US20120058853A1 - Lubrication system for right-angle drives used with utility vehicles - Google Patents
Lubrication system for right-angle drives used with utility vehicles Download PDFInfo
- Publication number
- US20120058853A1 US20120058853A1 US13/296,106 US201113296106A US2012058853A1 US 20120058853 A1 US20120058853 A1 US 20120058853A1 US 201113296106 A US201113296106 A US 201113296106A US 2012058853 A1 US2012058853 A1 US 2012058853A1
- Authority
- US
- United States
- Prior art keywords
- oil
- shaft
- pinion shaft
- pinion
- gear
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/14—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing the motor of fluid or electric gearing being disposed in or adjacent to traction wheel
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
- B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/342—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having a longitudinal, endless element, e.g. belt or chain, for transmitting drive to wheels
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/34—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles
- B60K17/356—Arrangement or mounting of transmissions in vehicles for driving both front and rear wheels, e.g. four wheel drive vehicles having fluid or electric motor, for driving one or more wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/0427—Guidance of lubricant on rotary parts, e.g. using baffles for collecting lubricant by centrifugal force
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2200/00—Type of vehicles
- B60L2200/40—Working vehicles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0469—Bearings or seals
- F16H57/0471—Bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0493—Gearings with spur or bevel gears
- F16H57/0495—Gearings with spur or bevel gears with fixed gear ratio
Definitions
- This invention is used to lubricate bearings which support a high speed pinion gear (input gear) mounted in a pinion housing which facilitates use of a right angle-drive (gear reducer) with utility vehicles.
- the invention is in the field of right-angle drives powered by high speed motors for use in utility vehicles.
- the right angle drives (gear reducers) are used in, for example, drive systems for utility vehicles but may be used in other applications.
- Skid-Steer® Loader Machines as made famous by manufacturers such as Bobcat® and the like have been powered almost exclusively by hydraulics. Skid-Steer® is a registered trademark of Arts-way Manufacturing Co., Inc., a Delaware Corporation. Bobcat® is a registered trademark of Clark Equipment Company of New Jersey.
- the pump usually provides power to two independently controlled hydraulic motors one for each side of the machine.
- the output of each motor drives a drive sprocket with two sets of sprocket teeth.
- One set of sprocket teeth drives a chain that goes to a front wheel sprocket and the other set of sprocket teeth drives a chain that goes to the rear wheel sprocket.
- the hydraulic pump also provides power for lifting functions and power takeoffs for implements that can be connected to the machine.
- FIG. 1 is a plan view of an electric drive system of U.S. Pat. No. 4,705,449 to Christianson et al. wherein battery 28 supplies electric power to two traction motors 60 , 64 which in turn are coupled 84 to a gear reducer 82 .
- the '449 patent states at col. 4 line 10 et seq.: “a first traction motor 60 provides the motive force for the left-hand side of the vehicle and a second traction motor 64 provides the motive force for a right-hand side of the vehicle 66 .
- Both the first traction motor 60 and the second traction motor 64 are powered by a battery pack 28 .
- the traction motor 64 is connected to a spur gear reduction assembly 82 through a coupling 84 .
- the spur gear reduction assembly engages a chain 86 which in turn engages a right rearward gear 74 and left forward gear 90 , which are respectively connected to wheels 14 a and 14 b through axles 92 and 94 .
- the traction motor 60 is operated independently of the traction motor 64 thereby permitting the wheels 14 c, 14 d to operate at different speed than wheels 14 a and 14 b to create skid steering.”.
- U.S. Pat. No. 4,705,449 to Christianson et al. discloses the use of two electric traction motors.
- the motors are not identified by type in Christianson et al as either DC or AC.
- the motors are DC electric motors as they are controlled by a device identified in the '449 patent to Christianson, namely, a General Electric EV 1 SCR Controller, which is designed to control DC motors.
- the General Electric EV 1 SCR Controller describes the use of rectifiers to pulse power to DC motors and has no provision for the control of AC motors.
- the EV 1 SCR Controller has been used in numerous automobiles (electric vehicles) in conjunction with DC series wound motors which provide high current and high torque at low rpm.
- DC traction motors have been used in applications involving forklifts and similar vehicles in the past.
- Internal combustion engines are not favored in such applications because an internal combustion engine produces zero torque at zero engine speed (RPM) and reaches its torque peak later in its operating range.
- Internal combustion engines generally require a variable-ratio transmission between the engine and the wheels to match engine speed to the road speeds and loads encountered.
- a clutch must be provided so that the engine can be mechanically decoupled from the wheels when the vehicle stops. Additionally, some slippage of the engine with respect to the drive train occurs while starting from a stop.
- Direct current electric traction motors produce considerable torque at zero RPM and thus may be connected directly to the wheels. Alternating current motors, hydraulic motors and pneumatic motors also produce torque at zero RPM.
- traction motor is usually referred to in the context of a direct current motor, the term is also applicable to alternating current motor applications as well. Additionally, the term traction motor is used to describe any motor of whatever type used to supply torque and power to a vehicle's wheel, tracks, etc.
- an electric motor it may be an alternating current motor or it may be a direct current motor.
- high speed electric motors are smaller in size, lighter in weight, and less expensive than low speed motors.
- alternating current motors are smaller than direct current motors.
- a bearing lubrication device which includes an output shaft carrier housed within a gear housing is disclosed and claimed.
- the output shaft resides partially within the output shaft carrier and upper and lower bearings support the output shaft.
- the output shaft carrier includes a first trough for catching lubricating fluid which is slung by an oil slinger.
- the first trough is in lubricating fluid communication with the upper bearing which pumps the lubricating fluid through the bearing and into an upper passageway which terminates in an opening from which the lubricating fluid emanates.
- U.S. Pat. No. 5,887,678 to Lavender discloses a lubrication apparatus for shaft bearings which includes a trough extending radially outwardly and inclined downwardly in a direction toward the shaft bearing.
- U.S. Pat. No. 6,439,208 to Jones discloses a centrifugal supercharger having a lubricating slinger.
- U.S. Pat. No. 6,698,762 to Newberg et al. discloses a rotary device shaft with oil slinger groove.
- United States Patent Application Publication No. US 2003/0159888 A1 to Burkholder discloses a disk oil slinger assembly.
- United States Patent Application Publication No. US 2006/0104838 A1 to Wood discloses an integrated eccentric flywheel slinger.
- a bearing lubrication device in a right angle gear reducer includes a gear housing having an interior portion and a lubricating fluid reservoir therein.
- the principles and structure disclosed herein may be used in a gear reducer whether or not it is denoted as a right-angle gear reducer.
- An oil slinger, rotating pinion shaft, pinion shaft housing, and bearings for supporting the pinion shaft within the pinion shaft housing work together to provide a continuous supply of oil to the bearings.
- the pinion shaft includes first and second radially and longitudinally extending passageways therethrough which supply oil from a recess in the nose end of the pinion shaft to the bearings.
- Oil is slung from the reservoir into the recess of the rotating pinion shaft where it is forced centrifugally outwardly in the cylindrical recess and forced centrifugally through the radially and longitudinally extending passageways to an oil supply chamber formed by the rotating pinion shaft, shaft housing and bearings.
- Tapered roller bearings pump the oil from the oil supply chamber back to the oil reservoir.
- Oil passageways in the shaft housing enable the return of oil from the first bearing set while the other bearing set returns the oil directly to the reservoir. In this way a very compact and efficient gear reducer is produced having a shaft driven oil slinger which is compact and minimizes the number of parts necessary.
- a method for lubricating bearings supporting a shaft in a gear box comprises the steps of: slinging oil from a lubricating oil reservoir using an oil slinger toward a first end of a pinion shaft; collecting oil in a cylindrical recess in the first end of the pinion shaft; rotating the shaft and forcing the collected oil radially outwardly in the cylindrical recess and into a passageway communicating with the recess and extending longitudinally and radially from the recess to the oil supply chamber formed by the shaft, the bearings and the shaft housing; pumping oil from the chamber through the bearings; and, returning the oil to the lubricating oil reservoir. Additionally, the step of returning the oil pumped from the oil return chamber to the lubricating oil reservoir is performed using a return passageway through the shaft housing.
- the right-angle drive described herein is particularly useful in a utility vehicle.
- the vehicle includes: a frame; a high speed motor having an output shaft; a right-angle gear reducer driven by the output shaft of the high speed motor; the right-angle gear reducer includes a bearing lubrication device comprising: a gear housing having an interior portion and a lubricating fluid reservoir therein; an oil slinger; a pinion shaft; a pinion shaft housing; a bearing for supporting the pinion shaft within the pinion shaft housing; the pinion shaft includes a passageway therethrough; and, the oil slinger supplies oil to the passageway communicating the oil to the bearing by way of an oil supply chamber;
- the right-angle gear reducer includes an output carrier interconnected with an output shaft;
- the output shaft includes first and second chain drive sprockets; the forward and rearward wheel shafts each have a wheel sprocket; a first and second chain; the first chain interengaging the first chain drive sprocket and the forward wheel s
- Another method for using a high-speed motor in a utility vehicle includes the steps of: orienting two high speed motors having shaft driven pinion gears parallel to the rails of the vehicle; mounting right angle planetary gear reducers in engagement with said shaft driven pinion gears, each of the planetary gear reducers include a gear driven by said shaft driven pinion gears, the gear driven by said shaft driven pinion gear drives a shaft which includes a second pinion gear which drives a planetary gear set and carrier reacting against a ring gear in the casing of the planetary gear reducer, the carrier of the planetary gear reducer includes a splined output, and each of the splined outputs being on the same axis; lubricating bearings supporting the pinion gear shafts with an oil slinger, the pinion gear shafts include a nose portion having a recess, at least one port, and at least one radially and longitudinally extending passageway communicating lubricating oil to a supply chamber feeding the lubric
- Electric motors typically rotate at much higher RPM than hydraulic motors, particularly those suitable for skid-steer loaders. It is desirable to minimize the size of the drive train components so as to maximize the space available for batteries and controls.
- the vehicle described herein may employ Nickel Metal Hydride, Lithium Ion, Lithium Ion polymer, lead acid batteries or other battery technology.
- the input to the gear box is an offset helical gear driven by a pinion.
- a planetary sun pinion inputs to the planetary stage.
- Planetary gear sets provide torque multiplication in compact packages.
- the output of the gear box is a carrier with a planetary gear-set reduction including a stationary ring gear.
- the gear box casing includes a ring gear which is a reaction gear and intermeshes with a three-gear planetary set.
- the carrier of the planetary gear set includes a spline which intermeshes with a splined output shaft.
- the offset reduction in the gearbox is an important aspect of the invention as it enables the electric motors to be placed side to side.
- Use of electric motors is enabled in this application by offsetting the gear box. In this way the left and right side motors can be mounted side-by-side without interference while still maximizing available space for other components such as batteries and controls.
- the offset gear box may be oriented differently (i.e., rotated 180 degrees) with the motors side by side.
- this example may result in reducing the width of the vehicle it may also result in increasing the length of the vehicle.
- this example may be used to drive one of the wheel shafts directly.
- a wheel driven utility vehicle includes a frame and two high speed alternating current electric motors arranged side by side for driving the vehicle.
- a variable frequency alternating current drive is utilized to control the speed of the motors and hence to control the direction and turning of the utility vehicle.
- high speed alternating current motors high speed direct current motors, high speed hydraulic motors and/or high speed pneumatic motors may be used.
- Each alternating current motor has an output which drives an offset planetary gear reducer.
- Each offset planetary gear reducer is affixed to the electric motor (or other motor type) and includes an output carrier interconnected with an output shaft.
- Each output shaft includes first and second chain drive sprockets which drive chains interconnected with shafts driving the front and rear wheels respectively.
- Each offset planetary gear reducer enables use of space saving high speed relatively low-torque alternating current electric motors (or other motors with similar performance characteristics) with attendant large speed reductions. Gear reduction enables the production of sufficient torque at the wheels of the vehicle. Applications in addition to utility vehicles are also specifically contemplated.
- a utility vehicle drive system comprises two alternating current electric motors (or other high speed motors with similar performance characteristics) each having a shaft driven pinion gear. Intermediate gears engage shaft driven pinion gears which in turn drive planetary gears.
- Each of the planetary gear reducers include an output spline and each of the output splines are axially aligned with each other.
- a method for using a high-speed electric motor (or high-speed hydraulic, pneumatic or direct current motors) in a utility vehicle includes the step of orienting the motors having shaft driven pinion gears side by side such that their shaft driven pinion gears are arranged on opposite sides of the vehicle.
- the offset planetary gear reducers are mounted in engagement with the shaft driven pinion gears.
- Each of the planetary gear reducers include a gear driven by the shaft driven pinion gear.
- the gear driven by the shaft driven pinion gears includes a shaft portion formed as a second pinion sun gear which drives a planetary gear set and carrier.
- the planetary gear set reacts against a ring gear in the casing of the planetary gear reducer.
- the carrier of the planetary gear reducer includes a splined output.
- Each of the splined outputs are on the same axis of the other splined output located on the other side of the vehicle.
- the method includes driving an output shaft coupled to the splined output of the carrier of the planetary gear reducer.
- the method includes driving, with chains, the wheel shafts of the vehicle.
- the pinion gear shaft includes a recess and passageways therethrough communicating with a first chamber for supply of oil to the bearings.
- a second chamber returns oil through the pinion housing adapted for return of oil to the reservoir within the main housing.
- FIG. 1 is a plan view of a prior art Skid-Steer vehicle powered by two DC traction motors.
- FIG. 2 is a top plan view of the utility vehicle illustrating two alternating current motors oriented side by side with each having an offset planetary gear reducer driving a respective output shaft.
- FIG. 2A is an enlarged portion of FIG. 2 illustrating a portion of the left side of the vehicle.
- FIG. 2B is an enlarged portion of FIG. 2A illustrating the gear reducer and output shaft.
- FIG. 2C is an exploded view of the input to the gear reducer, the gear reducer, and the output shaft.
- FIG. 2D is a perspective view of the carrier and the output shaft.
- FIG. 2E is a perspective view of the offset planetary gear speed reducer.
- FIG. 3 is a block diagram of the method for using high speed alternating current electric motors with offset planetary gear reducers.
- FIG. 4 is a top plan view of the utility vehicle illustrating two alternating current motors in conjunction with two right-angle drives.
- FIG. 4A is a cross-sectional view of one of the right-angle drives and motor.
- FIG. 4B is a perspective view of one of the right-angle drives.
- FIG. 4C is a perspective view of the pinion shaft housing.
- FIG. 4D is an end view of the pinion shaft housing.
- FIG. 4E is a cross-sectional view of the pinion shaft housing taken along the lines 4 E- 4 E of FIG. 4D .
- FIG. 4F is a cross-sectional view of the pinion shaft housing taken along the lines 4 F- 4 F of FIG. 4D .
- FIG. 4G is an enlargement of a portion of FIG. 4A .
- FIG. 4H is an enlarged view similar to FIG. 4F with the pinion shaft and bearings inserted therein.
- FIG. 4I is a perspective view of the pinion shaft and spiral bevel pinion.
- FIG. 4J is a top view of the pinion shaft and spiral bevel pinion.
- FIG. 4K is a view of the nose end of the pinion shaft and spiral bevel pinion.
- FIG. 4L is a cross-sectional view of the gear casing illustrating the spiral bevel pinion and the spinal bevel gear.
- FIG. 5 is a process flow chart for lubricating bearings supporting a pinion shaft in a pinion shaft housing.
- FIG. 6 is a process flow chart for using high speed motors in a utility vehicle with right angle planetary gear reducers.
- FIG. 2 is a top plan view 200 of the utility vehicle illustrating two alternating current electric motors 201 , 202 oriented side by side with each having an offset planetary gear reducer 203 , 204 driving a respective output shaft 208 , 214 .
- reference numerals 201 , 202 refer to high speed alternating current electric motors, it is specifically contemplated that other high speed motor types may be used such as direct current motors, hydraulic motors and pneumatic motors.
- the utility vehicle includes a frame 205 , 206 , 250 , 251 for supporting vehicle components.
- side frame member 205 is on the left hand side of the vehicle and side frame member 206 is on the right hand side of the utility vehicle.
- the two side frame members 205 , 206 are shown in section in FIG. 2 , FIG. 2A , and FIG. 2B .
- Frame side member 205 supports first chain driven wheel shaft 210 .
- Sprocket 210 S is formed as part of the wheel shaft 210 or alternatively is a separate sprocket affixed or attached to the wheel shaft 210 .
- Frame side member 205 also supports the output shaft 208 of the planetary gear reducer 203 .
- Output shaft 208 includes two sprockets 208 S which are identical.
- the sprockets 208 S may be an integral part of shaft 208 or they may be separately attached to the shaft.
- a metal chain 210 interengages sprockets 210 S and 208 S and communicates horsepower and torque therebetween.
- the reduction ratio of output shaft driving sprocket 208 S to driven sprocket 210 S is approximately 2.5-5:1 such that for every rotation of the output shaft 208 the forward sprocket 210 S and wheel shaft 210 turns 0.4 to 0.2 of a turn or revolution. Reduction in speed of the driven sprocket 210 S results in a corresponding increase in torque for a given applied power.
- Metal chain 211 interengages sprockets 212 S and 208 S and communicates horsepower and torque therebetween.
- the reduction ratio of the output shaft driving sprocket 208 S to driven sprocket 212 S is approximately 2.5-5:1 such that for every rotation of the output shaft 208 the rearward sprocket 212 S and wheel shaft 212 rotates just 0.4 to 0.2 of a turn or revolution.
- the reduction in speed of the driven sprocket 212 S results in a corresponding increase in torque for a given applied power.
- driven sprockets 216 S, 217 S, shafts 216 , 217 , frontward and rearward wheels 216 A, 217 A, sprockets 214 S, shaft 214 and chains 213 , 215 on the right side and within the right frame 206 are identical to the left frame side member 205 and frame 205 .
- the reduction ratio of the output shaft driving sprocket 214 S to driven sprockets 216 S, 217 S is the same as in connection with the left side of the vehicle, namely, approximately 2.5-5:1.
- Speed reduction of approximately 2.5-5:1 just described are in addition to the speed reduction of the planetary gear reducers 203 , 204 which are described further herein.
- Alternating current motors 201 , 202 reside side by side and have output shafts 221 S, 222 S with pinion gears 221 , 222 thereon for driving two offset planetary gear reducers 203 , 204 to effect speed reduction and increase torque.
- a helical pinion gear 221 H and a helical driven gear 223 H are a helical driven gear 223 H.
- Full load electric motor torque is generally defined as follows:
- high speed electric motors are smaller in size, lighter in weight, and less expensive than low speed motors.
- alternating current motors are smaller than direct current motors.
- direct current motors are smaller than direct current motors.
- planetary gear reducers 203 , 204 Use of planetary gear reducers 203 , 204 with alternating current motors 201 , 202 saves space.
- the motors may be hydraulic, pneumatic or direct current motors.
- Reducers 203 , 204 are approximately 8 inches in diameter and approximately 5.5 inches deep and occupy a volume of approximately 300 cubic inches.
- FIG. 2A is an enlarged portion 200 A of FIG. 2 illustrating a portion of the left side of the vehicle and FIG. 2B is a further enlargement of a portion 200 B of FIG. 2A illustrating the gear reducer 203 and pinion 221 on output shaft 221 S in more detail.
- the alternating current motors 201 , 202 are controlled by a variable frequency drive (not shown) to control the speed of the motors.
- the alternating current motors are three phase motors.
- Each of the offset planetary gear reducers 203 , 204 include a housing having a ring gear 224 affixed thereto. Ring gear 224 is trapped between housing portions 203 , 203 A of the reducer. Seals 224 S prevent leakage of lubricant from within the gear casing.
- Each of the planetary gear reducers 203 , 204 includes a carrier 230 having planetary gears 225 , 226 , 229 intermeshing with the ring gear 224 and an output spline 230 T.
- the planetary gear reducer illustrated has three planetary gears, any reasonable number of planetary gears may be used.
- Each of the planetary gear reducers includes a gear 223 having teeth 223 T driven by the pinion gear 221 of the output shaft 221 of the alternating current motor 201 .
- the gear 223 driven by the pinion gear 221 of the output shaft 221 S of the alternating current motor 201 includes a shaft portion forming a sun pinion 227 with gear teeth 227 T.
- Chain drive sprockets 208 S, 214 S in combination with wheel shaft sprockets 210 S, 212 S, 216 S and 217 S effect a speed reduction in the approximate range of 2 . 5 - 5 : 1 . That is, for every one rotation of the chain drive sprocket 208 S, the wheel sprockets 210 S, 212 S will rotate 0.4 to 0 . 2 of a revolution.
- Other speed reductions are specifically contemplated. Since torque is inversely proportional to the shaft rotational speed, torque is increased with a reduction in speed.
- Offset speed reducer as disclosed herein enables the efficient use of space and provides the same torque to the wheel with less input torque supplied by the high speed electric motor.
- the efficiency of the offset speed reducer is approximately 95% at rated load.
- Use of the offset speed reducer and electric motors enables use of high speed, light weight electric motors which are smaller in diameter and output less torque than slower, heavier larger motors whether they are alternating current motors or direct current motors.
- the savings in space, weight and money attained by use of the offset planetary gear reducers with high speed motors is considerable.
- Use of planetary gear reducers provides a stable transmission of power with torque amplification inversely proportional to the speed reduction.
- the planetary gear reducers of the instant invention weigh approximately 100 pounds but can vary in weight depending on the materials used such as steel, stainless steel or aluminum.
- the gears 223 , 225 , 226 , 229 and the carrier 230 are made of steel or stainless steel.
- Aluminum may be used for the gearbox casing 203 , 203 A if extremely light weight is desired.
- the low weight of the gear reducer having a volume of about 300 cubic inches (approx. 8 inches in diameter and 5.5 inches deep) in combination with a light-weight alternating current motor provides a compact low cost arrangement when placed side by side as illustrated in FIG. 2 .
- Alternating current electric motors 203 , 204 are water cooled motors and run at 7,000 to 8,000 RPM. At approximately 7500 RPM the three phase electric motor outputs approximately 14.75 ft-lbs. of torque which equates to approximately 21 horsepower. The peak starting torque is about 77 ft-lbs.
- the motors to be used are about 14 inches long and 8 inches in diameter and have a volume of approximately 700 cubic inches.
- FIG. 2C is an exploded view 200 C of the input to the gear reducer 221 T, the gear reducer 203 , and the output shaft 208 .
- sun pinion 227 is supported by bearing 223 B and 227 B.
- Use of gear 223 enables the planetary gear reducer to be offset as it is driven by pinion 221 which is on the shaft 221 S of the electric motor.
- Three planet gears 225 , 226 and 229 and, more specifically, their teeth 225 T, 226 T and 229 T intermesh with sun pinion teeth 227 T and ring gear 234 and its teeth 234 T.
- Planet gears 225 , 226 and 229 are supported by bearings (i.e., 235 B) and are pinned to the carrier by pins. See, for example, pin 235 in FIGS. 2A and 2B .
- Pin 225 P restrains pin 235 from movement within the carrier 230 and thus secures gear 225 in place.
- Gear 225 and the other planet gears are, of course, free to rotate but they are securely fastened to the carrier and impart rotational motion to the carrier 230 .
- Reference numeral 225 A indicates intermeshing between planet gear teeth 225 T and ring gear teeth 224 T.
- output shaft 208 is supported by bearings 208 B and 208 C and intermeshes its spline 208 T with spline 230 T of the carrier.
- Planetary gear reducer 203 distributes the load evenly to three planets, 225 , 226 and 229 . As previously indicated any reasonable number of planet gears from 1 to “n” may be used. Reciting the operation of the gear reducer, torque is applied by shaft 221 S through teeth 221 T of pinion 221 which imparts rotational movement and torque to gear 223 . Gear 223 includes sun pinion 227 which by and through its teeth 227 T imparts rotational movement and torque to gears 225 , 226 and 229 via teeth 225 T, 226 T and 229 T.
- planet gears 225 , 226 and 229 are free to rotate and impart rotational movement to carrier 230 effecting a speed reduction which is transmitted to output shaft 208 which is interconnected with the carrier spline 230 T.
- the gearbox 203 , 203 A is separable into two portions 203 and 203 A and they trap ring gear 224 when the gearbox is secured by fastener 240 A to the electric motor 201 and when the portions 203 , 203 A are secured together by fastener 240 .
- FIG. 2D is a perspective view 200 D of the carrier 203 , 203 A, planet gears 229 and 225 , and output shaft 208 with a corresponding spline 208 T.
- FIG. 2E is a perspective view 200 E of the offset planetary gear reducer without bearing 208 B illustrated therein.
- the principal dimensions of the offset planetary gear reducer are approximately 8 inches in diameter and 5.5 inches deep neglecting the input housing 241 which houses pinion 221 .
- the offset planetary gear reducer is generally cylindrically shaped and includes a housing 241 for the shaft driven pinion gear 221 .
- a flange (unnumbered) is fastened to the motor 201 .
- FIG. 3 is a block diagram 300 illustrating a method for using high-speed electric motors in combination with offset planetary gear reducers in a utility vehicle.
- the first step includes orienting two high speed electric motors having shaft driven pinion gears side by side 301 such that their shaft driven pinion gears are arranged on opposite sides of the vehicle.
- the method includes mounting offset planetary gear reducers in engagement with the shaft driven pinion gears 302 .
- Each of the planetary gear reducers 203 , 204 include a gear driven by the shaft driven pinion gears 221 , 222 .
- the gear driven by the shaft driven pinion gears includes a shaft portion formed as a sun pinion gear 227 which drives a planetary gear set and carrier 230 reacting against a ring gear 224 in the casing of the planetary gear reducer 203 , 203 A.
- the carrier 230 of the planetary gear reducer includes a splined output 230 T and each of the splined outputs 230 T are on the same axis.
- the method further includes driving an output shaft 208 , 214 coupled to the splined output 230 T of the planetary gear reducer.
- the method includes driving, with chains ( 209 , 211 , 213 , 215 ), the wheel shafts ( 210 , 212 , 216 , 217 ) of the vehicle.
- FIG. 4 is a top plan view 400 of the utility vehicle illustrating two alternating current motors 495 A, 496 A in conjunction with two right-angle drives 495 , 496 .
- Each of the right angle drives includes a main housing 401 and a pinion housing 402 .
- Frame supports 250 , 251 support motors 495 A, 496 A.
- Main housing 401 and gear housing 403 are preferably made of 8620 H annealed steel. See FIG. 4A .
- Main housing 401 is approximately 10′′ in diameter and 8′′ long.
- Pinion housing 402 is approximately 3′′ long and 4′′ in diameter.
- Motors 495 A, 496 A are preferably electric motors but may be hydraulic or pneumatic motors.
- FIG. 4A is a cross-sectional view 400 A of one of the right-angle drives 495 and motor 495 A taken along the lines 4 A- 4 A of FIG. 4B .
- a portion of the main housing defines a fluid reservoir which holds oil 498 at a level as indicated by reference numeral 499 . See FIG. 4L .
- Oil 498 is illustrated in the reservoir formed by the main housing 401 and the spacer 401 A and it is used to lubricate the intermeshing spiral bevel pinion gear and the spiral bevel gear as well as the planetary output gear set. Additionally, oil 498 is used to lubricate all bearings in the pinion housing and the main housing.
- Pinion housing 402 includes a flange 402 A for connection to the motor 495 A.
- Pinion housing 402 further includes a flange 402 B for connection with gear box 401 .
- Spacer 401 A is used to interconnect the main housing 401 of the right angle drive 495 to the vehicle sidewall 205 .
- FIG. 4B is a perspective view 400 B of one of the right-angle drives 495 and motor 495 A.
- flange 402 A secures the pinion housing to the motor 495 A.
- Gear housing 403 is secured to main housing 401 with threaded bolts 435 .
- Gear housing 403 includes a polycarbonate cap 404 secured therein by a snap ring 431 and sealed with an O-ring 428 .
- the main housing is attached to the spacer 401 A and the support 205 using bolts not shown.
- Spiral bevel pinion sometimes referred to herein as the spiral bevel pinion, gear 405 and spiral bevel gear 406 are preferably made of 8620 H annealed steel.
- motor mounting bolts 434 secure the motor 495 A to the flange 402 A of the pinion housing.
- Inspection plugs 438 , 439 and 439 are illustrated in FIG. 2B and enable quick and easy inspection of the main housing and/or enable the addition of oil.
- bearings 419 A, 419 B support the spiral bevel gear 406 which is driven by the spiral pinion gear 405 .
- Bearings 419 A, 419 B are supported by cones 422 , 422 A and cups 423 , 423 A.
- Spiral bevel gear bearing retention plate 412 traps and secures bearing 419 A against stop 479 .
- the retention plate is made of mild steel.
- Retention bolt 435 secures spiral gear bearing retention plate 412 to the spiral bevel gear 406 .
- a shim 419 is used between the bearing retention plate 412 and the gear body 406 .
- Spiral gear housing 403 is sealed with respect to main housing 401 with O-ring seals 427 .
- Pinion housing 402 is preferably made of mild steel as is gear housing 403 .
- Gear housing 403 is secured to the pinion housing 402 using a pinion housing shim pack 418 and a gear housing shim pack 417 .
- Pinion housing seal 426 seals the gear housing 403 and the main housing 401 to the pinion housing 402 .
- spiral pinion gear teeth 405 intermesh with spiral bevel gear teeth 406 A of the spiral gear 406 .
- Spiral bevel gear 406 includes a spline 476 which intermeshes with a reciprocal spline 445 in the sun gear shaft 407 to drive the oil slinger 413 and the sun gear 445 A.
- Sun gear shaft retaining ring 432 positions sun gear shaft 407 and prevents rightward travel of the shaft 407 when viewing FIG. 4A .
- Thrust plate 414 prevents shaft 407 from travel in the leftward direction when viewing FIG. 4A .
- the input to the gear box is the pinion shaft 405 and spiral bevel gear 405 .
- Pinion shaft 405 A drives gear 406 which in turn drives sun gear shaft 407 and sun gear 445 A.
- the planetary sun gear inputs to the planetary stage. Planetary gear sets provide torque multiplication in compact packages.
- the output of the gear box 495 is a carrier 410 with a planetary gear-set reduction including a stationary ring gear 409 .
- Carrier 410 is preferably made of D7003 grade steel.
- the main housing or casing 401 includes ring gear 409 which is a reaction gear and intermeshes with a three-gear planetary set comprising planet gears 408 .
- Ring gear 409 is secured to the main housing 401 though bolts not viewed in FIG. 4A .
- the carrier 410 of the planetary gear set includes an internal spline 481 which intermeshes with a splined output shaft 208 A which is the output to drive the vehicle.
- the right angle planetary gear reducers 495 , 496 effect a speed reduction in the approximate range of between 20-30:1. That is for every revolution of the input pinion gear 405 , the carrier 410 will rotate 1/20 to 1/30 of a revolution.
- Other speed reductions are specifically contemplated As discussed above in regard to FIGS. 2-2E , use of electric motors, hydraulic motors and/or pneumatic motors is specifically contemplated.
- the right angle planetary gear drive with the above stated speed reduction enables use of a utility vehicle having a relatively narrow width between side rails.
- planet gears 408 include gear teeth 408 T driven by sun gear teeth 445 A.
- Planet gears 408 are pinned to the carrier 410 using roll pins 433 mounted to planet pins 411 which provide support for the gears. Needle roller bearings 424 , spacers 416 and thrust bearings 415 position and support the planet gears 408 for rotation about the planet pins 411 .
- FIG. 4G is an enlargement 400 G of a portion of FIG. 4A .
- Pinion housing 402 is generally cylindrically shaped and carries pinion shaft 405 A supported by roller bearings 451 and 452 .
- Roller bearings 451 are supported by cup 421 and cone 420 and the roller bearings 452 are supported by cup 421 A and cone 420 A.
