JP4734890B2 - Driving means evaluation apparatus and vibration damping method used for driving means evaluation apparatus - Google Patents

Description

  The present invention relates to a drive means evaluation apparatus and a vibration buffering method used for the drive means evaluation apparatus. More specifically, the present invention relates to an apparatus for evaluating the output characteristics of a drive means such as an engine and a vibration buffer for accurately evaluating the output characteristics. It is about the method.

2. Description of the Related Art Conventionally, devices using an elastic body such as a string-wound spring or rubber are known as devices for supporting vibration isolation of an engine. These are intended to suppress transmission of engine normal range vibration to the fixed portion of the elastic body, and reduce the spring constant of the elastic body.
In order to prevent the crankshaft displacement of the engine, there is also known one provided with a stopper together with an elastic body (see, for example, Patent Document 1).
Furthermore, an engine vibration isolator that suppresses engine displacement with a stopper and positively changes the spring constant by detecting the engine speed is also known.
Japanese Utility Model Publication No. 5-54041

However, when resin rubber is used as the elastic body, the purpose is to reduce vibrations in the engine normal range vibration, so vibrations that cannot provide sufficient vibration isolation at frequencies other than the normal range vibration. There is a zone. Further, when the spring constant is small, the displacement of the engine supported by the elastic body becomes large, which may affect the output shaft connected to the engine.
Further, when the vibration isolating rubber is used as the elastic body, it is difficult to lower the resonance point, and there is a high possibility that the vibration isolating rubber will become loose due to continuous use. In addition, characteristics change with temperature, and there are problems such as heat resistance and cold resistance.
In an elastic body support with a stopper for preventing the displacement of the output shaft, engine vibration is easily transmitted when the displacement is suppressed by the stopper. In addition, in the case of performing vibration isolation by actively changing the spring constant, the structure becomes complicated, high cost is required for introducing the apparatus, and much labor is required for maintenance.

In engine evaluation equipment directly connected to the engine and dynamometer and in the line tester of the engine factory, the displacement between the engine torque shaft supported by anti-vibration rubber and the power rotation shaft increases, and the shaft connecting the engine and dynamometer There are problems such as breakage and bending of the dynamometer rotation shaft.
Further, when the engine is supported by another conventional anti-vibration rubber with a stopper, the vibration of the support tool is transmitted to the fixing portion of the support tool while the rubber of the support tool is bent and hits the stopper. For this reason, there is a need for an engine support device that restrains the crank end face and has vibration isolation.
The present invention has been made in consideration of the above-described problems, and is a drive means evaluation apparatus that can reliably perform vibration isolation of a drive means such as an engine with a compact and easy configuration. The purpose is to provide.

In order to solve the above-mentioned problems, the present invention connects the drive means to a dynamometer placed on a fixed base via a shaft connected to the output shaft of the drive means as described in claim 1. The drive means evaluation apparatus for evaluating the output of the drive means with the dynamometer, comprising a fixing means for fixing the drive means on a fixed base via a wire rope vibration isolator, the fixing means being And located between the driving means and the dynamometer and connected to the shaft-side end surface of the driving means, the shaft being disposed inside the fixing means, and the fixing means and the shaft being separated from each other. The fixing means is located below the shaft and extends in a vertical direction from above the fixing base, and extends in a substantially horizontal direction from the restraining support apparatus. With a fixed arm And the restraint support device and the other end of the arm are connected via the wire rope vibration isolator, and a plurality of the wire rope vibration isolator are arranged on the circumference centering on the shaft. The driving means evaluation apparatus is configured.

The drive means evaluation in which one end of the arm is fixed to a housing for housing the drive means, and the arm and the drive means are fixed via the housing. Configure the device.

The driving means is connected to the dynamometer placed on the fixed base via a shaft connected to the output shaft of the driving means, and the output of the driving means is evaluated by the dynamometer. In the vibration buffering method used in the driving means evaluation apparatus, the driving means is fixed on a fixing base via a fixing means provided with a wire rope vibration isolator, and the vibration generated from the driving means is buffered, and the fixing means Is located between the driving means and the dynamometer and connected to the shaft side end surface of the driving means, the shaft is disposed inside the fixing means, and the fixing means and the shaft are separated from each other and is, the fixing means is located below the shaft, and restraining the support device extending in a vertical direction from the upper fixing base extending in a substantially horizontal direction from the restraint support apparatus, the said driving means An arm to which an end is fixed, the restraint support device and the other end of the arm are connected via the wire rope vibration isolator, and the wire rope vibration isolator is connected to the shaft. A plurality are arranged on the circumference of the center.

In the drive means evaluation apparatus according to claim 1, since the drive means is fixed on a fixed base via a wire rope vibration isolator, the drive means is compared with a case where vibration isolation rubber or the like is used. While being able to fix easily and reliably, the displacement of the engine which arises at the time of a vibration can be absorbed efficiently.
The fixing means is located below the shaft and extends in a vertical direction from above the fixing base, and an arm extending substantially horizontally from the restraining support apparatus and having one end fixed to the driving means. The restraint support device and the other end of the arm are connected via a wire rope vibration isolator, and a plurality of the wire rope vibration isolator are arranged on a circumference centered on the shaft. Since they are arranged individually, a large number of wire rope anti-vibration devices can be arranged in a limited space, and the number of wire rope anti-vibration devices can be arbitrarily selected. Therefore, the number of wire rope vibration isolator can be appropriately selected with respect to the natural frequency of the spring mass system using the engine as a mass.

Moreover, in the drive means evaluation apparatus of Claim 2 , since the end of the said arm is being fixed with respect to the housing for accommodating the said drive means, a wire rope vibration isolator is the circumferential direction with respect to a shaft. Even in the case of the arrangement, the engine can be supported while easily avoiding interferences such as a starter, an air cleaner, and an exhaust pipe catalyst arranged near the end face of the engine crank. Further, by using the clutch housing, the mechanical design of the arm can be simplified, and much time and cost required for supporting the vibration isolation of the engine can be reduced.

Further, in the vibration damping method according to claim 3 , a driving means is connected to a dynamometer placed on the fixed base via a shaft, and an output of the driving means is evaluated by the dynamometer. In the vibration damping method used in the evaluation apparatus, the driving means is fixed on a fixed base via a fixing member equipped with a wire rope vibration isolator, and the vibration generated from the driving means is buffered. It is possible to easily cope with the problem by adjusting the number of devices, and the drive means evaluation apparatus can be configured compactly.
Furthermore, a fixing device suitable for supporting a complex multi-vibration system of an engine or supporting a rotating machine can be configured to efficiently absorb vibration while keeping the engine displacement small. Thereby, the measurement precision of a drive means evaluation apparatus can be improved.
The fixing means is located below the shaft and extends in a vertical direction from above the fixing base, and an arm extending substantially horizontally from the restraining support apparatus and having one end fixed to the driving means. The restraint support device and the other end of the arm are connected via a wire rope vibration isolator, and a plurality of the wire rope vibration isolator are arranged on a circumference centered on the shaft. Since they are arranged individually, a large number of wire rope anti-vibration devices can be arranged in a limited space, and the number of wire rope anti-vibration devices can be arbitrarily selected. Therefore, the number of wire rope vibration isolator can be appropriately selected with respect to the natural frequency of the spring mass system using the engine as a mass.

  The drive means evaluation apparatus according to the present invention will be described with reference to FIGS. FIG. 1 is a plan view showing an engine evaluation apparatus for evaluating an engine as drive means, and FIG. 2 is a side view showing a side of the engine evaluation apparatus. FIG. 3 is a side view showing a support structure in the front part of the engine, and FIG. 4 is a side view showing a support structure in the rear part of the engine.

On the fixed base 7, an engine 1 as a driving means and a dynamometer 2 as an evaluation device for the driving means are fixed. The engine 1 is disposed on a fixed base 7 via an anti-vibration support 3 and a restraint support device 4 which are fixing means, and a shaft 6 is connected to the output shaft of the engine 1. Thus, the output of the engine 1 is transmitted to the dynamometer 2. Then, the dynamometer 2 measures the output of the engine 1.
In addition, as shown in FIG. 2, the anti-vibration support 3 and the restraint support device 4 extend vertically upward from the fixed base 7, and the anti-vibration support 3 is connected to the front portion of the engine 1, and the restraint support device 4 is connected to the rear portion of the engine 1 to support the vibration isolation of the engine 1. The restraint support device 4 is located between the engine and the dynamometer 2 and is connected to the engine 1 via a connection arm 5 having one end fixed to the engine 1. The connection arm 5 extends in a substantially horizontal direction forward from the restraining device 4 and is connected to the left and right at the rear portion of the engine 1. A shaft 6 connected to the drive shaft of the engine 1 is disposed between the two connection arms 5. The restraint support device 4 is provided so as to cover both the left and right sides and the lower side of the shaft 6, and does not contact the shaft 6.

  As shown in FIG. 3, the anti-vibration support 3 connected to the front portion of the engine 1 includes a stay 3a, an anti-vibration rubber 3b, a bending arm 3c, and a column 3d. One end of the stay 3a is fixed to the front upper portion of the engine 1, and the other end of the stay 3a is connected to a vibration isolating rubber 3b. The anti-vibration rubber 3b is installed on the bending arm 3c, and the bending arm 3b is bent in a C shape in a side view so as to avoid interference with the engine 1. The lower part of the bending arm 3 c is fixed to a column 3 d installed on the fixing base 7.

The restraint support device 4 is disposed behind the engine 1 and is connected to the engine 1 by a connection arm 5 as shown in FIG. The front end of the connection arm 5 is fixed to the rear crank end surface of the engine 1, and the rear portion of the connection arm 5 is connected to the restraint support device 4 via the rear arm 5b. The rear arm 5 b is attached to the restraint support device 4 so as to face forward, and is connected to an inner portion of the restraint support device 4. As shown in FIG. 1, the shaft 6 is positioned between the rear arms 5b and 5b, and the shaft 6 is disposed further inside the inner side surface of the restraint support device 4 in plan view.
Thereby, the rear part of the engine 1 is supported by the restraint support device 4 and the restraint support device 4 and the shaft 6 do not interfere with each other.

Next, the configuration of the restraint support device 4 will be described with reference to FIGS.
FIG. 5 is a diagram showing the plane and side surfaces of the restraint support device, FIG. 6 is a diagram showing the front and rear surfaces of the restraint support device, and FIG. 7 is a schematic diagram showing the assembly configuration of the restraint support device.
As shown in FIGS. 5 and 6, the restraint support device 4 includes a frame 41 fixed on the fixed base 7, a connection portion 42 located inside the frame 41, and vibration isolation members 43, 43,. Composed. The vibration isolation member 43 is disposed between the frame 41 and the connection portion 42. The engine 1 is connected to the front surface of the connection portion 42 via the rear arm 5 b and the connection arm 5.
An opening 45 is formed in the upper portion of the restraint support device 4, and the shaft 6 is disposed inside the restraint device 4 through the opening 45. The restraint support device 4 and the shaft 6 are not in contact with each other when the engine 1 is supported by the restraint support device 4. The frame 41 and the connecting portion 42 are configured in a cylindrical shape and provided with an opening at the top, and are configured in a C shape with the opening facing upward in a front view. The opening 45 is configured by matching the openings of the frame 41 and the connection part 42 upward.
Further, as shown in FIG. 7, the vibration isolation member 43 disposed between the frame 41 and the connection portion 42 is disposed in parallel in the front-rear direction, and the inner surface of the frame 41 and the outer surface of the connection portion 42 are arranged. Connect. Accordingly, the connection portion 42 is supported by the frame 41 in an anti-vibration manner, and the engine 1 connected to the connection portion 42 via the rear arm 5b and the connection arm 5 is supported in an anti-vibration manner.

FIG. 8 is a diagram showing the arrangement configuration of the vibration isolation member, FIG. 8A shows the arrangement state of the vibration isolation member in the restraint support device, and FIG. 8B shows the minimum arrangement configuration of the vibration isolation member. FIG.
As shown in FIG. 8, the anti-vibration members 43 are arranged at substantially equal intervals in the circumferential direction of the shaft 6 between the frame 41 and the connection portion 42, and the number of the anti-vibration members 43 is determined. By appropriately selecting, the support characteristics of the restraint support device 4 can be easily adjusted. With such a configuration, not only can the support characteristics of the restraint support device 4 be easily adjusted, but also the assembly supportability of the restraint support device 4 is high, and high maintainability can be obtained.
Specifically, as shown in FIG. 8B, the vibration isolating member 43 is arranged so that it is point-symmetric about the axis of the shaft 6 and is symmetrical in the restraint support device. Arrangement is performed as follows. By disposing the vibration isolating member 43 in this way, it is possible to obtain a vibration isolating characteristic that absorbs vibration of the engine 1 with respect to the isotropic centering on the shaft 6. Thereby, the engine 1 can be fixed easily and reliably, and the displacement of the engine 1 can be efficiently absorbed regardless of the direction in which the engine 1 is displaced by vibration.
In the embodiment shown in FIG. 8 (b), six anti-vibration members 43 are used. However, the present invention is not limited to this, and as long as anti-vibration characteristics of engine vibration can be obtained, The number of anti-vibration members 43 is not particularly limited. In addition, in order to support the weight of the engine 1, it is preferable that a sufficient number of vibration isolating members 43 are disposed below the connection portion 42 that supports the engine 1. By arranging the vibration isolating member 43 in this way, the connection portion 42 connected to the engine 1 can be reliably held inside the frame 41 while maintaining a sufficient clearance. Then, it is possible to easily and appropriately cope with the natural frequency of the spring mass system having the engine 1 as a mass by adjusting the number of wire rope vibration isolator as the vibration isolating member 43.

Next, the configuration of the vibration isolation member 43 will be described.
FIG. 9 is a diagram showing the configuration of the vibration isolating member, FIG. 9 (a) is a perspective view, FIG. 9 (b) is a front view, and FIG. 9 (c) is a side view.
As the vibration isolating member 43, a member having an elastic element and a damping element with respect to three independent directions is used. In this embodiment, a wire rope vibration isolator is used. The vibration isolating member 43 includes a spiral wire 43b and guides 43c and 43c into which the wire 43b is inserted. The guides 43c and 43c extend in the direction of the central axis of the spiral of the wire 43b, and are disposed at symmetrical positions with respect to the central axis.
The anti-vibration member 43 is connected to the frame 41 and the connecting portion 42 via the guide 43c.
The vibration isolator 43 can obtain a large attenuation by the friction of the wire 43b, and can also absorb an impact by utilizing a large deflection of the wire 43b. Furthermore, vibration isolation can be performed against vibration in three independent directions.

Next, characteristics of the restraint support device 4 when a wire rope vibration isolator is used as the vibration isolation member 43 will be described.
FIG. 10 is a diagram showing gain characteristics and phase characteristics of the vibration isolating support device, FIG. 10 (a) is a diagram showing gain characteristics, and FIG. 10 (b) is a diagram showing phase characteristics.
In the figure, the thin line indicates the case where the anti-vibration rubber is used as the anti-vibration member 43, the chain line indicates the case where the anti-vibration rubber with a stopper is hitting the stopper, and the alternate long and short dash line is a metal and high rigidity support (metal support) The thick line shows the case where a wire rope vibration isolator is used.
When vibration-proof rubber is used, in order to restrain the crank end surface of the engine 1, it is necessary to select one having a large spring constant. However, when the engine 1 is restrained by the vibration proof rubber, the support portion becomes too large.
When a vibration-proof rubber with a stopper is used, the movement of the crank end surface of the engine 1 can be restricted, but a resonance point is provided in the normal rotation region of the engine 1, and a large vibration is transmitted to the fixed part near the resonance point. It will be.
In the case of using a metal support having high rigidity, the crank end surface of the engine 1 can be restrained, but a large vibration of the engine 1 is transmitted to the fixed portion. Moreover, it has a resonance point in the normal rotation range of the engine, and a large vibration is transmitted to the fixed part.
When a wire rope vibration isolator is used, it has a resonance point at a frequency lower than the normal rotation range of the engine 1 while sufficiently restraining the crank end face, and hardly amplifies vibration even near the resonance point due to high attenuation.

Next, an experiment was conducted to confirm the displacement of the engine 1 and the frame 41 of the support fixing device 4 when a wire rope vibration isolator was used as the vibration isolation member 43.
A laser displacement meter was used for measuring the displacement.
The vibration of the engine was measured in the vertical and horizontal directions on the crank end face and crank pulley side.
The vibration of the restraint support device 4 was measured by an accelerometer attached to the frame 41.
FIG. 11 is a graph showing engine vibration and vibration of the restraint support device 4 with respect to the engine speed. In FIG. 11, a indicates the magnitude of vibration (G) that occurs as the rotational speed of the engine 1 changes, and b similarly indicates the magnitude of vibration (G) that occurs as the rotational speed of the engine 1 changes. As shown in FIG. 11, it can be seen that the restraint support device 4 is attenuated over the entire engine speed range in which vibration from the engine 1 is shifted.
Although the engine vibration shows a maximum of 40G, the frame of the restraint device 4 is attenuated to about 5G.
As is apparent from this measurement result, by using the drive means evaluation apparatus of the present invention, the vibration of the engine 1 can be effectively suppressed in the entire engine speed range, so that highly accurate engine output measurement can be performed. Can be done.

In the second embodiment, a clutch housing is attached to the engine end surface, and the engine is connected to the restraint support device 4.
FIG. 12 is a diagram showing an engine support configuration of the second embodiment, FIG. 12 (a) is a plan view of the engine support configuration of the second embodiment, and FIG. 12 (b) is a side view of the engine support configuration of the second embodiment. FIG.
The engine 1 is supported on a fixed base 7 via an anti-vibration support 3 and a restraint support device 4, and the output of the engine 1 is transmitted to a dynamometer 2 via a shaft 6.
The anti-vibration support 3 is connected to the front part of the engine 1, and the restraint support device 4 is connected to the rear part of the engine 1 to support the anti-vibration of the engine 1.
A clutch housing 9 is attached to the rear end surface of the engine 1, and the rear portion of the clutch housing 9 is connected to the restraint support device 4. The clutch housing 9 is for housing the drive means, and the drive shaft of the engine 1 is mounted thereon.
The housing 9 and the restraint support device 4 are connected via a rear arm 5b, and can be easily connected to various engines 1 by the rear arm 5b.
The clutch housing 9 can be the same as that used when the engine 1 is mounted on a vehicle. By using the clutch housing 9 as an arm member for connecting to the restraint support device 4, it is possible to avoid interference such as a starter, an air cleaner, an exhaust pipe and a catalyst disposed near the crank end face of the engine 1. Further, since a clutch housing which is a member for mounting on a vehicle is used, it is not necessary to newly design and manufacture a connecting arm member, and the labor required for mounting the engine 1 can be reduced.

The top view which shows the engine evaluation apparatus for evaluating the engine as a drive means. The side view which shows the side of an engine evaluation apparatus. The side view which shows the support structure in the front part of an engine. The side view which shows the support structure in the rear part of an engine. The figure which shows the plane and side surface of a restraint support apparatus. The figure which shows the front and rear surface of a restraint support apparatus. The schematic diagram which shows the assembly | attachment structure of a restraint support apparatus. The figure which shows the arrangement configuration of a vibration isolator. The figure which shows the structure of a vibration isolator. The figure which shows the gain characteristic and phase characteristic of an anti-vibration support apparatus. The graph which shows the engine vibration with respect to engine speed, and the vibration of a restraint support apparatus. FIG. 6 is a diagram showing an engine support configuration of Embodiment 2.

DESCRIPTION OF SYMBOLS 1 Engine 2 Dynamometer 3 Anti-vibration support tool 4 Restraint support device 5 Connection arm 6 Shaft 7 Fixing base

Claims (3)

An apparatus for evaluating a drive means, wherein the drive means is connected to a dynamometer placed on a fixed base via a shaft connected to an output shaft of the drive means, and the output of the drive means is evaluated by the dynamometer. There,
Having a fixing means for fixing the driving means on a fixing base via a wire rope vibration isolator,
The fixing means is located between the driving means and the dynamometer, and is connected to the shaft side end surface of the driving means,
The shaft is disposed inside the fixing means;
The fixing means and the shaft are spaced apart ;
The fixing means is located below the shaft and extends in a vertical direction from above the fixing base, and extends substantially horizontally from the restraining support apparatus, and one end thereof is fixed to the driving means. An arm, and the restraint support device and the other end of the arm are connected via the wire rope vibration isolator,
A plurality of the wire rope anti-vibration devices are arranged on the circumference around the shaft,
The drive means evaluation apparatus characterized by the above-mentioned. The one end of the arm is fixed to a housing for accommodating the driving means, and the arm and the driving means are fixed via the housing . Drive means evaluation apparatus. A vibration buffer used in a drive means evaluation apparatus for connecting a drive means to a dynamometer placed on a fixed base via a shaft connected to an output shaft of the drive means and evaluating the output of the drive means with the dynamometer. In the method
Via the fixing means equipped with a wire rope vibration isolator, the driving means is fixed on a fixing base, and the vibration generated from the driving means is buffered,
The fixing means is located between the driving means and the dynamometer, and is connected to the shaft side end surface of the driving means,
The shaft is disposed inside the fixing means;
The fixing means and the shaft are spaced apart;
The fixing means is located below the shaft and extends in a vertical direction from above the fixing base, and extends substantially horizontally from the restraining support apparatus, and one end thereof is fixed to the driving means. An arm, and the restraint support device and the other end of the arm are connected via the wire rope vibration isolator,
A plurality of the wire rope anti-vibration devices are arranged on the circumference around the shaft,
The vibration buffering method used for the drive means evaluation apparatus characterized by the above-mentioned.

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