Patent Application
20090280936
The present invention relates to a variable belt drive.
It is desirable to vary the cooling fan speed relative to the engine speed so that the vehicle has adequate cooling for all conditions and energy use is minimized. This has been accomplished for four wheel drive loaders with the use of a hydraulic pump, valve and motor that allow variations in fan speed. Another solution used on the production John Deere 8030 Series agricultural tractors involves varying fan speed with a sheave which is moved by a single moveable piston actuated by engine oil. Another production John Deere 9030 Series agricultural tractor also uses moveable sheaves with a single moveable piston. The 9030 moveable piston is actuated by transaxle oil. Passenger cars solve this problem through the use of electrically driven fans and a larger alternator.
There is a need for a variable speed fan drive with movable fan sheave design which does not require rotating seals, which utilizes multiple smaller pistons and O-ring seals, and wherein the pistons are protected from the environment
Accordingly, an object of this invention is to provide a movable fan sheave design which has reduced leakage of hydraulic fluid.
A further object of the invention is to provide such a movable fan sheave design which does not require rotating seals to contain pressurized fluid.
A further object of the invention is to provide such a movable fan sheave design which utilizes multiple smaller pistons.
A further object of the invention is to provide such a movable fan sheave design which utilizes O-ring seals which have a very low leak rate.
A further object of the invention is to provide such a movable fan sheave design wherein the pistons are protected from the environment.
A further object of the invention is to provide such a movable fan sheave design wherein the bearings require no service and are not dependent on engine oil for lubrication.
These and other objects are achieved by the present invention, wherein a variable belt drive includes non-rotating piston housing which forms piston bores therein. The housing receives a rotatable input shaft which is supported by bearings and coupled to a power source. A first sheave is mounted for rotation with the shaft and fixed axially with respect to the shaft. A second sheave is mounted for rotation with the shaft and slidable axially with respect to the shaft. Pistons are axially movable in the piston bores in response to fluid pressure. A non-rotating carrier engages the ends of the pistons. A thrust bearing has an outer race fixed axially with respect to the carrier and rotatable with the carrier, and an inner race fixed axially with respect to the second sheave and rotatable with the second sheave.
The carrier includes an annular surface which engages an outer surface of the outer race of the thrust bearing. An annular inwardly opening groove is formed in the annular surface. An O-ring is received in the groove. The O-ring engages the outer surface of the outer race to resist rotation of the outer race.
A flexible boot has one end fixed to the piston housing and a second end fixed to the carrier. The boot prevents exposure of the piston to the environment.
Referring to
Referring now to
A first or fixed sheave 24 is bolted to the outer end of shaft 16 so that sheave 24 rotates with the shaft 16 and fixed axially with respect to the shaft 16. A second or movable sheave 26 is mounted on shaft 16 inboard of sheave 24. Sheave 26 includes a hollow generally cylindrical hub 28. Hub 28 includes inner splines 30 which slidably mesh with outer splines 32 formed on the shaft 16. Due to the splines 30, 32, the sheave 26 rotates with the shaft 16 and is slidable axially with respect to the shaft 16 and the housing 12. Grease seals 29 and 31 are carried by the sheave 26 and slidably and sealingly engage the outer surface of the shaft 16. A drive belt 25 is held between sheaves 24 and 26.
Pistons 40 are axially movable in the piston bores 14 in response to fluid pressure communicated to piston chambers 41 via fluid passages 42 formed in the housing 12. An annular non-rotating shift collar carrier 44 engages the ends of the pistons 40, and includes recesses 43 which receive a reduced diameter end portion 45 of each piston 40.
A thrust bearing 46 has an outer race 48 fixed axially with respect to the carrier 44 and rotatable with the carrier 44, and an inner race 50 fixed axially with respect to the second sheave 26 and rotatable with the second sheave 26.
The carrier 44 includes an annular surface 52 which faces radially inwardly and which engages an outer surface 54 of the outer race 48 of the thrust bearing 46. An annular inwardly opening groove 56 is formed in the annular surface 52. An O-ring 58 is received in the groove 56. The O-ring engages the outer surface 54 of the outer race 48 to resist rotation of the outer race 48. Bearing 46 is fixed axially with respect to sheave 26 between shoulder 60 on hub 28 and a ring 62 which is received by groove 64 on the hub 28.
An annular flexible boot 70 has one end 72 fixed to the piston housing 12 and a second end 74 fixed to the carrier 44. The boot 70 prevents exposure of the piston to the environment.
When chambers 41 are pressurized, the pistons 40 move to the left, which forces the carrier 44, bearing 46, hub 28 and sheave 26 to the left, viewing
Oil may be supplied to the drive 10 via a single line (not shown) from a control block (not shown) at the rear of the engine (not shown). The control block is preferably connected to a pressure supply line (not shown) from a transaxle (not shown) and a return to sump line attached in addition to the line to the drive 10. A solenoid actuated control valve (not shown) may be used to control oil flow within the block (not shown). The housing 10 preferably has a single oil inlet and drilled passages 42 that supply oil to the piston chambers 41. The rotating sheave 26 slides along the rotating shaft 16 until the valve (not shown) stops the supply or return of oil, or the moving sheave 26 contacts the fixed sheave 24. The bearings 16, 18 and 46 may be independently greased and sealed. The housing 10 is preferably sealed to the engine (not shown) with a gasket (not shown).
Rotating seals 29 and 31 are not required to contain pressurized fluid. The hydraulic fluid used to pressurize the piston chambers 41 may be transaxle fluid which is cleaner than engine oil for increased seal reliability. The smaller pistons 40 are easier to manufacture and handle than one large piston. The O-ring seals 58 have a near zero leak rate. With multiple pistons 40, the drive 10 can still operate if a single piston seizes into the housing 12. The bearings 18, 20 and 46 require no service and are not dependent on engine oil for lubrication. The oil passages 42 within the housing 12 minimize leak points, simplify assembly, and offer better protection to the oil supply than external lines and fittings. The O-ring 58 in the carrier 44 keeps the outer race 48 of the bearing 46 from spinning without a press fit assembly and allows more consistent resistance to rotation of the bearing 46 over a large range of temperatures. The oil stays cooler because it does not circulate through the drive 10 constantly. The drive 10 can be controlled by a remotely mounted valve (not shown) to minimize the total length of hoses and tubing (not shown).
While the present invention has been described in conjunction with a specific embodiment, it is understood that many alternatives, modifications and variations will be apparent to those skilled in the art in light of the foregoing description. Accordingly, this invention is intended to embrace all such alternatives, modifications and variations which fall within the spirit and scope of the appended claims.