- Inner circumferential stop 456 in conjunction with locknut 429 and pinion tanged lockwasher 430 support and secure bearings 451 and 452 within the pinion housing.
- Tang 460 of lockwasher 430 interengages slot 459 in pinion shaft 405 A and is compressed by locknut 429 threadingly interengaging 429 A shaft 405 A.
- pinion shaft 405 A includes grooves 455 which interengage motor coupling 455 A for driving the pinion shaft.
- Pinion shaft rotates at approximately 6-7000 rpm.
- Heat dissipation from the bearings is addressed by supplying oil to chamber 453 formed between roller bearings 451 , 452 , pinion shaft 405 A and the interior of the pinion housing 402 .
- Chamber 453 is fed by ports 446 B, 447 B in the pinion shaft 405 A.
- Ports 446 B, 447 B are supplied by passageways 405 B, 405 C.
- Passageways 405 B, 405 C are fed by ports 405 E, 405 F which are located in cylindrical recess 405 D.
- Ports 405 E and 405 F are located diametrically opposite each other in cylindrical recess 405 D. See, FIG. 4L , a cross-sectional view 400 L of the gear casing. Cylindrical recess 405 D receives oil from oil slinger 413 as viewed in FIG. 4A as pinion shaft 405 A rotates.
- Oil slinger 413 is coupled to shaft 407 by a press fit or threaded interconnection 407 A and rotates therewith.
- Gear 406 includes spiral bevel teeth 406 A interengaging teeth 405 of spiral bevel pinion 405 A.
- Oil slinger 413 is approximately 4.5 inches in diameter.
- FIG. 4L is a cross-sectional view 400 L of the gear casing indicating shaft 407 in phantom driving oil slinger 413 which picks up oil 499 from the reservoir within the main housing 401 and deposits it into the rotating recess 405 D.
- FIG. 4A illustrates oil flow as indicated by flow arrow 471 from the oil slinger 413 .
- chamber 453 fills with oil after shaft 405 A makes a sufficient number of revolutions (following startup) and supplies oil to tapered roller bearings 451 and 452 whereby oil is pumped outwardly through the bearings.
- Tapered roller bearings 452 pump oil to reservoir 499 and tapered roller bearings 451 pump oil to oil return chamber 454 .
- Chamber 454 is bounded by pinion housing 402 , lock washer 429 , lock nut 429 , pinion shaft 405 A, motor coupling 455 A and motor input seal 425 .
- seal 425 is a Viton seal.
- Wave spring 442 resides between the motor and the motor input seal 425 .
- Chamber 454 communicates with ports 494 , 497 in inner circumferential groove 448 which in turn communicate with passageways 446 A and 447 A. See FIG. 4H .
- Ports 446 B and 447 B are formed in inner circumferential groove 448 in the interior of the pinion housing 402 .
- Pinion housing 402 is generally cylindrically shaped with flanges 402 A, 402 B for interconnection with the main housing 401 of the gear box and the motor 495 A.
- Passageways 446 A, 447 B terminate, respectively, in ports 446 , 447 which permit oil to be discharged into the main housing 401 which serves and forms the oil reservoir.
- Ports 446 and 447 are preferably arranged vertically such that port 446 is submerged below the oil level 499 .
- FIG. 4C is a perspective view 400 C of the pinion shaft housing 402 illustrating motor flange 402 A and main housing flange 402 B. Ports 446 and 447 are illustrated in their vertical orientation. Other orientations of the ports 446 and 447 are specifically contemplated. Access ports 440 A are illustrated in FIG. 4C as are flange bolt holes 449 , 450 . Referring to FIGS. 4A and 4H , access ports 440 A are illustrated with plugs 440 threaded therein.
- FIG. 4D is an end view 400 D of the pinion shaft housing illustrating the vertical orientation of ports 446 , 447 . Ordinarily port 446 will be submerged in oil. Other configurations with more or fewer oil return ports may be used.
- FIG. 4H is an enlarged view 400 H similar to FIG. 4F with the pinion shaft 405 A and bearings 451 , 452 inserted therein.
- Groove 466 is an outer circumferential groove in the pinion shaft 405 A viewed in FIG. 4H and 4I .
- Ports 446 B and 447 B are formed in the outer circumferential groove 466 as viewed in FIGS. 4G and 4H .
- Ports 494 and 497 are illustrated in FIG. 4H in communication with oil return chamber 454 . Oil is pumped by tapered roller bearings 451 into oil return chamber 454 and groove 448 in the pinion shaft housing where it flows into passageways 446 A and 447 A to ports 446 and 447 respectively.
- Port 446 is actually submersed below the oil line 499 as illustrated in FIG. 4L .
- Bearings 451 , 452 are submersed in oil when the motor 495 A is started and pinion shaft 405 A begins to rotate.
- the bearings are lubricated adequately by submersion in the oil because the pinion shaft (although rotating at approximately 6000 to 7000 rpm) has not yet generated too much heat for the bearings to withstand since they are already lubricated due to their partial submersion in the oil.
- Full lubrication occurs very quickly as the oil slinger 413 gathers oil from the reservoir and slings or throws it into recess 405 D and thereafter through the pinion shaft 405 A.
- bearings 419 , 419 A support sun gear shaft 407 and are adequately lubricated by oil in the reservoir. Sun gear shaft 407 rotates considerably slower than the input pinion shaft 405 A thus generating less heat. Bearings 419 , 419 A sit partially submerged in oil when shaft 407 is not rotating.
- Oil is slung from the outer circumference 413 A of the oil slinger 413 as illustrated by flow arrow 471 in FIG. 4A .
- Some oil may be picked up from the sides of the oil slinger but the majority of oil 498 is picked up and slung from the outer circumference 413 A of the oil slinger.
- the oil slinger 413 is disc shaped and the outer circumference is not contoured and roughened. However, it is specifically contemplated that various shapes and configurations of oil slingers may be used such that the surfaces of the oil slinger are contoured or roughened.
- the oil slinger disc 413 is preferably made of mild steel.
- FIG. 4E is a cross-sectional view 400 E of the pinion shaft housing 402 taken along the lines 4 E- 4 E of FIG. 4D .
- Inner circumferential groove 448 is illustrated in FIG. 4E along with bearing stop 456 .
- Bearing stop 456 and pinion shaft 405 A secure tapered roller bearings 452 in place.
- Locknut 429 used with lockwasher 429 A secures bearing 451 against bearing stop 456 . See FIGS. 4G and 4H .
- FIG. 4F is a cross-sectional view 400 F of the pinion shaft housing taken along the lines 4 F- 4 F of FIG. 4D and illustrates the oil return passageways 447 A, 447 and 446 A, 446 without the pinion shaft 405 A inserted therein.
- FIG. 4I is a perspective view 4001 of the pinion shaft 405 A and gear 405 .
- FIG. 4I provides a view of the outer circumferential groove 466 communicating with port 446 B as well as slot 459 used in locking conjunction with tanged lockwasher 430 .
- Recess 405 D in the nose of the pinion gear and shaft reveals port 405 F therein.
- Pinion shaft 405 A illustrates exterior threads 429 A for interconnection with locking nut 429 as illustrated in FIG. 4A for the purpose of trapping the bearings 451 , 452 .
- FIG. 4J is a top view 400 J of the pinion shaft 405 A and gear 405 and FIG. 4K is a view 400 K of the nose end of the pinion shaft 405 A and gear 405 .
- Recess 405 D and ports 405 E and 405 F are viewed in FIG. 4K .
- FIG. 4L is a cross-sectional view 400 L of the gear casing indicating shaft 407 in phantom driving oil slinger 413 which picks up oil 499 from the reservoir within the main housing 401 and deposits it into the rotating recess 405 D of the pinion shaft 405 A.
- Pinion spiral bevel gear teeth 405 intermesh with spiral bevel gear teeth 406 A of gear 406 to effect a speed reduction.
- Bearing cones 423 , 423 A are illustrated for support of the shaft 407 as is bearing retention plate 412 and retention bolts 435 .
- FIG. 5 is a process flow chart 500 for lubricating bearings supporting a pinion shaft in a pinion shaft housing.
- a method for lubricating bearings supporting a pinion shaft in a pinion shaft housing is disclosed. The method includes the steps of: slinging oil from a lubricating oil reservoir using an oil slinger at a first end of a shaft 501 ; collecting oil in a cylindrical recess in the first end of the shaft 502 ; rotating the shaft and forcing the collected oil radially outwardly in the cylindrical recess and into a passageway communicating with the recess and extending longitudinally and radially from the recess to a chamber formed by said shaft, the bearings and a shaft housing 503 ; pumping oil from the chamber through the bearings 504 ; and, returning the oil to the lubricating oil reservoir 505 .
- the step of returning the oil to the lubricating oil reservoir may be performed using a return passageway through the shaft housing.
- the step of rotating the shaft and forcing the collected oil radially outwardly in the cylindrical recess includes forcing the collected oil into a second passageway communicating with the recess and extending longitudinally and radially from the recess to the chamber formed by the shaft, the bearings and the shaft housing.
- FIG. 6 is a process flow chart 600 for using high speed motors in a utility vehicle with right angle planetary gear reducers.
- a method for using high-speed motors in a utility vehicle is also disclosed and includes the steps of: orienting two high speed motors having shaft driven pinion gears parallel to the rails of the vehicle 601 ; mounting right angle planetary gear reducers in engagement with the shaft driven pinion gears 602 , each of the planetary gear reducers include a gear driven by the shaft driven pinion gears, the gear driven by the shaft driven pinion gear includes a shaft portion formed as a second pinion gear which drives a planetary gear set and carrier reacting against a ring gear in the casing of the planetary gear reducer, the carrier of the planetary gear reducer includes a splined output, and each of the splined outputs being on the same axis; lubricating bearings supporting the pinion gear shafts with an oil slinger 603 , the pinion gear shafts include a nose portion
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- General Details Of Gearings (AREA)
- Retarders (AREA)
- Automatic Cycles, And Cycles In General (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Lubricants (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
A bearing lubrication device in a right angle gear reducer includes a gear housing having an interior portion and a lubricating fluid reservoir therein. An oil slinger, rotating pinion shaft, pinion shaft housing, and bearings for supporting the pinion shaft within the pinion shaft housing work together to provide a continuous supply of oil to the bearings. The pinion shaft includes two radially and longitudinally extending passageways therethrough which supply oil from a recess in one end of the pinion shaft to the bearings. Oil is slung from the reservoir into the recess of the rotating pinion shaft where it is forced outwardly and through the passageways to a chamber formed by the rotating pinion shaft, shaft housing and bearings. The roller bearings pump the oil from the chamber back to the fluid reservoir. Oil passageways in the shaft housing enable the return of oil from one bearing set.
Description
- This is a continuation-in-part of application Ser. No. 11/690,785 filed Mar. 23, 2007 which is commonly owned. U.S. patent application Ser. No. 11/399,123 filed Apr. 6, 2006 entitled Cascading Oil flow Bearing Lubrication system employs an oil slinger and is commonly owned with the instant patent application.
- This invention is used to lubricate bearings which support a high speed pinion gear (input gear) mounted in a pinion housing which facilitates use of a right angle-drive (gear reducer) with utility vehicles. The invention is in the field of right-angle drives powered by high speed motors for use in utility vehicles. The right angle drives (gear reducers) are used in, for example, drive systems for utility vehicles but may be used in other applications.
- Traditionally, Skid-Steer® Loader Machines as made famous by manufacturers such as Bobcat® and the like have been powered almost exclusively by hydraulics. Skid-Steer® is a registered trademark of Arts-way Manufacturing Co., Inc., a Delaware Corporation. Bobcat® is a registered trademark of Clark Equipment Company of New Jersey.
- These machines traditionally have gasoline or diesel internal combustion engines that drive a hydraulic pump. The pump usually provides power to two independently controlled hydraulic motors one for each side of the machine. The output of each motor drives a drive sprocket with two sets of sprocket teeth. One set of sprocket teeth drives a chain that goes to a front wheel sprocket and the other set of sprocket teeth drives a chain that goes to the rear wheel sprocket. The hydraulic pump also provides power for lifting functions and power takeoffs for implements that can be connected to the machine.
- U.S. Pat. No. 4,705,449 to Christianson et al. discloses the use of two electric traction motors.
FIG. 1 is a plan view of an electric drive system of U.S. Pat. No. 4,705,449 to Christianson et al. whereinbattery 28 supplies electric power to twotraction motors gear reducer 82. Specifically, the '449 patent states at col. 4line 10 et seq.: “afirst traction motor 60 provides the motive force for the left-hand side of the vehicle and asecond traction motor 64 provides the motive force for a right-hand side of thevehicle 66. Both thefirst traction motor 60 and thesecond traction motor 64 are powered by abattery pack 28. Similarly, thetraction motor 64 is connected to a spurgear reduction assembly 82 through acoupling 84. The spur gear reduction assembly engages achain 86 which in turn engages a rightrearward gear 74 and left forward gear 90, which are respectively connected to wheels 14 a and 14 b through axles 92 and 94. As will be appreciated, thetraction motor 60 is operated independently of thetraction motor 64 thereby permitting the wheels 14 c, 14 d to operate at different speed than wheels 14 a and 14 b to create skid steering.”. - U.S. Pat. No. 4,705,449 to Christianson et al. discloses the use of two electric traction motors. The motors are not identified by type in Christianson et al as either DC or AC. However, the motors are DC electric motors as they are controlled by a device identified in the '449 patent to Christianson, namely, a General Electric EV 1 SCR Controller, which is designed to control DC motors. The General Electric EV 1 SCR Controller describes the use of rectifiers to pulse power to DC motors and has no provision for the control of AC motors.
- A copy of the EV 1 SCR Controller technical literature is submitted herewith in an Information Disclosure Statement and describes the use of the controller as being for the control of DC motors. Additionally, the EV 1 SCR Controller is identified in U.S. Pat. No. 4,265,337 to Dammeyer entitled Fork Lift Truck Speed Control Upon Fork Elevation and is used to control a DC motor 92.
- Additionally, the EV 1 SCR Controller has been used in numerous automobiles (electric vehicles) in conjunction with DC series wound motors which provide high current and high torque at low rpm.
- DC traction motors have been used in applications involving forklifts and similar vehicles in the past. Internal combustion engines are not favored in such applications because an internal combustion engine produces zero torque at zero engine speed (RPM) and reaches its torque peak later in its operating range. Internal combustion engines generally require a variable-ratio transmission between the engine and the wheels to match engine speed to the road speeds and loads encountered. A clutch must be provided so that the engine can be mechanically decoupled from the wheels when the vehicle stops. Additionally, some slippage of the engine with respect to the drive train occurs while starting from a stop. Direct current electric traction motors produce considerable torque at zero RPM and thus may be connected directly to the wheels. Alternating current motors, hydraulic motors and pneumatic motors also produce torque at zero RPM.
- Although the term traction motor is usually referred to in the context of a direct current motor, the term is also applicable to alternating current motor applications as well. Additionally, the term traction motor is used to describe any motor of whatever type used to supply torque and power to a vehicle's wheel, tracks, etc.
- In small utility vehicles and the like, space is an important consideration in the design of the vehicle. It is therefore desirable to use a small motor, electric, hydraulic, or pneumatic which is capable of supplying required torque and horsepower under all operating conditions. If an electric motor is used it may be an alternating current motor or it may be a direct current motor.
- Generally, for a given power, high speed electric motors are smaller in size, lighter in weight, and less expensive than low speed motors. Generally, for a given power, alternating current motors are smaller than direct current motors.
- It is highly desirable to save space, weight and cost in the powertrain of a utility vehicle through the use of a high speed motor so that the space may be used for batteries, controls or other components. It is further highly desirable to save space, weight and cost in the powertrain of a utility vehicle or similar vehicle through the use of a high speed motor. Space may be conserved for other components of the vehicle and, in doing so, it is necessary to dissipate large amounts of heat from pinion shaft support bearings. The pinion shaft may rotate at 6000-7000 rpm or higher depending upon the application. At these rotational speeds considerable heat is generated in the bearings. A high speed input from a small electric motor in combination with a right-angle gear reducer saves space while maintaining performance torque and horsepower requirements.
