JPH0731148Y2 - Torque measuring device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (a) Technical Field The present invention relates to a torque measuring device, and more particularly, to a torque measuring device for converting torque acting on a wheel into an electric quantity for measurement.

(B) Prior Art As a torque measuring device for measuring torque acting on a wheel of a vehicle such as an automobile, for example, by forming a large number of holes on a virtual circumference of a predetermined radius of a strain plate having a disk shape, Form a spoke-shaped strain-flexing piece extending in the radial direction of the hole, attach a strain gauge to this strain-flexing piece, and further mount the strain-flexing plate fixed so as to be orthogonal to the axis of the drive shaft, Some torque measuring devices that have been fixed to a disk and have the strain gauges configured to convert the torque acting on the wheels into an electric quantity and measure the torque have already been put into practical use.

As one example, a torque measuring device proposed in Japanese Examined Patent Publication No. 60-13453 (hereinafter sometimes referred to as "conventional device")
There is.

However, this conventional torque measuring device has the following problems.

First, in the strain-flexing plate of the above-mentioned conventional device, the portion to be mounted on the drive shaft (axle) and the strain-flexing piece are integrally configured, but the structure of the wheel mounting portion for mounting the wheel of the drive shaft, that is, Since the number of hub bolts and the location of the hub bolts differ depending on the vehicle type, it is not possible to cope with vehicles with different wheel mounting parts unless the entire torque measuring device is replaced, and therefore the structure of the wheel mounting parts is applicable. There is a problem in that it is uneconomical to prepare a large number of torque measuring devices of the same type.

Secondly, the conventional device described above has a fatal defect when the torque is measured under the condition that the regular wheel offset is not secured in a state where the wheel is mounted on the wheel, and therefore the offset change gives an error to the measurement. .

Thirdly, in the above-mentioned conventional device, when the strain-flexing piece of the strain-flexing plate receives an unexpected force such as overload and is completely destroyed, the wheel and the disc of the wheel are separated and rotated. No force is transmitted, and, conversely, no braking force is obtained even when the brakes are applied, causing a very dangerous situation.

(C) Purpose The present invention has been made in view of the above-mentioned circumstances, and the first object is to provide a wheel without substantially being affected by an acting force other than torque such as axle load. The acting torque can be faithfully converted into an electric quantity, and secondly, since a common member can be used regardless of the type of wheel and the structure of the wheel mounting portion of the drive shaft, the entire device can be manufactured inexpensively. Thirdly, the regular offset can be held, and therefore, the torque measurement under the condition that the offset change gives an error to the measurement can be accurately performed.
In addition, even if the strain plate is damaged due to unexpected overload, the braking function will not work even if the wheel and disk are separated and the brake is applied as in the past. It is an object of the present invention to provide a torque measuring device capable of reliably preventing a situation in which wheels are removed together with a disc.

(D) Configuration In order to achieve the above-mentioned object, the present invention is a torque measuring device that converts torque acting on a wheel into an electric quantity and measures the torque, and a hub bolt having a different number and arrangement position depending on the vehicle type is provided. A plurality of axle adapters each having hub bolt insertion holes suitable for each vehicle type so that a hub nut can be attached to the wheel mounting portion of the shaft, a wheel having a large circular hole formed at the center of the disk, and this wheel The disk spacer that is fitted into the circular hole and is firmly fixed to the wheel while maintaining the same offset as the regular wheel, and the overall shape is a substantially disk shape, and the axle adapter is located in the center part. , The disk spacers are concentrically overlapped with the peripheral portion, and on the circumference of a predetermined radius passing between the central portion and the peripheral portion. A plurality of spoke-shaped strain-flexing pieces extending in the radial direction are formed between the holes adjacent to each other by uniformly forming the number of holes divisible by at least 4, and the thickness of the strain-flexing pieces in the axial direction is radiated. And a strain plate which is formed to be larger than the minimum width in the direction and which is firmly fixed to the axle adapter with a first bolt in the vicinity of the inside of the strain piece, and which has a substantially disc shape and is outside the strain piece. A through hole having a diameter that overlaps with the strain-flexing plate and has a gap that does not come into contact with the outer circumference of the first bolt is formed at one portion, and the through hole is formed into the first hole.
In the state where they can be fitted to the respective bolts, the cover is firmly fixed to the disk spacer together with the strain-flexing plate with the second bolt, and the strain-breaking piece is broken at a portion near the center of the strain-flexing plate. At this time, in order to prevent the cover from moving a certain amount outward in the axial direction, there is a gap that does not always come into contact with the cover and is attached to the strain-flexing plate. A pair of the strain-flexing plates sandwiching a predetermined strain-deflecting piece, and a strain gauge attached to each of the first scheduled attachment surface on one side and the second scheduled attachment surface on the other side of the hole. The strain gauges attached to the first surface to be attached, which is one of the above, are respectively connected to the two opposing first and second bridge sides by circuits, and are attached to the second surface to be attached, which is the other of the pair. The strain gauge is Third and fourth bridges sides respectively adjacent to the second bridge sides with respective circuit connection is characterized in that a Wheatstone bridge for detecting the torque.

Further, the Wheatstone bridge circuit of the present invention comprises a strain gauge attached to one of the pair of first scheduled attachment surfaces and attached to a half circumference portion of the strain-flexing plate, the two first and the second opposing strain gauges. The first and second strain gauges are connected to the two bridge sides, respectively, and are attached to the second surface to be attached, which is the other of the pair, and attached to the semi-circular portion of the strain-flexing plate by the semi-circular portion. The third and fourth bridge sides adjacent to the bridge side are each connected to the circuit, respectively.

Hereinafter, an embodiment of the present invention will be specifically described with reference to the accompanying drawings.

FIG. 1 is a side view showing the entire structure of the torque measuring device according to the present invention by partially breaking it, FIG. 2 is a front view of the embodiment shown in FIG. 1 (however, wheels are omitted), and FIG. The figure is a side view showing the structure of the wheel slip prevention mechanism part of the embodiment shown in FIG. 1 partially broken (provided with a speed detection device), and FIG. 4 shows the other wheel slip prevention mechanism part. It is a side view which abbreviate | omits a part of fracture | rupture part of FIG. 1 which shows a structure.

In FIGS. 1 and 2, 1 is a drive shaft serving as a rotating shaft for driving wheels, 1a is a wheel mounting portion for mounting the wheel of the drive shaft 1, 1b is a plant attached to the wheel mounting portion 1a, and a male screw is attached. A mounting screw formed as a hub bolt into which a hub nut described later is screwed, the wheel mounting portion 1a shown in this figure has four mounting screws 1b, and a pitch circle diameter on which the mounting screw 1b is arranged (hereinafter, abbreviated as "PCD"). Is 100 mm.

Reference numeral 2 is a caliper composed of a brake drum, 3 is the above wheel (however, the tire portion is omitted), 3a is a rim of the wheel 3, 4 is a disc of the wheel 3 integrated with the rim 3a by welding, FIG. 4a indicated by a middle two-dot chain line will be described later in detail, but in this example, the disc 4 has already been cut out into a large circular shape and does not exist, 5 is an annular disc spacer, and 5a is this disc spacer 5 A welding screw hole formed by firmly fixing the disk spacer 5 and the disk 4 to each other, 7 an axle adapter mounted on the wheel mounting portion 1a, 7a and 7b an axle adapter A counterbore hole and a hub bolt insertion hole for a hub bolt as a mounting bolt for detachably mounting 7; 8 is a spigot portion which is formed in a circular shape on the right end surface of the axle adapter 7 to form a step portion; Similarly the axle adapter 7 in the strain generating plate mounting screw hole internally threaded in the through hole formed in the flange-shaped portion extending on the outer circumference of the axle adapter 7 is formed by screwed
In the figure, four counterbored holes 7a and 7b for the hub bolt are provided, PCD = 100, corresponding to the wheel mounting portion 1a.
mm, but the configuration of the wheel mounting part 1a of other vehicle types, that is, 5 or 6 mounting screws 1b, and 1 for PCD
It is assumed that a plurality of axle adapters 7 capable of handling either 10 mm or 114.3 mm are prepared. In these axle adapters 7, naturally, the configurations of the spigot portion 8 and the strain-flexing plate mounting screw hole 9 are common to all the axle adapters 7 (the same configuration).

Reference numeral 10 is a generally disk-shaped overall shape, and the flexure plate in which the axle adapter 7 and the disk spacer 5 are superposed on the left end face side portion near the center and the peripheral edge portion without contacting each other. (Details will be described later), 11 is a strain-flexing piece, 12 is a mounting hole formed in a portion communicating with the strain-flexing plate mounting screw hole 9, and 13 is fitted with the spigot portion 8 formed on the axle adapter 7. The spigot part that fulfills the function of aligning the heart, 14
Is a mounting hole formed at a position communicating with the mounting screw hole 5a, 15 is an annular groove formed in a concave cross-section along the entire circumference of the right end face side near the strain-flexing piece 11, and 16 is the strain-flexing piece 11 Inside, the mounting bolt as a first bolt, which is inserted into the mounting hole 12 and screwed into the strain-flexing plate mounting screw hole 9 to firmly fix the axle adapter 7 and the strain-flexing plate 10, 16a is The heads 17 of the mounting bolts 16 have a substantially disc shape, and the cover is overlapped with the peripheral portion of the strain plate 10 on the right end surface side. The mounting bolts 16 are inserted into the mounting bolts 16. A through hole having a gap so that the cover 17 does not come in contact with the left end of the cover 17 at a predetermined depth leaving a portion near the outer peripheral edge of the cover 17 so that the cover 17 does not come into contact with the flexure plate 10 (in particular, the flexure piece 11). A circular recess whose surface is cut into a circular shape, and 20 and 20a are counterbore holes and insertion holes provided at positions communicating with the mounting hole 14. , 21 are sequentially inserted into the counterbore hole 20, the insertion hole 20a, and the mounting hole 14 on the outer side of the strain-flexing piece 11, and are screwed into the mounting screw hole 5a. Is a cover mounting bolt as a second bolt for firmly fixing the gears together, 22 is a derailment prevention mechanism section described in detail later, and 23 is a gear mounting screw for mounting a gear for speed detection (in this figure, the above gear Is not attached), 24 is a slip ring device, 25 is a tire sensor position of the wheel 3, and 25a is a regular offset position. It should be noted that the strain-flexing plate 10, the cover 17, and the detachment prevention mechanism section
22, with slip ring device 24, the following torque detector
26.

In the following drawings, the same members as those shown in FIGS. 1 and 2 are designated by the same reference numerals, and the duplicated description will be omitted.

In FIG. 3, 27 is a hub nut for mounting the axle adapter 7 on the wheel mounting portion 1a, and 28 to 35 are schematic paths for transmitting the rotational force from the drive shaft 1 to the wheel 3, that is, the disk 4. Indicated arrow, 36 is an arrow indicating the direction of force applied in the direction of derailing, 37 is connected to the annular groove 15, a terminal chamber for accommodating a terminal plate (not shown) or connecting a strain gauge described later, Reference numeral 38 is an oblique wiring hole communicating with the annular groove 15, the circular recess 19 and the terminal chamber 37, 39 is a connecting portion formed in the central portion of the flexure plate 10, and 40 is a pipe coaxially bored. -Shaped connecting hole, 41 is provided on the right side of the connecting portion 39.
Is a columnar portion projecting in a substantially cylindrical shape, 42 is attached to the right end surface of the columnar portion 41, and is a substantially disk-shaped derailing stopper having a larger diameter than the columnar portion 41, and 42a is the derailing stopper 42 A stopper mounting bolt, 42b is a gap for preventing the cover 17 and the derailing stopper 42 from coming into contact with each other, and 43 is a flange-like projection on the right center portion of the cover 17 so that the columnar portion 41 of the strain plate 10 is concentrically loosened. A cover flange portion to be fitted, 44 is a bearing inserted between the cover flange portion 43 and the columnar portion 41, 44a is a snap ring for fixing one end of the bearing 44, 45 is the columnar portion 41 and the flange A dustproof and dripproof packing provided at the end of fitting with the portion 43.

In FIG. 4, 46 is the head 16a of the mounting bolt 16 of FIG.
Is a bolt-type stopper formed of a bolt head having a hexagonal outer circumference that is larger than the diameter of the through hole 18 and does not contact the right end surface of the cover 17 and the through hole 18.

5 and 6 are diagrams showing the structure of the strain-flexing plate 10 in detail. FIG. 5 is a front view, and FIG. 6 is a sectional view taken along the line AA 'in FIG.

In FIGS. 5 and 6, reference numeral 14 has already been described, but 16 mounting holes which are drilled on the same radius and through which the cover mounting bolt 21 of FIG. 1 is inserted, 15 have already been described. Hole
An annular groove having a concave cross-section formed in the circumferential direction at a radial position slightly inside 14; 47 is a wiring groove having a concave cross-section that communicates from the annular groove 15 to the terminal chamber 37; 48 is the wiring oblique hole from the terminal chamber 37.
The wiring groove communicates with 38 and has a concave cross-section.

