US20170343096A1 - Rotatable assembly including a coupling interface - Google Patents
Rotatable assembly including a coupling interface Download PDFInfo
- Publication number
- US20170343096A1 US20170343096A1 US15/165,604 US201615165604A US2017343096A1 US 20170343096 A1 US20170343096 A1 US 20170343096A1 US 201615165604 A US201615165604 A US 201615165604A US 2017343096 A1 US2017343096 A1 US 2017343096A1
- Authority
- US
- United States
- Prior art keywords
- rotatable component
- rotatable
- recess
- recesses
- protrusions
- 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.)
- Granted
Links
- 230000008878 coupling Effects 0.000 title claims description 20
- 238000010168 coupling process Methods 0.000 title claims description 20
- 238000005859 coupling reaction Methods 0.000 title claims description 20
- 230000007423 decrease Effects 0.000 claims description 17
- 230000005540 biological transmission Effects 0.000 claims description 5
- 230000000284 resting effect Effects 0.000 claims description 3
- 238000003754 machining Methods 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000002708 enhancing effect Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000000843 powder Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 1
- 239000012255 powdered metal Substances 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/0018—Shaft assemblies for gearings
- F16H57/0025—Shaft assemblies for gearings with gearing elements rigidly connected to a shaft, e.g. securing gears or pulleys by specially adapted splines, keys or methods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D1/101—Quick-acting couplings in which the parts are connected by simply bringing them together axially without axial retaining means rotating with the coupling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/06—Crankshafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/30—Chain-wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/32—Friction members
- F16H55/52—Pulleys or friction discs of adjustable construction
- F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
- F16H55/566—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable only adjustable when pulley is stationary
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/12—Arrangements for adjusting or for taking-up backlash not provided for elsewhere
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
- F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
- F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/30—Chain-wheels
- F16H2055/306—Chain-wheels with means providing resilience or vibration damping in chain sprocket wheels
Definitions
- the present disclosure relates to a rotatable assembly, such as a crankshaft assembly, including a coupling interface.
- crankshafts converts reciprocating linear movement of a piston into rotational movement about an axis to provide torque to propel a vehicle, such as but not limited to a train, a boat, a plane, or an automobile, or to drive any other apparatus powered by the engine.
- the present disclosure relates to a rotatable assembly, such as a crankshaft assembly, including a coupling interface.
- the presently disclosed coupling interface can be mass-produced and manufactured in a cost-effective manner.
- This coupling interface may be incorporated into automobiles, agricultural equipment, home appliance, etc.
- the coupling interface includes recesses and protrusions configured to mate with each other in order to couple different components of the rotatable assembly.
- a first rotatable component of a rotatable assembly includes a first body and defines a plurality of recesses extending into the first body.
- a second rotatable component of the rotatable assembly includes a second body and defines a plurality of protrusions extending from the second body.
- the protrusions are disposed inside the recesses to allow the second rotatable component to rotate in unison with the first rotatable component.
- the recesses can be formed using a machining or forming process, and the protrusions can be formed by using powder metal manufacturing processes, by attaching metal dowels to the second body, or by directly machining the second rotatable component.
- FIG. 1 is a schematic perspective, fragmentary view of a rotatable assembly including a post with circumferentially spaced recesses.
- FIG. 2 is a schematic perspective, fragmentary view of the rotatable assembly shown in FIG. 1 , illustrating a sprocket disposed over the post.
- FIG. 3 is a schematic, cross-sectional front view of the rotatable assembly shown in FIG. 2 .
- FIG. 4 is a schematic perspective, fragmentary view of the sprocket, illustrating an inner sprocket surface and protrusions of the sprocket.
- FIG. 5 is a schematic, fragmentary front view of a recess of the rotatable assembly shown in FIG. 1 .
- FIG. 6 is a schematic, fragmentary side view of a recess of the rotatable assembly shown in FIG. 1 .
- FIG. 7 is a schematic, fragmentary front view of a protrusion of the sprocket shown in FIG. 4 .
- FIG. 8 is a schematic, fragmentary side view of a protrusion of the sprocket shown in FIG. 4 ;
- FIG. 9 is a schematic, fragmentary top view of inner view of the sprocket shown in FIG. 4 , illustrating the protrusions.
- FIG. 10 is a schematic, fragmentary view of the sprocket, illustrating an inner sprocket surface and curved protrusions of the sprocket.
- FIG. 11 is a schematic, enlarged fragmentary view of the rotatable assembly shown in FIG. 2 , taken around area 11 in FIG. 3 .
- a rotatable assembly 100 is configured to rotate about a longitudinal axis X.
- the rotatable assembly 100 includes a coupling interface 101 for connecting a first rotatable component 102 to a second rotatable component 104 .
- the coupling interface 101 allows the first rotatable component 102 and the second rotatable component 104 to rotate in unison about the longitudinal axis X.
- the coupling interface 101 does not allow relative rotation between the first rotatable component 102 and the second rotatable 104 component across the coupling interface 101 .
- the coupling interface 101 allows torque transmission between the first rotatable component 102 and the second rotatable component 104 . In other words, due to the coupling interface 101 , torque can be transmitted between the first rotatable component 102 and the second rotatable component 104 . This torque transmission does not require a clamp load.
- the rotatable assembly 100 may be, for example, configured as a crankshaft assembly 106 .
- the first rotatable component 102 is configured as a shaft 108 ( FIG. 1 )
- the second rotatable component 104 is configured as a sprocket 110 ( FIG. 2 ).
- the crankshaft assembly 106 includes a plurality of counterweights 112 coupled to the shaft 108 .
- the first rotatable component 102 and the second rotatable component 104 both extend along the longitudinal axis X. Accordingly, the first rotatable component 102 and the second rotatable component 104 can rotate about the longitudinal axis X and are coaxial with respect to each other.
- the first rotatable component 102 includes a first body 114
- the second rotatable component 104 includes a second body 118 .
- the first body 114 is configured as a post 116
- the second body 118 is configured as a ring 120
- the sprocket 110 includes a plurality of teeth 122 coupled to the ring 120 .
- the teeth 122 are annularly arranged about the ring 120 .
- the first rotatable component 102 defines a plurality of recesses 124 extending into the first body 114 .
- the recesses 124 are part of the coupling interface and can be manufactured using grinding processes or any other suitable machining process.
- the first body 114 defines circumferential outer body surface 126 and a plurality of concave surfaces 128 each defining one of the recesses 124 .
- the concave surfaces 128 may have a substantially semi-elliptical cross-sectional shape in order to facilitate the connection between the first rotatable component 102 and the second rotatable component 104 .
- the recesses 124 may have a substantially scalloped shaped configuration.
- the substantially scalloped shaped configuration of the recesses 124 enhances the connection between the first rotatable component 102 and the second rotatable component 104 while allowing the second rotatable component 104 to easily slide over the first rotatable component 102 for assembly.
- the first body 114 defines three concave surfaces 128 circumferentially spaced apart from one another. However, it is contemplated that the first body 114 may define any plurality of concave surfaces 128 and recesses 124 .
- the first rotatable component 102 defines three recesses 124 circumferentially spaced apart from one another in order to ensure a proper alignment and connection with the second rotatable component 104 especially when the rotatable assembly 100 rotates about the longitudinal axis X.
- the second rotatable component 104 defines an inner body opening 130 extending through the second body 118 .
- the body opening 130 is configured, shaped, and sized to receive the first body 114 .
- the second body 118 has a circumferential inner surface 132 defining the body opening 130 .
- the second body 118 includes three protrusions 134 extending from the circumferential inner surface 132 toward a center C of the body opening 130 .
- the protrusions 134 may be formed by machining (e.g., grinding) the second rotatable component 104 .
- the protrusions 134 may be formed in powdered metal in order to minimize cost.
- each protrusion 134 is configured, shaped, and sized to mate with one of the recesses 124 of the first rotatable component 102 .
- each of the protrusions 134 mates with one of the recesses 124 , such that the first rotatable component 102 is prevented from rotating relative to the second rotatable component 104 while allowing the second rotatable component 104 to be slid over the first rotatable component 102 .
- the recess 124 and the protrusion 134 jointly define the coupling interface 101 .
- the rotatable assembly 100 may include one or more protrusions 134 and one or more recesses 124 .
- the second body 118 includes convex surfaces 136 extending from the circumferential inner surface 132 .
- the convex surfaces 136 may also be referred as raised surfaces and can be formed by using powder metal manufacturing processes, by attaching dowels to the second body, or by directly machining the second rotatable component 104 .
- the convex surfaces 136 at least partially define the protrusions 134 and are therefore circumferentially spaced apart from one another.
- the convex surfaces 136 may have a substantially semi-elliptical cross-sectional shape in order to facilitate the connection between the first rotatable component 102 and the second rotatable component 104 when the protrusions 134 are disposed inside the recesses 124 .
- the protrusions 134 may have a substantially scalloped shaped configuration in order to mate with the recesses 124 having the substantially scalloped shaped configuration.
- the substantially scalloped shaped configuration of the recesses 124 and the protrusions 134 allows the second body 118 to be slid over the first body 114 during assembly while rotatably coupling the first rotatable component 102 to the second rotatable component 104 .
- the convex surfaces 136 may have other suitable shapes.
- the convex surfaces 136 and the concave surfaces 128 may have variable radius.
- the particular radius of the convex surfaces 136 and the concave surfaces 128 may be determined based on the maximum allowable stress and the accuracy required.
- the radius and form of the protrusion 134 and recess 124 can be adjusted as desired to limit the contact stresses appropriate for the materials being considered.
- the convex surfaces 136 are in direct contact with the concave surfaces 128 when the protrusions 134 are disposed inside of the recesses 124 , thereby enhancing the connection between the first rotatable component 102 and the second rotatable component 104 .
- the second rotatable component 104 surrounds the first rotatable component 102 , such that the protrusions 134 are in direct contact with the concave surfaces 128 .
- the second rotatable component 104 includes three protrusions 134 circumferentially spaced apart from one another in order to ensure a proper alignment and connection with the first rotatable component 102 especially when the rotatable assembly 100 rotates about the longitudinal axis X.
- the second rotatable component 104 may include any plurality of protrusions 134 .
- the recesses 124 are not equally spaced from one another, and the corresponding protrusions 134 are not equally spaced from one another such that the first rotatable component 102 and the second rotatable component 104 can be assembled only a single orientation for error proofing. If error proofing orientation is not required, then the spacing may be equal.
- the recesses 124 include a first recess 124 a, a second recess 124 b, and a third recess 124 c
- the protrusions 134 include a first protrusion 134 a, a second protrusion 134 b, and a third protrusion 134 c.
- the angle between the first recess 124 a and the second recess 124 b is defined by a first angle ⁇ .
- the first angle ⁇ also represents the angle between the first protrusion 134 a and the second protrusion 134 b.
- the angle between the second recess 124 b and the third recess 124 c is defined by a second angle ⁇ .
- the second angle ⁇ also represents the angle between the second protrusion 134 b and the third protrusion 134 c.
- the angle between the third recess 124 c and the first recess 124 a is defined by a third angle ⁇ .
- the third angle ⁇ also represents the angle between the third protrusion 134 c and the first protrusion 134 a.
- At least two of the first angle ⁇ , the second angle ⁇ , and the third angle ⁇ are different to ensure that the first rotatable component 102 is properly aligned with the second rotatable component 104 during assembly.
- the first angle ⁇ and the second angle ⁇ may be equal to each other but each may be different from the third angle ⁇ . It is contemplated, the first angle ⁇ , the second angle ⁇ , and the third angle ⁇ may all be different from each other in order to further minimize the risk of misalignment between the first rotatable component 102 and the second rotatable component 104 .
- the radius of the protrusion 134 is slightly smaller than the radius of the recess 124 .
- the protrusion 134 is in conformal contact with the recess 124 to allow the coupling interface 101 to carry torque through the rotatable assembly 100 .
- the protrusion 134 is in tapered, conformal contact with the recess 124 to create a joint with minimized runout of the second rotatable component 104 from the first rotatable component 102 . Additional protrusions 134 and recesses 124 decrease the runout.
- the tapered, conformal contact between the protrusion 134 and the recess 124 creates a unique lateral final resting position when the second rotatable component 104 is slide onto the first rotatable component 102 .
- each recess 124 has a recess height RH that is defined as the maximum distance from the concave surfaces 128 to the circumferential inner surface 132 .
- each protrusion 134 may have a tapered configuration in order to facilitate sliding the second rotatable component 104 over the first rotatable component 102 .
- the protrusion height PH continuously decreases in an axial direction A, which is a direction from the outer post end 138 toward the inner post end 140 .
- the recess height RH of each recess 124 decreases exponentially in the axial direction A in order to facilitate sliding the second rotatable component 104 over the first rotatable component 102 .
- each recess 124 is also tapered such that the recess width RW ( FIG. 1 ) continuously decreases in the axial direction A.
- the recess width RW may decrease exponentially in the axial direction in order to facilitate sliding the second rotatable component 104 over the first rotatable component 102 .
- the recess height RH of each recess 124 may experience a quadratic or cubic spline decrease in the axial direction A.
- each protrusion 134 has a protrusion height PH that is defined as the distance from the convex surface 136 to a circumference CR ( FIG. 7 ) of the circumferential inner surface 132 .
- each protrusion 134 may have a tapered configuration in order to facilitate sliding the second rotatable component 104 over the first rotatable component 102 .
- the protrusion height PH continuously decreases in the axial direction A.
- the protrusion height PH of each protrusion 134 decreases exponentially in the axial direction A in order to facilitate sliding the second rotatable component 104 over the first rotatable component 102 .
- Each protrusion 134 is also tapered such that the protrusion width PW ( FIG. 9 ) continuously decreases in the axial direction A.
- the protrusion width PW may decrease exponentially in the axial direction A in order to facilitate sliding the second rotatable component 104 over the first rotatable component 102 .
- the protrusion width PW may experience a quadratic or cubic spline decrease in the axial direction A.
- the protrusions 134 may have a curved configuration about the longitudinal axis X ( FIG. 1 ) instead of being linear.
- the recesses 124 also have a curved configuration in order to mate with the protrusions 134 , thereby enhancing the connection between the first rotatable component 102 and the second rotatable component 104 .
- the spiral can be oriented to provide a self-tightening impact as a result of the direction of rotation of the part while in service.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Pivots And Pivotal Connections (AREA)
- Transmission Devices (AREA)
- Seats For Vehicles (AREA)
Abstract
Description
- The present disclosure relates to a rotatable assembly, such as a crankshaft assembly, including a coupling interface.
- Mechanical devices, such as internal combustion engines, include rotatable components for different purposes. For instance, internal combustion engines include at least one crankshaft. A crankshaft converts reciprocating linear movement of a piston into rotational movement about an axis to provide torque to propel a vehicle, such as but not limited to a train, a boat, a plane, or an automobile, or to drive any other apparatus powered by the engine.
- The present disclosure relates to a rotatable assembly, such as a crankshaft assembly, including a coupling interface. The presently disclosed coupling interface can be mass-produced and manufactured in a cost-effective manner. This coupling interface may be incorporated into automobiles, agricultural equipment, home appliance, etc. In certain embodiments, the coupling interface includes recesses and protrusions configured to mate with each other in order to couple different components of the rotatable assembly. As a non-limiting example, a first rotatable component of a rotatable assembly includes a first body and defines a plurality of recesses extending into the first body. A second rotatable component of the rotatable assembly includes a second body and defines a plurality of protrusions extending from the second body. The protrusions are disposed inside the recesses to allow the second rotatable component to rotate in unison with the first rotatable component. The recesses can be formed using a machining or forming process, and the protrusions can be formed by using powder metal manufacturing processes, by attaching metal dowels to the second body, or by directly machining the second rotatable component.
- The above features and advantages and other features and advantages of the present teachings are readily apparent from the following detailed description of the best modes for carrying out the teachings when taken in connection with the accompanying drawings.
-
FIG. 1 is a schematic perspective, fragmentary view of a rotatable assembly including a post with circumferentially spaced recesses. -
FIG. 2 is a schematic perspective, fragmentary view of the rotatable assembly shown inFIG. 1 , illustrating a sprocket disposed over the post. -
FIG. 3 is a schematic, cross-sectional front view of the rotatable assembly shown inFIG. 2 . -
FIG. 4 is a schematic perspective, fragmentary view of the sprocket, illustrating an inner sprocket surface and protrusions of the sprocket. -
FIG. 5 is a schematic, fragmentary front view of a recess of the rotatable assembly shown inFIG. 1 . -
FIG. 6 is a schematic, fragmentary side view of a recess of the rotatable assembly shown inFIG. 1 . -
FIG. 7 is a schematic, fragmentary front view of a protrusion of the sprocket shown inFIG. 4 . -
FIG. 8 is a schematic, fragmentary side view of a protrusion of the sprocket shown inFIG. 4 ; -
FIG. 9 is a schematic, fragmentary top view of inner view of the sprocket shown inFIG. 4 , illustrating the protrusions; and -
FIG. 10 is a schematic, fragmentary view of the sprocket, illustrating an inner sprocket surface and curved protrusions of the sprocket. -
FIG. 11 is a schematic, enlarged fragmentary view of the rotatable assembly shown inFIG. 2 , taken aroundarea 11 inFIG. 3 . - Referring to the drawings, wherein like reference numbers correspond to like or similar components throughout the several figures, and beginning with
FIGS. 1-4 , arotatable assembly 100 is configured to rotate about a longitudinal axis X. In the depicted embodiment, therotatable assembly 100 includes acoupling interface 101 for connecting a firstrotatable component 102 to a secondrotatable component 104. Thecoupling interface 101 allows the firstrotatable component 102 and the secondrotatable component 104 to rotate in unison about the longitudinal axis X. However, thecoupling interface 101 does not allow relative rotation between the firstrotatable component 102 and the second rotatable 104 component across thecoupling interface 101. Thecoupling interface 101 allows torque transmission between the firstrotatable component 102 and the secondrotatable component 104. In other words, due to thecoupling interface 101, torque can be transmitted between the firstrotatable component 102 and the secondrotatable component 104. This torque transmission does not require a clamp load. - The
rotatable assembly 100 may be, for example, configured as acrankshaft assembly 106. In such a case, the firstrotatable component 102 is configured as a shaft 108 (FIG. 1 ), and the secondrotatable component 104 is configured as a sprocket 110 (FIG. 2 ). In addition to thesprocket 110 and theshaft 108, thecrankshaft assembly 106 includes a plurality ofcounterweights 112 coupled to theshaft 108. Regardless of their respective configuration, the firstrotatable component 102 and the secondrotatable component 104 both extend along the longitudinal axis X. Accordingly, the firstrotatable component 102 and the secondrotatable component 104 can rotate about the longitudinal axis X and are coaxial with respect to each other. - The first
rotatable component 102 includes afirst body 114, and the secondrotatable component 104 includes asecond body 118. In thecrankshaft assembly 106, thefirst body 114 is configured as apost 116, and thesecond body 118 is configured as aring 120. In addition to thering 120, thesprocket 110 includes a plurality ofteeth 122 coupled to thering 120. Specifically, theteeth 122 are annularly arranged about thering 120. - The first
rotatable component 102 defines a plurality ofrecesses 124 extending into thefirst body 114. Therecesses 124 are part of the coupling interface and can be manufactured using grinding processes or any other suitable machining process. Specifically, thefirst body 114 defines circumferentialouter body surface 126 and a plurality ofconcave surfaces 128 each defining one of therecesses 124. Theconcave surfaces 128 may have a substantially semi-elliptical cross-sectional shape in order to facilitate the connection between the firstrotatable component 102 and the secondrotatable component 104. As such, therecesses 124 may have a substantially scalloped shaped configuration. The substantially scalloped shaped configuration of therecesses 124 enhances the connection between the firstrotatable component 102 and the secondrotatable component 104 while allowing the secondrotatable component 104 to easily slide over the firstrotatable component 102 for assembly. As a non-limiting example, thefirst body 114 defines threeconcave surfaces 128 circumferentially spaced apart from one another. However, it is contemplated that thefirst body 114 may define any plurality ofconcave surfaces 128 andrecesses 124. In the depicted non-limiting example, the firstrotatable component 102 defines threerecesses 124 circumferentially spaced apart from one another in order to ensure a proper alignment and connection with the secondrotatable component 104 especially when therotatable assembly 100 rotates about the longitudinal axis X. - The second
rotatable component 104 defines an inner body opening 130 extending through thesecond body 118. The body opening 130 is configured, shaped, and sized to receive thefirst body 114. In particular, thesecond body 118 has a circumferentialinner surface 132 defining the body opening 130. In the example, thesecond body 118 includes threeprotrusions 134 extending from the circumferentialinner surface 132 toward a center C of the body opening 130. Theprotrusions 134 may be formed by machining (e.g., grinding) the secondrotatable component 104. Alternatively, theprotrusions 134 may be formed in powdered metal in order to minimize cost. Irrespective of the manufacturing process employed, eachprotrusion 134 is configured, shaped, and sized to mate with one of therecesses 124 of the firstrotatable component 102. In other words, each of theprotrusions 134 mates with one of therecesses 124, such that the firstrotatable component 102 is prevented from rotating relative to the secondrotatable component 104 while allowing the secondrotatable component 104 to be slid over the firstrotatable component 102. Therecess 124 and theprotrusion 134 jointly define thecoupling interface 101. The tapered, conformal contact between theprotrusion 134 and therecess 124 creates a unique lateral final resting position when the secondrotatable component 104 is slide onto the firstrotatable component 102. Thus, when the firstrotatable component 102 and the secondrotatable component 104 are combined, the lateral relationship between the firstrotatable component 102 and the secondrotatable component 104 fixed and defined by their geometry. When used provide defined lateral alignment without requiring limited radial alignment or torque transmission, therotatable assembly 100 may include one ormore protrusions 134 and one or more recesses 124. - Accordingly, when the
protrusions 134 are disposed inside of therecesses 124, the firstrotatable component 102 is coupled to the secondrotatable component 104, thereby allowing the secondrotatable component 104 to rotate in unison with the firstrotatable component 102. Thesecond body 118 includesconvex surfaces 136 extending from the circumferentialinner surface 132. Theconvex surfaces 136 may also be referred as raised surfaces and can be formed by using powder metal manufacturing processes, by attaching dowels to the second body, or by directly machining the secondrotatable component 104. Moreover, theconvex surfaces 136 at least partially define theprotrusions 134 and are therefore circumferentially spaced apart from one another. Theconvex surfaces 136 may have a substantially semi-elliptical cross-sectional shape in order to facilitate the connection between the firstrotatable component 102 and the secondrotatable component 104 when theprotrusions 134 are disposed inside therecesses 124. As such, theprotrusions 134 may have a substantially scalloped shaped configuration in order to mate with therecesses 124 having the substantially scalloped shaped configuration. The substantially scalloped shaped configuration of therecesses 124 and theprotrusions 134 allows thesecond body 118 to be slid over thefirst body 114 during assembly while rotatably coupling the firstrotatable component 102 to the secondrotatable component 104. It is contemplated that theconvex surfaces 136 may have other suitable shapes. As non-limiting examples, theconvex surfaces 136 and theconcave surfaces 128 may have variable radius. The particular radius of theconvex surfaces 136 and theconcave surfaces 128 may be determined based on the maximum allowable stress and the accuracy required. In summary, the radius and form of theprotrusion 134 andrecess 124 can be adjusted as desired to limit the contact stresses appropriate for the materials being considered. Regardless of its particular shape, theconvex surfaces 136 are in direct contact with theconcave surfaces 128 when theprotrusions 134 are disposed inside of therecesses 124, thereby enhancing the connection between the firstrotatable component 102 and the secondrotatable component 104. The secondrotatable component 104 surrounds the firstrotatable component 102, such that theprotrusions 134 are in direct contact with the concave surfaces 128. As a non-limiting example, the secondrotatable component 104 includes threeprotrusions 134 circumferentially spaced apart from one another in order to ensure a proper alignment and connection with the firstrotatable component 102 especially when therotatable assembly 100 rotates about the longitudinal axis X. However, it is contemplated that the secondrotatable component 104 may include any plurality ofprotrusions 134. - With specific reference to
FIG. 3 , therecesses 124 are not equally spaced from one another, and the correspondingprotrusions 134 are not equally spaced from one another such that the firstrotatable component 102 and the secondrotatable component 104 can be assembled only a single orientation for error proofing. If error proofing orientation is not required, then the spacing may be equal. In the depicted embodiment, for example, therecesses 124 include afirst recess 124 a, asecond recess 124 b, and athird recess 124 c, and theprotrusions 134 include afirst protrusion 134 a, asecond protrusion 134 b, and athird protrusion 134 c. The angle between thefirst recess 124 a and thesecond recess 124 b is defined by a first angle α. The first angle α also represents the angle between thefirst protrusion 134 a and thesecond protrusion 134 b. The angle between thesecond recess 124 b and thethird recess 124 c is defined by a second angle β. The second angle β also represents the angle between thesecond protrusion 134 b and thethird protrusion 134 c. The angle between thethird recess 124 c and thefirst recess 124 a is defined by a third angle γ. The third angle γ also represents the angle between thethird protrusion 134 c and thefirst protrusion 134 a. At least two of the first angle α, the second angle β, and the third angle γ are different to ensure that the firstrotatable component 102 is properly aligned with the secondrotatable component 104 during assembly. For example, the first angle α and the second angle β may be equal to each other but each may be different from the third angle γ. It is contemplated, the first angle α, the second angle β, and the third angle γ may all be different from each other in order to further minimize the risk of misalignment between the firstrotatable component 102 and the secondrotatable component 104. - As shown in
FIG. 11 , the radius of theprotrusion 134 is slightly smaller than the radius of therecess 124. As such, theprotrusion 134 is in conformal contact with therecess 124 to allow thecoupling interface 101 to carry torque through therotatable assembly 100. Theprotrusion 134 is in tapered, conformal contact with therecess 124 to create a joint with minimized runout of the secondrotatable component 104 from the firstrotatable component 102.Additional protrusions 134 and recesses 124 decrease the runout. The tapered, conformal contact between theprotrusion 134 and therecess 124 creates a unique lateral final resting position when the secondrotatable component 104 is slide onto the firstrotatable component 102. - With reference to
FIGS. 1, 5, and 6 , eachrecess 124 has a recess height RH that is defined as the maximum distance from theconcave surfaces 128 to the circumferentialinner surface 132. Further, eachprotrusion 134 may have a tapered configuration in order to facilitate sliding the secondrotatable component 104 over the firstrotatable component 102. In particular, the protrusion height PH continuously decreases in an axial direction A, which is a direction from theouter post end 138 toward theinner post end 140. As a non-limiting example, the recess height RH of eachrecess 124 decreases exponentially in the axial direction A in order to facilitate sliding the secondrotatable component 104 over the firstrotatable component 102. In the present disclosure, the term “exponentially” means that the rate of change must be expressed using exponents. Eachrecess 124 is also tapered such that the recess width RW (FIG. 1 ) continuously decreases in the axial direction A. The recess width RW may decrease exponentially in the axial direction in order to facilitate sliding the secondrotatable component 104 over the firstrotatable component 102. In other non-limiting examples, the recess height RH of eachrecess 124 may experience a quadratic or cubic spline decrease in the axial direction A. - With reference to
FIGS. 4, 7, 8, and 9 , eachprotrusion 134 has a protrusion height PH that is defined as the distance from theconvex surface 136 to a circumference CR (FIG. 7 ) of the circumferentialinner surface 132. Further, eachprotrusion 134 may have a tapered configuration in order to facilitate sliding the secondrotatable component 104 over the firstrotatable component 102. In particular, the protrusion height PH continuously decreases in the axial direction A. In the depicted embodiment, the protrusion height PH of eachprotrusion 134 decreases exponentially in the axial direction A in order to facilitate sliding the secondrotatable component 104 over the firstrotatable component 102. Eachprotrusion 134 is also tapered such that the protrusion width PW (FIG. 9 ) continuously decreases in the axial direction A. As a non-limiting example, the protrusion width PW may decrease exponentially in the axial direction A in order to facilitate sliding the secondrotatable component 104 over the firstrotatable component 102. In other non-limiting examples, the protrusion width PW may experience a quadratic or cubic spline decrease in the axial direction A. - With reference to
FIG. 10 , theprotrusions 134 may have a curved configuration about the longitudinal axis X (FIG. 1 ) instead of being linear. In this embodiment, therecesses 124 also have a curved configuration in order to mate with theprotrusions 134, thereby enhancing the connection between the firstrotatable component 102 and the secondrotatable component 104. The spiral can be oriented to provide a self-tightening impact as a result of the direction of rotation of the part while in service. - While the best modes for carrying out the teachings have been described in detail, those familiar with the art to which this disclosure relates will recognize various alternative designs and embodiments for practicing the teachings within the scope of the appended claims. The rotatable assembly illustratively disclosed herein may be suitably practiced in the absence of any element which is not specifically disclosed herein.
Claims (12)
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/165,604 US9845861B1 (en) | 2016-05-26 | 2016-05-26 | Rotatable assembly including a coupling interface |
CN201710321013.2A CN107435687B (en) | 2016-05-26 | 2017-05-09 | Rotatable assembly comprising a coupling interface |
DE102017111494.7A DE102017111494A1 (en) | 2016-05-26 | 2017-05-25 | A ROTATABLE ARRANGEMENT WITH A COUPLING INTERFACE |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/165,604 US9845861B1 (en) | 2016-05-26 | 2016-05-26 | Rotatable assembly including a coupling interface |
Publications (2)
Publication Number | Publication Date |
---|---|
US20170343096A1 true US20170343096A1 (en) | 2017-11-30 |
US9845861B1 US9845861B1 (en) | 2017-12-19 |
Family
ID=60269410
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US15/165,604 Expired - Fee Related US9845861B1 (en) | 2016-05-26 | 2016-05-26 | Rotatable assembly including a coupling interface |
Country Status (3)
Country | Link |
---|---|
US (1) | US9845861B1 (en) |
CN (1) | CN107435687B (en) |
DE (1) | DE102017111494A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20150057784A (en) * | 2013-11-20 | 2015-05-28 | 엘지이노텍 주식회사 | Belt driven starter generator |
WO2019187116A1 (en) * | 2018-03-30 | 2019-10-03 | 本田技研工業株式会社 | Engine |
DE102018125617A1 (en) * | 2018-10-16 | 2020-04-16 | Bayerische Motoren Werke Aktiengesellschaft | crankshaft |
Family Cites Families (171)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2733943A (en) * | 1956-02-07 | nater | ||
US177337A (en) * | 1876-05-16 | Improvement in coupling-boxes for rolls | ||
US611556A (en) * | 1898-09-27 | Filling-piece for cams | ||
US581476A (en) * | 1897-04-27 | Shaft for stamp-mills | ||
US183426A (en) * | 1876-10-17 | Improvement in lightning-rod connections | ||
US390615A (en) * | 1888-10-02 | Chaeles g | ||
US1689730A (en) * | 1928-10-30 | Charles y | ||
USRE20270E (en) * | 1937-02-16 | Spline shaft | ||
US1507991A (en) * | 1919-10-14 | 1924-09-09 | Charles R Edwards | Tool joint |
US1381805A (en) * | 1919-12-09 | 1921-06-14 | Courtaulds Ltd | Spinning-box mounting |
US1375852A (en) * | 1920-05-13 | 1921-04-26 | Asa E Linendoll | Method of attaching universal-joint spiders to tubular propeller-shafts |
US1469304A (en) * | 1921-06-16 | 1923-10-02 | New Departure Mfg Co | Schaft coupling |
US1779805A (en) * | 1923-03-01 | 1930-10-28 | Dunwoodie David | Spline teeth |
US1586990A (en) * | 1924-04-22 | 1926-06-01 | Henry P Harrison | Spline shaft |
US1511910A (en) * | 1924-05-14 | 1924-10-14 | Rolls Royce | Change-speed mechanism for mechanically-propelled vehicles |
US1636262A (en) * | 1925-08-06 | 1927-07-19 | Harry P Troendly | Torque-cushioning means |
US1861640A (en) * | 1927-07-08 | 1932-06-07 | Apex Electrical Mfg Co | Washing machine |
US1909500A (en) * | 1930-05-19 | 1933-05-16 | Nat Alloy Steel Company | Shaft mounting for rollers or pulleys |
US1916259A (en) * | 1931-08-03 | 1933-07-04 | Otto F Ewert | Hob |
US1905277A (en) * | 1931-08-03 | 1933-04-25 | Otto F Ewert | Method of making spline couplings |
US1905278A (en) * | 1931-08-03 | 1933-04-25 | Barber Colman Co | Method of making spline couplings |
US2038554A (en) * | 1932-07-01 | 1936-04-28 | Barber Colman Co | Spline coupling |
US2119334A (en) * | 1934-08-16 | 1938-05-31 | William S Leffler | Self-affixing and self-tightening connection for rotating and rotated members |
US2089168A (en) * | 1934-10-12 | 1937-08-03 | Perry W Brown | Spline connection |
US2056688A (en) * | 1934-11-15 | 1936-10-06 | Lamson & Sessions Co | Weather-tight bolt |
US2015430A (en) * | 1935-03-02 | 1935-09-24 | Int Motor Co | Involute spline shaft |
US2111244A (en) * | 1935-04-22 | 1938-03-15 | Fed Merchandise Company | Fan stand |
US2326932A (en) * | 1935-10-21 | 1943-08-17 | Michigan Tool Co | Hob |
US2164643A (en) * | 1935-10-21 | 1939-07-04 | Michigan Tool Co | Method of cutting tapered spline |
US2083092A (en) * | 1936-01-20 | 1937-06-08 | Joseph R Richer | Screw |
US2297390A (en) * | 1939-01-18 | 1942-09-29 | Burger Peter | Splined connection |
US2259460A (en) * | 1939-04-17 | 1941-10-21 | Reynolds B Dexter | Resilient drive bushing |
US2363845A (en) * | 1942-05-18 | 1944-11-28 | Duggan James Edward | Mask structure |
US2440775A (en) * | 1944-12-26 | 1948-05-04 | Int Harvester Co | Sliding gear lock |
US2430683A (en) * | 1945-10-30 | 1947-11-11 | Morgan Construction Co | Wabbler coupling |
US2514675A (en) * | 1945-12-15 | 1950-07-11 | Nordberg Manufacturing Co | Gyratory crusher mantle |
US2471982A (en) * | 1946-11-04 | 1949-05-31 | Shulda Melvin | Splice for crankshaft bearings |
US2508832A (en) * | 1948-08-28 | 1950-05-23 | Borg Warner | Coupling device |
US2652271A (en) * | 1950-01-05 | 1953-09-15 | Gen Motors Corp | Turbine wheel mounting |
US2691899A (en) * | 1950-04-21 | 1954-10-19 | Reliance Gauge Columm Company | Valve stem adjuster |
US2653840A (en) * | 1950-05-02 | 1953-09-29 | O Cel O Inc | Jointed handle |
US2726357A (en) * | 1952-10-22 | 1955-12-06 | Columbia Broadcasting Syst Inc | Semiconductor device |
US2765529A (en) * | 1953-05-11 | 1956-10-09 | Borg Warner | Methods of forming splines in bores of machine elements |
US2821277A (en) * | 1953-11-11 | 1958-01-28 | English Electric Co Ltd | Splined clutches |
US2932207A (en) * | 1957-09-26 | 1960-04-12 | Whitney Chain Company | Chain sprocket |
US2969250A (en) * | 1959-01-05 | 1961-01-24 | Standard Pressed Steel Co | Socket drive |
US3290918A (en) * | 1963-12-06 | 1966-12-13 | Anthony V Weasler | Method of manufacturing a shaft coupling |
US3237469A (en) * | 1964-04-13 | 1966-03-01 | Banks M Berry | Timing gears |
US3396554A (en) * | 1966-04-14 | 1968-08-13 | Gen Motors Corp | Retaining ring for a universal joint member |
US3584667A (en) * | 1966-09-19 | 1971-06-15 | Textron Inc | Coupling arrangement and tools for same |
US3418012A (en) * | 1966-10-17 | 1968-12-24 | Mahoney Thomas P | Fastener for prestressing objects connected thereby |
US3415137A (en) * | 1967-04-07 | 1968-12-10 | Casale Engineering | Timing means |
US3487903A (en) * | 1967-07-19 | 1970-01-06 | August Stickan | Torque locked spline for clutch |
SE321900B (en) * | 1967-12-08 | 1970-03-16 | Atlas Copco Ab | |
US3477250A (en) * | 1968-06-20 | 1969-11-11 | Ford Motor Co | Anchor tooth spline for rotating gear mechanisms |
US3621945A (en) * | 1969-11-12 | 1971-11-23 | Carborundum Co | Disc brakes |
US3832076A (en) * | 1972-09-25 | 1974-08-27 | Gen Motors Corp | Splined assembly with retaining rings |
US3805552A (en) * | 1972-10-17 | 1974-04-23 | Atomic Energy Commission | Radial spline guide bearing assembly |
US3838929A (en) * | 1972-12-22 | 1974-10-01 | A Burrell | Interchangeable hub |
US3836272A (en) * | 1973-07-02 | 1974-09-17 | Gen Motors Corp | Connecting device with expanding splines |
US3865500A (en) * | 1973-07-09 | 1975-02-11 | E Strohm Newell | Locking handle |
US3889489A (en) * | 1974-08-23 | 1975-06-17 | Gen Motors Corp | Lubricated spline coupling |
US3932048A (en) * | 1975-01-17 | 1976-01-13 | Thermoplastic Processes, Inc. | Furniture jointing arrangement |
US3992117A (en) * | 1975-03-27 | 1976-11-16 | General Motors Corporation | Shaft retaining ring |
FR2352209A1 (en) * | 1976-05-17 | 1977-12-16 | Glaenzer Spicer Sa | IMPROVEMENT OF SLIDING RIBBON COUPLINGS |
US4210372A (en) * | 1977-02-11 | 1980-07-01 | Caterpillar Tractor Co. | Retainer for bearing lock nut |
US4098096A (en) * | 1977-05-25 | 1978-07-04 | The United States Of America As Represented By The Secretary Of The Navy | High strength, non-metallic coupling |
JPS5653143Y2 (en) * | 1977-09-06 | 1981-12-11 | ||
US4153260A (en) * | 1978-06-02 | 1979-05-08 | Dana Corporation | Slip spline seal assembly |
JPS551924A (en) * | 1978-06-21 | 1980-01-09 | Hitachi Ltd | Joint structure of metal and its jointing method |
US4685823A (en) * | 1980-12-23 | 1987-08-11 | The Boeing Company | Antibacklash shaft coupling |
US4368786A (en) * | 1981-04-02 | 1983-01-18 | Cousins James E | Downhole drilling apparatus |
US4473317A (en) * | 1981-06-22 | 1984-09-25 | The Boeing Company | Anti-backlash mechanism for a spline connection |
DE3200846A1 (en) * | 1982-01-14 | 1983-07-21 | Jean Walterscheid Gmbh, 5204 Lohmar | Wedge hub to connect two shafts |
US4433964A (en) * | 1982-06-11 | 1984-02-28 | Standard Oil Company | Composite timing gears and process |
US4552544A (en) * | 1982-12-27 | 1985-11-12 | Dana Corporation | Drive line slip joint assembly |
FR2560099B1 (en) * | 1984-02-24 | 1986-10-24 | Facom | TIGHTENING TOOL FOR HARDWARE |
US4554893A (en) * | 1984-10-01 | 1985-11-26 | General Motors Corporation | Lightweight engine |
DE3438918C2 (en) * | 1984-10-24 | 1986-10-02 | Daimler-Benz Ag, 7000 Stuttgart | Driver connection between splined shafts and splined hubs of safety steering columns |
US4572291A (en) * | 1984-11-06 | 1986-02-25 | Robison Robert E | Well casing scraper |
US4603597A (en) * | 1985-01-30 | 1986-08-05 | Xerox Corporation | Drive system |
AT384405B (en) * | 1985-07-22 | 1987-11-10 | Supervis Ets | LENGTH-CHANGEABLE STEERING SPINDLE FOR STEERING DEVICES IN MOTOR VEHICLES |
US4701068A (en) * | 1986-05-19 | 1987-10-20 | Allied Corporation | Spline anti-backlash device |
DE254106T1 (en) * | 1986-07-07 | 1988-10-13 | Edwin S. Fajardo P.R. Us Geary | PROPELLER AND FASTENER. |
DE3635916C1 (en) * | 1986-10-22 | 1988-03-24 | Voith Gmbh J M | Gearing for a shaft-hub connection |
DE313345T1 (en) * | 1987-10-21 | 1990-05-03 | ASSEMBLING A MULTI-STAGE SPROCKET FOR A BICYCLE. | |
US4807351A (en) * | 1988-02-18 | 1989-02-28 | Asea Composites, Inc. | Method for attaching an end-fitting to a drive shaft tube |
ES2042274T3 (en) * | 1988-12-10 | 1993-12-01 | Zf Friedrichshafen Aktiengesellschaft | INLET UNION WITH PRESSURE ADJUSTMENT BETWEEN A TREE AND A BUCKET. |
US4938731A (en) * | 1989-02-07 | 1990-07-03 | Barry Wright Corporation | Rotatable, self-aligning lobe coupling |
US4919221A (en) * | 1989-04-06 | 1990-04-24 | Numa Tool Company | Impact drill bit assembly and replaceable parts thereof |
US5019080A (en) * | 1990-02-13 | 1991-05-28 | Trextron Inc. | Drive system for prosthetic fasteners |
US5165881A (en) * | 1991-09-16 | 1992-11-24 | Opcon Autorotor Ab | Rotor for a screw rotor machine |
US5181432A (en) * | 1991-11-26 | 1993-01-26 | Cloyes Gear & Products | Timing gear having different keyways |
US5427580A (en) * | 1992-05-19 | 1995-06-27 | Borg-Warner Automotive, Inc. | Phased chain assemblies |
US5275577A (en) * | 1992-08-10 | 1994-01-04 | Emerson Electric Co. | Pulley retention mechanism |
JP3052037B2 (en) * | 1993-07-22 | 2000-06-12 | 本田技研工業株式会社 | Spline connection structure |
US5460574A (en) * | 1993-08-31 | 1995-10-24 | Trw Inc. | Variable length shaft assembly with a lash bushing |
US5469958A (en) * | 1993-11-16 | 1995-11-28 | Ucc Corporation | Conveyor drive spocket |
US5653764A (en) * | 1994-02-17 | 1997-08-05 | Murphy; Stephen B. | Modular hip prosthesis with discrete selectable angular orientation |
KR0174392B1 (en) * | 1994-03-31 | 1999-02-18 | 토니 헬샴 | Spline |
US5647683A (en) * | 1994-04-05 | 1997-07-15 | Dana Corporation | Axle and tube yoke attachment |
US5538355A (en) * | 1994-08-25 | 1996-07-23 | Caterpillar Inc. | Key apparatus |
US5480357A (en) * | 1995-01-03 | 1996-01-02 | Liang; Tzong T. | Freewheel assembly for bicycle |
US5569107A (en) * | 1995-05-31 | 1996-10-29 | Falcon Industrial Co., Ltd. | Multi-step bicycle transmission sprocket assembly |
US5785357A (en) * | 1995-09-22 | 1998-07-28 | Utd, Inc. | Locking joint |
US5690568A (en) * | 1996-01-31 | 1997-11-25 | Borg-Warner Automotive, Inc. | Idler sprocket assembly for a phased chain system |
US5699866A (en) * | 1996-05-10 | 1997-12-23 | Perf Drill, Inc. | Sectional drive system |
US5980406A (en) * | 1996-08-14 | 1999-11-09 | Borg-Warner Automotive, Inc. | Sprocket assembly for a phased chain system |
US6059378A (en) * | 1997-05-01 | 2000-05-09 | Impact Forge, Inc. | Taperlock axle apparatus and flange |
USD396436S (en) * | 1997-05-30 | 1998-07-28 | Gordon Liska | Sprocket gear for a chain-driven vehicle |
US5903965A (en) * | 1997-09-04 | 1999-05-18 | Dana Corporation | Method for applying a low friction coating on a splinned slip joint |
US6604885B1 (en) * | 1997-10-30 | 2003-08-12 | Bayerische Motoren Werke Aktiengesellschaft | Torque transmitter connection assembly |
DE19750005C1 (en) * | 1997-11-12 | 1999-04-22 | Supervis Ets | Length-alterable steering spindle for road vehicle |
WO1999057450A1 (en) * | 1998-05-04 | 1999-11-11 | Lukas Matt | Device comprising a shaft and at least one hub which is attached to said shaft, and a method for producing this device |
US6059480A (en) * | 1998-06-10 | 2000-05-09 | Dana Corporation | Composite stud |
US6267701B1 (en) * | 1998-09-21 | 2001-07-31 | Borgwarner Inc. | Sprocket for multiple axis phased chain systems |
US6238133B1 (en) * | 1998-10-20 | 2001-05-29 | Kennametal Pc Inc. | Anti-rotation mounting mechanism for round cutting insert |
US6101907A (en) * | 1998-11-25 | 2000-08-15 | Snap-On Tools Company | Interference fit joint and method and indexable ratchet wrench utilizing same |
US6754943B1 (en) * | 1998-12-31 | 2004-06-29 | Torque-Traction Technologies, Inc. | Method of manufacturing an axially collapsible driveshaft assembly |
US5987287A (en) * | 1999-01-29 | 1999-11-16 | General Plastic Industrial Co., Ltd. | Developer cylinder and drive gear arrangement |
JP3718080B2 (en) * | 1999-05-07 | 2005-11-16 | 日立建機株式会社 | Hydraulic motor with brake device |
JP2001021010A (en) * | 1999-07-06 | 2001-01-26 | Tsubakimoto Chain Co | Power transmission mechanism made in combination of silent chain and sprocket |
US6279221B1 (en) * | 1999-09-08 | 2001-08-28 | Visteon Global Tech., Inc. | Vehicle driveshaft |
SE516524C2 (en) * | 2000-05-18 | 2002-01-22 | Sandvik Ab | Utilities Connection |
JP2002062465A (en) * | 2000-08-16 | 2002-02-28 | Sony Corp | Optical component connecting device and optical module using it |
US6829455B2 (en) * | 2000-10-20 | 2004-12-07 | Canon Kabushiki Kaisha | Driving force transmission mechanism, image forming apparatus equipped with such a mechanism, and process unit of such an apparatus |
US6381933B1 (en) * | 2000-11-27 | 2002-05-07 | New Holland North America, Inc. | Shaft coupling with tapered splines for a pull-type forage harvester |
US6547479B2 (en) * | 2001-02-14 | 2003-04-15 | Ford Global Technologies, Inc. | Spline, an assembly utilizing the spline, and a method for transferring energy |
US6705949B2 (en) * | 2001-08-27 | 2004-03-16 | Visteon Global Technologies, Inc. | Shaft spline having a straight side tooth profile |
US6783553B2 (en) * | 2001-10-24 | 2004-08-31 | James B. Grimes | Prosthesis |
KR100423475B1 (en) * | 2001-11-27 | 2004-03-18 | 삼성전자주식회사 | coupling apparatus |
US6698076B2 (en) * | 2002-01-07 | 2004-03-02 | Meritor Heavy Vehicle Systems, Llc | Drive shaft manufacturing process |
US6736580B2 (en) * | 2002-01-16 | 2004-05-18 | Hi-Shear Corporation | Lobed drive for hi-lite fastener |
US6655888B2 (en) * | 2002-01-16 | 2003-12-02 | Hi-Shear Corporation | Lobed drive for hi-lite fastener |
US6761503B2 (en) * | 2002-04-24 | 2004-07-13 | Torque-Traction Technologies, Inc. | Splined member for use in a slip joint and method of manufacturing the same |
US7044860B2 (en) * | 2003-03-31 | 2006-05-16 | Torque-Traction Technologies Llc | Slip joint for vehicle driveshaft assembly |
US7722297B2 (en) * | 2003-04-15 | 2010-05-25 | Tdy Industries, Inc. | Antirotation tool holder and cutting insert |
SE526555C2 (en) * | 2003-08-21 | 2005-10-04 | Haldex Brake Prod Ab | Interface between disc and central part for disc brakes |
US7220083B2 (en) * | 2003-10-15 | 2007-05-22 | Tdy Industries, Inc. | Cutting insert for high feed face milling |
US7178786B2 (en) * | 2003-11-21 | 2007-02-20 | Brass-Craft Manufacturing Company | Stem construction for rotatable valve body |
US7661687B2 (en) * | 2004-03-30 | 2010-02-16 | Honda Motor Co., Ltd. | Vehicle and chain play adjusting device thereof |
WO2005121581A1 (en) * | 2004-06-14 | 2005-12-22 | Ernst Grob Ag | Grooved profile for a hub shaft connection |
FR2871537B1 (en) * | 2004-06-15 | 2006-09-22 | Snr Roulements Sa | AIR PASSING BEARING IN A BOREHOLE PROVIDED WITH CANNELS |
JP4566240B2 (en) * | 2004-09-03 | 2010-10-20 | ライストリッツ アーゲー | Extruder worm |
DE102004043621A1 (en) * | 2004-09-07 | 2006-03-23 | Volkswagen Ag | shaft assembly |
US7963388B2 (en) * | 2004-11-05 | 2011-06-21 | Tkf Incorporated | Spline roller for a belt-driven roller conveyor, and method for making |
US7225710B2 (en) * | 2005-05-27 | 2007-06-05 | Synthes Gmbh | Combination driver and combination fastener |
KR100627729B1 (en) * | 2005-06-21 | 2006-09-25 | 주식회사다스 | Shaft and hub fitting structure of a recliner |
JP2007011093A (en) * | 2005-06-30 | 2007-01-18 | Toshiba Corp | Drive connection mechanism and image forming apparatus having the mechanism |
US20070104535A1 (en) * | 2005-11-09 | 2007-05-10 | Brian Valovick | Spline interconnect |
JP4704202B2 (en) * | 2005-12-08 | 2011-06-15 | 住友電工ハードメタル株式会社 | Mounting structure of pin mirror cutter to adapter |
DE112007001006A5 (en) * | 2006-02-22 | 2009-01-22 | Shaft Form Engineering Gmbh | Constant velocity joint |
US7998007B2 (en) * | 2006-08-03 | 2011-08-16 | Borgwarner, Inc. | Phasing of chains, sprockets, and gears to provide enhanced noise vibration and harshness reduction |
US8133142B2 (en) * | 2007-05-08 | 2012-03-13 | Dunkermotoren Gmbh | Belt pulley for the output shaft of a gear, gear, electric motor, and output shaft |
US8540582B2 (en) * | 2007-09-12 | 2013-09-24 | Ntn Corporation | Bearing device for wheel, and axle module |
US8202043B2 (en) * | 2007-10-15 | 2012-06-19 | United Technologies Corp. | Gas turbine engines and related systems involving variable vanes |
US7810586B2 (en) * | 2007-11-19 | 2010-10-12 | Cousins James E | Sectional drive and coupling system |
JP2009220723A (en) * | 2008-03-17 | 2009-10-01 | Honda Motor Co Ltd | Steering device for small vessel |
CN101649884B (en) * | 2008-08-15 | 2013-11-13 | 德昌电机(深圳)有限公司 | Transmission structure and motor assembly with same |
DE102008049825B4 (en) * | 2008-10-01 | 2017-04-06 | Thyssenkrupp Presta Aktiengesellschaft | sliding sleeve |
US8545125B2 (en) * | 2009-06-01 | 2013-10-01 | Baker Hughes Incorporated | Non-parallel splined hub and shaft connection |
RU2513676C2 (en) * | 2009-06-24 | 2014-04-20 | ОЭсДжи СИСТЕМ ПРОДАКТС КО., ЛТД. | Screw tightening structure, screw and screw tightening tool |
US8313067B2 (en) * | 2009-12-15 | 2012-11-20 | Welch Allyn, Inc. | Pole shaft coupling assembly and related method |
IL207624A0 (en) * | 2010-08-16 | 2010-12-30 | Iscar Ltd | T-slot cutter |
US8555838B2 (en) * | 2010-12-01 | 2013-10-15 | Caterpillar Inc. | Engine with stub shaft supported cam gear and machine using same |
US8388455B2 (en) * | 2010-12-22 | 2013-03-05 | Thyssenkrupp Presta Aktiengesellschaft | Antifriction bushing |
EP2791516B1 (en) * | 2012-04-03 | 2017-06-07 | ITW Construction Products ApS | Fastener with multilobular tool engaging portion |
WO2014062374A1 (en) * | 2012-10-18 | 2014-04-24 | Borgwarner Inc. | Fluted sprocket/cog bore for reduced machining cycle times and reduced tool wear |
JP6230890B2 (en) * | 2012-12-13 | 2017-11-15 | ニッタ株式会社 | Shaft structure, male member, and female member |
PL3055576T3 (en) * | 2013-10-10 | 2021-09-13 | Acument Intellectual Properties Llc | Punch pins, associated sockets, and methods of forming sockets using punch pins |
JP6221893B2 (en) * | 2014-03-27 | 2017-11-01 | アイシン・エィ・ダブリュ株式会社 | Power transmission device |
-
2016
- 2016-05-26 US US15/165,604 patent/US9845861B1/en not_active Expired - Fee Related
-
2017
- 2017-05-09 CN CN201710321013.2A patent/CN107435687B/en not_active Expired - Fee Related
- 2017-05-25 DE DE102017111494.7A patent/DE102017111494A1/en not_active Withdrawn
Also Published As
Publication number | Publication date |
---|---|
CN107435687A (en) | 2017-12-05 |
US9845861B1 (en) | 2017-12-19 |
DE102017111494A1 (en) | 2017-11-30 |
CN107435687B (en) | 2020-03-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN107923510B (en) | Transmission with flexible gear | |
JP4262851B2 (en) | Wheel bearing device | |
US9845861B1 (en) | Rotatable assembly including a coupling interface | |
JP4909276B2 (en) | Camshaft for automobile engine | |
US8075218B2 (en) | Prestressed shaft and hub connection having a perfect cone shape | |
US10508594B2 (en) | Actuator for link mechanism for internal combustion engine | |
CN102963213B (en) | Wheel bearing arrangement | |
US11326681B2 (en) | Elastic gear wheel of a harmonic drive | |
US11560926B2 (en) | Power transmission shaft | |
US20030059144A1 (en) | Bearing apparatus for a wheel | |
JP6379798B2 (en) | Rolling bearing unit manufacturing method and vehicle manufacturing method | |
CN107466341B (en) | Tripod type constant velocity universal joint | |
EP2708376A1 (en) | Vehicle bearing apparatus | |
US9506379B2 (en) | Concentric camshaft phaser | |
US10962063B2 (en) | Fixed constant velocity universal joint | |
US9951822B2 (en) | Constant-velocity joint | |
US20160123405A1 (en) | Tube yoke assembly and driveshaft assembly formed therewith | |
US20150219165A1 (en) | Constant-velocity joint | |
US20190257362A1 (en) | Tripod roller for a constant velocity universal joint | |
US10895285B2 (en) | Torque converter installation assist | |
CN103085598A (en) | Wheel bearing device | |
US8257186B2 (en) | Sliding-type tripod-shaped constant-velocity universal joint | |
JP2005180641A (en) | Constant velocity universal joint and method of manufacturing outer ring of constant velocity universal joint | |
US20170102048A1 (en) | High performance flexplate with alternating radial wall thickness and multi-profile lightening holes | |
JP2010127311A (en) | Fixed type constant velocity universal joint and wheel bearing device using the same |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: GM GLOBAL TECHNOLOGY OPERATIONS LLC, MICHIGAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:HUCKER, SCOTT A.;HOSLER, CHRIS D.;BEALS, RONALD B.;REEL/FRAME:038905/0497 Effective date: 20160525 |
|
AS | Assignment |
Owner name: GM GLOBAL TECHNOLOGY OPERATIONS LLC, MICHIGAN Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE FILING DATE PREVIOUSLY RECORDED ON REEL 038905 FRAME 0497. ASSIGNOR(S) HEREBY CONFIRMS THE ASSIGNMENT;ASSIGNORS:HUCKER, SCOTT A.;HOSLER, CHRIS D.;BEALS, RONALD B.;REEL/FRAME:042744/0767 Effective date: 20160525 |
|
STCF | Information on status: patent grant |
Free format text: PATENTED CASE |
|
FEPP | Fee payment procedure |
Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
LAPS | Lapse for failure to pay maintenance fees |
Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY |
|
STCH | Information on status: patent discontinuation |
Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362 |
|
FP | Lapsed due to failure to pay maintenance fee |
Effective date: 20211219 |