CA1210963A - Blocking pin for a transmission synchronizer assembly - Google Patents
Blocking pin for a transmission synchronizer assemblyInfo
- Publication number
- CA1210963A CA1210963A CA000455741A CA455741A CA1210963A CA 1210963 A CA1210963 A CA 1210963A CA 000455741 A CA000455741 A CA 000455741A CA 455741 A CA455741 A CA 455741A CA 1210963 A CA1210963 A CA 1210963A
- Authority
- CA
- Canada
- Prior art keywords
- toothed element
- friction
- blocking
- gear drive
- toothed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D11/00—Clutches in which the members have interengaging parts
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- 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
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D23/0606—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation the blocking mechanism comprising an axially-extending shouldered pin passing through a hole in a radial wall
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- 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
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D2023/0618—Details of blocking mechanism comprising a helical spring loaded element, e.g. ball
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- 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
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D2023/065—Means to provide additional axial force for self-energising, e.g. by using torque from the friction clutch
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Structure Of Transmissions (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
The assembly includes a toothed element which is rotatable with an output shaft and adapted to be selectively engaged with a gear drive means for rotating the output shaft. A synchronizing friction element rotatable with the toothed element is adapted to be selectively engaged with a friction face of the gear drive means. A plurality of blocking pins are provided to slidably mount the toothed element axially with respect to the friction element. Each of the blocking pins includes a recessed portion for retaining the toothed element in a first position relative to the friction element. An inclined ramp portion is provided on each blocking pin having a first end adjacent in edge of the recessed portion and a second end recessed in the blocking pin for retaining the toothed element in a second position relative to the friction element. Locking means are resiliently retained in the tooth element and urged into frictional engagement with each of the blocking pins for cooperating with the recessed portions and the ramp portions to selectively retain the toothed element in one of the first and second positions.
The assembly includes a toothed element which is rotatable with an output shaft and adapted to be selectively engaged with a gear drive means for rotating the output shaft. A synchronizing friction element rotatable with the toothed element is adapted to be selectively engaged with a friction face of the gear drive means. A plurality of blocking pins are provided to slidably mount the toothed element axially with respect to the friction element. Each of the blocking pins includes a recessed portion for retaining the toothed element in a first position relative to the friction element. An inclined ramp portion is provided on each blocking pin having a first end adjacent in edge of the recessed portion and a second end recessed in the blocking pin for retaining the toothed element in a second position relative to the friction element. Locking means are resiliently retained in the tooth element and urged into frictional engagement with each of the blocking pins for cooperating with the recessed portions and the ramp portions to selectively retain the toothed element in one of the first and second positions.
Description
l~lQ96i3 ~
.
TITLE
~ IMPROVED BLOCKING ~IN FOR A
TRANSMISSIDN SYNCHRO~IZER ASSEMBLY
S ~ACKGROUND OF TH~ INVENTION
l. Field of the Invention-_~ . . .
The pxesent invention relates in general to motor vehicle transmissions and i~ particular to an improved blocking pin ~or a transmission ~ynchronizer assembly.
Synchronizing clutches, such as are used in transmission gearings for motor vehicles, are typically ~hiftable in oppo~ite direction~ from a neutral position to either of two different ~peed ratio or drive positions.
Clutches of this type typically include a single, toothed element and two friction elements, the toothed element having clutch teeth ~ormed on opposite ends thereof and the friction elements having a fxiction face formed on outwardly facing ends thereof. ~he two friction elements can be connected by a plurality of blocking pins, each having a blocking shoulder formed thereon to prevent the toothed element from shifting at undesired times. The blocking pin~ can each include a notch formed thereon to position the toothed element accurately in a neutral position between the two drive positions.
The toothed element and friction face at one end of the synchronizer assembly coact with a respective complementary element and face on a member in one gear drive means whil~ the toothed element and friction face at the other end of the synchronizer assembly coact with a respective complem~ntary element and face on a member in another gear drive means. The synchronizer assembly elements are shiftable as a unit in one direction or the other by applying a shifting foree to the toothed element until the friction face of the friction element at one end .
of the synchronizer a~sembly engages with the complementary friction face on the gear drive means. The toothed elemen~
~Z~L~9ti3 is then, after synchronization of the speeds of the output shaft and the gear drive means, shiftable axially relative to the fri~tion ~lement~ a~ the shifting force is continued .to b~ applied such that the toothed element is brought into 5 engageme~t with the coacting ~gear drive means element.
.
TITLE
~ IMPROVED BLOCKING ~IN FOR A
TRANSMISSIDN SYNCHRO~IZER ASSEMBLY
S ~ACKGROUND OF TH~ INVENTION
l. Field of the Invention-_~ . . .
The pxesent invention relates in general to motor vehicle transmissions and i~ particular to an improved blocking pin ~or a transmission ~ynchronizer assembly.
Synchronizing clutches, such as are used in transmission gearings for motor vehicles, are typically ~hiftable in oppo~ite direction~ from a neutral position to either of two different ~peed ratio or drive positions.
Clutches of this type typically include a single, toothed element and two friction elements, the toothed element having clutch teeth ~ormed on opposite ends thereof and the friction elements having a fxiction face formed on outwardly facing ends thereof. ~he two friction elements can be connected by a plurality of blocking pins, each having a blocking shoulder formed thereon to prevent the toothed element from shifting at undesired times. The blocking pin~ can each include a notch formed thereon to position the toothed element accurately in a neutral position between the two drive positions.
The toothed element and friction face at one end of the synchronizer assembly coact with a respective complementary element and face on a member in one gear drive means whil~ the toothed element and friction face at the other end of the synchronizer assembly coact with a respective complem~ntary element and face on a member in another gear drive means. The synchronizer assembly elements are shiftable as a unit in one direction or the other by applying a shifting foree to the toothed element until the friction face of the friction element at one end .
of the synchronizer a~sembly engages with the complementary friction face on the gear drive means. The toothed elemen~
~Z~L~9ti3 is then, after synchronization of the speeds of the output shaft and the gear drive means, shiftable axially relative to the fri~tion ~lement~ a~ the shifting force is continued .to b~ applied such that the toothed element is brought into 5 engageme~t with the coacting ~gear drive means element.
2. Description of the Prior Art United States Patent No. 2,384,439 to Carnagua et al.
discloses a positive clutch mechani5m wherein the shift frDm a lower ratio, such as a second speed, to a higher i 10 ratio, 8uch as a direct drive, is effected automatically in ~3 response ~o a decelerating tor~ue load transmitted from the lo~er ratio driving member to the clutch mechanism. The ds~nshift from the higher ratio to the lower rat~o may be effected by a torque responsive means under the control of 15 tbe operator in moving the engine throttle control in a tbrot~le opening direction. The torque responsive re~hanism energizes both a frictional synchronizing Y
echanism and a positive clutch means. Blocking pins in ~ frictional synchronizing mechanism can include a recess 20 or gx~ove positioned on either side of the neutral position -~ess for positioning a shift sleeve in a desired gear io. Similar grooves are illustrated in U~ited States F~tent No. 3,086,633 to Winter.
~nited States Patent No. 2,425,203 to Peterson et al.
25 ~loses a synchro~izing clutch having a blocking shoulder c~ blo~king tooth arran~ement whereby blocking takes place o~y when a shift is bei~g made from a lower speed drive ~o a higher speed drive or, if desired, from a higher ~r ratio into a l~wer gear drive wherein the vehicle is
discloses a positive clutch mechani5m wherein the shift frDm a lower ratio, such as a second speed, to a higher i 10 ratio, 8uch as a direct drive, is effected automatically in ~3 response ~o a decelerating tor~ue load transmitted from the lo~er ratio driving member to the clutch mechanism. The ds~nshift from the higher ratio to the lower rat~o may be effected by a torque responsive means under the control of 15 tbe operator in moving the engine throttle control in a tbrot~le opening direction. The torque responsive re~hanism energizes both a frictional synchronizing Y
echanism and a positive clutch means. Blocking pins in ~ frictional synchronizing mechanism can include a recess 20 or gx~ove positioned on either side of the neutral position -~ess for positioning a shift sleeve in a desired gear io. Similar grooves are illustrated in U~ited States F~tent No. 3,086,633 to Winter.
~nited States Patent No. 2,425,203 to Peterson et al.
25 ~loses a synchro~izing clutch having a blocking shoulder c~ blo~king tooth arran~ement whereby blocking takes place o~y when a shift is bei~g made from a lower speed drive ~o a higher speed drive or, if desired, from a higher ~r ratio into a l~wer gear drive wherein the vehicle is
3~ is~otion and a member in the gear train i~ rotating.
~bcking does .not take plsce when a shift:is.being made m a lower gear drive wh~n the vehicle is stationary or member in the lower gear drive is not rotating.
Vnited States Patent No. 2,900tO59-to Zittrell et al. .
35 ~closes an ~mproved synchronization device having a ~tion shift member and a push do~ sleeve which ean be . . ~
F
~ ~ ~ O 9~3 locked until synchronism is xeached. Locking members are guided so as to be radially movabl~ on a riction ring ~reely rotatable within the anner part of the gear ~hift 61eeves. The locking members have sloping rounded surfaces S at each end, the inwardly directed ends of which fit opposing surfaces ~ituated on the inner pcrtion of the gear shift sleeve and ar~ effected in the peripheral direction.
The outwaxdly directed ends of the sloping rounded surfaces meet opposite surfaces of the push dog sleeve and ~re ' .
10 effected in the axial direction. The opposite surfaces arranged in the inner part of the gear shift sleeve axe r formed in marginal recesses of the inner part which allow space for partial rotation of the friction ring relative to the inner part so as to permit radial movement of the ~.
15 locking members during rotation of the friction ring. ~.
SUMMARY O~ THE INVENTION
The present invention relates to an improved blocking pin for a transmission synchronizer assembly. The assembly includes a toothed element which is rotatable with an output shaft and adapted to be selectively engaged with a gear drive means for rotating the output shaft. A
synchronizing friction element rotatable with the toothed element is adapted to be selectively engaged with a friction face of the gear drive means. A plurality of blocking pins are provided to slidably mount the toothed element coaxially with respect to the fricti4n element.
Each of the ~locking pins includes a central recessed portion for retainlng the toothed element in..a first, typically non-engaged or neutral, position relative to the - ~
friction element. An inclined ramp portion is prouided on ~' each blocking pin having a first end adjacent to an edge of the neutral recessed portion and a second end recessed in the blooking pin for retaining the toothed element in a second, typically engaged, position re~ative to the . friotion element. Locking means are resiliently.retained : ~ 4 ~ i 12~9~3 - ~
in the toothed element and urged into frictional engagement with each of the blocking pins for eooperating with the L
rece5sed portions and the ramp portions to selectively xçtain the toothed element in the engaged position.
I~ is an object of the present invention to reduce the time required to shift ~rom one gear to the next in a synchronized multi-speed transmi~sion.
It is another object of the present invention to maintain the gear-changing elements of a synchronized multi-speed transmission in a generally planar relati~nship during shifting.
Other objects and advantages of the present invention will become apparent to those skilled in the art from the following detailed description of the preferred embodiment when read in light of the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is ~ sectional elevational view illustrating the upper half of a prior art transmission synchronizer assembly utilizing conventional blocking pins, wherein the transmission synchronizer assembly is shown in a neutral position.
Fig. 2 is a sectional elevation similar to Fig. 1, wherein the prior art transmission synchronizer assembly is shown in a selected gear engaging position.
Fig. 3 is a sectional elevational view illustrating the upper half of a transmission ~ynchronizer assembly utilizing improved blocking pins in accordance with the present invention, wherein the transmission synchronizer assembly is shown in a neutral position.
Fig. 4 is a sectional elevational view similar to Fig.
3 t wherein the transmission synchronizer assembly is shown in a selected gear engaging position.
s ~ ~ ~
- ~L2~ )96~3 ~
DETAILED DESCRIPTION oF-~rHE PREFERRED EMBODIMEN~
~ R~ferxing now to the drawings, there is illustrated in ~igs. 1 and ~ the upper h~lf of a transmission synchroni~er .
assembly 10 which is known in the art. The transmis~ion 5 synchronizer assembly 10 includes a toothed element, such .
as a disk-shaped shift sleeve 12 having an outer annular channel 14 connected by a generally flat central portion 16 to an enlarged inne~ sleeve portion 18. The outer annular ~
channel 14 cooperates with a manually operable shift fork ~-.
~not shown) to apply an axial shiftin~ force to the transmission synchronizer assembly 10. The inner sleeve portion 18 has a plurality of inwardly-extending splines 20 for engaging a drive~ output shaft (not shown) of the transmission synchronizex assembly 10.
The inner sleeve portion 18 also includes a first plurality of outwardly-extending splines 22 (only one is ;
illustrated) formed on one side of the shift sleeve 12 and a second plurality of outwardly-extending splines 24 (only one is illustrated) formed on the other side ~f the shift sleeve 12. ~he first and second pluralities of outwardly-extendin~ splines 22 and 24 are provided to cooperate with respective first and second gear drive means (not shown) which are each connected to an input shaft (not shawn) in a known manner to selectively rotate the output ~5 shaft at two different 5peed ratios with respect to the sp~ed of the input shaft.
A plurality.of apertures 26 (only one is illustrated) are formed in the central portion 16 of the shift sleeva 12. Typically, six such apertures 26 are foxmed in the ce~tral portion 16 and are spaced equidistantly therearound. Each aperture 26 has a conventional blocking pi~ 28 extending therethrough. Each blocking pin 28 includes an enlarged side re~ion 30 and a generally flat tapered cam surface 32. In practice, the blocking pins 28 are disposed around the shift sleeve 12 such that the.side , 6 ~ ~lV9~3 portions 30 are oriented in alternating fashion sequentially about the shift sleeve 12.
Each blocking pin 28 also includes a central recessed portion 34 formed on a generally flat inner surface 36 of the pin 28, as shown most clearly in Fig~ 2. A locking means is resiliently retained in central portion 16 of shift sleeve 12 for cooperating with the recessed portion 34 of each blocking pin 28 so as to releasably retain the shift sleeve 12 in a first position, such as the non-engaged or neutral position illustrated in Fig. 1. The locking means can include an outwardly-extending detent 38 which is slidably retained in and axially extending aperture 39 formed in the central portion 16 of the shift sleeve 12. The detent 38 is urged into frictional engagement with the blocking pin 28 by a spring 40.
The ends of each blocking pin 28 are attached in a known manner to respective synchronizing friction elements, such as synchronizer races or cones 42 and 44. Each of the synchronizer races 42 and 44 is an annular member having a 2n generally flat, threaded, tapered inner surface 46. A
plurality of axially extending channels 48 are formed in the inner surfaces 46 of each of the synchronizer races 42 and 44. The threaded inner surfaces 46 and the axially extending channels 48 of the synchronizer races 42 and 44 provide a path for draining transmission fluid or other lubricant from the region of the inner surface 46 such that a reliable frictional engagement with the corresponding friction face in the selected gear drive means can be obtained.
When it is desired to shift the transmission synchronizer assembly 10 out of the first or neutral position illustrated in Fig. 1 into a second or gear engaging position, a shifting force is applied to the outer annular channel 14 of the shift sleeve 12 by means of the shift fork. Initially, the entire transmission synchronizer assembly 10 slides a short distance along the - - -- 12~(3963 ~
~-~utpu~ shaft, typically .030 to .090 inch~s, until ~h~ .
inner sur~ace 46 of the synchroni.zer race 42 frictionally ~
e~gages the corresponding friction face of the desired ge~r .~.-driYe meansG Such frictional engagement ~6 necessary to synchronize the speeds of rotation of the input and output shafts during the gear shifting process. After such ~peed synchronization, additio~al ~hifting force causes the shift sleeve 12 to slide axially with respect to the synchronizer race 42 into the second position illustrated in Fig. 2, ~h~rein the first gear drive me~ns i8 engaged.
Durinq the above-described gear shifting process, it will be appreciated that the shifting force applied to the .
shift sleeve 12 causes the detent 38 to overcome the urging of the spring ~0 and retract inwardly withi~ the apertuxe 39 formed in the central portion 16 of the shift sleeve 12. .
Once removed from the recessed portion 34 of the bloc~ing pin 28, the detent 38 slides along the flat inner surface of the pin 28 until the shift sleeve 12 reaches the second position. As disclosed in the prior art, a second recess ~not shown) may be ~ormed in the blocking pin 28 such that the ~etent 38 may extend therein to releas~bly retain the shift sleeve 12 in the ~econd position. A similar .
structur~ may be utilized to move the shift sleeve 12 towards the other synchro~izing race 44 into a third position, wherein the second gear drive means is engaged.
Figs. 3 and 4 illustrate a similar transmission synchronizer assembly 50 utilizing an improved blocker pin 52 in accordance with the present invention. The structures of the shift sleeve 12 and the synchronizer - a 30 races 42 and 44 are identical to that described above and, - ~-accordingly, identical reference..numerals are utilized to descri~e these elements. ..The improved blocking pin S2 includes an enlarged.side region 54, a generally flat ~
tapered cam sur~ace 56, and a central recessed portion 58 .-res?ectively similar.to the side portion 30, cam surface 32, and central recessed portion 34 described above. The ~ 9 ~ 3 ~
blocking pin 52 additionally inGludes a pair of inclined .
ramp portions 60, each extending from a first end adjacent to an edge Qf the central recessed portion 58 outwardly toward a second end recessed to form recesse~ portion 62 in 5 the blocking pin 52. Although any desired incline may ~e ~,~
utilized for the ramp portion 60, it has been found desirable that a gradual ramp of approximately twelve degrees yield~ desirable results. o In operation, when the applied shifting force begin~
10 to move t~e shi$t sleeve 1~ with respect to the synchronizer races 42 and 44, the detent 38 will initially , be pushed radially inwardly within the aperture 39. .
However, once completely removed from the central recessed portion 58, the deten~ 38 will begin to move axially 15 outwardly under the urging of the spring 40 as the shift slee~e 12 slides farther along the inclined ramp portion 60 ~c until it reaches the fully recessed portion 62 of the second position illu~trated in Fig. 4~ ~
The in~lined ramp portions 60 provide several 20 significant advantages over the prior art blocking pins 28. P
The frictional engagement of the detent 38 with the inclined ramp portion 60 of the blocking pin 52 generates forces which tend to "pull" the shift sleeve 12 toward ~he selected gear engaging position. It ha-s been ~ound that 25 the additional force required to return the shift sleeve 12 to the neutral position is insignificant. The frictional .
engagement of the detent 38 with the inclined ramp portion 60 also generates forces which reduce the time required to shift from on~ gear engaging position to the other gear 30 engaging position. For example, if the transmission . x~
synchronizer assembly 50 is in the second position near the .
synchronizer race 42, as illustrated in Fig. 4, and it is desired to shift to the third position near the other synchronizer race 44, a shifting force is initially applied 35 to the shift sleeve 12. If the in~lined ramp portions 60 of the present invention were not present, the shift sleeve ~2~ '9~3 ` ~
.
12 would initially move to the neutral position before the transmission synchronizer assembly 50 would slide ac a unit along the output shaft until the synchroni~er race 44 engages the riction~1 face of the second gear drive means.
~owever, when the inclined r~mp port~ons 60 are present in the blocking pin 52, the transmission synchronizer assembly 50 will shift slightly along the output shaft as a unit in the relationship illustrated in Fig. 4 until the _ synchronizer race 44 engages the friction face of the ~
lO second gear drive means. Thereafter, the shift sleeve 12 .
will move through the first or neutral position i~to the~.
third position. Also, it can be seen that the above-descxibed movement o~ the transmis~ion synchronizer assembly 50 causes the first synchroni~er race 42 to be 15 pulled out of frictional engagement with the first gear drive means sooner than would otherwise occur. This movement minimizes the effect due to runout.
Additionally, the present invention tends to maintain the synchronizer races 42 and 44 in a generally planar 20 relationship with the shift ~leeve 12 during the shifting process. The detents 38 in the shift sleeve 12 exert small uniform forces about the synchronizer race 42 or 44 which the shift sleeve 12 i5 moving towards. Such forces tend to prevent cocking or other misalignment of the synchronizer 25 races 42 and 44.
In accordance with the provisions of the patents statutes, the prinoiple and mode of operation of the present invention have been explained and illus.trated in its preferred embodiment. However, it must be apprec.iated L
30 that the present invention may be practiced otherwise-than -3S specifically explained.:and illustrated without departing .
~rom its spirit or scope~ .
~bcking does .not take plsce when a shift:is.being made m a lower gear drive wh~n the vehicle is stationary or member in the lower gear drive is not rotating.
Vnited States Patent No. 2,900tO59-to Zittrell et al. .
35 ~closes an ~mproved synchronization device having a ~tion shift member and a push do~ sleeve which ean be . . ~
F
~ ~ ~ O 9~3 locked until synchronism is xeached. Locking members are guided so as to be radially movabl~ on a riction ring ~reely rotatable within the anner part of the gear ~hift 61eeves. The locking members have sloping rounded surfaces S at each end, the inwardly directed ends of which fit opposing surfaces ~ituated on the inner pcrtion of the gear shift sleeve and ar~ effected in the peripheral direction.
The outwaxdly directed ends of the sloping rounded surfaces meet opposite surfaces of the push dog sleeve and ~re ' .
10 effected in the axial direction. The opposite surfaces arranged in the inner part of the gear shift sleeve axe r formed in marginal recesses of the inner part which allow space for partial rotation of the friction ring relative to the inner part so as to permit radial movement of the ~.
15 locking members during rotation of the friction ring. ~.
SUMMARY O~ THE INVENTION
The present invention relates to an improved blocking pin for a transmission synchronizer assembly. The assembly includes a toothed element which is rotatable with an output shaft and adapted to be selectively engaged with a gear drive means for rotating the output shaft. A
synchronizing friction element rotatable with the toothed element is adapted to be selectively engaged with a friction face of the gear drive means. A plurality of blocking pins are provided to slidably mount the toothed element coaxially with respect to the fricti4n element.
Each of the ~locking pins includes a central recessed portion for retainlng the toothed element in..a first, typically non-engaged or neutral, position relative to the - ~
friction element. An inclined ramp portion is prouided on ~' each blocking pin having a first end adjacent to an edge of the neutral recessed portion and a second end recessed in the blooking pin for retaining the toothed element in a second, typically engaged, position re~ative to the . friotion element. Locking means are resiliently.retained : ~ 4 ~ i 12~9~3 - ~
in the toothed element and urged into frictional engagement with each of the blocking pins for eooperating with the L
rece5sed portions and the ramp portions to selectively xçtain the toothed element in the engaged position.
I~ is an object of the present invention to reduce the time required to shift ~rom one gear to the next in a synchronized multi-speed transmi~sion.
It is another object of the present invention to maintain the gear-changing elements of a synchronized multi-speed transmission in a generally planar relati~nship during shifting.
Other objects and advantages of the present invention will become apparent to those skilled in the art from the following detailed description of the preferred embodiment when read in light of the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is ~ sectional elevational view illustrating the upper half of a prior art transmission synchronizer assembly utilizing conventional blocking pins, wherein the transmission synchronizer assembly is shown in a neutral position.
Fig. 2 is a sectional elevation similar to Fig. 1, wherein the prior art transmission synchronizer assembly is shown in a selected gear engaging position.
Fig. 3 is a sectional elevational view illustrating the upper half of a transmission ~ynchronizer assembly utilizing improved blocking pins in accordance with the present invention, wherein the transmission synchronizer assembly is shown in a neutral position.
Fig. 4 is a sectional elevational view similar to Fig.
3 t wherein the transmission synchronizer assembly is shown in a selected gear engaging position.
s ~ ~ ~
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DETAILED DESCRIPTION oF-~rHE PREFERRED EMBODIMEN~
~ R~ferxing now to the drawings, there is illustrated in ~igs. 1 and ~ the upper h~lf of a transmission synchroni~er .
assembly 10 which is known in the art. The transmis~ion 5 synchronizer assembly 10 includes a toothed element, such .
as a disk-shaped shift sleeve 12 having an outer annular channel 14 connected by a generally flat central portion 16 to an enlarged inne~ sleeve portion 18. The outer annular ~
channel 14 cooperates with a manually operable shift fork ~-.
~not shown) to apply an axial shiftin~ force to the transmission synchronizer assembly 10. The inner sleeve portion 18 has a plurality of inwardly-extending splines 20 for engaging a drive~ output shaft (not shown) of the transmission synchronizex assembly 10.
The inner sleeve portion 18 also includes a first plurality of outwardly-extending splines 22 (only one is ;
illustrated) formed on one side of the shift sleeve 12 and a second plurality of outwardly-extending splines 24 (only one is illustrated) formed on the other side ~f the shift sleeve 12. ~he first and second pluralities of outwardly-extendin~ splines 22 and 24 are provided to cooperate with respective first and second gear drive means (not shown) which are each connected to an input shaft (not shawn) in a known manner to selectively rotate the output ~5 shaft at two different 5peed ratios with respect to the sp~ed of the input shaft.
A plurality.of apertures 26 (only one is illustrated) are formed in the central portion 16 of the shift sleeva 12. Typically, six such apertures 26 are foxmed in the ce~tral portion 16 and are spaced equidistantly therearound. Each aperture 26 has a conventional blocking pi~ 28 extending therethrough. Each blocking pin 28 includes an enlarged side re~ion 30 and a generally flat tapered cam surface 32. In practice, the blocking pins 28 are disposed around the shift sleeve 12 such that the.side , 6 ~ ~lV9~3 portions 30 are oriented in alternating fashion sequentially about the shift sleeve 12.
Each blocking pin 28 also includes a central recessed portion 34 formed on a generally flat inner surface 36 of the pin 28, as shown most clearly in Fig~ 2. A locking means is resiliently retained in central portion 16 of shift sleeve 12 for cooperating with the recessed portion 34 of each blocking pin 28 so as to releasably retain the shift sleeve 12 in a first position, such as the non-engaged or neutral position illustrated in Fig. 1. The locking means can include an outwardly-extending detent 38 which is slidably retained in and axially extending aperture 39 formed in the central portion 16 of the shift sleeve 12. The detent 38 is urged into frictional engagement with the blocking pin 28 by a spring 40.
The ends of each blocking pin 28 are attached in a known manner to respective synchronizing friction elements, such as synchronizer races or cones 42 and 44. Each of the synchronizer races 42 and 44 is an annular member having a 2n generally flat, threaded, tapered inner surface 46. A
plurality of axially extending channels 48 are formed in the inner surfaces 46 of each of the synchronizer races 42 and 44. The threaded inner surfaces 46 and the axially extending channels 48 of the synchronizer races 42 and 44 provide a path for draining transmission fluid or other lubricant from the region of the inner surface 46 such that a reliable frictional engagement with the corresponding friction face in the selected gear drive means can be obtained.
When it is desired to shift the transmission synchronizer assembly 10 out of the first or neutral position illustrated in Fig. 1 into a second or gear engaging position, a shifting force is applied to the outer annular channel 14 of the shift sleeve 12 by means of the shift fork. Initially, the entire transmission synchronizer assembly 10 slides a short distance along the - - -- 12~(3963 ~
~-~utpu~ shaft, typically .030 to .090 inch~s, until ~h~ .
inner sur~ace 46 of the synchroni.zer race 42 frictionally ~
e~gages the corresponding friction face of the desired ge~r .~.-driYe meansG Such frictional engagement ~6 necessary to synchronize the speeds of rotation of the input and output shafts during the gear shifting process. After such ~peed synchronization, additio~al ~hifting force causes the shift sleeve 12 to slide axially with respect to the synchronizer race 42 into the second position illustrated in Fig. 2, ~h~rein the first gear drive me~ns i8 engaged.
Durinq the above-described gear shifting process, it will be appreciated that the shifting force applied to the .
shift sleeve 12 causes the detent 38 to overcome the urging of the spring ~0 and retract inwardly withi~ the apertuxe 39 formed in the central portion 16 of the shift sleeve 12. .
Once removed from the recessed portion 34 of the bloc~ing pin 28, the detent 38 slides along the flat inner surface of the pin 28 until the shift sleeve 12 reaches the second position. As disclosed in the prior art, a second recess ~not shown) may be ~ormed in the blocking pin 28 such that the ~etent 38 may extend therein to releas~bly retain the shift sleeve 12 in the ~econd position. A similar .
structur~ may be utilized to move the shift sleeve 12 towards the other synchro~izing race 44 into a third position, wherein the second gear drive means is engaged.
Figs. 3 and 4 illustrate a similar transmission synchronizer assembly 50 utilizing an improved blocker pin 52 in accordance with the present invention. The structures of the shift sleeve 12 and the synchronizer - a 30 races 42 and 44 are identical to that described above and, - ~-accordingly, identical reference..numerals are utilized to descri~e these elements. ..The improved blocking pin S2 includes an enlarged.side region 54, a generally flat ~
tapered cam sur~ace 56, and a central recessed portion 58 .-res?ectively similar.to the side portion 30, cam surface 32, and central recessed portion 34 described above. The ~ 9 ~ 3 ~
blocking pin 52 additionally inGludes a pair of inclined .
ramp portions 60, each extending from a first end adjacent to an edge Qf the central recessed portion 58 outwardly toward a second end recessed to form recesse~ portion 62 in 5 the blocking pin 52. Although any desired incline may ~e ~,~
utilized for the ramp portion 60, it has been found desirable that a gradual ramp of approximately twelve degrees yield~ desirable results. o In operation, when the applied shifting force begin~
10 to move t~e shi$t sleeve 1~ with respect to the synchronizer races 42 and 44, the detent 38 will initially , be pushed radially inwardly within the aperture 39. .
However, once completely removed from the central recessed portion 58, the deten~ 38 will begin to move axially 15 outwardly under the urging of the spring 40 as the shift slee~e 12 slides farther along the inclined ramp portion 60 ~c until it reaches the fully recessed portion 62 of the second position illu~trated in Fig. 4~ ~
The in~lined ramp portions 60 provide several 20 significant advantages over the prior art blocking pins 28. P
The frictional engagement of the detent 38 with the inclined ramp portion 60 of the blocking pin 52 generates forces which tend to "pull" the shift sleeve 12 toward ~he selected gear engaging position. It ha-s been ~ound that 25 the additional force required to return the shift sleeve 12 to the neutral position is insignificant. The frictional .
engagement of the detent 38 with the inclined ramp portion 60 also generates forces which reduce the time required to shift from on~ gear engaging position to the other gear 30 engaging position. For example, if the transmission . x~
synchronizer assembly 50 is in the second position near the .
synchronizer race 42, as illustrated in Fig. 4, and it is desired to shift to the third position near the other synchronizer race 44, a shifting force is initially applied 35 to the shift sleeve 12. If the in~lined ramp portions 60 of the present invention were not present, the shift sleeve ~2~ '9~3 ` ~
.
12 would initially move to the neutral position before the transmission synchronizer assembly 50 would slide ac a unit along the output shaft until the synchroni~er race 44 engages the riction~1 face of the second gear drive means.
~owever, when the inclined r~mp port~ons 60 are present in the blocking pin 52, the transmission synchronizer assembly 50 will shift slightly along the output shaft as a unit in the relationship illustrated in Fig. 4 until the _ synchronizer race 44 engages the friction face of the ~
lO second gear drive means. Thereafter, the shift sleeve 12 .
will move through the first or neutral position i~to the~.
third position. Also, it can be seen that the above-descxibed movement o~ the transmis~ion synchronizer assembly 50 causes the first synchroni~er race 42 to be 15 pulled out of frictional engagement with the first gear drive means sooner than would otherwise occur. This movement minimizes the effect due to runout.
Additionally, the present invention tends to maintain the synchronizer races 42 and 44 in a generally planar 20 relationship with the shift ~leeve 12 during the shifting process. The detents 38 in the shift sleeve 12 exert small uniform forces about the synchronizer race 42 or 44 which the shift sleeve 12 i5 moving towards. Such forces tend to prevent cocking or other misalignment of the synchronizer 25 races 42 and 44.
In accordance with the provisions of the patents statutes, the prinoiple and mode of operation of the present invention have been explained and illus.trated in its preferred embodiment. However, it must be apprec.iated L
30 that the present invention may be practiced otherwise-than -3S specifically explained.:and illustrated without departing .
~rom its spirit or scope~ .
Claims (7)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A synchronized transmission assembly comprising:
a toothed element rotatable with an output shaft and adapted to be selectively engaged with a gear drive means for rotating the output shaft;
a synchronizing friction element rotatable with said toothed element and adapted to be selectively engaged with a friction face of said gear drive means;
a plurality of blocking pins for slidably mounting said toothed element axially with respect to said friction element, each of said blocking pins including a recessed portion for retaining said toothed element in a first position relative to said friction element and an inclined ramp portion having a first end adjacent an edge of said recessed portion and a second end recessed in said blocking pin for retaining said toothed element in a second position relative to said friction element; and locking means resiliently retained in said toothed element and urged into frictional engagement with each of said blocking pins for cooperating with said recessed portions and said ramp portions to releasably retain said toothed element in one of said first and second positions.
a toothed element rotatable with an output shaft and adapted to be selectively engaged with a gear drive means for rotating the output shaft;
a synchronizing friction element rotatable with said toothed element and adapted to be selectively engaged with a friction face of said gear drive means;
a plurality of blocking pins for slidably mounting said toothed element axially with respect to said friction element, each of said blocking pins including a recessed portion for retaining said toothed element in a first position relative to said friction element and an inclined ramp portion having a first end adjacent an edge of said recessed portion and a second end recessed in said blocking pin for retaining said toothed element in a second position relative to said friction element; and locking means resiliently retained in said toothed element and urged into frictional engagement with each of said blocking pins for cooperating with said recessed portions and said ramp portions to releasably retain said toothed element in one of said first and second positions.
2. The invention defined in Claim 1 wherein said toothed element includes an outer annular channel portion, a generally flat central portion, and an inner annular sleeve portion, said annular sleeve portion having means for securing said toothed element to the output shaft for rotation therewith and means for engaging said gear drive means for rotating the output shaft.
3. The invention defined in Claim 1 wherein each of said blocking pins is secured at one end to said friction element and slidably maintained in an aperture formed in said toothed element for slidably mounting said toothed element axially with respect to said friction element.
4. The invention defined in Claim 1 wherein said recessed portion of each of said blocking pins is formed in a central region thereof and said inclined ramp portion of each of said blocking pins extends longitudinally along said blocking pin toward said friction element.
5. The invention defined in Claim 1 wherein said locking means includes an outwardly-extending aperture formed in said toothed element for each of said blocking pins, a detent means slidably maintained in each of said apertures, and means for resiliently urging each of said detent means outwardly of said apertures into engagement with said recessed portions and said ramp portions of said blocking pins.
6. The invention defined in Claim 1 wherein said ramp portion is inclined at an angle of twelve degrees.
7. A synchronized transmission assembly comprising:
a toothed element rotatable with an output shaft and adapted to be selectively engaged with a first gear drive means for rotating the output shaft at a first speed ratio and a second gear drive means for rotating the output shaft at a second speed ratio;
first and second synchronizing friction elements rotatable with said toothed element, each of said friction elements disposed on opposing ends coaxially of said toothed element and adapted to be selectively engaged with respective first and second frictional faces of said first and second gear drive means;
a plurality of blocking pins for slidably mounting said toothed element axially with respect to said friction elements, each of said blocking pins extending from a first end attached to said first frictional element through a respective aperture formed in said toothed element to a second end attached to said second frictional element;
each of said blocking pins further including a recessed portion for retaining said toothed element in a first position relative to said friction elements wherein said friction elements are out of contact with said friction faces of said gear drive means, a first inclined ramp portion having a first end adjacent one edge of said recessed portion and a second end recessed in said blocking pin for retaining said toothed element in a second position closer to said first friction element and in engagement with said first gear drive means, and a second inclined ramp portion having a first end adjacent another edge of said recessed portion and a second end recessed in said blocking pin for retaining said toothed element in a third position closer to said second friction element and in engagement with said second gear drive means; and locking means resiliently retained in said toothed element and urged into frictional engagement with each of said blocking pins for cooperating with said recessed portions and said first and second ramp portions to releasably retain said toothed element in one of said first, second, and third positions.
a toothed element rotatable with an output shaft and adapted to be selectively engaged with a first gear drive means for rotating the output shaft at a first speed ratio and a second gear drive means for rotating the output shaft at a second speed ratio;
first and second synchronizing friction elements rotatable with said toothed element, each of said friction elements disposed on opposing ends coaxially of said toothed element and adapted to be selectively engaged with respective first and second frictional faces of said first and second gear drive means;
a plurality of blocking pins for slidably mounting said toothed element axially with respect to said friction elements, each of said blocking pins extending from a first end attached to said first frictional element through a respective aperture formed in said toothed element to a second end attached to said second frictional element;
each of said blocking pins further including a recessed portion for retaining said toothed element in a first position relative to said friction elements wherein said friction elements are out of contact with said friction faces of said gear drive means, a first inclined ramp portion having a first end adjacent one edge of said recessed portion and a second end recessed in said blocking pin for retaining said toothed element in a second position closer to said first friction element and in engagement with said first gear drive means, and a second inclined ramp portion having a first end adjacent another edge of said recessed portion and a second end recessed in said blocking pin for retaining said toothed element in a third position closer to said second friction element and in engagement with said second gear drive means; and locking means resiliently retained in said toothed element and urged into frictional engagement with each of said blocking pins for cooperating with said recessed portions and said first and second ramp portions to releasably retain said toothed element in one of said first, second, and third positions.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US50904583A | 1983-06-29 | 1983-06-29 | |
| US509,045 | 1983-06-29 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1210963A true CA1210963A (en) | 1986-09-09 |
Family
ID=24025067
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000455741A Expired CA1210963A (en) | 1983-06-29 | 1984-06-04 | Blocking pin for a transmission synchronizer assembly |
Country Status (11)
| Country | Link |
|---|---|
| KR (1) | KR850000616A (en) |
| AU (1) | AU558262B2 (en) |
| BR (1) | BR8402929A (en) |
| CA (1) | CA1210963A (en) |
| DE (1) | DE3421473A1 (en) |
| ES (1) | ES8605625A1 (en) |
| FR (1) | FR2548316A1 (en) |
| GB (1) | GB2142390B (en) |
| IT (1) | IT1177859B (en) |
| NL (1) | NL8401880A (en) |
| SE (1) | SE455433B (en) |
Families Citing this family (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2184177A (en) * | 1985-12-14 | 1987-06-17 | Ford Motor Co | Gear-shift clutch mechanism for change-speed gearboxes |
| US5085303A (en) * | 1990-10-01 | 1992-02-04 | New Venture Gear, Inc. | Drag-free strut-type synchronizer |
| US5161423A (en) * | 1990-12-24 | 1992-11-10 | Eaton Corporation | Self-energizing synchronizer for equalizing shift time and effort of a multi-ratio transmission |
| US5097930A (en) * | 1990-12-24 | 1992-03-24 | Eaton Corporation | Pre-energizer for a synchronizer |
| US5111922A (en) * | 1990-12-24 | 1992-05-12 | Eaton Corporation | Pre-energizer for a synchronizer |
| US5141087A (en) * | 1990-12-24 | 1992-08-25 | Eaton Corporation | Self-energizing synchronizer |
| US5086897A (en) * | 1990-12-24 | 1992-02-11 | Eaton Corporation | Pre-energizer pins for a synchronizer |
| GB9107771D0 (en) * | 1991-04-12 | 1991-05-29 | Eaton Corp | Synchroniser sliding sleeve |
| GB9322319D0 (en) * | 1993-10-29 | 1993-12-15 | Eaton Corp | Neutral position detent for synchronizer |
| DE4404093C2 (en) * | 1994-02-09 | 1996-08-14 | Porsche Ag | Device for switching a transmission via a synchronization device |
| JP3161244B2 (en) * | 1994-08-26 | 2001-04-25 | トヨタ自動車株式会社 | Transmission synchronization device |
| US5785162A (en) * | 1997-01-16 | 1998-07-28 | Ford Global Technologies, Inc. | Re-indexing manual transmission synchronizer |
| US5901824A (en) * | 1997-08-11 | 1999-05-11 | Eaton Corporation | Synchronizer including radially-moveable self-energizing member |
| US5901823A (en) * | 1997-08-11 | 1999-05-11 | Eaton Corporation | Synchronizer including radially-moveable, resiliently-biased self-energizing member |
| CN102494048A (en) * | 2011-12-01 | 2012-06-13 | 中国重汽集团济南动力有限公司 | Synchronous structure for twin countershaft transmission |
| DE102013218241A1 (en) | 2013-09-12 | 2015-03-26 | Zf Friedrichshafen Ag | Claw switching element comprising a sliding sleeve for an automatic transmission of a motor vehicle |
| DE102016220702B4 (en) * | 2016-10-21 | 2018-05-24 | Schaeffler Technologies AG & Co. KG | Apparatus and method for synchronizing |
| CN112539227B (en) * | 2019-09-23 | 2022-07-15 | 比亚迪股份有限公司 | Synchronous system and vehicle that has it |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR752115A (en) * | 1933-03-07 | 1933-09-16 | Automobiles Unic Soc Nouv | Synchronization device for speed change gears |
| US2384439A (en) * | 1943-06-26 | 1945-09-11 | Borg Warner | Transmission |
| GB580513A (en) * | 1944-09-16 | 1946-09-10 | Humber Ltd | Improvements relating to synchro-mesh change-speed gearing |
| US2425203A (en) * | 1944-10-17 | 1947-08-05 | Dana Corp | Synchronizing clutch |
| GB884236A (en) * | 1959-08-13 | 1961-12-13 | Zahnradfabrik Friedrichshafen | Improvements in or relating to change speed gear boxes |
| US3270843A (en) * | 1964-05-04 | 1966-09-06 | Ford Motor Co | Synchronizer clutch assembly |
| DE2510657A1 (en) * | 1975-03-12 | 1976-09-23 | Helmut Droeschel | Synchronizing ring for gear wheel coupling - has friction taper on secondary rings to produce drive and axial gear teeth |
-
1984
- 1984-06-04 AU AU29013/84A patent/AU558262B2/en not_active Ceased
- 1984-06-04 CA CA000455741A patent/CA1210963A/en not_active Expired
- 1984-06-04 GB GB08414192A patent/GB2142390B/en not_active Expired
- 1984-06-08 DE DE3421473A patent/DE3421473A1/en not_active Withdrawn
- 1984-06-14 NL NL8401880A patent/NL8401880A/en not_active Application Discontinuation
- 1984-06-15 BR BR8402929A patent/BR8402929A/en unknown
- 1984-06-27 KR KR1019840003659A patent/KR850000616A/en not_active Application Discontinuation
- 1984-06-27 ES ES533769A patent/ES8605625A1/en not_active Expired
- 1984-06-28 FR FR8410231A patent/FR2548316A1/en not_active Withdrawn
- 1984-06-28 SE SE8403443A patent/SE455433B/en not_active IP Right Cessation
- 1984-06-29 IT IT48485/84A patent/IT1177859B/en active
Also Published As
| Publication number | Publication date |
|---|---|
| GB2142390A (en) | 1985-01-16 |
| SE8403443L (en) | 1984-12-30 |
| KR850000616A (en) | 1985-02-28 |
| SE455433B (en) | 1988-07-11 |
| ES8605625A1 (en) | 1986-03-16 |
| BR8402929A (en) | 1985-05-28 |
| AU2901384A (en) | 1985-01-03 |
| GB8414192D0 (en) | 1984-07-11 |
| FR2548316A1 (en) | 1985-01-04 |
| ES533769A0 (en) | 1986-03-16 |
| IT8448485A0 (en) | 1984-06-29 |
| DE3421473A1 (en) | 1985-01-03 |
| GB2142390B (en) | 1986-09-17 |
| AU558262B2 (en) | 1987-01-22 |
| IT1177859B (en) | 1987-08-26 |
| SE8403443D0 (en) | 1984-06-28 |
| NL8401880A (en) | 1985-01-16 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |