JPH02258465A - Rack construction for monorail carrying vehicle - Google Patents

Abstract

PURPOSE:To increase the anti-wear property of a rack and the rigidity of a monorail by firmly fixing a rack, provided with a specified pressure angle, a specified distance in module from pitch circle to addendum, and a specified distance in module from pitch circle to dedendum, on the side surface of a rail main body with rectangular cross-section. CONSTITUTION:A single-rail carrying vehicle used in orange park, etc. is so constructed that the motive power unit and the carriage of the vehicle can travel on a monorail by themselves. In this case, a rack 23 with a specified composition is stamped firmly on the side surface of a rail main body 20 with rectangular cross-section. Namely, the rack 23 is formed by cutting a steel material containing a carbon of 0.1 to 1.7% in gears, and the pressure angle, the distance from the pitch circle to the addendum, and the distance from the pitch circle to the dedendum are set at 25 deg., 0.7 to 0.9 module, 0.875 to 1.125 module, respectively. Thus, anti-wear property of the rack 23 can be increased, cutting time and cost can be reduced, and the rigidity of the rail main body 20 can be increased.

Description

[Detailed description of the invention] ■Technical field The present invention relates to a rack structure for a single-rail transport vehicle.

A single-rail transport vehicle is a transport vehicle in which a power vehicle and a bogie run on a single track (mole rail) using their own blades. - Vehicles are generally designed to run unmanned.

Rails are easy to lay, can pass through narrow spaces, and have the advantage of being resistant to steep slopes and curves.

For example, single-rail transport vehicles with a capacity of 200 kg are widely used in mandarin orange orchards.

For civil engineering, a stack of 1 is used.

The rail is a long member with a square cross section. A rack is welded to the side or bottom. Rails are laid by connecting a number of units, each about 3m to 6m in length.

The structure of a power vehicle consists of a driving mechanism, a power transmission mechanism, a drive pinion rotated by the drive mechanism, wheels for supporting the power vehicle on rails, and a frame that accommodates these members.

The drive binion of the motor vehicle meshes with the rack, and when the drive binion rotates, it pushes the rack, and the reaction force causes the motor vehicle to run.

It is a combination of a binion and a rack, so there is no slippage.
It can also climb high slopes.

(b) Conventional technology The applicant has been manufacturing single-rail transport vehicles for many years.

The rack was made of metal plate bent into a corrugated shape.

This was welded to the side of the square rail.

For example, Sho 53-15057 (S53.4.21), Tokko Sho 58-18241 (358,4,,1,2), Sho 63-40054 (S 63.10.20), Sho 58-23268 (S 58. 5.13) Tokuko Showa 5
8-47385 (S 58.10.21) Special public show 6
3-5309 (S63.2.3) Special public service 1986-41
34.1 (S 63.8.16) Special public service 1986-51
202 (S 63.10.12) Special public service 1986-65
541 (S 63. I2.1.6) etc.

The material of the rack is low carbon (less than 0.04%) steel strip. This is then pressed and bent into a wave shape.

This is a special soft steel material called rimmed steel. Materials with higher carbon content will break when pressed and can be made into racks.

The pressure angle is 30° and the rack has low teeth.
-15057). Because it is pressed and bent,
- Can be molded at once. Manufacturing is easy. The larger the pressure angle, the smaller the bending angle during pressing, so it is less difficult to press. Also, the teeth of the binion can be made strong, so I set it to 300.

Actually, a steel strip with a thickness of 6++tN and a width of 12 mm is bent into a corrugated shape. The pitch of the waves is 33 degrees. In this case, the module m is 105.

The drive pinion has 11 teeth and the pitch diameter is 11.
It's 5.5 friends.

(1) Problems to be Solved by the Invention Since the rack is made by bending soft steel strips, the following problems arise.

Since the material is soft, it will gradually wear out due to contact with the pinion teeth. Initially, it is 6mm thick, but as it gradually wears out, it becomes thinner and weaker.

However, even such a material can be used sufficiently for agricultural and civil engineering purposes.

In the case of agricultural use, it is light with a load of 200 to 240 kg. Also, the usage time is short. As a result, rack wear does not occur significantly.

In the case of civil engineering, the construction period is short, and construction at one site can be completed in about three to four months. When finished, the rail is removed. The rails are sent to other sites, but those with worn racks are often replaced with new rails.

As described above, racks made by bending steel strips have had problems with durability, but since they are rarely used continuously for many years, the problems with durability have not surfaced.

However, single-track transport vehicles are expanding their uses.

There is also the possibility that there will be many uses where it will be used continuously for many years.

Another problem is vibration and noise.

FIG. 6 shows a diagram of a corrugated rack.

A steel band 12mm wide and 6mm thick is bent so that the pressure angle is 300mm. The module is 1o, 5.

Since we are bending something thick, the bent part is curved bluntly. In the standard case, the outer diameter is 9mm (radius) and the inner diameter is 3mm.
It can be bent at the radius.

The height is about 21cm. The flat part that touches the teeth of the drive pinion is about 9 mm.

This is not even enough for one module (10.5 mm).

The teeth of the drive pinion only hit this narrow section.

Therefore, the engagement ratio becomes smaller than 1.

The meshing ratio here is a value that indicates how many gears are in contact with two mutually meshing gears at the same time.
This is the average value of the number of sheets in contact.

In the case of external gears, the meshing ratio is low, but in the case of a combination of external gears and internal gears, the meshing ratio is high.

In the case of a rack and a pinion, the engagement ratio takes an intermediate value between them.

Since it takes an intermediate value, the meshing ratio should be higher than that of external gears. But in reality this is not the case.

For external and internal gears, the distance from the pitch circle to the tooth tip is often 1 module, and the distance from the pitch circle to the tooth bottom is often 125 modules.

In other words, the length of the tooth contact area is 2 modules.

However, in the case of a rack made of corrugated steel strips, it is not possible to have such a long contact area.

In the above example, the length of the flat part (in the vertical direction) of the corrugated rack was 9 zm. Since the module is 105, this corresponds to 0.86 module. 0 above the pitch circle.
43, 0.43 modules are distributed below.

If the length of the racks that can be engaged is short as described above, the engagement ratio Q will be 1 or less.

This means that the mesh between the pinion and the rack is always in contact with only one tooth. If it is less than 1, there is a moment when the teeth completely separate during engagement from one tooth to the next. The next tooth hits the rack hard, creating a strong impact force. Therefore, in the case of corrugated racks, extremely large vibrations produced noise.

B) Structure In the present invention, a rack made of a square bar with gears is used. The material may be ordinary structural carbon steel. For example 5
45G: etc.

Compared to corrugated racks, the materials are more readily available and cheaper.

However, cutting gears takes more time and costs than bending steel strips.

Therefore, the overall cost is higher for the hob rack.

Therefore, it is important to reduce cutting costs.

A commercially available standard rack has a pressure angle of 1 module from the 200 pitch line to the tooth tip, and 1.25 modules from the pitch line to the tooth bottom. The module is 6.7.8.
9.1o, . . . are arbitrary.

Figure 2 shows the shape of a standard rack.

The inventor does not use standard racks. Because I don't think it's necessarily the best one.

The pressure angle is 25°. This is because the larger the pressure angle, the stronger the teeth. The drive pinion teeth have a more stubby shape. The root of the tooth is thicker and the tip is thinner.

In fact, the distance from the pitch line to the tooth tip is not one module.
087-09 module low teeth. The height from the pitch line to the tooth bottom is 0.875 to 1.125 modules. A rack used in the present invention is shown in FIG.

The length from the pitch line to the tooth tip is S, and the length from the pitch line to the tooth bottom is t. It is desirable to set t to 1.25 times S to provide a margin at the bottom of the tooth.

Next, the standard product and the rack of the present invention will be compared.

It is.

It is assumed that the i5[11) binion also corresponds to this rack. The pressure angle is 25°, S is 0.7 to 0.9 modules, and t is 0875 to 1.125 modules.

If the number of teeth is the same, the smaller the pressure angle α, the higher the meshing ratio. Naturally, the noise level is also low.

However, the strength of the pinion and rack teeth increases as the pressure angle α increases. Since the strength of the teeth is prioritized over vibration noise, the pressure angle is set to 25° in the present invention.

Furthermore, the reason why the teeth are made low is to reduce the amount of cutting when cutting steel to form the tooth surface. If the amount of cutting is small, there will be less wear and tear on the cutting tool and the time required for cutting will be shorter.

Regarding the material issue, the corrugated rack was close to pure iron containing less than 0.04% carbon.

The present invention instead uses structural steel containing 0.1% to 1.7% carbon. If it is less than 0.1%, it will be too soft and wear will become a problem. If it is 1.7% or more, it will be hard to cut and it will be difficult to cut the teeth.

Steel materials in this range are more readily available and cheaper than iron with a carbon content of 0.04% or less.

ke) production The cutting amount of the rack will be explained with reference to FIG.

The trapezoid of the cut section is represented by EFGH. The pitch line is MN. One pitch of teeth along the pitch line is πm, so
MN is half of that, πm/2.

Here m is a module.

The tips of the teeth are DE and HI.

The distance from the pitch line MN to the tooth bottom FG is mx.

Let the distance from MN to the tooth tip EH be my. For a standard rack, X = 1.25 and y = 1. This is used as a parameter here.

The cutting volume V is obtained by multiplying the cutting area S by the rack width d.

V = dS Since d is constant, consider the cutting area S. S is the area of trapezoid EFGH. When the pressure angle is α, the slope EF%GH forms an angle of (α+π/2) with the line segment FG.

FG = −m −2xmtanα (2)
EH=-" + 2 ym tanα (3) Since the height of the tooth is m(x+y) (4), the cutting area S is. If y-x<O, the larger α is the cutting area S will decrease.To prevent the tip of the opponent's tooth from hitting the base of the tooth,
The root of the tooth is usually gouged deeper than the tip.

Therefore, generally y−x<O. Therefore, the larger the pressure angle, the smaller the cutting amount.

The amount of cutting is smaller when α=25° in the present invention than when α=20° in the standard rack.

The lower tooth is (X (1, 25, y (1) standard tooth (x =
The amount of cutting is smaller than 1.25°y=1). This is natural.

An example will be shown assuming that module m is 7.

Standard tooth x=1.25 7=1 α=20 S
= 163.14mrA low tooth x=o, 98 ymo, 8
α= 20 S = 131.29m++! low teeth
X = 0.98)' = 0.8 α= 2
5 3 = 129.68 mA If the teeth are made low, the amount of cutting will be reduced, and cutting time and cost can be saved.

This is an advantage 0 However, when the teeth are made low, the meshing ratio becomes low.

A balance must be struck between reducing the engagement rate and reducing the amount of cutting.

FIG. 8 is a diagram for determining the engagement ratio of the rack and binion. Let the number of teeth of the binion be 2Z.

The center of the drive pinion is set to 0. The pitch circle is p1, the tip circle is q, and the root circle is r.

The pitch line of the rack is 11, the tooth bottom line is m, and the tooth tip line is n.

Let J, C, and K be the legs of the perpendicular lines drawn from the 0 point to the tooth root line m1, pitch line l, and tooth tip line n.

Draw a straight line that passes through point C and forms an angle α with l, and let Q be the point of intersection with the tip circle q, and let R be the point of intersection with the tip line n.

Line segments Q and R are the meshing action lines between the rack and the pinion. The tooth surface of the pinion hits the tooth surface of the rack only during the length QRQ. On the line of action, the distance between the two tooth surfaces is πm c
It is osα. This is also called normal pitch. The value obtained by dividing the line segment QR by the normal pitch indicates how many teeth are in mesh with each other. In other words, it is the meshing ratio U.

Therefore, the positions of the nine points must be determined.

Consider a coordinate system centered on point 0 and with OJ as the y-axis.

Assuming that the tip circle q is one module away from the pitch circle, the equation for q can be written as x"+y"=m2(Z+1)2(6). The straight line QC can be written as 7 = -(tanα)x-)-mZ. The 9 points are the intersections of these points, so solve them as simultaneous equations and get x == mZsin acosa -mcos
(X 4te'sin"d-〒-22chi11--choichi (8).The length QC is 1x multiplied by secα, so QC= m Z"sin"(lj -)- 22-)-
1-mZsinαCR=m-ααD. The engagement ratio U is πm cosα (12+). This is the formula for the standard case. In other words, when the distance from the pitch circle to the tip circle is 1 module, and from the pitch circle to the root circle is 1.25 modules. It is.

The meshing is done with one module on each side of the pitch circle.

When the pressure angle is 25°, the meshing ratio is as follows due to the number of teeth: 22.

2Z=22 U=1.5442Z=2
4 U = 1.5512Z = 80
U = 1.5682Z = 3.6
U = 1.5801 The greater the number of teeth in the binion, the higher the meshing ratio.

In the case of the low tooth shown in FIG. 7, formula 03 must be modified. The distance from the tooth tip to the pitch is ym, and the distance from the pitch to the tooth bottom is xm. If this is true not only for the rack but also for the pinion, the meshing portion is in the area x ym from the pitch, and the meshing ratio is obtained by multiplying (12) by y.

In the case of a corrugated rack as shown in FIG. 6, since ym is 0.43, the engagement ratio is about 0.7. This resulted in large vibration noise.

The higher the meshing ratio, the less vibration there will be, but if it is 1 or more, discontinuous meshing will be completely eliminated. In other words, U(y) must be 1 or more.

Then, from which example Z=11 to 18, y is 0.7
It turns out that it has to be more than that.

The cutting area S is a function of x and y. X can be any parameter, but since this is the amount by which the bottom of the tooth is hollowed out,
It can be estimated to be about 1.25 times y.

Suppose x = 1.257
side, 5(y) = -x 2;25y (π-0,5tanα
y)(+5).

5(y) should be smaller, but compared to ym1,
This is smaller when y<x. When 7 = 0.9, it is approximately 0.9 times as large as when ym1.

If the engagement ratio is 1 or more and the cutting amount is less than ym1, then y should be 0.7 to 0.9.

If we assume that X is 1.25 times y, then the range of X will be 0.875 to 1.125 modules correspondingly.

In this way, the range of ym0.7 to 0.9 module is selected from the viewpoint that the engagement ratio is 1 or more and the amount of cutting is small.

For example, if we say ymo, s, the meshing rate U
is (α=25°) Z = 11 U = 1.235Z = 1
2 U = 1. ．． 241Z= 15
U = 1.254Z = 18
0 = 1.264. The cutting area 5(y) is calculated from 05) under the assumption of αa, m = 7, α = 2
Assuming 5°, S (1) = 160 m ( S (0,9) = 14.5 mt?.

S (0,8) = 130 mfflS (07) = 1
It becomes 15m111. The reduction in meshing ratio cannot be confirmed unless the number of teeth 22 is determined. For example, if it is ym18, then U (],) = 1. with y as a parameter. ．． 580 U (0,9) = 1.422 1J (0,8) = 1.264 U (0,7) = 1.10 The meshing ratio is higher than the rack made of corrugated steel strips. It is taller and cuts less than a standard rack.

There is another effect. That is, the rigidity of the rail is increased by the rack.

Since the cut rack is welded to the side surface of the upper rail, the rack reinforces the rail against left and right bending.

(The material itself is soft and has a small Young's modulus when steel strips are bent into a corrugated shape.) The thickness of the rack is the same as that of the steel strips, so it is difficult to reinforce the rails.

However, in the case of the present invention, since the material is harder and thicker, the rail reinforcement effect is excellent and the rail is thicker.

Compare with (secondary moment of area) I. The wall thickness is d and aXa
The moment of inertia of the rail with a square cross section is IO - ±(a' - (a-2d)')
16). 2S to SO==a2(a-2d)2I: where the cross-sectional area is So.

It can be written as

For example, if a = 50 mm and d = 3 mm, IQ = 2. I x 105 4 SO = 564 mm2 and 2 = 370 mm2 (1,9).

A plate having a thickness D and a width W is welded to the side of this rail (as shown in FIG. 9), and the moment of inertia of the area is s,=wp. For example, let the width W be 22mm and the average thickness be 16mm.
If it is made of porcelain, it will be 2.3 x 10'mm' 0.1), and the moment of inertia of area will be about 10% larger.

In this way, it has the effect of reinforcing the rigidity of the rail.

Utility Model No. 63-54579 (S 63.4., 12)
uses racks, but these are attached to vertical angles and do not have the effect of reinforcing the rails.

(6) Embodiment An embodiment of a power vehicle of a single-rail transport vehicle having a rack structure of the present invention will be explained with reference to drawings.

FIG. 3 is a left side view of the power vehicle, FIG. 4 is a rear view, and FIG. 5 is a right side view.

The rack structure is as shown in FIG.

A power vehicle consists of a mechanism that generates power, a mechanism that transmits power, a wheel structure that holds itself against the rail, and a drive pinion that meshes with the rack and pushes the rack by receiving power transmission. .

The distribution of these mechanisms is arbitrary, and what is shown here is just one example.

The frame 1 of the single-rail transport vehicle is made of, for example, aluminum alloy or cast iron. A power transmission mechanism including a large number of gears, gear shafts, and bearings is provided inside the frame 1, and the frame 1 is divided into approximately one section by rails. The left side is sometimes called the transmission case and the right side is called the gear case. Here, they are collectively referred to as frames.

Outside the frame 1 are an engine 2, a fuel tank 3, a motor 4, an oil tank 5, a centrifugal clutch 6, and a belt 7.
, V pulley 8.8, mission switching lever 9, stop/start lever 10. A battery cover 11 and the like containing a battery (not shown) are provided.

The power of the engine is transmitted to the V-pulley via the centrifugal clutch 6, and then transmitted from the belt 7 to another V-pulley 8. The rotational force of this V-pulley is transmitted to the gear train inside the frame 1.

The mission switching lever 9 changes the meshing of the gears,
It is used to switch between forward, reverse, low speed, high speed, etc.

The stop/start lever 10 operates or releases the stop brake 29.

The flexible connection fitting 12 is a member for connecting a truck (not shown) to the rear.

The constant speed brake 13 is provided to prevent excessive speed when descending.

Four lower guide rollers 14 are rotatably attached to the lower end of the frame 1 in the left, right, front and rear directions.

The wheels of the power vehicle include, in addition to the lower guide roller 14, an upper wheel 15, an upper wheel 16, an upper guide roller 17, a drive pinion 18, and the like.

Let's talk about rails.

An upper rail 20 and a lower rail 21 having a square cross section are connected by a connecting fitting 22. In this example, the top and bottom rails are 5
It is a rail with a square cross section of 0+++m x 50mm.

A rack 23 is fixed downward to the lower half of one side (the right side in this example) of the upper rail.

The lower rail 21 is fixed onto the pillow vibrator 24 by a plate.

Sleepers 25 are installed on the ground. A jack base 26 with a male thread is provided on the sleeper 25 in the vertical direction by a coach screw 27.

The jack handle stopper 2 is attached to the jack base 26.
8 are screwed together. This supports the pillow vibrator 24.

Revealing the wheel structure again.

(a) Upper wheel 15 (b) Upper wheel 16 (C) Drive binion 18 (d) Left and right guide rollers 17 are in contact with the upper rail 20. The upper wheel 15 rolls in contact with the upper surface of the upper rail. The upper wheel contacts and rolls on the side of the lower surface of the upper rail. A part of the drive binion has the same flange as the upper wheel, and cooperates with the upper wheel to press down on the lower surface of the rail.

The left and right guide rollers 17 roll in contact with the upper half of the rail above the rack.

In addition to the same function as the upper wheel, the drive pinion 18 has the function of meshing with the rack 23 to obtain thrust.

For the lower rail 21 (e) Left and right guide rollers 14 is holding down the side of the bottom rail.

There are four upper and lower guide rollers 17 and 14 on the front, rear, left and right sides. There are three upper wheels, one of which is replaced by a drive pinion. There are two upper wheels, front and rear.

A rack 23 is secured to the rail 20, which is the rack shown in FIG. A side view of what is attached to the rail is shown in Figure 10.

FIG. 11 is a longitudinal sectional view. In this example, the module is 7 and the pressure angle is 25°. The pitch of the rack is 21.
It is 9912 mm. The width of the rack is 22 mm, the thickness from the tooth tip is 22 mm, and the thickness from the tooth bottom is 9.54 mm.
It is.

The height from the pitch line to the tooth tip is 0.8 module, 5
6 friends.

The height from the pitch line to the tooth bottom is 0.98 modules,
It has 6.86 rhymes.

This means that a low-tooth rack is cut from a 22 mm x 22 mm piece of steel.

For example, high carbon content (0.42% to 0.18%)
It is made from structural carbon steel like S45G.

The cutting speed was about 70 m/min. In other words, approximately 3 pitches can be cut in 1 minute. Of course, this will vary depending on the performance of the machine.

(g) Effects of the invention Conventionally, racks made of soft low-carbon steel bent into corrugated shapes have been used. This was because it could not be bent otherwise. However, since this corrugated rack is soft, it is susceptible to wear due to contact with the drive pinion. It wore out after about 5 years, so I had to replace it. Moreover, this steel material had a carbon content of 0.0.4% or less, was a special material, and was expensive.

In the present invention, a rack is made by cutting a steel material with a carbon content of 01 to 17%. Ordinary steel materials that are easily available can be used. Since it is made of ordinary steel, it is not easily worn out by contact with the drive pinion. It has a long lifespan.

In addition, the corrugated rack had a short straight section and a low engagement ratio. In the present invention, since racks with properly geared teeth are used, the meshing ratio can be increased.

This reduces noise and vibration.

Even if it is a geared rack, it is not a standard rack with a pressure angle of 200. The standard rack has 1 module from the pitch to the tooth tip and 1.25 modules from the pitch to the tooth bottom.

In the present invention, the pressure angle is 25° and the tooth tip to pitch distance is 0.7
~09 module, tooth root to pitch distance is 0.875 to 1
．． ．． There are 125 modules. Use low teeth like this.

The large pressure angle makes the teeth stronger. The safety of single-track transport vehicles depends largely on the rack.

If the rack is damaged, it will lead to an accident. It is important that the rack be robust.

In addition, since the teeth are made low, the cutting volume becomes small, cutting time and cost can be reduced.

Furthermore, since the rack is welded to the side of the rail, the rigidity of the rail can be increased.

This is a useful invention.

[Brief explanation of drawings]

FIG. 1 is a front view showing the rack structure of the present invention. FIG. 2 is a front view showing the standard rack structure. FIG. 3 is a right side view showing an example of a power vehicle of a single-rail transport vehicle used in the rail rack structure of the present invention. Figure 4 is a rear view of the same power vehicle. Figure 5 is a left side view of the same power vehicle. Figure 6 is a partial front view of a rack and rail made of conventional bent steel bands. FIG. 7 is an explanatory diagram for calculating the cutting volume of the rack. FIG. 8 is an explanatory diagram for calculating the engagement ratio between the rack and the pinion. FIG. 9 is a cross-sectional view of a rail with a square cross section, in which a square piece with a width W1 and a height D is fixed to the side. FIG. 10 is a front view of the rack/rail structure according to the embodiment of the present invention. FIG. 11 is a longitudinal sectional view of the same thing. 1... Frame 2... Engine 3... Fuel tank 4... Cell motor 5... Oil tank 6... Centrifugal Clutch 7... V-belt 8... V-pulley 9... Mission switching lever 10... Stop/start lever 11... Battery cover 12. ......Flexible fitting for connection 13...Constant speed brake 14...Lower guide roller 15...Upper wheel 16...Upper wheel 17... ...Upper guide roller 18...Drive binion 20...Upper rail 21...Lower rail 22...Connection fittings 23... Rack 24...Pillow vibrator 25...Pillow tree 26...Jack heath 27/River...Coach screw 28...Jack handle stopper 29...
... Stop brake inventor Hideo Chikusa

Claims (1)

[Claims] It is a gear rack made of steel containing 0.1% to 1.7% carbon, with a pressure angle of 25°, a distance of 0.7 to 0.9 modules from the pitch line to the tip of the tooth, and a width of 0.7 to 0.9 modules from the pitch line to the tooth tip. A rack structure for a single-rail transport vehicle, characterized in that a rack having 0.875 to 1.125 modules to the bottom is fixed to the side surface of a rail with a square cross section.