JPH06100260B2 - Torque converter unbalance correction method - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Objects of the Invention (1) Field of Industrial Application The present invention relates to a method for correcting an imbalance of an outer member of a torque converter that transmits torque from an internal combustion engine to a driven side. .

(2) Conventional Technology The conventional torque converter unbalance correction method uses a torque converter in which an inner member made up of a turbine impeller and a stator impeller is assembled inside an outer member made up of a pump impeller and an input case. The unbalance is set by rotating the outer member and the inner member integrally, and the balance weight is fixed to a part of the outer member based on the measurement result. The balance is corrected (see, for example, JP-A-59-65660 and JP-A-63-40829).

(3) Problem to be Solved by the Invention However, since the outer member and the inner member rotate independently in the actual use state of the torque converter, a general imbalance between the outer member and the inner member as in the conventional case is achieved. It is difficult to accurately measure the imbalance of the outer member itself by using the measurement. As a result, if the balance weight for unbalance correction is fixed to the outer member, the balance state may be further deteriorated.

Further, in the actual use state of the torque converter, the outer member is filled with oil, and the torque is transmitted from the outer member side to the inner member side via this oil. However, in the above-described conventional unbalance correction method, since the unbalance is measured without oil filling, when the outer member is filled with oil in a used state, the outer surface of the outer member has a circular shape. Due to the non-uniformity of the direction, the once-corrected balance state may be broken again by the filled oil.

The present invention has been made in view of the above circumstances, and an object thereof is to correct the unbalance of the outer member of the torque converter accurately and efficiently according to the usage state.

B. Configuration of the Invention (1) Means for Solving the Problems In order to achieve the above object, an unbalance correction method for a torque converter according to the present invention is directed to an outer member of a torque converter in which an outer member and an inner member are coupled to each other. Filling the inside with oil; changing the phase connecting the outer member and the inner member by a predetermined angle, performing an unbalanced measurement a plurality of times, and processing the measurement results of the plurality of times, whereby the inner member is obtained. A step of canceling the unbalance caused by the above and calculating the unbalance caused by the outer member and the oil; cutting the balance weight of the weight capable of correcting the calculated unbalance from the strip-shaped metal plate, and Connecting to a predetermined position on the outer periphery of the torque converter; discharging the oil inside the outer member ; Wherein the more it becomes.

(2) Operation According to the above-mentioned feature of the present invention, after the inner member is integrally incorporated inside the outer member of the torque converter,
Oil is injected into the outer member according to the actual use condition. Next, the imbalance is measured in a state where the outer member and the inner member of the torque converter are connected at a predetermined phase, and the imbalance is measured again after changing the phases of both members by a predetermined angle. In this way, after performing unbalance measurement a plurality of times while changing the phase of both members, the unbalance caused by the inner member is canceled by performing arithmetic processing on the measurement result, and the outer member and the outer member. Only the imbalance due to the oil injected inside is calculated. Next, in order to correct the calculated imbalance, the strip-shaped metal plate is cut into a predetermined length to form a balance weight, and the balance weight is coupled to a predetermined position on the outer circumference of the torque converter. And finally, the oil injected into the outer member is discharged.

(3) Embodiment One embodiment of the present invention will be described below with reference to the drawings.

FIG. 1 is a diagram showing a layout of an unbalance correction line of a torque converter, which is an oil filling station.
It consists of four stations: S ₁ , unbalance measuring station S ₂ , balance weight coupling station S ₃ , and oil draining station S ₄ .

FIG. 2 is a cross-sectional view showing the structure of the torque converter. This torque converter T has a large number of blades on its inner surface.
A bowl-shaped pump impeller 1 forming 1a and a bowl-shaped input case 2 that is integrally coupled to the pump impeller 1 and forms an outer shell of the torque converter T are provided. Inside the pump impeller 1 and the input case 2, a turbine impeller 3 having a large number of blades 3a and a pump impeller for forming an impeller chamber 9 in cooperation with the pump impeller 1 and the turbine impeller 3 are formed. A stator wheel 4 having a large number of blades 4a arranged between the wheel 1 and the turbine wheel 3 is arranged. Thus, the pump impeller 1 and the input case 2 form an outer member O that forms the outer shell of the torque converter, and the turbine impeller 3 and the stator impeller 4 are housed inside the outer member O. An inner member I that rotates relative to the outer member O is formed.

A cylindrical portion 1b coaxial with the rotation axis of the pump impeller 1 is provided so as to extend to one side in the axial direction (upper side in the drawing), and the turbine is provided in the central portion of the input case 2. A bag-shaped bearing portion 2a for rotatably supporting an end of an output shaft (not shown) inserted into the torque converter T so as to be coupled to the impeller 3 and the stator impeller 4 is provided in a protruding manner. .

The turbine impeller 3 has a cylindrical output portion 3c having a spline 3b for spline coupling to the output shaft in the central portion, and the output portion 3c is located near the central portion of the input case 2 and is a thrust bearing. It is supported through 5. The stator impeller 4 has a one-way clutch 6 at its radially inner end.
The one-way clutch 6 has an outer ring portion 6a.
A thrust bearing 7 is interposed between the pump impeller 1 and the pump impeller 1, and a thrust bearing 8 is interposed between the outer ring portion 6a and the turbine impeller 3. A spline 6c for spline coupling to the output shaft is formed on the inner ring portion 6b of the one-way clutch 6. A drive plate 10 connected to the engine is attached to the input case 2 in order to rotationally drive the outer member O of the torque converter T.

FIG. 3 shows an oil filling device in the oil filling station S _1, which comprises an insertion unit 11 which can be removably inserted into the torque converter T from the cylindrical portion 1b of the pump impeller 1. There is.

This insertion unit 11 has a cylindrical portion 11a fitted into the cylindrical portion 1b of the pump impeller 1 with a slight gap, a flange portion 11b protruding outward in the radial direction at its upper end, and the cylindrical portion 1 described above.
An oil supply pipe 11c is provided coaxially in the lower portion of 1a and passes through the center of the torque converter T to reach the bag-shaped bearing portion 2a at the lower end of the input case 2. When the insertion unit 11 is inserted into the torque converter T, the opening of the cylindrical portion 1b is sealed by the seal member 12 attached to the flange portion 11b of the insertion unit 11, and the impeller compartment 9 inside the torque converter T is exposed to the atmosphere. Communication is cut off.

An oil tank 13 for storing oil to be filled in the impeller chamber 9 of the torque converter T is connected to the insertion unit 11 by an oil passage having an oil supply pump 14 interposed therebetween.
It communicates with the upper end of the oil supply pipe 11c through the first passage 15 formed in the flange portion 11b of the shaft 11. On the other hand, the insertion unit 11
A second passage 16 is bored in the flange portion 11b to discharge the air and excess oil in the torque converter T, and the second passage 16 is connected to the oil tank 13 through the oil passage. .

FIG. 4 shows the structure of the unbalance measuring device in the unbalance measuring station S _{2. On} the upper surface of the measuring table 22 supported horizontally on the base 21, the turn driven by the first drive motor 23 is provided. A table 24 is provided, and the input case 2 of the torque converter T is supported on the turntable 24 with its axis aligned with the rotation axis of the turntable 24.

An elevating arm 26, which is connected to a drive source (not shown) and moves up and down, is slidably supported on a column 25 standing on the side of the measuring table 22, and the tip of the elevating arm 26 has a first end. A two drive motor 27 is provided. The output shaft of the second drive motor 27 is arranged coaxially with the rotation shaft of the turntable 24,
A drive shaft 28 inserted from above is attached to a cylindrical portion 1b formed in the center of the pump impeller 1 of the torque converter T.

As is apparent from FIGS. 5 and 6, the drive shaft 28
Is the first step portion 28 that fits into the bag-shaped bearing portion 2a from the lower end side.
a, a second step portion 28b fitted to the output portion 3c of the turbine impeller 3,
A third step portion 28c fitted to the inner ring portion 6b of the one-way clutch 6,
And a shaft portion 28d that fits into the cylindrical portion 2b of the pump impeller 1. A key 28e engageable with the spline 3b formed on the output portion 3c of the turbine impeller 3 is formed on the second step portion 28b of the drive shaft 28, and the third step portion 28c has the one direction Splines formed on the inner ring portion 6b of the clutch 6
A key 28f that can be engaged with 6c is formed. Therefore, the drive shaft 28 inserted into the torque converter T is rotatable relative to the pump impeller 1 and the input case 2 that form the outer member O, and the turbine impeller 3 and the stator that form the inner member I. The impeller 4 is integrally rotatable.

A measuring device 29 for measuring the unbalance of the torque converter T is arranged inside the base 21, and the measuring device 29 and the first and second drive motors 23, 27 are control devices equipped with a microcomputer. Connected to 30. Then, normally, the first drive motor 23 and the second drive motor 27 are driven at the same rotation speed in synchronization with each other, and in the process of measurement, the first drive motor 23 and the second drive motor 27 are driven with respect to the phase of the first drive motor 23. The phase is controlled to be displaced by 180 °.

7 to 10 show the balance weight connecting station S ₃
The structure of the balance weight supply mechanism 31 and the balance weight joining mechanism 49 provided in FIG. 7 is shown. As is clear from FIG.
A balance weight 34 that cuts the strip-shaped metal plate 33 wound on the sheet into a predetermined length and welds it to the outer periphery of the torque converter T.
And is composed of a feeding mechanism for the strip-shaped metal plate 33 and a cutting mechanism for the strip-shaped metal plate 33.

The feeding mechanism for the strip-shaped metal plate 33 is a rack 37 that meshes with a pinion 36 that is rotationally driven by a feeding servomotor 35 and reciprocates.
Is provided with an L-shaped drive plate 38, and the pressing cylinder 40 supported on the upper part of the drive plate 38 via a bracket 39 is provided with a strip-shaped metal plate 33 between the drive plate 38 and the drive cylinder 38. A pressing plate 41 is provided so as to be vertically movable so as to be sandwiched. The reel 32 is attached to the output shaft of the tensioning / releasing motor 42 so as to sequentially feed the strip-shaped metal plates 33, and the tension of the strip-shaped metal plate 33 is applied to the upper part of the strip-shaped metal plate 33 fed from the reel 32. A limit switch 43 is provided for detecting and controlling the drive of the tensioning / releasing motor 42.

The cutting mechanism for the strip-shaped metal plate 33 drives a cutting table 44 provided adjacent to the moving end of the drive plate 38 and a clamp member 45 for fixing the tip of the strip-shaped metal plate 33 to the cutting table 44. Clamping cylinder 46 and fixed strip metal plate 33
And a cutting cylinder 48 for driving a cutter 47 for cutting in cooperation with the cutting table 44. Then, the tip end portion of the sent out strip-shaped metal plate 33 is cut by the cutter 47 while being held by a pair of chuck claws 68 described later, and the balance weight 34 having a predetermined length is formed.

As is clear from FIGS. 8 to 10, the balance weight joining mechanism 49 includes a conveying mechanism for the balance weight 34, a welding mechanism for spot welding the conveyed balance weight 34 to the outer periphery of the torque converter T, and this torque converter. T
And a rotation drive mechanism for supporting and rotating.

The balance weight 34 transfer mechanism has two guide rods.
A base 53 slidably supported by 50, connected to a piston rod 52 of a moving cylinder 51, and reciprocally driven in a direction parallel to the feed direction of the metal strip 33 is provided. Base 53
Two guide rods 54 arranged in a direction orthogonal to the guide rods 50 are supported on the upper surface of the slider, and a slider 55 slidably supported by both guide rods 54 is a connecting rod.
56 connected to each other. A base block 57a of a swing arm 57 is rotatably supported in the middle of the connecting rod 56, and a U-shaped shape provided at the tip of a piston rod 60 of a swing cylinder 59 supported on a base 53 via a bracket 58. The knuckle 61 of is connected. A cam plate 62 is fixed to the upper surface of the base 53 in parallel with the guide rod 54, and a cam groove 62a formed in the cam plate 62 is engaged with a roller 63 provided on the lower side surface of the base block 57a. I am fit. Therefore, when the base block 57a is retracted along the guide rod 54 by contracting the rocking cylinder 59, the roller 63 is guided by the cam groove 62a of the cam plate 62, and the rocking arm 57 is chained together with the base block 57a. Tilt to the horizontal position indicated by. When the rocking cylinder 59 is extended, the rocking arm 57 moves forward and stands up in the vertical position shown by the solid line.

A fixed plate 64 is fixed to the tip of the swing arm 57, and a movable plate 67 biased by a spring 66 is slidably supported by two guide pins 65 planted on the front surface thereof. . On the front surface of the movable plate 67, the strip-shaped metal plate
A chuck cylinder 69 having a pair of chuck claws 68 that can be opened and closed is provided in order to hold the balance weight 34 cut from 33. That is, when the swing arm 57 is in the tilted position indicated by the chain line, the tip of the strip-shaped metal plate 33 is supplied and gripped between the pair of chuck claws 68, and the cutter
It is cut by 47 (see FIG. 7). Then, the chuck claw 68 holding the balance weight 43 cut from the strip-shaped metal plate 33 moves horizontally together with the base 53, and at the same time, the base 53.
As the swing arm 57 stands up in the position indicated by the solid line above,
The balance weight 34 held by the chuck claw 68 contacts the side surface of the torque converter T supported by the rotation drive mechanism described later. At this time, as the spring 66 is compressed, the chuck claw 68 is slightly retracted, and the balance weight 34 is pressed against the side surface of the torque converter T with a predetermined pressure.

The welding mechanism is equipped with a welding cylinder 72 supported by a bracket 71 on the upper end of the column 70, and its piston rod.
A welding tip 74 of laser welding or beam welding is attached to the tip of 73. When the swing arm 57 stands up at the position indicated by the solid line, the welding tip 74 contacts the side surface of the balance weight 34 held by the chuck claw 68 due to the extension of the welding cylinder 72.

The rotary drive mechanism includes a turntable 76 that rotatably supports the torque converter T on a base 75. A rotary servomotor 77 is provided on the upper part of the turntable 76 so as to be able to move up and down, and a drive member 78 which is engageable with the center of the torque converter T is attached to the lower end of its output shaft. A detection device 79 for detecting the rotational position of the torque converter T is provided near the turntable 76.

FIG. 11 shows an oil draining device at the oil draining station S _4, which is insertable into the torque converter T so that it can be removably inserted from the cylindrical portion 1 a provided in the pump impeller 1. It has a unit 81.

The insertion unit 81 includes a unit main body 82 integrally formed with a flange portion 82b protruding outward in the radial direction at one end of a columnar portion 82a, and an oil discharge coaxially connected to the other end of the columnar portion 82a. The pipe 83, the other end of the cylindrical portion 82a, and the oil discharge pipe 8
And a piston 84 that is slidably fitted to the shaft 3.

The cylindrical portion 82a of the unit main body 82 is formed in a cylindrical shape having an outer diameter such that it can be inserted into the cylindrical portion 1b of the pump impeller 1, and the other end of the cylindrical portion 82a has a cross section. A circular recess 85 is coaxially provided. Oil drain pipe
83 has a diameter smaller than that of the columnar portion 82a, and is screwed to the closed end of the recess 85 so as to be coaxially connected to the other end of the columnar portion 82a. Thus, the piston 84 has a cylindrical portion with an O-ring 87 interposed between the piston 84 and the inner surface of the recess 85 and an O-ring 87 between the outer surface of the oil discharge pipe 83 and the piston 85.
82a and the oil discharge pipe 83 are slidably fitted, and an annular pressure chamber 88 is defined between the closed end of the recess 85 and the piston 84.

An annular receiving portion 89 facing the piston 84 is integrally provided at an intermediate portion of the oil discharge pipe 83 so as to extend radially outward while forming an annular groove 90 between the oil discharge pipe 83 and the outer surface of the oil discharge pipe 83. A spring 91 is interposed between the piston 84 and the closed end of the annular groove 90 so as to exert a spring force for urging the piston 84 in the direction of contracting the volume of the pressure chamber 88.

On the other hand, on the outer peripheral edge of the surface of the piston 84 facing the receiving portion 89, a tapered surface 84 that becomes smaller in diameter as it gets closer to the receiving portion 89.
a is provided, and the tubular first seal member 92 is sandwiched between the tapered surface 84a and the receiving portion 89. The base of the flange portion 82b of the unit main body 82 has an annular second seal member that abuts the outer end of the cylindrical portion 1b of the pump impeller 1.
93 is fitted.

Thus, with the insertion unit 81 inserted into the torque converter T until the second seal member 93 contacts the outer end of the cylindrical portion 1b, the first seal member 20 causes the inner ring portion 6b of the inner ring portion 6b of the one-way clutch 6 to be 92. The length of the cylindrical portion 82a, the disposition position of the receiving portion 89, and the like are set so as to make contact with each other.

The unit body 82 has a passage 94 whose one end is opened to the outer surface of the flange portion 82b and whose other end is communicated with the pressure chamber 88.
a and a plurality of through holes 94b that are open to the outer surface of the columnar portion 82a while communicating with the pressure chambers 88, and thereby the first through holes 94a from the passage 94a through the pressure chambers 88 to the first through holes 94a. A passage 94 is formed. Further, the unit body 82 and the oil discharge pipe 83 are provided with a second passage 95 having one end opened to the outer surface of the flange portion 82b and the other end opened to the tip of the oil discharge pipe 83.

A pressurized gas supply means 96 such as a compressor for supplying pressurized gas, for example, pressurized air, is connected to the first passage 94, and an oil tank 97 is connected to the second passage 23.

Next, the operation of the embodiment of the present invention having the above configuration will be described.

First, the torque converter T in which the turbine impeller 3 and the stator impeller 4 that form the inner member I are integrally assembled inside the pump impeller 1 that forms the outer member O and the input case 2 is carried into the oil filling station S ₁ . Then, the insertion unit 11 is inserted into the cylindrical portion 1b of the pump impeller 1 that constitutes the outer member O (see FIG. 3). As a result, the first passage 15 communicates with the impeller compartment 9 via the oil supply pipe 11c and the thrust bearing 6, and the second passage 16 communicates with the impeller compartment 9 via the thrust bearing 7. When the oil supply pump 14 is driven from this state, the oil in the oil tank 13 is supplied to the bottom of the impeller compartment 9 of the torque converter T via the first passage 15 of the insertion unit 11 and the oil supply pipe 11c. Then, as the oil level in the impeller chamber 9 gradually rises, the air in the impeller chamber 9 is discharged through the second passage 16, and when the impeller chamber 9 is filled with oil, excess oil is eventually discharged. Is returned to the oil tank 13 through the second passage 16.

The torque converter T filled with oil as described above
Is set on the turntable 24 of the measuring device 29 at the next unbalance measuring station S ₂ , the elevating arm 26 is lowered, and the key 28e formed on the second step portion 28b thereof.
Is engaged with the spline 3b of the output portion 3c of the turbine impeller 3, and the key 28f formed on the third step portion 28c thereof is engaged with the spline 6c of the inner ring portion 6b of the one-way clutch 6 (see FIG. 6).

When the first drive motor 23 and the second drive motor 27 are started from this state, the turntable 24 and the drive shaft 28 start to rotate integrally with each other in synchronization with each other, and the rotational speed of the torque converter T gradually increases. As indicated by the solid line in FIG. 12, when the rotation of the torque converter T reaches the measured rotation speed N, the measuring device 29 operates and the first unbalance measurement of the torque converter T is performed, and the result is the control device. Remembered in 30. When the first measurement is completed, the rotation speed of the second drive motor 27 is slightly accelerated or decelerated with respect to the rotation speed of the first drive motor 23, and the outer member O supported by the turntable 24 and the drive shaft 28 are supported. The phase of the supported inner member I is displaced by 180 ° compared to the first measurement.
When the phase of the outer member O and the inner member I is displaced by 180 ° as described above, the rotation speed of the first drive motor 23 and the rotation speed of the second drive motor 27 are synchronized again, and the outer member O and the inner member I are Rotate as a unit while maintaining the 180 ° phase shift. At this time, the measuring device 29 is activated to perform the second imbalance measurement, and the result is stored in the control device 30. Then, when the second measurement is completed, the first drive motor 23 and the second drive motor 27 are decelerated and stopped. Thus, the control device 30 calculates the unbalance of the outer member O based on the results of the two measurements.

As is clear from FIG. 13, a vector C indicating the unbalance of the entire torque converter T detected in the first measurement.
Is expressed as the sum of the vector A indicating the imbalance caused by the inner member I and the vector B indicating the imbalance caused by the outer member O (including the imbalance caused by the oil filled in the outer member O). . Also, 2
C ′ indicating the unbalance of the entire torque converter T detected in the second measurement is expressed as the sum of A ′ indicating the imbalance caused by the inner member I and B indicating the imbalance caused by the outer member O. .

At this time, in the first measurement and the second measurement, the unbalances A and A'caused by the inner member I whose phases are shifted by 180 ° have the same absolute value and opposite directions, whereas the outer member O. The imbalances B due to are equal. Therefore, if you add the results of the first and second measurements, Therefore, the unbalance B caused by the outer member O is calculated by B = (C + C ') / 2.

Then, when the vector B corresponding to the imbalance caused by the outer member O is detected, the balance weight having the weight corresponding to its absolute value is fixed at the position P on the extension line of the vector B, and the outer weight is fixed. The unbalance of the member O is corrected. Since this correction simultaneously corrects the imbalance caused by the oil with which the outer member O is filled, it is possible to obtain the optimum balance adapted to the actual usage state of the torque converter T. And the above 2
Since the measurement of one time is completed while the torque converter T is held at the measured rotation speed N, after the first measurement is completed, the rotation of the torque converter T is stopped and the phase of the inner member I is changed. The time required for the measurement can be significantly shortened compared to the case where the torque converter T is rotated again and the second measurement is performed (see the chain line in FIG. 12).

Next, after carrying in the unbalance-measured torque converter T to the balance weight coupling station S ₃ , the seventh
As shown in the figure, in the state where the pressing cylinder 40 of the balance weight supply mechanism 31 is extended and the strip-shaped metal plate 33 is sandwiched between the pressing plate 41 and the drive plate 38, the torque converter T detected in the previous step is not operated. Servo motor for supply according to the balance amount
When 35 is driven by a specified amount, pinion 36 and rack 37
The drive plate 38 moves forward via and the tip of the strip-shaped metal plate 33 is inserted between the chuck claws 68 provided at the tip of the swing arm 57 in the horizontal position. Subsequently, the chuck cylinder 69 is driven to grip the tip of the strip-shaped metal plate 33 with the chuck claws 68, and the clamp cylinder 46 is extended to clamp the clamp member 45.
The band-shaped metal plate 33 is fixed on the cutting table 44 with. Next, when the cutting cylinder 48 is driven and the strip metal plate 33 is cut by the cutter 47, the balance weight 34 of a predetermined length held by the chuck claws 68 is separated from the strip metal plate 33. At this time,
When the feeding servo motor 35 feeds the strip-shaped metal plate 33 and the tension acts on the strip-shaped metal plate 33, the limit switch 43 is actuated to rotate the tensioning / releasing motor 42, whereby the strip-shaped metal plate 33 is fed. The reel 32 is driven to compensate for this.

Now, when the balance weight 34 is gripped by the chuck claw 68 as described above, as shown in FIGS. 8 to 10, the moving cylinder 51 of the balance weight joining mechanism 49 contracts to move the base 53. It is moved along the guide rod 54, and at the same time, the rocking cylinder 59 extends and rocks the rocking arm 57 from the tilted position to the standing position. Thereby, the chuck claw 68
The balance weight 34 gripped by the abutting member contacts the side surface of the torque converter T supported by the turntable 76.

Subsequently, the rotation servomotor 77 is operated to rotate the turntable 76 to a predetermined position while detecting the rotation angle with the detection device 79 in order to position the balance weight 34 at a predetermined position on the outer circumference of the torque converter T. Next, the welding cylinder 72 extends and the welding tip 74 provided at the tip of the piston rod 73 is inserted between the pair of chuck claws 68, and the balance weight 34 gripped by the chuck claws 68 is transferred to the torque converter T. Spot welding on the outer periphery of. At this time, when the length of the balance weight 34 is short, only one spot is spot-welded, but when the length of the balance weight 34 is long, the rotation servomotor 77 is driven to drive the torque converter T. While rotating, the balance weight 34 is spot-welded at a plurality of positions in the longitudinal direction.

When the balance weight 34 is welded to the torque converter T as described above, the balance weight 34 is welded to the torque converter T that is subsequently loaded onto the turntable 76.
In order to receive, the welding tip 7 first retracts from the original position, then the base 53 returns to the original position and the swing arm 57 swings to the tilted position to complete one cycle.

Next, the torque converter T is carried into the oil discharge station S ₄ , and the oil with which it is filled is discharged. That is, as shown in FIG. 11, first, insert unit 81,
The second seal member 93 is inserted into the torque converter T from the cylindrical portion 1b until it comes into contact with the outer end of the cylindrical portion 1b. At this time, the first seal member 92 is inserted to the position corresponding to the inner surface of the inner ring portion 6b of the one-way clutch 6 in the torque converter T, but the piston 84 is biased by the spring 91 in the direction away from the receiving portion 89. Therefore, the first seal member 92 does not come into strong contact with the inner surface of the inner ring portion 6b, and therefore a large frictional force does not act between the first seal member 92 and the inner ring portion 6b at the time of insertion, which is relatively small. The insertion unit 81 can be inserted into the torque converter T by force.

In such an inserted state of the insertion unit 81 in the torque converter T, the first passage 94 communicates with the impeller compartment 9 via the thrust bearing 7, and the second communication 95 communicates with the impeller compartment 9 via the thrust bearing 8. Communicate.

When pressurized gas, for example, pressurized air is supplied from the pressurized gas supply means 96 to the first passage 94 while the second seal member 93 is strongly pressed against the outer end of the cylindrical portion 1b, pressure acts on the pressure chamber 88. In response to this, the piston 84 is pressed toward the receiving portion 89 side, and the first
The seal member 92 is pinched between the tapered surface 84a and the receiving portion 89, and is expanded outward in the radial direction by the tapered surface 84a, whereby the diameter is expanded. Therefore, the first seal member 92 strongly contacts the inner surface of the inner ring portion 6b of the one-way clutch 6,
Between the pump impeller 1 and the stator impeller 4, that is, the portion of the thrust bearing 7, the turbine impeller 3 and the stator impeller 4
The space and the space of the thrust bearing 8 are blocked by the first seal member 92. Further, since the second seal member 93 is strongly pressed against the outer end of the cylindrical portion 1b,
The pump impeller 1 and the stator impeller 4 are disconnected from the outside. As a result, a flow path is formed from the first passage 94 to the second passage 95 via the thrust bearing 7, the impeller chamber 9, and the thrust bearing 8.

When the pressurized air supply from the pressurized gas supply means 96 is continued in this state, the pressurized air enters the impeller chamber 9 through the first passage 94 and pushes the oil in the impeller chamber 9 downward. Therefore, the oil removed from the impeller chamber 9 is discharged from the second passage 95 to the discharge tank 97.

Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above embodiments, and various small design changes can be made without departing from the present invention described in the claims. It is possible.

For example, in the embodiment, the outer member O and the inner member I differ in phase by 180 ° and are measured twice, but the number of measurements is not limited to two, and the phase difference is 120 ° and three measurements are performed. Or it is possible to perform the measurement four times with a phase difference of 90 °, which can improve the measurement accuracy. Further, the means for connecting the balance weight to the torque converter T is not limited to spot welding, and other means such as adhesion can be used.

C. Effect of the Invention As described above, according to the present invention, an imbalance measurement is performed a plurality of times in a state where the phases of the outer member and the inner member are changed, and the imbalance caused by the inner member is obtained from the plurality of measurement results. Since the above is canceled, only the imbalance caused by the outer member can be accurately detected. At that time, since the measurement is performed in a state where the outer member of the torque converter is filled with oil, the unbalance caused by the outer member and the uneven distribution of the oil inside the outer member are caused. The unbalance can be detected at the same time, and the unbalance can be corrected according to the actual usage state of the torque converter. Further, since the balance weight is formed by cutting a strip-shaped metal plate into a predetermined length, it is not necessary to prepare a large number of balance weights of various weights in advance, and the weight of the balance weight can be precisely adjusted. Can be adjusted.

[Brief description of drawings]

1 to 13 show an embodiment of the present invention.
The drawing shows the layout of the unbalance correction line of the torque converter, FIG. 2 is a sectional view showing the structure of the torque converter, FIG. 3 is a drawing showing the oil filling device, and FIG. 4 is a drawing showing the unbalance measuring device. 5 is an enlarged perspective view of the drive shaft, FIG. 6 is a view showing the torque converter with the drive shaft inserted, FIG. 7 is a perspective view of the balance weight supply mechanism, and FIG. 8 is a balance weight joining mechanism. Overall plan view,
9 is a sectional view taken along line IX-IX in FIG. 8, and FIG. 10 is X in FIG.
-X sectional view, FIG. 11 is a diagram showing the oil discharge device, FIG. 12 is a graph for explaining the operation of the imbalance measuring step, and FIG. 13 is a diagram for explaining the calculation contents. I ... Inner member, O ... Outer member, 33 ... Band-shaped metal plate, 34 ... Balance weight

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁵ Identification number Reference number within the agency FI Technical display location G01M 1/32 (72) Inventor Zenichiro Kumida 1-10 Shin-Sayama, Sayama-shi, Saitama Honda Engineering Incorporated (72) Inventor Shunji Kano 1-10-1 Shin-Sayama, Sayama City, Saitama Prefecture Honda Engineering Co., Ltd. (56) Reference JP 63-40829 (JP, A) JP 59-65660 ( JP, A)

Claims (1)

[Claims] 1. An outer member (O) and an inner member (I)
Filling the inside of the outer member (O) of the torque converter (T) in which the torque converter (T) is coupled; changing the phase coupling the outer member (O) and the inner member (I) by a predetermined angle, and A step of performing an unbalance measurement and calculating the unbalance caused by the inner member (I) and the unbalance caused by the outer member (O) and oil by performing arithmetic processing on the measurement results of the plurality of times. And a balance weight (34) having a weight capable of correcting the calculated imbalance is cut from the strip-shaped metal plate (33), and the balance weight (34) is coupled to a predetermined position on the outer periphery of the torque converter (T). And a step of discharging the oil inside the outer member (O);