Map the damper before you tune it
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Course: Design suspension geometry that actually wins races
Module: Look inside the damper
Estimated duration: 52 minutes
The job of damper mapping is to stop guessing.
Before you soften rebound because the car feels nervous, before you add compression because the nose moves too much, and before you blame the knob because the car is slow over a curb, you need to know what the damper is actually doing. A damper is not good or bad in isolation. A damper that is perfectly sound on the bench can still be wrong for the vehicle, the installation, the surface, the temperature, and the phase of the corner you are trying to improve. That is the central rule of this lesson: characterize the damper and its operating environment before you tune it.
This lesson sits inside damper internals and construction, so the focus is not how to choose a twin-tube, single-tube, reservoir, or separator-piston architecture from scratch. That is the neighboring architecture lesson. It is also not a full shim-stack design lesson, and it is not the heat-management lesson. Your task here is narrower and more practical: build a usable map that connects the damper force-velocity behavior, the suspension motion ratio, the vehicle events that create damper speed, and the on-track symptoms you are trying to change.
The principle: the damper is only meaningful in context.
The damper responds to relative motion. The vehicle does not care about the knob label. It cares about the force that reaches the suspension and the tire during the event that is happening: a road input, a braking pitch transient, a throttle pitch transient, a roll transient at corner entry or exit, a combined event, or an extreme rough-track condition. Dixon separates the estimation of suspension bump velocity into drop tests, ride motions, longitudinal acceleration transients, lateral acceleration transients, combined effects, and damper failure speeds. That list is a useful mental framework because it keeps you from treating all damper motion as one thing.
The wheel bump speed is not automatically the damper speed. The vehicle motion defines suspension wheel bump speed, but the actual damper velocity depends on the installation geometry and the damper-to-wheel motion ratio. On a simple installation the ratio may be fairly steady. On a racing car, the linkage may deliberately make the velocity ratio rise rapidly with bump. When that rising-rate linkage acts on the spring it increases wheel rate with bump; when it acts on the damper it produces rising-rate damping. If the spring and damper are coaxial, the same motion ratio commonly affects both, which can make the wheel damping coefficient rise with wheel rate. That means the same bench curve can behave differently at the wheel depending on how the damper is installed.
This is why a damper dyno plot by itself is not a setup answer. It is a component map. You still have to ask where the car operates on that map. You also have to ask whether the map is stable enough, repeatable enough, and appropriate enough for the vehicle. Dixon is blunt about the hierarchy: the ultimate test of a damper is on the vehicle. Laboratory testing remains essential, but a good component can fail the vehicle test if it is unsuitable for that car.
For a track-day, HPDE, or club-racing driver, this has a practical meaning. You do not map the damper because you want a prettier graph. You map it because dampers influence traction and tire grip, and in racing they influence the fore-aft distribution of lateral load transfer during body roll at corner entry and exit. Those are transient-handling effects, not just ride-comfort effects. If the car is lazy to take a set, abrupt as you release the brake, reluctant to put power down, or unstable over a rough patch, the damper may be involved. But without a map you do not know whether you are changing the event that actually matters.
What a useful damper map contains.
A useful map has four layers. The first layer is the hardware identity. You need to know the configuration of the damper: single-tube or double-tube, whether it has a floating gas-separator piston, whether it uses a remote reservoir, and whether it is built for easy rebuilding or altered characteristics. Modern racing dampers can be complex hydraulic devices with remote reservoirs, free-floating pistons, internal adjustment spindles, and sealed assemblies intended to allow changes. Those details are not trivia. They affect what can be adjusted, rebuilt, cooled, serviced, and trusted.
The second layer is the force-velocity characterization. Dixon refers to the F(V) curve as an object whose accuracy and predictability can matter enough in high-grade racing and rally applications to justify cost. That curve is the controlled laboratory statement of what force the damper produces at a given damper velocity. For tuning, you care about both directions of motion. Compression and rebound do different work in the vehicle, and dampers are commonly asymmetric. The asymmetry is not something to explain with one folk story. Dixon lists multiple possible contributors to rebound-compression asymmetry, including tire behavior over large deflections, bump-trough asymmetry in the road, passenger sensitivity, internal construction, tire enveloping, and manufacturing cost. The mapping mindset is to record the asymmetry, then test its vehicle effect, not to assume that one side of the curve is correct because a paddock saying made it sound correct.
