PROGRESSIVE DAMPING SYSTEM FOR A TRACK SYSTEM

• US 20180118286A1
• Filed: 04/11/2016
• Published: 05/03/2018
• Est. Priority Date: 09/29/2014
• Status: Active Grant

• Current Assignee: Soucy International Inc. (Soucy Holding Incorporated)
• Original Assignee: Soucy International Inc. (Soucy Holding Incorporated)
• Inventors: SAUVAGEAU, Yves, PELLERIN, Jonathan
• Granted Patent: US 10,640,160 B2
• Time in Patent Office: Days
• CPC Class Codes: B60G 17/0165 to an external condition, e.g. rough road surface, side wind
• CPC Class Codes: B60G 17/056 Regulating distributors or valves for hydropneumatic systemsB60G17/044 - B60G17/048, B60G17/0416 take precedence; Fluid interconnection systems to control vehicle inclination B60G21/06, B60G21/10; valves per se F16K
• CPC Class Codes: B60G 17/08 Characteristics of fluid dampers adjusting fluid dampers in general F16F9/44 - F16F9/53
• CPC Class Codes: B60G 2202/154 with an accumulator
• CPC Class Codes: B60G 2300/32 Track vehicles
• CPC Class Codes: B60G 2400/25 Stroke; Height; Displacement
• CPC Class Codes: B60G 2500/11 Damping valves
• CPC Class Codes: B62D 49/0635 using additional ground engaging means, e.g. endless tracks vehicles with endless tracks and either additional or alternative ground wheels B62D55/02, B62D55/04
• CPC Class Codes: B62D 55/04 with tracks and alternative ground wheels, e.g. changeable from endless track vehicle into wheeled vehicle and vice versa for multi-purpose tractors B62D49/0635
• CPC Class Codes: B62D 55/112 with fluid springs, e.g. hydraulic pneumatic
• CPC Class Codes: B62D 55/12 Arrangement, location, or adaptation of driving sprockets
• CPC Class Codes: B62D 55/15 Mounting devices, e.g. bushings, axles, bearings, sealings with lubrication means B62D55/092
• CPC Class Codes: F16F 9/065 Expansion chamber provided on the upper or lower end of a damper, separately there from or laterally on the damper
• CPC Class Codes: F16F 9/346 Throttling passages in the form of slots arranged in cylinder walls
• CPC Class Codes: F16F 9/512 Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity F16F9/504, F16F9/516 take precedence; non-automatic damper adjustment from a distance using servo control, the servo pressure being created by the flow of damping fluid F16F9/465; self-pumping fluid springs in vehicle suspensions B60G17/044

Abstract

The present invention generally relates to vehicle and machinery in agriculture, construction, forestry, mining and powersport. It further generally relates to track systems and traction assemblies used with such vehicles. The track system comprises a drive wheel and a plurality of idler wheels mounted on a support frame. At least one of the plurality of wheels is operatively mounted on the support frame via a damping system adapted to provide a damping value dynamically varying as a function of the load applied. Track systems do not benefit from the damping provided by the layer of air within the tires. The disclosed damping system has the objective to overcome one this drawback by providing a smooth ride for tracked vehicles. The damping system comprises a cylinder fluidly connected to a reservoir. Damping ratio is varied by varying a flow circulating area between the cylinder and the reservoir.

Claims

1-28. -28. (canceled)

29. A method for varying the damping value of a damping system of a track system, the method comprising varying the flow of a fluid between a hollow portion of a suspension element and a reservoir in relation to movement of a piston within the hollow portion to provide a damping value dynamically varying as a function of load applied on the track system.

30. The method as claimed in claim 29, the method further comprising:

reducing the flow of the fluid as load increases on the track system;

increasing the flow of the fluid as load decreases on the track system.

31. The method as claimed in claim 29, the method further comprising:

measuring the position of the piston in relation to length of the hollow portion;

modifying the flow of the fluid based on the measured position of the piston.

32. The method as claimed in claim 30, the method further comprising communicating a control signal to an active fluid flow control means configured to vary the flow based on the control signal.

33. The method as claimed in claim 31, the method further comprising communicating the measured position to a controller configured to communicate the control signal to the active fluid flow control means.

34. The method as claimed in claim 31, the active fluid flow control means being one or more solenoid valves, the method further comprising controlling one or more solenoid valves to vary the flow of fluid between the cylinder and the reservoir.

35. The method as claimed in claim 32, the active fluid flow control means being one or more solenoid valves, the method further comprising controlling one or more solenoid valves to vary the flow of fluid between the cylinder and the reservoir.

36. The method as claimed in claim 30, the method further comprising:

measuring the position of the piston in relation to length of the hollow portion;

modifying the flow of the fluid based on the measured position of the piston.

37. The method as claimed in claim 36, the method further comprising communicating the measured position to a controller configured to communicate the control signal to the active fluid flow control means.

38. The method as claimed in claim 36, the active fluid flow control means being one or more solenoid valves, the method further comprising controlling one or more solenoid valves to vary the flow of fluid between the cylinder and the reservoir.