Method and Apparatus for the Conversion of Two Wheel Drives to Four Wheel Drives With a Self Engaging Bi-Directional Double Overrunning Clutch Assembly

Abstract

A drive arrangement comprising a motor, a self engaging, double overrunning, bi-directional pump, and a wheel is usable in converting two wheel drive vehicles to four wheel drive vehicles.

Description

CROSS REFERENCES TO RELATED APPLICATIONS

This application claims the benefit of co-pending U.S. patent application Ser. No. 12/592,375 filed Nov. 24, 2009 which claims the benefit of U.S. Provisional Patent Application Ser. No. 61/200,199 filed Nov. 25, 2008.

A portion of the disclosure for this patent document contains material to which a claim for copyright is made. The copyright owner has no objection to the facsimile reproduction of by anyone of the patent document or the patent disclosure, as it appears in the Patent and Trademark Office patent file or records, but reserves all other copyrights whatsoever.

STATEMENT AS TO RIGHTS TO INVENTIONS MADE UNDER FEDERALLY SPONSORED RESEARCH AND DEVELOPMENT

Not applicable

BACKGROUND OF INVENTION

1. Field of the Invention

This invention relates to the application of a self engaging bi-directional overrunning Clutch assembly for the conversion of two wheel driven vehicles to four wheel driven vehicles, especially for vehicles with front wheel drives where a simple four wheel drive conversion would be of value.

2. Background Information

Hydraulic systems are popular in applications involving hazardous, dirty, and nasty environments, such as coal mines, quarries, food processing plants, and construction sites.

Much effort has been expended in trying to increase the efficiency and performance ranges of hydraulic drives.

The experience of co-inventor, George H. Morgan, over the past 35 years, has been that simple mechanisms in convenient packages for bolting between hydraulic components such as hydraulic pumps and motors, greatly simplify and extend the range of applications for hydraulic driven machinery and equipment.

This is especially true in the use of brakes, clutches, and brake/clutch combinations.

Past industrial surveys have indicated that the field of brakes and clutches is most frustrating for machinery designers. They can't find what they want and application information is inadequate in many instances. The problem is especially acute for short run equipment and machinery manufacturers.

As an example, the development of the AUSCO™ failsafe brake and clutch line featured brakes, brakes with one way clutches, and clutches in convenient configurations that bolted between planetary gear boxes and hydraulic motors, most of which had mounting configurations to the SAE J744 pump mounting standards. With standard convenient configurations, ready to bolt into position, with large factors of safety, the simple approach was very well received by equipment and machinery designers. By having standard, off the shelf configurations, matching what was already out there, marketed through fluid power distributors as an afterthought with the hydraulic motors and pumps, produced in respectable volumes, the approach swept the industry in the 1970s and 1980s. The approach solved a real problem in the application of brakes and clutches for the short line equipment builders. The volume demand permitted economics of scales that led to the acceptance by major manufacturers beyond short run equipment builders, around the world.

While there is a self engaging double over-running clutch available from HILLIARD™, it is not in a package convenient to short run equipment manufacturers.

Also, there is a long standing felt need for simpler ways to convert two wheel drive vehicles to four wheel drive vehicles, especially for cars with front wheel drives.

SUMMARY OF THE INVENTION

The present invention in the preferred embodiment is the application of a clutch assembly comprising a housing, at least one self engaging bi-directional double overrunning clutch, a power input shaft, a power output shaft, shaft supporting bearings, seals, and retaining rings. A motor, such as, but not restricted to an electrical motor or a hydraulic motor, drives through the clutch assembly to power a driven load.

The housing, in the preferred embodiment of the present invention comprises a forward male pilot and a rear female pilot, and mounting flanges to simplify installation.

The at least one bi-directional over-running clutch fits between the power input and the power output shafts.

This is especially applicable for converting two wheel driven vehicles to four wheel drives, especially front wheel driven vehicles.

BRIEF SUMMARY OF THE DRAWINGS

FIGS. 1 and 11A illustrate potential applications of the preferred embodiment of the present invention, a self engaging bi-directional overrunning clutch assembly,

FIG. 2 illustrates the preferred embodiment of the present invention in a configuration facilitating installation.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to FIG. 2, the preferred embodiment of the present invention, a wheel, a motor, and a self engaging bi-directional double overrunning clutch assembly 1 that comprises a housing 2, at least one self engaging bi-directional double overrunning clutch 3, a power input shaft 6, a power output shaft 17, shaft supporting bearings 10, 11, 13, 14, and 20, seals 5 and 18, snap rings 9, 14, 15, and 16, and a spacer 4.