Reference numeral 49 denotes 32 strain-flexing piece forming holes as a large number of holes evenly arranged inward of the annular groove 15, and 11 has already been described, but the space between the adjacent strain-generating piece forming holes 49 is between the two holes. Has a minimum width S and has a thickness t in the axial direction, and is a spoke-shaped strain element formed so that the thickness t is larger than the minimum width S. 50 is a strain element for torque which is selected every other one of the strain elements 11 in the circumferential direction, 51 and 52 are provided on the strain element 50 for torque of the strain plate 10, and a strain gauge described later is provided. It is the strain gauge attachment surface to be attached (hereinafter, simply referred to as “attachment surface”).

Each flexure piece 11 has a surface seen from the clockwise direction and a surface seen from the counterclockwise direction. In this example, the former is referred to as a first attachment scheduled surface and the latter is referred to as a second attachment scheduled surface. To do. Therefore, the planned attachment surfaces 51 and 52 become the first planned attachment surface 52 and the second planned attachment surface 51, respectively. A1, A2,
A3, ..., A16 are the first scheduled attachment surface 5 of the strain element 50 for each torque.
Strain gauges for torque detection attached to 2, B1, B2, B3,
...... B16 is a strain gauge for torque detection that is similarly attached to the second attachment surface 51 of each strain element 50 for torque.

FIG. 7 is an enlarged cross-sectional view showing an attached state of a strain gauge for torque detection as a representative of the portion of the second scheduled attachment surface 51 shown in FIG.

In FIG. 7, reference numeral 53 indicates the position of the minimum width S of each flexure piece 11, and in this example, the center of the flexure piece 50 substantially coincides with the center of the flexure piece forming hole 49. 54 is the base of strain gauge B11, 5
Reference numeral 5 is a strain receiving portion (so-called gauge grid) for detecting the bending stress, 56 is a gauge tab, and 57 is a gauge lead.
As can be seen from the figure, the strain receiving section 55 of the strain gauge B11 is
The base 54 is attached to the second scheduled surface 51 so that the maximum bending stress is generated at a position P inward of the center 53. The applicant has experimentally confirmed that the above-mentioned position generates the maximum bending stress.

FIG. 8 is a circuit diagram showing an embodiment of a torque detecting bridge (Wheatstone bridge).

In the figure, 61 to 64 are connection terminals of the bridge, and 65 is a series branch path in which strain gauges A1 to A8 attached to a portion corresponding to a half circumference of the strain plate 10 are connected in series.
The first side 66 connected in between is opposed to the first side 65, and the series branch of the strain gauges A9 to A16 attached to the portion corresponding to the remaining half circumference is connected to the connection terminal 62. The second side 67, 68 connected between the first and second sides 64, 64 is adjacent to the first side 65 and the second side 66 and faces each other. Of these, 67 is a half circumference of the flexure plate 10. The third side, which is formed by connecting the series branches of the strain gauges B1 to B8 of between the connection terminals 61 and 64, 6
Reference numeral 8 denotes a fourth side formed by connecting in series the branch branches of the strain gauges B9 to B16 attached to the portion corresponding to the remaining half circumference of the strain plate 10 in parallel between the connection terminals 62 and 63. In this example, the connection terminals 61 and 62 are output terminals of the bridge, and the connection terminals 63 and 64 are bridge power supply input terminals.

FIG. 9 is an enlarged plan view showing, in an exaggerated manner, the vicinity of the torque straining piece 50 having the second scheduled attachment surface 51 in order to explain the torque detecting operation.

In the figure, 69 and 70 are arrows indicating the direction of action of force and the direction of action of reaction force, 71 is the outer part of the strain element 50 for torque, 72 is the inner part, and 73 is the second attachment, for example. FIG. 6 is a diagram showing a distribution of bending stress on the surface 51.

The assembling procedure of the present embodiment configured as above will be briefly described. First, the strain gauge is attached to the position shown in FIG. 5, more specifically, in the state shown in FIG. Since the connection of these strain gauges is a series connection for each half circumference of the strain plate 10 as shown in FIG.
To describe A1 to A8 as representatives, the gauge leads A1 to A2 and A2 to A3 are sequentially connected in series, and the connected gauge leads are provided along the annular groove 15. Further, the gauge leads of the strain gauges A1 and B1 that are connected to the connection terminals 61 are connected in the terminal chamber 37 along the nearest wiring groove 47, respectively, and from this connection point to another lead wire. Then, preparation is made so that the slip ring device 24 can be connected through the wiring groove 48, the wiring oblique hole 38, and the communication hole 40 in order.

On the other hand, the primary processing of the wheel 3 is performed. That is, a commercially available general wheel 3 has a disc 4 as shown in FIG.
Is integrally molded up to the cutting portion 4a indicated by the one-dot chain line, so this cutting portion 4a is cut into a large circular shape and removed,
The disk spacer 5 is inserted into the circular hole formed by this, and welded at the welding portion 6 to firmly fix the disk 4 and the disk spacer 5. By this primary processing, the regular offset 25a can be held.

Next, the strain-flexing plate 10 is superposed on the disc spacer 5 integrated with the wheel 3 to form the columnar portion 41 and the connecting portion 39 of the strain-flexing plate 10.
The bearing (44) and the packing (45) are fitted into the above, respectively, and then the cover flange portion (43) is fitted into the bearing (44) so that the cover (17) is superposed on the strain plate (10). Then, attach the cover mounting bolt 21 to the counterbore hole 20 and the insertion hole of the cover 17.
20a and the mounting plate 14 are sequentially inserted into the mounting holes 14 of the strain plate 10 and screwed into the mounting screw holes 5a of the disk spacer 5 to firmly fix them.

Then, the derailing stopper 42 is attached to the right end surface of the columnar portion 41 with the stopper attaching bolt 42a. Further contact hole 40
The lead wire that has been used up to now is connected to the rotating body portion (slip ring) side of the slip ring device 24, and the rotating body portion and the columnar portion 41 are connected to the concentric portion.

On the other hand, the axle adapter 7 is firmly fixed to the wheel mounting portion 1a of the drive shaft 1 with the hub nut 27. And the wheels 3 as described above
The torque detector 26 integrated with the
8, 13 are fitted and overlapped on the axle adapter 7, and the mounting bolts 16 are sequentially inserted into the through holes 18 of the cover 17 and the mounting holes of the strain plate 10.
The torque detector 28 is attached to the axle adapter 7 by screwing it into the strain-flexing plate mounting screw hole 9 for completion.

Therefore, the torque detector 26 can be used in common by simply replacing the number of the axle adapters 7 corresponding to the type of the wheel mounting portion 1a. Therefore, only one torque detector 26 is required, and the economical merit is extremely large.

Next, the operation of this embodiment thus assembled will be described. First, the torque detection operation will be described.

In FIG. 5, it is assumed that the outer peripheral side of the flexure plate 10 is fixed and the inner peripheral side is given a rotational force in the clockwise direction indicated by the arrow M.

The deformation mode of the strain-flexing piece 50 at this time will be described based on FIG. 9 as a representative of the strain gauges A11 and B11 attached. By receiving a force in the direction of the arrow 69, the first planned attachment surface 52 side of the inner part 72 of the strain-flexing piece 50 is compressed, and the opposite second planned attachment surface 51 side is expanded. Therefore strain gauge A1
The resistance value of 1 decreases and the resistance value of the strain gauge B11 increases. That is, the resistance values of the strain gauges B1 to B16 attached to the first attachment surface 52 of the strain-flexing plate 10 increase, and the second attachment surface 5
The resistance value of strain gauges A1 to A16 attached to 1 decreases.
That is, in the bridge shown in FIG. 8, the resistance values of the first side 65 and the second side 66 decrease, and the resistance values of the third side 67 and the fourth side 68 increase, so that the connection terminals 61 to 62 are detected. An electric current flows. It goes without saying that if the direction of the rotational force M is reversed, the direction of the detected current is reversed.

Next, the removal of interference in this torque detection operation will be described. First, the force in the axial direction of the drive shaft 1, that is, the interference of the side force is first reduced by making the thickness t sufficiently larger than the width S of the strain-flexing piece 11.
In addition, the strain gauges A1 to A16 and B16 to B16 for torque detection are attached to the inner side where large bending stress is generated as shown in the diagram 73 of FIG. 9, and as shown in FIG. The sensitive axis of is selected in the orthogonal direction in which the influence of the side force is the least, and thirdly, the slight influence is electrically canceled by the distribution of the strain gauges on each side of the torque detection bridge. Eventually, the side force will have no practical effect.

Next, it is assumed that a vertical force indicated by an arrow V in FIG. 5, that is, a wheel load is received. In order not to complicate the explanation, the pair of strain gauges A15 and B15 that receive the largest wheel load, A
A pair of 7, B7 is explained as a representative. By the force V, the strain gauges A7 and B15 are expanded, and conversely the strain gauges B7 and A15 are compressed. Therefore, in the bridge of FIG. 8, the resistance increases at the first side 65 and the fourth side 68, and the resistance decreases at the third side 67 and the second side 66, and the potential between the connection terminals 61 and 62 does not change. The load is canceled.

Further, when a force (wheel load) in the vertical direction V indicated by an arrow V is received, a strain-flexing piece located above a horizontal line passing through the drive shaft 1
11 is stretched, but a strain-flexing piece located below the horizontal line
11 is compressed, and its expansion amount and compression amount are equal, so
The effect of vertical forces is canceled electrically.

Next, the action when the strain-flexing piece 11 is destroyed for some reason (for example, overload), that is, the action of the wheel slip prevention mechanism 22 will be described.

As shown in FIG. 3, the rotational force of the drive shaft 1 is generated by the wheel mounting portion 1a.
Is transmitted to the axle adapter 7 through the hub bolt 1b in the order of arrows 28 and 29, and further through the strain-flexing plate mounting bolt 16 as the first bolt, in the order of arrows 30 and 31 of the strain-flexing piece 11. To the outer part (lower part in the figure), to the outer part via the strain-flexing piece 11 (the torque is detected at this time), and to the arrow via the cover mounting bolt 21 as the second bolt. 3
2, 33, 34 are transmitted in this order, and finally are transmitted from the disc spacer 5 to the disc 4 as indicated by arrow 35, and the wheel 3 (not shown in FIG. 3) rotates.

Now, it is assumed that the flexure piece 11 is destroyed here. In order to make the explanation easy to understand, it is assumed that the strain-flexing piece 11 is completely destroyed. Therefore, the inner side (lower side in the figure) and the outer side (lower side in the figure) of the strain-flexing piece 11 are completely separated. It is assumed that Then, hereinafter, a combined body including the wheel 3, the outer peripheral edge portion of the strain-flexing plate 10 (the portion on the outer side of the strain-flexing piece 11) and the cover 17 will be referred to as a separating body portion.

In such a state, the rotational force is transmitted only to the arrow 31, and the wheel 3 does not rotate. Conversely, it means that the braking force cannot be obtained even when the brake is applied, which is a very dangerous state. In the example of FIG. 3, in such a case, with respect to the rotation direction, the head portion 16a of the strain-flexing plate mounting bolt 16 is restricted by the through hole 18 of the cover 17, and between the through hole 18 and the head portion 16a. The free rotation is possible only by a small gap in the above, and the separating body portion can substantially transmit the rotational force of the axle adapter 7, and the brake is also effective.

In addition, when the flexure piece 11 is destroyed as described above, the flexure piece
Although the separation body portion, that is, the axis of the wheel 3 and the axis of the drive shaft 1 tend to deviate by the radial length of 11, the flange portion 43 of the cover 17 causes the strain plate through the bearing 44. Since they are fitted concentrically with the ten columnar portions 41, the axis does not deviate as described above.

Further, with respect to the axial direction, the separator part is
Since it abuts on the central portion of the wheel, it cannot move in the direction of the drive shaft 1, but tries to move in the direction of derailing as indicated by the arrow 36. However, in this embodiment, the cover flange portion 43, which is about to move in the direction of the arrow 36, is regulated by the derailment stopper 42, and therefore the derailment is not performed.

The gap 42b is defined by the cover flange portion 43 and the derailing stopper 42.
Since it is a slight amount that does not come into contact with and influence the torque measurement, the influence can be ignored regarding the above regulation.

Further, an annular groove 15, a circular recess 19, a gap between the head portion 16a of the flexure plate mounting bolt 16 and the through hole 18, a gap 42b between the cover flange 43 and the derailing stopper 42 are provided, and a bearing 44 is further inserted. As a result, the cover 17 does not restrict the deformation of the strain-flexing piece 11 that receives and deforms the torque to be measured, that is, the cover 17 is related to the torque detection operation.
Since the portion of the strain-flexing plate 10 closer to the center than the strain-flexing piece 11 is non-contacted or loosely overlapped, it does not affect the torque detection.

Next, the operation of the other wheel slip prevention mechanism shown in FIG. 4 will be briefly described.

Since the above-mentioned separation body portion which is going to move in the direction of the arrow 36 is restricted by the bolt-shaped stopper 46, it does not come off. Other functions are similar to those described with reference to FIG.

Thus, according to the present embodiment, the wheel mounting portion of the drive shaft 1
Prepare the number of axle adapters 7 corresponding to the type (structure) of 1a, fix the disk spacer 5 to the disk 4 of the wheel 3 at the welded portion 6, and fix the strain plate 10 and the cover 17 by superposing on this. Then, a derailment stopper 42 is provided on the columnar portion 41 of the strain-flexing plate 10 to form a derailment prevention mechanism portion 22, and a torque detector 26 formed by connecting a slip ring device 24 thereto is fixed to the axle adapter 7. With this configuration, there is an advantage that one torque detector 26 can be used regardless of the type (vehicle type) of the wheel mounting portion 1a and the type of the wheel 3.

