KR20000010647A - Device for eliminating twist and plural translation vibration - Google Patents

Abstract

PURPOSE: An device is provided to eliminate the twist vibration and the plural translation vibrations effectively. CONSTITUTION: A twist vibration and a translation vibration eliminating device(34) is formed by:a ring shaped twist vibration damping weight body(42) located in a ring shaped groove in a housing for being freely rotated during a rotation of the balancing device(34); and a translation vibration compensating weight body(50) stored in the ring shaped groove in the ring shaped twist vibration damping weight body for being freely rotated for reducing the twist vibration.

Description

Torsional and translational vibration eliminator

Rotating systems, such as the axis of rotation, are often torsional and translational. Generally, torsional vibration is referred to as vibration which vibrates the rotating body (e.g., rotational axis) about its central longitudinal axis. On the other hand, translational vibrations are referred to as vibrations that move the rotor in a direction perpendicular to its central longitudinal axis.

In various other systems such as automotive engines, jet skis, etc., torsional vibrations and translational vibrations are generated. In the case of an engine, for example, torsional vibrations and translational vibrations can move the sliding masses that make up the various parts of the engine. The mass includes a piston, a connecting rod, a crank draw and the like. In addition to the movement of the sliding rotating mass, the combustion process of the cylinder when the engine is operated can contribute to the generation of torsional vibrations and translational vibrations.

In the past, proposals have been made to use dished viscous torsional vibration devices to reduce torsional vibrations. 1 shows a viscous torsional vibration device distracted with respect to a pulley. The pulley 30 is provided with a cylindrical cavity that is rotationally driven by the shaft 31 and contains the disk-damping mass 32. The space between the inner wall of the cavity in the pulley 30 and the outer surface of the damping mass 32 defines a shear gap, which typically is defined within the pulley 30 relative to the interior of the damping mass 32. Filled with the appropriate viscous fluid selected to maximize torsional damping for the ratio. The amount of shear damping that occurs in the shear gap between the pulley 30 and the damping mass 32 depends on the size of the space, the viscosity of the fluid, and the relative rotational speed between the pulley and the damping mass.

The raw viscous damping described above can offset some torsional vibrations, but has various drawbacks and drawbacks. In one aspect, the disturbed viscous damping is not designed to address translational vibrations resulting from the movement of the rotational axis in a direction perpendicular to the central longitudinal axis of the axis. As a result, they exist outside the equilibrium state of the system, which can be adversely affected by the operation, performance and life of the system.

It is necessary to have a device that eliminates both translational and torsional vibrations, but it is relatively compact and complex in design so that the device can be used in combination with existing machine and system.

The present invention relates generally to a balancer and a vibration damper. In particular, the present invention relates to a torsional and translational vibration removing device designed to be effective in eliminating torsional and translational vibrations.

1 is a cross-sectional view of a pulley equipped with a dished viscous damper.

2 is a cross-sectional view of a torsional and translational vibration removing device according to a first embodiment of the present invention depicted mounted on magneto.

3 is a cross-sectional view of the torsional and translational vibration removing device shown in FIG. 2 taken along line 3-3 in FIG.

4 is an exploded view of a magneto-crankshaft assembly equipped with a front balancer in accordance with the present invention.

5 is an exploded view of a crankshaft assembly equipped with a rear balancer in accordance with the present invention.

6 is a perspective view of a two-cylinder engine equipped with front and rear balancers in accordance with the present invention.

7 is a cross-sectional view showing a portion of a torsional and translational vibration removing device according to another embodiment of the present invention.

8 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with a further embodiment of the present invention.

9 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with a further embodiment of the present invention.

10 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with a further embodiment of the present invention.

11 is a cross-sectional view showing a portion of a torsional and translational vibration removing device according to another embodiment of the present invention.

12 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with a further embodiment of the present invention.

13 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with a further embodiment of the present invention.

14 is a cross-sectional view showing a portion of a torsional and translational vibration removing device according to another embodiment of the present invention.

15 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with another embodiment of the present invention.

16 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with another embodiment of the present invention.

17 is a cross-sectional view showing a portion of a torsional and translational vibration removing device according to another embodiment of the present invention.

18 is a cross-sectional view of a portion of a torsional and translational vibration removing device in accordance with another embodiment of the present invention.

The present invention provides a combined torsional and translational vibration removing device specially adopted to eliminate both translational and torsional vibrations of a rotating element such as an axis. The balancer according to the invention can be achieved by a relatively compact and complex design. Therefore, there is a system to be equipped with the present invention in an effective way to eliminate torsional and translational vibrations. The balancer according to the invention can be shaped as a device to be installed on a rotating element. Optionally, if space permits, the rotating element itself can be modified to embody the features of the invention described in more detail below.

According to one aspect of the invention, the torsional and translational vibration removing device is a torsional and translational vibration removing device comprising: a housing provided with at least one open annular groove, an outer sealed annular hollow inside and one side to close the housing; And means for installing a cover fixed to the housing and the housing on the rotating element. The annular torsional vibration damping mass is located inside the hollow and has an outer peripheral surface which is smaller than the inner wall surface engaging with the hollow interior, so that the shear gap is between the outer peripheral surface of the torsional vibration damping mass and the inner wall surface engaging with the hollow interior. Is present. The torsional vibration damping mass is provided with at least one annular groove, and the viscous liquid is disposed inside the hollow. The plurality of torsional vibration compensating masses are located in the annular groove of the torsional vibration damping mass. While the torsional and translational vibration removing device is rotated so that the translational vibration compensating mass can move freely in the annular groove of the torsional vibration damping mass, the translational vibration compensating mass is used to indicate the position where the translational vibration of the rotating element is reduced. The torsional vibration damping mass is moved in the annular groove and rotated inside the hollow to reduce the torsional vibration.

According to another aspect of the present invention, a torsional and translational vibration removing device includes a body having a hollow interior, an annular torsional vibration damping mass located inside the hollow and provided with at least one annular groove, and a viscous liquid inside the hollow of the body. And a plurality of translational vibration compensating masses disposed in the annular groove of the torsional vibration damping mass and arranged in an annular single row. Since the plurality of translational vibration compensating masses are freely movable in the annular groove of the torsional vibration damping mass, the rotation of the body to take a piston that reduces the translational vibration while the torsional vibration damping mass rotates inside the hollow to reduce the torsional vibration. While the translational vibration compensating mass moves into the annular groove of the torsional vibration damping mass.

