JPS581295B2 - torque limiter - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a torque limiter that cuts off torque transmission when an overload is applied.

Various types of torque limiters are known, but they are satisfactory as they can absorb misalignment that occurs between the rotary drive shaft and the driven shaft, that is, angular errors, parallel errors, and clearance errors between the two axes. There was nothing.

In addition, there is also known a device that facilitates resetting after torque transmission is cut off, such as in Japanese Patent Application Laid-open No. 52-19845, but in this device as well, when resetting, the pressing plate is moved from the disc spring. Since the reset cannot be performed without pulling against the pressing force, if the set torque is high, the spring force becomes quite strong, which has the disadvantage that it cannot be easily reset manually or with a tool.

The present invention was made in view of these points, and its purpose is to provide a torque limiter that can absorb misalignment between two axes and that can be easily reset by applying a small amount of force. There it is.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The structure of the present invention will be described in detail below based on an embodiment shown in the accompanying drawings.

In FIGS. 1 and 3, a is a rotating and driving member, b
The driven members are both made of shaft bodies, and are arranged with a predetermined gap between each shaft end.

Reference numeral 1 denotes an interlocking connection body made of a sleeve-shaped member, which is fitted onto the outer periphery of the shaft end of the rotary drive member a, and is integrally attached to the shaft end of the rotary drive member a together with a tightening ring 3 and a tightening span ring 4 by a tightening bolt 2. It has been concluded.

Reference numeral 5 denotes an interlocking connection body formed in a flange shape, which is fitted onto the outer periphery of the shaft end of the driven member b, and is integrally connected to the driven member b by a tightening bolt 6 of a tightening ring 7 which is also fitted into the driven member b. It has been concluded.

8 is a tightening Schwan ring of the tightening ring 7.

Reference numeral 9 denotes an interlocking connection cylinder which is fitted onto the outer periphery of the interlocking connection body 1, one end of which is integrally connected to the interlocking connection body 5 by connection tightening bolts 1 and 10, and a stop at the bottom edge 12 of the other end. A ring 11 is provided.

Reference numeral 13 denotes a tapered thrust sleeve fitted between the interlocking connection tube 9 and the interlocking connection body 1, and its downwardly inclined surface 13
' is designed to come into contact with a torque transmitting steel ball 22, which will be described later, and has a tapered thrust ring 14 on its outer periphery.
loosely fit into the vertical surface 13'' of the tapered thrust sleeve 13 and the upwardly inclined surface 1 of the tapered thrust ring 14.
4' and the inner flat surface 12' of the interlocking connecting cylinder 9.
A plurality of steel balls 15 are interposed between the tapered thrust ring 14 and an inner inclined surface 9' connected to the inner inclined surface 9'. It is supposed to be done.

17 is a pressure nut screwed onto one end of the tapered thrust sleeve 13, and a torque spring;
This is for adjusting the strength of step 6.

Reference numeral 18 denotes a rotation retaining ring installed within the pressure nut 17, and 19 indicates a steel ball for facilitating rotation of the pressure nut 17.

Reference numeral 20 denotes a plurality of axially extending engagement recesses provided on the outer peripheral surface of the interlocking connecting body 1, and 21 represents radial recesses provided on the inner peripheral surface of the interlocking connecting cylinder 9. The grooves are provided in the same number as the engagement grooves 20.

Reference numeral 22 denotes a torque transmitting steel ball that is fitted across the engagement notch 20 and the notch 21, respectively.

In the present invention, it is also possible to use the rotating/driving member a on the output side and the driven member on the input side.

Next, the effect will be explained.

In the normal load range, as shown in Fig. 3 and Fig. 5 ■ and ■, the steel balls 15 and 22 are pressed in the inner radial direction by the Herc spring 16, so that the rotary driving member a and the driven member b rotates together with the interlocking coupling bodies 1 and 5, the interlocking coupling cylinder 9, the tapered thrust sleeve 13, and the tapered thrust ring 14, and the required power is transmitted, but when overloaded, the As shown, first steel ball 2
2 is removed from the notch-shaped engagement recess 20 provided on the outer circumferential surface 7 of the interlocking coupling body 1 due to the rotation of the rotational drive member a, and the outer circumferential surface of the interlocking coupling body 1 engages the recess of the interlocking coupling cylinder 9. Since it is pushed into the groove 21, the tapered thrust sleeve 13, whose downwardly inclined surface 13' is in contact with one side of the steel ball 22, receives a force that moves to the right in FIG. 3, compressing the torque spring 16. Then, the steel ball 15 located between the inner inclined surface 9' of the interlocking connecting cylinder 19, the vertical shaft 13'' of the tapered thrust sleeve 13, and the upwardly inclined surface 14' of the tapered thrust ring 14 is inserted into the sixth steel ball 15. It moves to the position shown in FIG.

In such a case, the steel ball 15 is connected to the tapered thrust ring 1.
The bottom edge 1 of the interlocking connecting cylinder 9 is formed by the upwardly inclined surface 14' of 4.
2 and maintains the state shown in FIG. 6I.

Therefore, the tapered thrust sleeve 13 also uses its downwardly inclined surface 13' to move the steel ball 22 into the concave groove 21 of the interlocking connecting tube 9.
It cannot be pushed out from inside, and the engagement between the rotary drive member a and the driven member b becomes disengaged, and the rotation of the rotary drive member a is not transmitted to the driven member b.

In addition, when the cause of overload is removed and the rotational drive member a and the driven member b are reset, the lower surface of the steel ball 22 should be aligned with the circular engagement recess 22 of the interlocking connection body 1. After rotating and aligning the interlocking connecting cylinder 9, the tapered thrust sleeve 13 is removed manually or with an appropriate tool.
When pressed to the left in FIG. 6I, the steel ball 22 receives a downward pressing force from the downwardly inclined surface 13' of the tapered thrust sleeve 13, and the steel ball 22 is pushed into the engaging concave notch 20 of the interlocking connector 1. Since the lower surfaces are fitted, the tapered thrust sleeve 13 moves to the left, and this movement causes the steel ball 15 to return to its original state due to the restoring force of the torque spring 16.
In other words, as shown in FIG.
and the upward tilting position 14' of the tapered thrust ring 14.
Positioned between them, the rotating driving member a and the driven member b are connected again and rotate together, so that the required power transmission is performed.

As described above, the present invention transmits the necessary power during normal loads and cuts off the power transmission during overloads. This axial displacement occurs when a steel ball pressed by an elastic pressing means, that is, a torque spring, moves along the groove in a circular engagement groove extending in the axial direction on the outer periphery of the driving member or driven member. By moving with friction,
Friction can be absorbed, and rotation and relative radial displacement between the driving member and the driven member can be absorbed by radial grooves extending in the radial direction machined inside the rotary driving member or the driven member. , the steel ball pressed in the inner radial direction by the elastic pressing means overcomes the elastic force and moves along the concave groove by the amount of displacement thereof, thereby absorbing the elastic force; The deviation angle error with respect to the center of rotation can be absorbed by simultaneous axial frictional movement and radial elastic movement of the steel ball. It completely absorbs the parallelism error of the shafts, the gap error between both shafts, and has a large degree of freedom in installation and connection. The grooves corresponding to each other are simultaneously machined by simple processing means, and by placing torque transmission steel balls with the same dimensions as the width of the groove in each of the created grooves, their mutual positions are as follows: By completely matching and using the elastic pressing means, the rotational direction backlash between the rotary driving member and the driven member is minimized, the rotational displacement is accurately transmitted integrally, and the grooves correspond to the grooves. By increasing the number of steel balls, rotational unevenness in the transmitted rotation can be minimized, and the axial force of the tapered thrust ring pressurized by the torque spring is transferred between the tapered thrust sleeve and the taper ring. Due to their contact angle, the steel balls sandwiched between the thrust rings are pushed radially outward and come into contact with a tapered part of the inner diameter of the interlocking coupling cylinder, and the force pushes the tapered thrust sleeve in the axial direction, causing the tapered The torque transmitting steel ball that comes into contact with the tapered part of the thrust sleeve is configured to be pushed toward the center by that force, so even when rotating at high speed, the influence of centrifugal force is extremely small and excessive When a load is applied, it can respond accurately and achieve the intended purpose, so it is suitable for high-speed rotation, and the limit torque can be adjusted by using a taper thrust. This can be done more accurately and easily by rotating a pressure nut screwed into the outer periphery of the sleeve and pressurizing the torque spring, and when resetting, the pressing force of the torque spring can be used to easily reset with a small force. It has many advantages, such as being able to be reset.

