JP2006132741A - Mesh spring type elastic joint - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a mesh spring type elastic joint capable of reducing vibration torque, and increasing transmission torque. <P>SOLUTION: A mesh spring 31 transmits rotational torque from a rotating member 1 to an outer case 2. By providing the mesh spring 31 with a nonlinear load characteristic wherein a spring constant is small when a load is small, and the spring constant becomes larger when the load is large, since the spring constant is small when the load is small, the vibration torque can be reduced. By providing the mesh spring 31 with the nonlinear load characteristic, since the spring constant becomes large when the load is large, the transmission torque can be increased. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a mesh spring type elastic joint used for, for example, an onshore plant, an offshore plant, a marine main engine, a marine auxiliary engine, and the like.

  Elastic joints are used to transmit the output of rotating shafts in land plants, marine main engines and auxiliary machinery plants. For example, in a ship, the rotational torque generated by the output shaft of the main engine is transmitted to the input shaft of the speed reducer via an elastic joint. The elastic joint reduces torsional vibration of the input shaft of the speed reducer.

  Conventionally, as an elastic joint, there is a coil sling type disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 6-213247). This coil spring type elastic joint transmits the rotational torque of the first hub to the second hub via a coil spring arranged in the circumferential direction.

  However, in the conventional coil spring type elastic joint, when the spring constant of the coil spring is reduced, the vibration torque (fluctuation torque) can be reduced, but the transmission torque is also reduced. Therefore, if the spring constant of the coil spring is increased in order to increase the transmission torque, the vibration torque increases.

  Therefore, the conventional coil spring type elastic joint can realize only one of reducing the vibration torque and increasing the transmission torque. That is, the conventional coil spring type elastic joint has a problem that vibration torque can be reduced and transmission torque cannot be increased.

Moreover, in the conventional coil spring type elastic joint, since the coil spring itself does not have a damping effect, a secondary damping effect is provided by silicon oil or the like. As a result, a seal structure is required and silicon oil or the like can be replaced. It must be implemented in the future.
JP-A-6-213247

  Therefore, an object of the present invention is to provide a mesh spring type elastic joint capable of reducing vibration torque and increasing transmission torque.

  In order to solve the above problems, a mesh spring type elastic joint according to the present invention includes a first member, a second member, and a mesh spring that transmits torque from the first member to the second member. It is characterized by that.

  Here, the mesh spring refers to a product obtained by knitting a metal wire such as a piano wire or a stainless steel wire, and then corrugating and further molding.

  According to the mesh spring type elastic joint having the above-described configuration, the mesh spring has a non-linear load characteristic in which the spring constant is small at a low load, while the spring constant is small at a low load. Therefore, vibration torque can be reduced.

  In addition, since the mesh spring has the non-linear load characteristic, the spring constant increases at high loads, so that the transmission torque can be increased.

  Therefore, the mesh spring type elastic joint can reduce vibration torque and increase transmission torque.

  Further, since the mesh spring has hysteresis, the effect of reducing the amplitude is great.

  In the mesh spring type elastic joint of the present invention, the mesh spring having non-linear load characteristics transmits the torque of the first member to the second member, so that the spring constant at the time of low load of the mesh spring is small. The torque can be reduced, and the transmission torque can be increased because the spring constant of the mesh spring at high load is large. Therefore, the mesh spring type elastic joint can reduce vibration torque and increase transmission torque.

  Further, since the mesh spring has hysteresis, the effect of reducing the amplitude is great.

  Hereinafter, the mesh spring type elastic joint of the present invention will be described in detail with reference to the illustrated embodiments.

  FIG. 1 shows a schematic front view of a mesh spring type elastic joint according to an embodiment of the present invention. FIG. 2 shows a schematic cross-sectional view taken along line II-II in FIG. FIG. 1 shows a state in which a part of the rotating member 1, the transmission device 3, and the second flange 13 is removed.

  As shown in FIGS. 1 and 2, the mesh spring type elastic joint is disposed in the circumferential direction of the annular rotating member 1, the outer case 2, the rotating member 1 and the outer case 2, and the rotating member 1 extends to the outer case. 2 and a transmission device 3 for transmitting rotational torque to 2. The rotating member 1 surrounds the end of the output shaft 11, and the outer case 2 surrounds the rotating member 1. That is, the rotating member 1 is disposed on the radially outer side of the end portion of the output shaft 11, and the outer case 2 is disposed on the radially outer side of the rotating member 1. The inner peripheral edge of the outer case 2 is in the rotating member 1. The rotating member 1 and the transmission device 3 are sandwiched between the first flange 12 and the second flange 13. The first flange 12 is fixed to the peripheral surface of the end portion of the output shaft 11, while the second flange 13 is fixed to the end surface of the output shaft 11 in the axial direction with bolts 51.

  Since the rotating member 1 is connected to the first and second flanges 12 and 13 by bolts 52, the rotating member 1 rotates integrally with the output shaft 11. Further, as shown in FIG. 3, screw holes 1b into which the bolts 52 are screwed are provided in the inner peripheral edge portion of the rotating member 1 at a phase interval of 45 degrees. On the other hand, the outer peripheral edge of the rotating member 1 is provided with notches 1a for accommodating the transmission device 3 at a phase interval of 45 degrees. Further, the outer peripheral edge of the rotating member 1 is divided into two as shown in FIG. The inner peripheral edge of the outer case 2 is located between the two outer peripheral edges.

  The outer case 2 is fastened to a driven side portion (not shown) with a bolt 53. And as shown in FIG. 4, the notch 2a which accommodates the transmission apparatus 3 is provided in the inner peripheral edge part of the said outer side case 2 with the phase space | interval of 45 degree | times. On the other hand, the outer peripheral edge of the outer case 2 is a flange.

  As shown in FIG. 5, the transmission device 3 includes a cylindrical mesh spring 31 and a spring seat 32 connected to the mesh spring 31. The spring seat 32 includes a semi-spherical contact portion 32 a and a columnar fitting portion 32 b that fits the mesh spring 31. The contact portion 32 a is in close contact with the side surface of the notch 1 a of the rotating member 1 and in close contact with the side surface of the notch 2 a of the outer case 2. In addition, as shown in FIG. 1, the transmission device 3 accommodates the notches 1a and 2a with the phase of the notch 1a and the phase of the notch 2a. The number of the transmission devices 3 is the same as the number of the notches 1a and 2a, but only one is shown in FIG.

  The mesh spring 31 is formed as follows.

  First, a wire net 101 is formed by knitting a SUS304 wire with a knitting machine (not shown) as shown in FIG. Next, the corrugated nets 104 shown in FIG. 6C are formed by corrugating the nets 101 with the rollers 102 and 103 with molds shown in FIG. 6B. When the corrugated net 104 is compression-molded, a mesh spring 31 shown in FIG. 6D is obtained.

  Since the mesh spring 31 formed as described above has nonlinear characteristics as shown in FIG. 7, the slope of the tangential spring constant is small and the torsion spring constant is small at low loads, while the tangential spring is at high loads. The slope of the constant is large and the torsion spring constant is large. Since the rotational torque of the rotating member 1 is transmitted to the outer case 2 through such a mesh spring 31, the mesh spring type elastic joint can have the characteristics shown in FIGS.

  FIG. 8 shows the relationship between the vibration torque and the rotational speed. The solid line in FIG. 8 shows the above relationship when the output shaft of the 4-cycle, 6-cylinder engine and the driven side are connected by a mesh spring type elastic joint. Also, the alternate long and short dash line in FIG. 8 shows the above relationship when the output shaft of the four-cycle, six-cylinder engine and the driven side are connected by a coil spring type elastic joint.

  A linear spring such as a coil spring used for the coil spring type elastic joint has a spring constant corresponding to a rated torque. The spring constant of the coil spring does not change even when the load is low or high.

  On the other hand, a non-linear spring such as a mesh spring used for the mesh spring type elastic joint also determines a spring constant corresponding to the rated torque, like the coil spring, but the spring constant is a non-linear characteristic at low load. This reduces the tangential spring constant.

Therefore, for example, at the time of idle 350 min ⁻¹ , the resonance point of the elastic joint using the nonlinear spring is lower than the resonance point of the elastic joint using the linear spring. As a result, the vibration torque during idling of the elastic joint is reduced.

  That is, as shown in FIG. 8, the resonance point of the mesh spring elastic joint is lower than the resonance point of the conventional coil spring elastic joint. Thereby, in the mesh spring type elastic joint, the vibration torque in the idle rotation region is also lower than that of the conventional coil spring type elastic joint. Specifically, the vibration torque in the idle rotation region of the mesh spring elastic joint is approximately ½ of the vibration torque in the idle rotation region of the conventional coil spring elastic joint.

  As described above, the mesh spring type elastic joint has a small inclination of the tangential spring constant and a small torsion spring constant at a low load, so that the idle rotation speed can be set low.

  Further, the mesh spring type elastic joint has a large inclination of the tangential spring constant and a large torsion spring constant at the time of high load, so that it can cope with high torque. That is, the mesh spring elastic joint can increase the transmission torque.

  The mesh spring 31 has a load capacity larger than that of the coil spring. Therefore, the mesh spring elastic joint can be made smaller and lighter than the coil spring elastic joint.

  Further, since the mesh spring 31 is formed by compression-molding a SUS304 wire, creep hardly occurs even when used for a long period of time, and is excellent in heat resistance and oil resistance. Therefore, the mesh spring 31 can be used semi-permanently, and the replacement interval of the mesh spring 31 can be long, so that the maintenance cost can be reduced.

  Further, since the frictional heat between the wires constituting the mesh spring 31 diverges on the surface of the wire, the mesh spring 31 does not accumulate heat.

  Further, it is not necessary to lubricate the mesh spring 31. Therefore, the mesh spring type elastic joint can reduce the running cost as compared with the coil spring type elastic joint that requires silicone oil.

  Moreover, since the mesh spring 31 has hysteresis, the effect of reducing the amplitude is great.

  Further, the mesh spring type elastic joint can be a damper that can reduce torsional vibration when attached to the tip of the crankshaft.

  In the above embodiment, the transmission device 3 is configured by the mesh spring 31 and the spring seat 32. However, the transmission device may be configured by only the mesh spring 31. That is, the mesh spring 31 may be in direct contact with the side surfaces of the notches 1a and 2a.

  In the above embodiment, the mesh spring 31 is arranged so as to have an axis substantially parallel to the circumferential direction of the output shaft 11. However, the mesh spring 31 has an axis substantially parallel to the axis of the output shaft 11. 31 may be arranged.

  The present invention can be applied to various elastic joints.

FIG. 1 is a schematic front view of a mesh spring type elastic joint according to an embodiment of the present invention. FIG. 2 is a schematic sectional view taken along line II-II in FIG. FIG. 3 is a schematic front view of the rotating member of the mesh spring type elastic joint. FIG. 4 is a schematic front view of the outer case of the mesh spring elastic joint. FIG. 5 is a schematic cross-sectional view for explaining the transmission device of the mesh spring type elastic joint. 6A to 6D are manufacturing process diagrams of the mesh spring of the transmission device. FIG. 7 is a graph showing the relationship between the load received by the mesh spring and the deflection generated by the mesh spring. FIG. 8 is a graph showing the relationship between vibration torque and rotational speed.

Explanation of symbols

1 Rotating member 2 Outer case 31 Mesh spring

Claims (1)

A first member;
A second member;
A mesh spring type elastic joint, comprising: a mesh spring that transmits torque from the first member to the second member.

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