JPH0529257B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a synchro evaluation method for quantitatively evaluating the behavior of a synchro device in a manual transmission for an automobile.

(Prior Art) In general, manual transmissions installed in automobiles have multiple gear trains with different gear ratios arranged in parallel between a counter shaft interlocked with an input shaft and an output shaft parallel to the shaft. In addition, among the gears constituting each gear train, the gear provided on the output shaft is usually rotatable with respect to the output shaft, and one of the rotatable gears is operated in the lateral direction of the shift lever ( (select operation) and vertical operation (shift operation)
By selectively coupling the gear train to the output shaft via a synchronizer, the gear train is brought into a power transmission state, and a gear position corresponding to the gear ratio of the gear train can be obtained.

Further, as shown in FIG. 1, the synchronizer 1 generally includes a clutch hub 3 that is fitted and fixed to a shaft 2, rotates integrally with the shaft 2, and has a spline formed around the outer periphery, and A sleeve 4 that is spline-fitted and slid in the axial direction by a shift operation of a shift lever, keys 5 that are interposed at a plurality of positions in the circumferential direction at the spline-fitting portion between the hub 3 and the sleeve 4, and the shaft 2. A gear spline 7 is integrally formed with a gear 6 (hereinafter referred to as a synchronized gear) rotatably supported by a gear spline 7, and a taper cone 8 is also integrally formed with the synchronized gear 6.
and a synchronizer ring 9 loosely fitted on the tapered cone 8 between the clutch hub 3 and the gear spline 7, and a spline around the outer periphery of the clutch hub 3 and a spline around the outer periphery of the synchronizer ring 9 and the gear spline 7. The teeth of each spline are formed to form splines with the same specifications, and the tips of the teeth forming the splines of the sleeve 4 and the tips of the teeth forming the splines of the synchronizer ring 9 and gear spline 7 opposing thereto. The structure is such that spline chimneys 4a, 9a, and 7a are formed to separate the parts into a positional relationship that allows them to mesh with each other.

According to this synchronizer 1, a force in the direction a applied to the sleeve 4 in the axial direction during a shift operation first causes the synchronizer ring 9 to move through the key 5.
The inner circumferential surface of the gear spline 7 (synchronized gear 6) is pressed against the tapered cone 8, and due to the frictional force, the rotational speed of the gear spline 7 (synchronized gear 6) is changed to the sleeve 4 (shaft 2), and at time I, the inner peripheral surface of the synchronizer ring 9 and the taper cone 8 completely engage, and both, that is, the sleeve 4 and the gear spline 7, are synchronized.

Next, the spline chimney 4a of the sleeve 4
The movement of separating the synchronizer ring 9 from the spline chimney 9a is performed.
At this time, the sleeve 4 and the synchronizer ring 9
This means that the gear spline 7 and sleeve 4 rotate integrally with the synchronizer ring 9 because the channels 4a and 9a rotate relative to each other by a predetermined displacement angle.
A relative rotation shown by the number B in FIG. 2 occurs between the two. When this scraping operation is completed at this point, the sleeve 4 slides and the splines of the sleeve 4 and the splines of the synchronizer ring 9 are engaged, but during this engagement operation, the sleeve 4 and the synchronizer ring Since the synchronizer ring 9 and the gear spline 7 rotate together, there is no difference in rotational speed between the sleeve 4 and the gear spline 7, as shown by the symbol C.

Furthermore, if the engagement of the splines between the sleeve 4 and the synchronizer ring 9 is completed at this point,
Next, the spline chimney 4a of the sleeve 4 meets the spline chimney 7a of the gear spline 7, and a sweeping operation between these chimneys 4a and 7a is performed. In this scraping operation, the bite between the inner circumferential surface of the synchronizer ring 9 that rotates integrally with the sleeve 4 and the taper cone 8 integrally attached to the gear spline 7 is temporarily eliminated, and the sleeve 4 is and gear spline 7 rotate relative to each other by a predetermined rotation angle. When this scraping operation is completed at this point, the sleeve 4 slides further and the splines of the sleeve 4 and the gear splines 7 are engaged with each other. As a result, the synchronized gear 6 is coupled to the shaft 2 via the gear spline 7, the sleeve 4, and the clutch hub 3.

(Problems to be Solved by the Invention) Incidentally, in order for the synchronized gear 6 to be properly coupled to the shaft 2 by this synchronizer 1, it is necessary that the above-mentioned operation of the synchronizer 1 is performed correctly. However, the sleeve 4 and the gear spline 7 may not be reliably synchronized, or problems may occur, such as an abnormal rotational speed difference occurring between them after they have been synchronized. Such a problem may occur, for example, even though the rotational speed of the gear spline 7 has become equal to the rotational speed of the sleeve 4 at the time shown in FIG. Since the plowing operation with the channel 9a is not started, both the spline channels 4a, 9 are removed during the original plowing period between
In cases where relative rotation as shown by symbol ho occurs which is greater than the predetermined scraping rotation angle of a, or when this sleeve 4
During the meshing period of both splines between the time after the end of the scraping operation of the spline thickeners 4a and 9a of the synchronizer ring 9, the biting state between the inner circumferential surface of the synchronizer ring 9 and the taper cone 8 deteriorates, After this point, a relative rotation as shown by the symbol F may occur between the sleeve 4 and the gear spline 7 before the spline chimfers 4a, 7a of the sleeve 4 and the gear spline 7 start to be moved apart.

And when such a problem occurs,
This not only deteriorates the feeling of the shift operation and generates abnormal noises, but also causes erroneous judgments, especially when testing the shift feeling.

In other words, the temporal changes in the load acting on the shift lever and the stroke of the lever during shift operation are measured, and based on these measurement data,
For example, an attempt is made to quantitatively evaluate the shift feeling, such as the weight and smoothness of the shift operation, but if a malfunction of the synchronizer 1 as described above occurs during this test, errors in the load, stroke, etc. As a result, accurate evaluation of shift feeling cannot be performed.

The present invention deals with the above-mentioned actual situation in transmissions, and makes it possible to quantitatively evaluate the behavior of a synchronizer device during a shift operation, thereby identifying the presence or absence of the above-mentioned malfunction phenomenon, and When testing the shift feeling, the purpose is to select only data obtained when the vehicle operates correctly so that accurate shift feeling can be determined.

(Means for Solving the Problems) That is, the transmission synchronization evaluation method according to the present invention connects a synchronized gear rotatably supported on a shaft to the shaft via a synchronization device by a shift operation. In this case, the temporal change in the rotational speed of the shaft and the synchronized gear during the shift operation is measured, and from the measured data, the rotational speed of the shaft and the synchronized gear in a predetermined operating range of the synchronizer during the shift operation is measured. It is characterized by determining the difference in rotation amount from the synchronizing gear and evaluating the behavior of the synchronizing device based on this difference.

The predetermined operating range of the synchronizer is as follows:
For example, the area where the spline of the sleeve and the synchronizer ring separate from each other after the rotational speeds of the shaft and the synchronized gear become equal, and the engagement area between the spline of the sleeve and the synchronizer ring following this area are adopted. be able to.

(Function) According to the above configuration, during a shift operation, for example, the difference in the amount of rotation between the shaft and the synchronized gear in the spacing area of the spline front wheel between the sleeve and the synchronizer ring, or the difference in the amount of rotation between the shaft and the synchronized gear in the engagement area of the spline between the sleeve and the synchronizer ring, The difference between the amount of rotation between the shaft and the synchronized gear is determined.
In that case, the difference in the amount of rotation in the former region is
If the raking motion of the sleeve and synchronizer ring's spline fronts starts immediately after the rotational speeds of the shaft and synchronized gear become equal, the raking angle will be equal to the predetermined raking angle determined by the number of teeth of these splines. Furthermore, the difference in the amount of rotation between the shaft and the synchronized gear in the latter region is due to the biting state between the inner circumferential surface of the synchronizer ring and the taper cone during the meshing of the sleeve and the splines of the synchronizer ring in this region. It should be zero unless it is resolved. Therefore, by determining the difference in the amount of rotation between the shaft and the synchronized gear in these regions and comparing this with a predetermined value, it is possible to determine whether the behavior of the synchronizer is good or not, and the degree of abnormality.

(Example) Examples of the present invention will be described below. still,
This embodiment is for evaluating the behavior of a synchronizer during a shift feeling test, and first a description will be given of a test device on which this evaluation and shift feeling test are performed.

As shown in FIG. 3, this test device 10 includes a motor 11 that drives a transmission A, a clutch 13 interposed on an input shaft 12 between the motor 11 and the transmission A, Output shaft 14 of transmission A (shaft 2 shown in Figure 1)
A flywheel 15 is connected to the transmission A and applies an inertial mass equivalent to the vehicle body to the output side of the transmission A. In addition, as sensors for collecting various data, a motor rotation speed sensor 16 that detects the output rotation speed of the motor 11, and a transmission A
an input rotation speed sensor 17 and an output rotation speed sensor 18 that respectively detect the input rotation speed and output rotation speed of the
A torque sensor 19 that detects the output torque of the transmission A, and a load sensor 20 and a stroke sensor 21 that respectively detect the load acting on the shift lever B of the transmission A and the stroke of the lever B are provided. There is. Furthermore, each of the above-mentioned sensors 16 to 2 is used for controlling the device 10.
a personal computer 24 into which signals a to f from 1 are input via an amplifier 22 and an A/D converter 23; and a sequencer 26 which is operated via an interface unit 25 according to a program set in the personal computer 24. The operation of the motor 11 and the clutch 13 is controlled by the signals g and h from the sequencer 26, and the operation of the shift lever B is controlled by the output signal i from the interface unit 25 via the servo amplifier 27. The operation of the operating actuator 28 is controlled. In addition, the signals a from each of the above-mentioned sensors 16 to 21
-f are also input to the interface unit 25, and feedback control of the entire apparatus is performed based on these signals a-f.

However, using this testing device 10, the shift feeling evaluation method according to the present invention is carried out as follows.

That is, while the transmission A, which has been shifted to a certain gear, is driven by the motor 11 via the clutch 13 at a predetermined rotational speed, the clutch 13 is disengaged, and the actuator 28 moves the shift lever B. Operate to shift to a predetermined gear to be evaluated. At this time, due to the shift operation of the shift lever B, the synchronizer 1 configured as shown in FIG. The shaft 14) and the synchronized gear 6 are coupled. Further, the output signals e and f of the load sensor 20 and the stroke sensor 21 measure changes in the load acting on the shift lever B and the stroke of the lever B as shown in FIGS. Based on the output signals b and c of the rotational speed sensor 17 and the output rotational speed sensor 18, changes in the rotational speed of the shaft 2 (output shaft 14) and the synchronized gear 6 as shown in FIG.
A change in the output torque as shown in FIG. 5d is measured using the output signal d of 9.

Here, the specific operation of the synchronizer 1 during the shift operation and the temporal changes in each data accompanying this will be explained in detail.

First, when the sleeve 4 is slid in the direction a by an amount corresponding to the initial stroke S ₁ (see FIG. 5 b) of the shift lever by a shift operation from the neutral state shown in FIGS. 1 and 4 a, the sleeve 4 The key 5, which moves in the direction a together with the synchronizer 4, pushes the synchronizer ring 9 in the same direction, and presses the inner peripheral surface of the ring 9 against the taper cone 8 that is integrated with the synchronized gear 6. At this time, as shown in FIG. 4b, the chamfers 4a, .
...9a (time point P ₁ in FIG. 5), and in this state, the synchronizer ring 9 rotates integrally with the shaft 2 via the sleeve 4 and the clutch hub 3.

On the other hand, the synchronized gear 6 is activated when the synchronizer ring 9 is pressed against the taper cone 8.
At P ₁ , there is a relative rotation between the axis 2 and the synchronizer ring 9 as shown in Figure 5c.
The abutting surface of the tapered cone 8 and the tapered cone 8 slide, and a frictional force is generated on the surface based on the force of the shift lever that presses the sleeve 4 in the direction a. Due to this frictional force, the synchronized gear 6 is synchronized with the sleeve 4 or the shaft 2 via the taper cone 8, and the rotational speeds of the gear 6 and the shaft 2 become equal at time _P2 , as shown in FIG. 5c. . In that case, in the synchronization region T ₁ from this time point P ₁ to time point P ₂ ,
As shown in FIG. 5a, a large load is applied to the shift lever to generate the above-mentioned frictional force.
As shown in Fig. 5b, the stroke _S2 of the shift lever is extremely small in this synchronization region _T1 , and as shown in Fig. 5d, the shaft 2 is connected to the synchronized gear 6 (and Torque is generated based on the inertial force of each interlocking rotating member.

In this way, at time P ₂ , shaft 2 and synchronized gear 6
When the rotational speeds of the sleeve 4 and the synchronizer ring 9 become equal in rotational speed, the force in the a direction applied to the sleeve 4 by the shift lever causes the sleeve 4 and the synchronizer ring 9 to be moved apart by the spline fronts 4a...4a, 9a...9a. In other words, from the state in which both the channels 4a...4a, 9a...9a meet as shown in FIG. 4b, the sleeve 4 slides in the direction a by an amount corresponding to the stroke _S3 of the shift lever shown in FIG. 5b. , and channel 4a...4a,9
The synchronizer ring 9 rotates relative to the sleeve 4 by a certain amount along the inclined surface of a...9a. Since this synchronizer ring 9 rotates integrally with the synchronized gear 6, a relative rotation as shown in FIG. 5c occurs between the gear 6 and the sleeve 4 or shaft 2, and this relative rotation amount Δθ ₁ is (180/ Z）゜. Then, at time point _P3 , both the spline chimneys 4a...4a, 9a...9
The raking operation ends when the positional relationship of point a becomes as shown in Figure 4 c, but at this point
In the clearing region T ₂ between P ₂ and _{P 3} , the synchronizer ring 9 and the synchronized gear 6 must be rotated relative to the sleeve 4 by the above rotation amount Δθ ₁ by the force in the direction a acting on the sleeve 4. Therefore, as shown in FIG. 5a, a load of a predetermined magnitude continues to act on the shift lever following the synchronization area _T1 .

Also, the spline chimneys 4a...4a, 9a...9 of this sleeve 4 and the synchronizer ring 9
When the scraping operation of a is completed, the sleeve 4 is
The splines of the sleeve 4 and the splines of the synchronizer ring 9 are engaged with each other in this engagement region _T3 .
Since there is no longer any resistance to the sliding of the sleeve 4 in the direction a, the load decreases rapidly as shown in FIG. 5a. Further, since the sleeve 4 and the synchronizer ring 9 rotate together, and the synchronizer ring 9 and the synchronized gear 6 also rotate together, in this region _T3 , the sleeve 4 and the synchronized gear 6 rotate together.
The relative rotation amount Δθ ₂ becomes zero. Then, the sleeve 4 moves toward the shift lever stroke shown in FIG. 5b.
At the time point _P4 when the sleeve ₄ has slid by an amount corresponding to S4, the spline yang faces 4a...4a of the sleeve 4 meet the spline yams 7a...7a of the gear spline 7, and then these A sweeping operation of the channels 4a...4a, 7a...7a is performed.

During this scraping operation, the gear spline 7 or the synchronized gear 6 is rotated relative to the sleeve 4 and the synchronizer ring 9, but this relative rotation is caused by frictional resistance on the contact surface between the taper cone 8 and the synchronizer ring 9. is carried out against. Therefore, the above-mentioned channel 4a...
From the point _P4 when 4a, 7a...7a meet, a large load starts acting on the shift lever again as shown in FIG. The contact surfaces of the sleeve 4 and the gear spline 7 begin to rotate relative to each other. At this time, the friction coefficient on the contact surface changes from a static friction coefficient to a kinetic friction coefficient, so that the load on the shift lever decreases rapidly as shown in Figure 5a, and the sleeve 4 shifts as shown in Figure 5b. At the time point _P5 when the lever slides by an amount corresponding to the stroke _S5 and the sleeve 4 and the gear spline 7 rotate relative to each other by a predetermined amount, these spline shafts 4a...4a, 7a...7a move as shown in FIG. 4e. The positional relationship shown is reached, and the raking operation is completed. In that case, as shown in FIG. 5c, the shaft 2 and the synchronized gear 6
A relative rotation of a certain amount Δθ ₃ occurs between the sleeve 4 and the gear spline front wheels 4a...4a, 7a...7a, but this amount of relative rotation varies depending on the state of the sleeve 4 and the gear spline front wheels 4a...4a, 7a...7a, and the direction of the relative rotation. is also not constant.

Then, after the sliding area T ₄ of the sleeve 4 and the spline inch fronts 4a...4a, 7a...7a of the gear spline 7 from time point _P4 to time point _P5 is completed, the sleeve 4 further slides to the stroke end. As shown in FIG. 4f, the splines in the sleeve 4 mesh with the gear splines 7, thereby completing the coupling operation between the shaft 2 and the synchronized gear 6.

However, in the operation of the synchronizer 1 as described above, the operating state is evaluated as follows.

That is, based on the data of _the rotational speeds of the shaft ₂ and the synchronized gear 6 shown in FIG. The above-mentioned sleeve 4 at the time point P ₃ to _{P 4} following the scraping area T ₂
and the meshing area T ₃ of the splines of the synchronizer ring 9, and the spline engagement area 4 of the sleeve 4 and the gear spline 7 at subsequent points P ₄ to P ₅
The relative rotation amounts Δθ ₁ , Δθ ₂ , Δθ ₃ between the shaft 2 and the synchronized gear 6 are determined in each of the scraping regions T ₄ of a...4a, 7a...7a. These relative rotation amounts are obtained by integrating the rotational speeds of the shaft 2 and the synchronized gear 6 in each of the above regions T ₂ , T ₃ , and T ₄ with respect to time, and
It can be obtained by finding the difference between the integral values.
In addition, the points P ₂ , P ₃ , which separate each region T ₂ , T ₃ , T ₄
P ₄ and P ₅ detect the peak of the output torque, indicated by the symbol G, the start of a drop in the load, indicated by the symbol C, and the time when the load changes from decrease to increase, indicated by the symbols R and N, respectively, in Fig. 5. It is identified by

Then, shaft 2 and synchronized gear 6 in region T ₂
Depending on whether the relative rotation amount Δθ ₁ between the sleeve 4 and the synchronizer ring 9 is equal to a predetermined channel sweep angle (for example, (180/Z)°), the channel _4a of the sleeve 4 and the synchronizer ring 9 is . . 4a, 9a . . . It is determined whether the scraping operations of 9a have been started correctly. Also, area T ₃
Whether or not the synchronizer ring 9 and the taper cone 8 are reliably held in a biting state when the splines of the sleeve 4 and the synchronizer ring 9 are engaged, depending on whether the relative rotation amount Δθ ₂ is zero or not. Determine. This results in
The quality of the behavior of the synchronizer 1 during the shift operation is determined, or the degree of abnormality of the synchronizer operation is evaluated based on the difference from the normal values of the rotation amounts Δθ ₁ and Δθ ₂ . Here, relative rotation amount Δθ ₃ in region T ₄
is used to confirm how the sleeve 4 and the spline chimney faces 4a...4a, 7a...7a of the gear spline 7 meet.

In this example, evaluation was performed as described above.
If the determined behavior of the synchronizer 1 is normal, then the shift feeling, such as the weight and smoothness of the shift operation, is determined. This determination is based on, for example, the temporal change in the load in the synchronization region T ₁ and the separation region T ₂ between the sleeve 4 and the synchronizer ring 9 from time P ₁ to _{P 3} shown in FIG. This is done by determining the impulse and amount of work applied to the shift lever in these areas. Also, regarding smoothness,
Based on the temporal changes in the load in the sliding area _T4 between the sleeve 4 and the gear spline 7 from time _P4 to _P5 , by determining the impulse and amount of work applied to the shift lever in these areas, is performed by determining the height of the peak of the load in the region _T4 . In either case, only data collected when the behavior of the synchronizer 1 is determined to be normal as described above is used as data such as loads used in evaluating shift feeling. By doing so, the shift feeling will always be evaluated correctly.

(Effects of the Invention) As described above, according to the present invention, the behavior of a synchronizer in a transmission during a shift operation can be quantitatively evaluated. This results in
In addition to making it possible to identify defects in the synchronizer itself without relying on human senses, it is especially useful when evaluating shift feeling based on the load acting on the shift lever, the stroke of the lever, etc. It becomes possible to collect data only when the synchronizer operates correctly, and the accuracy and reliability of shift feeling evaluation are ensured.

[Brief explanation of drawings]

FIG. 1 is a schematic cross-sectional view showing the configuration of a synchronizer in a transmission to which the present invention is applied, FIG. Configuration diagram of the test device used for carrying out the invention, Figures 4 a to f
5 is an explanatory diagram showing each operation stage during a shift operation of the synchro device, and FIG. 5 is a diagram showing changes over time of various data during a shift operation. A...Transmission, B...Shift lever,
1... Synchronizer device, 4... Sleeve, 7... Gear spline, 9... Synchronizer ring, 4a, 7
a, 9a...Spline inch yanhua.

[Claims]

1. Quantitatively evaluate the smoothness of the shift operation in a manual transmission configured to put one of a plurality of gear trains into a power transmission state via a synchronized meshing device by selecting and shifting a shift lever. This is a method for evaluating time-based changes in the load acting on the shift lever during a shift operation, and based on this measurement data, the sleeve and gear spline of the synchronized meshing device are synchronized during the shift operation. The minimum value of the load during the period from the time when the sleeve and the synchronizer ring's spline inch front are finished scraping until the time when the sleeve and the gear spline's spline inch inch meet, and the spline inch front of the sleeve and gear spline. A shift feeling evaluation method characterized in that the maximum value of the load during the shifting period is determined, and the smoothness of the shift operation is evaluated based on the difference between the minimum value and the maximum value.