JP3662045B2 - Vehicle engine test pallet and test bench - Google Patents

Description

[0001]
[Industrial application fields]
The present invention relates to a test pallet and a test bench for performing a firing test or the like of a single engine in a vehicle engine completion inspection process or the like.
[0002]
[Prior art]
In the manufacturing process of engines for vehicles such as automobiles, a complete inspection is carried out for all the engines after assembly is completed by a firing test in which the engine is started and warmed up with no load.
[0003]
In this firing test, the engine before being mounted on the vehicle is transported to the test bench in a state of being placed on the test pallet, the engine is tested on the test pallet, and visual inspections such as oil leaks and engine The product will be evaluated based on the sound, vibration, etc. of the product, and products that pass such a firing test will be shipped, while if a defect is found, it will be sent to a separate repair bench. In this repair bench, a load such as a dynamometer is connected to the engine placed on the test pallet and the operation is performed again to identify the defective part. In addition, sensor evaluation based on human sensation and automatic determination by a measuring instrument are performed as appropriate to evaluate engine malfunctions based on engine sound and vibration, and both of these may be used together. Is collectively referred to as sound vibration determination.
[0004]
In such a completion inspection line, the test pallet used for transporting the engine is composed of two plate-like members, a base pallet 92 and a support pallet 93, as shown in FIGS.
[0005]
Anti-vibration rubber 94 is interposed at predetermined positions between the base pallet 92 and the support pallet 93, for example, at four corners of the support pallet 93, in order to suppress transmission of engine vibration to the base pallet 92. . As the anti-vibration rubber 94, a mountain-shaped one shown in FIG. 11 or a V-shaped one shown in FIG. 12 is used.
[0006]
The support pallet 93 supports the engine (not shown) through support columns 96 and 97 projecting upward, while the base pallet 92 engages with a transfer means and a test bench (not shown) to transfer and position the engine. Although not shown in the drawing, auxiliary equipment for connecting the engine fuel system, lubrication system, electrical system, and cooling system to the test bench is provided. The through-hole 93A formed in the support pallet 93 is provided for connection to an oil pan (not shown) of the engine and auxiliary equipment such as a drain.
[0007]
After the engine sent from the assembly line is placed on the support pallet 93, it is transported and positioned to the test bench by the transport means, and is started and warmed up. Is transported to the exit of the completion inspection line, and the engine is removed from the support pallet 93 and shipped. On the other hand, if the engine is defective, the base pallet 92 is moved from the test bench and transported to a predetermined repair bench. Then, connect the engine output shaft to a dynamometer (not shown) via a clutch and perform further tests.
[0008]
In addition, as an engine transportation and positioning means in the completion inspection line, there is also known one that transports the engine to a test bench while hanging the engine with a hanger.
[0009]
[Problems to be solved by the invention]
By the way, in the sound vibration determination based on the sound and vibration of the above firing test, it is determined whether there is a missing part or a poor assembly from abnormal noise from the engine, abnormal vibration of the engine, etc. I have to figure it out.
[0010]
However, in the conventional test pallet, the vibration isolating rubber 94 of FIG. 11 or FIG. 12 has a high natural frequency and a high dynamic spring constant in the vibration frequency region of the engine. The engine vibrates as one inertial system including these test pallets, and as shown in FIG. 14, the vibration level is remarkable in a normal V type 6 cylinder engine and an engine in which only one cylinder is misfired. Since there is no significant difference, the vibration of the engine alone cannot be accurately grasped, and the accuracy of sensory evaluation by sound and vibration may be reduced. In addition, the engine and dynamometer on the repair bench are simply connected via a clutch, etc., and likewise vibrates as an inertial system that includes the dynamometer side. There was a problem that I could not.
[0011]
Therefore, the present invention has been made in view of the above problems, and an object of the present invention is to provide a test pallet and a test bench for a vehicle engine that can accurately grasp the vibration of a single engine.
[0012]
[Means for Solving the Problems]
A first invention is a vehicle engine test bench comprising measuring means for measuring an output of an engine and means for connecting the measuring means and an output shaft of the engine.
A universal joint coupled to the measuring means for absorbing axial displacement; a supporting means for supporting one end of the universal joint on the engine side so as to be relatively displaceable with respect to the measuring means; and an output of the engine at one end A universal joint having a coupling coupled to a shaft and having the other end coupled to the universal joint; and a housing housing a bearing that pivotally supports the coupling on the engine side of the universal joint; Is supported so as to be relatively displaceable in the radial direction and the axial direction of the universal joint with respect to the support means via a fluid sealing mount, and has one end formed to be fastened to an end surface of the engine, and supports the engine. A first pallet and a second pallet that supports the first pallet via a fluid-filled mount; For example,
The second pallet is disposed at a position where the output shaft of the engine is coupled to the coupling .
[0013]
The second invention is the first invention, the front Stories second pallet, as well as arranging a plurality of the fluid-filled mount, substantially equal from the center of gravity position of the combined said first pallet and the engine distance fluid filled mount respectively Ru Hai設Su.
[0015]
In the third invention, the first pallet includes a through hole for weight reduction.
[0016]
[Action]
In the first invention , the universal joint and the universal joint are interposed between the engine output measuring means and the engine output shaft, and the housing supporting the universal joint on the engine side is supported via the fluid sealing mount. The vibration system integrated with the engine extends to the universal joint on the engine side, blocking the transmission of engine vibration to the measurement means to suppress equipment noise and reducing the natural frequency of the vibration system to be mounted on the vehicle. The engine can be operated under conditions close to the state.
[0017]
In the second aspect of the invention, vibration generated during operation of the engine is suppressed from being transmitted from the first pallet to the second pallet by the fluid-filled mount. Further, since the plurality of fluid enclosure mounts are disposed at substantially the same distance from the center of gravity position of the vibration system integrated with the engine, the vibration attenuation characteristics of the respective fluid enclosure mounts can be made substantially uniform. Transmission of vibration to the pallet can be reliably suppressed.
[0019]
In the third aspect of the invention, the through-hole for reducing the weight is formed in the first pallet. Therefore, the mass of the vibration system integrated with the engine can be reduced, and the engine can be operated under conditions close to the vehicle mounted state. Driving tests can be performed.
[0020]
【Example】
Embodiments of the present invention will be described below with reference to the accompanying drawings.
[0021]
As shown in FIGS. 1 to 4, in the same completion inspection line as the conventional example, the test pallet 20 used for transporting the engine is composed of two substantially square plate-like members, a base pallet 2 and a support pallet 3. The support pallet 3 is disposed above the base pallet 2.
[0022]
The support pallet 3 is formed in a predetermined area smaller than that of the base pallet 2, and a through hole 30 for reducing the weight is formed substantially in the center. The through hole 30 can support the engine 1 and has a predetermined rigidity. Set to be possible.
[0023]
From the upper surface of the support pallet 3, support columns 6 and 7 for supporting the engine 1 are projected upward in the figure, and the engine 1 is supported by a total of five points including the four support columns 6 and the one support column 7. .
[0024]
A through hole 2A for inserting a locating pin 11 protruding from a test bench (not shown) is formed at a predetermined position of the base pallet 2, and the base pallet 2 sent to the test bench by a conveying means (not shown) 11 is inserted in the through hole 2 </ b> A to be arranged at a predetermined position on the test bench.
[0025]
Furthermore, the base pallet 2 includes auxiliary equipment (not shown) for connecting the engine fuel system, lubrication system, electrical system, and cooling system to the test bench.
[0026]
Here, between the base pallet 2 and the support pallet 3, fluid sealing mounts 4 that block vibration from the engine 1 to the base pallet 2 are arranged at a plurality of predetermined locations.