- Previously, external or internal oil pumps have been used in gear reducers to lubricate bearings which support high rotational speed shafts and gears. These devices are powered by one of the shafts within the gear housing or casing. While satisfactory performance has been achieved with the shaft-driven oil pumps, more parts are necessary to accomplish lubrication of the bearings of the high speed shaft. Higher speed shafts generate more heat which must be dissipated. External pumps necessitate passageways through the pump casing to bring oil to bearings and gears.
- U.S. patent application Ser. No. 11/399,123 filed Apr. 6, 2006 entitled Cascading Oil flow Bearing Lubrication system employs an oil slinger and is commonly owned with the instant patent application. A bearing lubrication device which includes an output shaft carrier housed within a gear housing is disclosed and claimed. The output shaft resides partially within the output shaft carrier and upper and lower bearings support the output shaft. The output shaft carrier includes a first trough for catching lubricating fluid which is slung by an oil slinger. The first trough is in lubricating fluid communication with the upper bearing which pumps the lubricating fluid through the bearing and into an upper passageway which terminates in an opening from which the lubricating fluid emanates.
- U.S. Pat. No. 5,887,678 to Lavender discloses a lubrication apparatus for shaft bearings which includes a trough extending radially outwardly and inclined downwardly in a direction toward the shaft bearing. U.S. Pat. No. 6,439,208 to Jones discloses a centrifugal supercharger having a lubricating slinger. U.S. Pat. No. 6,698,762 to Newberg et al. discloses a rotary device shaft with oil slinger groove. United States Patent Application Publication No. US 2003/0159888 A1 to Burkholder discloses a disk oil slinger assembly. United States Patent Application Publication No. US 2006/0104838 A1 to Wood discloses an integrated eccentric flywheel slinger.
- None of the foregoing references provide pinion shaft bearing lubrication in a right angle gear reducer using an oil slinger, pinion shaft and pinion housing configured for use in a utility vehicle.
- None of the foregoing references disclose a right angle gear reducer which includes the an oil slinger lubrication system in conjunction with a utility vehicle.
- A bearing lubrication device in a right angle gear reducer includes a gear housing having an interior portion and a lubricating fluid reservoir therein. The principles and structure disclosed herein may be used in a gear reducer whether or not it is denoted as a right-angle gear reducer. An oil slinger, rotating pinion shaft, pinion shaft housing, and bearings for supporting the pinion shaft within the pinion shaft housing work together to provide a continuous supply of oil to the bearings. The pinion shaft includes first and second radially and longitudinally extending passageways therethrough which supply oil from a recess in the nose end of the pinion shaft to the bearings. Oil is slung from the reservoir into the recess of the rotating pinion shaft where it is forced centrifugally outwardly in the cylindrical recess and forced centrifugally through the radially and longitudinally extending passageways to an oil supply chamber formed by the rotating pinion shaft, shaft housing and bearings. Tapered roller bearings pump the oil from the oil supply chamber back to the oil reservoir. Oil passageways in the shaft housing enable the return of oil from the first bearing set while the other bearing set returns the oil directly to the reservoir. In this way a very compact and efficient gear reducer is produced having a shaft driven oil slinger which is compact and minimizes the number of parts necessary.
- A method for lubricating bearings supporting a shaft in a gear box is disclosed and comprises the steps of: slinging oil from a lubricating oil reservoir using an oil slinger toward a first end of a pinion shaft; collecting oil in a cylindrical recess in the first end of the pinion shaft; rotating the shaft and forcing the collected oil radially outwardly in the cylindrical recess and into a passageway communicating with the recess and extending longitudinally and radially from the recess to the oil supply chamber formed by the shaft, the bearings and the shaft housing; pumping oil from the chamber through the bearings; and, returning the oil to the lubricating oil reservoir. Additionally, the step of returning the oil pumped from the oil return chamber to the lubricating oil reservoir is performed using a return passageway through the shaft housing.
- The right-angle drive described herein is particularly useful in a utility vehicle. The vehicle includes: a frame; a high speed motor having an output shaft; a right-angle gear reducer driven by the output shaft of the high speed motor; the right-angle gear reducer includes a bearing lubrication device comprising: a gear housing having an interior portion and a lubricating fluid reservoir therein; an oil slinger; a pinion shaft; a pinion shaft housing; a bearing for supporting the pinion shaft within the pinion shaft housing; the pinion shaft includes a passageway therethrough; and, the oil slinger supplies oil to the passageway communicating the oil to the bearing by way of an oil supply chamber; the right-angle gear reducer includes an output carrier interconnected with an output shaft; the output shaft includes first and second chain drive sprockets; the forward and rearward wheel shafts each have a wheel sprocket; a first and second chain; the first chain interengaging the first chain drive sprocket and the forward wheel sprocket driving the forward wheel shaft; and, the second chain interengaging the second chain drive sprocket and the rearward wheel sprocket driving the rearward wheel shaft.
- Another method for using a high-speed motor in a utility vehicle is disclosed. The method includes the steps of: orienting two high speed motors having shaft driven pinion gears parallel to the rails of the vehicle; mounting right angle planetary gear reducers in engagement with said shaft driven pinion gears, each of the planetary gear reducers include a gear driven by said shaft driven pinion gears, the gear driven by said shaft driven pinion gear drives a shaft which includes a second pinion gear which drives a planetary gear set and carrier reacting against a ring gear in the casing of the planetary gear reducer, the carrier of the planetary gear reducer includes a splined output, and each of the splined outputs being on the same axis; lubricating bearings supporting the pinion gear shafts with an oil slinger, the pinion gear shafts include a nose portion having a recess, at least one port, and at least one radially and longitudinally extending passageway communicating lubricating oil to a supply chamber feeding the lubricating bearings; pumping oil through the lubricating bearings and into a passageway for return to the right angle gear reducer; coupling an output shaft to the splined output of the planetary gear reducer and driving the output shaft at a desired rate; and, driving, with chains, the wheel shafts of the vehicle.
- As electric motor technology has advanced to provide more performance for less cost it makes sense to replace hydraulic systems with electric systems. Electric motors typically rotate at much higher RPM than hydraulic motors, particularly those suitable for skid-steer loaders. It is desirable to minimize the size of the drive train components so as to maximize the space available for batteries and controls. The vehicle described herein may employ Nickel Metal Hydride, Lithium Ion, Lithium Ion polymer, lead acid batteries or other battery technology.
- Although one example of the invention as described herein uses high speed alternating current electric motors it is specifically contemplated that the invention may be used with high speed direct current electric motors, high speed hydraulic motors and high speed pneumatic motors.
- In one example, the input to the gear box is an offset helical gear driven by a pinion. A planetary sun pinion inputs to the planetary stage. Planetary gear sets provide torque multiplication in compact packages. The output of the gear box is a carrier with a planetary gear-set reduction including a stationary ring gear. The gear box casing includes a ring gear which is a reaction gear and intermeshes with a three-gear planetary set. The carrier of the planetary gear set includes a spline which intermeshes with a splined output shaft.
- The offset reduction in the gearbox is an important aspect of the invention as it enables the electric motors to be placed side to side. Use of electric motors is enabled in this application by offsetting the gear box. In this way the left and right side motors can be mounted side-by-side without interference while still maximizing available space for other components such as batteries and controls.
- In another example, the offset gear box may be oriented differently (i.e., rotated 180 degrees) with the motors side by side. Although this example may result in reducing the width of the vehicle it may also result in increasing the length of the vehicle. Still alternatively, this example may be used to drive one of the wheel shafts directly.
- A wheel driven utility vehicle includes a frame and two high speed alternating current electric motors arranged side by side for driving the vehicle. A variable frequency alternating current drive is utilized to control the speed of the motors and hence to control the direction and turning of the utility vehicle. Instead of high speed alternating current motors, high speed direct current motors, high speed hydraulic motors and/or high speed pneumatic motors may be used.
- Each alternating current motor has an output which drives an offset planetary gear reducer. Each offset planetary gear reducer is affixed to the electric motor (or other motor type) and includes an output carrier interconnected with an output shaft. Each output shaft includes first and second chain drive sprockets which drive chains interconnected with shafts driving the front and rear wheels respectively. Each offset planetary gear reducer enables use of space saving high speed relatively low-torque alternating current electric motors (or other motors with similar performance characteristics) with attendant large speed reductions. Gear reduction enables the production of sufficient torque at the wheels of the vehicle. Applications in addition to utility vehicles are also specifically contemplated.
- In an example of the invention, a utility vehicle drive system comprises two alternating current electric motors (or other high speed motors with similar performance characteristics) each having a shaft driven pinion gear. Intermediate gears engage shaft driven pinion gears which in turn drive planetary gears. Each of the planetary gear reducers include an output spline and each of the output splines are axially aligned with each other.
- In an example of the invention, a method for using a high-speed electric motor (or high-speed hydraulic, pneumatic or direct current motors) in a utility vehicle includes the step of orienting the motors having shaft driven pinion gears side by side such that their shaft driven pinion gears are arranged on opposite sides of the vehicle. Next, the offset planetary gear reducers are mounted in engagement with the shaft driven pinion gears. Each of the planetary gear reducers include a gear driven by the shaft driven pinion gear. The gear driven by the shaft driven pinion gears includes a shaft portion formed as a second pinion sun gear which drives a planetary gear set and carrier. The planetary gear set reacts against a ring gear in the casing of the planetary gear reducer. The carrier of the planetary gear reducer includes a splined output. Each of the splined outputs are on the same axis of the other splined output located on the other side of the vehicle. Additionally, the method includes driving an output shaft coupled to the splined output of the carrier of the planetary gear reducer. And, finally, the method includes driving, with chains, the wheel shafts of the vehicle.
- It is an object of the present invention to save motor space in a utility vehicle, recreational vehicle, and the like while providing for high torque at the vehicle wheel and tire.
- It is an object of the present invention to provide a planetary gear reducer in a utility vehicle, recreational vehicle and the like which enables use of a smaller, lighter, high speed motor while providing for high torque at the vehicle wheel and tire.
- It is an object of the present invention to provide a planetary gear reducer in a utility vehicle, recreational vehicle and the like which enables use of a smaller, lighter high speed motor selected from the group of alternating current motors, direct current motors, hydraulic motors, and pneumatic motors.
- It is an object of the present invention to provide a planetary gear reducer in a utility vehicle, recreational vehicle and the like which enables use of a smaller, lighter, high speed alternating current electric motor while providing for high torque at the vehicle wheel and tire.
- It is an object of the present invention to provide for an efficient planetary gear reducer for use in a utility vehicle, recreational vehicle and the like.
- It is an object of the present invention to provide for two offset electric motors in a utility vehicle, recreational vehicle, and the like by utilizing two offset planetary gear reducers.
- It is an object of the present invention to utilize high speed alternating current motors in a utility vehicle, recreational vehicle or the like.
- It is an object of the present invention to provide a method of using two high speed electric motors.
- It is an object of the present invention to provide offset planetary gear reducers for use in combination with high speed motors for efficient use of space in a utility vehicle.
- It is an object of the present invention to provide offset planetary gear reducers for use in combination with alternating current electric motors for efficient production of torque at the wheels of a utility vehicle.
- It is an object of the present invention to provide right-angle planetary gear reducers in combination with high speed motors for efficient use of space in a utility vehicle.
- It is an object of the present invention to provide right-angle planetary gear reducers for use in combination with alternating current electric motors for efficient production of torque at the wheels of a utility vehicle.
- It is an object of the present invention to provide right-angle planetary gear reducers which employ an oil slinger for lubricating bearings which support a pinion gear shaft. The pinion gear shaft includes a recess and passageways therethrough communicating with a first chamber for supply of oil to the bearings. A second chamber returns oil through the pinion housing adapted for return of oil to the reservoir within the main housing.
- It is an object of the present invention to provide a right angle gear reducer having first and second chambers for the lubrication of the pinion shaft bearings.
- It is an object of the present invention to provide a utility vehicle with compact right angle gear reducers with motors oriented lengthwise enabling close spacing of vehicle side rails.
- These and other objects of the invention will best be understood when reference is made to the Brief Description of the Drawings, Description of the Invention and Claims which follow hereinbelow.
-
FIG. 1 is a plan view of a prior art Skid-Steer vehicle powered by two DC traction motors. -
FIG. 2 is a top plan view of the utility vehicle illustrating two alternating current motors oriented side by side with each having an offset planetary gear reducer driving a respective output shaft. -
FIG. 2A is an enlarged portion ofFIG. 2 illustrating a portion of the left side of the vehicle. -
FIG. 2B is an enlarged portion ofFIG. 2A illustrating the gear reducer and output shaft. -
FIG. 2C is an exploded view of the input to the gear reducer, the gear reducer, and the output shaft. -
FIG. 2D is a perspective view of the carrier and the output shaft. -
FIG. 2E is a perspective view of the offset planetary gear speed reducer. -
FIG. 3 is a block diagram of the method for using high speed alternating current electric motors with offset planetary gear reducers. -
FIG. 4 is a top plan view of the utility vehicle illustrating two alternating current motors in conjunction with two right-angle drives. -
FIG. 4A is a cross-sectional view of one of the right-angle drives and motor. -
FIG. 4B is a perspective view of one of the right-angle drives. -
FIG. 4C is a perspective view of the pinion shaft housing. -
FIG. 4D is an end view of the pinion shaft housing. -
FIG. 4E is a cross-sectional view of the pinion shaft housing taken along thelines 4E-4E ofFIG. 4D . -
FIG. 4F is a cross-sectional view of the pinion shaft housing taken along thelines 4F-4F ofFIG. 4D . -
FIG. 4G is an enlargement of a portion ofFIG. 4A . -
FIG. 4H is an enlarged view similar toFIG. 4F with the pinion shaft and bearings inserted therein. -
FIG. 4I is a perspective view of the pinion shaft and spiral bevel pinion. -
FIG. 4J is a top view of the pinion shaft and spiral bevel pinion.FIG. 4K is a view of the nose end of the pinion shaft and spiral bevel pinion. -
FIG. 4L is a cross-sectional view of the gear casing illustrating the spiral bevel pinion and the spinal bevel gear. -
FIG. 5 is a process flow chart for lubricating bearings supporting a pinion shaft in a pinion shaft housing. -
FIG. 6 is a process flow chart for using high speed motors in a utility vehicle with right angle planetary gear reducers. - The drawings will be best understood when reference is made to the Description of the Invention and Claims below.
-
FIG. 2 is atop plan view 200 of the utility vehicle illustrating two alternating currentelectric motors planetary gear reducer respective output shaft reference numerals - The utility vehicle includes a
frame FIG. 2 ,side frame member 205 is on the left hand side of the vehicle andside frame member 206 is on the right hand side of the utility vehicle. The twoside frame members FIG. 2 ,FIG. 2A , andFIG. 2B . -
Frame side member 205 supports first chain drivenwheel shaft 210.Sprocket 210S is formed as part of thewheel shaft 210 or alternatively is a separate sprocket affixed or attached to thewheel shaft 210.Frame side member 205 also supports theoutput shaft 208 of theplanetary gear reducer 203. -
Output shaft 208 includes twosprockets 208S which are identical. Thesprockets 208S may be an integral part ofshaft 208 or they may be separately attached to the shaft. Ametal chain 210interengages sprockets shaft driving sprocket 208S to drivensprocket 210S is approximately 2.5-5:1 such that for every rotation of theoutput shaft 208 theforward sprocket 210S andwheel shaft 210 turns 0.4 to 0.2 of a turn or revolution. Reduction in speed of the drivensprocket 210S results in a corresponding increase in torque for a given applied power. - Referring to
FIGS. 2 and 2B ,output shaft 208 is splined and is coupled to thesplined output 230T of thecarrier 230 of theplanetary gear reducer 203.Frame side member 205 also supports the second chain drivenwheel shaft 212.Sprocket 212S is formed as part of thewheel shaft 212 or alternatively is a separate sprocket affixed or attached to thewheel shaft 212 for driving arearward wheel 212A. -
Metal chain 211interengages sprockets shaft driving sprocket 208S to drivensprocket 212S is approximately 2.5-5:1 such that for every rotation of theoutput shaft 208 therearward sprocket 212S andwheel shaft 212 rotates just 0.4 to 0.2 of a turn or revolution. The reduction in speed of the drivensprocket 212S results in a corresponding increase in torque for a given applied power. - Similarly, the structure and operation of driven sprockets 216S, 217S,
shafts rearward wheels shaft 214 andchains right frame 206 are identical to the leftframe side member 205 andframe 205. The reduction ratio of the outputshaft driving sprocket 214S to drivensprockets - Speed reduction of approximately 2.5-5:1 just described are in addition to the speed reduction of the
planetary gear reducers current motors output shafts planetary gear reducers helical pinion gear 221H and a helical drivengear 223H. - Full load electric motor torque is generally defined as follows:
-
Torque(ft-lbs)=5250×horsepower/RPM - Generally, for a given power, high speed electric motors are smaller in size, lighter in weight, and less expensive than low speed motors. Generally, for a given power, alternating current motors are smaller than direct current motors. Additionally, for a given power, alternating current motors are smaller than direct current motors.
- Use of
planetary gear reducers current motors Reducers -
FIG. 2A is anenlarged portion 200A ofFIG. 2 illustrating a portion of the left side of the vehicle andFIG. 2B is a further enlargement of aportion 200B ofFIG. 2A illustrating thegear reducer 203 andpinion 221 onoutput shaft 221 S in more detail. - Referring to
FIGS. 2A and 2B , the alternatingcurrent motors planetary gear reducers ring gear 224 affixed thereto.Ring gear 224 is trapped betweenhousing portions Seals 224S prevent leakage of lubricant from within the gear casing. - Each of the
planetary gear reducers carrier 230 havingplanetary gears ring gear 224 and anoutput spline 230T. Although the planetary gear reducer illustrated has three planetary gears, any reasonable number of planetary gears may be used. Each of the planetary gear reducers includes agear 223 havingteeth 223T driven by thepinion gear 221 of theoutput shaft 221 of the alternatingcurrent motor 201. Thegear 223 driven by thepinion gear 221 of theoutput shaft 221S of the alternatingcurrent motor 201 includes a shaft portion forming asun pinion 227 withgear teeth 227T. - Sun pinion or
gear 227 intermeshes with threeplanet gears teeth ring gear 224.Ring gear 224 extends around the inner circumference of the gearbox. Each of thechain drive shafts spline 208T thereon which intermeshes withoutput spline 230T of thecarrier 230 as best viewed inFIG. 2B .Planetary gear reducers carrier 230 will rotate 1/20 to 1/30 of a revolution. Other speed reductions are specifically contemplated.Chain drive sprockets wheel shaft sprockets chain drive sprocket 208S, thewheel sprockets - Other speed reductions are specifically contemplated depending on the desired torque at the wheels and traveling speed of the machine taking loads, inclines and other variables into consideration. Use of the offset speed reducer as disclosed herein enables the efficient use of space and provides the same torque to the wheel with less input torque supplied by the high speed electric motor. The efficiency of the offset speed reducer is approximately 95% at rated load.
- Use of the offset speed reducer and electric motors enables use of high speed, light weight electric motors which are smaller in diameter and output less torque than slower, heavier larger motors whether they are alternating current motors or direct current motors. The savings in space, weight and money attained by use of the offset planetary gear reducers with high speed motors is considerable. Use of planetary gear reducers provides a stable transmission of power with torque amplification inversely proportional to the speed reduction. The planetary gear reducers of the instant invention weigh approximately 100 pounds but can vary in weight depending on the materials used such as steel, stainless steel or aluminum. The
gears carrier 230 are made of steel or stainless steel. Aluminum may be used for thegearbox casing FIG. 2 . - Alternating current
electric motors -
FIG. 2C is an explodedview 200C of the input to thegear reducer 221T, thegear reducer 203, and theoutput shaft 208. Referring toFIGS. 2B and 2C ,sun pinion 227 is supported by bearing 223B and 227B. Use ofgear 223 enables the planetary gear reducer to be offset as it is driven bypinion 221 which is on theshaft 221 S of the electric motor. Three planet gears 225, 226 and 229 and, more specifically, theirteeth sun pinion teeth 227T and ring gear 234 and its teeth 234T. - Planet gears 225, 226 and 229 are supported by bearings (i.e., 235B) and are pinned to the carrier by pins. See, for example,
pin 235 inFIGS. 2A and 2B .Pin 225 P restrainspin 235 from movement within thecarrier 230 and thus securesgear 225 in place.Gear 225 and the other planet gears are, of course, free to rotate but they are securely fastened to the carrier and impart rotational motion to thecarrier 230.Reference numeral 225A indicates intermeshing between planet gear teeth 225T andring gear teeth 224T. Referring toFIG. 2A ,output shaft 208 is supported bybearings spline 208T withspline 230T of the carrier. -
Planetary gear reducer 203 distributes the load evenly to three planets, 225, 226 and 229. As previously indicated any reasonable number of planet gears from 1 to “n” may be used. Reciting the operation of the gear reducer, torque is applied byshaft 221S throughteeth 221T ofpinion 221 which imparts rotational movement and torque to gear 223.Gear 223 includessun pinion 227 which by and through itsteeth 227T imparts rotational movement and torque togears teeth carrier 230 effecting a speed reduction which is transmitted tooutput shaft 208 which is interconnected with thecarrier spline 230T. Thegearbox portions ring gear 224 when the gearbox is secured byfastener 240A to theelectric motor 201 and when theportions fastener 240. -
FIG. 2D is aperspective view 200D of thecarrier output shaft 208 with acorresponding spline 208T.FIG. 2E is aperspective view 200E of the offset planetary gear reducer without bearing 208B illustrated therein. The principal dimensions of the offset planetary gear reducer are approximately 8 inches in diameter and 5.5 inches deep neglecting theinput housing 241 which housespinion 221. - The offset planetary gear reducer is generally cylindrically shaped and includes a
housing 241 for the shaft drivenpinion gear 221. A flange (unnumbered) is fastened to themotor 201. -
FIG. 3 is a block diagram 300 illustrating a method for using high-speed electric motors in combination with offset planetary gear reducers in a utility vehicle. The first step includes orienting two high speed electric motors having shaft driven pinion gears side byside 301 such that their shaft driven pinion gears are arranged on opposite sides of the vehicle. Next, the method includes mounting offset planetary gear reducers in engagement with the shaft driven pinion gears 302. Each of theplanetary gear reducers sun pinion gear 227 which drives a planetary gear set andcarrier 230 reacting against aring gear 224 in the casing of theplanetary gear reducer carrier 230 of the planetary gear reducer includes asplined output 230T and each of thesplined outputs 230T are on the same axis. The method further includes driving anoutput shaft splined output 230T of the planetary gear reducer. Finally, the method includes driving, with chains (209, 211, 213, 215), the wheel shafts (210, 212, 216, 217) of the vehicle. -
FIG. 4 is atop plan view 400 of the utility vehicle illustrating two alternatingcurrent motors main housing 401 and apinion housing 402. Frame supports 250, 251support motors Main housing 401 andgear housing 403 are preferably made of 8620H annealed steel. SeeFIG. 4A .Main housing 401 is approximately 10″ in diameter and 8″ long.Pinion housing 402 is approximately 3″ long and 4″ in diameter.Motors -
FIG. 4A is across-sectional view 400A of one of the right-angle drives 495 andmotor 495A taken along thelines 4A-4A ofFIG. 4B . A portion of the main housing defines a fluid reservoir which holdsoil 498 at a level as indicated byreference numeral 499. SeeFIG. 4L .Oil 498 is illustrated in the reservoir formed by themain housing 401 and the spacer 401A and it is used to lubricate the intermeshing spiral bevel pinion gear and the spiral bevel gear as well as the planetary output gear set. Additionally,oil 498 is used to lubricate all bearings in the pinion housing and the main housing.Pinion housing 402 includes aflange 402A for connection to themotor 495A.Pinion housing 402 further includes aflange 402B for connection withgear box 401. Spacer 401A is used to interconnect themain housing 401 of the right angle drive 495 to thevehicle sidewall 205. -
FIG. 4B is aperspective view 400B of one of the right-angle drives 495 andmotor 495A. Referring toFIGS. 4A and 4B ,flange 402A secures the pinion housing to themotor 495A.Gear housing 403 is secured tomain housing 401 with threadedbolts 435.Gear housing 403 includes apolycarbonate cap 404 secured therein by asnap ring 431 and sealed with an O-ring 428. The main housing is attached to the spacer 401A and thesupport 205 using bolts not shown. - Spiral bevel pinion, sometimes referred to herein as the spiral bevel pinion,
gear 405 andspiral bevel gear 406 are preferably made of 8620H annealed steel. - Still referring to
FIG. 4B ,motor mounting bolts 434 secure themotor 495A to theflange 402A of the pinion housing. Inspection plugs 438, 439 and 439 are illustrated inFIG. 2B and enable quick and easy inspection of the main housing and/or enable the addition of oil. - Referring to
FIG. 4A ,bearings spiral bevel gear 406 which is driven by thespiral pinion gear 405.Bearings cones retention plate 412 traps and secures bearing 419A againststop 479. Preferably the retention plate is made of mild steel.Retention bolt 435 secures spiral gear bearingretention plate 412 to thespiral bevel gear 406. Ashim 419 is used between the bearingretention plate 412 and thegear body 406.Spiral gear housing 403 is sealed with respect tomain housing 401 with O-ring seals 427.Pinion housing 402 is preferably made of mild steel as isgear housing 403.Gear housing 403 is secured to thepinion housing 402 using a pinionhousing shim pack 418 and a gearhousing shim pack 417.Pinion housing seal 426 seals thegear housing 403 and themain housing 401 to thepinion housing 402. - Still referring to
FIG. 4A , spiralpinion gear teeth 405 intermesh with spiralbevel gear teeth 406A of thespiral gear 406.Spiral bevel gear 406 includes aspline 476 which intermeshes with areciprocal spline 445 in thesun gear shaft 407 to drive theoil slinger 413 and thesun gear 445A. Sun gearshaft retaining ring 432 positionssun gear shaft 407 and prevents rightward travel of theshaft 407 when viewingFIG. 4A .Thrust plate 414 preventsshaft 407 from travel in the leftward direction when viewingFIG. 4A . - Still referring to
FIG. 4A , the input to the gear box is thepinion shaft 405 andspiral bevel gear 405.Pinion shaft 405A drivesgear 406 which in turn drivessun gear shaft 407 andsun gear 445A. The planetary sun gear inputs to the planetary stage. Planetary gear sets provide torque multiplication in compact packages. The output of thegear box 495 is acarrier 410 with a planetary gear-set reduction including astationary ring gear 409.Carrier 410 is preferably made of D7003 grade steel. The main housing orcasing 401 includesring gear 409 which is a reaction gear and intermeshes with a three-gear planetary set comprising planet gears 408.Ring gear 409 is secured to themain housing 401 though bolts not viewed inFIG. 4A . Thecarrier 410 of the planetary gear set includes aninternal spline 481 which intermeshes with asplined output shaft 208A which is the output to drive the vehicle. The right angleplanetary gear reducers input pinion gear 405, thecarrier 410 will rotate 1/20 to 1/30 of a revolution. Other speed reductions are specifically contemplated As discussed above in regard toFIGS. 2-2E , use of electric motors, hydraulic motors and/or pneumatic motors is specifically contemplated. The right angle planetary gear drive with the above stated speed reduction enables use of a utility vehicle having a relatively narrow width between side rails. - Still referring to
FIG. 4A , planet gears 408 includegear teeth 408T driven bysun gear teeth 445A. Planet gears 408 are pinned to thecarrier 410 using roll pins 433 mounted to planet pins 411 which provide support for the gears.Needle roller bearings 424,spacers 416 and thrustbearings 415 position and support the planet gears 408 for rotation about the planet pins 411. -
FIG. 4G is anenlargement 400G of a portion ofFIG. 4A .Pinion housing 402 is generally cylindrically shaped and carriespinion shaft 405A supported byroller bearings Roller bearings 451 are supported bycup 421 andcone 420 and theroller bearings 452 are supported bycup 421A andcone 420A. Innercircumferential stop 456 in conjunction withlocknut 429 and piniontanged lockwasher 430 support andsecure bearings lockwasher 430interengages slot 459 inpinion shaft 405A and is compressed bylocknut 429 threadinglyinterengaging 429A shaft 405A. - Still referring to
FIGS. 4A and 4G ,pinion shaft 405A includesgrooves 455 whichinterengage motor coupling 455A for driving the pinion shaft. Pinion shaft rotates at approximately 6-7000 rpm. Heat dissipation from the bearings is addressed by supplying oil tochamber 453 formed betweenroller bearings pinion shaft 405A and the interior of thepinion housing 402.Chamber 453 is fed byports pinion shaft 405A.Ports passageways Passageways ports cylindrical recess 405D.Ports cylindrical recess 405D. See,FIG. 4L , across-sectional view 400L of the gear casing.Cylindrical recess 405D receives oil fromoil slinger 413 as viewed inFIG. 4A aspinion shaft 405A rotates. -
Oil slinger 413 is coupled toshaft 407 by a press fit or threadedinterconnection 407A and rotates therewith.Gear 406 includesspiral bevel teeth 406Ainterengaging teeth 405 ofspiral bevel pinion 405A.Oil slinger 413 is approximately 4.5 inches in diameter.FIG. 4L is across-sectional view 400L of the gearcasing indicating shaft 407 in phantom drivingoil slinger 413 which picks upoil 499 from the reservoir within themain housing 401 and deposits it into therotating recess 405D.FIG. 4A illustrates oil flow as indicated byflow arrow 471 from theoil slinger 413. - Referring to
FIGS. 4A , 4G and 4L, aspinion shaft 405A rotates, oil inrecess 405D is urged radially outwardly under centrifugal force and intoports ports passageways flow arrows Passageways ports chamber 453.Ports groove 466 in the exterior of thepinion shaft 405A and communicate with and supply oil tochamber 453. SeeFIGS. 4G , 4I and 4J. - Still referring to
FIGS. 4A and 4G ,chamber 453 fills with oil aftershaft 405A makes a sufficient number of revolutions (following startup) and supplies oil to taperedroller bearings Tapered roller bearings 452 pump oil toreservoir 499 and taperedroller bearings 451 pump oil tooil return chamber 454.Chamber 454 is bounded bypinion housing 402,lock washer 429,lock nut 429,pinion shaft 405A,motor coupling 455A andmotor input seal 425. Preferably seal 425 is a Viton seal.Wave spring 442 resides between the motor and themotor input seal 425. -
Chamber 454 communicates withports circumferential groove 448 which in turn communicate withpassageways FIG. 4H .Ports circumferential groove 448 in the interior of thepinion housing 402.Pinion housing 402 is generally cylindrically shaped withflanges main housing 401 of the gear box and themotor 495A.Passageways ports main housing 401 which serves and forms the oil reservoir.Ports port 446 is submerged below theoil level 499. -
FIG. 4C is aperspective view 400C of thepinion shaft housing 402 illustratingmotor flange 402A andmain housing flange 402B.Ports ports Access ports 440A are illustrated inFIG. 4C as are flange bolt holes 449, 450. Referring toFIGS. 4A and 4H ,access ports 440A are illustrated withplugs 440 threaded therein.FIG. 4D is anend view 400D of the pinion shaft housing illustrating the vertical orientation ofports -
FIG. 4H is anenlarged view 400H similar toFIG. 4F with thepinion shaft 405A andbearings Groove 466 is an outer circumferential groove in thepinion shaft 405A viewed inFIG. 4H and 4I .Ports circumferential groove 466 as viewed inFIGS. 4G and 4H .Ports FIG. 4H in communication withoil return chamber 454. Oil is pumped by taperedroller bearings 451 intooil return chamber 454 and groove 448 in the pinion shaft housing where it flows intopassageways ports Port 446 is actually submersed below theoil line 499 as illustrated inFIG. 4L .Bearings motor 495A is started andpinion shaft 405A begins to rotate. The bearings are lubricated adequately by submersion in the oil because the pinion shaft (although rotating at approximately 6000 to 7000 rpm) has not yet generated too much heat for the bearings to withstand since they are already lubricated due to their partial submersion in the oil. Full lubrication occurs very quickly as theoil slinger 413 gathers oil from the reservoir and slings or throws it intorecess 405D and thereafter through thepinion shaft 405A. - Similarly,
bearings sun gear shaft 407 and are adequately lubricated by oil in the reservoir.Sun gear shaft 407 rotates considerably slower than theinput pinion shaft 405A thus generating less heat.Bearings shaft 407 is not rotating. - Oil is slung from the
outer circumference 413A of theoil slinger 413 as illustrated byflow arrow 471 inFIG. 4A . Some oil may be picked up from the sides of the oil slinger but the majority ofoil 498 is picked up and slung from theouter circumference 413A of the oil slinger. Theoil slinger 413 is disc shaped and the outer circumference is not contoured and roughened. However, it is specifically contemplated that various shapes and configurations of oil slingers may be used such that the surfaces of the oil slinger are contoured or roughened. Theoil slinger disc 413 is preferably made of mild steel. -
FIG. 4E is across-sectional view 400E of thepinion shaft housing 402 taken along thelines 4E-4E ofFIG. 4D . Innercircumferential groove 448 is illustrated inFIG. 4E along with bearingstop 456.Bearing stop 456 andpinion shaft 405A secure taperedroller bearings 452 in place. Locknut 429 used withlockwasher 429A secures bearing 451 against bearingstop 456. SeeFIGS. 4G and 4H . -
FIG. 4F is across-sectional view 400F of the pinion shaft housing taken along thelines 4F-4F ofFIG. 4D and illustrates theoil return passageways pinion shaft 405A inserted therein. -
FIG. 4I is aperspective view 4001 of thepinion shaft 405A andgear 405.FIG. 4I provides a view of the outercircumferential groove 466 communicating withport 446B as well asslot 459 used in locking conjunction withtanged lockwasher 430.Recess 405D in the nose of the pinion gear and shaft revealsport 405F therein.Pinion shaft 405A illustratesexterior threads 429A for interconnection with lockingnut 429 as illustrated inFIG. 4A for the purpose of trapping thebearings -
FIG. 4J is atop view 400J of thepinion shaft 405A andgear 405 andFIG. 4K is aview 400K of the nose end of thepinion shaft 405A andgear 405.Recess 405D andports FIG. 4K . -
FIG. 4L is across-sectional view 400L of the gearcasing indicating shaft 407 in phantom drivingoil slinger 413 which picks upoil 499 from the reservoir within themain housing 401 and deposits it into therotating recess 405D of thepinion shaft 405A. Pinion spiralbevel gear teeth 405 intermesh with spiralbevel gear teeth 406A ofgear 406 to effect a speed reduction. Bearingcones shaft 407 as is bearingretention plate 412 andretention bolts 435. -
FIG. 5 is aprocess flow chart 500 for lubricating bearings supporting a pinion shaft in a pinion shaft housing. A method for lubricating bearings supporting a pinion shaft in a pinion shaft housing is disclosed. The method includes the steps of: slinging oil from a lubricating oil reservoir using an oil slinger at a first end of ashaft 501; collecting oil in a cylindrical recess in the first end of theshaft 502; rotating the shaft and forcing the collected oil radially outwardly in the cylindrical recess and into a passageway communicating with the recess and extending longitudinally and radially from the recess to a chamber formed by said shaft, the bearings and ashaft housing 503; pumping oil from the chamber through thebearings 504; and, returning the oil to the lubricatingoil reservoir 505. The step of returning the oil to the lubricating oil reservoir may be performed using a return passageway through the shaft housing. The step of rotating the shaft and forcing the collected oil radially outwardly in the cylindrical recess includes forcing the collected oil into a second passageway communicating with the recess and extending longitudinally and radially from the recess to the chamber formed by the shaft, the bearings and the shaft housing. -
FIG. 6 is aprocess flow chart 600 for using high speed motors in a utility vehicle with right angle planetary gear reducers. A method for using high-speed motors in a utility vehicle is also disclosed and includes the steps of: orienting two high speed motors having shaft driven pinion gears parallel to the rails of thevehicle 601; mounting right angle planetary gear reducers in engagement with the shaft driven pinion gears 602, each of the planetary gear reducers include a gear driven by the shaft driven pinion gears, the gear driven by the shaft driven pinion gear includes a shaft portion formed as a second pinion gear which drives a planetary gear set and carrier reacting against a ring gear in the casing of the planetary gear reducer, the carrier of the planetary gear reducer includes a splined output, and each of the splined outputs being on the same axis; lubricating bearings supporting the pinion gear shafts with anoil slinger 603, the pinion gear shafts include a nose portion having a recess, at least one port, and at least one radially and longitudinally extending passageway communicating lubricating oil to a chamber feeding said lubricating bearings; pumping oil through the lubricating bearings and into a passageway for return to the rightangle gear reducer 604; coupling an output shaft to the splined output of the planetary gear reducer and driving the output shaft at a desiredrate 605; and, driving, with chains, the wheel shafts of thevehicle 606. - A list of reference numerals follows.
- 14 a-d-tires of vehicle
- 28-battery
- 60, 64-motor
- 62, 66-sides of vehicle
- 68, 84-coupling
- 70, 82-spur gear reduction assembly
- 72, 86-chain
- 74, 76, 88, 90-gears
- 78, 80, 92, 94-axles
- 70, 82-spur gear reduction assembly
- 100-prior art utility vehicle
- 200-utility vehicle
- 200A-enlarged portion of utility vehicle
- 200B-further enlargement of planetary gear reducer
- 200C-exploded view of powertrain
- 200D-perspective exploded view of carrier and output shaft
- 200E-perspective view of offset planetary gear reducer
- 201, 202-alternating current motor
- 203, 203A, 204-gearbox
- 205, 206-vehicle side wall
- 208, 214-output shafts
- 208B, 223B, 227B, 235B, 208C-bearing
- 208T-spline on output shaft
- 209, 211, 213, 215-drive chains
- 210, 212, 216, 217-wheel shaft
- 210A, 212A, 216A, 217A-wheel tire
- 221T-pinion teeth
- 221, 222-motor shaft pinion gear
- 221H-helical pinion
- 221S, 222S-motor shaft
- 223-gear
- 223H-helical gear
- 223B-bearing
- 223T-teeth on gear
- 224-stationary ring gear
- 224T-ring gear teeth
- 224S, 259S-seal
- 225, 226, 229 -planet gear
- 225A-mesh between
planet gear teeth 223T andring gear teeth 224T - 225P-pin
- 225T, 226T, 229T-planet gear teeth
- 227-sun pinion
- 227T-sun gear teeth
- 230-carrier
- 230T-spline on carrier
- 235-pin
- 240, 240A-bolt
- 241-pinion housing
- 250, 251-frame member
- 300-block diagram of method of using high speed motor and offset planetary gear reducers
- 301-orienting and mounting high speed motors side by side with pinions oppositely arranged
- 302-mounting offset planetary gear reducer in engagement with the shaft driven pinion gears
- 303-coupling an output shaft to the spined output at a desired rate
- 304-driving the wheel shifts of the vehicle
- 400-schematic of right angle drives used in skid-steer application
- 400A-cross-sectional schematic view of right angle drive
- 400B-perspective schematic view of right angle drive and motor
- 400C-perspective schematic view of pinion housing
- 400D-end schematic view of pinion housing
- 400E-cross-sectional view of pinion housing taken along line 4 e-4 e
- 400E-cross-sectional view of pinion housing taken along line 4 f-4 f
- 400G-cross-sectional view of pinion housing and pinion similar to
FIG. 4 e - 400H-cross-sectional view of pinion housing and pinion similar to
FIG. 4 f - 400I-perspective view of pinion gear and shaft
- 400J-orthogonal view of pinion gear and shaft
- 400K-front view of pinion gear
- 400L-exploded view of pinion housing and pinion gear and shaft
- 401-main housing
- 401A-spacer to interconnect right angle drive to vehicle side wall
- 402-pinion housing
- 402A-flange portion of pinion housing-motor connection
- 402B-flange portion of pinion housing-gear box connection
- 403-gear housing
- 404-gear housing cap
- 405-spiral bevel pinion gear teeth
- 405A-pinion shaft
- 405B-first passageway
- 405C-second passageway
- 405D-recess in pinion shaft
- 405E-port
- 405F-port
- 406-spiral bevel gear
- 406A-spiral bevel gear teeth
- 407-sun gear shaft
- 407A-press fit or threaded interconnection
- 408-planet gear
- 408T-planet gear teeth
- 409-ring gear
- 410-carrier
- 411-planet pin
- 412-spiral gear bearing retention plate
- 413-oil slinger disc
- 413A-outer circumference of oil slinger disc
- 414-sun gear shaft thrust plate
- 415-planet gear thrust washers
- 416-needle roller spacer
- 417-pinion housing shim pack
- 418-gear housing shim pack
- 419-spiral gear bearing shim pack
- 419A-bearing
- 419B-bearing
- 420-spiral pinion tapered bearing cones
- 420A-spiral pinion tapered bearing cones
- 421-spiral pinion tapered bearing cups
- 421A-spiral pinion tapered bearing cups
- 422-spiral gear tapered bearing cones
- 422A-spiral gear tapered bearing cones
- 423-spiral gear tapered bearing cups
- 423A-spiral gear tapered bearing cups
- 424-needle roller bearings
- 425-motor input seal
- 426-pinion housing o-ring
- 427-gear housing o-ring
- 428-gear housing cap o-ring
- 429-spiral pinion locknut
- 429A-threaded interconnection of spiral locknut to pinion shaft
- 430-spiral pinion tanged lockwasher
- 431-gear housing cap retaining ring
- 432-sun gear shaft retaining ring
- 433-roll pin
- 434-motor mounting bolts
- 435-pinion gear housing, bearing retention plate bolts
- 438-drain/fill/inspection plugs
- 439-inspection plugs with pipe threads
- 440-⅛ npt pipe plugs
- 440A-hole
- 441-¼ NPT pipe plugs
- 442-input bearing wave spring
- 445-spline
- 445A-sun gear teeth
- 446-pinion housing port
- 446A-pinion housing oil return passageway
- 446B-port in pinion shaft
- 447-pinion housing port
- 447A-pinion housing oil return passageway
- 447B-port in pinion shaft
- 448-pinion housing inner circumferential groove
- 449-bolt hole
- 450-bolt hole
- 451-tapered roller bearing
- 452-tapered roller bearing
- 453-oil chamber
- 454-oil chamber
- 455-spline on pinion shaft
- 455A-motor coupling
- 456-inner circumferential bearing stop
- 457-arrow indicating oil flow path
- 458-arrow indicating oil flow path
- 459-exterior slot in
pinion shaft 405A - 460-tang on
lockwasher 429 - 466-groove in exterior of pinion shaft
- 471-flow arrow from oil slinger
- 476-spline
- 479-stop
- 481-spline
- 494-port
- 495-right angle drive assembly
- 495A-motor
- 496-right angle drive assembly
- 496A-motor
- 497-port
- 498-oil
- 499-oil level
- 500—process flow chart for lubricating bearings supporting a pinion shaft housing
- 501—slinging oil from a lubricating oil reservoir using an oil slinger at a first end of a shaft
- 502—collecting oil in a cylindrical recess in the first end of the shaft
- 503—rotating the shaft and forcing the collected oil radially outwardly in the cylindrical recess and into a passageway communicating with the recess and extending longitudinally and radially from the recess to a chamber
- 504—pumping oil from the chamber through the bearings
- 505—returning the oil to the lubricating oil reservoir
- 600—process flow chart for using high speed motor in a utility vehicle with right angle planetary gear reducers
- 601—orienting two high speed motors having shaft driven pinion gears parallel to the rails of the
vehicle 601 - 602—mounting right angle planetary gear reducers in engagement with the shaft driven pinion gears
- 603—lubricating bearings supporting the pinion gear shafts with an oil slinger
- 604—pumping oil through the lubricating bearings and into a passageway for return to the right angle gear reducer
- 605—coupling an output shaft to the splined output of the planetary gear reducer and driving the output shaft at a desired rate
- 606—driving, with chains, the wheel shafts of the
vehicle 606 - The invention has been set forth by way of example with particularity. Those skilled in the art will readily recognize that changes may be made to the invention without departing from the spirit and the scope of the claimed invention.
Claims (17)
1. A bearing lubrication device comprising: a gear housing having an interior portion and a lubricating fluid reservoir therein; an oil slinger; a pinion shaft; a pinion shaft housing; a bearing for supporting said pinion shaft within said pinion shaft housing; said pinion shaft includes a passageway therethrough; and, said oil slinger supplying oil to said passageway communicating said oil to said bearing.
2. A bearing lubrication device as claimed in claim 2 wherein said pinion shaft includes a second passageway therethrough for communicating oil to said bearing.
3. A bearing lubrication device as claimed in claim 1 wherein said pinion shaft includes a first end portion; said first end portion includes a recess for receiving oil from said oil slinger; and, said first passageway communicates with said recess and said bearing.
4. A bearing lubrication device as claimed in claim 2 wherein said pinion shaft includes a first end portion; said first end portion includes a recess for receiving oil from said oil slinger; and, said second passageway communicates with said recess and said bearing.
5. A bearing lubrication device as claimed in claim 3 wherein said recess is cylindrically shaped.
6. A bearing lubrication device as claimed in claim 4 wherein said recess is cylindrically shaped.
7. A bearing lubrication device as claimed in claim 5 wherein said pinion shaft includes an exterior and said first passageway extends radially and longitudinally from said recess in said first end of said pinion shaft to said exterior of said pinion shaft.
8. A bearing lubrication device as claimed in claim 6 wherein said pinion shaft includes an exterior and said first and second passageways extend radially and longitudinally from said recess in said first end of said pinion shaft to said exterior of said pinion shaft.
9. A bearing lubrication device as claimed in claim 7 further including a second bearing; a chamber formed between said bearings, said pinion shaft housing and said pinion shaft; and, said first passageway in communication with said chamber.
10. A bearing lubrication device as claimed in claim 8 further including a second bearing; a chamber formed between said bearings, said pinion shaft housing and said pinion shaft; and, said first and second passageways in communication with said chamber.
11. A bearing lubrication device as claimed in claim 9 wherein said pinion shaft housing includes an interior and an exterior; said first bearing pumps oil from said chamber to said exterior of said pinion shaft housing and said second bearing pumps oil from said chamber to an oil return passageway communicating with said exterior of said pinion shaft housing.
12. A bearing lubrication device as claimed in claim 10 wherein said pinion shaft housing includes an interior and an exterior; said first bearing pumps oil to said chamber and said second bearing pumps oil out of said chamber to said interior of said pinion shaft housing; said pinion shaft housing includes an oil return passageway communicating with said interior of said pinion shaft housing and said exterior of said pinion shaft housing.
13. (canceled)
14. A method for lubricating bearings supporting a shaft in a gear box, comprising the steps of:
slinging oil from a lubricating oil reservoir using an oil slinger at a first end of said shaft;
collecting oil in a cylindrical recess in said first end of said shaft;
rotating said shaft and forcing said collected oil radially outwardly in said cylindrical recess and into a passageway communicating with said recess and extending longitudinally and radially from said recess to a chamber formed by said shaft, said bearings and a shaft housing;
pumping oil from said chamber through said bearings; and,
returning said oil to said lubricating oil reservoir.
15. A method for lubricating bearings supporting a shaft in a gear box as claimed in claim 14 wherein the step of returning said oil to said lubricating oil reservoir is performed using a return passageway through said shaft housing.
16. A method for lubricating bearings supporting a shaft in gear box as claimed in claim 14 wherein said step of rotating said shaft and forcing said collected oil radially outwardly in said cylindrical recess includes forcing said collected oil into a second passageway communicating with said recess and extending longitudinally and radially from said recess to said chamber formed by said shaft, said bearings and a shaft housing.
17. (canceled)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/296,106 US20120058853A1 (en) | 2007-03-23 | 2011-11-14 | Lubrication system for right-angle drives used with utility vehicles |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/690,785 US7954574B2 (en) | 2007-03-23 | 2007-03-23 | Offset drive system for utility vehicles |
US11/948,657 US8056662B2 (en) | 2007-03-23 | 2007-11-30 | Lubrication system for right-angle drives used with utility vehicles |
US13/296,106 US20120058853A1 (en) | 2007-03-23 | 2011-11-14 | Lubrication system for right-angle drives used with utility vehicles |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/948,657 Continuation US8056662B2 (en) | 2007-03-23 | 2007-11-30 | Lubrication system for right-angle drives used with utility vehicles |
Publications (1)
Publication Number | Publication Date |
---|---|
US20120058853A1 true US20120058853A1 (en) | 2012-03-08 |
Family
ID=39773579
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/948,657 Active 2029-08-19 US8056662B2 (en) | 2007-03-23 | 2007-11-30 | Lubrication system for right-angle drives used with utility vehicles |
US13/296,106 Abandoned US20120058853A1 (en) | 2007-03-23 | 2011-11-14 | Lubrication system for right-angle drives used with utility vehicles |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/948,657 Active 2029-08-19 US8056662B2 (en) | 2007-03-23 | 2007-11-30 | Lubrication system for right-angle drives used with utility vehicles |
Country Status (9)
Country | Link |
---|---|
US (2) | US8056662B2 (en) |
EP (1) | EP2125491B1 (en) |
CN (1) | CN101680524B (en) |
AT (1) | ATE547652T1 (en) |
CA (1) | CA2673148C (en) |
DK (1) | DK2125491T3 (en) |
ES (1) | ES2380150T3 (en) |
PL (1) | PL2125491T3 (en) |
WO (1) | WO2008118625A2 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140066242A1 (en) * | 2012-08-29 | 2014-03-06 | Greg SEBLANTE, SR. | Sprocket Box for Increasing the Gas Mileage of a Vehicle with an Automatic Transmission |
CN103758986A (en) * | 2014-01-10 | 2014-04-30 | 宁波东力机械制造有限公司 | Gear box hollow splined shaft output structure |
US20150045163A1 (en) * | 2013-08-09 | 2015-02-12 | Schaeffler Technologies Gmbh & Co. Kg | Idler sprocket lubrication assembly and method |
US10436306B2 (en) | 2017-12-14 | 2019-10-08 | Nio Usa, Inc. | Methods and systems for noise mitigation in multiple motor gearbox drive units |
US10486512B2 (en) * | 2017-08-29 | 2019-11-26 | Nio Usa, Inc. | Compact side-by-side motor gearbox unit |
US10703201B2 (en) | 2017-12-13 | 2020-07-07 | Nio Usa, Inc. | Modular motor gearbox unit and drive system |
DE102021101599A1 (en) | 2021-01-26 | 2022-07-28 | Audi Aktiengesellschaft | Motor vehicle with two electric machines as traction drives |
Families Citing this family (51)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7954574B2 (en) * | 2007-03-23 | 2011-06-07 | Fairfield Manufacturing Company, Inc. | Offset drive system for utility vehicles |
US8133143B2 (en) * | 2008-06-16 | 2012-03-13 | Fairfield Manufacturing Company, Inc. | Gear reducer electric motor assembly with internal brake |
US8474347B2 (en) * | 2009-06-08 | 2013-07-02 | Hub City, Inc. | High efficiency right angle gearbox |
DE202009010444U1 (en) * | 2009-08-02 | 2010-09-23 | Hema Metallbearbeitung Gmbh | Trolley for inspection work |
US8323143B2 (en) | 2009-12-02 | 2012-12-04 | Fairfield Manufacturing Company, Inc. | Integrated spindle-carrier electric wheel drive |
DE102010001750A1 (en) * | 2010-02-10 | 2011-08-11 | ZF Friedrichshafen AG, 88046 | Arrangement for driving a vehicle wheel with a drive motor |
US8485289B2 (en) * | 2011-02-24 | 2013-07-16 | Deere & Company | Air pressure regulated axle sump |
US8783393B2 (en) * | 2011-02-25 | 2014-07-22 | Deere & Company | Interface for a motor and drive assembly |
US9387544B2 (en) | 2011-05-02 | 2016-07-12 | Fairfield Manufacturing Company, Inc. | Smilled spline apparatus and smilling process for manufacturing the smilled spline apparatus |
US8556761B1 (en) * | 2012-05-30 | 2013-10-15 | Fairfield Manufacturing Company, Inc. | Bearing lubrication |
DE102012110269A1 (en) * | 2012-10-26 | 2014-04-30 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Drive train of a purely electrically driven motor vehicle |
US9650088B2 (en) * | 2012-12-06 | 2017-05-16 | Cnh Industrial America Llc | Work vehicle |
SK6817Y1 (en) | 2013-10-17 | 2014-07-02 | Cobrra S R O | Lubrication device and method of its operation |
US9358880B2 (en) * | 2013-12-13 | 2016-06-07 | Deere & Company | Tandem differential for a bogey application |
CN103863100B (en) * | 2014-03-26 | 2016-04-27 | 广西大学 | A kind of pure electronic four-wheel driving type construction machinery and equipment slippage chassis |
CN104149604B (en) * | 2014-08-19 | 2016-09-21 | 广西大学 | A kind of single motor drives and can make two and drives or the sliding chassis of 4 wheel driven switching |
US10124844B2 (en) | 2015-04-28 | 2018-11-13 | Cnh Industrial America Llc | System and method for supplying fluid to a track drive box of a work vehicle |
US10065500B2 (en) * | 2015-08-20 | 2018-09-04 | Sharp Kabushiki Kaisha | Vehicle body structure of autonomous traveling vehicle |
USD800198S1 (en) | 2016-01-21 | 2017-10-17 | Auburn Gear, Inc. | Combined electric motor and planetary transmission |
DE102016220414A1 (en) * | 2016-10-18 | 2018-04-19 | Audi Ag | Vehicle axle for a motor vehicle |
WO2020185719A2 (en) | 2019-03-08 | 2020-09-17 | Gecko Robotics, Inc. | Inspection robot |
CA3046651A1 (en) | 2016-12-23 | 2018-06-28 | Gecko Robotics, Inc. | Inspection robot |
US11307063B2 (en) | 2016-12-23 | 2022-04-19 | Gtc Law Group Pc & Affiliates | Inspection robot for horizontal tube inspection having vertically positionable sensor carriage |
US10400883B2 (en) | 2017-01-04 | 2019-09-03 | United Technologies Corporation | Gear with fluid control dam and apertures |
US10495185B2 (en) | 2017-03-06 | 2019-12-03 | Fairfield Manufacturing Company, Inc. | Planetary wheel drive using bushings |
US10272773B2 (en) | 2017-03-06 | 2019-04-30 | Fairfield Manufacturing Company, Inc. | Planetary wheel drive using thrust washer—cover arrangement |
US10093177B2 (en) | 2017-03-06 | 2018-10-09 | Fairfield Manufacturing Company, Inc. | Compact planetary wheel drive |
US10066735B1 (en) | 2017-03-06 | 2018-09-04 | Fairfield Manufacturing Company, Inc. | Planetary wheel drive single wall lugged output carrier |
US10132372B2 (en) | 2017-03-06 | 2018-11-20 | Fairfield Manufacturing Company, Inc. | Planetary wheel drive brake |
CN110546326B (en) | 2017-04-19 | 2022-10-28 | 克拉克设备公司 | Loader frame |
JP2019015393A (en) * | 2017-07-11 | 2019-01-31 | 株式会社ジェイテクト | Rotary device |
WO2019014479A1 (en) | 2017-07-12 | 2019-01-17 | Axle Tech International Ip Holdings, Llc. | Axle assembly for low floor vehicle |
CN111108012A (en) * | 2017-08-16 | 2020-05-05 | 艾里逊变速箱公司 | Axle assembly for frame rail vehicle |
DE102017123264B3 (en) * | 2017-10-06 | 2018-12-27 | Schaeffler Technologies AG & Co. KG | Electromechanical drive device for a multi-track motor vehicle |
GB2571130A (en) * | 2018-02-20 | 2019-08-21 | Jaguar Land Rover Ltd | Drive system for electric or hybrid vehicles |
CN108757842A (en) * | 2018-07-16 | 2018-11-06 | 宁津县金宏机械有限责任公司 | Planetary reduction gear and transmission system |
CN108775392A (en) * | 2018-08-08 | 2018-11-09 | 江苏欧邦电机制造有限公司 | A kind of Novel reducer |
CN108716490B (en) * | 2018-08-23 | 2023-08-04 | 安徽合力股份有限公司 | Hydraulic system of lifting appliance of stacker |
US11811296B2 (en) | 2020-02-12 | 2023-11-07 | Deere & Company | Electric machine with configurable stator/rotor cooling |
WO2021178202A1 (en) * | 2020-03-06 | 2021-09-10 | Manitou Equipment America, Llc | Loader with pivoting battery array support |
US11780319B2 (en) * | 2020-04-07 | 2023-10-10 | Deere & Company | Work vehicle electric drive assembly cooling arrangement |
US11628713B2 (en) * | 2020-06-04 | 2023-04-18 | Rivian Ip Holdings, Llc | Electric vehicle powertrain assembly having nested shafts |
US11787275B2 (en) * | 2020-06-10 | 2023-10-17 | Deere & Company | Electric drive with hydraulic mounting interface |
JP7339229B2 (en) * | 2020-11-16 | 2023-09-05 | トヨタ自動車株式会社 | electric vehicle |
EP4326493A1 (en) | 2021-04-20 | 2024-02-28 | Gecko Robotics, Inc. | Flexible inspection robot |
EP4327047A1 (en) | 2021-04-22 | 2024-02-28 | Gecko Robotics, Inc. | Systems, methods, and apparatus for ultra-sonic inspection of a surface |
EP4330062A1 (en) | 2021-04-26 | 2024-03-06 | Ree Automotive Ltd | Dual-axle vehicle corner assembly |
WO2023021510A1 (en) * | 2021-08-16 | 2023-02-23 | Ree Automotive Ltd | Dual-wheels corner system with transverse suspension |
CN113525718B (en) * | 2021-09-10 | 2022-05-24 | 吉林大学 | Z-shaped small lunar vehicle with high folding-unfolding ratio |
CN114538313B (en) * | 2022-02-28 | 2023-08-15 | 杭州兴珹传动有限公司 | Screw rod lifter |
US20240149667A1 (en) * | 2022-11-04 | 2024-05-09 | Borgwarner Inc. | Modular electric vehicle drive module |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5209321A (en) * | 1990-05-10 | 1993-05-11 | Nissan Motor Co., Ltd. | Power transmission apparatus |
US7178424B2 (en) * | 2004-12-06 | 2007-02-20 | American Axle & Manufacturing, Inc. | Pinion unit in axle assembly |
US7396308B2 (en) * | 2004-12-21 | 2008-07-08 | Toyota Jidosha Kabushiki Kaisha | Vehicular drive system |
Family Cites Families (110)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US558180A (en) * | 1896-04-14 | hutchinson | ||
US1570356A (en) * | 1922-06-03 | 1926-01-19 | Pb Yates Machine Co | Lubricating appliance |
US1869776A (en) * | 1929-07-29 | 1932-08-02 | Deming Co | Automatic oiling system |
US2258077A (en) * | 1937-07-28 | 1941-10-07 | Robert S Taylor | Oiling system for gearing |
US2191221A (en) * | 1938-07-16 | 1940-02-20 | Ingraham E Co | Synchronous electric motor structure |
US2263936A (en) * | 1938-11-28 | 1941-11-25 | Robert S Taylor | Oiling system for axles |
US2417957A (en) * | 1939-09-02 | 1947-03-25 | Robert S Taylor | Planetary transmission |
US2336513A (en) * | 1939-09-02 | 1943-12-14 | Robert S Taylor | Speed change system |
US2574986A (en) * | 1947-10-30 | 1951-11-13 | Pacitic Car And Foundry Compan | Transfer transmission mechanism |
US2638173A (en) * | 1950-05-31 | 1953-05-12 | Clark Equipment Co | Dual wheel drive with lubricating means |
US2950773A (en) * | 1956-02-01 | 1960-08-30 | Yale & Towne Mfg Co | Gear drive steering and traction unit |
US3214989A (en) * | 1963-04-01 | 1965-11-02 | Falk Corp | Vertical right angle speed reducer |
US3767013A (en) * | 1971-08-16 | 1973-10-23 | Pennwalt Corp | Start-up lubricator |
US3770074A (en) * | 1972-04-24 | 1973-11-06 | Gen Motors Corp | Reduction drive for electric axle |
US3848702A (en) * | 1972-10-02 | 1974-11-19 | Copeland Corp | Lubricating system for vertical machine elements |
US3796108A (en) * | 1972-12-18 | 1974-03-12 | Chemineer | Right angle speed reducer |
US3798991A (en) * | 1972-12-18 | 1974-03-26 | Chemineer | Intermediate right angle speed reducer |
US3857301A (en) * | 1973-03-01 | 1974-12-31 | Westinghouse Electric Corp | Speed reducer |
US4050544A (en) * | 1974-05-01 | 1977-09-27 | Kalyan Jagdish C | Lubrication system for an air motor |
US4031780A (en) * | 1974-11-29 | 1977-06-28 | Chrysler Corporation | Coupling apparatus for full time four wheel drive |
US4051922A (en) * | 1975-08-13 | 1977-10-04 | Sukle Vincent F | Lubricating system for bearings |
US4121694A (en) * | 1975-10-28 | 1978-10-24 | New River Manufacturing Company, Inc. | Labyrinth lubricant seal for belt conveyor roll |
US4170549A (en) * | 1975-12-08 | 1979-10-09 | Johnson Louis W | Vibrating screen apparatus |
US4018097A (en) * | 1976-01-07 | 1977-04-19 | Eaton Corporation | Axle lubrication system |
US4057126A (en) * | 1976-03-25 | 1977-11-08 | The Falk Corporation | Lubricant wiper |
US4090588A (en) * | 1976-09-17 | 1978-05-23 | Ingersoll-Rand Company | Means for lubricating machine components |
JPS5479374U (en) * | 1977-11-15 | 1979-06-05 | ||
US4222283A (en) * | 1978-04-27 | 1980-09-16 | General Motors Corporation | Manual transmission lubrication system |
US4221279A (en) * | 1978-12-11 | 1980-09-09 | Dana Corporation | Centrifugal lubrication system for transmission pocket bearing |
US4359142A (en) * | 1979-02-08 | 1982-11-16 | Dana Corporation | Impeller lubrication system for transmission pocket bearing |
US4327950A (en) * | 1979-03-29 | 1982-05-04 | Elliott Turbomachinery Co., Inc. | Bearing and lubrication system |
US4265337A (en) | 1979-07-16 | 1981-05-05 | Crown Controls Corporation | Fork lift truck speed control dependent upon fork elevation |
JPS6039573Y2 (en) * | 1980-08-20 | 1985-11-27 | トヨタ自動車株式会社 | Foreign object jamming prevention device in gear transmission |
US4361774A (en) * | 1980-09-24 | 1982-11-30 | Whirlpool Corporation | Lubrication slinger with lint sweeper for a motor |
DE3169258D1 (en) * | 1981-08-28 | 1985-04-18 | Howden James & Co Ltd | Bearing |
US4588385A (en) * | 1981-09-10 | 1986-05-13 | Yamaha Hatsudoki Kabushiki Kaisha | Water cooled, four-cycle internal combustion engine for outboard motors |
US4575311A (en) * | 1981-12-21 | 1986-03-11 | Indal Technologies Inc. | Gear box assembly-upper head assembly |
JPS60107450U (en) * | 1983-12-23 | 1985-07-22 | トヨタ自動車株式会社 | Lubrication mechanism of automotive final reducer |