[Brief explanation of the drawing]

Fig. 1 is a front view of the torque limiter of the present invention, Fig. 2 is a side view thereof, Fig. 3 is a sectional view taken along the line I--I of Fig. 2, Fig. 4 is a sectional view taken along the line ■-■ of Fig. 3, and Fig. 5 is a sectional view taken along the line I--I of Fig. 3. Figure I is an explanatory cross-sectional view of the operating state, Figure 5 ■ is a cross-sectional view taken along the line ■-■ of Figure 5 1, and Figure 6 I is a cross-sectional view showing the positions of the groove and the torque transmission steel ball during overload. , Fig. 6 ■ is a sectional view taken along the line ■-■ of Fig. 6 I, Fig. 7 is an explanatory sectional view showing angular error, Fig. 8 is an explanatory sectional view showing parallel error, and Fig. 9 is an explanatory sectional view showing gap error. It is a diagram. a... Rotation drive member, b... Driven member, 1... Interlocking coupling body, 2... Tightening bolt, 3... Tightening ring, 5... Interlocking coupling body, 6... Tightening bolt, 7... Tightening ring , 9...
Interlocking connection tube, 10... Connection tightening bolt, 15, 19...
...Steel ball, 20...Circular engagement groove, 21...Radial groove, 22...Torque transmission steel ball, α, β, θ...
Taper partial slope angle, γ, ω...Axis error between rotational drive member a and driven member b, X, Y, R, S...Movement direction, P...Torque spring pressure direction, A, B, C, D ...Torque transmission, contact point with steel ball.

Claims (1)

[Claims] 1 A plurality of shafts extending in the axial direction are mounted on the outer circumferential surface of the interlocking coupling body 1 fitted to the outside of one of the rotary drive member a and the driven member b to be coupled, which are arranged with a predetermined gap between each shaft end. On the inner circumferential surface of the interlocking connection cylinder 9, which is provided with a notched circular engagement recess 20 and attached to the interlocking connection body 5 which is fitted and attached to the other outer side of the rotational drive member a and the driven member b. , a plurality of radial grooves 21 extending in the radial direction are connected to the circular engagement grooves 20 of the interlocking coupling body 1, and each of the radial grooves 21 is provided with a plurality of radial grooves 21, respectively. The torque transmitting steel ball 22 is movable only in the radial direction, is constrained in the rotational direction and the axial direction, and is fitted in such a way that it can rotate on its own axis. An inner inclined surface 9 that is in contact with the downwardly inclined surface 13' of the tapered thrust sleeve 13 that is lowered on the inner side and that is connected to the vertical surface 13'' of the tapered thrust sleeve 13 and the inner flat surface 12' of the interlocking connecting cylinder 9. ' and a plurality of steel balls 15 are interposed between the upwardly inclined surface 14' of the tapered thrust ring 14 that is loosely fitted around the outer periphery of the tapered thrust sleeve 13, and one end of the tapered thrust sleeve 13 is attached to the back surface of the tapered thrust ring 14. A torque limiter characterized in that the tip of a torque spring 16 is brought into pressure contact with a pressure nut 17 that is screwed on.