[0027]
As shown in FIGS. 4 and 5, the fluid sealing mount 4 has a through-hole 42 and a cylindrical portion 40 in which an elastic member such as rubber is formed in a substantially cylindrical shape, and penetrates in the X-axis direction in the figure at a predetermined position. The cutouts 41 and 41 are mainly configured. In addition, fluid chambers 4A and 4B filled with a predetermined working fluid are defined inside the cylindrical portion 40, and the fluid chambers 4A and 4B communicate with each other through an orifice (not shown), and penetrate the outer periphery of the cylindrical portion 40. A damping force is generated by the relative movement of the hole 42.
[0028]
The fluid sealing mount 4 configured as described above is inserted through the inner periphery of the through hole 42 into the pin 43 supported at both ends by a substantially U-shaped bracket 5 fixed at a predetermined position on the upper surface of the base pallet 2. On the other hand, the cylindrical portion 40 is accommodated in a cylindrical bracket 44 fixed to the lower surface of the support pallet 3 and interposed between the support pallet 3 and the base pallet 2.
[0029]
In this embodiment, the support pallet 3 is supported by the four fluid-filled mounts 4, and the center of gravity of the engine 1 is set to GC in the XY plane shown in FIG. 2, and the engine 1 and the support pallet 3 are combined. Assuming that the center of gravity position is GC ′, the fluid sealing mount 4 is disposed at a predetermined distance R from the center of gravity position GC ′ of the engine 1 and the support pallet 3 together. Arranged in parallel along the axis.
[0030]
It is comprised as mentioned above, Next, an effect | action is demonstrated.
[0031]
The engine 1 sent from the assembly line (not shown) is placed on the support pallet 3 and then transported to a test bench by a transport means (not shown) and arranged at a predetermined position. Start-up and warm-up operation are performed.
[0032]
During this time, visual confirmation and sound vibration determination based on sound and vibration are performed. If the engine 1 satisfies a predetermined standard, it is conveyed to the exit of a completion inspection line (not shown).
[0033]
Here, as shown in FIG. 6, the characteristics of the fluid sealing mount 4 that supports the support pallet 3 are such that the loss coefficient indicating the magnitude of the damping force is maximum at about 10 Hz, compared with the conventional anti-vibration rubber. If the idling speed of the engine 1 is about 600 rpm, transmission of vibration from the engine 1 to the base pallet 2 near the idling speed can be reliably suppressed.
[0034]
FIG. 6B shows a dynamic magnification that is a ratio of the dynamic spring constant K * and the static spring constant Kst. Since the dynamic spring constant of the fluid-filled mount 4 is smaller than the vibration-proof rubber, the engine is used even during steady operation. Transmission of vibration from 1 to the base pallet 2 can be suppressed.
[0035]
The plurality of fluid sealing mounts 4 are disposed at substantially the same distance from the gravity center position GC ′ including the support pallet 3 constituting the vibration system integrated with the engine 1, so that each fluid sealing mount 4 is arranged. Therefore, it is possible to reliably suppress vibration transmission from the engine 1 to the base pallet 2.
[0036]
Further, the test pallet 20 is divided into a support pallet 3 for supporting the engine 1 and a base pallet 2 for mounting and transporting and positioning auxiliary equipment, and the support pallet 3 has a through-hole for weight reduction. Since 30 is formed, the mass of the support pallet 3 can be reduced as compared with the conventional example, and the natural frequency of the vibration system that vibrates integrally with the engine 1 can be reduced. In comparison, sound and vibration can be evaluated in a state closer to the actual vehicle mounted state, and the evaluation accuracy can be improved.
[0037]
Thus, by reducing the natural frequency of the vibration system integrated with the engine 1 by reducing the weight of the support pallet 3 and supporting it by the fluid sealing mount 4, and by supporting this vibration system with a low dynamic spring constant, The transmission of vibrations to the base pallet 2 is suppressed, and it becomes possible to perform a firing test of the engine 1 in a state close to the actual vehicle mounted state even though the test pallet 20 is used. The vibration level when only one cylinder is misfired is shown in FIG. 13, and the difference between the vibration level when one cylinder is misfired with respect to the normal state is different from that in FIG. As a result, it becomes possible to facilitate the completion inspection of the engine by sound vibration determination and improve the accuracy of the completion inspection, It become possible to improve the accuracy of the inspection in the case of performing automatic evaluation process the vibration or sound detected by etc..
[0038]
In addition, the vibration transmitted from the base pallet 2 to the floor surface has been reduced, making it possible to promote the quietness of the equipment. The accuracy of sensory evaluation can be further improved by suppressing vibration.
[0039]
7 and 8 show a repair bench using the test pallet 20 described above .
[0040]
This repair bench mainly includes a constant velocity ball joint 9, a clutch 14 and a universal joint 16, which connect an output shaft (not shown) of the engine 1 conveyed by the test pallet 20 to the hydrodynamic meter 10 . A power test of the engine 1 or the like that has failed on such a test bench is performed. In this repair bench, the inspection engine, the special engine or the engine assembled in the special process is inspected in addition to the above-mentioned failure.
[0041]
A hydraulic dynamometer 10 that measures the output of the engine 1 is fixed to a predetermined height from the floor, and is a clutch supported by a linear guide 15 that can be displaced in the axial direction (X-axis direction in the figure) via a universal joint 16. 14. The linear guide 15 is displaced in the axial direction in order to adjust the coupling position with the engine 1 and is fixed to the floor side during operation of the engine 1.
[0042]
The universal joint 16 smoothly transmits the power of the engine 1 to the hydrometer 10 while absorbing the axial displacement of the linear guide 15.
[0043]
The linear guide 15 supports a constant velocity ball joint 9 for coupling with the output shaft of the engine 1.
[0044]
The constant velocity ball joint 9 couples relatively displaceable joints 9A and 9B with a shaft 9C, and joins the joint 9B to the input shaft 17 of the clutch 14, while the joint 9A is supported on the test pallet 20 through the coupling 13. The output shaft of the engine 1 is coupled. In the figure, 1A represents the flywheel of the engine 1, and the coupling 13 is coupled to the shaft of the flywheel 1A.
[0045]
Here, the joint 9 </ b> A and the coupling 13 of the constant velocity ball joint 9 are coupled to a shaft 19 supported by a bearing 18 housed in a housing 12 that can be displaced relative to the linear guide 15.
[0046]
The housing 12 is attached to the linear guide 15 via a plurality of cylindrical fluid sealing mounts 8 configured in the same manner as the fluid sealing mount 4 described above . A cylindrical bracket 80 attached to the clutch 14 side of the housing 12 supports the outer periphery of the fluid sealing mount 8 on the inner periphery, and the inner periphery of the fluid sealing mount 8 with a pin 81 fixed to the base end of the linear guide 15. The housing 12 is supported by the linear guide 15 so as to be relatively displaceable in the radial direction and the axial direction of the shaft 19 in accordance with the elasticity of the fluid sealing mount 8.
[0047]
Then, a flange portion 12A of the housing 12 that can be relatively displaced with respect to the linear guide 15 is fastened to an end face of the engine 1, and the engine 1 is coupled to the hydrodynamic meter 10 through the constant velocity ball joint 9 so as to be relatively displaceable. The
[0048]
When the operation of the engine 1 supported by the test pallet 20 is started, the vibration of the engine 1 is transmitted to the housing 12, but the transmission of vibration from the housing 12 to the linear guide 15 is absorbed and suppressed by the fluid sealing mount 8. The displacement of the output shaft due to the vibration of the engine 1 is absorbed by the constant velocity ball joint 9.
[0049]
While the engine 1 is supported on the floor via the fluid enclosure mount 4 of the test pallet 20, the output shaft side is coupled to the hydrodynamic meter 10 side via the fluid enclosure mount 8, so that a vibration system integrated with the engine 1 is provided. The support pallet 3 and the housing 12 are used to reduce the natural frequency of the vibration system as compared to the conventional example, and support the vibration system with a low dynamic spring constant. suppressing transmission of vibration, it is possible to perform power testing of the engine 1 in a state close to the actual vehicle mounted state, thereby improving the measurement accuracy of the power test, it is possible to promote the quietness of equipment.
[0050]
【The invention's effect】
As described above, in the first invention, the vibration system integrated with the engine is up to the universal joint on the engine side, and the transmission of the engine vibration to the measuring means can be cut off to promote the silence of the equipment. Furthermore, the natural frequency of the vibration system can be reduced as compared with the conventional example, and the operation test of the engine alone can be performed under conditions close to the vehicle mounted state, and the accuracy of measurement and evaluation of the engine Can be improved.
[0051]
The second invention includes a first pallet that supports the engine and a second pallet that supports the first pallet via a fluid sealing mount, and vibrations generated during operation of the engine are fluid-sealed. The low dynamic spring constant of the mount makes it possible to suppress the transmission from the first pallet to the second pallet, and the engine can be approximated to a state where it vibrates almost alone, compared to the conventional example. As a result, it is possible to improve the accuracy of the engine sound vibration determination, and to suppress the transmission of vibration from the second pallet to the floor surface, thereby reducing the noise of the equipment. In addition, the vibration attenuation characteristics of each fluid-filled mount are made almost uniform to reliably suppress the transmission of vibration from the first pallet to the second pallet, to suppress the noise of the equipment, and to perform sensory evaluation by sound and vibration. Accuracy can be improved.
[0053]
In the third invention, since the first pallet has a through hole for reducing the weight, the natural frequency is reduced by reducing the mass of the vibration system integrated with the engine, and the vehicle mounting state It is possible to accurately perform an operation test of the engine alone under conditions close to the above, and it is possible to improve test accuracy such as sensory evaluation of the engine as compared with the conventional example.
[Brief description of the drawings]
FIG. 1 is a front view of a test pallet showing an embodiment of the present invention.
FIG. 2 is also a plan view.
FIG. 3 is a right side view of the same.
FIG. 4 is a front view of a fluid sealing mount.
FIG. 5 is a sectional view of the same.
FIG. 6 is an explanatory diagram showing vibration characteristics of a fluid-filled mount and vibration-proof rubber.
FIG. 7 is a front view showing a test palette and test bench.
FIG. 8 is a cross-sectional view of an essential part showing a constant velocity ball joint.
FIG. 9 is a front view of a test pallet showing a conventional example.
FIG. 10 is also a plan view.
FIG. 11 is a perspective view showing a vibration-proof rubber.
FIG. 12 is a perspective view showing another anti-vibration rubber.
FIG. 13 is a graph showing the relationship between engine rotation order and vibration level according to the test pallet of the present application;
FIG. 14 is a graph showing the relationship between engine rotation order and vibration level according to a conventional test pallet;
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Engine 2 Base pallet 3 Support pallet 4 Fluid enclosure mount 8 Fluid enclosure mount 9 Constant velocity ball joint 10 Hydrodynamic meter 12 Housing 13 Coupling 14 Clutch 20 Test pallet 30 Through-hole

Claims (3)

Measuring means for measuring the output of the engine;
In a vehicle engine test bench comprising the measuring means and means for connecting the output shaft of the engine,
A universal joint coupled to the measuring means for absorbing axial displacement;
Supporting means for supporting one end of the universal joint on the engine side so as to be relatively displaceable with respect to the measuring means;
A universal joint having one end coupled to the output shaft of the engine and the other end coupled to the universal joint;
A housing that houses a bearing that pivotally supports the coupling on the engine side of the universal joint,
The housing is supported so as to be relatively displaceable in the radial direction and the axial direction of the universal joint with respect to the support means via a fluid-filled mount, and one end is formed to be fastened to an end surface of the engine .
A first pallet that supports the engine;
A second pallet that supports the first pallet via a fluid-filled mount;
A test bench for a vehicular engine , wherein the second pallet is disposed at a position where an output shaft of the engine is coupled to the coupling . The second pallet is provided with a plurality of the fluid-filled mounts, and the fluid-filled mounts are disposed at substantially equal distances from the center of gravity of the first pallet and the engine. Item 12. A test bench for a vehicle engine according to Item 1.   The vehicle engine test bench according to claim 2, wherein the first pallet includes a through hole for weight reduction.

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