According to another embodiment of the present invention, a torsional and translational vibration removing device includes a body having first and second hollow spaces separated from each other by a wall portion, and an annular torsional vibration damping mass located in the first hollow space. And a plurality of translational vibration compensating masses located in the second hollow space. The first hollow space is larger than the torsional vibration damping mass such that the shear gap is present between the outer circumference of the torsional vibration damping mass and the inner wall surface of the body restricting the first hollow space. The viscous liquid is disposed in the first hollow space to be located in the shear space. The translational vibration compensating masses located in the second hollow space are well arranged in a single row of annulus. Since the plurality of translational vibration compensating masses are freely movable in the second hollow space, the body is adapted to take a piston that reduces the translational vibration while the annular torsional vibration damping mass rotates in the first hollow space to reduce the torsional vibration. During the rotation of the translational vibration compensation mass moves into the second hollow space.

The present invention provides a rotary or vacuum removal device that compensates for both torsional vibrations as well as translational vibrations of rotating elements such as shafts. Generally speaking, the rotary or vibration removing device comprises at least one torsional vibration damping mass and a plurality of translational compensation masses. Torsional vibration damping masses are preferably in the form of cylindrical, donut or annular disks that compensate or eliminate torsional vibration that may be due to various sources, such as the sticking of the piston of an internal combustion engine. Torsional vibration damping masses can be made from a variety of materials that provide a desired weight of metal (eg, steel, stainless steel, tungsten carbide, etc.) and a ceramic material such as silicon nitride. The translational vibration compensating mass may be a ball, cylindrical mass or disc type that compensates for or eliminates translational vibration resulting from, for example, mass imbalance, hydraulic imbalance or aerodynamic imbalance caused by, for example, a propeller uneven pitch. Weight forms are preferred. The compensation mass also provides a desired amount of weight, for example metals (ie, steel, stainless steel, tungsten carbide, etc.) and ceramic materials such as silicon nitride. Various rotating devices for implementing the above characteristics according to the invention are described in detail below.

In Fig. 2, one embodiment of a rotating device or torsional and translational vibration removing device 34 according to the present invention consists of a disc-shaped body 36 adapted to be mounted on a rotating element such as a shaft. The disc-shaped body 36 includes a housing 38 provided with a continuous annular groove extending from the outer circumference of the housing. One side of the annular groove is open to the outside and the lid 40 is fixed to the housing 38 to close the open side of the annular groove, thereby defining an annular hollow interior in the body 36 sealed from the outside.

The annular torsional vibration damping mass 42 is located inside the hollow of the body 36. The torsional vibration damping mass 42 is smaller than the inner wall surface surrounding the hollow interior of the body 36 such that the shear gap 42 is present between the torsional vibration damping mass 42 and the inner wall surface surrounding the hollow interior of the body. It has an outer circumferential surface. These shear gaps 44 are shown more clearly in the cross-sectional view of FIG. 3. The torsional vibration damping mass 42 can rotate freely in the housing 38 without significantly moving in the radial direction.

Torsional vibration damping mass 42 is a one-piece type element. As shown in FIG. 2, the torsional vibration damping mass 42 is formed with a continuous annular groove 46. The annular groove 46 is formed on the side of the torsional vibration damping mass 42 radially inwards towards the longitudinal axis of rotation 48 of the balancer.

The plurality of translational vibration compensating masses 50 are disposed in the annular groove 46 in the damping mass 42. In the embodiment shown in Fig. 2, it can be seen that the translational vibration compensation mass can take other shapes, for example cylindrical or disc shaped weights, but the translational vibration compensation mass 50 is a spherical ball. Shape.

As shown in FIG. 3, the translational vibration compensating mass 50 is arranged in a single annular row. The translational vibration compensating mass 50 can move freely in the annular groove 46 formed in the torsional vibration damping mass 42. Each translational vibration compensating mass 50 in the annular groove 46 preferably has the same or nearly the same weight and dimensions. Compensation mass 50 that performs translational vibration compensation may be used in other shapes, for example cylindrical or disc shaped masses, although spherical shapes are preferred.

The inner surface of the torsional vibration damping mass 42 surrounding the annular groove 46 is preferably cured to minimize the rolling resistance of the translational vibration compensating mass 50. The shear gap 44 formed between all annular grooves 46 and the torsional vibration damping mass 42 and the inner wall surface surrounding the hollow interior of the body 36 is preferably filled with a viscous fluid. The viscous fluid provides lubrication and damping for the translational vibration compensating mass 50 and also provides viscous damping to the shear gap 14.

As shown in FIG. 3, the central portion of the body 36 is provided with a central through hole 52 for mounting the rotating device on a rotating element such as a shaft. Several additional through holes 54 are located radially outward of the central through hole 52. These through holes 54 hold the rotating device in place on the rotating element.

The torsional and translational vibration removing device according to the present invention is used in almost any position where the rotating element is subjected to not only torsional vibration but also translational vibration. One that the invention has been found to be particularly useful is that shown in FIG. 4 where a magneto-crank shaft assembly is shown. In particular, the detailed description of the magneto-crankshaft assembly is not particularly relevant to this specification and thus detailed descriptions of the various features of the assembly are omitted. Generally speaking, the magneto-crankshaft assembly includes a crankshaft 56, a magneto disc or flywheel 58, a magneto stator 63 and two casing parts 60, 61. The casing component 60 is adapted to be mounted on the engine block and is provided with a through hole extending the front end of the crankshaft 56. The magneto stator 63 is mounted over the casing component 60 and provided with a through hole extending the front end of the crankshaft 56. A magneto disc or magneto flywheel 58 is operably mounted on the front protruding end of the crankshaft 56 and extends over the magneto stator 63. The magneto casing part 61 is fastened to another magneto casing part 60 to cover the magneto assembly.

As shown in Fig. 4, the torsional and translational vibration removing device 34 of the present invention is mounted on a magnetic disk (fly wheel) 58. The vibration removing device 34 is arranged on the magnetic disk 58 by aligning the through hole 54 on the center of the body 36 with a corresponding hole on the magnet generator and by using the screw 62 shown in FIG. Is placed on. In the device shown in FIG. 4 the torsional and translational vibration removing device 34 acts as a front balancer for the self-crankshaft assembly.

5 shows another example of use of a balancing device according to the invention. In FIG. 5, the crankshaft assembly 56 has a torsional and translational vibration removing device 34 that acts as a rear balancer. In this arrangement the centrally arranged through hole 52 in the center of the body 36 can be screwed to screw the threaded portion 64 onto the end of the crankshaft assembly.

6 shows another example of use of the torsional and translational vibration removing device of the present invention. Figure 6 shows a two-cylinder engine 66 with a pair of torsional and translational vibration removal devices 34 ', 34 ". The torsional and translational vibration removal device 34' is front connected to the magneto-generator. It acts as a balancer and the torsional and translational vibration removing device 34 "acts as a rear balancer mounted on the crankshaft.

In operation, the torsional and translational vibration removing device of the present invention is rotated through the rotation of a rotating element (for example a magnetogenerator or shaft). As the torsional and translational vibration removing device rotates, the translational vibration compensating mass 50 freely moves in the annular groove 46 in the torsional vibration damping mass 42 to occupy a position to reduce or almost eliminate the translational vibration. Done. At the same time, the annular torsional vibration damping mass is freely rotated within the hollow interior of the body 36 to reduce or almost eliminate torsional vibration.

The present invention therefore provides a mechanism for reducing or nearly eliminating torsional and translational vibrations. In addition, the structure of the balancer is simple and not complicated in size. This means that the balancer is well adapted to existing equipment supply systems and machinery where space is limited. In addition, the performance of the balancer to reduce not only the translational vibration but also the torsional vibration means that the torsional vibration has less influence on the behavior of the translational vibration compensation mass 50 as compared with the case where the torsional vibration damping mass is not provided. In the arrangement of the invention described above, the torsional vibration damping mass 42 exhibits a lower level of torsional vibration compared to the body 36 operatively mounted on the rotating element. Since the annular groove or race 46 containing the translational vibration compensating mass 50 is assembled into the torsional vibration damping mass 42, the effect of torsional vibration on the performance of the translational vibration compensating mass 50 is significantly reduced.

Another embodiment of the invention is shown in FIG. This embodiment of the torsional and translational vibration removing device 70 includes a body 72, a torsional vibration damping mass 74, and a plurality of translational vibration compensation masses 76. It is understood that the content shown in FIG. 7 shows only a portion of the balancer and that the balancer has a shape that is generally similar to that shown in FIG. 2.

The body 72 includes a housing 78 and a cover 80 fixed to one side of the housing. The housing 78 has an annular groove opening toward the one side of the housing, which extends along the annular circumference of the housing. The cover 80 is secured to the housing 78 in a manner that closes the open side of the housing to form an annular hollow interior that is sealed from the outside in the body 72. The open side of the housing 78 allows the torsional vibration damping mass 74 and the translational vibration compensating mass 76 to be disposed in the annular groove of the housing 78. When the torsional vibration damping mass 74 and the translational vibration compensating mass 76 are disposed in the annular groove of the housing 78, the cover 80 is fixed to the housing 78.

The torsional vibration damping mass 74 has an outer dimension thereof smaller than that of an inner wall surface bounding the hollow interior in the body 72 so that the outer surface of the torsional vibration damping mass 74 and the body 72 A shear gap 82 is formed between the inner wall surfaces that border the hollow interior. The annular torsional vibration damping mass 74 has two spaced apart annular grooves 84 separated from each other by a wall portion 86 located at the center of the torsional vibration damping mass 74. The two annular grooves 84 are located on opposite sides of the center plane 88 of the balancer and are equally spaced from the center plane 88 of the housing 72. Viscous fluid is provided in the hollow interior of the body 72 to fill the annular groove 84 as well as the shear gap 82.

Inside each of the annular grooves 84 is provided an annular row of translational vibration compensating masses 76. Although FIG. 7 shows only a single translational vibration compensation mass 76 of each of the grooves 84, the grooves 84 are each arranged in a manner similar to that shown in FIG. 3. Each includes a single annular row. Preferably, all of the translational vibration compensating masses 76 in one of the grooves are the same or nearly the same in weight and size, and all the translational vibration compensation masses in the other annular grooves are the same or almost the same in weight and size. . Further, the mass in one of the annular grooves 84 is the same or nearly the same as the mass in the other annular groove 84.

Another embodiment of the present invention is a diagram showing an equalizer 90 comprising a body 92, an annular torsional vibration damping mass 94 and three sets of translational vibration compensating masses 96, 98, 100. 8 is described. The body 92 is composed of a housing 102 having an annular groove. The annular groove of the housing 102 is open at one end to allow the torsional vibration damping mass 94 and the translational vibration damping mass 96, 98, 100 to be located in the housing 102. The annular groove is increased in the radial direction from one end (ie the closed end) toward the opposite end (ie the open end). The cover 104 is secured to the housing 102 to close the open end of the annular groove, thereby forming an annular hollow interior within the body 102.

As described above in connection with another embodiment, the damping mass 94 provides a shear gap 99 between the outer periphery of the damping mass 94 and the inner wall surface that borders the hollow interior of the body 2. It becomes size to say. The annular grooves 106, 108, 110 are spaced apart from each other in a direction parallel to the axis of rotation 97 of the balancer. The annular groove 106 is smaller in width and depth than the annular groove 108 located in the middle, and the annular groove 108 located in the middle is smaller in the width and depth of the annular groove 110.

The vibration compensation mass 96 of the translation is arranged in a single annular row similar to that shown in FIG. 3. Similarly, the translational vibration compensating masses 98, 100 are aligned in each annular groove in a single annular row similar to that shown in FIG. Each mass 96 in the smallest groove 106 has the same or nearly the same weight and size, and each of the masses 98 of the intermediately located annular groove 108 is the same in weight and size or Almost the same. In addition, the mass 96 is smaller in weight and size than the mass 98 in the annular groove 108 positioned in the middle, and the mass 98 is smaller than the mass 100 in the annular groove 110. Much smaller in size and weight. As shown in FIG. 8, the three annular grooves are separated from each other in a direction parallel to the longitudinal axis in which the balancer rotates.

As shown in FIG. 8, the viscous fluid may fill the annular grooves 106, 108, 110 as well as the shear gap 99 between the outer surface of the torsional vibration damping mass 94 and the inner wall surface that borders the hollow interior of the body 92. Fully charge

In the embodiment of the present invention shown in FIG. 9, the torsional and translational vibration removing device or balancer 112 includes a body 114, an annular torsional vibration damping mass 116, and four sets of translations. Kinetic vibration compensation masses 118, 120, 122, 124. The body 114 is composed of a housing 126 having an annular groove opening at one side of the housing 126, and a cover 128 closing the open side of the housing 126.

The torsional vibration damping mass 116 has four annular grooves 130, 132, 134 and 136. The annular grooves 130, 134, 136 open on one side of the torsional vibration damping mass 116 to insert masses 118, 122, 124. The cover 138 is secured to the annular torsional vibration damping mass 116 to close and seal the annular grooves 130, 134, 136. The annular groove 132 is opened to the opposite side of the torsional vibration damping mass 116 and is covered by the cover 140.

The compensation masses 118, 120, 122, 124 are arranged in their respective grooves 130, 132, 134, 136 as a single annular row of masses similar to that shown in FIG. As shown, each of the annular grooves 130, 132, 134, 136 has a different size. The width and depth of the annular groove 132 is greater than the width and depth of the annular groove 130, the width and depth of the annular groove 134 is greater than the width and depth of the annular groove 132, the radius Direction outermost groove 136 has a width and depth greater than the width and depth of radially intermediate annular groove 134.

Each of the compensating masses 118 of the annular groove 134 is preferably the same or almost the same as the same weight and size, and each mass 120 of the annular groove 132 is the same almost the same size and weight Is good, and each mass 122 of the annular groove 134 has the same or nearly the same size and weight, and each mass of the annular groove 136 preferably has the same or nearly the same size and weight. Do.

In addition, the size and weight of the compensating mass varies from one groove to the next groove. As shown in FIG. 9, the mass body 118 of the annular groove 130 is smaller in size and weight than the mass body 120 of the annular groove 132, and of the annular groove 134 intermediate in the radial direction. The weight 122 is preferably larger in size and weight than the weight 120, and the weight 124 in the radially outermost annular groove 136 is in the middle of the annular groove 134 in the radial direction. Larger in size and weight than mass 122 in. As in the description of all previous embodiments, the outer size of the torsional vibration damping mass 116 is smaller than the inner size of the hollow interior of the body 114, so that the shear gap 142 is the annular torsional vibration damping. It exists between the outer peripheral surface of the mass body 116, and the inner wall surface which borders the hollow inside of the said body 114.

The embodiment shown in FIG. 9 has the advantage that one form of viscous fluid is located in the shear gap 142 and that different viscous fluids are located in the annular grooves 130, 132, 134 and 136. In order to improve the reaction rate of the vibration compensating masses 118, 120, 122 and 124 of the translation, lightweight lubricating and damping liquids must be used. In this way, as the balancer begins to rotate, the masses 118, 120, 122, 124 begin to rotate faster. On the other hand, it is desirable to supply fluid in the shear gap 142 with greater viscosity, such as silicone oil with insufficient lubricating properties.

The embodiment of the balancer 144 shown in FIG. 10 includes a body 146, a pair of annular torsional vibration damping masses 148, and two sets of translational vibration compensation masses 150. The body 146 consists of a housing 152 having two spaced apart and separate annular grooves arranged opposite to the opposite side of the center plane 153 of the balancer. Each annular groove is opened along one side of the housing 152 and a cover 154 is provided on each side of the housing to close the opening side.

Each annular torsional vibration damping mass 148 has a respective annular groove 156 that opens radially inward toward the longitudinal axis of the balancer. Each of the torsional vibration damping masses 148 has an outer circumferential surface that is smaller in size than an inner wall surface that borders the respective hollow inner chambers, so that each of the torsional vibration damping masses bounds the hollow inner chamber It exists between the inner wall surfaces.

Mass 150 disposed in each annular groove 156 of each torsional vibration damping mass 148 is disposed in a single annular column similar to that shown in FIG. Compensation masses in one of the annular grooves 156 are the same or nearly the same size and weight with respect to each other, and the weight of the other annular grooves 156 is the same or almost the same in size and weight. Also, as shown in FIG. 10, the mass of one of the annular grooves 156 is the same or nearly the same size and weight relative to the mass of the other annular groove 156.

FIG. 11 shows an embodiment of a balancer 160 that includes a body 162, three annular torsional vibration damping masses 164, 166, 168, and three sets of translational vibration compensating masses 170, 172, 174. The body 162 has a housing having torsional vibration damping masses 164, 166, 168 and three annular grooves opened along one side of the housing 176 to insert the vibration compensating masses 170, 172, 174 of the translational movement ( 176). The cover 1768 is secured to the open side of the housing 176 to close the annular groove, thereby forming three hollow interiors within the body 162. The annular grooves of the housing 176 are separated from each other by the wall portion 186.

The three torsional vibration damping masses consist of the radially innermost damping mass 164, the radially intermediate damping mass 166 and the radially outermost damping means 168. The radially innermost torsional vibration damping means 164 has an annular groove 180 which receives the vibration compensating means 170 of translational movement aligned in a single annular column similar to that shown in FIG. 3. Similarly, the radially intermediate torsional vibration damping mass 166 has an annular groove 182 disposed in the compensation mass 172, and the radially outermost damping mass 168 is a compensation mass ( An annular groove 184 for receiving 174. The compensation masses 172 and 174 are also aligned in a single annular row similar to that shown in FIG. 3. Each of the annular torsional vibration damping masses 164, 166, 168 fills each shear gap 175 between an outer surface of each of the damping masses 164, 166, 168 and an inner wall surface that defines a respective hollow interior of the body 162. It becomes the dimension to form.

All compensating masses 170 in the annular groove 180 have the same or almost the same size and weight, and all the compensating masses 172 of the annular groove 182 are the same or almost the same in size and weight, All compensating masses 174 in the annular groove 184 have the same or nearly the same size and weight. The compensation mass 170 located in the annular groove 180 of the radially innermost damping mass 164 is less than the compensation mass 172 of the annular groove 182 of the radially damping mass 166. Smaller in size and weight. Similarly, the compensation mass 172 in the annular groove 182 of the radial intermediate damping means 166 is the compensation mass 174 in the annular groove 184 of the radially outermost damping means 168. It is smaller in size and weight than).

The embodiment of the balancer 190 shown in FIG. 12 comprises a body 192, three annular torsional vibration damping masses 194, 196, 198 and three sets of translational vibration compensating means 200, 202, 204. Similar to the embodiment shown in FIG. The body 192 is formed by a housing 206 having three annular grooves for receiving one of the annular damping masses 194, 196, 198. The grooves of the housing 206 containing the damping masses 196 and 198 are open on one side of the housing, and the grooves of the housing 206 containing the damping mass 194 open opposite to the housing 206. The housing 206 has a cover 208 for holding the damping masses 194, 196, 198 in each of the hollow interior of the housing 206.

As shown in FIG. 12, the annular damping mass 194 is smaller in size than the annular damping mass 196, and the annular damping mass 196 is smaller in size than the annular damping mass 198. As in other embodiments, the damping masses 194, 196, 198 are each shear gaps 205 between the outer periphery of the respective damping masses 194, 196, 198 and the respective inner wall surfaces of the hollow interior in which the damping masses 194, 196, 198 are accommodated. It will be size to form.

As shown in FIG. 12, the two smaller damping masses 194, 196 are spaced apart from each other in the axial direction, and the largest damping mass 198 is the radial outward direction of the two smaller damping masses 194, 196. Spaced apart. Further, each of the damping masses 194, 196, 198 has respective annular grooves 210, 212, 214 which receive respective sets of compensating masses 200, 202, 204. The width and depth of the annular groove 210 of the annular body 214 is smaller than the width and depth of the annular groove 212 of the damping body 196, the annular groove 214 of the damping mass 198 is It has a width and depth greater than the width and depth of the annular groove 212 of the damping mass 196.

The compensation masses 200 are arranged in a single annular row in a manner similar to that shown in FIG. 3. Similarly, the compensation masses 202 and compensation masses 204 are arranged in a single respective annular row. Each of the compensating masses 200 in the smallest annular groove 210 is the same or nearly the same size and weight, and each of the compensating masses 202 in the medium annular groove 212 is of size and size. The weight is the same or about the same, and the compensation mass 204 in the largest annular groove 214 is the same or almost the same in size and weight. Further, the compensation mass 200 in the annular groove 210 of the annular damping mass 194 is smaller in size and weight than the compensation mass 202 in the annular groove 212 of the annular damping means 196. Further, the compensation mass 202 in the annular groove 212 of the damping mass 196 is smaller in size and weight than the compensation mass 204 of the annular groove 214 of the damping mass 198.

FIG. 13 shows a further embodiment of a balancer 220 comprising a body 222, an annular torsional vibration damping means 224, and a set of translational vibration compensating masses 226. The body 222 comprises an annular groove open along one side of the housing 228 to allow insertion of the damping means 224 and a cover 230 covering the open side of the housing 228.

The torsional vibration damping means 224 has an annular groove 232 open to one side of the damping mass 224 to allow insertion of a plurality of compensating masses 226. The open side of the damping mass 224 is closed by a cover 234. The damping mass 224 is formed to provide a shear gap 236 between an outer circumferential surface of the damping mass 224 and an inner wall surface that borders a hollow interior containing the damping mass 224.

The annular groove 232 and the plurality of damping masses 226 disposed in the damping means 224 are aligned in a single annular row similar to that shown in FIG. 3. Further, each of the compensation masses 226 is the same or nearly identical in size and weight. 13 shows a through hole 238 that allows the balancer 220 to be attached to a rotatable element such as a crankshaft or a magnet generator.

In the embodiment of the present invention shown in FIG. 13, a form of viscous liquid is located in the shear gap 236 to effectively effect the fast response of the compensation mass 226 when the balancer 220 initially begins to rotate. And other various liquids are similar as described above with respect to the embodiment of FIG. 9 in that various liquids are located in the hollow interior 240 in the annular damping mass 224.

In the embodiment of FIG. 14, the embodiment of the present invention, shown in FIG. 14, has a needle bearing 242 in an annular torsional vibration damping mass 224 and an inner wall that borders the hollow interior of the housing 228. Similar to that shown in FIG. 13 except that it is located between one. The needle bearing 242 is fixed in position with a snap ring 244 along, for example, the inner shear gap 237. The embodiment of the balancer 220 shown in FIG. 14 requires that the radial position of the torsional damping mass 224 must be maintained with high precision, or that excess force and friction are applied to the housing 228 in the inner shear gap 237. ) And the annular damping mass 224.

Figure 15 shows another embodiment of the invention in which the torsional vibration damping mass and the vibration compensating mass of translational movement are located separately in a groove separate from the housing. As shown in FIG. 15, the balancer 250 comprises a body 252, three annular torsional vibration damping masses 254, 256, 258, and three sets of translational vibration compensating means 260, 262, 264. The body 252 consists of a housing 266 having six annular grooves, where three annular grooves open to one side of the housing 266, and the other three annular grooves face the housing 266. Open to the side. The cover 268 is fixed on the opposite side of the housing 266 to close the annular groove, and forms a plurality of hollow interiors in the body 252.

The damping masses 254, 256, 258 are located on one side of the center plane of the balancer 250, and the set of compensating masses 260, 262, 264 is located opposite the center plane of the balancer. Each set of compensating masses 260 is positioned opposite to one of the annular damping masses 254, 256, 258. The axial magnitude of the damping masses 254, 256, 258 is gradually reduced from the radially innermost damping mass 254 to the radially outermost damping means 258.

Each set of compensating masses 260, 262, 264 is arranged in a single, single row similar to that shown in FIG. As in the other embodiments described, all of the compensation masses 260 are the same or nearly the same size and weight, and all of the compensation masses 262 are the same or nearly the same size and weight. Further, the radially innermost compensation mass set 260 is smaller in size and weight than the radial middle set of compensation masses 262, and the size and weight of the radial middle set of compensation masses 262 is radial. It is smaller than the size and weight of the set of compensation masses 264 in the outermost direction.

The annular torsional vibration damping masses 254, 256, 258 are provided such that a shear gap 257 is provided between the outer circumferential surface of each damping mass 254, 256, 258 and the inner wall surface of each hollow interior in which the damping masses are received. It is composed. In addition, a viscous fluid is disposed inside each shear gap 257. Light lubricant and damping fluid are also provided inside each annular groove in which compensation masses 260, 262, 264 are disposed. The viscous fluid filled in the annular groove in which the compensation masses 260, 262, 264 are arranged is preferably different from the viscous fluid disposed in the shear gap 257 and preferably when the balancer rotates ( 260, 262, 262 are selected to react at a good rate. It is also possible to use fluids of different viscosities in each annular groove comprising compensating masses 260, 262, 264 to obtain different desirable degrees of response for each compensating mass. It is also possible to use different viscous and different fluids in each shear gap for the damping masses 254, 256, and 258.

FIG. 16 shows an equalizer 270 similar to that shown in FIG. 15, with the only difference being that the damping masses 272, 274, 276 and the compensation masses 278, 280, 282 are on each side of the central plane of the balancer. Is located in a staggered relationship with each other. As shown in FIG. 15, the equalizer 270 is mounted to a body 284 consisting of a housing 286 having three annular grooves opened to one side of the housing 286 and opened to the opposite side of the housing 286. Is formed by. Several covers 288 are secured on opposite sides of the housing 286 to retain the damping mass and compensation mass in each hollow interior of the body 252 and to close the open grooves. In the embodiment shown in FIG. 15, the compensation weights 278, 280, 282 increase from the radially innermost set of the compensation weights 278 to the radially outermost of the compensation weight 282 in size and weight. In another embodiment of the balancer 300 shown in FIG. 17, the balancer 300 is radially inward and outward of the body 302, the torsional vibration damping mass 308, and the torsional vibration damping mass 308. Two sets of translational vibration compensating masses (310). Body 302 includes a housing 304 with three annular grooves positioned coplanar with respect to one another. The annular groove in the housing 304 is opened toward one side of the housing 304 and the cover is fixed to the side opening of the housing 304 to close the annular groove and forms three hollow portions in the body 302.

The annular torsional vibration damping mass 308 provides a shear gap 312 between the outer periphery of the damping mass 308 and the inner wall surface that borders the interior of the hollow in which the damping mass 308 is located. The viscous fluid is disposed inside the shear gap 312.

Each of the radially outermost annular grooves 314 and the radially outermost annular grooves 316 receive one of the sets of compensation masses 310. Each of these sets of compensating masses 310 are arranged in a single annular column format similar to that shown in FIG. 3. The mass 310 located in each successive groove 314, 316 is the same or substantially the same in size and weight with respect to each other. In addition, the set of compensation masses 310 in the radially outermost groove 316 is the same or substantially the same in size and weight as the size and weight of the compensation masses 310 in the radially innermost annular grooves 314. . FIG. 17 also shows one of a plurality of through holes 320 that facilitates securing the balancer 300 to a rotating member such as a rotating shaft.

Various embodiments of the torsional and translational vibration removing device described above and shown in the figures may be used in various ways depending on the requirements of a particular system. For example, the embodiment shown in FIGS. 2 and 3 provides a maximally compact design and can be widely applied when space is constrained and conditions are required. The embodiment shown in FIG. 7 provides additional compensation capacity for translational vibration for two sets of translational vibration compensation masses.

The embodiment shown in FIG. 9 is particularly useful when the translational equilibrium demand is high under certain conditions. In this regard, the arrangement shown in FIG. 9 provides a series of different races or directions spaced at various radial distances from the axis of rotation. The embodiment depicted in FIG. 8 provides similar advantages in combination with the arrangement of FIG. 9, but an optional device is provided for a condition that does not allow for coplanar radial placement of the various races as the geometry of the machine.

The embodiment of the present invention shown in FIG. 10 provides the additional advantage of allowing two different fluids (ie different viscous fluids) to be used within each path and shear gap. This is because the annular groove in the damping mass on one side of the shear gap and the central wall 157 is filled or partially filled with a special viscous fluid or a form of fluid, while the one side of the shear gap and the central wall 157 The annular grooves in the damping mass on the bed are filled or partially filled with other types of fluids or other viscous fluids. The arrangement shown in FIG. 10 may be useful if the stability of the system is taken into account during all stages of operating speed.

The embodiment of the present invention shown in FIG. 11 is particularly useful in the form of compact and relatively lightweight devices where precise compensation is required for both torsional and translational vibrations. The arrangement of the plurality of masses is located at different radial distances from the axis of rotation, which gives the possibility of further "tuning" the device for the torsional coordination that may exist in a particular system. This arrangement can greatly improve the quality of the balancer, the reaction rate and the operational stability of the device.

The arrangement shown in FIG. 12 is optionally provided in combination with the advantages combined with the arrangement shown in FIGS. 10 and 11. The embodiment shown in FIG. 13 provides the advantage of using different viscous fluids or other fluids in the race as the compensation mass moves, while using one type of fluid or fluid with special viscosities in the shear gap. Therefore, silicone oils with good torsional damping properties but insufficient lubrication properties can be used in the race for the effect of the first reaction time of the compensating mass. In addition, heavier fluids in the shear gap can increase the size of the shear gap, thereby minimizing the effect of manufacturing tolerances on the performance of the rotating device.

The embodiment shown in FIG. 14 provides similar advantages as the embodiment shown in FIG. 13, but further provides the advantage of providing a relatively precise centering of the damping mass. The arrangement shown in FIG. 14 is also useful when the expected load between the damping mass and the housing is relatively high such that a needle bearing is required.

The embodiments of the present invention shown in FIGS. 15 and 16 exclude the compensation mass separated from other viscous or other viscous fluids and damping masses that may be employed in each groove or pathway. It provides similar advantages described above in connection with the arrangement described in.

In various embodiments of the present invention, the rotating device, which acts as a damper that is not tuned to torsion sensing, is not well tuned for any particular frequency, but is well suited to compensate for vibrations exceeding a wide range of frequencies. In some applications that are special characteristics of the system that occur in relation to vibrations having a particular frequency or vibrations within a frequency range, an adjusted mass damper or an unadjusted viscous damper as shown in FIG. 18 may be employed. The rotary device or damper 320 shown in FIG. 18 including the body 322 has a housing 324 in which an annular groove is opened to open one side of the housing 324. The cover 326 defines a hollow interior of the housing and fits against the open end of the housing 324 to close the open end of the housing.

The annular torsional vibration damping mass 328 is located inside the hollow of the body 322. Annular damping mass 328 is provided in groove 330 and has a U-shaped cross section. As shown in FIG. 3, a number of translational vibration compensating masses 322 are located within the annular groove 330 and are arranged in a similar single annular row for a single annular column arrangement. The replenishment masses 332 disposed in the annular groove 330 preferably have the same weight and size.

Two annular disc shaped elastomeric elements 334 are also disposed in the hollow inside the body 322 and on opposite sides of the annular damping weight 328. The elastomeric element 334 is secured not only to the annular damping mass 328 but also to the inner wall of the body 322 to limit the angular motion of the annular damping mass 328 during rotation of the balancer 320.

The balancer 320 shown in FIG. 18 may be rotated to damp a particular torsional vibration frequency or range of torsional vibration frequencies by appropriately selecting the material and properties of the elastomeric element 334. In other words, the natural frequency of the rotary damper is equal to the square root of the rotational stiffness of the elastomeric element divided by the inertia of the damping mass 328. Then, by appropriately selecting the material and properties of the elastomeric element 334, the natural frequency of the rotary damper can be designed to correspond to the specifically associated torsional vibration frequency or torsional vibration frequency.

In the context of each of the embodiments described above, the through-holes 52 and 54 shown in FIGS. 2 and 3 for mounting and securing the equalizer in the proper position of the rotating element (ie, shaft, magnet oscillator or other rotating body); It can be seen that similar through holes can be installed in the balancer. In addition, in each of the disclosed embodiments, the supplemental mass may have a spherical ball shape or other shapes such as cylindrical weight or disk weight.

The present invention provides various other embodiments to eliminate or substantially cancel translational vibration as well as torsional vibration. In the initial test, it was found that the balancer according to the present invention significantly reduced vibration. Depending on the background in which the balancer is used, the advantages resulting from the use of the balancer can be realized in many different forms. For example, the use of an equalizer in the environment of a jet ski allows the user to operate the jet ski for a longer period of time without experiencing the continuous vibrations typically associated with such vessels. In these as well as other environments, the reduction of torsional and translational vibrations is advantageous in terms of improving operation, increasing the efficiency of the rotating element and further increasing the efficiency of the entire system. It also extends the life of machinery or systems.

Various embodiments of the balancer according to the invention are also advantageous in that they are relatively small in size and compact. This means that the balancer can be used in conjunction with existing systems and machinery.

The fact that the balancer according to the invention can reduce torsional and translational vibrations means that the torsional vibrations have less influence on the behavior of the translational vibration compensating masses than when no torsional vibration damping masses are present. Torsional vibration damping masses exhibit significantly reduced levels of translational vibration compared to the absence of a translational vibration compensating mass.

While the various embodiments described above and shown in the figures have been described as separate balancers attached to a rotating element, the invention may be embodied in other forms. For example, if space is allowed on the rotating element, an annular groove for receiving the damping mass and the compensating mass according to various embodiments shown in the drawings may be formed directly in the rotating element.

The principles of operation of the present invention, the preferred embodiments and their modes are described in the foregoing detailed description. However, the invention to be protected is not to be considered as limited to the specific embodiments disclosed herein. Various modifications and variations are possible without departing from the spirit of the invention, and equivalent inventions may also be employed. It is, therefore, to be understood that all such variations, modifications and equivalents are included within the spirit and scope of the invention as defined in the claims.

Claims (24)

A torsional and translational vibration removing device for removing torsional and translational vibrations in a rotating element, A housing having an annular groove open along at least one side; A cover which is fixed to the housing and closes one side and defines an annular hollow interior which is bounded by an inner wall and sealed from the outside; Means for mounting the housing on the rotating element; It is located inside the hollow so as to be able to rotate freely inside the hollow interior, and has an outer circumferential surface having a smaller dimension than the inner wall surface that borders the hollow so that a shear gap is formed between the inner wall surface and the outer circumferential surface that borders the hollow interior. An annular torsional vibration damping mass having at least one annular groove, A viscous fluid disposed within the hollow interior, Positioned in an annular groove of the torsional vibration damping mass, and at the time of rotation of the torsional and translational vibration removing device, the position where the torsional vibration damping mass is reduced to reduce the torsional vibration in the hollow interior is reduced. A torsional and translational vibration removing device comprising a translational vibration compensation mass that is free to move in an annular groove of the torsional vibration damping mass to take. 2. The annular groove of claim 1, wherein the annular groove in the torsional vibration damping mass is a first annular groove comprising a second annular groove provided in the torsional vibration damping mass, The second annular groove is spaced apart from the first annular groove by the wall of the torsional vibration damping mass, The plurality of translational vibration compensating masses is disposed in the first annular groove of the torsional vibration damping mass and includes a plurality of freely movable translational vibration compensating masses located in the second annular groove of the torsional vibration damping mass. Removal device. 3. The torsional and translational vibration removing device of claim 2, wherein the first and second annular grooves are spaced at an equal distance from the central plane of the housing. 3. The torsional and translational vibration removing device of claim 2, wherein the second annular groove is radially located toward the outside of the first annular groove. 3. The method of claim 2, wherein the plurality of translational vibration compensation masses in the first annular groove are substantially equal in weight, The translational vibration compensating mass in the second annular groove is substantially equal in weight, And a plurality of translational vibration compensation masses in the first annular groove have a weight different from that of the plurality of translational vibration compensation masses in the second annular groove. 2. The hollow interior of claim 1 wherein the hollow interior is divided into first and second hollow interiors that are separated from each other, And the torsional vibration damping mass is a first torsional vibration damping mass disposed inside the first hollow, and includes a second annular torsional vibration damping mass located within the second hollow interior. 7. The torsional and translational vibration removing device of claim 6, wherein the second torsional vibration damping mass is formed in an annular groove and comprises a plurality of translational vibration compensating masses disposed in the annular groove of the second torsional vibration damping mass. 2. The torsional vibration damping mass of claim 1, wherein the torsional vibration damping mass has first, second, and third annular grooves disposed adjacent to each other in a direction parallel to the axis of rotation of the housing, wherein the plurality of translational vibration compensating masses are torsional. A torsional and translational vibration removing device disposed in the first annular groove of the vibration damping mass and comprising a plurality of translational vibration compensation masses disposed in the second annular groove and a plurality of translational vibration compensation masses disposed in the third annular groove. 9. The torsional and translational vibration removing device of claim 8, wherein each of the plurality of translational vibration compensating masses in the first annular groove has a different weight from each of the translational vibration compensating masses in the second annular groove and the third annular groove. . A torsional and translational vibration removing device for removing torsional and translational vibrations in a rotating member, Body having a hollow inside, Annular torsional vibration damping mass located in the hollow of the body to be rotatable in the hollow of the body, Viscous liquid in the hollow interior of the body, A plurality of translational vibration compensation masses disposed in an annular groove of the torsional vibration damping mass and arranged in each annular row, The torsional vibration damping mass has at least one annular groove, Since the plurality of translational vibration compensating masses move freely in the annular groove of the torsional vibration damping mass, the torsional vibration damping mass rotates inside the hollow to reduce the torsional vibration during the rotation of the body, while the translational vibration compensating mass is the torsional vibration damping mass. Torsional and translational vibration removing device that enters a position to move within the annular groove to reduce translational vibration. 11. The torsional and translational vibration removing device of claim 10, wherein the body is mounted to a rotating member. 12. A torsional and translational vibration removing device as recited in claim 11, comprising means for mounting a body on a rotating member. 12. The torsional vibration damping mass of claim 10, wherein the annular groove in the torsional vibration damping mass is a first annular groove, and includes a second annular groove formed in the torsional vibration damping mass, wherein the second annular groove is a wall of the torsional vibration damping mass. a plurality of freely moving parts spaced apart from the first annular groove, the plurality of translational vibration compensating masses disposed in the first annular groove of the torsional vibration damping mass and located in the second annular groove of the torsional vibration damping mass. Torsional and translational vibration removing device comprising a possible translational vibration compensation mass. 14. The torsional and translational vibration removing device of claim 13, wherein the second annular groove is located radially outward of the first annular groove. The method of claim 13, wherein the plurality of translational vibration compensation masses in the first annular groove are substantially the same weight, and the translational vibration compensation masses in the second annular groove are substantially the same weight, A torsional and translational vibration removing device having a translational vibration compensating mass having a weight different from that of the plurality of translational vibration compensating masses in the second annular groove. 11. The method of claim 10, wherein the hollow interior is divided into first and second hollow interior regions separated from each other, the torsional vibration damping mass is a first torsional vibration damping mass disposed in the first hollow interior region, and the second hollow interior. A torsional and translational vibration removing device comprising a second annular torsional vibration damping mass located in the region. 17. The torsional and translational vibration removing device of claim 16, wherein the second torsional vibration damping mass has an annular groove and comprises a plurality of translational vibration compensating masses disposed in the annular groove of the second torsional vibration damping mass. 11. The torsional vibration damping mass of claim 10, wherein the torsional vibration damping mass has first, second, and third annular grooves disposed adjacent to each other in a direction parallel to the axis of rotation of the housing. A torsional and translational vibration removing device disposed in the first annular groove of the torsional vibration compensating mass and comprising a plurality of translational vibration compensation masses disposed in the second annular groove and a plurality of translational vibration compensation masses disposed in the third annular groove. 11. A torsional and translational vibration as set forth in claim 10, comprising a pair of elastomeric elements located inside the hollow, the elastic element being fixed to an annular torsional vibration compensating mass and fixed to an inner wall defining the hollow interior. Removal device. A torsional and translational vibration removing device for removing torsional and translational vibrations of a rotating member, A body having a first annular hollow space and a second annular hollow space, Annular torsional vibration damping mass located in the first hollow space and having an outer periphery, A viscous fluid disposed in the first hollow space, A plurality of translational vibration compensation masses located in the second hollow space and arranged in each annular row, The first and second hollow spaces are separated from each other by the wall of the body, Since the first hollow space has a larger dimension than the torsional vibration damping mass, there is a shear gap between the outer periphery of the torsional vibration damping mass and the inner wall portion of the body defined by the second hollow space, The plurality of translational vibration compensating masses can move freely in the second hollow space, so that during rotation of the body, the annular torsional vibration damping mass rotates in the first hollow space to reduce the torsional vibration while the translational vibration compensating mass is the second hollow space. Torsional and translational vibration removing device to move into the position to reduce translational vibration. 21. A torsional and translational vibration removing device as set forth in claim 20, wherein said body is mounted to a rotating member. 22. A torsional and translational vibration removing device as set forth in claim 21 comprising means for mounting a body on a rotating member. 21. The body of claim 20, wherein the body comprises a third annular end space separated from the first hollow space by the wall of the body, the first hollow space being located between the second hollow space and the third hollow space, A torsional and translational vibration removing device comprising a plurality of translational vibration compensation masses disposed in the hollow space and arranged in respective annular rows. 24. The torsional and translational vibration removing device of claim 23, wherein the first hollow space is located radially outward of the third hollow space.