JPS60157593A (en) | 1984-01-27 | 1985-08-17 | Hitachi Ltd | Bearing lubrication device |
US6327994B1 (en) | 1984-07-19 | 2001-12-11 | Gaudencio A. Labrador | Scavenger energy converter system its new applications and its control systems |
JPH064070Y2 (en) * | 1984-11-06 | 1994-02-02 | 株式会社東芝 | Rotary compressor |
US4683985A (en) * | 1985-01-04 | 1987-08-04 | Dresser Industries, Inc. | Lubrication system for a vertical gear unit |
US4705449A (en) * | 1985-07-10 | 1987-11-10 | Christianson Leslie L | Skid-steer vehicle |
US4616736A (en) * | 1985-07-25 | 1986-10-14 | Dresser Industries, Inc. | Oil system for contiguous gear boxes |
GB2186342A (en) * | 1986-02-06 | 1987-08-12 | Johnson Electric Ind Mfg | An electric motor and gearbox unit and component parts thereof |
US4700808A (en) * | 1986-07-17 | 1987-10-20 | Haentjens Walter D | Shaft mounted bearing lubricating device |
US4741303A (en) * | 1986-10-14 | 1988-05-03 | Tecumseh Products Company | Combination counterbalance and oil slinger for horizontal shaft engines |
US4766859A (en) * | 1987-07-24 | 1988-08-30 | Yamaha Hatsudoki Kabushiki Kaisha | Lubricating system for vertical shaft engine |
US4803897A (en) * | 1987-09-18 | 1989-02-14 | General Electric Company | Drive system for track-laying vehicles |
US5024636A (en) * | 1989-06-27 | 1991-06-18 | Fairfield Manufacturing Company, Inc. | Planetary wheel hub |
CH676739A5 (en) * | 1988-08-02 | 1991-02-28 | Asea Brown Boveri | |
US4962821A (en) | 1989-03-22 | 1990-10-16 | Daewoo Heavy Industries Ltd. | Discrete drive system for a skid steer loader |
US4987974A (en) * | 1989-12-11 | 1991-01-29 | Saturn Corporation | Device to assist with the radial distribution of lubricating fluid from a rotating shaft |
US5261676A (en) * | 1991-12-04 | 1993-11-16 | Environamics Corporation | Sealing arrangement with pressure responsive diaphragm means |
US5161644A (en) * | 1992-04-17 | 1992-11-10 | A. E. Chrow | Lubrication system for tandem axle assembly |
SE506126C2 (en) * | 1993-02-22 | 1997-11-10 | Scania Cv Ab | Device at gearbox for reconditioning of lubricant |
US5333704A (en) * | 1993-04-01 | 1994-08-02 | John Hoff | Rotating lubricating technique for equipment |
US5591018A (en) * | 1993-12-28 | 1997-01-07 | Matsushita Electric Industrial Co., Ltd. | Hermetic scroll compressor having a pumped fluid motor cooling means and an oil collection pan |
US5478290A (en) * | 1994-01-28 | 1995-12-26 | Fairfield Manufacturing Co., Inc. | Two speed high shift transmission |
US5505112A (en) * | 1994-02-18 | 1996-04-09 | Eaton Corporation | Churning loss reduction means for gear type devices |
JP3471071B2 (en) * | 1994-04-12 | 2003-11-25 | 株式会社荏原製作所 | Bearing lubrication system for rotating machinery |
DE4414164A1 (en) * | 1994-04-22 | 1995-10-26 | Zahnradfabrik Friedrichshafen | Gear housing |
JP3322072B2 (en) * | 1994-08-12 | 2002-09-09 | トヨタ自動車株式会社 | Power transmission lubrication system |
US5480003A (en) * | 1994-09-09 | 1996-01-02 | Emerson Electric Co. | Passive lubrication delivery system and integral bearing housing |
JP3329417B2 (en) * | 1994-09-21 | 2002-09-30 | 株式会社フジユニバンス | Lubrication structure of transfer device |
US5718302A (en) * | 1994-09-27 | 1998-02-17 | Aisin Aw Co., Ltd. | Hydraulic circuit for electric car drive train |
US5630481A (en) * | 1995-03-07 | 1997-05-20 | Tuthill Corporation | Radial sleeve bearing and associated lubrication system |
US5601155A (en) * | 1995-07-05 | 1997-02-11 | Delaware Capital Formation, Inc. | Journal bearing using disk for transporting lubricant |
US5616097A (en) * | 1995-10-06 | 1997-04-01 | Fairfield Manufacturing Co., Inc. | Press fit carrier/spindle for use in planetary transmission |
DE19538192A1 (en) | 1995-10-13 | 1997-04-17 | Zahnradfabrik Friedrichshafen | Oil supply device for shaft bearing |
FR2740853B1 (en) | 1995-11-07 | 1998-01-23 | Peugeot | DEVICE FOR DYNAMIC LUBRICATION OF A GUIDE BEARING FOR AN ELECTRIC MOTOR SHAFT |
TW487770B (en) * | 1995-12-15 | 2002-05-21 | Honda Motor Co Ltd | Lubricating system in a 4-stroke engine |
JP3074135B2 (en) * | 1995-12-19 | 2000-08-07 | 住友重機械工業株式会社 | Gear transmission |
US6047678A (en) * | 1996-03-08 | 2000-04-11 | Ryobi North America, Inc. | Multi-position operator-carried four-cycle engine |
US5667036A (en) * | 1996-05-21 | 1997-09-16 | New Venture Gear, Inc. | Lubrication system for transmissions |
JP3190008B2 (en) * | 1996-10-09 | 2001-07-16 | 本田技研工業株式会社 | Oil mist generator for lubrication in engines |
US6276474B1 (en) | 1997-02-18 | 2001-08-21 | Rockwell Heavy Vehicle Systems, Inc. | Low floor drive unit assembly for an electrically driven vehicle |
US5810116A (en) * | 1997-06-04 | 1998-09-22 | New Venture Gear, Inc. | Bearing lubrication mechanism |
US5887678A (en) * | 1997-06-19 | 1999-03-30 | Briggs & Stratton Corporation | Lubrication apparatus for shaft bearing |
DE19732637C5 (en) | 1997-07-29 | 2006-09-14 | Daimlerchrysler Ag | Electric drive for a wheel hub |
JP2984640B2 (en) * | 1997-12-18 | 1999-11-29 | 三菱重工業株式会社 | Hermetic scroll compressor |
JP3646498B2 (en) * | 1997-12-26 | 2005-05-11 | スズキ株式会社 | Transmission lubrication device |
JP3518333B2 (en) * | 1998-05-15 | 2004-04-12 | 日産自動車株式会社 | Lubrication structure of vehicle power transmission |
US6146118A (en) * | 1998-06-22 | 2000-11-14 | Tecumseh Products Company | Oldham coupling for a scroll compressor |
US6810849B1 (en) * | 1999-01-25 | 2004-11-02 | Briggs & Stratton Corporation | Four-stroke internal combustion engine |
US6705555B1 (en) * | 2000-02-04 | 2004-03-16 | Jack R. Bratten | Lift station and method for shallow depth liquid flows |
US6374951B1 (en) * | 2000-02-22 | 2002-04-23 | Eaton Corporation | Gear isolation shroud for transmission |
US6616563B2 (en) * | 2000-09-04 | 2003-09-09 | Kanzaki Kokyukoki Mfg. Co., Ltd. | Transmission of working vehicle |
US6439208B1 (en) * | 2000-09-22 | 2002-08-27 | Accessible Technologies, Inc. | Centrifugal supercharger having lubricating slinger |
US6616567B2 (en) * | 2000-10-10 | 2003-09-09 | Terex Corporation | Two speed gear box |
US6855083B1 (en) * | 2001-01-18 | 2005-02-15 | Dana Corporation | Lubrication pump for inter-axle differential |
US6702703B2 (en) * | 2001-01-18 | 2004-03-09 | Dana Corporation | Lubrication pump for inter-axle differential |
US6488110B2 (en) | 2001-02-13 | 2002-12-03 | Mtd Products Inc. | Vehicle drive system |
US20030159888A1 (en) | 2001-05-18 | 2003-08-28 | Burkholder Robert F. | Disk oil slinger assembly |
US6588539B2 (en) * | 2001-07-12 | 2003-07-08 | Caterpillar Inc | Wheel and final drive assembly for a ground driven work machine |
US6742482B2 (en) * | 2001-08-22 | 2004-06-01 | Jorge Artola | Two-cycle internal combustion engine |
FR2830486B1 (en) * | 2001-10-05 | 2004-04-23 | Gkn Glaenzer Spicer | MOTOR-STEERING AXLE FOR MOTORIZED VEHICLES |
US6616432B2 (en) * | 2001-12-28 | 2003-09-09 | Visteon Global Technologies, Inc. | Fluid pump mechanism for use in existing helical gearsets |
US6698762B2 (en) * | 2002-07-10 | 2004-03-02 | Emerson Electric Co. | Rotary device shaft with oil slinger groove |
US6852061B2 (en) * | 2002-09-30 | 2005-02-08 | Benjamin Warren Schoon | Planetary gearbox with integral electric motor and steering means. |
US6964313B2 (en) * | 2003-01-23 | 2005-11-15 | Biketoo, Incorporated | Personal transport vehicle, such as a bicycle |
US7011600B2 (en) * | 2003-02-28 | 2006-03-14 | Fallbrook Technologies Inc. | Continuously variable transmission |
US7166052B2 (en) * | 2003-08-11 | 2007-01-23 | Fallbrook Technologies Inc. | Continuously variable planetary gear set |
US20060104838A1 (en) | 2004-04-30 | 2006-05-18 | Wood Mark W | Integrated eccentric flywheel oil slinger |
US7455616B2 (en) | 2004-05-05 | 2008-11-25 | General Electric Company | Removable thrust washer retainer for a motorized wheel off-highway dump truck |
JP4200938B2 (en) * | 2004-05-18 | 2008-12-24 | トヨタ自動車株式会社 | Electric wheel |
US7160219B2 (en) | 2004-06-03 | 2007-01-09 | Arvinmeritor Technology Llc. | Method and apparatus for lubricating a differential gear assembly |
US7420301B2 (en) | 2004-10-04 | 2008-09-02 | Axletech International Ip Holdings, Llc | Wheel assembly with integral electric motor |
US7866444B2 (en) | 2006-04-06 | 2011-01-11 | Fairfield Manufacturing Company, Inc. | Cascading oil flow bearing lubrication device |
US7954574B2 (en) * | 2007-03-23 | 2011-06-07 | Fairfield Manufacturing Company, Inc. | Offset drive system for utility vehicles |
-
2007
- 2007-11-30 US US11/948,657 patent/US8056662B2/en active Active
-
2008
- 2008-03-08 WO PCT/US2008/056337 patent/WO2008118625A2/en active Application Filing
- 2008-03-08 DK DK08731764.0T patent/DK2125491T3/en active
- 2008-03-08 CA CA2673148A patent/CA2673148C/en not_active Expired - Fee Related
- 2008-03-08 PL PL08731764T patent/PL2125491T3/en unknown
- 2008-03-08 AT AT08731764T patent/ATE547652T1/en active
- 2008-03-08 CN CN2008800011742A patent/CN101680524B/en not_active Expired - Fee Related
- 2008-03-08 ES ES08731764T patent/ES2380150T3/en active Active
- 2008-03-08 EP EP08731764A patent/EP2125491B1/en not_active Not-in-force
-
2011
- 2011-11-14 US US13/296,106 patent/US20120058853A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5209321A (en) * | 1990-05-10 | 1993-05-11 | Nissan Motor Co., Ltd. | Power transmission apparatus |
US7178424B2 (en) * | 2004-12-06 | 2007-02-20 | American Axle & Manufacturing, Inc. | Pinion unit in axle assembly |
US7396308B2 (en) * | 2004-12-21 | 2008-07-08 | Toyota Jidosha Kabushiki Kaisha | Vehicular drive system |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20140066242A1 (en) * | 2012-08-29 | 2014-03-06 | Greg SEBLANTE, SR. | Sprocket Box for Increasing the Gas Mileage of a Vehicle with an Automatic Transmission |
US9163706B2 (en) * | 2012-08-29 | 2015-10-20 | Greg SEBLANTE, SR. | Sprocket box for increasing the gas mileage of a vehicle with an automatic transmission |
US20150045163A1 (en) * | 2013-08-09 | 2015-02-12 | Schaeffler Technologies Gmbh & Co. Kg | Idler sprocket lubrication assembly and method |
US9228653B2 (en) * | 2013-08-09 | 2016-01-05 | Schaeffler Technologies AG & Co. KG | Idler sprocket lubrication assembly and method |
CN103758986A (en) * | 2014-01-10 | 2014-04-30 | 宁波东力机械制造有限公司 | Gear box hollow splined shaft output structure |
US10486512B2 (en) * | 2017-08-29 | 2019-11-26 | Nio Usa, Inc. | Compact side-by-side motor gearbox unit |
US10703201B2 (en) | 2017-12-13 | 2020-07-07 | Nio Usa, Inc. | Modular motor gearbox unit and drive system |
US10436306B2 (en) | 2017-12-14 | 2019-10-08 | Nio Usa, Inc. | Methods and systems for noise mitigation in multiple motor gearbox drive units |
DE102021101599A1 (en) | 2021-01-26 | 2022-07-28 | Audi Aktiengesellschaft | Motor vehicle with two electric machines as traction drives |
DE102021101599B4 (en) | 2021-01-26 | 2023-10-19 | Audi Aktiengesellschaft | Motor vehicle with two electric machines as a traction drive |
Also Published As
Publication number | Publication date |
---|---|
EP2125491A2 (en) | 2009-12-02 |
PL2125491T3 (en) | 2012-06-29 |
ES2380150T3 (en) | 2012-05-09 |
WO2008118625A2 (en) | 2008-10-02 |
DK2125491T3 (en) | 2012-04-02 |
CA2673148C (en) | 2013-02-19 |
CA2673148A1 (en) | 2008-10-02 |
CN101680524B (en) | 2012-09-26 |
EP2125491A4 (en) | 2010-07-14 |
ATE547652T1 (en) | 2012-03-15 |
US20080230289A1 (en) | 2008-09-25 |
US8056662B2 (en) | 2011-11-15 |
CN101680524A (en) | 2010-03-24 |
WO2008118625A3 (en) | 2009-12-30 |
EP2125491B1 (en) | 2012-02-29 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US8056662B2 (en) | Lubrication system for right-angle drives used with utility vehicles | |
US7954574B2 (en) | Offset drive system for utility vehicles | |
AU2016210756B2 (en) | Axle Assembly with Interaxle Differential Lubrication | |
CN101602326A (en) | A kind of differential retarder | |
US20050250611A1 (en) | Sun pinion cover | |
EP3825161A1 (en) | Drivetrain system having an axle assembly | |
US8128524B2 (en) | Sheath assembly for a planetary gear | |
US11655882B2 (en) | Chain driven e-drive gearbox | |
US7416504B2 (en) | Lubrication plug | |
US10112483B2 (en) | Hydraulic pump assembly with forward driveshaft clearance | |
US10082196B2 (en) | Hybrid transaxle | |
US20180156326A1 (en) | Passive lubrication system for concentric gear drive for an electric vehicle | |
US20220213957A1 (en) | Vehicle drive device | |
CN207961482U (en) | A kind of low speed and large torque car deceleration device with lubricating system | |
CN216045338U (en) | Transmission structure of double-output power takeoff | |
US20240174078A1 (en) | Integrated electric power take-off for use with an electric vehicle | |
CN212080059U (en) | Planetary gear mechanism for hybrid power transmission | |
US20110296662A1 (en) | Input shaft with internal dry splines and sealed plug and method of manufacturing a hybrid powertrain utilizing the same | |
WO2017147033A1 (en) | Motor-driven pump for hydraulic control system | |
JP2011185402A (en) | Device of differential gear for vehicle |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: FAIRFIELD MANUFACTURING COMPANY, INC., INDIANA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SCHOON, BENJAMIN WARREN;DAMMON, JAMES R.;SIGNING DATES FROM 20071120 TO 20071130;REEL/FRAME:027225/0062 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |