JP2000338002A - Rotation variation tester - Google Patents

Abstract

PROBLEM TO BE SOLVED: To test the performance of various transmitting elements with a crank shaft as a prime mover by providing a rotation variation tester to freely set a rotation variation period and a rotation regulation in the simulation of an output shaft in which a rotation variation component is superposed on a crank shaft of an internal combustion engine for a motor vehicle or the like. SOLUTION: In this method, a planetary gear swinging mechanism 2 is brought into reciprocating swinging motions at any angular velocity (ωM by reciprocating a piston (bearing 102) provided at one end of an arm 30. By superposing an angular velocity variation component at the time on the angular velocity ωA of an input shaft 10, it is possible to extract the output of an angular velocity ωA' with any rotation variation component from an output shaft 20.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a simulation device for a power transmission mechanism using an internal combustion engine as its prime mover,
Particularly, it is a simulation test machine for a power transmission mechanism associated with an automobile engine whose output shaft angular speed fluctuates greatly periodically. To be more specific, the output shaft is used as a drive unit and a toothed belt, a V-ribbed belt, a chain, or a gear is used. The present invention relates to a simulated testing machine of a power transmission mechanism for driving a driven shaft, that is, an engine camshaft, or an engine accessory through the power.

[0002]

2. Description of the Related Art Toothed belts, chains, V-belts, gears driven by the crankshaft of a reciprocating engine such as an internal combustion engine, or toothed pulleys, chain sprockets, V-pulleys, and couplings associated therewith. In performance tests of power transmission mechanisms such as bearings, dampers, etc., a substitute prime mover excellent in controllability of an electric motor or the like is generally used without using an actual engine in terms of stability or safety of the evaluation method. . However, general-purpose electric motors perform smooth rotation, that is, constant angular speed operation, and are not suitable for directly simulating operation in which a rotational fluctuation component such as engine output is superimposed.

[0003] For this reason, the present applicant has disclosed in Japanese Patent Application Laid-open No. Hei 3-927.
Japanese Patent Publication No. 43 discloses a rotation fluctuation tester applying a cardan error of a universal joint. This method is a method in which a universal joint is arranged at a predetermined bending angle, and an angular velocity fluctuation component is superimposed twice on the output side per one rotation of the shaft.

However, in this method, the magnitude of the fluctuation component can be adjusted by the bending angle, but the rotation fluctuation cycle per one rotation of the shaft cannot be changed. Therefore, this rotation fluctuation output can simulate the crankshaft output of a four-cycle four-cylinder engine, but cannot simulate a four-cycle three-cylinder engine or a four-cycle six-cylinder engine.

Accordingly, the present applicant has disclosed in Japanese Patent Application Laid-Open No. 8-43256.
In this publication, a mechanical power transmission mechanism is provided between the universal output shaft and the input shaft of the device under test, and the speed change ratio is converted into an integer ratio to obtain a rotation fluctuation period per one rotation of the input shaft of the device under test. Proposed a testing machine that can be changed.

[0006]

However, in the above-described test machine, the change of the gear ratio is performed by mechanical means, and the change of the setting cannot be said to be easy. Further, for the same reason, it has never been easy to make this speed ratio an arbitrary integer ratio. Therefore, the present inventor has invented a rotation fluctuation tester that can easily change the rotation fluctuation period per one rotation of the input shaft generated on the output shaft of the rotation fluctuation tester, that is, the input shaft of the device under test.

[0007]

That is, according to the first aspect of the present invention, a sun gear and a planetary gear are provided on the input side and the output side in a meshing state, and the opposing planetary gears are integrally rotated. An input side gear train and an output side gear train, an arm that enables the input side and the output side planetary gears to move around the sun gear while simultaneously meshing with the sun gear, and a piston rod connected to one end of the arm. A planetary gear turning mechanism provided with a crank mechanism for reciprocating motion, and among the pair of sun gears, an axis directly connected to one sun gear is used as an input shaft, and an axis directly connected to the other sun gear is used as an input shaft. Output shaft,
This is a rotation fluctuation tester that superimposes an arbitrary rotation fluctuation component on the output shaft.

According to a second aspect of the present invention, there is provided the rotation fluctuation testing machine according to the first aspect, wherein the crank pulley of the crank mechanism is driven by one of the sun gears.

[0009]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment according to the present invention will be described below with reference to FIGS. FIG. 1 is a front view of a rotation fluctuation tester according to the present invention, and FIG. 2 is a side view of FIG. In FIG. 1, a rotation fluctuation tester 1 includes a sun gear A
And an input side gear train 1a including a planetary gear B, and an output side gear train 1 including a planetary gear train B ′ and a sun gear A ′.
b, an arm 30 for rotating a planetary gear shaft 40 that integrally connects the opposed planetary gears B and B ′ around the sun gears A and A ′ while meshing therewith, and a bearing provided at one end of the arm 30 It comprises a planetary gear turning mechanism 2 for turning the arm 30 around 101 as a center of rotation.

The planetary gear turning mechanism 2 reciprocates around the output shaft 20 around the bearing 101 by the reciprocating movement of the piston rod 61 connected to the other end of the arm 30.

In FIG. 2, the crank mechanism for reciprocating the arm 30 includes a piston rod 61 connected to a bearing 102, a crank pin 62 connecting the piston rod 61, and a crank pulley 60 for eccentrically rotating the crank pin 62. You. A toothed pulley 53 that rotates integrally with the crank pulley 60 is directly connected to the crank pulley 60, and the toothed pulley 53 is driven by a toothed pulley 51 directly connected to the output shaft 20 via a toothed belt 52. .

Next, the power transmission path of the rotation fluctuation tester 1 will be described with reference to FIG. In FIG. 1, an input ωA for base rotation is applied to one end of an input shaft 10 supported by a bearing 100 on the input side gear train 1a side. This input ωA
Rotates the sun gear A in the directly connected state.

Further, the sun gear A rotates the planetary gear B in a meshing state, and at the same time, rotates the planetary gear B 'of the output side gear train 1b directly connected to the planetary gear B. Subsequently, the planetary gear B 'rotates the sun gear A', which is also in the meshing state, and finally transmits the output ωA 'to one end of the output shaft 20 directly connected to the sun gear A'.

Using the output ωA ′, various transmission elements connected to the output shaft 20 can be tested. The above is the overall configuration of the rotation fluctuation testing machine 1 according to the present invention and the power transmission path.

Next, the principle of superimposing the rotational fluctuation component on the input ωA and extracting the output on which the target rotational fluctuation component is superimposed from the output ωA ′ will be described. A differential gear train is a gear train in which one gear revolves with respect to the other gear among a pair of gears in a meshing state.The revolving gear is called a planetary gear, and the fixed gear is called a sun gear. Is defined as a planetary gear train in which the rotation of the gear and the revolution of the planetary gear are independent. That is, by independently controlling the rotation of the gear and the arm, a differential motion different from the motion of the fixed gear train can be realized. The planetary gear train in such a usage form is defined as a differential gear train.

Specifically, in order to support a pair of gears in a rotatable meshing state, the shafts are connected and fixed by an arm,
A differential gear train is formed by regulating the distance between the shafts. Hereinafter, a detailed description will be given with reference to FIGS. 3, a planetary gear train composed of gears A and B is referred to as an input-side planetary gear train 1a, and a rotation shaft of the gear A is referred to as an input shaft 10. Similarly, a planetary gear train composed of gears A 'and B' is referred to as an output-side planetary gear train 1b, and a rotating shaft of the gear A 'is defined as an output shaft 2
Set to 0.

Each of the gears is a gear A (the number of teeth Z).
A, pitch circle radius rA), gear B (number of teeth ZB, pitch circle radius rB), gear A '(number of teeth ZA', pitch circle radius r)
A '), gear B' (number of teeth ZB ', pitch circle radius rB')
Is defined by Here, the input-side planetary gear train 1a and the output-side planetary gear train 1b have the gear A and the gear A ′ as sun gears, and the gear B and the gear B ′ as planet gears, respectively. The planetary gears B 'are connected to one shaft 4
The arm 40 is rotatably supported by a bearing 102 provided at one end of the arm 30. On the other hand, the sun gear A and the sun gear A ′ are respectively connected to the input shaft 1
0, fixed to the output shaft 20.

In FIG. 3, the output shaft 20 is used as the rotating shaft of the bearing 101 for turning the arm 30. However, the rotating shaft is not limited to the output shaft 20, and it is not possible to provide the input shaft 10 or a separate intermediate shaft. It can be done arbitrarily.

Although not shown in FIGS. 3 and 4,
A piston 102 of a reciprocating crank mechanism is connected to a bearing 102 provided at one end of the arm 30. The reciprocating crank mechanism is driven from the output shaft 20 via a toothed belt transmission mechanism (not shown).

The arm 30 has an angular velocity ω around the output shaft 20 via a toothed belt transmission mechanism and a reciprocating crank mechanism.
Perform M acceleration / deceleration turning motion. In the input side planetary gear train 1a shown in FIGS. 3 and 4, the angular velocity of the sun gear A is ωA,
Assuming that the angular velocity of the planetary gear B is ωB and the angular velocity of the arm 30 for rotating the planetary gear B around the sun gear A is ωM,
The relationship between the angular velocities can be expressed by equation (1). Equation (1) ωB = (1 + rA / rB) × ωM− (rA / r
B) × ωA Similarly, in the output-side planetary gear train 1b, the arm 30 for turning the angular speed of the sun gear A ′ to ωA ′, the angular speed of the planetary gear B ′ to ωB ′, and turning the planetary gear B ′ around the sun gear A ′.
Is the angular velocity of ωM, the relationship between the angular velocities can be expressed by equation (2). Equation (2) ωB ′ = (1 + rA ′ / rB ′) × ωM− (r
A '/ rB') × ωA '

Incidentally, since the planetary gear B and the planetary gear B 'are integrally fixed to the common shaft 40, the equation (3) is established. Equation (3) ωB = ωB ′ Using the above equations (1), (2), and (3), the angular velocity ωA ′ of the output shaft 20 is calculated by the angular velocity ωA of the input shaft and the angular velocity ωM of the arm 30. Equation (4) is obtained by expressing. Equation (4) ωA ′ = {1− (rA × rB ′) / (rA ′ ×
rB)｝ × ωM + (rA × rB ′) / (rA ′ × rB)
× ω In equation (4), rA, rA ′, rB, and rB ′ indicate the pitch circle radii of the respective gears and become constants after the gear specifications are determined. 4)
Equation (5) is simplified. Equation (5) ωA ′ = C1 × ωM + C2 × ωA, where C
1 and C2 are constants. As can be seen from the above equation (5), since the angular velocity ωA ′ of the output shaft 10 can be represented by a linear combination of the angular velocity ωM of the arm 30 and the angular velocity ωA of the input shaft 10, controlling the angular velocity ωM Thus, a rotation fluctuation output on which an arbitrary rotation fluctuation component is superimposed can be obtained.

FIG. 5 shows a crank mechanism which reciprocates the planetary gear B 'in an arc of radius R around the rotation center K2 of the sun gear A'. The planetary gear B ′ corresponds to a piston of a crank mechanism, and the bearing 102 at one end of the arm 30 that rotatably supports the planetary gear B ′ corresponds to a piston pin. A piston rod 61 having a length L is connected to the piston pin, and a crank pulley 60 on the opposite side is connected.
Is connected to the crank pin 62 of The crank pin 62 rotates at a position of a radius r from the rotation center K1.

Therefore, the positional relationship between the position of the crank pin 62 and the position of the piston pin (bearing 102)
When the position of P1 is P1, the position of the piston pin (bearing 102) is P1 '.
In the case of 2 'and P3, it becomes P4' in the case of P3 'and P4.

If a circular arc having a radius R that regulates the positions P1 ', P2', P3 ', and P4 of the piston pin (bearing 102) is approximated by a straight line, the positional relationship between the crank pin 62 and the piston pin (bearing 102) is as follows. , Piston pin (bearing 10
If the position of 2) is XP, it is given by equation (6). Expression (6) XP = r × ｛COS θ + L / r × ｛1- (r /
^{L) 2 × SIN 2 θ}} 1/2} Here, if the r / L and 1 / 3-1 / 4, approximately formula (7) is obtained. Expression (7) XP = L × {1-1 / 4 × (r / L) ² } +
r × COS θ + ／ × (r / L) × r × COS 2θ When the equation (7) is differentiated with respect to the time axis t, the speed of the piston pin (bearing 102), that is, the turning speed of the arm 30 is given by the equation (8). . Expression (8) dXP / dt = −rω × ｛SINωt + ／
× (r / L) SIN2ωt｝, where ω = 2πN / 6
0, N (rpm). As described above, the turning speed dXP / dt and the turning angular speed ωM of the arm 30 can be expressed by Expression (8). In addition, focusing on the sine wave SINωt, which is the fundamental wave of Expression (8), the turning angular velocity ωM includes one rotation fluctuation component per one rotation of the crankshaft.

By driving the crank pulley 60 from the sun gear A 'or the input shaft 10 or the output shaft 20 directly connected to the sun gear A via a toothed belt transmission or the like, the output rotation ωA' and the rotation are output. It becomes possible to synchronize the fluctuation component ωM. The period of the rotation fluctuation component can be arbitrarily changed by changing the gear ratio of the toothed belt transmission or the like, and the magnitude of the rotation fluctuation component can be arbitrarily changed by changing the eccentric amount of the crank pin 62.

[0026]

An embodiment will be described below with reference to Tables 1 and 2 and FIGS. 6 and 7.

[0027]

[Table 1]

In the embodiment No. 1 shown in Table 1 above. 1 to N
O. Numeral 5 indicates that the final gear ratio of the differential gear train, which is a component of the present invention, is 1/4, 0.64, 1, 1.56, and 4.0. 1000 rp
m (angular velocity: ωA = 2 × π × N / 60 = 2 × π × 100
0/60) and the rotation speed of the arm is ± 100 rpm.
Table 2 shows the rotational speed (angular speed: ωA ′) of the output shaft when the setting is made by (angular speed: ωM).

[0029]

[Table 2]

In Example No. 1 shown in Table 2, As can be seen from FIG. 1, for a constant speed rotation input ωA = 1000 rpm,
It can be seen that by controlling the turning speed of the arm to ± 100 rpm, the rotation output ωA ′ = 250 ± 75 rpm is finally obtained.

That is, in the rotation fluctuation tester using the conventional universal joint, as shown in FIG. 6, only two rotation fluctuation components can be superimposed per rotation of the shaft. However, in the rotation fluctuation test machine 1 according to the present invention, the rotation fluctuation output in which an arbitrary rotation fluctuation component is superimposed can be taken out by periodically accelerating and decelerating the arm 30.

That is, as shown in FIG.
If the acceleration / deceleration cycle is set to a predetermined cycle, the rotation fluctuation component is superimposed on the output rotation on the output shaft 20 as it is. In the embodiment of the present invention, the crank pulley 6 of the reciprocating crank mechanism is used.
Since the number of rotations of 0 can be set arbitrarily and the amount of eccentricity of the crankpin 62 can be set arbitrarily, a rotation output ωA ′ in which an arbitrary rotation fluctuation component is superimposed is obtained.

It is possible to freely change the rotation speed of the arm by controlling the crankshaft with a separately provided motor, but it is not possible to mechanically synchronize the rotation cycle and the fluctuation cycle of the output shaft. .

[0034]

According to the first aspect of the present invention, by using a reciprocating crank mechanism for the planetary gear turning mechanism, a rotational output in which an arbitrary rotational fluctuation component is superimposed on the output shaft can be easily obtained. There is an excellent effect that it is possible to simulate the actual rotational output generated on the crankshaft.

According to the second aspect of the present invention, it is possible to mechanically synchronize the rotation cycle of the output shaft with the cycle of the rotation fluctuation component. Therefore, it is possible to more accurately simulate the rotation output of the crankshaft. it can.

[Brief description of the drawings]

FIG. 1 is a front view showing a rotation fluctuation testing machine according to the present invention.

FIG. 2 is a side view of FIG.

FIG. 3 is a front view showing a gear train according to the present invention.

FIG. 4 is a side view of FIG. 3;

FIG. 5 is a schematic view showing a reciprocating crank mechanism according to the present invention.

FIG. 6 is a graph showing an input / output shaft angular velocity according to a conventional example.

FIG. 7 is a graph showing an input / output shaft angular velocity according to the present invention.

[Explanation of symbols]

 Reference Signs List 1 rotation fluctuation testing machine 1a input side gear train 1b output side gear train 10 input shaft 20 output shaft 30 arm 40 planetary gear shaft 100 bearing 101 arm rotation bearing 102 planetary gear bearing A, A 'sun gear B, B' planetary gear ωA , ΩA 'angular velocity ωB, ωB' angular velocity ωM angular velocity

Claims (2)

[Claims] 1. A rotation fluctuation tester for superimposing an arbitrary rotation fluctuation component on an angular velocity of an output shaft, wherein a sun gear and a planetary gear are meshed on an input side and an output side, and opposing planetary gears are connected. An input-side gear train and an output-side gear train that are arranged to rotate integrally with each other; an arm that enables the input-side and output-side planetary gears to move around the sun gear while simultaneously meshing with the sun gear; A planetary gear turning mechanism provided with a crank mechanism for reciprocating a piston rod connected to one end of the pair of sun gears. Of the pair of sun gears, an axis directly connected to one sun gear is used as an input shaft, and the other sun gear A rotation fluctuation tester characterized in that a shaft directly connected to a motor is used as an output shaft. 2. The rotation fluctuation testing machine according to claim 1, wherein the crank pulley of the crank mechanism is driven by one of the sun gears.