CA2152716A1 - Connecting rod with stress relief feature - Google Patents
Connecting rod with stress relief featureInfo
- Publication number
- CA2152716A1 CA2152716A1 CA 2152716 CA2152716A CA2152716A1 CA 2152716 A1 CA2152716 A1 CA 2152716A1 CA 2152716 CA2152716 CA 2152716 CA 2152716 A CA2152716 A CA 2152716A CA 2152716 A1 CA2152716 A1 CA 2152716A1
- Authority
- CA
- Canada
- Prior art keywords
- aperture
- connecting rod
- recited
- intermediate portion
- bore
- 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
- 238000000926 separation method Methods 0.000 claims 2
- 210000000707 wrist Anatomy 0.000 abstract description 22
- 238000002485 combustion reaction Methods 0.000 abstract description 3
- 238000000034 method Methods 0.000 description 4
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- 229910052782 aluminium Inorganic materials 0.000 description 3
- 238000004512 die casting Methods 0.000 description 2
- 238000001125 extrusion Methods 0.000 description 2
- 239000003562 lightweight material Substances 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000007373 indentation Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
Landscapes
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
A connecting rod for an internal combustion engine or a compressor. The shank of the connecting rod has a stress relief aperture near the hole which accommodates the wrist pin of the piston. The aperture may be a cylindrical through bore.
Description
2i~27 1~
The invention relates to connecting rods. More particularly, it relates to connecting rods used in internal combustion engines and compressors to connect a crankshaft to a piston.
In internal combustion engines and other machines, connecting rods transmit the reciprocating motion of the pistons to the crankshaft and thereby convert reciprocating motion to rotary motion. Typically, connecting rods have been made by a die-casting process which facilitates providing the shank of the rod with an indented or "I-beam" shape in order to reduce weight without sacrificing strength. To reduce manufacturing costs and achieve further reduction in weight, efforts have been made to produce connecting rod parts by an extrusion process, often from a light weight material such as aluminum and even plastic. The extrusion process produces a connecting rod whose shank is unindented, i.e., it lacks the typical "I-beam" cross-sectional shape.
It has been found that the I-beam shape of the conventional connecting rod diffuses the high stresses to which the shank is subjected at the bottom of the aperture which accepts the wrist pin of the piston (the "wrist pin holen). Because an extruded rod lacks this indented I-beam shape, a severe hoop and tangential stress condition can occur at that location. This stress condition produces high cycle fatigue which causes cracks to propagate down the center line of the shank from the bottom of the wrist pin hole.
Machining the extruded rod to create the I-beam shape would be expensive and could also weaken the rod 215271~
excessively if it were made out of a light weight material such as aluminum.
Accordingly, there is a need for a way to prevent the excessive stress condition which is inexpensive and which does not unduly weaken the rod.
The present invention provides a connecting rod for connecting a piston to a crankshaft, comprising a beam made of one or more components, the beam having lengthwise an elongated intermediate portion between a first end portion and a second end portion, wherein the first end portion includes a first aperture located on a first axis and adapted for connecting the beam to the piston, wherein the second end portion includes a second aperture located on a second axis and adapted for connecting the beam to the crankshaft, wherein the beam includes a third aperture which is located on a third axis nearer to the first aperture than to the second aperture.
In one embodiment of the invention, the intermediate portion of the beam, which lies along a longitudinal axis, has an unindented cross-sectional shape in a plane perpendicular to the longitudinal axis. In another embodiment, the third aperture is a cylindrical through-bore which is located nearer to the first aperture than to the second aperture. Other aspects of the invention relate to sizing and locating the third aperture.
While the invention necessitates little additional manufacturing cost and substantially preserves the strength of the connecting rod, it diffuses the stress to which the rod is subjected at the bottom of the wrist pin `` ' 21527:1~
hole and thereby reduces cracks and failures which result from high cycle fatigue.
These and other features and advantages of the invention will be apparent from the description which follows. The preferred embodiments will be described in reference to the accompanying drawings. These embodiments do not represent the full scope of the invention. Rather, the invention may be employed in other embodiments.
In the drawings:
Figures 1 and 2 are perspective and front elevational views respectively of a connecting rod embodying the present invention;
Figure 3 is an enlarged partial cross-sectional view taken along line 3-3 of Figure 2;
Figure 4 is an enlarged cross-sectional view taken on line 4-4 of Figure 2; and Figure 5 illustrates the indented or I-beam cross-sectional shape of the shank of a typical die cast connecting rod.
Figures 1 and 2 illustrate a connecting rod 10 made of two parts, a forked member 12 and an arcuate cap 14, fastened together by two bolts 16. The assembled connecting rod comprises a beam having a shank 17 ("intermediate portion") between a piston end 18 ("first end portion"), which is adapted for connecting the rod to the wrist pin of a piston (not shown), and a crankshaft end 20 (nsecond end portionn), which is adapted for connecting the beam to the crankshaft. The boundaries of the portions are identified by lines 19. The shank 17 lies along a longitudinal axis 21.
` ~ 21527 tS
~ 4 The piston end 18 includes a knuckle 22 of enlarged width which has an aperture ("first aperture") in the form of a cylindrical through bore 24 ("wrist pin hole"
24) oriented on a first axis 26. The wrist pin hole 24 is designed to accept the wrist pin of a piston (not shown). In some embodiments, a bearing could be inserted in the wrist pin hole 24, but no bearing is included in the embodiment of the drawings herein.
The crankshaft end 20 is generally a rectangular base having an aperture ("second aperture") in the form of a through bore 28 (ncrankpin hole" 28) oriented on second axis 30. The crankpin hole 28 is designed to accommodate a crankpin on the crankshaft of the engine.
As illustrated particularly by Figure 3, the shank 17 has a simple rectangular cross-sectional shape--i.e., it does not have an I-beam cross-sectional shape (such as shown in Figure 5) or any other indented cross-sectional shape which is typical of connecting rods made from a die casting process. As noted above, the unindented cross-sectional shape of shank 17 results in excess stress conditions on the shank 17 at the bottom 32 of the crankpin hole 24. The excessive stress condition is believed to result from the relative lack of compliance of the shank near the bottom 32 of the wrist pin hole 24.
This lack of compliance causes load to accumulate on the surface of crankpin hole 24 near the bottom 32. This loading accumulates both circumferentially and in the direction of first axis 26. It is believed that in conventional connecting rods the indentation (33a in Figure 5) of the shank results in the distribution of these loads downward along the unindented edges of the shank (33b in Figure 5).
As shown in Figures 1, 2 and 4, forked member 12 includes an aperture ("the third aperture") in the form of a stress relief hole 34 which extends through forked member 12 along the third axis 36 and which is located near wrist pin hole 24. The stress relief hole 34 is sized and placed to relieve the local stiffness in the forked member 12, which helps to produce a more uniform stress field at the bottom 32 of the wrist pin hole 24.
The third aperture need not extend completely through the forked member 12. There could be more than one third aperture.
A cylindrical stress relief hole 34 can be manufactured very economically by drilling. A circular shape also appears to be most effective in achieving the desired diffusion of stress. Some other shapes, such as an arched-shaped hole, may increase rather than reduce stress concentration. Centering the stress relief hole widthwise (i.e., along the lengthwise centerline of forked member 12) appears to be more effective than offsetting one or more holes. The appropriate size and location of the stress relief hole 34 depends on the geometry of the piston end 18, particularly on the relative size of the wrist pin hole 24. The stress relief hole 34 needs to be located far enough away from the wrist pin hole 24 to prevent undue variation in the shape of wrist pin hole 24 in operation, which could cause excessive wear. However, the stress relief hole 34 should be near enough to wrist pin hole 24 so that the local flexibility in forked member 12 resulting from ~ Z1~271~
.
stress relief hole 34 can effectively distribute of the stress resulting from the load at the bottom 32 of wrist pin hole 24.
Finite element analysis has been used successfully to size and locate the stress relief hole 34. In an extruded aluminum rod, best results have been obtained when a cylindrical stress relief hole 34 is centered widthwise on the shank and one more of the following relationships pertain: the ratio of the cross-sectional area of the wrist pin hole 24 to the cross-sectional area of the stress relief hole 34 is in the range of 5 to 10;
the ratio of the diameter of the stress relief hole 34 to the width of the shank at the location of stress relief hole 34 is in the range of 0.3 to 0.4; the ratio of (a) the shortest distance from the circumference of stress relief hole 34 to the bottom 32 of wrist pin hole 24 to (b) the shortest distance from the circumference of stress relief hole 34 to the edge of the shank 17 is in the range of 1.0 to 1.6.
In one particular application, the forked member 12 and the cap 14 were extruded from an aluminum alloy 6061.
The overall length of the connecting rod 10 was 160 mm and its thickness (i.e., the dimension along an axis parallel to first axis 26) was 26 mm. The width of the knuckle 22 was 29 mm and the width of shank 17 at its narrowest point was 11 mm. The wrist pin hole 24 had a diameter of 19 mm. It was found that effective stress relief occurred when the stress relief hole 34 had a diameter of 7 mm and its center was located 20 mm from the center of the wrist pin hole 24. The axes 26, 30 and 36 were parallel. The invention is not limited to a 7 1 ~
connecting rod with the foregoing specifications.
Rather, they are given as an example of an embodiment of the invention.
The invention relates to connecting rods. More particularly, it relates to connecting rods used in internal combustion engines and compressors to connect a crankshaft to a piston.
In internal combustion engines and other machines, connecting rods transmit the reciprocating motion of the pistons to the crankshaft and thereby convert reciprocating motion to rotary motion. Typically, connecting rods have been made by a die-casting process which facilitates providing the shank of the rod with an indented or "I-beam" shape in order to reduce weight without sacrificing strength. To reduce manufacturing costs and achieve further reduction in weight, efforts have been made to produce connecting rod parts by an extrusion process, often from a light weight material such as aluminum and even plastic. The extrusion process produces a connecting rod whose shank is unindented, i.e., it lacks the typical "I-beam" cross-sectional shape.
It has been found that the I-beam shape of the conventional connecting rod diffuses the high stresses to which the shank is subjected at the bottom of the aperture which accepts the wrist pin of the piston (the "wrist pin holen). Because an extruded rod lacks this indented I-beam shape, a severe hoop and tangential stress condition can occur at that location. This stress condition produces high cycle fatigue which causes cracks to propagate down the center line of the shank from the bottom of the wrist pin hole.
Machining the extruded rod to create the I-beam shape would be expensive and could also weaken the rod 215271~
excessively if it were made out of a light weight material such as aluminum.
Accordingly, there is a need for a way to prevent the excessive stress condition which is inexpensive and which does not unduly weaken the rod.
The present invention provides a connecting rod for connecting a piston to a crankshaft, comprising a beam made of one or more components, the beam having lengthwise an elongated intermediate portion between a first end portion and a second end portion, wherein the first end portion includes a first aperture located on a first axis and adapted for connecting the beam to the piston, wherein the second end portion includes a second aperture located on a second axis and adapted for connecting the beam to the crankshaft, wherein the beam includes a third aperture which is located on a third axis nearer to the first aperture than to the second aperture.
In one embodiment of the invention, the intermediate portion of the beam, which lies along a longitudinal axis, has an unindented cross-sectional shape in a plane perpendicular to the longitudinal axis. In another embodiment, the third aperture is a cylindrical through-bore which is located nearer to the first aperture than to the second aperture. Other aspects of the invention relate to sizing and locating the third aperture.
While the invention necessitates little additional manufacturing cost and substantially preserves the strength of the connecting rod, it diffuses the stress to which the rod is subjected at the bottom of the wrist pin `` ' 21527:1~
hole and thereby reduces cracks and failures which result from high cycle fatigue.
These and other features and advantages of the invention will be apparent from the description which follows. The preferred embodiments will be described in reference to the accompanying drawings. These embodiments do not represent the full scope of the invention. Rather, the invention may be employed in other embodiments.
In the drawings:
Figures 1 and 2 are perspective and front elevational views respectively of a connecting rod embodying the present invention;
Figure 3 is an enlarged partial cross-sectional view taken along line 3-3 of Figure 2;
Figure 4 is an enlarged cross-sectional view taken on line 4-4 of Figure 2; and Figure 5 illustrates the indented or I-beam cross-sectional shape of the shank of a typical die cast connecting rod.
Figures 1 and 2 illustrate a connecting rod 10 made of two parts, a forked member 12 and an arcuate cap 14, fastened together by two bolts 16. The assembled connecting rod comprises a beam having a shank 17 ("intermediate portion") between a piston end 18 ("first end portion"), which is adapted for connecting the rod to the wrist pin of a piston (not shown), and a crankshaft end 20 (nsecond end portionn), which is adapted for connecting the beam to the crankshaft. The boundaries of the portions are identified by lines 19. The shank 17 lies along a longitudinal axis 21.
` ~ 21527 tS
~ 4 The piston end 18 includes a knuckle 22 of enlarged width which has an aperture ("first aperture") in the form of a cylindrical through bore 24 ("wrist pin hole"
24) oriented on a first axis 26. The wrist pin hole 24 is designed to accept the wrist pin of a piston (not shown). In some embodiments, a bearing could be inserted in the wrist pin hole 24, but no bearing is included in the embodiment of the drawings herein.
The crankshaft end 20 is generally a rectangular base having an aperture ("second aperture") in the form of a through bore 28 (ncrankpin hole" 28) oriented on second axis 30. The crankpin hole 28 is designed to accommodate a crankpin on the crankshaft of the engine.
As illustrated particularly by Figure 3, the shank 17 has a simple rectangular cross-sectional shape--i.e., it does not have an I-beam cross-sectional shape (such as shown in Figure 5) or any other indented cross-sectional shape which is typical of connecting rods made from a die casting process. As noted above, the unindented cross-sectional shape of shank 17 results in excess stress conditions on the shank 17 at the bottom 32 of the crankpin hole 24. The excessive stress condition is believed to result from the relative lack of compliance of the shank near the bottom 32 of the wrist pin hole 24.
This lack of compliance causes load to accumulate on the surface of crankpin hole 24 near the bottom 32. This loading accumulates both circumferentially and in the direction of first axis 26. It is believed that in conventional connecting rods the indentation (33a in Figure 5) of the shank results in the distribution of these loads downward along the unindented edges of the shank (33b in Figure 5).
As shown in Figures 1, 2 and 4, forked member 12 includes an aperture ("the third aperture") in the form of a stress relief hole 34 which extends through forked member 12 along the third axis 36 and which is located near wrist pin hole 24. The stress relief hole 34 is sized and placed to relieve the local stiffness in the forked member 12, which helps to produce a more uniform stress field at the bottom 32 of the wrist pin hole 24.
The third aperture need not extend completely through the forked member 12. There could be more than one third aperture.
A cylindrical stress relief hole 34 can be manufactured very economically by drilling. A circular shape also appears to be most effective in achieving the desired diffusion of stress. Some other shapes, such as an arched-shaped hole, may increase rather than reduce stress concentration. Centering the stress relief hole widthwise (i.e., along the lengthwise centerline of forked member 12) appears to be more effective than offsetting one or more holes. The appropriate size and location of the stress relief hole 34 depends on the geometry of the piston end 18, particularly on the relative size of the wrist pin hole 24. The stress relief hole 34 needs to be located far enough away from the wrist pin hole 24 to prevent undue variation in the shape of wrist pin hole 24 in operation, which could cause excessive wear. However, the stress relief hole 34 should be near enough to wrist pin hole 24 so that the local flexibility in forked member 12 resulting from ~ Z1~271~
.
stress relief hole 34 can effectively distribute of the stress resulting from the load at the bottom 32 of wrist pin hole 24.
Finite element analysis has been used successfully to size and locate the stress relief hole 34. In an extruded aluminum rod, best results have been obtained when a cylindrical stress relief hole 34 is centered widthwise on the shank and one more of the following relationships pertain: the ratio of the cross-sectional area of the wrist pin hole 24 to the cross-sectional area of the stress relief hole 34 is in the range of 5 to 10;
the ratio of the diameter of the stress relief hole 34 to the width of the shank at the location of stress relief hole 34 is in the range of 0.3 to 0.4; the ratio of (a) the shortest distance from the circumference of stress relief hole 34 to the bottom 32 of wrist pin hole 24 to (b) the shortest distance from the circumference of stress relief hole 34 to the edge of the shank 17 is in the range of 1.0 to 1.6.
In one particular application, the forked member 12 and the cap 14 were extruded from an aluminum alloy 6061.
The overall length of the connecting rod 10 was 160 mm and its thickness (i.e., the dimension along an axis parallel to first axis 26) was 26 mm. The width of the knuckle 22 was 29 mm and the width of shank 17 at its narrowest point was 11 mm. The wrist pin hole 24 had a diameter of 19 mm. It was found that effective stress relief occurred when the stress relief hole 34 had a diameter of 7 mm and its center was located 20 mm from the center of the wrist pin hole 24. The axes 26, 30 and 36 were parallel. The invention is not limited to a 7 1 ~
connecting rod with the foregoing specifications.
Rather, they are given as an example of an embodiment of the invention.
Claims (17)
1. A connecting rod for connecting a piston to a crankshaft, comprising:
(a) a beam made of one or more components, the beam having lengthwise an elongated intermediate portion between a first end portion and a second end portion;
(b) wherein the first end portion includes a first aperture located on a first axis and adapted for connecting the beam to the piston;
(c) wherein the second end portion includes a second aperture located on a second axis and adapted for connecting the beam to the crankshaft; and (d) wherein the beam includes a third aperture located on a third axis nearer to the first aperture than to the second aperture.
(a) a beam made of one or more components, the beam having lengthwise an elongated intermediate portion between a first end portion and a second end portion;
(b) wherein the first end portion includes a first aperture located on a first axis and adapted for connecting the beam to the piston;
(c) wherein the second end portion includes a second aperture located on a second axis and adapted for connecting the beam to the crankshaft; and (d) wherein the beam includes a third aperture located on a third axis nearer to the first aperture than to the second aperture.
2. A connecting rod as recited in claim 1, in which the third aperture is sized and located so that in operation the stress on the beam at the first aperture is diffused, the shape of the first aperture is preserved and the rigidity of the beam is maintained.
3. A connecting rod as recited in claim 1, in which the separation between the third aperture and the first aperture is sufficient, but not greater than necessary, to preserve the shape of the first aperture during operation.
4. A connecting rod as recited in claim 1, in which the third aperture is centrally located widthwise.
5. A connecting rod as recited in claim 1, in which the third aperture is a cylindrical through bore and the first aperture and the third aperture have a first cross-sectional area and a third cross-sectional area respectively, the ratio of the first cross-sectional area to the third cross-sectional area being in the range of 5 to 10 inclusive.
6. The connecting rod as recited in claim 1, in which the third aperture is a cylindrical through bore which is centered widthwise on the intermediate portion of the beam, the through bore being sized so that the ratio of its diameter to the width of intermediate portion at the location of the third aperture is in the range of 0.3 to 0.4 inclusive.
7. A connecting rod as recited in claim 1, in which the third aperture is a cylindrical through bore which is centered widthwise on the intermediate portion of the beam, the through bore being located so that the ratio of (a) the shortest distance from the periphery of the third aperture to the periphery of the first aperture to (b) the shortest widthwise distance from the periphery of the third aperture to an edge of intermediate portion of the beam is in the range of 1.0 to 1.6 inclusive.
8. A connecting rod for connecting a piston to a crankshaft, comprising:
(a) a beam made of one or more components, the beam having lengthwise an elongated intermediate portion between a first end portion and a second end portion;
(b) wherein the first end portion includes a first aperture located on a first axis and adapted for connecting the beam to the piston;
(c) wherein the second end portion includes a second aperture located on a second axis and adapted for connecting the beam to the crankshaft;
(d) wherein the intermediate portion lies along a longitudinal axis and wherein the intermediate portion of the beam has an unindented cross-sectional shape in a plane perpendicular to the longitudinal axis; and (e) wherein the beam includes a third aperture located on a third axis and located nearer to the first aperture than to the second aperture.
(a) a beam made of one or more components, the beam having lengthwise an elongated intermediate portion between a first end portion and a second end portion;
(b) wherein the first end portion includes a first aperture located on a first axis and adapted for connecting the beam to the piston;
(c) wherein the second end portion includes a second aperture located on a second axis and adapted for connecting the beam to the crankshaft;
(d) wherein the intermediate portion lies along a longitudinal axis and wherein the intermediate portion of the beam has an unindented cross-sectional shape in a plane perpendicular to the longitudinal axis; and (e) wherein the beam includes a third aperture located on a third axis and located nearer to the first aperture than to the second aperture.
9. A connecting rod as recited in claim 8, in which the third aperture is sized and located so that in operation the stress on the beam at the first aperture is diffused, the shape of the first aperture is preserved and the rigidity of the beam is maintained.
10. A connecting rod as recited in claim 8, in which the separation between the third aperture and the first aperture is sufficient, but not greater than necessary, to preserve the shape of the first aperture during operation.
11. A connecting rod as recited in claim 8, in which the first and third apertures are cylindrical through bores having a first cross-sectional area and a third cross-sectional area respectively, the ratio of the first cross-sectional area to the third cross-sectional area being in the range of 5 to 10 inclusive.
12. A connecting rod as recited in claim 8, in which the third aperture is a cylindrical through bore which is centered widthwise on the intermediate portion of the beam, the through bore being sized so that the ratio of its diameter to the width of intermediate portion at the location of the third aperture is in the range of 0.3 to 0.4 inclusive.
13. A connecting rod as recited in claim 8, in which the third aperture is a cylindrical through bore which is centered widthwise on the intermediate portion of the beam, the through bore being located so that the ratio of (a) the shortest distance from the periphery of the third aperture to the periphery of the first aperture to (b) the shortest widthwise distance from the periphery of the third aperture to an edge of intermediate portion of the beam is in the range of 1.0 to 1.6 inclusive.
14. A connecting rod as recited in claim 8, in which the third aperture is a through bore.
15. A connecting rod as recited in claim 14, in which the third aperture has a cylindrical shape.
16. A connecting rod as recited in claim 15, in which the third aperture is centrally located widthwise.
17. A connecting rod as recited in claim 8, in which the first, second and third axes are parallel.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US26764094A | 1994-06-28 | 1994-06-28 | |
| US267,640 | 1994-06-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2152716A1 true CA2152716A1 (en) | 1995-12-29 |
Family
ID=23019617
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2152716 Abandoned CA2152716A1 (en) | 1994-06-28 | 1995-06-27 | Connecting rod with stress relief feature |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2152716A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113833740A (en) * | 2021-09-17 | 2021-12-24 | 李志强 | Novel process for machining engine connecting rod |
-
1995
- 1995-06-27 CA CA 2152716 patent/CA2152716A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113833740A (en) * | 2021-09-17 | 2021-12-24 | 李志强 | Novel process for machining engine connecting rod |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Dead |