 2.9 43 1.8 7500 10000 22205 CK 0.18
25 52 18 1 43 43 7500 10000 22205 C A
25 52 18 1 43 0.35 1.9 2.9 43 1.8 7500 10000 22205 CK W33 0.18
30 62 20 1 59 0.36 1.9 2.8 62 1.9 6300 8500 22206 C 0.28
30 62 20 1 59 0.36 1.9 2.8 62 1.9 6300 8500 22206 CK 0.28
30 62 20 1 59 0.36 1.9 2.8 62 1.9 6300 8500 22206 CK W33 0.28
30 62 20 1 59 62 6300 8500 22206 C A
35 72 23 1.1 81 0.36 1.9 2.8 88 1.9 5300 7000 22207 C 0.43
35 72 23 1.1 81 0.36 1.9 2.8 88 1.9 5300 7000 22207 CK 0.43   
 
 

Bearing

Basic Design:
The tapered roller thrust bearings are produced with the logarithmic contact profile between raceways and rollers to guarantee optimum stress distribution in the bearing, thus enhancing bearing life.
Detailed Description:
• Series: 617500, 353153, 353115, 353116, 353106, 351182 and so on
• Available with cage or full complement of rollers
• This type bearings enable axially very compact bearing arrangements to be produced which can carry very heavy axial loads, are insensitive to shock loads and are stiff
• Types: Single direction taper roller thrust bearing, double direction taper roller thrust bearing, screws-down taper roller thrust bearing
• Typical Applications: kingpin bearing arrangement of commercial vehicles, oil well swivels, crane hooks, pulp refiners, extruders, piercing mills, vertical boring mills, vertical grinding machines, rolling mil applications, and so on.
Bearing Features:
• Compact bearing arrangements
• Heavy axial loads
• Increased bearing life
• Optimum stress distribution in the bearing
• A variety of industrial applications