The housing comprises mounting flanges 22 and 23.

In operation, when an input torque is imparted to either of said shafts 6 or 17, the at least one bi-directional overrunning clutch 3 engages the other of said shafts 6 or 17, imparting the torque from the either of said shafts 6 or 17 to the other of said shafts 6 or 17, to drive a load such as a wheel 109 (Ref. FIG. 1A) or a wheel 109 through a differential 105 (Ref. FIG. 1).

To simplify the explanation, say the said shaft 6 is driving the said shaft 17 through said clutch assembly 1, which is driving the wheel 109 shown in FIG. 1A. If the wheel 109 overruns the driving shaft 6, the said shaft 17 can overrun the said shaft 6 because of the at least one self engaging bi-directional double overrunning clutch 3. In the arrangement shown in FIG. 2 there are two clutches 3 mechanically acting in parallel, that is to say each clutch 3 carries half the load and in overrunning both clutches overrun.

This provides significant advantage over simply making a bigger clutch as a bigger clutch would take up more space causing the shaft 6 to be larger in diameter which in turn would cause the housing 2 to be larger in diameter which is very undesirable in many applications. Using the concept it would be possible to arrange 3 or 4 clutches in parallel to carry higher loads.

In FIG. 1, a motor 107, such as, but not restricted to, a hydraulic or and electric motor, is driving through said clutch assembly 1 into a differential 105, to turn the wheels 109, while the transmission 103 is in neutral, When an operator of a vehicle drive with an internal combustion engine 102, serving as the power source, the transmission 103, a driveline 104, the differential 105, axles 108, and wheels 109, wants to go faster, such as after start up with the motor 107, the operator of the vehicle drive can engage the transmission 103 and drive the driveline 104 which drives through the differential 105 which drives the axles 108 which drive the wheels 109 from the engine 102 through the transmission 103, through the driveline 104, through the differential 105, through the axles 108, overrunning the motor 107 because of the self engaging bi-directional overrunning clutches 3 within the clutch assembly 1. This is a much simpler approach than using a multiple disc or jaw or cone clutch with all the problems of engagement and disengagement.

Referring to FIG. 1A, a drive assembly 100 is shown comprising the wheel assembly 109, which in this case represents a driven load, the clutch 1, the motor 107, and the power supply lines 112A. The motor 107 can be electric or hydraulic, and the power supply lines 112A can be electrical supply lines or fluid power supply lines, whichever is appropriate for a given type of motor 107. While hydraulic componentry is discussed extensively in this specification, ways and means of supplying electric power to an electric motor is a very well developed art, so the applicants have not delved into how to supply electric power to an electric motor.

In FIG. 1A, in a multiple wheel vehicle, driving the vehicle faster with other wheels is greatly simplified with the self engaging bi-directional double overrunning clutch assembly 1 (Ref. FIG. 1). This facilitates multiple speed arrangements for vehicle designers, such as, but not restricted to construction equipment where sometimes extra torque is required in a low speed mode.

In the preferred embodiment of the present invention, the at least one self engaging bi-directional double overrunning clutch 3 is a HILLEARD™ self engaging bi-directional overrunning clutch such as is known in the snowmobile and ATV trade.

As HILLIARD™ has limited sizes available, having said shafts 6 and 17 properly sized to allow multiple said clutches 3 to be inserted between said shafts 6 and 17, the torque rating of said clutch assembly 1 can be increased, with minimal effect on configuration profile.

The differential 105, as shown in FIG. 1, has two inputs, one from the drive line 104 and one from the hydraulic motor 107 through the clutch assembly 1. This permits two inline torque inputs into the differential 105 which is a very simple design approach as compared to existing cumbersome approaches. Extra pieces and extra connections are very unacceptable in the automotive design world.

FIG. 1 illustrates a hydraulic pump 110, with hydraulic lines 112, which are in fluid communication with a hydraulic motor 107 attached to said clutch assembly 1 which is connected to a differential 105 which is connected to a driveshaft 104 and axles 10, said axles 118 driving wheels 109, said transmission 103, attached to an engine 102.

The hydraulic pump 110, in the preferred embodiment of the present invention comprises a solenoid actuated clutch engageable pulley 111 driven by a belt drive off the engine 102.