The third layer is the installation map. You translate vehicle motion into damper motion through the motion ratio. If the damper velocity ratio changes with position, you record that too. On cars with pushrods and rockers, the linkage is not just packaging. It can separate heave from roll, and in strong-aero cars a heave-only center unit can be used so heave springing and damping can be adjusted without altering roll and load-transfer characteristics. That matters because aero-sensitive cars are ride-height-sensitive. The damper map has to tell you not only what the damper does on the bench, but also what part of the car motion it is attached to.
The fourth layer is the use-case map. You identify the vehicle events the damper must handle: low-amplitude ride inputs, pitch changes during acceleration and braking, roll velocity during corner entry and exit, combined motion, rough-track operation, and possible failure-speed conditions. For an HPDE car, the map may be built around repeatable braking zones, corner-entry balance, exit traction, and known rough sections. For a club-racing car, minimum lap time dominates the test goal, but ride still matters because poor ride can fatigue the driver and degrade performance in longer runs. For a rally car, rough-road temperature and aeration risks can dominate the damper requirement. The same damper curve does not have the same meaning in all three situations.
A map is not a pile of data. It is an interpretation tool.
If you have only the dyno curve, you can say what the component did in the lab. If you have only driver notes, you can say what the car felt like. If you have only the motion ratio, you can say how wheel motion becomes damper motion. The map is the connection between those things. It lets you say: this symptom happens in this vehicle event, that event produces this region of damper velocity after motion-ratio translation, the damper has this force behavior and asymmetry in that region, and the on-car test confirms or rejects the change.
That is the difference between tuning and knob-chasing.
Technique: build the map in order.
Start with the question you are trying to answer. Do not begin with the adjuster. Begin with the vehicle problem. Is the car poor over low-amplitude surface roughness? Is it hard to trust during brake release and turn-in? Does it lose traction as power is applied? Does it become worse on a rough surface late in a session? Is the issue a minimum-lap-time issue, a driver-fatigue issue, a durability issue, or some combination? Dixon separates public-road tests into ride, handling, and durability purposes. Racing track testing is more concerned with lap time, but handling and ride still interact. Your map should preserve that distinction.
Next, identify the damper hardware and configuration. Record whether the damper is single-tube or double-tube, whether it has gas separation, whether it has a reservoir, and what adjustment or rebuild paths exist. If the damper is a precision racing or rally component, the accuracy and predictability of the F(V) curve may be part of the reason it is expensive. If the vehicle is a less critical or lower-budget application, do not write a technical specification that is more demanding than the vehicle requires. The map is not a shopping list for the most sophisticated damper; it is a way to align the damper specification with the job.
Then create the laboratory characterization. The corpus here does not give a full shock-dyno operating procedure, so do not invent one. The grounded requirement is simpler: obtain the damper force-velocity behavior you intend to tune from. If the damper has settings or rebuild states you will actually use, those states belong in the characterization. If the damper is intended to be altered by rebuilding, the baseline curve is still the starting point. Record compression and rebound separately. Record whether the curve is smooth, predictable, and repeatable enough to trust. Record whether the forces are consistent with the intended application. The point is not to worship the graph; the point is to know what physical behavior you are putting on the car.
After that, translate the curve through the installation. You need the damper velocity for the vehicle event, not just the wheel bump velocity. Dixon gives the relationship in concept: vehicle motion defines suspension wheel bump speed, and the installation geometry determines the velocity ratio between damper and suspension bump speed. If the suspension is rising-rate, the translation changes with position. For an intermediate driver or club racer, this is often the missed step. The damper was tested as a damper, but the car uses it through a linkage. A small change in linkage behavior can shift the relevant part of the force-velocity curve.
Now classify the operating events. A single lap contains several damper jobs. Road roughness is not the same as brake pitch. Brake pitch is not the same as roll velocity at turn-in. Turn-in is not the same as exit roll recovery. Combined events happen when the car is braking and turning, or turning and accelerating, or landing on an uneven surface while loaded. Dixon's categories are useful because they prevent a vague complaint from becoming a vague change. If the driver says the car is harsh everywhere, you ask whether the issue is ride over roughness, a pitch transient, or a roll transient. If the driver says the car is loose on entry, you ask whether the symptom appears during braking, brake release, initial steering, or steady cornering.
Finally, compare laboratory, installation, and track results. Road and track testing are not ceremonial. Dixon treats damper testing in the laboratory and on the road as permanently essential, even as simulation improves. The test driver should notice ride motion over different surfaces, peculiar behavior on particular surfaces, and behavior under particular conditions such as very high or very low ambient temperature. Special handling tracks use curves of various radii on good surfaces. Special rough tracks deliberately challenge reliability, ride, and handling. Racing-car testing aims at minimum lap time, but it still has to account for tire grip, traction, transient balance, aero ride-height sensitivity, and driver fatigue. Your damper map is complete only when it can explain what changed on the car.
Sub-skill one: separate wheel speed from damper speed.
The beginner error is to think the wheel and damper move the same way. They often do not. The damper is attached through suspension geometry, and that geometry decides how fast the damper moves for a given wheel motion. When the motion ratio changes through travel, the damper may see a different velocity relationship at different positions. In a rising-rate racing suspension, this is intentional. The linkage can produce an increasing velocity ratio with bump, which changes the wheel damping behavior without requiring a position-dependent damper. That is why a damper that looks mild on the bench can become stronger at the wheel in a particular travel range.
Practice this sub-skill by translating every setup complaint into a motion question. What is the wheel doing? What is the body doing? What is the damper doing after the motion ratio? If you cannot answer those three questions, you are not ready to tune the damper. You are ready to gather more information.
Sub-skill two: name the event before naming the cure.
Dampers see different kinds of work. A drop test is a different event from ride over random road input. Longitudinal acceleration creates pitch change during braking or acceleration. Lateral acceleration creates roll velocity during corner entry and exit. Real tracks combine these effects. If you skip the event naming step, you will misread the symptom. A car that is uncomfortable on rough pavement may need a different investigation from a car that refuses to settle during a fast transition. A car that is nervous during brake release may be telling you about a transient load-transfer effect, not a steady-state balance issue.
For the intermediate driver, the useful habit is to write notes by phase. Entry under braking. Entry after brake release. Mid-corner over surface. Exit as throttle is applied. Straight-line roughness. Late-session behavior. Those categories line up better with damper function than a single note that says the car was bad.
Sub-skill three: treat asymmetry as information.
Compression and rebound are not expected to be identical in many dampers. The reasons for asymmetry can come from tires, roads, occupants, internal construction, tire enveloping, and cost. That means you should not treat asymmetry as automatically good or automatically wrong. You map it, then ask whether the car needs that behavior. If the car is controlled in large body motions but harsh in small road motions, you are looking at the damper's ability to control large amplitudes without overdamping small ones. Dixon identifies that ability as an important characteristic in damper development. If the car is soft enough over small disturbance but poorly controlled in pitch or roll, you may be looking at a different part of the curve.
The point is to keep the curve tied to the car. An asymmetrical curve can be appropriate. A symmetrical curve can be inappropriate. The map tells you which region and which direction of damper motion you are actually using.
Sub-skill four: know when simulation helps and when it does not replace testing.
Computer analysis can provide specific numbers. Dixon describes numerical suspension-geometry packages as useful when they work, but also warns that not every package handles every racing configuration and that numerical output does not replace qualitative understanding and simple models. Ride simulations can show trends in body acceleration and tire deflection, and they can be improved by adding longitudinal acceleration for pitch and lateral acceleration for roll. But a basic ride simulation is not a complete handling model because it does not include all the ways stiffness and damping reduce pitch and roll and affect handling.
Use simulation as a way to sharpen the map. Do not use it as permission to skip the car. If your computer output says the damper should be acceptable but the vehicle test repeatedly shows a problem in a defined event, the vehicle gets the last word.
Sub-skill five: separate damper suitability from damper quality.
This is a discipline skill. A well-built damper can be wrong for the car. A damper may be ideal for one vehicle and fail the vehicle test on another. A racing or rally application may justify high precision, predictable F(V) behavior, and long-life reliability. A less critical application may not justify the same cost or technical specification. Your map should prevent two opposite mistakes: accepting a damper because it is expensive, and rejecting a damper because it is simpler than the most exotic racing part. Suitability is proven by the map and the vehicle test.
Calibration cues: how you know the map is working.
The first cue is sharper language. Your notes become more specific. Instead of saying the car needs more damping, you can say the problem appears during braking pitch, or during roll velocity at corner entry, or over sustained rough-road motion late in a run. That is progress. The more accurately you name the event, the less likely you are to change the wrong part of the curve.
The second cue is better prediction. Before a test, you should be able to say which vehicle event the change is aimed at and why the mapped damper region is relevant. You should know whether you are trying to influence ride motion, pitch, roll, combined behavior, traction, tire grip, aero ride-height control, or rough-track reliability. If you cannot predict the affected event, the map is not yet doing its job.
The third cue is agreement between lab and track. The dyno characterization should explain why the adjustment or rebuild state could affect the symptom. The motion-ratio map should explain why that region of the curve is active on the car. The track result should either confirm the hypothesis or force you to revise it. The test does not have to give you the answer you wanted. It has to give you information you can interpret.
The fourth cue is condition awareness. Dixon points out that vehicle behavior may show peculiarities on particular surfaces or under particular ambient temperatures. Rough-track testing can create high damper temperatures and aeration risk. If your notes capture the surface and conditions that create the issue, the map is becoming useful. If you describe every problem as a generic balance problem, you are still too coarse.
The fifth cue is fewer false fixes. When the map is working, you stop making changes that improve one part of the lap while accidentally damaging the phase that mattered. You stop treating a steady-state cornering complaint, a transient entry complaint, a traction complaint, and a rough-surface complaint as if they were one damper problem.
Failure modes: what wrong looks like.
The first failure mode is dyno-only confidence. The damper curve looks clean, so you assume the car will be good. Dixon's warning is direct in concept: the vehicle test is ultimate, and a good damper may fail if it is unsuitable for the vehicle. The recovery is to put the curve into the installation and event map, then verify on the car.
The second failure mode is track-only guessing. The car feels poor, so you change a knob without knowing which part of the damper curve moved or whether the damper was operating in that region. The recovery is to go back to the force-velocity characterization, the motion ratio, and the event classification.
The third failure mode is ignoring the linkage. You compare two dampers by bench force at damper velocity but ignore how the car drives each damper. A rising-rate mechanism can increase wheel damping behavior with bump. A pushrod or rocker car can separate heave and roll paths. The recovery is to translate the map to wheel and body motion before making a conclusion.
The fourth failure mode is flattening every complaint into ride. Basic ride analysis can guide trends, but Dixon notes that it is not a complete representation of handling because it does not include all the effects of spring and suspension changes on pitch and roll. The recovery is to include longitudinal and lateral transients in your thinking, especially brake pitch and corner-entry or exit roll velocity.
The fifth failure mode is ignoring heat and aeration. Sustained fast driving on rough roads can create high damper temperatures and oil aeration problems. Rally dampers commonly need separated gas or designs that can work in an emulsified state, plus generous size for cooling. The recovery is to treat late-run rough-surface symptoms as possible operating-condition problems, not only as curve-shape problems. The sibling lesson on keeping the damper working when it gets hot is the right place to go deeper.
The sixth failure mode is over-specifying. A high-grade racing car or rally car may justify expensive precision and predictable F(V) behavior. A lower-criticality vehicle may not. The recovery is to write the technical requirement to the vehicle, not to the most expensive damper you have seen.
Cross-references inside this module.
When the map shows that the damper architecture cannot support the required stability, cooling, separation, or adjustment path, go back to the architecture lesson. When the map shows that the adjuster range cannot reach the shape you need, go to the shim-stack lesson rather than chasing the knob. When the map shows that the car changes behavior with sustained rough running or high temperature, go to the heat lesson. This lesson is the diagnostic bridge: it tells you whether the next question is architecture, internal valving, installation geometry, or operating condition.
The working rule.
Do not tune a damper until you can answer four questions. What is the damper's force-velocity behavior? How does the installation turn wheel and body motion into damper velocity? Which vehicle event creates the symptom? What did the car do when tested under the relevant surface, temperature, and handling condition?
If you can answer those, you are tuning. If you cannot, you are guessing.
Worked example: pushrod aero car with a heave unit
Use the Penske-style racing layout Dixon describes as the high-end example. The suspension uses pushrods driven by the lower wishbones or uprights. Those pushrods actuate rockers, and the rockers drive the spring-damper units. A center unit can be effective in heave only and not in roll. That separation matters because the team can adjust heave springing and damping without changing the roll and load-transfer characteristics.
The mapping lesson is that you cannot read one damper curve and assume it applies to every body motion. On this kind of car, heave and roll can be deliberately separated. The heave unit is tied to ride-height control, which is especially important on cars with strong aerodynamics because they are sensitive to ride height. The corner dampers may be more involved in roll and individual wheel events. If a driver reports that the car loses grip when the platform moves at speed, the first question is not simply whether compression should be stiffer. The first question is which unit is active in that event.
A useful map for this car separates the heave path from the roll path. It records the force-velocity curve of the relevant unit, then translates the linkage motion to the damper velocity that unit sees. It also names the event: pure heave from aero load or track surface, roll velocity at corner entry or exit, or a combined event. Only then does the team decide whether the next change belongs in the heave damper, the roll-related damping, the springing, or the aerodynamic ride-height control strategy.
The worked point is simple: the more sophisticated the damper installation, the less useful a single uncontextualized dyno plot becomes. The map has to describe what motion each damper is controlling.
Worked example: rally car on a sustained rough-road test
Now use Dixon's rough-road case. Special rough tracks are intended to challenge reliability, ride, and handling. Sustained fast driving on rough roads can produce extreme suspension motion. Under those conditions the dampers may struggle with high temperatures and aeration of the damper oil. This is why rally cars commonly require special dampers, usually with separated gas or a design that can operate in the emulsified state, and generous size for cooling.
The mapping mistake would be to treat a late-run rough-road problem as if it were only a cold force-velocity issue. Suppose the car feels acceptable early in the run but becomes uncontrolled over repeated rough sections later. The map should separate the cold lab curve from the operating condition. The vehicle event is sustained high-amplitude rough-road motion, not a single smooth-corner transient. The relevant risk is not only whether the initial F(V) curve has enough force; it is whether the damper can continue to behave predictably when temperature rises and oil condition changes.
The correct test interpretation is therefore conditional. If the damper is good on a smooth handling track but deteriorates on a rough track, the map points toward rough-road durability, temperature, aeration, and damper size or configuration. That does not prove the curve shape is irrelevant, but it stops you from chasing a neat cold-dyno adjustment when the vehicle is showing an operating-condition failure.
Worked example: club-racing car with rising-rate linkage
Consider a club-racing car whose linkage gives the damper a rising velocity ratio with bump. Dixon notes that this is common enough in racing practice and that rising rate obtained by mechanism design can be easier and more controllable than manufacturing rising-rate springs or position-dependent dampers. If the spring and damper are coaxial, the same motion ratio can make wheel damping rise with wheel rate.
The driver complaint is that the car feels acceptable in small motions but becomes abrupt when loaded hard over a bump in a fast corner. A bench curve alone may not explain the problem because the damper curve is measured against damper velocity, while the car experiences wheel and body motion through a changing linkage. At deeper bump, the damper may be moving faster for the same wheel-speed input than it does near static ride height. The car may therefore be using a stronger part of the curve than the tuner assumed.
The map forces the right question. Where in suspension travel does the complaint occur? What is the velocity ratio there? Does the linkage make the damper velocity rise rapidly as the wheel moves into bump? If yes, the same nominal damper setting may be much more aggressive at the wheel in that loaded condition. The solution may not be a global softening of the damper. It may be a more precise change to the force-velocity behavior in the region the linkage actually uses, or a reconsideration of whether the linkage and damper curve are matched.
Drill: build a three-layer damper map at your next event
Do this drill over three sessions, not one heroic thrash. The goal is not to find the final setup. The goal is to prove that you can connect the component map, the installation map, and the vehicle event.
Session one is the event-naming session. Run your normal baseline. For every meaningful note, write the phase and the surface. Use categories that match damper work: straight-line roughness, braking pitch, acceleration pitch, entry roll, exit roll, combined braking and turning, combined turning and throttle, and late-run roughness. The success criterion is that every complaint names a vehicle event rather than a generic feeling.
Between sessions, make the installation translation. Use your known suspension layout and motion ratio information to identify whether the problem event is likely to drive the damper at low, moderate, high, or position-dependent velocity. If the car has a rising-rate linkage, note where in travel the complaint occurs. If the car has separated heave and roll control, identify which unit is likely involved. The success criterion is that you can say which damper or damping path is relevant before touching an adjuster.
Session two is the verification session. Run the same section of track with attention to the named event. Your job is to confirm whether the symptom is repeatable under the same surface and condition. If the symptom appears only on one rough section, record that. If it appears only late in the run, record that. If it appears only during brake release and initial steering, record that. The success criterion is repeatability: the note should be specific enough that another competent driver or engineer could watch the same phase.
Session three is the change-and-check session. Make only the change that your map says is relevant, then repeat the same observation. The grounded reason for this discipline is that the vehicle test is the final authority, but the vehicle test has to be interpreted through the laboratory and installation map. The success criterion is not necessarily a faster lap. It is that the change affects the predicted event, improves it, worsens it, or proves your hypothesis wrong. All three outcomes are useful. A change that affects a different event than predicted means the map needs revision.
Common mistakes
Mistake one is calling the dyno plot the answer. The plot is a controlled component characterization. It does not prove vehicle suitability. A damper can be good and still wrong for the vehicle. Good looks like using the plot as one layer of the map, then validating it on the car.
Mistake two is ignoring motion ratio. The wheel and damper do not necessarily move at the same speed. A rising-rate mechanism can deliberately change damper velocity ratio with bump. Good looks like translating the vehicle event into damper motion before interpreting the curve.
Mistake three is treating every handling complaint as a steady-state balance problem. Dampers are especially important in transient events such as pitch during braking and acceleration, and roll velocity during corner entry and exit. Good looks like naming the phase of the corner where the symptom begins and ends.
Mistake four is using ride analysis as if it fully explains handling. A basic ride model can show useful trends, but Dixon notes that it does not fully represent the effect of suspension on handling because it misses important pitch and roll effects. Good looks like considering ride, pitch, roll, and combined events separately.
Mistake five is forgetting operating condition. Rough-track running can raise damper temperatures and create aeration problems. Very high or very low ambient temperatures can expose peculiar behavior. Good looks like recording surface, session length, and temperature conditions alongside the setup note.
Mistake six is overbuying or over-specifying. High-grade racing and rally applications may justify expensive precision and predictable F(V) behavior. Not every vehicle needs the same specification. Good looks like matching the damper requirement to the vehicle and the test goal.
When this principle breaks down
The principle does not really break down, but your ability to apply it can be limited by missing information. If you do not have a force-velocity characterization, you can still test the car, but you are working without the component layer of the map. If you do not know the motion ratio, you can still describe the symptom, but you cannot confidently connect wheel motion to damper velocity. If the car uses unusual racing geometry, some analysis packages may struggle, and numerical output may not give design insight by itself.
There is also a scope boundary. This lesson tells you how to characterize before tuning. It does not teach complete damper construction, complete shim-stack design, or complete thermal design. If the map shows that the architecture is wrong, go to the architecture lesson. If it shows that the force curve needs internal reshaping rather than knob movement, go to the shim-stack lesson. If it shows that behavior deteriorates with heat or rough-road operation, go to the heat lesson.
The fallback is honest documentation. If the map is incomplete, do not pretend the setup conclusion is proven. Record what is known, what is unknown, and what test would close the gap.
Author Review
No quiz questions are attached to this lesson.
Sources
| # | Document | Chunk | Pages | Score | Collection |
|---|---|---|---|---|---|
| 1 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 1e72ce46-189c-88bf-2a7f-c6896727cde0 | 377 | 1 | uio_books_raw_v1 |
| 2 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 0f56ef7b-0f8f-dc33-54c0-3364a4ecad70 | 376 | 1 | uio_books_raw_v1 |
| 3 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | a218f0a9-cd7d-6dfb-8568-3df30de6ced3 | 66 | 1 | uio_books_raw_v1 |
| 4 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 67ebbada-5067-ca67-8fe5-396703fa6231 | 156 | 1 | uio_books_raw_v1 |
| 5 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 2c73db1d-2f1c-319e-c022-57e6d2609ab6 | 378 | 1 | uio_books_raw_v1 |
| 6 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 5fe51cac-899e-690e-e2f2-1650d42d298b | 147 | 1 | uio_books_raw_v1 |
| 7 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 1470f537-23af-61f3-47b0-2b0329b8b472 | 157 | 1 | uio_books_raw_v1 |
| 8 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 2c9bae5e-bfec-3dd6-d559-02fb14bf4488 | 153 | 1 | uio_books_raw_v1 |
| 9 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 7ce134cc-37f8-2df7-5fa1-24c26e3fe26a | 354 | 1 | uio_books_raw_v1 |
| 10 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | 1f2e8a65-9ed9-dc13-8d97-d8e7ad4ac6f6 | 353 | 1 | uio_books_raw_v1 |
| 11 | The Shock Absorber Handbook Wiley-Professional Engineering Publishing Series - 2nd edition John Dixon | ef96de18-d6cf-6d9a-a782-83e3b7313208 | 73 | 1 | uio_books_raw_v1 |
| 12 | Racing Chassis and Suspension Design Carroll Smith | 148524fa-62af-201e-6dff-3b729c84477a | 8 | 1 | uio_books_raw_v1 |