FIELD OF THE INVENTION This invention relates to internal combustion engines, and more particularly to a centrifugally responsive mechanical compression release.

BACKGROUND OF THE INVENTION Compression release mechanisms are common in pull-start engines to make the engines easier to start. In a normal pull-start engine, the operator pulls a rope which moves the engine through one or more cycles. During the compression stroke of the engine cycle, the operator must exert enough force to compress the air in the combustion chamber, and the additional force from compressing the air makes it more difficult to start the engine. In a pull-start engine with a compression release mechanism, pressure in the combustion chamber is slightly released during the compression stroke to reduce the resistive force on the rope. This makes the engine easier to start because the operator does not have to pull the rope as hard. Typically, a compression release mechanism slightly unseats the exhaust valve to vent the combustion chamber during starting while the engine is revolving at cranking speeds. The mechanism then typically disengages when the engine reaches normal operating speeds.

Some compression release mechanisms use centrifugal forces to disengage themselves from the cam follower. These designs generally have a cam member and a flyweight. When the cam shaft rotation speed reaches a certain point, the flyweight moves away from the cam shaft, which positions the cam member out of contact with the cam follower. Some previous saddle-type compression release designs had pivot points on the cam shaft that required machining or drilling of the cam shaft. Modifying and machining a cam shaft is difficult because of its hardness and curved surface. The flyweights of some saddle-type designs also required apertures in the cam gear for clearance.

Other compression release mechanisms involve complex shapes that are difficult to manufacture and assemble. Complex designs usually require additional manufacturing steps which increase the cost of the part. Also, a complex part usually takes longer to assemble and is more likely to be assembled improperly.

SUMMARY OF THE INVENTION The present invention includes a cam with a cam lobe and base radius. The cam is preferably slip fit over a cam shaft. A compression release member is preferably located adjacent the base radius and retained by a retainer, although the compression release member could be placed in other locations. In one embodiment, the compression release member is disposed in a slot on the base radius. The compression release member preferably comprises a first portion, a second portion, and a bridging portion that interconnects the first and second portions. Preferably, the first portion has an arc-shaped auxiliary cam surface that engages a cam follower, and the second portion functions as a flyweight. The pivot pin is preferably disposed within the curvature of the bridging portion and retains the compression release member in the slot. The bridging portion contacts the back surface of the slot, which absorbs the forces the cam follower applies on the compression release member. In the preferred embodiment, the compression release member may be symmetrical about a line through the bridging portion, but by no means is the invention limited to this embodiment. A symmetrical design provides additional benefits, but is not necessary to practice this invention.

In operation, the cam follower contacts the cam lobe as the cam shaft rotates. The compression release member is located in a slot along the base radius. At low speeds, the auxiliary cam surface engages the cam follower and slightly lifts the cam follower from the cam. Once the engine reaches higher running speeds, centrifugal forces pivot the compression release member out of contact with the cam follower.

The present invention achieves many advantages over previous compression release mechanisms. Biasing springs are not needed when the invention is incorporated into vertical shaft engines. The costly process of machining the cam shaft is no longer necessary because the compression release member is preferably integrated into the cam, which can be slip fit over the cam shaft. This arrangement can be readily integrated into an engine utilizing a cam lever and direct lever overhead valve system.

The back surface of the slot bears the forces the cam follower applies upon the compression release member. This substantially flat back surface is capable of supporting a relatively large amount of force and minimizes the forces applied on the pivot pin. The auxiliary cam surface is curved so there are no corners to cut into the cam follower. The cam follower is also preferably curved, and this smooth transition of the cam follower from the base radius to the compression release member extends the life of the parts.

In the preferred embodiment applied to a 5 hp engine, the compression release member is approximately 0.375 inches wide. This width dimension is wider than most previous compression release mechanisms and allows the forces transferred to the back surface to be distributed along a larger surface area. One skilled in the art will realize the invention does not require this large of a width dimension, and the size of the compression release member ultimately depends on the size of the cam lobe and the engine. The invention is by no means limited to this dimension, which merely provides an additional benefit of the preferred embodiment.

Additional advantages of this invention are derived from its efficient design. The compression release member may be easily stamped, or cut from a metal coil and bent into the proper shape. As previously mentioned, the compression release member may be symmetrical about a line through the bridging portion. While not necessary, the symmetrical design provides benefits during assembly of the invention. Since both the first and second portions are the substantially the same in this embodiment, either arced surface may be the auxiliary cam surface; the compression release member cannot be placed in the slot upside-down. This feature saves time during the assembly process, eliminates many mis-assembled parts, and reduces costs.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a perspective view of the cam follower and cam gear with the compression release member in the disengaged position.

Fig. 2 is a cross-sectional view, taken along line 2-2 of Fig. 1.

Fig. 3 is a perspective view of the cam gear with the compression release member in the engaged position.

Fig. 4 is a cross-sectional view, taken along line 4-4 of Fig. 3 with the cam follower in contact with the compression release member.

Fig. 5 is a bottom view of an overhead valve engine embodying the invention with the engine crankcase cover removed.

Fig. 6 is a top view of the cam gear showing nubs to retain the compression release member.

Fig. 7 is a top view of the cam gear showing a pivot pin to retain the compression release member.

Fig. 8 is a perspective view of an alternative embodiment of the cam follower and cam gear with the compression release member in the disengaged position.

Fig. 9 is a cross-sectional view, taken along line 9-9 of Fig. 8.

Before the embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangements of components set forth in the following description or illustrated in the drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting.

DETAILED DESCRIPTION FIGS. 3 and 4 illustrate the cam 4 with the compression release member 24 in the engaged position while the engine is rotating at starting speeds. The cam 4 includes a cam lobe 8, a base radius 16, and a slot 20 that extends into, and is formed in the base radius 16.

The compression release member 24 is pivotably retained in the slot 20 between the base radius 16 and the cam shaft 2.

In FIG. 4, the compression release member 24 is substantially V-shaped and consists of a first portion 40, a second portion 44 and a bridging portion 48. The first portion 40 and second portion 44 are preferably substantially flat surfaces. An arc-shaped auxiliary cam surface 36 at the end of the first portion 40 extends slightly beyond the base radius 16 to contact the cam follower 12. The second portion 44 preferably has sufficient mass to function as a flyweight. Preferably, the bridging portion 48 is substantially U- shaped and interconnects the first portion 40 and second portion 44. The pivot pin 28 is disposed within the curved segment of the bridging portion 48.

In the preferred embodiment, the first portion 40 and second portion 44 may be substantially identical and the compression release member may be symmetrical about a line through the bridging portion 48 that is substantially parallel to the pivot axis 56 (Fig.

3). This configuration is not necessary for the invention to function, but a symmetrical design offers advantages during the device's assembly. If the first portion 40 and second portion 44 are interchangeable, the compression release member 24 can be installed with the first and second portions 40,44 reversed. This eliminates confusion, saves time, and reduces costs during assembly.

The overall design of the compression release member 24 provides for cost effective manufacturing methods. Preferably, the compression release member 24 is cut from a strip of coiled metal and bent into the desired shape. The compression release

member 24 could also be starr ped from a metal strip or sheet. Relatively little waste material is generated from the. ; e processes due to the part's efficient design. The inexpensive material along wi : h the uncomplicated manufacturing process leads to the reduced cost of the compression release member 24.

The compression release member 24 is preferably retained in the slot 20 by a pivot pin 28. In the preferred embodiment, planes containing the substantially flat surfaces 42, 46 respectively of the first portion 40 and the second portion 44 are substantially parallel to the pivot axis 56. The compression release member 24 is free to pivot about the pivot pin 28, and the pivot axis 56 of the compression release member 24 substantially passes through the pivot pin 28. The compression release member 24 is positioned such that the cam shaft 2 and the pivot axis 56 do not intersect. Costly machining of the cam shaft 2 is no longer needed because the pivot axis 56 is offset from the cam shaft 2.

The pivot pin 28 preferably does not support the force exerted on the compression release member 24 by the cam follower 12. The bridging portion 48 contacts the back surface 32 which buttresses the compression release member 24. Most of the force the cam follower 12 applies on the compression release member 24 is absorbed by the back surface 32. Because of this arrangement, the pivot pin 28 will not suffer from large shear stresses and may last longer.

While in the engaged position, the first portion 40 contacts the shoulder 22, which provides vertical support for the compression release member 24. In the preferred embodiment, the first portion 40 is positioned vertically below the pivot pin 28 when installed on a vertical shaft engine. When the auxiliary cam surface 36 is below the pivot pin 28, gravity returns the compression release member 24 to the engaged position, so a biasing spring is not needed in vertical shaft applications. A return spring may be needed in a horizontal shaft application. This arrangement also allows the cam follower 12 to apply a downward force upon the compression release member 24 and prevent the compression release member 24 from moving out of the engaged position prematurely.

Another feature is that once the speed increases enough to move the auxiliary cam surface 36 above the pivot pin 28, the cam follower 12 will help push the compression release member 24 to the disengaged position.

FIGS. 1 and 2 illustrate the compression release member 24 in the disengaged position. As the rotation speed of the cam 4 reaches normal running speeds, the flyweight second portion 44 is centrifugally forced away from the cam shaft 2, causing the compression release member 24 to pivot into the disengaged position. The auxiliary cam

surface 36 then moves out of contact from the cam follower 12. In the preferred embodiment applied to a 5 hp engine, the kick-out speed when the compression release member moves to the disengaged position is approximately 600 RPM, but it could vary between 300 and 1200 RPM. The compression release member 24 in the preferred embodiment pivots approximately 20 degrees, but one skilled in the art will recognize that this angle depends on the length of the compression release member 24 and size of the engine. In an engine with a cam 4 having a smaller base radius 16 and shorter compression release member 24, the compression release member 24 may pivot 25 to 30 degrees before the auxiliary cam surface 36 disengages from the cam follower 12.

A preferred embodiment of the mechanical compression release 24 of the present invention is illustrated in FIG. 5 as it would appear in a vertical shaft engine with a direct lever overhead valve system. A preferred embodiment has one cam lobe 8. An alternative embodiment could have two cam lobes, one for each valve actuation. The cam 4 preferably slips over the cam shaft 2 and rotates about the cam shaft 2, which is pressed into the crankcase cover. In this embodiment, the cam shaft 2 is stationary, although the cam shaft 2 could rotate with the cam lobe 8 in other embodiments.

The cam 4 preferably consists of the base radius 16 and the cam lobe 8. The cam followers 12,14 control the exhaust and intake valves respectively and contact the cam 4 as it rotates. A valve is closed when a cam follower 12,14 engages the base radius 16, and opened when a cam follower 12,14 engages the cam lobe 8. The cam followers 12,14 respectively for the exhaust and intake valves preferably contact the cam 4 at slightly different levels. The cam 4 preferably has a slot 20 that extends into the base radius 16. A compression release member 24 is preferably disposed within this slot 20 at a level that is only capable of contacting the exhaust valve cam follower 12 as the cam 4 rotates. In the alternative, compression release member 24 could operate on the intake valve.

FIG. 7 illustrates a view of the cam 4. The compression release member 24 of the present invention is preferably interconnected with the rotating cam 4, although the compression release member 24 could be placed in other locations. In the preferred embodiment, the compression release member 24 is disposed within the slot 20, and the auxiliary cam surface 36 extends slightly beyond the base radius 16. In the preferred embodiment, the compression release member 24 can be located between the base radius 16 and the cam shaft 2 because this engine design uses a relatively large cam 4.

The auxiliary cam surface 36 is preferably arc-shaped so there are no corners to contact the cam follower 12 (FIG. 3) and cause excessive wear. Cam follower 12 (FIG. 3)

is also preferably arc-shaped to reduce wear on the parts. As the cam 4 rotates, the compression release member 24 preferably moves the cam follower 12 (FIG. 3) far enough from the base radius 16 to slightly open the exhaust valve. The shape of the auxiliary cam surface 36 is selected to obtain a specific valve opening profile. In the preferred embodiment applied to a 5 hp engine of the direct lever type, the compression release member 24 causes the exhaust valve to open approximately 0.035 inches.

The compression release member 24 is preferably retained by a retainer. As illustrated in FIG. 7, the compression release member 24 is retained by the pivot pin 28.

In an alternate embodiment illustrated in FIG. 6, nubs 128 are used to retain the compression release member 24. The cam 4 may be fabricated with the nubs 128 integrally formed on the opposing side walls 134,135 of the slot 20. Preferably, the nubs 128 are at the end of flexible extensions 130 that interconnect them to the slot 20. With the nubs 128, the compression release member 24 can simply be pressed into place without the additional assembly step of installing the pivot pin 28 (FIG. 7). The flexible extensions 130 allow the nubs 128 to bend and provide clearance for the compression release member 24, and then return to their original positions to properly retain the compression release member 24.

The nubs 128 serve the same function as the pivot pin 28 (FIG. 7) and eliminate the need for a separate pivot pin 28 (FIG. 7). The design of the cam 4 and the compression release member 24 allows the nubs 128 to be substituted for the relatively stronger pivot pin 28 (FIG. 7). As mentioned above, the force applied on the compression release member 24 by the cam follower 12 (FIG. 3) is supported by the back surface 32.

Therefore the nubs 128 preferably only retain the compression release member 24, and do not have to be of sufficient strength to support all of the forces applied on the compression release member 24.

Another alternate embodiment is illustrated in FIGS. 8 and 9 in which the slot 220 does not extend all the way to the base radius 216. In this embodiment, the edge of the cam 204 gradually slopes to the shoulder 222 instead of suddenly dropping off near the end of the slot 20 (FIG. 4). This embodiment shows the compression release member 24 in the disengaged position, and the cam follower 12 contacting the base radius 216. The edge of the cam 204 near the base radius 216 slopes to meet the shoulder 222, but there is still enough surface remaining on the base radius 216 to properly position the cam follower 12.