JPS62288712A - Resonance preventing mechanism for linear member - Google Patents

Abstract

PURPOSE:To enable a control cable to be prevented from its resonance, by restricting the movement in a node part of a flow pipe to the turning about two axes with a supporting part serving as the rotary center and limiting the turning about the node part by a damping means. CONSTITUTION:A case main unit 10 resists by its pipe-shaped part 11 and peripheral part 13 against external force in the axial direction as shown by an arrow head Fa in the drawing, further an annular elastic member, to which compression force is uniformly applied, shows strong resistance. While a part between a flange 5 and a root part 19 shows strong resistance against forces Fr1, Fr2 acting in the radial direction. However, a secured member 6, for its turning in the direction of arrow heads P1, P2, can be relatively freely turned with the vicinity of a part, shown by a code X, serving as the center. Accordingly, the turning is damped by internal friction of an elastic ring 21, which is a pressure medium pressurized mainly by a conical coil spring 27, and a control cable is formed so as to enable its resonance to be prevented.

Description

[Detailed description of the invention] 3 Detailed explanation of the invention [Industrial application field] The present invention relates to a resonance prevention mechanism for a linear member.

More specifically, the present invention relates to a resonance prevention mechanism for a linear member in a structure in which one end or a portion of the linear member is connected to a vibration source, and the other end or other portion of the linear member is connected to and supported by a stationary member.

The linear member referred to in this specification refers to a control cable,
When one fixed end of an electric wire, flexible tube, etc. receives external vibration, the part between the other fixed end and the one fixed end vibrates like a string or beam depending on its natural frequency. , a concept that includes all elongated members that produce resonance primarily in the lateral direction.

Hereinafter, in order to facilitate understanding, a control cable will be described in detail as a representative example, but the present invention is not limited thereto, and can be applied to any of the linear members described above.

[Conventional technology]

The control cable consists of, for example, a flexible conduit made of a metal spiral tube coated with synthetic resin, and an inner cable made of twisted metal wire that is slidably inserted in the conduit in the axial direction.
has been completed. In this type, the conduit receives the reaction force of the tension or pressing force exerted by the inner cable, thereby smoothly guiding the inner cable along the axial direction.

Such a control cable is used, for example, to remotely control a driven device in the engine compartment of an automobile by operating or operating means such as a lever in the driver's seat. In that case, one end of the conduit is fixed inside the engine room, and the other end is fixed inside the driver's cab, but as mentioned above, the conduit is fixed to ensure that it supports the reaction force of the operating force applied to the inner cable. Both ends of the conduit are usually firmly fixed with cable caps made of metal cylindrical members or the like. Therefore, there is a problem in that vibrations in the engine compartment are transmitted to the driver's seat, causing discomfort to passengers.

Conventionally, in order to solve this problem, for example, as shown in FIG. 11, a mounting flange (82) provided on the front member (81) and a stationary member (8
3) between the anti-vibration rubber block or rubber pad (8
4) etc. are interposed.

[Problem that the invention seeks to solve]

Conventional anti-vibration rubber simply blocks the vibrations transmitted from the vibration source, and due to the wide frequency band vibration generated by vibration sources such as the engine, the control cable is fixed at the part in the engine room and during operation. There is almost no effect in preventing the resonance phenomenon in which the portion within the seat between the seat and the fixed portion vibrates greatly according to its natural frequency.

In particular, even when an engine is rotating at a constant number of revolutions, it generates vibrations with frequencies distributed over a certain range, and the number of revolutions changes over a wide range depending on the accelerator operation. Therefore, there is a problem in that the control cable resonates with the vibration corresponding to the natural frequency of the broadband white noise, and generates unexpectedly large noise.

On the other hand, it is possible to improve the anti-resonance performance by improving the overall damping effect of the vibration isolating rubber, but in that case, the displacement of the fixed position of the conduit, especially in its axial direction, would be large. , the stroke loss of the control cable (loss when the amount of operation on the output side is smaller than the amount of operation on the input side of the inner cable) not only increases, the force transmission efficiency decreases, but also the natural vibration of the system The problem is that it won't go away.

The present invention has been made in order to solve the above problem, and aims to provide a mechanism that can prevent resonance without impairing the fixing action of a linear member to a stationary member, especially the operability of a control cable. There is.

[Means for solving problems]

The resonance prevention mechanism for a linear member of the present invention is such that (a part of the linear member is not moved in the axial direction and in two directions perpendicular to the axial direction, and in a direction perpendicular to the axial direction). A support member for rotatably supporting the curved linear member around the two axes, and a damping means for restricting the rotation of the curved linear member around the two axes and damping the rotation around the two axes. It is configured.

[For production]

In the mechanism of the present invention, a part of the conduit of the control cable is supported by the support structure so as not to move in the axial direction and in two axes perpendicular to the axial direction, and furthermore, Since rotation is allowed, movement of the conduit node is limited to rotation around two axes around the support site.

Note that wire members such as control cables are usually
In the low frequency range, only transverse vibration is performed, so
Even if the movement of the joints is restrained as described above, the joints vibrate freely with their positions fixed. In this state, the damping means restricts the rotation around the joint, so that a certain damping effect is provided, and resonance of the control cable does not occur.

In that case, the damping means act only in the rotational direction, so that no axial displacement of the conduit occurs. Therefore, even when the control cable is operated, based on the function of suppressing the movement of the support means in the axial direction, no stroke cross is caused in the control cable, and the transmission efficiency is not reduced.

The above effect is the same for other linear members other than the control cable, and resonance of electric wires, flexible tubes, etc. can be effectively prevented.

〔Example〕

Next, various embodiments of the mechanism of the present invention embodying the above configuration will be described with reference to the drawings.

1 to 3 are longitudinal cross-sectional views showing embodiments of the mechanism of the present invention, and FIGS. 4 and 5 are plan and front views of an apparatus for measuring the damping effect of the mechanism of the present invention, respectively. 6 and 7 are longitudinal cross-sectional views of the test mechanism used to measure the damping effect of the mechanism of the present invention, respectively.
Figures a to 8h, Figures 9a to 9h, and Figures 10a to 10h are graphs showing measurement results by the apparatus shown in Figures 4 to 5, respectively.

The mechanism (A) shown in FIG. 1 is for fixing one end of the conduit (1) of a control cable consisting of a conduit (1) and an inner cable (2) to a stationary member (3).

This has a sleeve (4) fixed to the outer periphery of one end of the conduit (1) and a fixing member (6) consisting of a disc-shaped flange (5) provided at one end of the sleeve (4). A hole (7) for inserting the inner cable (2) is formed in the flange (5).

Inserted into the hole (7) is one end (8a) of a liner (8) that is durable and slippery against sliding friction with the inner cable (2). A case body 00) having an annular groove (9) opening in the axial direction and having a U-shaped cross section is provided around the outer periphery of the liner (8) and the flange (5).

That is, the main body 00) curves from one end of the tubular part 01) surrounding the liner (8) and rises perpendicular to the axis, and comes into contact with the flange (5) of the fixing member (6). A disk-shaped wall part 021 and a cylindrical outer peripheral part (2) extending in the axial direction from the outer peripheral edge of the wall part on the same side as the tubular part 011 are nailed together.

Furthermore, the flange (
5) is integrally formed with an engaging protrusion having an engaging groove (141) that is engaged with the outer periphery of the engaging protrusion.

A plate Oe is in close contact with the opening side of the annular groove 04), and the tubular portion 01) is in close contact with the central part of the plate Of3.
A hole is formed in close contact with the outer periphery of the hole.

A base 09 of a cylindrical metallic spring case 5 is fitted onto the outer periphery of the outer periphery 03 of the case body 00), and is adhered to the case body (to) and the plate Oe with adhesive, respectively. This reinforces the connection and sealing between the case body 00) and the plate Oe.

A conical coil spring is installed between the radially inwardly bent tip of the spring case 4 and the flange (5) of the fixing member (6) for constantly pressing the flange (5) in the direction of the arrow (Pa). is interposed in a compressed state.

The tip of the conical coil spring blade is circular with a relatively small diameter, so the arrows (Pl) and (P2) of the fixing member (6)
There is almost no resistance to rotation in the direction.

Moreover, since the diameter near the end of the conical coil spring tray is large, there is no interference when the fixing member (6) rotates.

Incidentally, a bolt hole (2) for connecting the entire mechanism (A) to the stationary member (3) is formed near the outer periphery of the plate OG. That is, the plate Oe also serves as a mounting flange for the mechanism (A).

In the annular cavity formed by the annular groove (9) and the plate O, there is an elastic ring (2) made of a relatively soft polymer elastomer such as rubber with a JIS hardness of A30°.
1) is sealed under pressure.

The elastic ring opening constitutes the pressure medium.

The case body (G) is usually made of rubber with a JIS hardness of A60''.
), the base (1 (1) and the plate 0e are made of a rigid metal such as mild steel, and the liner (8) is made of a synthetic resin material such as polyacetal resin.

That is, the mechanism (A) has a base a between the fixing member (6) and the plate OQ, each having rigidity.
It is constructed by interposing an annular elastic member (main body OO) surrounded by g and an elastic ring (2° C.).

In the mechanism (A) configured as shown in Section 2, the case body 00)
The tubular part H and the outer peripheral part (131) resist, and the annular elastic member (case body (goods) and elastic ring (2v)
It exhibits strong resistance because the compressive force is applied uniformly to the

Furthermore, the wall portion 02, particularly the portion between the flange (5) and the base portion OC4, exhibits strong resistance to the forces (Frl) and (Pr2>) applied in the radial direction.

However, the fixing member (6) can be rotated relatively freely in the directions of arrows (Pl), (P2), etc. around the area indicated by the symbol (X). In that case, it can be damped mainly by internal friction of an elastic ring (211) which is a pressure medium pressurized by a conical coil spring.

The hardness of the elastic ring (21) is preferably as soft as possible in order to enhance the damping effect, but the lower limit is usually around JIS hardness A30' due to molding problems, so it is recommended to have a hardness of around A30~40°. is used.

In the mechanism (B) shown in FIG. 2, the mechanism (A) shown in FIG.
) in the elastic ring (2n), a relatively high viscosity semi-fluid (31) such as silicone grease is used as the pressure medium.Therefore, in order to seal the semi-fluid under pressure so that it does not leak, the spring Case 4 base 09
The rib (32) of the case body (to) extends radially outward.
), seal plate (33) and seal sheet (34)
) is roll-tightened so as to integrally cover the outer peripheral edge of the seal plate (33), and the inner peripheral side of the seal plate (33) is in close contact with the outer peripheral part of the cylindrical part 01) of the case body (a)) over a wide area. .

Further, in order to attach the entire mechanism (13) to the stationary member (3), a ring-shaped flange (35) is arranged around the outer periphery of the base shell.

Furthermore, a spacer (36) made of, for example, rubber is bonded with an adhesive so as to cover the entire outer surface of the flange (35), the base Og4, and the seal seat (34).

Note that the fixing member (6) and the case body 00), the case body (
10) and the seal plate (33), the spacer (36) and the seal sheet (34), and the flange (35) and the spacer (36), etc., are each bonded to each other with an oil-resistant adhesive.

As the grease to be sealed, it is preferable to use an exotropic grease such as silicone grease with a consistency of about 19. Compared to the mechanism (A) shown in FIG. 1, this mechanism (B) exhibits a more efficient and reliable damping effect based on the fluid friction of grease, and therefore has a high resonance prevention effect.

In the mechanism (C) shown in FIG. 3, a ball joint (41) is employed as a means for rotatably holding the fixed member (6) relative to the stationary member (3). In other words, the cylindrical portion (42) extends to the distal end side of the fixing member (6).
Fit the ball (43) on the outer periphery of the mounting flange (44), fit the socket member (46) into the opening side of the bottom cylindrical case (45), and insert the socket member (4B) into the socket member (4B). The ball (43) is rotatably fitted into the formed spherical recess (47), and the case (45)
) and seal the rubber body (49) under pressure in the case (4).
A configuration is adopted in which the open end (48) of 5) is rolled around the outer periphery of the socket member (46).

In the mechanism (C), everything except the rubber body (49) is made of rigid material.

Next, using the embodiment of the mechanism of the present invention, we will explain how to measure the relationship between the initial pressing force (parameter that specifies the damping coefficient) applied to the elastic ring (21) etc. and the effect of suppressing resonance. , will be explained based on actual tests and their results.

In Figures 4 and 5, (51) is a vibration testing machine modeled on the engine room of an automobile. The vibration tester (51) is I
MV Corporation (7) VS-32OS was used. On the vibration tester (51) are two mounting plates (52), (
53) was established. In addition, another mounting plate (54) was installed on a stationary member separate from the vibration tester (51). A conduit (1
) is connected to one mounting plate (52) on the vibration tester (51) using a cable cap (55), and the other end is connected to the mounting plate (54) of the stationary member. They were connected via a prevention mechanism (M). Furthermore, one end of the inner cable (2) was attached to the other mounting plate (53) on the vibration tester (51), and the other end was connected to one end of a lever (5G) that was modeled as a clutch pedal. The other end (57) of the lever (5G) has a pickup (5
B) and expanded inner cable (2) with lever ratio 5,8.
) is picked up as vibration acceleration.
58).

The vibration direction of the vibration tester (51) is indicated by the arrow (Kl) - (K2
) direction, the vibration acceleration was kept constant with IG, and only the frequency was changed in the range of 20 to 200 Hz.

In other words, the vibration tester (51) is likened to a car engine, and the lever (5B) corresponding to the clutch pedal in the driver's seat is
) to measure the vibrations that should be transmitted to the driver's feet.

The distance fi (Ll) between the mounting plates (52) and (54)
) is 389 m, and the height difference (H) between both ends of conduit (1) is 28
5mm.

The horizontal distance (L2) was 435 mm.

The following three types of resonance prevention mechanisms (M) were measured.

Example 1 The mechanism (A2) shown in FIG. 6 was used as Example 1. This one has substantially the same structure as the mechanism (8) shown in Figure 1, but the spring case (to) has been removed leaving only the base 09, and the initial pressure to be applied to the flange (5) via the conical coil spring surface is (F) is configured so that it can be changed. In addition, as an elastic ring, JIS rubber hardness is A30.
' rubber was used.

Example 2 The mechanism (B2) shown in FIG. 7 was used as Example 2. This device has substantially the same mechanism as the mechanism (B) shown in FIG. 2, but like the first embodiment, the tip side of the spring case (42) is removed. In addition, semifluid (
As 3), silicone grease (consistency No. 1) manufactured by Nippon Grease ■ is used.

Comparative Example As a representative conventional vibration-proof cable cap, one having the structure shown in FIG. 11 was adopted as a comparative example. The rubber pad (84) of this item is made of EPDM and has a thickness of 3III11.
It is.

The pickup (
The results of measuring the detected values of 58) are shown in the graphs of Figures 8a to 8h and 9a to 9b.

Note that the measurement results for the comparative example are shown in the graphs of FIGS. 1Qa to 1011.

As is clear from the graphs in Figures 10a to 10h, in the comparative example, even if the initial pressure (F) was increased, resonance occurred at one of the frequencies simply by changing the resonance frequency to jjlj. That is, it can be seen that although the conventional mechanism can block the transmission of vibration to some extent, it has no effect on the resonance phenomenon of abnormal vibration at a specific frequency.

Next, as shown in the graphs in Figures 8a to 8h, in the mechanism of Example 1, when the initial pressing force was 58 kgr, that is, in the case of Figure 8e, resonance development was almost suppressed for all frequencies. I know that there is.

Also, as shown in the graphs of FIGS. 9a-9b, Example 2
In this mechanism, resonance can be best prevented when the initial pressing force is set to 17.4)cgl', that is, in the case shown in FIG. 911.

The results obtained by the tests on the ridges also indicate a method for determining conditions such as the damping coefficient, that is, the initial pressing force, of the damping means that can provide the most resonance prevention effect when designing the mechanism of the present invention.

In other words, depending on the type of control cable, the frequency distribution range of the engine that is the vibration source, etc., the type of pressure medium enclosed and the initial pressing force, or in the case of Figures 1 and 2, the biasing force of the conical coil spring, etc. It is sufficient to determine the parameters of

〔Effect of the invention〕

When using the resonance prevention mechanism of the present invention, it is possible to almost eliminate the resonance phenomenon of a linear member to which vibration is applied to one end or the like. For example, by using the ntM of the present invention in a control cable for operating a clutch in an automobile, indoor noise can be significantly reduced.

Brief Description of the 4 Drawings Figures 1 to 3 are longitudinal cross-sectional views showing embodiments of the mechanism of the present invention, and Figures 4 and 5 are views of an apparatus for measuring the damping effect of the mechanism of the present invention, respectively. A plan view and a front view, and FIGS. 6 and 7 are longitudinal sectional views of the mechanism used to measure the damping effect of the mechanism of the present invention, and FIGS. 8a to 811, respectively.
Figures 9a to 9h and 10a to 10h are graphs showing measurement results by the apparatus shown in Figures 6 to 7, respectively. Figure 11 is a partially sectional side view showing a conventional mechanism.

(Main symbols in the drawing) (1): Conduit (2): Inner cable (3): Stationary member (6): Fixed member (9): Annular groove 00): Case body 12 elastic ring ■: Nispring case Biconical coil spring (31): Semi-fluid (4t): Ball joint (43): Ball (45): Case (4B): Socket member (49): Rubber body Patent applicant: 0 Cable System Co., Ltd. ,′
('Representative Patent Attorney Asahi Na Sota Haka 1 name 2 figures 3 figures 49: Gomu Taorokusha Fa 8a insai 80 figure input frequency (Hz) A'8t) figure 8 d figure input Frequency (Hz) IAE 8G Figure Input Frequency (Hz) 781 Figure 8H Figure Human Power Frequency (Hz) Age 9A Figure Age 90 Figure Input Frequency (Hz) Age 9B Figure Age 9D Figure Human Power Frequency (Hz) Age 9E Figure Age Figure 9g Input frequency (Hz) Age 9 ↑ Figure 29h Figure input 1. 'd wave number (Hz) 10a human power frequency (HzJ) Input frequency (Hz) 10b 10d oral input frequency (Hz) 10e 10g input frequency (Hz) 7101 10h input frequency (Hz)

Claims (1)

[Claims] 1 (a) A part of the linear member is fixed so as not to move in the axial direction and in two directions perpendicular to the axial direction, and around two axes perpendicular to the axial direction. a support member for rotatably supporting; (b) restricting rotation of the linear member about the two axes;
A resonance prevention mechanism for a linear member comprising a damping means for damping. 2. Claim 1, wherein the supporting member is a case made of an elastic material having an annular cavity surrounding a linear member, and the damping means is a pressure medium sealed in a pressurized state within the cavity of the case. Mechanism described in section. 3. The mechanism according to claim 2, wherein a rigid ring is fitted around the outer periphery of the case for restraining expansion of the case in the radial direction. 4. Claim 3, wherein a rigid flange for fixing to a stationary member is fixed to one end face of the case, and the other end face is pressed by a spring so as to pressurize the inside of the cavity. mechanism. 5. The supporting member includes a bottomed cylindrical case made of a rigid material arranged so as to surround the linear member, and a pressure medium that is inserted into the opening side of the case and constitutes a damping means in the cavity. A socket member made of a rigid material that is fitted so as to be sealed in a pressurized state, and a ball that is rotatably fitted into a spherical recess of the socket member and has a fixing portion for fixing the linear member. 2. A mechanism according to claim 1, comprising a member.