CN112524170A - Transmission synchronizing mechanism, gear shifting system, gear shifting method and transmission - Google Patents
Transmission synchronizing mechanism, gear shifting system, gear shifting method and transmission Download PDFInfo
- Publication number
- CN112524170A CN112524170A CN202011522539.5A CN202011522539A CN112524170A CN 112524170 A CN112524170 A CN 112524170A CN 202011522539 A CN202011522539 A CN 202011522539A CN 112524170 A CN112524170 A CN 112524170A
- Authority
- CN
- China
- Prior art keywords
- engaging
- tooth
- gear
- sleeve
- face
- 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.)
- Pending
Links
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
- 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
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
- F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
- F16H61/0204—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
- F16H61/0213—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal characterised by the method for generating shift signals
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The application provides a synchronizing mechanism, a gear shifting system, a gear shifting method and a transmission of the transmission, and belongs to the technical field of transmissions. The synchronizing mechanism includes an engaging ring gear and an engaging sleeve. A plurality of first engaging teeth are circumferentially arranged at intervals on one side of the engaging ring gear in the axial direction. And a plurality of second engaging teeth are arranged on one axial side of the engaging sleeve at intervals. The first engaging tooth is provided with a first contra-tooth side face, a first consequent tooth side face, a first end face and a first chamfer face, wherein the first contra-tooth side face is connected with the first end face, and the first end face is connected with the first consequent tooth side face through the first chamfer face. The second engaging tooth has a second inverted tooth flank surface, a second consequent tooth flank surface, a second end surface and a second chamfer surface, the second inverted tooth flank surface is connected with the second end surface, and the second end surface is connected with the second consequent tooth flank surface through the second chamfer surface. The second chamfer surface is used for being in contact fit with the first chamfer surface when the joint sleeve moves axially. The synchronous mechanism of the transmission with the structure eliminates the inverse tooth engagement process and shortens the whole shifting time.
Description
Technical Field
The application relates to the technical field of transmissions, in particular to a synchronizing mechanism, a gear shifting system, a gear shifting method and a transmission of the transmission.
Background
At present, in a synchronous mechanism of a transmission, generally, a joint sleeve moves on a power shaft, so that a plurality of joint teeth on the joint sleeve are meshed with a plurality of joint teeth on a joint gear ring, so that the joint sleeve and the joint gear ring rotate synchronously, and the joint gear ring which is idle along with a transmission gear on the power shaft rotates synchronously with the power shaft, so that the transmission gear and the power shaft rotate synchronously.
In the prior art, both the engaging teeth on the engaging sleeve and the engaging teeth on the engaging gear ring adopt a double-sided chamfer structure, when the gear is shifted (the engaging sleeve moves on a power shaft), the engaging teeth on the engaging sleeve and the engaging teeth on the engaging gear ring are engaged with each other along the teeth possibly, or engaged with each other in an inverted manner, the engaging time of the along teeth is short, the engaging time of the inverted teeth is long, the engaging time of the inverted teeth is relatively engaged with the along teeth, the engaging time is obviously increased, the total time of the gear shifting process is prolonged, the power interruption time is prolonged, and the dynamic property of the transmission is influenced.
Disclosure of Invention
The embodiment of the application provides a synchronous mechanism, a gear shifting system, a gear shifting method and a transmission of the transmission, and aims to solve the problem that the double-edge chamfering structure of an engaging tooth is long in gear shifting time.
In a first aspect, embodiments of the present application provide a synchronizing mechanism of a transmission, including an engaging ring gear and an engaging sleeve;
a plurality of first engaging teeth are arranged on one side of the engaging gear ring in the axial direction at intervals;
a plurality of second engaging teeth are arranged on one side of the engaging sleeve in the axial direction at intervals, the engaging sleeve is coaxially arranged with the engaging gear ring, and the engaging sleeve is used for enabling the plurality of second engaging teeth to be meshed with the plurality of first engaging teeth when moving in the axial direction so as to enable the engaging sleeve and the engaging gear ring to rotate synchronously;
the first engaging tooth is provided with a first contra-tooth side face, a first consequent tooth side face, a first end face and a first chamfer face, the first contra-tooth side face and the first consequent tooth side face are respectively positioned at two sides of the first engaging tooth in the circumferential direction of the engaging gear ring, the first consequent tooth side face is connected with the first end face, and the first end face is connected with the first contra-tooth side face through the first chamfer face;
the second engaging tooth is provided with a second inverse tooth side surface, a second consequent tooth side surface, a second end surface and a second chamfer surface, the second inverse tooth side surface and the second consequent tooth side surface are respectively positioned at two sides of the second engaging tooth in the circumferential direction of the engaging sleeve, the second consequent tooth side surface is connected with the second end surface, and the second end surface is connected with the second inverse tooth side surface through the second chamfer surface;
the second chamfer surface is used for being in contact fit with the first chamfer surface when the joint sleeve moves axially.
In the above technical solution, the first engaging tooth that engages the ring gear has only the first chamfered surface, and the second engaging tooth has only the second chamfered surface, that is, both the first engaging tooth and the second engaging tooth adopt single-side chamfered engagement. During gear shifting (the engaging sleeve moves axially to a direction close to the engaged gear ring), three engaging conditions can occur, namely, the first chamfer surface is contacted with the second chamfer surface, namely, the first chamfer surface is engaged with the second chamfer surface along the teeth, and the engaging time is short; the other is that the first end surface is contacted with the second end surface, namely, the flat teeth are jointed, the jointing gear ring can quickly skip the process of the flat teeth jointing and is transited to the process of the straight teeth jointing in the rotating process, and the jointing time of the flat teeth is shorter; still another is that the first engaging teeth are directly engaged with the second engaging teeth. In addition, during gear shifting, no matter whether the gear is engaged with the straight teeth or the flat teeth, the situation that the engaging sleeve jacks back does not occur. The synchronous mechanism of the transmission with the structure eliminates the inverse tooth engagement process and shortens the whole shifting time. After shifting, the first plurality of engaging teeth mesh with the second plurality of engaging teeth, the first and second inverted tooth flanks are both longer, and the first and second inverted tooth flanks have less distributed stress.
In some embodiments, the first end face is perpendicular to the axis of the engaged ring gear;
the second end face is perpendicular to an axis of the adapter sleeve.
In the above technical scheme, because the first end face and the second end face are respectively perpendicular to the axis of the joint gear ring and the axis of the joint sleeve, and the joint gear ring and the joint sleeve are coaxially arranged, the first end face is parallel to the second end face, and under the condition that the lengths of the first chamfer face and the second chamfer face are fixed, the lengths of the first end face and the second end face are shorter, so that the flat tooth joint time of the first joint tooth and the second joint tooth can be further shortened.
In some embodiments, the first chamfer surface and the second chamfer surface are both planar;
in the technical scheme, the first chamfer surface and the second chamfer surface are planes, so that the forming processing is convenient.
In some embodiments, the first chamfer surface forms a first included angle with the axis of the engaging gear ring;
the second chamfer surface and the axis of the joint sleeve form a second included angle;
the first included angle is equal to the second included angle.
In the technical scheme, a first included angle formed by the first chamfer surface and the axis of the joint gear ring is equal to a second included angle formed by the second chamfer surface and the axis of the joint sleeve, and the structure enables the first joint tooth to be in contact with the second joint tooth surface when the gear is engaged with the gear, so that the first joint tooth and the second joint tooth are more stable in the engaging process.
In some embodiments, the first chamfer surface and the second chamfer surface are coplanar with the first end surface and the second end surface, respectively.
In the technical scheme, the first chamfer surface and the second chamfer surface are coplanar with the first end surface and the second end surface respectively, so that a flat tooth engagement process in a gear shifting process is eliminated, and the gear shifting time is further shortened.
In some embodiments, the first chamfer surface and the second chamfer surface are both arc surfaces.
In the technical scheme, the first chamfer surface and the second chamfer surface are both arc surfaces, and when the tooth is engaged with the tooth, the first engaging tooth and the second engaging tooth are in line contact, so that the first engaging tooth and the second engaging tooth are engaged more easily, namely the second engaging tooth is clamped into a gap between two adjacent first engaging teeth more easily.
In some embodiments, the first contra-tooth flank and the first cis-tooth flank are distributed in an "octant" shape such that the first engaging tooth has a first large end and a first small end, the first small end being closer to the engaging ring gear than the first large end;
the second contra-tooth flank and the second consequent-tooth flank are distributed in an "octagon" shape so that the second engaging tooth has a second large end and a second small end, the second small end being closer to the engaging sleeve than the second large end.
In the above-mentioned scheme, first contrary flank with first be in the same direction as the flank and personally submit "eight" shape and distribute, the second is contrary flank and second and is in the same direction as the flank and personally submit "eight" shape and distribute for behind a plurality of first joint teeth and a plurality of second joint teeth meshing, first joint tooth and the mutual locking of second joint tooth make the second joint tooth card difficult for withdrawing from behind two adjacent first joint teeth, the difficult condition that takes off the shelves that appears.
In a second aspect, an embodiment of the present application further provides a gear shifting system, including:
the above-described synchronizing mechanism of the transmission;
first detecting means for detecting first rotational angle information of the engaged ring gear;
second detection means for detecting second rotational speed rotational angle information of the clutch collar;
a controller for adjusting a rotation speed rotation angle of the engaging sleeve according to the first rotation speed rotation angle information and the second rotation speed rotation angle information to reduce a relative rotation speed rotation angle between the engaging ring gear and the engaging sleeve to a preset value;
and the gear shifting mechanism is used for driving the joint sleeve to axially move when the relative rotation speed rotation angle between the joint gear ring and the joint sleeve reaches the preset value so as to realize gear shifting.
In the above scheme, the first detection device and the second detection device can respectively detect the rotation speed rotation angles of the engaging gear ring and the engaging sleeve, and the controller can reduce the relative rotation speed between the engaging gear ring and the engaging sleeve to a preset value according to the rotation speed information detected by the first detection device and the second detection device.
In a third aspect, an embodiment of the present application provides a gear shifting method, which is applied to the gear shifting system described above, and includes:
acquiring the contact condition of the second engaging teeth and the first engaging teeth when the engaging sleeve is driven to move by the gear shifting mechanism in the gear shifting process according to the first rotating speed rotating angle information and the second rotating speed rotating angle information;
if the second end surface is in contact with the first end surface, controlling the gear shifting mechanism to unload so that the gear shifting force applied to the joint sleeve by the gear shifting mechanism is zero;
and if the first chamfer surface is in contact with the second chamfer surface, controlling the gear shifting mechanism to continue to be loaded so as to enable the plurality of second joint teeth to be meshed with the plurality of first joint teeth, and realizing gear shifting.
In the above scheme, during the gear shifting process, if the first end surface of the first engaging tooth is in contact with the second end surface of the second engaging tooth, the gear shifting mechanism is unloaded, so that the gear shifting force applied to the engaging sleeve by the gear shifting mechanism is zero, the friction force between the first end surface and the second end surface (the tangential friction force between the first engaging tooth and the second engaging tooth) is small, the engaging sleeve and the engaging gear ring can rapidly rotate by an angle under the inertia effect of relative speed, the first engaging tooth and the second engaging tooth are in sequential tooth contact, and the time of the plane contact process is shortened. Meanwhile, the inter-tooth collision when the first engaging tooth is engaged with the second engaging tooth is reduced, so that the gear shifting process is more stable.
In a fourth aspect, embodiments of the present application further provide a transmission including the synchronization mechanism of the transmission described above.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present application and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained from the drawings without inventive effort.
Fig. 1 is a schematic structural diagram of a synchronization mechanism of a speed reducer in the prior art provided in an embodiment of the present application;
FIG. 2 is a force analysis graph of the engaging teeth of the engaging sleeve and the engaging teeth of the engaging gear ring in clockwise engagement according to the prior art provided by the embodiment of the present application;
FIG. 3 is a force analysis diagram of the engaging teeth of the engaging sleeve and the engaging teeth of the engaging ring gear in the reverse tooth engagement according to the prior art provided in the embodiment of the present application;
FIG. 4 is a schematic structural diagram of a synchronizing mechanism of a speed reducer according to an embodiment of the present disclosure;
fig. 5 is a schematic structural view of a synchronizing mechanism of a speed reducer according to a first embodiment of the present application;
fig. 6 is a schematic structural view of a synchronizing mechanism of a speed reducer according to a second embodiment of the present application;
fig. 7 is a schematic structural view of a synchronizing mechanism of a speed reducer according to a third embodiment of the present application;
fig. 8 is a schematic structural view of a synchronizing mechanism of a speed reducer according to a fourth embodiment of the present application;
fig. 9 is a schematic structural view of a synchronizing mechanism of a speed reducer according to a fifth embodiment of the present application;
FIG. 10 is a schematic block diagram of a gear shifting system provided in accordance with certain embodiments of the present application;
FIG. 11 is a logic diagram of a shift method provided by an embodiment of the present application.
Icon: 10-a power shaft; 20-a synchronizer; 30-a transmission gear; 40-engaging the ring gear; 41-a first engaging tooth; 411-first contra-tooth flank; 412-first flank; 413 — a first end face; 414 — a first chamfer face; 50-a joint sleeve; 51-a second engagement tooth; 511-second contra-flank; 512-second flank; 513 — a second end face; 514-second chamfer face; 100-a synchronization mechanism; 200-a gear shift system; 210-a first detection device; 220-a second detection device; 230-a controller; 240-a gear shift mechanism; 241-a shift motor; 242-a shift actuator; 250-a motor; 260-control unit.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are some but not all of the embodiments of the present application. The components of the embodiments of the present application, generally described and illustrated in the figures herein, can be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the present application, presented in the accompanying drawings, is not intended to limit the scope of the claimed application, but is merely representative of selected embodiments of the application. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, it need not be further defined and explained in subsequent figures.
In the description of the embodiments of the present application, it should be noted that the indication of orientation or positional relationship is based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship which is usually placed when the product of the application is used, or the orientation or positional relationship which is usually understood by those skilled in the art, or the orientation or positional relationship which is usually placed when the product of the application is used, and is only for the convenience of describing the application and simplifying the description, but does not indicate or imply that the indicated device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the application. Furthermore, the terms "first" and "second" are used merely to distinguish one description from another, and are not to be construed as indicating or implying relative importance.
As shown in fig. 1, in a synchronizing mechanism 100 of a transmission, a synchronizer 20, a transmission gear 30 and a joint ring gear 40 are arranged on a power shaft 10, the joint ring gear 40 is fixed on the transmission gear 30, the transmission gear 30 and the joint ring gear 40 are both sleeved outside the power shaft 10 and can idle relative to the power shaft 10, namely, the power shaft 10 can rotate relative to the transmission gear 30, the transmission gear 30 can also rotate relative to the power shaft 10, the synchronizer 20 comprises a joint sleeve 50, the joint sleeve 50 is connected with the power shaft 10 through a spline, and the joint sleeve 50 can axially move relative to the power shaft 10 and cannot rotate relative to the power shaft 10. During gear shifting, the engaging sleeve 50 is shifted by a gear shifting mechanism (not shown in fig. 1) to move relative to the power shaft 10, so that engaging teeth on the engaging sleeve 50 are engaged with engaging teeth on the engaging gear ring 40, the engaging sleeve 50 and the engaging gear ring 40 rotate synchronously, the engaging gear ring 40 which is originally idle-rotated on the power shaft 10 along with the transmission gear 30 rotates synchronously with the power shaft 10, and the transmission gear 30 and the power shaft 10 rotate synchronously.
In the prior art, as shown in fig. 2 and 3, the engaging teeth on the engaging sleeve 50 and the engaging gear ring 40 are both in double-sided chamfer engagement, and during gear shifting, the engaging sleeve 50 moves on the power shaft 10, and the engaging teeth on the engaging sleeve 50 and the engaging teeth on the engaging gear ring 40 may be in sequential engagement, as shown in fig. 2; reverse tooth engagement may also occur, as shown in FIG. 3; it is also possible that the engaging teeth of the engaging sleeve 50 directly mesh with the engaging teeth of the engaging ring gear 40 (not shown). The clockwise engagement and the counterclockwise engagement are analyzed in detail below.
In fig. 2 and 3, the shifting force is FsThe tooth tip chamfer is α, the tooth surface friction coefficient is μ, ω is the relative rotational speed difference between the engaging sleeve 50 and the engaging ring gear 40, and ν is the moving direction of the engaging sleeve 50.
As shown in fig. 2, for a straight-tooth engagement, the force down the chamfer face is:
Finclined plane＝Fs cosα-μFs sinα；
The force resisting the shift is: fs-re＝Fs sin2α+μFs sinαcosα。
As shown in fig. 3, for the inverse tooth engagement, there is an additional reaction force in the direction perpendicular to the chamfered surface, which is caused by the opposite movement direction of the engagement ring gear 40 and the engagement sleeve 50, so that the larger the load or inertia at the end of the engagement ring gear 40, the larger the reaction force.
The force down the chamfer is:
Finclined plane＝Fs cosα-μFs sinα；
The force resisting the shift becomes:
Fs-re＝Fs sin2α+μFs sinαcosα+Fsupport reaction forcesinα。
By comparing the two contact conditions, the force F causing the engaging sleeve 50 to slide into engagement with the ring gear 40Inclined planeForce F against shifting, remaining unchanged, but under contra-tooth engagements-reAs a result, the speed at which the sleeve 50 slides into engagement with the ring gear 40 becomes slower, resulting in a longer reverse engagement time. In particular, when Fs-re＞FsAt this time, the engaging sleeve 50 is retreated, and after the engaging ring gear 40 is retreated from the engagement, the engaging ring gear 40 rotates by an angle to become the engagement with the teeth, and the time of the process is far longer than that of the engagement with the teeth.
From the above analysis, it can be seen that in the prior art, the engagement time is significantly increased in the case of the contra-tooth engagement as compared to the consequent-tooth engagement, resulting in an extended total time for the shifting process and an extended power interruption time, which affect the dynamic performance of the vehicle.
In view of this, the embodiment of the present application provides a synchronous mechanism 100 of a transmission, in which the engaging teeth of the engaging ring gear 40 and the engaging teeth of the engaging sleeve 50 both adopt a single-side chamfer structure, so as to eliminate the engagement of the reverse teeth and shorten the whole shifting time.
As shown in fig. 4, the synchronizing mechanism 100 of the transmission includes an engaging ring gear 40 and an engaging sleeve 50. The engaging ring gear 40 is used for connection with the transmission gear 30, and a plurality of first engaging teeth 41 are circumferentially provided at intervals on one side of the engaging ring gear 40 in the axial direction. A plurality of second engaging teeth 51 are circumferentially arranged at intervals on one axial side of the engaging sleeve 50, the engaging sleeve 50 is coaxially arranged with the engaging gear ring 40, and the engaging sleeve 50 is used for enabling the plurality of second engaging teeth 51 to be meshed with the plurality of first engaging teeth 41 when moving axially so as to enable the engaging sleeve 50 and the engaging gear ring 40 to rotate synchronously;
the first engaging tooth 41 has a first inverted tooth side 411, a first consequent tooth side 412, a first end face 413 and a first chamfered face 414, the first inverted tooth side 411 and the first consequent tooth side 412 are respectively located on two sides of the first engaging tooth 41 in the circumferential direction of the engaging ring gear 40, the first inverted tooth side 411 is connected with the first end face 413, and the first end face 413 is connected with the first consequent tooth side 412 through the first chamfered face 414; the second engaging tooth 51 has a second inverted tooth flank surface 511, a second straight tooth flank surface 512, a second end surface 513, and a second chamfer surface 514, the second inverted tooth flank surface 511 and the second straight tooth flank surface 512 are respectively located on both sides of the second engaging tooth 51 in the circumferential direction of the engaging sleeve 50, the second inverted tooth flank surface 511 is connected to the second end surface 513, and the second end surface 513 is connected to the second straight tooth flank surface 512 via the second chamfer surface 514. The second chamfered surface 514 is adapted to engage in contact with the first chamfered surface 414 upon axial movement of the clutch collar 50.
As can be seen from the above structure, the first engaging tooth 41 engaging the ring gear 40 has only one first chamfered surface 414, and the second engaging tooth 51 has only one second chamfered surface 514, i.e., the first engaging tooth 41 and the second engaging tooth 51 are both engaged by a single-sided chamfer. During gear shifting (the engaging sleeve 50 moves axially closer to the engaged ring gear 40), three engagement conditions occur, one is that the first chamfered surface 414 contacts the second chamfered surface 514, i.e., the clockwise engagement, and the engagement time is short; the other is that the first end face 413 is in contact with the second end face 513, namely, the first end face is in flat tooth engagement, the engagement gear ring 40 can rapidly skip the flat tooth engagement process and transition to the straight tooth engagement during the rotation process, and the flat tooth engagement time is short; still another is that the first engaging teeth 41 are directly engaged with the second engaging teeth 51. Further, during shifting, neither the straight engagement nor the flat engagement occurs, and the sleeve 50 does not lift back. The synchronization mechanism 100 of the transmission of this structure eliminates the reverse tooth engagement process, shortening the entire shift time. After the gear shift, the plurality of first engaging teeth 41 are engaged with the plurality of second engaging teeth 51, the first inverted tooth flank 411 and the second inverted tooth flank 511 are both longer than the conventional double-sided chamfered tooth flank, and the first inverted tooth flank 411 and the second inverted tooth flank 511 have less distributed stress.
Wherein, in fig. 4, the first contra-tooth flank 411 is oriented in the rotational direction of the engaging ring gear 40, and the first consequent-tooth flank 412 is oriented in the rotational direction of the engaging ring gear 40; the second contra-tooth flank 511 is oriented in the direction of rotation of the engaging ring gear 40 and the second consequent-tooth flank 512 is oriented in the direction of rotation of the engaging ring gear 40.
It should be noted that, the plurality of first engaging teeth 41 and the plurality of second engaging teeth 51 are engaged, and it is understood that each first engaging tooth 41 is snapped into the gap between two adjacent second engaging teeth 51, and each second engaging tooth 51 is snapped into the gap between two adjacent first engaging teeth 41.
In some embodiments, with continued reference to FIG. 4, the first end face 413 is perpendicular to an axis engaging the ring gear 40; second end face 513 is perpendicular to the axis of sleeve 50. Since the engaging ring gear 40 and the engaging sleeve 50 are coaxially arranged, it can be understood that the first end face 413 and the second end face 513 are arranged in parallel, and under the condition that the lengths of the first chamfer face 414 and the second chamfer face 514 are fixed, the lengths of the first end face 413 and the second end face 513 are shorter, and the flat tooth engaging time of the first engaging tooth 41 and the second engaging tooth 51 can be further shortened.
Of course, in some embodiments, as shown in FIG. 5, the first end face 413 may also be disposed at an acute angle relative to the axis joining the ring gear 40; second end face 513 may also be disposed at an acute angle with respect to the axis of engaging sleeve 50.
In some embodiments, as shown in fig. 4 and 5, the first chamfer 414 and the second chamfer 514 are both planar, which facilitates the forming of the first chamfer 414 and the second chamfer 514.
Optionally, the first chamfer surface 414 forms a first included angle with the axis of the engagement gear ring 40; the second chamfer surface 514 forms a second included angle with the axis of the engaging sleeve 50, and the first included angle is equal to the second included angle. This structure allows the first engaging tooth 41 to come into surface contact with the second engaging tooth 51 at the time of the clockwise engagement, so that the first engaging tooth 41 and the second engaging tooth 51 are more smoothly engaged during the engagement.
In the case where the first end surface 413 and the axis of the engagement ring gear 40 are arranged at an acute angle, and the second end surface 513 and the axis of the engagement sleeve 50 are arranged at an acute angle, the inclination angle of the first end surface 413 and the inclination angle of the first chamfered surface 414 may be different, and the inclination angle of the second end surface 513 and the inclination angle of the second chamfered surface 514 may be different, as shown in fig. 5; of course, in some embodiments, as shown in fig. 6, the inclination angle of the first end surface 413 and the inclination angle of the first chamfered surface 414 may be the same, and the inclination angle of the second end surface 513 and the inclination angle of the second chamfered surface 514 may be the same, so that the first end surface 413 and the first chamfered surface 414 are coplanar, and the second end surface 513 and the second chamfered surface 514 are coplanar, which eliminates the flat tooth engagement process during the gear shifting process, and further shortens the gear shifting time.
Of course, in addition to the first chamfer surface 414 and the second chamfer surface 514 being flat surfaces, in some embodiments, as shown in fig. 7 and 8, the first chamfer surface 414 and the second chamfer surface 514 are both arc surfaces. In the tooth following engagement, the first engaging tooth 41 and the second engaging tooth 51 are in line contact, so that the first engaging tooth 41 and the second engaging tooth 51 are more easily engaged, and the second engaging tooth 51 is more easily snapped into the gap between the adjacent two first engaging teeth 41.
In the present embodiment, as shown in fig. 7, the first end face 413 may be perpendicular to the axis of the engaging ring gear 40, and the second end face 513 may be perpendicular to the axis of the engaging sleeve 50; of course, as shown in fig. 8, the first end face 413 may be disposed at an acute angle to the axis of the engagement ring 40, and the second end face 513 may be disposed at an acute angle to the axis of the engagement sleeve 50.
It should be noted that in some embodiments of the present application, first contra-tooth flank 411 and first consequent-tooth flank 412 may each be parallel to the axis of engaging ring gear 40, and second contra-tooth flank 511 and second consequent-tooth flank 512 may each be arranged parallel to the axis of engaging sleeve 50, as shown in fig. 4-8.
Of course, in some embodiments, the first contra-tooth flank 411 and the first consequent flank 412 may each be disposed at an angle to the axis of the engaging ring 40, and the second contra-tooth flank 511 and the second consequent flank 512 may each be disposed at an angle to the axis of the engaging sleeve 50.
Illustratively, as shown in fig. 9, the first contra-tooth flank 411 and the first consequent flank 412 are distributed in an "eight" shape such that the first engaging tooth 41 has a first large end and a first small end, the first small end being closer to the engaging ring gear 40 than the first large end; the second contra-tooth flank 511 and the second consequent-tooth flank 512 are distributed in an "eight" shape so that the second engaging tooth 51 has a second large end and a second small end, the second small end being closer to the engaging sleeve 50 than the second large end. With the structure, after the plurality of first engaging teeth 41 are meshed with the plurality of second engaging teeth 51, the first engaging teeth 41 and the second engaging teeth 51 are locked with each other, so that the second engaging teeth 51 are clamped into two adjacent first engaging teeth 41 and are not easy to withdraw, and the gear is not easy to be disengaged.
The embodiment of the application also provides a transmission, and the transmission comprises the synchronization mechanism 100 of the transmission provided by any one of the embodiments.
In addition, as shown in fig. 10, the embodiment of the present application further provides a gear shifting system 200, which includes a first detecting device 210, a second detecting device 220, a controller 230, a gear shifting mechanism 240, and the synchronizing mechanism 100 of the transmission in any one of the above embodiments.
The first detecting means 210 is for detecting first rotational angle information of the engaging ring gear 40. The second detection means 220 is for detecting second rotational speed rotational angle information of the engaging sleeve 50. The controller 230 is configured to adjust the rotation speed rotation angle of the engaging sleeve 50 based on the first rotation speed rotation angle information and the second rotation speed rotation angle information to reduce the relative rotation speed rotation angle between the engaging ring gear 40 and the engaging sleeve 50 to a preset value. The shift mechanism 240 is used to drive the engaging sleeve 50 to move axially when the relative rotational speed rotational angle between the engaging ring gear 40 and the engaging sleeve 50 reaches a preset value, so as to achieve shifting.
The first detecting device 210 and the second detecting device 220 can respectively detect the rotation speed rotation angles of the engaging ring gear 40 and the engaging sleeve 50, and the controller 230 can reduce the relative rotation speed between the engaging ring gear 40 and the engaging sleeve 50 to a preset value according to the rotation speed information detected by the first detecting device 210 and the second detecting device 220, in which case, the shifting mechanism 240 can drive the engaging sleeve 50 to move axially to realize shifting, so as to avoid the shifting mechanism 240 performing shifting action when the relative rotation speed between the engaging ring gear 40 and the engaging sleeve 50 is too high.
It should be noted that the relative rotational speed rotational angle between the ring gear 40 and the sleeve 50 is the rotational speed rotational angle difference between the ring gear 40 and the sleeve 50.
Optionally, the gear shifting system 200 further comprises a motor 250, the motor 250 is in driving connection with the coupling sleeve 50, and when the motor 250 is operated, the power shaft 10 and the coupling sleeve 50 will rotate together. The motor 250 is electrically connected to the controller 230.
Illustratively, the first detecting device 210 may be an encoder, and the encoder may be connected to an output shaft, a gear on the output shaft is meshed with the transmission gear 30 on the power shaft 10, and the information of the rotation speed and the rotation angle of the engagement ring gear 40 can be indirectly obtained through the encoder.
For example, the second detecting device 220 may be a motor resolver, which is connected to the motor 250 and can indirectly obtain the rotation angle information of the engaging sleeve 50 through the motor resolver.
For example, the controller 230 may be an MCU (micro controller Unit), and calculates the torque and the rotation speed that the motor 250 needs to output based on the first rotation speed angle information and the second rotation speed angle information detected by the first detecting device 210 and the second detecting device 220 to control the output of the motor 250 such that the relative rotation speed between the engaging ring gear 40 and the engaging sleeve 50 is reduced to a preset value, such that the rotation speed angles of both the engaging ring gear 40 and the engaging sleeve 50 are as close as possible.
Optionally, the gear shifting system 200 further comprises a control unit 260, wherein the control unit 260 is electrically connected with the controller 230 and the gear shifting mechanism 240, and is used for controlling the gear shifting mechanism 240 to drive the engaging sleeve 50 to axially move when the relative rotation speed rotation angle between the engaging ring gear 40 and the engaging sleeve 50 reaches a preset value, so as to realize gear shifting. Illustratively, the Control Unit 260 is a TCU (Transmission Control Unit, automatic Transmission Control Unit 260).
Illustratively, the shifting mechanism 240 includes a shifting motor 241 and a shifting actuator 242, the shifting motor 241 is electrically connected to the control unit 260, and the shifting motor 241 is used for driving the shifting actuator 242 to drive the engaging sleeve 50 to move axially to realize the shifting.
Furthermore, as shown in fig. 11, the embodiment of the present application further provides a shifting method, which is applied to the shifting system 200, and the method includes obtaining the contact condition between the second engaging teeth 51 and the first engaging teeth 41 when the shift mechanism 240 drives the engaging sleeve 50 to move during shifting according to the first rotational angle information and the second rotational angle information.
If the second end face 513 is in contact with the first end face 413, the shifting mechanism 240 is controlled to unload such that the shifting force applied to the engaging sleeve 50 by the shifting mechanism 240 is zero; if the first chamfer surface 414 contacts the second chamfer surface 514, the shift mechanism 240 is controlled to continue to be loaded to engage the plurality of second engagement teeth 51 with the plurality of first engagement teeth 41 to achieve the shift.
During shifting, if the first end face 413 of the first engaging tooth 41 contacts the second end face 513 of the second engaging tooth 51, the shifting mechanism 240 is unloaded, so that the shifting force applied to the sleeve 50 by the shifting mechanism 240 is zero, the friction force between the first end face 413 and the second end face 513 (the tangential friction force between the first engaging tooth 41 and the second engaging tooth 51) is small, the sleeve 50 and the engaging ring gear 40 can rotate rapidly through an angle under the inertia effect of the relative speed, the first engaging tooth 41 and the second engaging tooth 51 are in direct-tooth contact, and the time of the plane contact process is shortened. At the same time, the inter-tooth collision when the first engaging teeth 41 are engaged with the second engaging teeth 51 is reduced, making the shifting process more smooth.
Alternatively, the contact condition of the second engaging tooth 51 with the first engaging tooth 41 may be detected by a condition detecting device. For example, the detection device may be a pressure sensor disposed on the first end face 413 and/or the second end face 513.
The above description is only a preferred embodiment of the present application and is not intended to limit the present application, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, improvement and the like made within the spirit and principle of the present application shall be included in the protection scope of the present application.
Claims (10)
1. A synchronizing mechanism for a transmission, comprising:
the gear ring is connected with the gear ring in a rotating mode, and a plurality of first connecting teeth are arranged on one axial side of the gear ring at intervals; and
a plurality of second engaging teeth are circumferentially arranged on one axial side of the engaging sleeve at intervals, the engaging sleeve is coaxially arranged with the engaging gear ring, and the engaging sleeve is used for enabling the plurality of second engaging teeth to be meshed with the plurality of first engaging teeth when moving axially so as to enable the engaging sleeve and the engaging gear ring to rotate synchronously;
the first engaging tooth is provided with a first contra-tooth side face, a first consequent tooth side face, a first end face and a first chamfer face, the first contra-tooth side face and the first consequent tooth side face are respectively positioned at two sides of the first engaging tooth in the circumferential direction of the engaging gear ring, the first contra-tooth side face is connected with the first end face, and the first end face is connected with the first consequent tooth side face through the first chamfer face;
the second engaging tooth is provided with a second contra-tooth side surface, a second consequent tooth side surface, a second end surface and a second chamfer surface, the second contra-tooth side surface and the second consequent tooth side surface are respectively positioned at two sides of the second engaging tooth in the circumferential direction of the engaging sleeve, the second contra-tooth side surface is connected with the second end surface, and the second end surface is connected with the second consequent tooth side surface through the second chamfer surface;
the second chamfer surface is used for being in contact fit with the first chamfer surface when the joint sleeve moves axially.
2. The synchronizing mechanism of a transmission according to claim 1, characterized in that the first end face is perpendicular to an axis of the engaging ring gear;
the second end face is perpendicular to an axis of the adapter sleeve.
3. The synchronizing mechanism of a transmission according to claim 1, wherein the first chamfer surface and the second chamfer surface are both planar.
4. The synchronizing mechanism for a transmission according to claim 3, wherein the first chamfer is at a first angle with respect to the axis of the ring gear;
the second chamfer surface and the axis of the joint sleeve form a second included angle;
the first included angle is equal to the second included angle.
5. The synchronizing mechanism of a transmission according to claim 3, characterized in that the first chamfer surface and the second chamfer surface are coplanar with the first end surface and the second end surface, respectively.
6. The synchronizing mechanism of a transmission according to claim 1, wherein the first chamfer surface and the second chamfer surface are both circular arc surfaces.
7. The synchronizing mechanism for a transmission according to claim 1, wherein the first contra-tooth flank and the first cis-tooth flank are distributed in an "octant" shape so that the first engaging tooth has a first large end and a first small end, the first small end being closer to the engaging ring gear than the first large end;
the second contra-tooth flank and the second consequent-tooth flank are distributed in an "octagon" shape so that the second engaging tooth has a second large end and a second small end, the second small end being closer to the engaging sleeve than the second large end.
8. A gear shift system, comprising:
a synchronizing mechanism of a transmission according to any one of claims 1-7;
first detecting means for detecting first rotational angle information of the engaged ring gear;
second detection means for detecting second rotational speed rotational angle information of the clutch collar;
a controller for adjusting a rotation speed rotation angle of the engaging sleeve according to the first rotation speed rotation angle information and the second rotation speed rotation angle information to reduce a relative rotation speed rotation angle between the engaging ring gear and the engaging sleeve to a preset value;
and the gear shifting mechanism is used for driving the joint sleeve to axially move when the relative rotation speed rotation angle between the joint gear ring and the joint sleeve reaches the preset value so as to realize gear shifting.
9. A method of shifting a gear, adapted for use in the gear shifting system of claim 8, the method comprising:
acquiring the contact condition of the second engaging teeth and the first engaging teeth when the engaging sleeve is driven to move by the gear shifting mechanism in the gear shifting process according to the first rotating speed rotating angle information and the second rotating speed rotating angle information;
if the second end surface is in contact with the first end surface, controlling the gear shifting mechanism to unload so that the gear shifting force applied to the joint sleeve by the gear shifting mechanism is zero;
and if the first chamfer surface is in contact with the second chamfer surface, controlling the gear shifting mechanism to continue to be loaded so as to enable the plurality of second joint teeth to be meshed with the plurality of first joint teeth, and realizing gear shifting.
10. A transmission characterized by comprising a synchronizing mechanism of a transmission according to any one of claims 1-7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011522539.5A CN112524170A (en) | 2020-12-21 | 2020-12-21 | Transmission synchronizing mechanism, gear shifting system, gear shifting method and transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011522539.5A CN112524170A (en) | 2020-12-21 | 2020-12-21 | Transmission synchronizing mechanism, gear shifting system, gear shifting method and transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112524170A true CN112524170A (en) | 2021-03-19 |
Family
ID=75002289
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011522539.5A Pending CN112524170A (en) | 2020-12-21 | 2020-12-21 | Transmission synchronizing mechanism, gear shifting system, gear shifting method and transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112524170A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113685544A (en) * | 2021-09-07 | 2021-11-23 | 清华大学 | Parking gear-shifting control method with rotation angle difference estimation |
| CN114251445A (en) * | 2021-12-21 | 2022-03-29 | 潍柴动力股份有限公司 | Vehicle gear shifting control method and device |
| CN114635962A (en) * | 2022-03-17 | 2022-06-17 | 宜宾丰川动力科技有限公司 | Clutch-free synchronizer-free AMT gear shifting control method and system and vehicle |
| CN114877035A (en) * | 2022-07-12 | 2022-08-09 | 清华大学 | Transmission system with one-way adaptive engagement device and shift control method thereof |
| CN115045962A (en) * | 2022-08-17 | 2022-09-13 | 索特传动设备有限公司 | Transmission system, vehicle and gear shifting control method |
-
2020
- 2020-12-21 CN CN202011522539.5A patent/CN112524170A/en active Pending
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113685544A (en) * | 2021-09-07 | 2021-11-23 | 清华大学 | Parking gear-shifting control method with rotation angle difference estimation |
| CN113685544B (en) * | 2021-09-07 | 2022-05-10 | 清华大学 | Parking gear-shifting control method with rotation angle difference estimation |
| CN114251445A (en) * | 2021-12-21 | 2022-03-29 | 潍柴动力股份有限公司 | Vehicle gear shifting control method and device |
| CN114635962A (en) * | 2022-03-17 | 2022-06-17 | 宜宾丰川动力科技有限公司 | Clutch-free synchronizer-free AMT gear shifting control method and system and vehicle |
| CN114635962B (en) * | 2022-03-17 | 2023-07-25 | 宜宾丰川动力科技有限公司 | Clutch-free synchronizer-free AMT gear shifting control method and system and vehicle |
| CN114877035A (en) * | 2022-07-12 | 2022-08-09 | 清华大学 | Transmission system with one-way adaptive engagement device and shift control method thereof |
| CN115045962A (en) * | 2022-08-17 | 2022-09-13 | 索特传动设备有限公司 | Transmission system, vehicle and gear shifting control method |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN112524170A (en) | Transmission synchronizing mechanism, gear shifting system, gear shifting method and transmission | |
| US3983979A (en) | Sensor unblocking ramps | |
| JP4762016B2 (en) | Control method of automatic transmission | |
| US20140283637A1 (en) | Automatic shift device for automated transmission for vehicle | |
| US20110167957A1 (en) | Automatic dual-clutch transmission | |
| WO2011037023A1 (en) | Drive device for vehicle, using electric motor | |
| EP0267714A2 (en) | Synchronizer | |
| US6227063B1 (en) | Automatically operated transmission and controlling method therefor | |
| US20170343056A1 (en) | Synchromesh mechanism and transmission | |
| CN111656050B (en) | Transmission for vehicle | |
| CN214304932U (en) | Synchronous mechanism of transmission, gear shifting system and transmission | |
| JPS62288748A (en) | Block type jaw clutch device | |
| US4922767A (en) | Helical gear transmission device | |
| JP2011098679A (en) | Controller of mechanical automatic transmission | |
| EP0303841B1 (en) | Positive clutch structure | |
| EP0883758A1 (en) | Motor vehicle gearbox | |
| JPH04228929A (en) | Gear coupler | |
| EP0299930B1 (en) | Motor vehicle gearbox with a device for synchronised engagement of reverse | |
| US4280370A (en) | Clutch assembly for gear-type transmission system | |
| US5031741A (en) | Synchronous coupling with locking means | |
| CN114198426B (en) | Position locking type high-speed synchronous automatic clutch | |
| US4330053A (en) | Meshing device for an after-running transmission shaft | |
| JP2010181003A (en) | Transmission | |
| JP5155205B2 (en) | Gearbox synchronizer | |
| EP1992831B1 (en) | Synchronizing unit for a gearbox of a motor vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |