CA2333374A1 - Lightweight transportation vehicle - Google Patents

Abstract

A three wheeled lightweight transportation vehicle comprising a human powered hydraulic drive means, a primary and secondary frame, two rear wheel (6, 7) and suspension (14) assemblies and one front wheel (8) and suspension assembly attached to the primary frame, steering means (9) attached to the front wheel (8) and suspension assembly and to the primary frame for controlling the front wheel and suspension assembly, wherein the hydraulic drive means includes pump means (34) for generating pressurized oil and at least one hydraulically powered motor (6a, 7a) adapted to drive at least one of the wheel assemblies.

Description

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2 PCT/CA99/00488 LIGHTWEIGHT TRANSPORTATION VEHICLE
Field of Invention This invention relates to three wheel vehicles with leanable suspension that are hydraulically powered.
Background to the Invention Three wheeled vehicles are known in the art. One example is the vehicle disclosed in U5 Patent 4,313,517. In this patent, an electrically powered, three wheeled vehicle is described wherein an electric motor drives the rear wheel assemblies. In order to overcome the instability associated with three wheeled vehicles, heavy batteries are strategically positioned to lower the vehicles' centre of gravity. Power transmission is accomplished by the use of the systems batteries in conjunction with the rear wheel electric motors. The vehicle's braking system includes both mechanical and electro-magnetic brake systems which co-operate together. Electromagnetic braking is accomplished by a short circuiting system which locks the electric motor, causing the vehicle to slow down. Additionally, pedals may be coupled to at least one of the wheels to supply motive power to the vehicle. Finally, the invention features a lightweight canopy which can be removably attached to the existing frame to provide an the occupant with protection from the weather.
This vehicle has several disadvantages. The use of strategically positioned heavy batteries to overcome the stability problem associated with three wheeled vehicles adds additional weight which affects overall vehicle performance.
Further, the batteries must be recharged at regular intervals which can be time consuming and inconvenient. As well, the power generated by the manual pedal system cannot be stored for later use nor can the energy expended when braking either mechanically or electro-magnetically. Finally, the absence of a sophisticated suspension system reduces rider comfort as well as vehicle handling around corners at high speeds.
Hydraulically powered vehicles are also known in the art. For example, US Patent 5,423,560 discloses an hydraulically powered bicycle with a manually actuated pump. At the hub of both the _ front and rear wheel are positioned vane motors, and a pump assembly is positioned where the crankshaft is located on a conventional bicycle. Forward motion is achieved when pressure is applied to pedal assemblies attached to the pump input shaft. The pressure on the pedal turns the pump and forces fluid through the bicycle tubular frame. The frame serves as a distribution network carrying the hydraulic fluid to the motors. This system has several deficiencies. All bicycles are inherently unstable, relying on the agility of the rider to ensure that the bicycle remains upright while in motion. The bicycle has no suspension means, which is uncomfortable for the rider over rough ground. Finally, there are no means for storing the energy produced by the rider, or for recovering energy under braking.
Chain driven bicycles, both human powered and engine powered are well known, and integrated advanced suspension systems have been used for both the rear and front tire. However, since the ability to lean into a curve is inherent in a bicycle, the suspension systems used have little relevance for a three wheeled vehicle. Further, although a faring serves to protect the rider of a motorcycle to some extent from the weather, ultimately the rider is left exposed.
An example of a full sized hydraulically powered vehicle is disclosed in US Patent 3,966,365, which includes an hydraulic power transmission and braking system for a vehicle such as a passenger automobile. Hydraulic fluid under pressure is supplied by a variable displacement hydraulic pump which is powered by an internal combustion engine. Fixed displacement hydraulic machines are connected to the both the front and rear wheels. Operator manipulation of fluid flow control mechanisms causes the machines to act as either motors or pumps. In the power transmission mode, high pressure fluid from the variable displacement pump is circulated to the wheel motors to propel the vehicle. A flow regulator determines the rate of fluid flow and thereby the acceleration of the vehicle. Braking is accomplished by creating back pressure on the wheel motors, so that they act as pumps and decelerate the vehicle.
This system also has several disadvantages. The vehicle as a whole is very heavy, and it is relatively large and cumbersome due to the combination of the hydraulic and internal combustion engine components. Further, the braking system is not regenerative, so that the energy used in braking is not stored and recycled. Surplus energy from the variable displacement pump also cannot be stored. Finally, driving the pump with an internal combustion engine adds additional weight, and is environmentally unfriendly.
summary of the Invention The present invention seeks to overcome the problems of the prior art by providing a highly efficient three wheeled lightweight transportation vehicle with leanable suspension.
This invention seeks to provide a tricycle vehicle whose power system is a human powered hydraulic propulsion system, combined with integrated front and rear wheel suspension wherein the rear suspension allows the vehicle both to lean into turns and to remain essentially vertical on rough terrain.

3 In a preferred embodiment of this invention the tricycle is provided with a removable weather protection shield.
Thus in a first broad embodiment this invention seeks to provide a lightweight hydraulically powered vehicle including:
a chassis;
one front and two rear suspension means attached to the chassis for dampening vibrations associated with the movement of the vehicle;
at least two rear wheel assemblies and one front wheel assembly attached to the suspension means;
drive means secured to the chassis for propelling the vehicle;
braking means; and steering means attached to both the front suspension means and front wheel assembly and the chassis for steering the front wheel assembly;
wherein the drive means comprises in combination:
pump means for generating pressurized oil;
a reservoir hydraulically connected to said pump means for storing unpressurized oil;
at least one hydraulically powered motor adapted to drive at least one of the wheel assemblies;
an accumulator for storing energy in the form of pressurized oil generated by both pump means acting on the oil in the oil reservoir;
pressure transducer means hydraulically connected to the oil reservoir, accumulator, pump means and the motor for preventing significant energy loss during charging and discharging of the accumulator;
control means for regulating the flow of the pressurized oil between the accumulator and at least one wheel assembly; and clutch means integrated with the motor,

4 and wherein the rear suspension means comprises inwardly leanable suspension means.
' Preferably, the hydraulically powered motors are vane motors.
' Preferably, the tricycle further includes a weather protection shell which can be removably attached to the chassis.
Preferably the leanable rear suspension means comprises:
a first hydropneumatic strut means interposed between the first trailing arm and the frame, having an air chamber separated by a flexible diaphragm from an oil cylinder including a piston means, a first valve means included in the piston means constructed and arranged to limit the flow of oil from one side of the piston to the other, and control means for opening and closing the first valve means, interposed between the first rear suspension means and the frame;
a second hydropneumatic strut means interposed between the second trailing arm and the frame, having an air chamber separated by a flexible diaphragm from an oil cylinder including a piston means, a second valve means included in the piston means constructed and arranged to limit the flow of oil from one side of the piston to the other, and control means for opening and closing the second valve means, interposed between the first rear suspension means and the frame a balancing pipe connecting together the air chambers of the first and second hydropneumatic strut means;
an air reservoir connected to the balancing pipe by a first and a second air connection;
a one way valve in the first connection constructed and arranged to allow air flow only out of the air reservoir;

and a flow controlling valve in the second connection constructed and arranged to allow air flow at a selected rate into or out of the air reservoir.
The advantages of this vehicle are numerous. By avoiding the use of heavy propulsion systems, the vehicle can be extremely lightweight. The integrated wheel suspension enhances ride comfort by allowing the rider to lean into turns, and by allowing the tricycle to remain essentially upright over surface irregularities. Further, the removable protection shell ensures that the occupant can use the vehicle in a variety of weather conditions.
The regenerative braking system ensures that the energy expended in braking is at least partially recovered for later use when the vehicle is powered. The use of human power to drive the pump simplifies the design and eliminates the need for an auxiliary power source which must be regularly replenished. Finally, the ability of the propulsion system to store energy releases the operator from having to continuously drive the pump, and allows delivery of drive energy much in excess of what the operator could provide.
Brief Description of the Drawings Preferred embodiments of the invention will be described with reference to the accompanying drawings, wherein:
Figures 1 and 2 are top and side views;
Figures 3, 4, 5 and 6 show three rear suspension systems of the vehicle;
Figure 7 is a schematic diagram of the power transmission and regenerative braking system;
Figure 8 is a cross-sectional view of the wheel motors;
Figure 9 is a cross-sectional view of the wheel motor rotor shown in Figure 8;

Figures 10, 11 and 12 are cross-sectional views of spool valves used to control hydraulic fluid flow;
Figures 13 and 15 are cross-sectional views of the variable displacement treadle pedal piston pump;
Figure 14 is a detail view of part of Figure 13;
Figure 16 is a side view of a slot arm integral to the variable displacement treadle pedal piston pump of Figures 13 and 15;
Figures 17 and 18 are views of the wheel motor clutch;
Figures 19 to 26 show alternative rear suspension systems;
Figure 27 shows detail of one trailing arm mounting arrangement; and Figures 28, 29 and 30 show a preferred hydropneumatic rear suspension.
For clarity, the rear portion of the tricycle frame is omitted from the Figures; construction of the required supporting elements on the frame follows normal bicycle construction practises.
Description of the Preferred Embodiment Referring first to Figures 1 and 2, the major components of the hydraulically powered version of the vehicle are shown. Chassis 2 has primary and secondary sub-frames. The primary frame supports the vehicle occupant and all other mechanical and suspension components. The secondary frame supports minor vehicle components, and the weather protection shell 4 which can be removably attached to the secondary frame.
Rear wheel assemblies 6, 7 and front wheel assembly 8 form a triangular vehicle base. The rear wheel assemblies 6, ? include the propulsion system motors. Front wheel assembly 8 is removably attached to cantilever front forks 13. The forks 13 are connected to the steering mechanism 9 which consists of a steering column 12, linkage 10, and handlebars 11. The steering mechanism 9 is rotatably attached to chassis 2 by the steering column 12. Rear suspension means 14 are shown connected to rear wheel assemblies 6, 7 and to the chassis 2.
Treadle pedals 16 are used by operator 18 to drive a variable displacement pump. The hydraulic drive system is described in more detail below.
Figures 3, 4, 5 and 6 show leanable suspension means. In these suspensions, an equalizing means is used in conjunction with suspension members to eliminate imparting roll torque along the longitudinal axis of the frame, particularly when cornering at speed. The suspension is arranged such that when one of the rear wheel assemblies 6,7 moves upwardly relative to the axis of the chassis 2, the other rear wheel assembly can move. This has two consequences. When cornering, it allows the tricycle to lean, as indicated by the angle a in Figure 3. When negotiating an irregular surface it allows the tricycle to remain substantially vertical, as indicated by the surface A
shown in chain line in Figure 3. These two circumstance can also be combined, thus providing the operator with significantly improved control of the tricycle.
In the configuration of Figure 3, crossbeam 20 is pivotally attached at its centre point 21 to frame 2, shown chain dotted.
Extending substantially vertically downwards from the ends of crossbeam 20 are combined spring and shock absorber struts 22, 23. The bottom ends of struts 22, 23 are connected to trailing arms 19. The front ends of each trailing arm is pivotally connected to the chassis, and the rear ends carry the rear wheel assemblies 6, 7. The coordinated movement of the beam 20 and the trailing arms 19 ensures that the tricycle can be controlled, enhancing vehicle stability and leanability.

_, WO 99/61302 PCT/CA99/00488 Figures 4 and 5 outline a further embodiment of the rear suspension of the proposed hydraulic vehicle. In this forward cross beam system, a horizontally positioned crossbeam 15 is pivotally connected to chassis 2 at point 17. A pair of struts 22, 23 extend substantially horizontally rearward from crossbeam 15 and pivotally attach to L-shaped trailing arms 25, 26 which carry rear wheel assemblies 6, 7. The elbows of L-shaped trailing arms 25, 26 are pivotally connected to the frame 2 at points 27, 28 (only point 28 is shown in figure 4).
This system operates in the same fashion as that in Figure 3, and has the advantage of requiring less space in the vehicle.
It also transmits the suspension loads directly into the main chassis frame 2 of the tricycle. A variation on the system of Figure 3 is shown in Figure 6. This is shown arranged vertically; it can also be used horizontally as shown in Figure

5. In this system the struts 22,23 are replaced by rigid members 22A, 23A. A single strut 24 is used to provide springing, which is located between the pivot point 21 in the crossbeam and its mounting to the chassis at 21A.
Figure 7 shows a schematic layout respectively of the hydraulic system. A manually actuatable piston pump 34, in co-operation with oil reservoir 30 provides pressurized oil. The manually actuatable pump can be either fixed or variable displacement and can be operated using either a treadle pedal or a standard pedal and crankshaft mechanism. By varying the displacement in the variable displacement option, the operator can vary the pedalling effort along with the cycle rate of the pump. The low pressure oil reservoir 30 is required because the volume of the accumulator 32, which will be described later, can change by up to four litres during the charge and discharge cycles. The oil reservoir 30 is a conventional tank that stores unpressurized oil. In a preferred embodiment, the oil reservoir 30 is approximately 4 liters in size, and includes an air WO 99!61302 PCT/CA99/00488 chamber, a diaphragm and an oil chamber wherein the diaphragm will either expand or contract depending on the volume of oil in the tank. This structure is designed to keep air and dirt out of the system and also serves as a pressure equalizer, so that changes of oil level due to hydraulic system draw or the ambient atmospheric condition changes will not cause any significant pressure differential across moving seals such as those found on pump 34.
Pump 34 connects to pressure regulator 42 which in turn connects to accumulator 32. The most important function of pressure regulator 42 is to prevent significant energy loss during the charging and discharging cycles of the accumulator 32. The pressure regulator 42 is a compact single armature device with two chambers which can allow any pressure and flow of supplied or delivered oil to or from the accumulator 32.
This serves to maintain a high conversion efficiency. The accumulator 32 stores energy in the form of pressurized oil.
Like the oil reservoir, the internal structure comprises an air chamber, a diaphragm and an oil chamber. Pump 34 drives oil into either or both the wheel motors 6A, 7A, or the accumulator 32 causing the internal diaphragm to expand and compress the air held in the air chamber to create a pressure differential between the air chamber and oil chamber. When pressurized oil is required at the rear wheel hydraulic motors 106, 107, the pressurized air drives the oil out of the accumulator 32 through the hydraulic pressure transducer 42 to the wheel motor control valve. Through the manipulation of control valves 29, 31, 33, 37, and 39 the flow of hydraulic fluid to the various components of the system can be controlled. For example, if the rider wishes to stop fluid flow to the accumulator 32 so that all fluid is directed to the rear wheel motors 6A, 7A then control valve 37 would be closed. The relief valves shown solid in Figure 7 return oil to reservoir 30 in the event of over pressurization in the system. In this system, control of the various valves is conveniently incorporated into two hand grips 36, 38 (see Figures 1 and 2), which will also include integral brake levers. In a preferred embodiment, handgrip 38 controls forward acceleration, decent centre and regenerative braking, and handgrip 36 controls pedal pump displacement. The fixed displacement wheel motors have a bi-directional clutch (described below) designed to disengage the armature from the wheel shaft, thereby allowing the vehicle to coast with little friction. When handgrip 38 is placed in the regenerative braking position, operation of pump 34 can be used to charge the accumulator while the vehicle is stationary.
Turning handgrip 38 to the forward acceleration position will connect accumulator 32 to the wheel motors 6A, 7A causing the vehicle to move forward. Sustained operation of pump 34 will continue to provide hydraulic fluid to the accumulator and to the wheel motors as desired.
Braking is accomplished through both primary and secondary systems. The primary system is a regenerative braking system while the secondary system is a conventional mechanical braking system such as internally expanding drum brakes actuated by hand brake levers included with the handgrips 36, 38. The regenerative braking system uses the motors 106, 107 as pumps during the deceleration phase. By setting the valves so that the motors 6A, 7A to pump the pressurized oil in the hydraulic system, the rotation of the motor is continuously resisted, thereby causing the vehicle to slow down or even stop. The oil pumped by the motors is directed to accumulator 32 so that the kinetic energy of the moving vehicle is translated into stored energy in the form of pressurized oil. The fluid flow required to accommodate regenerative braking is managed by reversing the in and out ports of the wheel motors 6A, 7A using valves 29, 31, 33. Oil flow is thereby directed to pressure transducer 42.

Depending on how much operator 18 turns handgrip 38, more or less pressure can be placed on the wheel motors.
A preferred wheel motor construction for the motors 6A, 7A is shown in Figure 8. The main shaft 53 is preferably stainless steel, to ensure that the oil seal 54 is not damaged by shaft corrosion. Clutch pack 44 enables disconnection of the motor to allow near frictionless coasting. Steel cam ring 45 houses rotor 49 which rides on torque tube 48. This arrangement completely isolates rotor 49 from forces arising from shaft 53 moving during cornering loads. Shaft 53 rotates freely on ball bearings 46 and roller bearing 50. Ball bearing 46 also serves to counteract thrust on shaft 53. Wheel bolt hole 52 allows for easy engagement and disengagement of a rear wheel (not shown). This single bolt arrangement is also used to secure the front wheel on the axle included in cantilever arm 13. The single bolt arrangement could be replaced by other well known means for securing the front and rear wheel assemblies. The motor is completed by end plates 55, 56 between which the steel cam ring 45 is fastened. End plates 55, 56 are preferably aluminum to reduce weight.
Figure 9 provides a more detailed view of wheel motor rotor 49 positioned inside steel cam ring 45. Through crowned spline 58, rotor 49 is connected to the torque tube 48 which in turn rides in a hole through end plates 55 and 56, and due to sufficient clearance avoids contact with the main shaft 53. The rotor 49 includes a plurality of slots 57 occupied by pressure balanced dual vanes 60. The steel cam ring 45 is provided with constant radius sections, so that vane slot losses due to friction are eliminated by the constant radius sections in areas where the vanes have a differential pressure across them.

Figure 10 illustrates the operation of valve 30A of Figure 7.
Figure 11 is a schematic diagram of the valve 37 of Figure 7.
Referring to Figure 7, it will be noted that the wheel motors are shown with ports 206 and 207 which are connected to 206A
and 207A of valve 30A. As illustrated, the valve also includes ports 29, 31, 33, and 35 and a connection leading to the reservoir 30. The valve is shown in the rest or motor position. When the valve moves from the rest position to the non-rest position it redirects the motor port 206A from port 31 to port 29 and blocks off 207A motor port from port 33. The 207A motor port can still exit to port 35 through a check valve. Similarly with valve 37 of Figure 11, the valve is shown in the open position, not the rest position and moving the spool to the rest position blocks the pedal pump port PUMP
from the motor circuit.
In both Figures 10 and 11, R indicates a drain connection to reservoir 30.
Figure 12 details the control valve labelled as 39 in figure

6. This control valve is a pilot operated valve that has three purposes: first, it prevents accumulator leak down; second, it prevents unintended reverse operation of the vehicle; and third, it prevents accidental over speed of the wheel motors when they are in the free wheel mode. The valve 39 includes port A connected to the accumulator and a port B connected to the wheel motor and pedal pump circuit. Piston 79 is composed of a head portion 80 and a rod portion 88. Piston 79 is slidably received into housing 82. At the base of head portion 80 is seated 0-ring 84 designed to inhibit fluid flow when the control valve is in the closed position (shown). Wound around rod portion 88 is spring 86.In operation, the valve has four possible conditions as follows:

WO 99!61302 PCT/CA99/00488 1. The vehicle is stopped, the accumulator is charged and the brake signal is effected.
There is no pilot operation; valve 39 remains closed.
2. The vehicle is stopped or moving, the accumulator is charged.
A set of pilot valves (not shown) makes use of the higher pressure of accumulator 32 compared to port B to cause valve 39 to open rapidly (i.e. head portion 80 slides into housing 82). The action occurs with the operator's forward acceleration signal.
3. Vehicle coasting, some accumulator charge, operator signals regenerative braking.
There is no a pilot valve signal, but instead pressure build-up at port B forces valve 39 open. Once open, the valve remains open unless signalled to close, and only if the pressure at A and B is at least 600 psi above the pressure of reservoir 30.
4. System Discharged.
Spring 86 will open valve 39 readying the vehicle for pedalling via port A or regenerative braking via port B.
Figure 13 shows a cross-sectional side view of a one cylinder variable displacement treadle pedal piston pump that operator 18 acts upon to propel the vehicle and charge accumulator 32.
Drive arc 91 is pivotally connected to chassis 2 at point 90.
Foot 92 is seated against drive arc 91. Movement of foot 92 relative to drive arc 91 is restricted by co-operating interlocking teeth integral to the bottom surfaces of drive arc 91 and foot 92 (see Figure 14). Connecting rod 93 extends between foot 92 and piston 96 and is linked by pins 94 and 99 respectively. Piston 96 is seated in cylinder 98, the base of which houses spring 97. When drive arc 91 is rotated about point 90, it drives con rod 93 forward which in turn moves piston 96 down cylinder 98 and compresses spring 97. Piston 96 is returned to its' rest position (shown) by the expansion of spring 97. The cycling of piston 96 moves oil through cylinder 98. The oil enters and leaves cylinder 98 by self actuating check valves. Drive arc 91 and foot 92 have the same centre of curvature at pin 94.
Slotted arms 100 and 101 which rotate about pin 102 (see Figures 15 and 16), serve to hold base 92 in a given position and limit the travel of piston 96. Slotted arms 100, 101 ensure that when the piston is in its rest position, a small gap is present between the interlocking teeth of drive arc 91 and foot 92 (see Figure 14). If operator 18 wants to change the displacement of the pump 34, then foot 92 is moved to a different position on drive arc 91. Movement of slotted arms 100, 101 and in turn foot 92 can be accomplished by a cable extended to a control mechanism (not shown) on handgrip 36.
Pin 94 could be replaced by a ball and socket joint which is more typical in hydraulic design. The travel of piston 96 can be limited by a piston stop in the end of cylinder 98. The variable displacement treadle pedal piston pump can also be replaced by a standard pedal assembly and a fixed displacement pump or with a two cylinder variable displacement treadle pedal piston pump. The latter requires that each pedal be connected to an individual treadle pedal which would co-operate with a piston associated with one of the two cylinders. This would necessitate the use of a mechanism, such as a chain or linkage, interconnecting the treadle pedals to ensure equal and opposite pedal movement.
Operation of the bi-directional clutch 44 in Figure 8 will now be explained with reference to Figures 17 and 18. In order to explain the operation of the bi-directional clutch, it is shown for simplicity sake as a linear arrangement in Figure 17 rather than as a circular arrangement. A grooved roller 103 occupies most of the pockets 104 in race 105. Springs 106, in slots 107, push the rollers I03 to the centre bottom of pockets 104. This action moves retainer 108 to the position shown in Figure 18.
Ratchet pawl 109 is attached to retainer 108 by a slot 110 and is pushed in the direction of arrow 17A in the slot by springs (not shown). In the "passive" direction, the pawl 109 is spring loaded to enter pockets 121 in race 112 as race 112 travels in the direction of arrow 17B. During regenerative braking, another pocket 104 contains another pawl (not shown) which points in the direction of arrow 17B. Means are also provided for raising the pawl manually, so that regenerative braking can be disabled if not required. The regenerative braking pawl should not be raisable while under load, but a brief motor direction pulse will cause it to release. If the race 112 moves in the direction of arrow 17B, pawl 109 will engage pocket 111 and cause retainer 108 to move in the same direction. The slot spring for pawl 109 is strong enough to override all the roller springs 106 at once. This action also moves rollers 103 in the direction of arrow 17B, and out into pockets 111 and 104.
Roller pin slots in retainer 108 permit this. The rollers 103 engage pockets 111 and 104 simultaneously transmitting the load. Pawl slot 110 and springs (not shown) prevent any significant load from being transmitted by pawl 109. Similarly, when the reverse pawl is lowered the clutch will engage in the opposite direction. The groove in rollers 103 could be eliminated by providing a second spring slot in race 112.
This clutch has several benefits. First, the rollers 103 have a large load carrying capacity. This, combined with a light engagement pawl 109, means that the clutch can be small as well as having a small coasting friction. Second, the clutch is made of simple parts. Third, since the wheel rpm of the tricycle wheels is relatively low, the small size of the clutch permits engagement of regenerative braking without damage to the clutch.
The chassis parts, and the primary and secondary frames, conveniently are constructed from welded mild steel, chromoly tubing, silver brazed lightweight tubing, fibre reinforced plastic or the like. In the preferred embodiment, the primary frame is a triangulated tube design providing maximum rigidity and minimum weight.
The preferred hydraulic fluids are either power steering or automatic transmission fluid, although other fluids are suitable.
The front suspension system incorporates a conventional design in which a shock absorber is integrated into the cantilever arm 13. Alternatively a standard bicycle fork can be used, either with our without resilient suspension means.
In Figures 19 - 26 alternative rear suspension systems are shown.
A cable based system is shown in Figures 19 and 20. Two cranked trailing arms 191, 192 are connected by the cable 190 which passes around the pulleys 193, 194, which are supported by a cable frame 195. The cable frame I95 is supported on the tricycle frame, and moves against a combined spring and shock absorber strut 196. Net vertical movement of both wheel is controlled by the strut 196, and the ability of wheels to move relatively is provided by the cable 190 moving around the pulleys 193, 194.
Figures 21, 22, and 23 show a group of suspension systems analogous to the earlier Figures in which a fluid based system is used to provide the equalisation function. Thus such systems can utilise pneumatic, hydropneumatic, or hydraulic components for both the springing and leaning functions.
Figures 21 and 22 are similar to Figures 3 and 4. In Figure 21, which is a rear view, the struts and cross beam of Figure 3 are replaced by two pneumatic, or hydropneumatic, struts 210, 211, which are connected together by the pipe 213. Although air can flow freely through pipe 213, the overall air pressure in the system is controlled by the regulation unit 214. In Figure 22, which is a side view, the arrangement shown in Figure 4 is similarly revised, using two pneumatic, or hydropneumatic, struts 210 (only one is shown) linked by a pipe 213; the air pressure is controlled by the regulator 214. In both of these arrangements, each wheel can respond to irregularities, and both can move in opposite directions by air transfer between the units to allow the tricycle to lean into a corner. The regulation unit controls the effective spring rate of the units.
The arrangement shown in Figure 21 can be modified if instead of hydropneumatic struts, double acting hydraulic cylinders are used for 210 and 211. With a double acting cylinder, both chambers can be connected together, the upper ones by the pipe 213, and the lower ones by the pipe 221, shown ghosted. The pipe 221 also includes a similar reservoir 224, and both of the pipes 213, 221 are provided with shut off valves 223, 224, 225 and 226. The regulator 214 is also replaced by an air over oil pressurised unit. This system functions as follows.
The upper ends of the cylinders 210, 211 together with the air pressurised reservoir provide the suspension functions; the effective springing rate being determined by the air pressure in the reservoir. The lower ends of the cylinders 210, 211 WO 99!61302 PCT/CA99/00488 provide the leaning function, by allowing oil to flow through the pipe 221 between them. The reservoir 222 has no effect on this flow, as it is not pressurised. The four shut off valves 223, 224, 225 and 226 control fluid flow between the two cylinders. When the tricycle is being ridden under normal circumstances they are open. When these valves are closed there is no fluid movement into and out of the two cylinders 210, 211, and the suspension is locked and cannot move. This has several uses. It makes the tricycle more manouverable at low speeds. It facilitates keeping the tricycle vertical when stopped. It also acts as an anti-theft device: the valves can easily be controlled by a key, thus allowing the rider to lock the suspension with the rear wheels out of vertical. The tricycle can then only be ridden in a circle.
The arrangement shown in Figure 23 is related to both of Figures 21 and 22. A simple trailing arm 233 is used as in Figure 4, attached to a frame mounted pivot means 235. A
rotary multiple vane pneumatic unit 236 is mounted between the trailing arm 233 and the frame, to control the movement of the wheel assembly. The other trailing arm is similarly mounted.
As before the two rotary units are interconnected by the pipe 233, and the air pressure is controlled by the regulator 234.
Figures 24 and 25 show an alternative mechanical arrangement, in which a gear differential unit is used. The two trailing arms 243, 244 are each mounted onto shafts 250, 251, which are carried on suitable mounts on the frame (not shown . The shafts are each connected to a gear in the differential, and these gears are interconnected by a pair of gears carried by a spider, which is attached to the gear case 252. Movement of the gear case is controlled by at least one strut 253, and desirably two struts 253,254, attached to mounting points on the frame. As shown in Figure 17, strut 253 is located rearwards, and strut 254 is located forwards. If desired, both struts can be in the forward direction, thus saving some space.
In response to irregularities, either or both wheels move and cause the carrier to rotate against the struts. When the vehicle is leaned into a corner, the shafts 251, 252 rotate relative to each other, thus providing the required leaning function.
In Figure 26 is shown schematically a simpler unsprung system, related to Figure 3. To the rear of the frame 260 is attached a bearer 261 which carries a support 262 with a pivot 263 at its end. Attached to the pivot 263 is an equalising beam 264.
The beam 264 is thus able to rotate through a limited arc about the pivot 263. At each end of the beam 264 a pair of connecting links 21A, 22A are pivotally attached at their upper ends to the beam 264 and at their lower ends to the two trailing arms 19. The two trailing arms are carried by the pivots 265, 266 on a cross bar 267 which is rigidly attached to the rear end of the frame 260. The two trailing arms 19 can each rotate vertically through a limited arc. As this system does not include any springing means, the two trailing arms 19 cannot move together in the same direction. As shown by the pairs of arrows X, Y if one arm moves upwards, the other has to move downwards, thus allowing the tricycle to lean into a curve, and to r_egotiate »neven ground. Thus the integration of the pivoting beam 264 into the suspension system serves to eliminate the imparting of roll torque to the frame by forces arising when uneven ground is encountered or when the vehicle rounds a curve sharply.
In the preceding description, the mounting means whereby the front end of each trailing arm is attached to the frame are spaced apart, more or less at the spacing required to obtain the desired track for the rear wheels. For a single person tricycle this will typically be of the order of 45cm to 50cm, so that the tricycle needs little more space, it any, than a conventional bicycle. This has the advantages that the trailing arms are substantially straight, and are not subjected to significant torsional stresses as the suspension moves.
Additionally, a cross beam, if used as shown in these Figures, is of a reasonable length. If desired, as shown schematically in Figure 27, the mounting pivots 271, 272 may be located close together onto the rear end of the frame 283, and cranked trailing arms 284, 285 used to obtain the desired track.
A preferred hydropneumatic suspension system which can be used with several of the suspensions described above is shown in Figure 28, and details of the valuing arrangement used are shown in Figures 29 and 30.
Each hydropneumatic unit is attached at one end 290 to a trailing arm, and at the other end 291 to the tricycle frame.
Conventional rubber bushed mountings, as shown schematically at 290, are used at both ends. The cylinder 292 contains a piston 293 attached to the tube 294. A suitable seal, not shown, is also provided between the piston 293 and the inside of the cylinder 292. The upper end of the cylinder is sealed by the flexible diaphragm 295 attached at one end to the end of the cylinder at 292A and at the other end to the support plate 296. A second flexible diaphragm 297 is attached at one end also to the cylinder at 292A, at its other end 298 to the casing 299. Both of these diaphragms are of the so-called "rolling sock" type. A bearing 300 for the tube 294 is also provided at the end 292A of the cylinder which contains a suitable seal (not shown). It can thus be seen that as the two ends 290, 291 move relative to each other the piston 293 slides within the cylinder, and the tube 294 slides within the bearing WO 99/61302 PCT/CA99/004~°
300. The spaces 301,302,303 and 304 all contain oil, and the space 305 contains air.
The piston 293 is provided with at least two bores 306, 307 which communicate with the space 304 within the tube 294.
Within the tube 294 and inside the piston 293 is a valve 308, the details of which are discussed below. The valve 308 is operated by the rotatable control rod 309, which passes through the oil seal 310. Control rod 309 does not move when the ends 290,291 of the strut move relative to each other, as it is attached at its lower end to the valve 308 within the piston 293. The air space 305 is connected by pipe 311 to the strut on the other side of the tricycle(not shown). Air flows freely through pipe 311 between the two linked air spaces. An air reservoir 312 is connected to the air pipe 311 by two connecting pipes 313, 314. Pipe 313 includes a control valve 315, and pipe 314 includes a one-way valve 316, which is set to allow air flow only out of the reservoir 312.
The valve 308 is shown in Figure 29 in the closed position.
The piston 293 has bares 306 and 307 along with a pin 580 facing inward.
The tube 294 is not connected to the valve body 400. The valve body 400 is rotatably housed within the piston 293. The valve body 400 is a tube open at both ends. The valve body 400 contains a pair of rollers 510, at least one upper hole 520, at least one lower hole 530, a pair of springs 540, and a pair of stoppers 5.50. Also, the inner face of the valve body 400 has two pairs of ridges 560. Each roller 510 is captive between a pair of ridges 560. Each upper hole 520 is in communication with a corresponding lower hole 530. For every pair of ridges 560, one ridge has adjacent a spring 540 while another has adjacent a stopper 550 and a roller 510 in between a ridge pair 560. The upper hole 520 is above the lower hole 530. The holes 520, 530 are between a stopper 550 and a spring 540. The outside of the valve body 400 has a slot 570.
Captive in this slot 570 is the pin 580 on the inner face of the piston 293. The slot 570 is long enough to only allow the valve body 400 to rotate within a certain distance.
The control rod 309 enters the piston 293 through the open end and enters the lower tube 294 through its corresponding open end. The end of the control rod 309 has a pair of detents 600.
Each detent 600 is in contact with a roller 510. Each detent 600 is also shaped to engage a stopper 550. The control rod 309 is free to rotate within the valve body 400.
The workings of the valve 308 will now be examined. The valve 308 has two positions, locked and unlocked. In the unlocked position, the upper pair of connecting holes 520 are aligned with the bores 306 on the piston 293 and the lower pair of connecting holes 530 are aligned with the bores 307 on the piston 293. In the unlocked position, oil can freely travel from the space 301 to the space 302 through holes 520 and 530 and through bores 306 and 307. In the locked position, the upper hole 520 is not aligned with the bore 306 on the piston 293 and the lower hole 530 is not aligned with the bore 307 on the piston 293. This effectively stops oil from flowing from space 301 to space 302.
The locking function is accomplished by rotating the valve body 400. To explain the workings of the locking function, the following description will only take into account one side of the valve body 400. It must be understood that the other side of the valve body 400 functions in a similar manner. When in the unlocked position, the spring 540 is extended and pushes the roller 510 against the ridge 560 adjacent the stopper 550.
At this point the detent 600 at the bottom of the control rod 309 is engaging the stopper 550. To lock the mechanism, the control rod 309 is rotated clockwise, carrying with it valve body 400 until the pin 580 encounters the end of the slot 570.
This removes the alignment between the connecting holes 520, 530 and bores 306, 307. Continued rotation of rod 309 causes roller 510 to be squeezed against the inner wall of valve body 400 due to detent shape 600 and this causes the valve body 400 to deform and expand outwardly. The friction between the outer face of the valve body 400 and the inner face of the piston 293 prevents rotation of valve body 400, while detent shape 600 locks the valve mechanism.
To unlock the valve 308, the control rod 309 is rotated counterclockwise. By doing so, the roller 510 is moved away from the spring 540. The spring 540 assists in this as it is compressed. By the time the roller 510 is in contact with the other ridge 560, the detent &00 is in contact with the stopper 550. At this point the valve body 400 is no longer deformed and is no longer locked. Further rotation of the control rod 309 causes the valve body 400 to rotate as well. However, this rotation is not uncontrolled as the pin 580 reaches the end of slot 570, thereby preventing further rotation. The pin 580, when it reaches the end of the slot 570 in the unlocked position, aligns the connecting holes 520, 530 and the bores 306, 307. This allows the free flow of oil between spaces 301 and 302.
This suspension system can function in two separate modes, which are unlocked, and locked.
During unlocked operation, valve 308 in piston 293 is open, and piston 293 is free to move; oil can flow between spaces 301 and 302, and any volume change in the space 304 is accommodated by the orifice 317. If one strut is moved upwardly, for example due to a surface irregularity, or if the tricycle is leaned, air flows through connection 311, thus maintaining constant air pressure in both struts and air chamber 312. A shock absorber function is provided by the valves 315 and 316. When the pressure in the reservoir 312 is higher than that in the pipe 311, valve 316 opens, and the pressures equalise. When the pressure in pipe 311 is higher than that in the reservoir air flows though valve 315 until the pressures again equalise] the setting of valve 315 controls the air flow, and thus the rate at which the pressures are equalised.
During locked operation, the valves 308 are closed. This seals both spaces 301 and 302, and prevents oil flow between spaces 301,302, and 304. When locked, the trailing arms cannot move, and the ability to respond to an irregular surface and to lean is lost.
It must be noted that the air chamber 312 with the attendant connecting pipes 313, 314 arid the valves 315 and 316 can be omitted without affecting the vehicle's ability to lean or its ability to respond to irregular surfaces. However, omission of this sub-system will remove the shock absorbing function.
In this arrangement, the oil is present only as a lubricant and to enable the locking function. The air chambers provide both springing and shock absorber functions, and allow reaction to irregular surfaces and leaning.
In the preceding description, the embodiment described is a trailing arm system. For a number of reasons, this is the preferred arrangement. It permits the use of many conventional bicycle parts, is light and compact, is well adapted to locate WO 99/61302 - PC'T/CA99/0048R
both rear wheels reliably, and accommodates the loads imposed when the tricycle is ridden. However, it is understood that other suspension means, which may or may not incorporate a springing function, can also be used, such as a sliding pillar arrangement. The trailing arm itself can also be modified, for example as a twin arm similar to a bicycle front fork, and as a trailing A-frame.
The rear suspension of this invention in addition to providing the option of a more comfortable ride, improves the handling of the tricycle, by allowing it to lean into corners at speed, and to negotiate broken ground in a more or less vertical position.

Claims (19)

We Claim:

1. In a suspension system, the improvement comprising:
first and second telescopic support members for connection between a suspended and unsuspended masses;
a piston secured to one of said members and sealingly engaged with the other of said members and defining with said support members first and second hydraulic chambers;
means defining a third hydraulic chamber having a moveable wall;
means providing fluid communication between said first, second and third chambers; and valve means moveable between an open position in which said valve permits fluid flow between said first, second and third chambers and a closed position in which said valve prevents communication between said chambers and prevents movement of said support members so as to lock said members in a locked position.

2. A suspension system as defined in claim 1, further including means for moving said valve means between said open and closed positions.

3. A suspension system as defined in claim 1, one of said support members comprising a housing having an open end and a closed end secured to one of said masses, and a bore communicating with said open end; said piston being sealingly mounted in said bore for axial movement therein, the other of said support members comprising a tubular member concentrically received in said bore and having one end secured to said piston for movement therewith, an opposite end extending outwardly of said housing for connection to the other of said masses, an outer surface sealingly engaged with said one of said members for telescopic movement therein and an axial fluid passage extending from said one end and along a substantial portion of the length thereof and an opening in said other end communicating with said third chamber, said one end of said tubular member communicating with first and second chambers.

4. A suspension system as defined in claim 3, said piston having end faces at opposite ends thereof, one end face defining a movable surface in said first chamber and the other face defining a movable surface in said second chamber and a bore for receiving said one end of said tubular member and said valve means.

5. A suspension system as defined in claim 4, said piston having first fluid passages connecting one of said faces with said piston bore and second fluid passages connecting the other of said faces with said piston bore, said valve means being rotatably mounted in said bore of said piston for movement between said open and closed positions, said open position of said valve means being angularly displaced from said closed position and providing fluid communication between said first and second fluid passages so as to permit fluid flow between said first and second hydraulic chambers, said closed position of said valve means preventing fluid flow between said first and second fluid passages.

6. A suspension system as defined in claim 5, said valve means comprising an elastically deformable tubular valve member rotatably mounted in said piston bore having open ends and an axial bore extending therethrough, one of said ends of said valve member communicating with said one end of said tubular support member, the other one of said ends of said valve member communicating with said first hydraulic chamber, said valve member further including:
first port means for communicating with said first fluid passages in said piston in said open position of said valve means; and second port means for communicating with said second fluid passages in said piston in said open position of said valve means;
said valve means having locking means mounted in said valve member for urging said valve member against said bore of said piston for locking said valve member in said closed position.

7. A suspension system as defined in claim 6, further including locking means engageable with portions of said tubular member containing said ports for closing said ports and urging said portions into intimate frictional engagement with said piston bore.

8. A suspension system as defined in claim 6, said locking means including cylindrical roller means mounted in and in engagement with said bore of said valve member, at least one longitudinally extending cam ridge in said bore of said valve member and means for moving said roller into and out of engagement with said ridge so that engagement of said roller with said cam ridge elastically deforming said valve member radially outwardly.

9. A suspension system as defined in claim 8, further including a control rod concentrically mounted into said tubular support member and said valve member and having a detent for engaging said roller means, said control rod extending outwardly of said tubular support member to permit manual manipulation thereof.

10. A suspension system, comprising:
first and second telescopic support members for connection between a suspended and unsuspended masses;
a piston secured to one of said members and sealingly engaged with the other of said members and defining with said support members first and second hydraulic chambers in said other of said members;
means defining a third hydraulic chamber;
means providing fluid communication between said first, second and third chambers;
valve means moveable between an open position in which said valve means permits fluid flow between said first, second and third chambers and a closed position in which said valve means prevents communication between said chambers and prevents movement of said support members so as to lock said members in a locked position;
means for moving said valve means between said open and closed positions; and means defining a pneumatic chamber, said means surrounding said second telescopic support members for supporting said suspended mass.

11. A suspension system as defined in claim 10, said means defining said third chamber and said pneumatic chamber comprising "rolling sock" type diaphragms, each said diaphragms being sealingly secured to one end of one of said supported members.

12. A suspension system as defined in claim 10, one of said support members comprising a housing having an open end and a closed end secured to one of said masses, and a bore opening into said open end, said piston being sealingly mounted in said bore for axial movement therein, the other of said support members comprising a tubular member concentrically received in said bore and having one end secured to said piston for movement therewith, an opposite end extending outwardly of said housing for connection to the other of said masses, an outer surface sealingly engaged with said one of said members for telescopic movement therein and an axial fluid passage extending from said one end and along a substantial portion of the length thereof and an opening in said other end communicating with said third chamber, said one end communicating with first chamber.

13. A suspension system as defined in claim 12, said piston having end faces at opposite ends thereof, one end face defining a movable surface in said first chamber and the other face defining a movable surface in said second chamber and a bore for receiving said one end of said tubular member and said valve means.

14. A suspension system as defined in claim 13, said piston having first fluid passages connecting one of said faces with said piston bore and second fluid passages connecting the other of said faces with said piston bore, said valve means being rotatably mounted in said bore of said piston, said open position of said valve means being angularly displaced from said closed position and providing fluid communication between said first and second fluid passages so as to permit fluid flow between said first and second hydraulic chambers, said closed position of said valve means preventing fluid flow between said first and second fluid passages.

15. A suspension system as defined in claim 14, said valve means comprising an elastically deformable tubular valve member rotatably mounted in said piston bore having open ends and an axial bore extending therethrough, one of said ends of said valve member communicating with said one end of said tubular support member, the other one of said ends of said valve member communicating with said first hydraulic chamber, said valve member further including:
first port means for communicating with said first fluid passages in said piston in said open position of said valve means; and second port means for communicating with said second fluid passages in said piston in said open position of said valve means;
said valve means having locking means mounted in said valve member for urging said valve member against said bore of said piston for locking said valve member in said closed position.

16. A suspension system as defined in claim 15, said locking means including cylindrical roller means mounted in and in engagement with said bore of said valve member, at least one longitudinally extending cam ridge in said bore of said valve member and means for moving said roller into and out of engagement with said ridge so that engagement of said roller with said cam ridge elastically deforming said valve member radially outwardly.

17. A suspension system as defined in claim 16, further including a control rod concentrically mounted into said tubular support member and said valve member and having a detent for engaging said roller means, said control rod extending outwardly of said tubular support member to permit manual manipulation thereof.

18. A suspension system for a vehicle having a chassis and a plurality of ground engaging wheels, comprising:
a telescopic support assembly associated with each of at least two of said wheels, one end of each said assembly being secured to said chassis and the other end thereof secured to an associated wheel, each said assembly having:
first and second hydraulic fluid chambers;
a piston between said first and second fluid chambers;
valve means in said piston, said valve means having an open and a closed position for selectively opening and closing fluid communication between said first and second chambers so that when communication is open, fluid is free to flow between said first and second chambers and when communication is closed, fluid is precluded from entering or leaving either of said first and second chambers;
a hydraulic fluid reservoir having a moveable wall and communicating with one of said first and second chambers permitting fluid flow between said reservoir and said one chamber when communication between said first and second chambers is open; and an air chamber having a moveable wall in engagement with said moveable wall of said reservoir for maintaining fluid in said reservoir under pressure;
a balancing pipe connecting said air chambers of each said support assemblies; and an air reservoir for storing air under pressure and connected to said balancing pipe for maintaining the pressure in said pipe and said air chambers at a predetermined pressure.

19. A suspension system for a vehicle as defined in claim 18, further including first and second conduits connecting said air reservoir and said balancing pipe; a one way valve in said first conduit for providing fluid flow from said air reservoir to said balancing pipe; and a flow control valve in the second conduit for selectively controlling the rate of flow into or out of said air reservoir.