JP3099701B2 - Vehicle or / and payload measurement device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an apparatus for measuring the weight of a vehicle and / or a load mounted on the vehicle, and more particularly to a vehicle and / or an apparatus for measuring the weight of a vehicle having a trunnion shaft on a tandem shaft.

[0002]

2. Description of the Related Art Conventionally, load measurement of a vehicle is mainly performed on a large vehicle such as a truck. Normally, the load of a vehicle is measured by a load measuring device installed on the road. A wheel is placed on a load plate provided with a load converter, and the wheel weight or axle weight of the wheel is measured. And the like are added to obtain the vehicle weight, and the weight of the occupants and the vehicle itself is subtracted from the measured vehicle weight to obtain the loaded load.

However, since the above-described load measuring device is installed only at a specific location on a road,
In addition, since the load measuring device itself is large and the installation cost is high, there are restrictions on the installation location and the number of installations, and it is not possible to place it at all the loading locations, and overloading often occurs without the driver's or loader's recognition. There was a possibility.

[0004]

In order to solve such a drawback, it has been studied to incorporate a load measuring device into the vehicle itself. For example, Japanese Unexamined Utility Model Publication No. 6-16826 discloses a technique in which a strain gauge type sensing element is provided in a slide plate or a vehicle height adjusting plate located between a leaf spring and an axle case of a vehicle.

However, in the case where the sensing element is mounted in the slide plate, the leaf spring slides on the slide plate surface, so that the slide plate may be worn and the strength of the slide plate may change the output characteristics of the sensing element. There is a problem.

In order to solve such a drawback, two heavy axles, which are often used as rear axles for heavy trucks and rough terrain trucks, are used.
In a truck having a so-called tandem axle structure in which a road surface pressure is reduced by providing the center, as shown in Japanese Utility Model Application Laid-Open No. 6-69759, the center of a trunnion shaft connecting a shackle supporting a vehicle suspension and a bracket attached to a vehicle body frame. There has been proposed a vehicle load measuring device in which a shaft hole is formed in a line along an axial direction, and a sensing element for detecting distortion is fitted and arranged in the shaft hole.

Referring to FIG. 11, such a structure will be described. A bracket 2 fixed to a carrier frame 1 (not shown)
A trunnion shaft 3 is fitted to the shaft. A leaf spring 11 is supported via a spring seat 4 at an end of the trunnion shaft 3 protruding from a bracket fitting portion. A hollow hole 6 is formed from the end face of the trunnion shaft 3 along the center axis direction, and a magnetostrictive sensing element 7 is fitted and mounted inside the hole 6. Of course, it is also described that the sensing element 7 may be constituted by a strain gauge type sensing element 7.

In the case of the magnetostrictive sensing element 7, four small holes are formed in a cross direction in a plate-shaped portion made of a magnetic material such as permalloy, and a coil is wound in a cross shape through the holes. And the lead wire 8 is drawn out from the coil. And the lead wire 8
Is drawn out from the shaft hole 6 of the trunnion shaft 3 to the outside.

According to the prior art, the load of the vehicle is applied to the trunnion shaft 3 supporting the leaf spring 11 via the bracket 2. For this reason, a shearing force acts on the trunnion shaft 3, and the sensing element 7 disposed inside the trunnion shaft 3 is distorted, so that the load on the vehicle (specifically, the sprung load of the suspension on the trunnion shaft 3) is detected.

In the prior art, in order to effectively detect the shear strain, a detection center of the sensing element 7 is disposed at a band-shaped gap position (hereinafter referred to as a band-shaped gap position) between an end face of a bracket and a spring seat. doing.

However, in the above-described configuration in which the detection center of the sensing element 7 is disposed at the position of the band-shaped gap, sensitivity, accuracy, and stability are not sufficient for shear strain (stress) measurement, and there are various practical problems. Was.

According to the present invention, as a result of various studies on the factors causing the above-mentioned instability of the sensitivity, accuracy, etc., it was found that there was a problem in the arrangement position, and in particular, the trunnion shaft 3 Provided is a vehicle or / and a loaded weight measuring device provided with a sensing element for obtaining a shear strain (stress) distribution when receiving the shear stress and efficiently measuring the shear strain (stress) based on the shear stress distribution. For the purpose.

[0013]

SUMMARY OF THE INVENTION In view of the above technical problem, according to the present invention, a hole 6 is formed in a trunnion shaft 3 fitted and supported by a trunnion bracket 2 mounted on a vehicle body frame 1 along an axial direction. The present invention is applied to a vehicle or / and a loaded weight measuring apparatus in which a sensing element 7 for detecting a strain is fitted and arranged in the hole 6, and is characterized by the arrangement of the sensing element 7. The position is shifted by a predetermined distance in the axial direction XX from the strip-shaped gap position CC, and the sensing element 7 is placed at a position substantially corresponding to the maximum stress area of the shear stress diagram on the hole 6 axis. It is characterized by being arranged.

That is, as shown in FIG. 1 and FIG.
In the central axis of the trunnion shaft 3 which coincides with the axis, the maximum stress range of the shear stress diagram is in the P ₁ and P ₂ point out from the bracket 2 end surface, and said P ₁ or P ₂
Point, than fulcrum C _P located on the intersection of the bracket 2 end surface and the shaft axis 3a periphery, 30 to 60 ° in the axial direction relative to the shaft axis 3a perpendicular plane, preferably 40 ° to 50
°, more preferably 45 °.

[0015] Then the maximum stress zone is located in the P ₁ and P ₂ point in the shaft axis center line, vertical trunnion shaft 3 through the trunnion shaft 3 is subjected to load chi-Y axis plane (the pin central axis in the cross section), as shown in FIG. 3, there is a maximum stress range in P _3, P ₄ points deviated fulcrum C _P side of the P ₁ and P ₂ points. (In this case, the positive principal stress is the tensile stress and the negative principal stress is the compressive stress. However, since it is not clear in the drawing, the reference photograph 1 corresponding to FIG. 2 and the maximum on the Χ-Y axis plane where the trunnion shaft receives the load are shown. Reference photograph 2 corresponding to the stress distribution diagram showing the stress area in color is attached.) Therefore, in the case of the present invention, it is more preferable that the arrangement position of the sensing element 7 is set to the maximum stress with respect to the center axis of the trunnion shaft 3. it is preferable to dispose by shifting the position in the radial direction in the development area side (fulcrum C _P side). That is, the maximum stress range of shear stress diagram on the hole 6 axis, when the hole 6 is positioned on the central axis is the P ₁ and P ₂ points, and chi-Y
When a hole 6 is formed on an arbitrary axis of the shaft surface, P ₃
And good P ₄ points.

However, since it is necessary to make a hole 6 for fitting the sensing element 7 in the trunnion shaft 3, it cannot be arranged on the outer peripheral side of the pin more than the strength thereof. However, it is preferable that the bending stress of the trunnion shaft 3 is low, that is, equal to or less than の of the shaft radius.

The maximum stress area is determined by the band-shaped gap position C-.
It is located on both left and right sides of C, and its main stresses are in opposite directions of positive and negative (see tensile stress and compressive stress in FIG. 3).
Therefore positioned in the axial left and right sides, the maximum stress range substantially corresponding two positions (P ₁ and P ₂ point, and P ₃ and P ₄ points), the disposed respectively the sensing element 7, the 2
Between the output signals of the two sensing elements 7 (ρ ₁ −ρ ₂ ,
By taking ₃ −ρ ₄ ), it is possible to obtain a gain twice as large as in the case of one, and it is possible to detect signals with higher sensitivity and accuracy. The output sensitivity is further improved by fitting the sensor body 70 (see FIG. 13) including the sensing element 7 to the trunnion shaft 3 by interference fit.

[0018]

DETAILED DESCRIPTION OF THE INVENTION The load from the upper peripheral surface of the shaft end supporting the leaf spring to the lower end of the bracket second end face which is fitted and fixed as a fulcrum C _P in the trunnion shaft 3 according to the prior art To receive
It was believed that the trunnion shaft 3 had a bending moment and a shearing force based on the beam theory.
Therefore, the fulcrum of the bracket 2 in the prior art C _P position immediately above, in other words the bracket 2 end surface and the sensing element 7 at the intersections P ₀ of the shaft axis 3a central axis
And the above-mentioned shear strain (stress) was measured.

However, when the shear stress diagram when the trunnion shaft 3 receives the load described above is obtained by the finite element method analysis CAE using a supercomputer, as shown in FIG. 2, the intersection position P _{0 is obtained.} When the sensing element 7 is disposed above the intersection position P ₀ , the sensitivity is low and the signal output (gain) greatly varies due to a slight change in the arrangement position in the axial direction. A stable gain cannot be obtained.

[0020] Therefore, in the present invention, on the central axis of the trunnion shaft 3, the maximum stress range of the shear stress diagram is from fulcrum C _P on the bracket second end face,
It is found that the imaginary line K is turned at an angle of about 45 ° in the axial direction with respect to the plane orthogonal to the shaft axis 3a and is located at the intersections {P ₂ (leaf spring 11 side) and P ₁ point (bracket 2 side)}. is for disposing the sensing element 7 in either or both of the two P ₂ or P ₁ point.

FIG. 12 is a sensing element which is disposed on the P ₂ points, a graph showing the relationship of the load / gain output of the sensing device which is arranged in the intersecting position P ₀ point, as will be understood from this figure It can be understood that the sensitivity is more than doubled at the points P ₂ and P ₀ . The reason that the maximum stress region of the shear stress diagram exists at a position shifted by a predetermined distance in the axial direction from the intersection is that the main stress is inclined at about 45 ° with respect to the horizontal axis, so that the shear stress is in the axial direction. It is presumed that it becomes larger at the position shifted to.

[0022] In this case, because the maximum stress is higher than P ₁ point in the bracket 2 side if the sensing device 7 is disposed on the P ₂ point in the leaf-spring-side, good sensitivity, and P ₁ point of the bracket 2 side When the sensing element 7 is disposed in the shackle side, the inflection point curve at the top of the maximum stress area
_Since it is gentler than the _two points, the element in which the gain fluctuates even if the disposition position in the axial direction slightly fluctuates is further reduced, and the stability is further increased.

The stresses at the points P ₂ and P ₁ located on the left and right sides of the band-shaped gap position CC are shown in FIG.
P ₂ and P ₁ pulling a point stress (toward the outer arrow) and compressive stress (toward the center arrow) is located at the respective opposite polarity direction as shown in. Accordingly, as shown in FIG. 1 (C), the sensing element 7 disposed on the people P ₂ and P ₁ point each other across the bracket 2 end faces, the two differences (ρ ₁ -ρ output signal of the sensing device 7 By taking ₂ ), it is possible to obtain a gain twice as large as when gain is obtained from one element, and it is possible to detect signals with higher sensitivity and accuracy.

The load received by the trunnion shaft 3 is received on a pin Χ-Y axis plane (a vertical cross section of the trunnion shaft 3 passing through the center axis of the pin). Therefore, as shown in the reference photograph (color copy),
Maximum stress generation area in the Y-axis plane is not in the central axis, in P _3, P ₄ points displaced downward (fulcrum C _P side of the bracket end surface) of the center line.

Therefore, the sensitivity can be further improved by disposing the sensing element 7 at a position radially away from the center axis of the trunnion shaft 3 toward the maximum stress generation area. However, since the hole 6 for fitting the sensing element 7 needs to be formed in the trunnion shaft 3, the trunnion shaft 3 cannot be located much closer to the outer periphery of the pin than the strength surface of the trunnion shaft 3. The amount is set to 以下 or less of the axial radius of the trunnion shaft 3.

Next, a change in the load / gain depending on the fitting state of the sensor body 70 (see FIG. 13) including the sensing element 7 and the trunnion shaft 3 will be examined. As shown in FIG. Is +0.025 mm (tight) and the interference is -0.025 mm (loose), the former is more than twice as sensitive and the output sensitivity is further improved by the interference fit I was able to confirm.

[0027]

Embodiments of the present invention will be described below with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention unless otherwise specified, and are merely illustrative examples. It's just FIG. 5 shows a schematic configuration of a suspension portion of a heavy-duty truck to which the present invention is applied.
Tandem axle configuration, and each uses a leaf spring 11 as a suspension.

The leaf spring 11 on the front shaft 10 side
In the center of the, along with a shock absorber (not shown)
An axle 12 (axle case) is mounted. The rear end 11B of the leaf spring 11 is supported by a bracket 32 fixed to the carrier frame 1 via a shackle link 14 having a substantially inverted Y-shape. Since such a configuration is publicly known, detailed description will be omitted.

An eye portion 11A on the front end side of the leaf spring 11 is supported by a bracket 32 fixed to the carrier frame 1 via a shackle pin 30.

As shown in FIG. 6, the eye portion 11A of the leaf spring 11 is fitted with the shackle pin 30 via the bush 13, and
A groove 30a is provided on the peripheral surface of the bracket fitting portion of the shackle pin 30 on the side fitted with the bracket 2, and the bracket 3
When fitting 2, the pin fixing bolt 35 is inserted into the groove 30 a from the hole on the side surface of the bracket 32 and tightened, so that the shackle pin 30 does not rotate with respect to the bracket 32 and does not move in the axial direction. It is fixed to. A hollow narrow hole 6 is formed along the center axis direction from the end face of the shackle pin 3, and a sensor body including a magnetostrictive sensing element 7 is fitted and mounted inside the hole 6.

FIG. 13 shows the structure of the magnetostrictive sensor 70. As shown in FIG. 13 (A), the center of a rectangular thin plate 10 made of a ferromagnetic material such as permalloy,
And the four small holes 79
Two imaginary lines M in a direction deviated left and right by 45 ° with respect to the winding direction of the exciting coil 71 from the intersection connecting the centers in a cross shape
The upper and lower edges of the thin plate 80 sandwiched between the two imaginary lines M are notched symmetrically in a flat U-shape to provide a pair of notches 75. When the length of the edge of the thin plate 80 sandwiched between two imaginary lines M of 45 ° passing through the intersection is L, the width L ₀ of the notch 75 is expressed by the following formula 1). And the notch 75
A parallel tangent to the imaginary line M passing through the bottom corner and the imaginary line M
Notch 75 so that the distance m with respect to the following expression 2) is satisfied.
And the shape is not particularly limited. L ₀ ≦ L (1) m> 0, preferably M ≧ 1 mm (2) Then, coil wires are inserted through the four holes 79 in a crosswise manner in a vertical direction and a horizontal direction so as to be orthogonal to each other, and the exciting coil 71 is formed.
And the output coil 72 are arranged in the direction of 45 ° with respect to the direction of the force. Then, as shown in FIG. 13B, the sensing element 7 configured as described above is housed in the sensor holding space 76 in the tubular holder 77, and the tubular holder 77 and the thin plate 80 are spot-welded. The fixed position p is set at the intersection of the two virtual lines M and the edge line of the thin plate 10 or in the vicinity thereof.

In the fitting position of the sensor body 70, it is arranged at the position shown in FIG. That is, FIG. 9 is a schematic view showing a state in which the bracket 32 and the leaf spring 11 are connected via the shackle pin 30, and FIG.
(A) is the P ₂ points shifted toward the center from the bracket 32 end surface corresponding to the maximum stress zone of shear stress diagram of the center axis of the shackle pin 30 shown in FIG. 9, respectively one by one arranged to I have. FIG. 8 (B) is a graph showing the P shifted from the end face of the bracket 2 corresponding to the maximum stress area in the shear stress diagram shown in FIG.
_One at a time, one for each. FIG. 8 (C)
The P ₂ and P ₁ point displaced on both sides from the bracket 2 end surfaces corresponding to the maximum stress zone of shear stress diagram shown in Figure 9, are respectively one by one arranged.

Next, the arrangement position of the sensor body 70 on the rear wheel side 20 of the vehicle will be described. Since the rear wheel of this embodiment is a two-wheel vehicle having a tandem axle structure, as shown in FIG. 5, the axle cases 21A and 21B are arranged in two front and rear rows.
For this reason, the leaf spring 11 has an annular spring seat 4 and a U-shaped fixing jig 15 on the upper end side of the trunnion shaft 30 that is fitted and supported on the trunnion bracket 32 whose center is fixed to the carrier frame 1. The leaf spring 11 is attached through the intermediary of the leaf spring 11. That is, the trunnion shaft 3 has a central portion curved upward in a U-shape, and both sides of the trunnion shaft 3 extend horizontally to form a mounting portion for the trunnion bracket 32 and the leaf spring 11.

As shown in FIG. 7, the trunnion bracket 2 is formed so as to expand from the lower surface side of the carrier frame 1 in an eight-shape, and the horizontal shaft portion of the trunnion shaft 3 is fitted to the lower portion of the bracket 2. On the end side of the horizontal shaft portion 3a of the trunnion shaft 3 protruding from the bracket 2, the center portion of the leaf spring 11 is mounted via the spring seat 4 and the fixing jig 15 as described above. As described above, the fitting between the bracket 2 and the trunnion shaft 3 is preferably performed by interference fit.

In the trunnion shaft 3, a hollow hole 6 is formed along the center axis direction from the end face of the trunnion shaft 3, and a magnetostrictive sensor body 70 is fitted and mounted inside the hole 6. Have been. The sensor 70 is disposed at the position shown in FIG.

That is, FIG. 1 is a schematic diagram showing a state in which the trunnion shuff 3 is connected to the trunnion bracket 2 and the leaf spring 11, and FIG. 1A shows a shear stress on the central axis of the trunnion shaft shown in FIG. P ₂ points shifted toward the center from the bracket 2 end surfaces corresponding to the maximum stress zone of the diagram,
More specifically fulcrum C _P located on the intersection of the shaft axis 3a periphery, intersecting with the virtual line K and the shaft center line and the angle deflection of 45 ° substantially toward the center side with respect to the shaft axis 3a perpendicular surface It is preferable to dispose the detection center of the sensing element 7 at a position where the detection is performed.

[0037] Matazu. 1 (B), P ₁ point displaced outwardly from the bracket 2 end surfaces corresponding to the maximum stress zone of shear stress diagram shown in Figure 2, specifically the intersection of the shaft axis 3a periphery from fulcrum C _P is close to the detection center position of the sensing element 7 in crossover positions of the angle deflection virtual line K and the shaft center line of the 45 ° shown toward the end side with respect to the shaft axis 3a perpendicular surface The sensor bodies 70 are provided one by one so as to perform the operations. FIG. 1C shows that the detection center of the sensing element 7 is located at points P ₂ and P ₁ which are shifted to both sides from the end face of the bracket 2 corresponding to the maximum stress area of the shear stress diagram shown in FIG. The sensor bodies 70 are disposed one by one. Note that the fitting between the sensor body 70 and the trunnion shaft 3 is performed by an interference fit having an interference of +0.025 mm (tight).

Next, the sensing element arranged as described above
Figure 7 shows the measurement process of the load using the output signal of 7.
10 will be described. In this embodiment, the gain is low.
In order to ensure qualitativeness and accuracy, FIG. 1 (C) and FIG.
A measuring device based on the configuration (C) will be described. First
On the front wheel side, a sensor body 70 is provided for each of the right wheel and the left wheel.
2 × provided on both ends of the shackle pin 30
｛2 × (P_Two, P₁) About a total of eight sensor bodies 70
Measure both left and right wheel sides and calculate each sensing position in the calculator 41.
And a pair (P 2, P₁) Output signal difference (ρ₁−ρ_TwoTake
And the gain value ρ at each sensing position_RR, Ρ_RL, Ρ
_LL, Ρ_LRAnd the gain output F corresponding to the front shaft load
Get ρ.

Next, on the rear wheel side, four (2 × (P ₂ , P ₁ )) in total are disposed at both ends of the trunnion shaft 3 in which the sensor bodies 70 are disposed on the right wheel and the left wheel, respectively. The left and right sides of the sensor body 70 are measured, and the difference (ρ ₁ −ρ ₂ ) between the output signals of each pair (P ₂ , P ₁ ) at each sensing position is calculated in the arithmetic unit 43, and the gain value at each sensing position is obtained. By taking the sum of ρ _R and ρ _L , a gain output Bρ corresponding to the rear axle load is obtained.

After the gain outputs Fρ and Bρ are summed by the computing unit 44, a value obtained by converting (Fρ + Bρ) according to the load is obtained as a sprung load of the vehicle. A pre-measured unsprung load is added to this, and the display 45 displays the vehicle weight. When the load is measured, the display on the display 45 may be set to "0" while the loading platform is empty, and then the change in the display after the load is loaded may be read.

[0041]

As described above, according to the present invention, the shear strain (stress) distribution when the load is applied to the trunnion shaft 3 is determined by the finite element method analysis CAE, and the shear strain is determined based on the cut distribution. Since the sensing element 7 for efficiently measuring (stress) is arranged at the most appropriate position, a gain value sufficient for shear strain (stress) measurement can be obtained in all of sensitivity, accuracy, and stability. Moreover, in the present invention, the arrangement position of the sensing element 7 is changed to the band gap position CC.
It is only necessary to displace a predetermined distance further in the axial direction and dispose it at a position substantially corresponding to the maximum stress area of the shear stress diagram on the axis, so that the gain can be easily increased without changing existing parts and the like. It is possible. Further, the position of the sensing element 7 is shifted in the radial direction toward the load fulcrum CP along the imaginary line K of about 45 ° with respect to the center axis of the trunnion shaft 3, thereby further increasing the gain. Can be increased. Also, since all of the sensing elements are arranged in the maximum stress area on the axis of the fitting hole,
Even if the mounting position of the element 7 is slightly deviated, the gain does not change sensitively and there is stability.

[Brief description of the drawings]

FIGS. 1A, 1B, and 1C are schematic views showing the arrangement position of a sensing element according to an embodiment of the present invention.

FIG. 2 shows a shear stress diagram on the central axis of the trunnion shaft.

FIG. 3 shows a Χ-Y in which the trunnion shaft receives a load.
It is a stress distribution diagram which shows the compressive stress and the tensile stress in an axial surface with an arrow.

FIG. 4 is a graph showing a change in load / gain depending on a fitting state of the bracket and the trunnion shaft;
(A) When the interference is +0.025 mm (tight),
(B) shows the case where the interference is -0.025 mm (loose).

FIG. 5 shows a schematic configuration of a suspension section of a large truck to which the present invention is applied.

FIG. 6 is an enlarged sectional view of a sensing element mounting portion of a leaf spring on the front wheel side.

FIG. 7 shows a fitting state of a trunnion shaft and a trunnion bracket that supports a leaf spring on the rear wheel side.

FIGS. 8A, 8B, and 8C are schematic diagrams showing the arrangement positions of sensing elements fitted and mounted in shackle pins on the front wheel side.

FIG. 9 is a shear stress diagram on the central axis of the shackle pin.

FIG. 10 is a diagram illustrating a process of measuring a load using an output signal of a sensing element arranged as shown in FIGS. 1 (C) and 8 (C).

FIG. 11 is a schematic diagram showing an arrangement position of a sensing element according to the related art.

[Figure 12] and a sensing element disposed on P ₂ points of the present invention, is a graph showing the relationship between load / gain output of the sensing device which is disposed in P ₀ point of the prior art.

13A and 13B show a structure of a magnetostrictive sensor according to an embodiment of the present invention, wherein FIG. 13A shows a shape of a thin plate constituting a sensing element, and FIG. 13B shows a sectional view of a sensor body inserted into a tubular holder.

[Explanation of symbols]

1 a vehicle body (loading platform) Frame 2 bracket 3 trunnion shaft 6 holes 7 sensing element 11 leaf suspension C-C bracket end face the shaft axis orthogonal plane P ₂ passing _{through, P 1, P 3, P} 4 shear stress diagram

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int. Cl. ⁷ , DB name) G01G 19/12 B60G 17/00 B60P 5/00

Claims (4)

(57) [Claims] 1. An end fitted to a bracket attached to a vehicle body frame and protruding from the bracket,
In a vehicle or / and a loaded weight measuring apparatus, a hole is formed in a trunnion shaft that supports a leaf spring via a spring seat along an axial direction, and a sensing element for detecting distortion is fitted and arranged in the hole. The detection center of the sensing element is displaced by a predetermined distance in the axial direction from a band-shaped gap position (hereinafter referred to as a band-shaped gap position) between a bracket end surface and a spring seat, and the trunnion shaft is positioned on the axis of the drilled hole. A vehicle or / and a loaded weight measuring apparatus, wherein the sensing element is disposed at a position substantially corresponding to a maximum stress area in a shear stress diagram. 2. An arrangement position of the sensing element is set to be 30 to 60 in an axial direction with respect to a plane orthogonal to the shaft axis from a load fulcrum located on an intersection between an end face of the bracket and an outer periphery of the shaft.
°, preferably 40 ° to 50 °, more preferably 45 °
2. The device according to claim 1, wherein the first member is disposed so as to be deflected in the angle direction.
Vehicle or / and payload measurement device as described 3. The vehicle according to claim 1, wherein an arrangement position of the sensing element is shifted from a center axis of the trunnion shaft toward a maximum stress generation area in a radial direction. And loading weight measuring device 4. The vehicle and / or loaded weight measuring apparatus according to claim 3, wherein the amount of displacement in the radial direction is equal to or less than １ ／ of the axial radius of the trunnion shaft.