EP1255916B1 - Mechanical compression release - Google Patents
Mechanical compression release Download PDFInfo
- Publication number
- EP1255916B1 EP1255916B1 EP01907150A EP01907150A EP1255916B1 EP 1255916 B1 EP1255916 B1 EP 1255916B1 EP 01907150 A EP01907150 A EP 01907150A EP 01907150 A EP01907150 A EP 01907150A EP 1255916 B1 EP1255916 B1 EP 1255916B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compression release
- release member
- cam
- engine
- cam follower
- 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.)
- Expired - Lifetime
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Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/08—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio
- F01L13/085—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio the valve-gear having an auxiliary cam protruding from the main cam profile
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
- F02B63/02—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for hand-held tools
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/08—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio
Definitions
- said pivot axis is substantially parallel to said back surface.
- said first and second portions are substantially identical.
- Preferred embodiments of the present invention achieve 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 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.
- 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.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- This invention relates to internal combustion engines, and more particularly to a centrifugally responsive mechanical compression release.
- 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.
- In accordance with the present invention there is provided an internal combustion engine, comprising:
- a cam shaft;
- a cam having
- a cam lobe that engages a cam follower to lift an engine valve;
- a base radius; and a compression release member, the engine being characterized in that said compression release member is pivotably retained by a retainer adjacent said base radius, said compression release member engages said cam follower at engine starting speeds, and has a pivot axis that is substantially transverse to but does not intersect said cam shaft.
-
- Desirably said retainer is at least one pivot pin that retains said compression release member.
- More desirably said retainer includes two nubs formed integral with said cam.
- Conveniently a slot is formed in said base radius, and said compression release member is disposed within said slot.
- Preferably said slot is partially defined by a back surface that bears load forces imparted on said compression release member by said cam follower.
- Conveniently said pivot axis is substantially parallel to said back surface.
- Preferably said cam shaft extends in a vertical direction during normal engine operation, said compression release member has an auxiliary cam surface that engages the cam follower, said compression release member has a pivot axis, and the auxiliary cam surface is disposed at a position lower than said pivot axis in the vertical direction.
- Desirably said compression release member has an arc-shaped auxiliary cam surface that engages the cam follower.
- Preferably said compression release member pivots about a pivot axis, and said compression release member is symmetrical about said pivot axis.
- Desirably said compression release member is substantially V-shaped.
- More preferably said compression release member includes a first portion having an auxiliary cam surface that engages said cam follower; a second portion having sufficient mass to function as a flyweight; and a bridging portion that interconnects said first and second portions.
- Conveniently said first and second portions are substantially identical.
- Desirably said compression release member pivots about a pivot axis disposed between said first and second portions.
- Preferably the pivot axis is disposed between said base radius and said cam shaft.
- Preferably said cam includes a back surface that bears load forces imparted on said compression release member by said cam follower, and said compression release member includes a U-shaped portion having a rounded surface that contacts said back surface while said compression release member pivots with respect to said cam.
- Desirably said compression release member pivots between an engaged position, in which said auxiliary cam surface engages said cam follower at engine starting speeds, and a disengaged position, in which said auxiliary cam surface does not engage said cam follower, and wherein both said first and second portions are disposed radially outwardly from said pivot axis with respect to said cam shaft when said compression release member is in the disengaged position.
- In a 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 of preferred embodiments, 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.
- Preferred embodiments of the present invention achieve 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 a 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 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.
-
- 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.
- FIGS. 3 and 4 illustrate the
cam 4 with thecompression release member 24 in the engaged position while the engine is rotating at starting speeds. Thecam 4 includes acam lobe 8, abase radius 16, and aslot 20 that extends into, and is formed in thebase radius 16. Thecompression release member 24 is pivotably retained in theslot 20 between thebase radius 16 and thecam shaft 2. - In FIG. 4, the
compression release member 24 is substantially V-shaped and consists of afirst portion 40, asecond portion 44 and a bridgingportion 48. Thefirst portion 40 andsecond portion 44 are preferably substantially flat surfaces. An arc-shapedauxiliary cam surface 36 at the end of thefirst portion 40 extends slightly beyond thebase radius 16 to contact thecam follower 12. Thesecond portion 44 preferably has sufficient mass to function as a flyweight. Preferably, the bridgingportion 48 is substantially U-shaped and interconnects thefirst portion 40 andsecond portion 44. Thepivot pin 28 is disposed within the curved segment of the bridgingportion 48. - In the preferred embodiment, the
first portion 40 andsecond portion 44 may be substantially identical and the compression release member may be symmetrical about a line through the bridgingportion 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 thefirst portion 40 andsecond portion 44 are interchangeable, thecompression release member 24 can be installed with the first andsecond portions - The overall design of the
compression release member 24 provides for cost effective manufacturing methods. Preferably, thecompression release member 24 is cut from a strip of coiled metal and bent into the desired shape. Thecompression release member 24 could also be starr ped from a metal strip or sheet. Relatively little waste material is generated from these processes due to the part's efficient design. The inexpensive material along with the uncomplicated manufacturing process leads to the reduced cost of thecompression release member 24. - The
compression release member 24 is preferably retained in theslot 20 by apivot pin 28. In the preferred embodiment, planes containing the substantiallyflat surfaces first portion 40 and thesecond portion 44 are substantially parallel to the pivot axis 56. Thecompression release member 24 is free to pivot about thepivot pin 28, and the pivot axis 56 of thecompression release member 24 substantially passes through thepivot pin 28. Thecompression release member 24 is positioned such that thecam shaft 2 and the pivot axis 56 do not intersect. Costly machining of thecam shaft 2 is no longer needed because the pivot axis 56 is offset from thecam shaft 2. - The
pivot pin 28 preferably does not support the force exerted on thecompression release member 24 by thecam follower 12. The bridgingportion 48 contacts theback surface 32 which buttresses thecompression release member 24. Most of the force thecam follower 12 applies on thecompression release member 24 is absorbed by theback surface 32. Because of this arrangement, thepivot pin 28 will not suffer from large shear stresses and may last longer. - While in the engaged position, the
first portion 40 contacts theshoulder 22, which provides vertical support for thecompression release member 24. In the preferred embodiment, thefirst portion 40 is positioned vertically below thepivot pin 28 when installed on a vertical shaft engine. When theauxiliary cam surface 36 is below thepivot pin 28, gravity returns thecompression 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 thecam follower 12 to apply a downward force upon thecompression release member 24 and prevent thecompression release member 24 from moving out of the engaged position prematurely. Another feature is that once the speed increases enough to move theauxiliary cam surface 36 above thepivot pin 28, thecam follower 12 will help push thecompression 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 thecam 4 reaches normal running speeds, the flyweightsecond portion 44 is centrifugally forced away from thecam shaft 2, causing thecompression release member 24 to pivot into the disengaged position. Theauxiliary cam surface 36 then moves out of contact from thecam 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. Thecompression 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 thecompression release member 24 and size of the engine. In an engine with acam 4 having asmaller base radius 16 and shortercompression release member 24, thecompression release member 24 may pivot 25 to 30 degrees before theauxiliary cam surface 36 disengages from thecam 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 onecam lobe 8. An alternative embodiment could have two cam lobes, one for each valve actuation. Thecam 4 preferably slips over thecam shaft 2 and rotates about thecam shaft 2, which is pressed into the crankcase cover. In this embodiment, thecam shaft 2 is stationary, although thecam shaft 2 could rotate with thecam lobe 8 in other embodiments. - The
cam 4 preferably consists of thebase radius 16 and thecam lobe 8. Thecam followers cam 4 as it rotates. A valve is closed when acam follower base radius 16, and opened when acam follower cam lobe 8. Thecam followers cam 4 at slightly different levels. Thecam 4 preferably has aslot 20 that extends into thebase radius 16. Acompression release member 24 is preferably disposed within thisslot 20 at a level that is only capable of contacting the exhaustvalve cam follower 12 as thecam 4 rotates. In the alternative,compression release member 24 could operate on the intake valve. - FIG. 7 illustrates a view of the
cam 4. Thecompression release member 24 of the present invention is preferably interconnected with therotating cam 4, although thecompression release member 24 could be placed in other locations. In the preferred embodiment, thecompression release member 24 is disposed within theslot 20, and theauxiliary cam surface 36 extends slightly beyond thebase radius 16. In the preferred embodiment, thecompression release member 24 can be located between thebase radius 16 and thecam shaft 2 because this engine design uses a relativelylarge 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 thecam 4 rotates, thecompression release member 24 preferably moves the cam follower 12 (FIG. 3) far enough from thebase radius 16 to slightly open the exhaust valve. The shape of theauxiliary 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, thecompression 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, thecompression release member 24 is retained by thepivot pin 28. In an alternate embodiment illustrated in FIG. 6,nubs 128 are used to retain thecompression release member 24. Thecam 4 may be fabricated with thenubs 128 integrally formed on the opposingside walls slot 20. Preferably, thenubs 128 are at the end offlexible extensions 130 that interconnect them to theslot 20. With thenubs 128, thecompression release member 24 can simply be pressed into place without the additional assembly step of installing the pivot pin 28 (FIG. 7). Theflexible extensions 130 allow thenubs 128 to bend and provide clearance for thecompression release member 24, and then return to their original positions to properly retain thecompression 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 thecam 4 and thecompression release member 24 allows thenubs 128 to be substituted for the relatively stronger pivot pin 28 (FIG. 7). As mentioned above, the force applied on thecompression release member 24 by the cam follower 12 (FIG. 3) is supported by theback surface 32. Therefore thenubs 128 preferably only retain thecompression release member 24, and do not have to be of sufficient strength to support all of the forces applied on thecompression 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 thebase radius 216. In this embodiment, the edge of thecam 204 gradually slopes to theshoulder 222 instead of suddenly dropping off near the end of the slot 20 (FIG. 4). This embodiment shows thecompression release member 24 in the disengaged position, and thecam follower 12 contacting thebase radius 216. The edge of thecam 204 near thebase radius 216 slopes to meet theshoulder 222, but there is still enough surface remaining on thebase radius 216 to properly position thecam follower 12.
Claims (16)
- An internal combustion engine, comprising:a cam shaft (2);a cam (4) havinga cam lobe (8) that engages a cam follower (12) to lift an engine valve;a base radius (16); and a compression release member (24), the engine being characterized in that said compression release member (24) is pivotably retained by a retainer (28, 128) adjacent said base radius (16), said compression release member (24) engages said cam follower (12) at engine starting speeds, and has a pivot axis (56) that is substantially transverse to but does not intersect said cam shaft (2).
- An engine as claimed in claim 1, characterized in that said retainer is at least one pivot pin (28) that retains said compression release member (24).
- An engine as claimed in claim 1, characterized in that said retainer includes two nubs (128) formed integral with said cam (4).
- An engine as claimed in claim 1, characterized by a slot (20) formed in said base radius, wherein said compression release member is disposed within said slot.
- An engine as claimed in claim 4, characterized in that said slot is partially defined by a back surface (32) that bears load forces imparted on said compression release member by said cam follower.
- An engine as claimed in claim 1, characterized in that said pivot axis (56) is substantially parallel to said back surface (32).
- An engine as claimed in claim 1, characterized in that said cam shaft extends in a vertical direction during normal engine operation, wherein said compression release member has an auxiliary cam surface (36) that engages the cam follower, wherein said compression release member has a pivot axis, and wherein the auxiliary cam surface is disposed at a position lower than said pivot axis in the vertical direction.
- An engine as claimed in claim 1, characterized in that said compression release member has an arc-shaped auxiliary cam surface (36) that engages the cam follower.
- An engine as claimed in claim 1, characterized in that said compression release member pivots about a pivot axis, and wherein said compression release member is symmetrical about said pivot axis.
- An engine as claimed in claim 1, characterized in that said compression release member is substantially V-shaped.
- An engine as claimed in claim 1, characterized in that said compression release member includes:a first portion (40) having an auxiliary cam surface that engages said cam follower;a second portion (44) having sufficient mass to function as a flyweight; anda bridging portion (48) that interconnects said first and second portions.
- An engine as claimed in claim 11, characterized in that said first and second portions are substantially identical.
- An engine as claimed in claim 11, characterized in that said compression release member pivots about a pivot axis disposed between said first and second portions.
- An engine as claimed in claim 1, characterized in that the pivot axis is disposed between said base radius and said cam shaft.
- An engine as claimed in claim 1, characterized in that said cam includes a back surface that bears load forces imparted on said compression release member by said cam follower, and said compression release member includes a U-shaped portion having a rounded surface that contacts said back surface while said compression release member pivots with respect to said cam.
- An engine as claimed in claim 13, characterized in that said compression release member pivots between an engaged position, in which said auxiliary cam surface engages said cam follower at engine starting speeds, and a disengaged position, in which said auxiliary cam surface does not engage said cam follower, and wherein both said first and second portions are disposed radially outwardly from said pivot axis with respect to said cam shaft when said compression release member is in the disengaged position.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/507,070 US6349688B1 (en) | 2000-02-18 | 2000-02-18 | Direct lever overhead valve system |
US507070 | 2000-02-18 | ||
US09/782,468 US6494175B2 (en) | 2000-02-18 | 2001-02-09 | Mechanical compression release |
PCT/US2001/004140 WO2001061157A1 (en) | 2000-02-18 | 2001-02-09 | Mechanical compression release |
US782468 | 2001-02-09 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1255916A1 EP1255916A1 (en) | 2002-11-13 |
EP1255916B1 true EP1255916B1 (en) | 2005-09-14 |
Family
ID=27055692
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01907150A Expired - Lifetime EP1255916B1 (en) | 2000-02-18 | 2001-02-09 | Mechanical compression release |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1255916B1 (en) |
AU (1) | AU2001257885A1 (en) |
DE (1) | DE60113384T2 (en) |
WO (1) | WO2001061157A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6439187B1 (en) | 1999-11-17 | 2002-08-27 | Tecumseh Products Company | Mechanical compression release |
US6886518B2 (en) * | 2000-02-18 | 2005-05-03 | Briggs & Stratton Corporation | Retainer for release member |
US6782861B2 (en) * | 2001-02-09 | 2004-08-31 | Briggs & Stratton Corporation | Vacuum release mechanism |
US6536393B2 (en) | 2000-09-11 | 2003-03-25 | Tecumseh Products Company | Mechanical compression and vacuum release |
US6499453B1 (en) * | 2000-10-30 | 2002-12-31 | Tecumseh Products Company | Mid cam engine |
JP4454872B2 (en) * | 2001-02-20 | 2010-04-21 | 本田技研工業株式会社 | Decompression device for internal combustion engine |
US6539906B2 (en) | 2001-03-30 | 2003-04-01 | Tecumseh Products Company | Mechanical compression and vacuum release |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3395689A (en) * | 1966-09-15 | 1968-08-06 | Studebaker Corp | Engine decompression apparatus |
US5150674A (en) * | 1991-05-21 | 1992-09-29 | Briggs & Stratton Corporation | Centrifugally responsive compressing release mechanism |
US5301643A (en) * | 1993-05-05 | 1994-04-12 | Briggs & Stratton Corporation | Low oil sensor using compression release to affect engine operation |
DE19543445C1 (en) * | 1995-11-22 | 1997-02-20 | Porsche Ag | Automatic decompression device for control valve of IC engine |
-
2001
- 2001-02-09 AU AU2001257885A patent/AU2001257885A1/en not_active Abandoned
- 2001-02-09 DE DE60113384T patent/DE60113384T2/en not_active Expired - Lifetime
- 2001-02-09 EP EP01907150A patent/EP1255916B1/en not_active Expired - Lifetime
- 2001-02-09 WO PCT/US2001/004140 patent/WO2001061157A1/en active IP Right Grant
Also Published As
Publication number | Publication date |
---|---|
DE60113384D1 (en) | 2005-10-20 |
AU2001257885A1 (en) | 2001-08-27 |
DE60113384T2 (en) | 2006-06-22 |
WO2001061157A1 (en) | 2001-08-23 |
EP1255916A1 (en) | 2002-11-13 |
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