For hydraulic driving of the wheels 109 at low speed, the transmission 103 is in neutral, the solenoid actuated clutch engageable pulley 111 is engaged, engaging the pump 110 which pumps oil to the motor 107 to drive through said clutch assembly 1 with a mounting housing 2, engaging said at least one clutch 3 (Ref. FIG. 2), which drives through the differential 105, which drives the axles 108, which drives the wheels 109.

When a higher speed is desired, the transmission 103 is engaged, the hydraulic pump 110 disengaged, and the drive shaft 104 drives through the differential 105 at a higher speed than the hydraulic motor 107, and the power output shaft 107 (FIG. 2) overruns the power input shaft 6, thanks to said at least one clutch 3. This greatly simplifies clutch engaging arrangements as compared to cone clutches, multiple disc clutches, or other types of clutches that require force inputs for actuation or release.

In the preferred embodiment the differential 105 is of the type with a ring gear and two pinion gears which is common to the trade.

In the preferred embodiment of the present invention, the pump clutch 111 is a solenoid operated belt and pulley driven electric clutch such as is used in automotive air conditioning systems. Scherer Fluid Power, of Troy, Mich. applied such a clutch to a hydraulic pump some 25 or 30 years ago. The pump clutch 111 is shown with the pump 110 with hydraulic lines 112 which are in fluid communication with the hydraulic motor 107.

In the preferred embodiment of the present invention, the motor 107 is a ROLLER STATOR™ HB series hydraulic motor manufactured by White Hydraulics of Hopkinsville. Ky.

In the preferred embodiment of the present invention, the dutch 3 is a self actuating bi-directional double overrunning dutch such as is manufactured by the Motion Control Division of the Hilliard Corporation of Elmira, N.Y. It was used by Polaris Industries to produce the first 4-wheel drive, all-terrain vehicle capable of providing automatic front-wheel drive engagement in both forward or reverse modes. The dements only engage upon power input, from either direction, but permits a driven load to overrun the power input.

In operation, when smooth operation of a vehicle drive (not shown) at low speeds is desired, the engine 102 power is diverted from the mechanical drive line 104 by having the transmission 103 in neutral and using the hydraulic pump 110, through the belt drive 113 and the pump clutch 111.

Hydraulic fluid is pumped from the hydraulic pump 110 to drive the motor 107 mounted on the differential 105, said hydraulic motor 107 driving the axles 108 through the clutch assembly 1 which is engaged by the activation of the at least one clutch 3 upon receiving an input motion from the motor 107. The axles 108 drive the wheels 109. Said engine 102 is operated in a speed range where the engine operation is smooth, and efficient, while the speed of the driven wheels 109 of the vehicle (not shown) can be controlled by various means such as a variable speed axial piston pump 110, a variable speed hydraulic motor 107, or, with proper sizing, a fixed displacement pump 110 and a fixed displacement hydraulic motor 107, such as the previously mentioned ROLLER STATOR HB motor 107 and a variable engine 102 speed. Danfoss Sauer, with plants in Denmark, Germany, and the United States, manufactures a range of axial piston hydraulic pumps with electro/hydraulic controls that would be quite suitable for this application.

When a given speed is reached where said engine 102 can operate a vehicle drive in a conventional manner, the transmission 103 is engaged, the hydraulic pump 110 is declutched. The motor 107 is not engaged because of the overrunning feature of said at least one said clutch 3 of said clutch assembly 1.

In the preferred embodiment of the present invention, said engine 102 is a gasoline engine which is using homogeneous charge compression ignition (i.e. HCCI) technology from diesel engines to improve engine performance.

By setting said engine 102 in the conventional manner to operate a vehicle drive at optimum transit speeds for fuel economy, and using the hydraulic drive arrangements at slow speeds, such as initial start up speeds to reach transit speeds, the limitations inherent in current HCCI engines are considerably alleviated.

Combining a hydraulic drive apparatus with a homogeneous charge compression ignition technology prime mover, alleviates the problem of rough operation of a vehicle with a homogeneous charge compression ignition technology prime mover engine 102 operating at low speeds.

The drive assembly 100 (Ref. FIG. 1A) is usable for the conversion of front wheel drive vehicles to four wheel drive vehicles by using the engine 102 to power two motors 107, each of the motors 107 driving through a respective clutch assembly 1 to drive a respective rear wheel 109. This is a solution for converting front wheel drive vehicles to four wheel drives, a problem that has perplexed vehicle designers to the present day.

(Ref. FIG. 1A). The at least one self engaging bi-directional double overrunning clutch 3 in the clutch assembly 1 permits forward and reverse operation, without external means of clutch engagement.

A second alternative embodiment would be an auxiliary vehicle drive means comprising the engine 102 powering each of two motors 107 through its respective clutch assembly 1 into each of two front wheels 109 of s rear wheels 109 driven vehicle. This is a means of converting two rear wheel 109 driven vehicles such as, but not restricted to, pickup trucks used as service auxiliary vehicles in surface mining operations to four wheel drives, providing the higher torque required for driving up mine access slopes that is available with four wheel drive vehicles. FIG. 1A illustrates a hydraulic motor into said clutch assembly 1 into the wheel 109.

As an example, with a differential 105 with a 3.5/1 input/output ratio, and a 210 foot pound Hilliard self engaging bi-directional double overrunning clutch 3 tied into the driveline 4 through the differential 105. with a 6.5 cubic inch White ROLLER STATOR™ HB series motor 107, with the hydraulic pump 110 producing 4.4 gallons per minute (gpm) at 3,000 psi, with a wheel 109 rolling radius of 13 inches. the tractive effort of each wheel 109 would be approximately 680 pounds.

The 4.5 gpm would result in approximately 10 miles per hour vehicle speed. This figure assumes an 85% mechanical efficiency with a 90% volumetric efficiency of the hydraulic motor 107 and a 90% volumetric for the hydraulic pump 110. For a hydraulic pump or motor, the volumetric efficiency represents the usable output of fluid as compared to the fluid input. The difference is the internal leakage required for lubrication of internal parts of the hydraulic pump or motor. The internal leakage is a function of pressure differential across the hydraulic pump or motor.

Using multiple said clutches 3, multiples of the above calculated torques can be obtained with off the shelf clutches 3, thereby avoiding tooling costs for special configuration, such as larger diameters.

The White Hydraulics ROLLER STATOR™ HB series White motor has very smooth operation at unusually low revolutions. Applicant witnessed a HB series motor (with a 24 cubic inch displacement, as memory serves, some 20 years ago) tested at one sixth of a revolution per minute, with no visible output shaft clocking or rippling. It was used on hydraulic wheel chair drives because of this characteristic. In the preferred embodiment of this invention, the operating speed is from zero to approximately 132 revolutions per minute. With proper fluid selection the speed range is approximately triple that. However, the intent is to operate a vehicle with hydraulics until the vehicle speed is such the said engine 2 can smoothly operate the vehicle.

In co-applicant Morgan's experience, spanning some forty years in the field of hydraulics comprising product design, circuit design, and sales and marketing experience, the combination of an axial piston pump 110 and a White Hydraulics model HB motor 109 in vehicle drives, can preclude a requirement of a high speed hydraulic motor/planetary gear box combination.

Although the description above contains many specificities, these should not be construed as limiting the scope of the invention but as merely providing illustrations of some of the presently preferred embodiments of this invention.

For example, the HILLIARD self engaging bi-directional double overrunning clutch 3 is the preferred embodiment, as is the pulley driven electric actuated clutch. Weight is an important consideration in vehicle design. However, as obvious to anyone skilled in the art, there are almost countless varieties of clutches that can be made to work, albeit perhaps with weight and complexity disadvantages. In the good old days, weight was considered good for traction, and steel was cheap, so fuel conservation was not much of an issue. However, some 30 years ago, automotive designers realized that not only were steel prices going up, but to meet customer demand for fuel efficiency, weight reduction was a primary way to achieve fuel consumption. Now, weight reduction is a major goal for mobile equipment manufacturers.

Also, there are other ways to tie in the said clutch assembly 1 and the hydraulic motor 107 into the driveline 104, Adding a power take off gearing arrangement would be an off highway type solution. However, this involves added weight, additional gears with resultant slight decrease in operating efficiencies, and possible loss of smoothest operation potential.

Also, the hydraulic pump 110 and pump clutch 111 can be connected to the engine in a variety of ways, by a vehicle manufacture's engineers, such as, but not restricted to, off the crankshaft at the front of the engine, off an accessory drive gearing arrangement, or a chain accessory drive. Space limitations, weight, reliability, and cost are among the factors involved.

In front wheel drives, the drive shaft 104 and the differential 105 functions, as well as the transmission 103 functions, are incorporated adjacent, if not within, the engine 102. So, the said clutch assembly 1 and the motor 107 could be tied into the differential 105 in the engine 102/transmission 103 region of the vehicle, as opposed to the rear of the vehicle as indicated in FIG. 1.

While FIG. 1 illustrate a differential 105 applied as a rear end differential 105, the differential 105 could be near the front of a front wheel drive vehicle, incorporated within an different type housing as opposed to what is represented in FIG. 1.

While the input power shaft 6 is shown as an internally splined shaft, and the output power shaft 1 is shown as an externally splined shaft, as obvious to anyone skilled in the art, either of the shafts 6 or 17 could be internally or externally splined.

The term fluid is intended to cover any fluid suitable for serving its intended purpose in the preferred embodiment of the invention described. There are many different types of fluids currently used or being developed for hydraulic drives, such as, but not restricted to, hydraulic oils, engine oils, synthetic oils, vegetable base oils, even water with and without additives.

For enablement purposes, MOBIL 1 synthetic oil with a 10W30 viscosity should serve well. The temperature rating is in the order of 400 degrees F. as opposed to most hydraulic oils designed for 120 degree F. system temperatures. This oil worked well for an application of a hydraulic drives designed by co-applicant Morgan in a region where the ambient temperatures reach 165 degrees F. in the summer.

While the preferred embodiment of the present invention stresses hydraulics, i.e. a hydraulic motor in communication with a hydraulic pump, the basic concept of a motor is not restricted to a hydraulic motor, it would also work with an electric motor, but that would entail all the stuff involved with electric drives. While all the stuff is currently bulky and expensive, i.e. battery, controls and so on, there are developments on the horizon that make electric driven power trains very competitive with conventional internal combustion engines power trains.

Applicant Morgan is confident there will be dramatic improvements in the range of electric vehicles within a few years.

Also, as the potential of this invention is realized, the self engaging double overrunning bi-directional clutch can be incorporated into the motor design or the wheel assembly design for applications such as, but not restricted to vehicle drive applications. It will be obvious to those skilled in the art that modifications may be made to the embodiments described above without departing from the scope of the present invention. Thus the scope of the invention should be determined by the appended claims in the formal application and their legal equivalents, rather than by the examples given.

Claims

1. A drive comprising:

wheels,

a power source,

at least one of the wheels driven by an axle powered by the power source,

a hydraulic pump driven by the power source,

at least one hydraulic motor,

at least one of the wheels not driven by the axle,

at least a first and second self engaging double overrunning bi-directional clutch acting in parallel said first bi-directional dutch rotating in a first direction, and said second bi-directional dutch rotating in the same, first direction, and wherein said at least first and second clutches are engaged in said first direction and said at least first and second clutches are disengaged when rotating in a second direction, and wherein said at least first and second clutches configured to operate in unison in all operating conditions,

wherein the at least one hydraulic motor is in fluid communication with the hydraulic pump,

wherein the at least one of the wheels not driven by the axle is driven by the hydraulic motor through the at least one self engaging double overrunning bi-directional dutch,

wherein the drive can operate driving only the at least one of the wheels driven by the axle,

wherein the drive can also operate by means of the at least one of the wheels driven by the hydraulic motor through the at least one self engaging double overrunning bi-directional clutch.

2. The drive of claim 1 wherein the power source is an internal combustion engine.

3. (canceled)

4. The drive of claim 2 wherein the internal combustion engine drives the hydraulic pump to selectively supply hydraulic fluid to the at least one hydraulic motor.

5. (canceled)

6. (canceled)

7. (canceled)

8. (canceled)

9. (canceled)

10. The drive of claim 5, wherein the self engaging bi-directional double overrunning clutch fits between said input and output shafts.

11. A drive comprising:

at least two wheels, and wherein at least one of said at least two wheels is driven by an axle powered by a power source;

a self engaging bi-directional overrunning clutch assembly comprising: a housing, at least one self engaging bi-directional double overrunning clutch, an input shaft, an output shaft, and a gearing for operation without external actuation, wherein each of said at least one self engaging bi-directional overruning clutches engage in rotating the same direction and configured to operate in unison in all operating conditions;

a hydraulic pump driven by said power source, and wherein an at least one hydraulic motor is in fluid communication with said hydraulic pump; and

wherein any of said at least one wheels not driven by said axle is then driven by said hydraulic motor through the at least one self engaging double overrunning bi-directional clutch.

12. The drive as recited in claim 11, wherein said dutch assembly is configured for application without external actuation.

13. The assembly as recited in claim 12, wherein each of said at least one self engaging bi-directional double overrunning clutches act in parallel.

14. The assembly as recited in claim 13, wherein each of said at least one self engaging bi-directional double overrunning clutches operate in either direction.

15. The drive of claim 11, wherein said at least one self engaging bi-directional double overrunning clutch is disposed between said input and output shafts.