Further, even if the strain-flexing piece 11 is broken, the wheel-release prevention mechanism can prevent the wheel-release, and the strain-flexing plate 1 mounting bolt 16 and the cover 17 can maintain the transmission of the rotational force.
There is an advantage that the driving force and the braking force are retained and the above-mentioned danger can be prevented.

In addition, as shown in FIG. 5, strain gauges A1 to A16, B
Since the attachment positions of 1 to B16 are arranged so that the strain receiving portion 55 is on the inner side by P from the position of the minimum width S of the strain-flexing piece 11.
There is an advantage that the maximum output is obtained and the torque detection sensitivity is high.

The present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the invention.

For example, as shown in FIG. 3, a speed detecting device 74 may be interposed between the slip ring device 24 and the wheel slip prevention mechanism 22. That is, the structure thereof will be described. Reference numeral 75 denotes a speed detecting gear having a tubular portion on the left end face side, and 23 has been touched in the outer periphery of the cover flange portion 43 concentrically, as mentioned in the explanation of FIG. A gear mounting screw that rotatably supports the gear 75 by fixing the tubular portion to the cover flange portion 43, 76 is a magnetic sensor that detects the rotation speed of the gear 75, and 77 is a case of the slip ring device 24. A sensor support arm that is continuously provided from above and supports the magnetic sensor 76, a coupling flange portion 78a is coupled to the gear 75 by a mounting screw 78b, and is rotatably supported concentrically with the gear 75. It is a rotating body portion of the slip ring device 24. Since the operation of the speed detecting device 74 is known, it will be omitted.

Further, the bolt-type stopper 46 shown in FIG. 4 is not limited to the hexagonal outer periphery, and may have an octagonal shape, or may be a so-called hexagonal bolt having a circular outer periphery and having a hexagonal hole. Good.

(E) Effect As described in detail above, according to the present invention, firstly, the present invention acts on the wheel without being substantially affected by the axial load and the force in the axial direction of the drive shaft, that is, the side force. It is possible to provide a torque measuring device that can faithfully convert torque into an electric quantity.

Secondly, the device can be applied to all types of wheels by preparing only a plurality of axle adapters that are simple in structure and can be easily manufactured according to the type of wheel and the structure of the wheel mounting portion of the drive shaft. Since they can be mounted in common, each time the type of wheel and the structure of the wheel mounting part differ, a strain plate corresponding to this, or a large number of discs and connecting members provided with a detection part are manufactured. It is possible to provide a torque measuring device which is easy to manufacture and has a small number of component parts as compared with what must be kept, and which is therefore very economical.

Thirdly, there is provided a torque measuring device capable of holding a regular offset, and therefore capable of accurately measuring torque under the condition that an offset change gives an error to the measurement under conditions that are close to those of an actual vehicle. Can be provided.

Fourthly, even if all of the strain-flexing pieces are destroyed by an unpredictable force applied to the strain-flexing pieces of the strain-flexing plate due to an overload or the like on the present apparatus, the wheel-release prevention mechanism can prevent the wheel-release. At the same time, the transmission of the rotational force can be held by the engagement of the first bolt and the through hole formed in the cover, so that the driving force and the braking force can be held as well as the stable running after the fact. It is possible to provide a torque measuring device capable of reliably avoiding a dangerous state in which a braking force cannot be obtained even when a brake is applied when the wheel and the disc of the wheel are separated, like the device. it can.

[Brief description of drawings]

FIG. 1 is a side view showing the entire structure of a torque measuring device according to the present invention with a part thereof broken away, FIG. 2 is a front view in which the wheels of the embodiment shown in FIG. 1 are omitted, and FIG. 1 is a side view showing a part of the wheel slip prevention mechanism part of the embodiment shown in FIG. 1 (however, a speed detecting device is attached), and FIG. 4 shows a structure of another wheel slip prevention mechanism part. A side view of the broken portion of FIG. 1 partially omitted, and FIGS. 5 and 6 are diagrams showing in detail the structure of the strain-flexing plate, of which FIG. 5 is a front view and FIG. 5 is a sectional view taken along the line AA 'in FIG. 5, and FIG.
FIG. 8 is an enlarged cross-sectional view showing an attachment state of a strain gauge for torque detection, which is representative of one of the planned attachment surfaces, FIG. 8 is a circuit diagram showing an embodiment of a Wheatstone bridge for torque detection, and FIG. FIG. 6 is an enlarged plan view exaggeratingly showing the vicinity of the torque strain piece to explain the detection operation. 1 ... Drive shaft, 1a ... Wheel mounting portion, 1b ... Mounting screw (hub bolt), 2 ... Caliper, 3 ... Wheel, 3a ... Rim, 4 ... Disc, 4a ... Cutting portion, 5 ... … Disc spacer, 5a… Mounting screw hole, 6… Welded part, 7… Axle adapter, 7a, 20… Counterbore hole, 7b, 20a… Insertion hole, 8, 1
3 ... Inlay part, 9 ... Strain plate mounting screw hole, 10 ... Strain plate, 11 ... Strain piece, 12,14 ... Mounting hole, 15 ... Annular groove, 16 ... Strain plate Mounting bolt (first bolt), 16a ...
… Head, 17 …… Cover, 18 …… Through hole, 19 …… Circular recess, 21 …… Cover mounting bolt (second bolt), 22 ……
Wheel loss prevention mechanism, 24 …… Slip ring device, 25a ……
Regular offset position, 26 …… Torque detector, 27 …… Hub nut, 41 …… Column, 42 …… Derailment stopper, 46 ……
Bolt type stopper, 49 …… Strain bending piece forming hole, 50 …… Torque bending piece, 51,52 …… Strain gauge attachment surface, 65 ……
1st side of bridge, 66 ... 2nd side of bridge, 67 ... 3rd side of bridge, 68 ... 4th side of bridge, 74 ... Speed detector, A1 to A16, B1 to B16 .. gauge.

Claims (2)

[Scope of utility model registration request] 1. A torque measuring device for measuring a torque acting on a wheel by converting it into an electric quantity so that a hub nut can be mounted on a wheel mounting portion of a drive shaft in which hub bolts having different numbers and disposition positions are provided depending on a vehicle type. A plurality of axle adapters each having a hub bolt insertion hole that fits each vehicle type, a wheel having a large circular hole formed in the center of the disk, and a regular wheel fitted into the circular hole of the wheel. The disk spacer firmly fixed to the wheel while maintaining the same offset as the above, and the overall shape is a substantially disc shape, and the axle adapter is concentric with the central portion and the disk spacer is concentric with the peripheral portion. Are uniformly overlapped with each other, and the number of holes which can be divided by at least 4 is evenly distributed on the circumference of the predetermined radius passing between the center portion and the peripheral portion. A plurality of spoke-shaped strain elements extending in the radial direction are formed between the holes adjacent to each other by being formed, and the axial thickness of the strain elements is formed to be larger than the minimum width in the radial direction. A strain plate that is firmly fixed to the axle adapter with a first bolt in the vicinity of the inside of the strain piece, and a strain plate that has a substantially disc shape and is located outside the strain piece to the strain plate. A through hole having a diameter that is overlapped with the first bolt and does not contact the outer circumference of the first bolt is bored, and the second bolt is attached to the disk spacer with the second bolt in a state where the through holes can be fitted into the first bolt and the first bolt, respectively. If the strain piece breaks at a position near the center of the strain plate and the cover firmly fixed together with the strain plate, the cover is prevented from moving outward a certain amount or more in the axial direction. Always touch the cover to get A derailing prevention mechanism attached to the strain generating plate gap exist to the like not,
A pair of the strain-flexing plates sandwiching a predetermined strain-deflecting piece, and a strain gauge attached to each of the first scheduled attachment surface on one side and the second scheduled attachment surface on the other side of the hole. The strain gauges attached to the first surface to be attached, which is one of the above, are respectively connected to the two opposing first and second bridge sides by circuits, and are attached to the second surface to be attached, which is the other of the pair. A torque measuring device characterized in that a strain gauge is circuit-connected to third and fourth bridge sides adjacent to the first and second bridge sides, respectively, to form a Wheatstone bridge for torque detection. 2. The Wheatstone bridge has two strain gauges attached to a first surface to be attached, which is one of a pair, and a strain gauge attached to a half circumference portion of the strain-flexing plate. Of the strain gauges, which are respectively connected to the bridge sides of the pair, and are attached to the second surface to be attached forming the other side of the pair and attached to the semi-circular portion of the strain-flexing plate by the semi-circular portions. The torque measuring device according to claim 1, wherein the torque measuring device is configured by respectively connecting circuits to the third and fourth bridge sides adjacent to the bridge side.