KR100466904B1 - Torsion and Vibration Elimination Device - Google Patents

Abstract

The torsional and translational vibration removing device 34 or balancer comprises a combination of at least one annular torsional vibration damping mass 42 and a plurality of translational vibration compensating masses 50. The annular torsional vibration damping mass 42 is located in the annular groove 46 in the housing and is freely rotatable during the rotation of the balancing device 34. The annular torsional vibration damping mass 42 has an annular groove 46 for receiving the translational vibration compensating mass 50. The compensation mass 50 rotates freely in the annular groove 46 in the torsional vibration damping mass 42, so that during the rotation of the balancing device 34 the torsional vibration damping mass 42 rotates to reduce the torsional vibration while compensating for it. Mass 50 is moved into the annular groove 46 of damping mass 42 to enter a position to reduce translational vibration.

Description

Torsional and translational vibration eliminator

The present invention relates generally to a balancer and a vibration damper. In particular, the present invention is directed to a torsional and translational vibration removing device that is effectively designed to eliminate torsional and translational vibrations.

Rotating systems such as rotary shafts are often torsionally vibrated and translationally vibrated. In general, torsional vibration is referred to as vibration which vibrates a rotating body (eg, a rotating shaft) 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, and the like, torsional vibrations and translational vibrations occur. 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. Figure 1 shows a viscous torsional vibration device displaced in relation to a pulley. The pulley 30 has a cylindrical cavity rotatably driven by a shaft 31 and containing a 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 dimensions of the space, the viscosity of the fluid, and the relative rotational speed between the pulley and the damping mass.

The scattered viscous damping described above can offset some torsional vibrations, but has a number of disadvantages 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 lifetime of the system.

While the presence of a device that eliminates both translational and torsional vibrations is required, it is relatively small and compact in design so that the device can be used in combination with existing machines and systems.

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 shown to be 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 according to the present invention.

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

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

7 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.

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

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

11 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.

12 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.

13 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.

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 adapted to eliminate both translational and torsional vibrations of a rotating element such as a shaft. The balancer according to the invention can be achieved by means of a relatively small and compact design. Therefore, there are mechanisms and systems in which the present invention will be equipped in an effective way to eliminate torsional and translational vibrations. The balancing device 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 fixed to the housing to define a housing with an annular groove open along at least one side and an annular hollow interior sealed from the outside and to close one side. A cover and means for mounting the housing on the rotating element. Since the annular torsional vibration damping mass has an outer circumferential surface which is smaller in dimension than the inner wall surface bounding the hollow interior, the shear gap is present between the outer circumferential surface of the torsional vibration damping mass and the interior wall bordering the hollow interior. 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. Since the translational vibration compensating mass moves freely in the annular groove of the torsional vibration damping mass, the translational vibration compensating mass is annular of the torsional vibration damping mass to indicate the position where the translational vibration of the rotating element is reduced while the torsional and translational vibration removing device is rotated. Moved into the groove, the torsional vibration damping mass is rotated inside the hollow to reduce the torsional vibration.

According to another feature of the invention, the torsional and translational vibration removing device comprises a body having a hollow interior, an annular torsional vibration damping mass located in the hollow interior of the body and provided with at least one annular groove, and a viscous liquid inside the hollow of the body And a plurality of translational vibration compensation masses disposed in the annular groove of the torsional vibration damping mass and arranged in a single annular 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 invention, the torsional and translational vibration removing device comprises a body having first and second hollow spaces separated from each other by a wall portion of the body, and an annular torsional vibration damping mass located within the first hollow space. And a plurality of translational vibration compensating masses located in the second hollow space. The first hollow space is dimensioned larger than the torsional vibration damping mass such that the shear gap is between the outer periphery of the torsional vibration damping mass and the inner wall surface of the body bordering 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 annular row. Since the plurality of translational vibration compensating masses are freely movable in the second hollow space, taking a position to reduce the translational vibration while the annular torsional vibration damping mass rotates in the first hollow space to reduce the torsional vibration during rotation of the body. The translational vibration compensating mass in order to move into the second hollow space.

The present invention provides a rotary device or vacuum removal device that compensates for both torsional vibration as well as translational vibration of a rotating element such as a shaft. 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 vibrations that may be due to various sources, such as the seizure of pistons in internal combustion engines. Torsional vibration damping masses can be made from a variety of materials that provide a desired weight of metal (eg, steel, stainless steel, tinsten carbide, etc.) and ceramic materials 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.

With reference to FIG. 2, one embodiment of a balancing device or torsional and translational vibration removing device 34 according to the invention consists of a disk-shaped body 36 mounted on a rotating element such as a shaft. The disc-shaped body 36 includes a housing 38 having a continuous annular groove extending around the outer circumference of the housing. One side of the annular groove opens outward and the cover 40 is secured to the housing 38 to close the open side of the annular groove, thereby forming an annular hollow interior in the body 36 that is sealed from the outside.

The annular torsional vibration damping mass 42 is located in the hollow interior of the body 36. The torsional vibration damping mass 42 is less than the inner wall surface bounding the hollow interior of the body 36 such that the shear gap 44 is present between the outer circumferential surface of the torsional vibration damping mass 42 and the inner wall facing the hollow interior of the body. It has an outer circumferential surface which is a small dimension. 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 disc shaped element. As shown in FIG. 2, the torsional vibration damping mass 42 is provided with a continuous annular groove 46. The annular groove 46 is formed on the side of the torsional vibration damping mass 42 which faces radially inward 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, such as cylindrical or disc shaped weights, but the translational vibration compensation mass 50 is 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. The compensation mass 50 for performing the translational vibration compensation can be used in other shapes such as cylindrical or disc shaped masses, but a spherical shape is preferred.

The inner surface of the torsional vibration damping mass 42 bounded by 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 the outer circumference of all the annular grooves 46 and the torsional vibration damping mass 42 and 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 balancing device on a rotating element such as a shaft. Several additional through holes 54 are arranged radially outward of the central through hole 52. These through holes 54 hold the balancer in place on the rotating element.

The torsional and translational vibration removing device according to the present invention is used in almost every position where the rotating element is subjected to translational vibration as well as torsional vibration. One content with which the present invention has been found to be particularly useful is 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 part 60 has a through hole adapted to be mounted to the engine block and extending the front end of the crankshaft 56. The magneto stator 63 has a through hole that is mounted to the casing part 60 and extends the front end of the crankshaft 56. A magneto disc or magneto flywheel 58 is operably mounted to the front protruding end of the crankshaft 56 and extends over the magneto stator 63. The magneto casing component 61 is fastened to another magneto casing component 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 magneto disk (flywheel) 58. The vibration removing device 34 aligns the through hole 54 on the center of the body 36 with a corresponding hole on the magneto and fixes the vibration removing device in place by using the screw 62 shown in FIG. It is disposed on the magnetic disk 58. In the configuration shown in FIG. 4 the torsional and translational vibration removing device 34 acts as a front balancer for the magneto-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 configuration a centered through hole 52 in the center of the body 36 can be screwed to threadably receive the threaded portion 64 on the end of the crankshaft assembly.

6 illustrates 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 a front balancer connected to magneto. On the other hand, 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 (eg magneto or shaft). As the torsional and translational vibration removing device rotates, the translational vibration compensating mass 50 freely moves in the annular groove 46 of 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 rotates freely inside the hollow of the body 36 to reduce or almost eliminate the torsional vibration.

Accordingly, the present invention provides a mechanism for reducing or substantially eliminating torsional and translational vibrations. In addition, the structure of the balancer is simple and not complicated in dimensions. This means that the balancer is well adapted to existing systems and machinery where space is limited. In addition, the performance of the balancer to reduce the torsional vibration as well as the translational vibration means that the torsional vibration has less influence on the behavior of the translational vibration compensation mass 50 as compared to the case where the torsional vibration damping mass is not provided. In the above-described configuration of the present invention, the torsional vibration damping mass 42 exhibits a low 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 produced in 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 balancing device and that the balancing device has an overall shape 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 of the torsional vibration damping mass 74 smaller than the dimension of an inner wall surface bounded by a hollow interior in the body 72. And a shear gap 82 between the inner wall surface that borders the hollow interior of the body 72. The annular torsional vibration damping mass 74 has two spaced annular grooves 84 separated from one another 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 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 each represent a single annular row of translational vibration compensation masses aligned in a manner similar to that shown in FIG. 3. It includes each. Preferably, all of the translational vibration compensating masses 76 in one of the grooves are the same or nearly identical in weight and dimensions, and all of the translational vibration compensation masses in the other annular grooves are the same or nearly identical in weight and dimensions. 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 illustrated in FIG. 8, which shows a balancing device 90 comprising a body 92, an annular torsional vibration damping mass 94 and three sets of translational vibration compensation masses 96, 98, and 100. do. 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 radial direction from one end (i.e. closed end) to the opposite end (i.e. 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 dimension 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 translational vibration compensating masses 96 are arranged in a single annular row similar to that shown in FIG. 3. Similarly, the translational vibration compensation 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 dimensions, and each of the masses 98 of the intermediately located annular groove 108 is the same in weight and dimensions or Almost the same. In addition, the mass 96 is smaller in weight and dimension 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. The dimensions and weight are much smaller. 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 equalizer 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 the balancing device 112 includes a body 114, an annular torsional vibration damping mass 116, and four sets of translational vibration compensation masses ( 118,120,122,124. The body 114 is composed of a housing 126 having an annular groove opening to 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 to one side of the torsional vibration damping mass 116 to insert masses 118, 122, 124. A 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 different dimensions. 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 in weight and dimensions, and each mass 120 of the annular groove 132 is substantially the same in size and weight. Is good, and each mass 122 of the annular groove 134 has the same or nearly the same dimensions and weights, and each mass of the annular groove 136 preferably has the same or nearly the same dimensions and weights. Do.

In addition, the dimensions and weight of the compensation mass vary from one groove to the next. 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 the mass of the annular groove 134 is intermediate in the radial direction. Preferably, the weight 122 is larger in dimension and weight than the weight 120, and the weight 124 in the radially outermost annular groove 136 is in the middle in the radial direction. Larger in dimension and weight than mass 122 in. As in the description of all the above embodiments, the outer dimension of the torsional vibration damping mass 116 is smaller than the inner dimension of the hollow interior of the body 114, so that the shear gap 142 is the annular torsional vibration damping mass ( 116 is present between the outer circumferential surface and the inner wall surface that borders the hollow interior of the 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 translational vibration compensating masses 118, 120, 122, 124, 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 to shear gaps 142 with greater viscosity, such as silicone oils with insufficient lubrication properties.

An embodiment of the balancing device 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 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 open 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 having a smaller dimension than an inner wall surface that is bounded by each of the hollow inner chambers, such that the outer circumferential surface of the torsional vibration damping mass and each inner wall surface that is bounded by the hollow inner chamber Exists between.

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 dimensions and weight with respect to each other, and the weight of the other annular grooves 156 is the same or almost the same in dimension and weight. In addition, as shown in FIG. 10, the mass of one of the annular grooves 156 is the same or nearly the same dimension and weight with respect to the mass of the other annular groove 156.

FIG. 11 shows an embodiment of an equilibrium device 160 that includes a body 162, three annular torsional vibration damping masses 164, 166, 168, and three sets of translational vibration compensation masses 170, 172, 174. The body 162 is a housing 176 having torsional vibration damping masses 164, 166, 168 and three annular grooves opened along one side of the housing 176 to insert the translational vibration compensation masses 170, 172, 174. It consists of. The cover 1768 is fixed 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 mass 164 has an annular groove 180 that receives a translational vibration compensating mass 170 aligned in a single annular column similar to that shown in FIG. 3. Similarly, the radial 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 the compensation mass 174. Is provided with an annular groove (184). 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 defines a respective shear gap 175 between an outer surface of each of the damping masses 164, 166, 168 and an inner wall surface bounding each hollow interior of the body 162. It becomes a dimension.

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

The embodiment of the balancing device 190 shown in FIG. 12 includes a body 192, three annular torsional vibration damping masses 194, 196, 198, and three sets of translational vibration compensation masses 200, 202, 204. Similar to the embodiment shown. 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 open to 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 define respective shear gaps 205 between the outer periphery of each of the damping masses 194, 196, 198 and the respective inner wall surface of the hollow interior in which the damping masses 194, 196, 198 are accommodated. It becomes the dimension 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 spaced radially outward of the two smaller damping masses 194, 196. do. 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 194 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 greater width and depth 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 about the same or nearly the same in size and weight, and each of the compensating masses 202 in the annular grooves 212 of the intermediate dimension is in size and weight. Equal or nearly identical, the compensating mass 204 in the largest annular groove 214 is identical or nearly identical in dimension and weight. Further, the compensation mass 200 in the annular groove 210 of the annular damping mass 194 is of a smaller dimension 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 dimension and weight than the compensation mass 204 of the annular groove 214 of the damping mass 198.

FIG. 13 shows a further embodiment of the balancing device 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 grooves 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 dimension and weight. 13 shows a through hole 238 in which the balancing device 220 is attached to a rotating element such as a crankshaft or magneto.

The embodiment of the present invention shown in FIG. 13 illustrates that a form of viscous liquid may be placed in the shear gap 236 in order to effectively effect the fast response of the compensation mass 226 when the balancing device 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 other liquids are located in the hollow interior 240 in the annular damping mass 224. Torsional vibration damping mass 224 freely rotates in an annular groove formed in housing 228 without sufficient rotational motion.

In the embodiment shown in FIG. 14, the embodiment of the invention shown in FIG. 14 has a needle bearing 242 in which an annular torsional vibration damping mass 224 and an inner wall boundary delimiting 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 balancing device 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. It is advantageous when it must be predicted between and the annular damping mass 224.

Figure 15 shows another embodiment of the invention in which the torsional vibration damping mass and the translational vibration compensating mass are positioned separately in a groove separate from the housing. As shown in FIG. 15, the balancing device 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. 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 compensation 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 dimension of the damping masses 254, 256, 258 is gradually reduced from the radially innermost damping mass 254 to the radially outermost damping mass 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 compensating masses 260 are the same or nearly the same in size and weight, and all of the compensating masses 262 are the same or nearly the same in dimension and weight. Further, the radially innermost compensation mass set 260 is smaller in dimension and weight than the radial middle set of compensation masses 262, and the dimension and weight of the radial middle set of compensation masses 262 is radial. It is smaller than the dimension and weight of the set of compensation masses 264 in the outermost direction.

The annular torsional vibration damping mass 254, 256, 258 is 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 mass is received therein. Dimensioned. In addition, a viscous fluid is disposed inside each shear gap 257. Light weight lubrication and damping fluid is also provided inside each annular groove in which the compensation masses 260, 262, 264 are disposed. The viscous fluid filled in the annular groove on which the compensating masses 260, 262, 264 are arranged is preferably different from the viscous fluid disposed in the shear gap 257 and preferably when the compensating device rotates. 262, 262). It is also possible to use fluids of different viscosities in each annular groove comprising compensating masses 260, 262 and 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 a balancing device 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 balancing device. Is located in a staggered relationship with each other. As shown in FIG. 15, the balancing device 270 consists of a housing 286 having three annular grooves opened to one side of the housing 286 and opening to opposite sides of the housing 286. Is formed by Several covers 288 are secured to opposite sides of the housing 286 to retain the damping mass and compensating mass in the hollow interior of each of the bodies 252 and to close the open grooves. In the embodiment shown in FIG. 15, the compensation weights 278, 280, 282 gradually increase in dimension and weight from the radially innermost set of compensation weights 278 to the radially outermost set compensation weights 282. . Another embodiment of the balancing device 300 is shown in FIG. 17, with two sets of radially inward and outward positions of the body 302, the torsional vibration damping mass 308, and the torsional vibration damping mass 308. A translational vibration compensating mass 310. Body 302 includes a housing 304 with three annular grooves located 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 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 innermost annular groove 314 and the radially outermost annular groove 316 receives one of the sets of compensating mass 310. Each of these sets of compensating masses 310 are arranged in a single annular column format similar to that shown in FIG. The masses 310 located in the continuous grooves 314 and 316, respectively, are the same or nearly identical in size and weight with respect to each other. In addition, the set of compensating masses 310 in the radially outermost groove 316 is the same or nearly identical in size and weight to the size and weight of the compensating mass 310 in the radially innermost annular grooves 314. FIG. 17 also shows one of a plurality of through holes 320 that facilitates securing the balancing device 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 Figures 2 and 3 provides a maximally compact design and can be widely applied when space is constrained and conditions are needed. 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 requirement 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 shown in FIG. 8 combines with the arrangement of FIG. 9 to provide similar advantages, but an optional device is provided for a state where the machine shape does not allow the coplanar radial configuration of the various races.

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 shear gap and the central wall 157 On one side the annular groove in the damping mass is filled or partially filled with another type of fluid or other viscous fluid. The configuration 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 invention shown in FIG. 11 is particularly useful in the form of compact and relatively lightweight devices where precise compensation for both torsional and translational vibration is required. The installation of a plurality of masses is located at different radial distances from the axis of rotation, providing further "tuning" of the device for torsional coordination that may exist in a particular system. This configuration can greatly improve the quality of the balancer, the reaction rate and the operational stability of the device.

The configuration shown in FIG. 12 is optionally provided in combination with the advantages combined with the configurations shown in FIGS. 10 and 11. The embodiment shown in FIG. 13 provides the advantage of using a fluid or other fluid with different viscosities in the race as the compensating 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 compensation mass. In addition, heavier fluids in the shear gap can increase the dimension 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 advantages similar to those associated with the embodiment shown in FIG. 13, but further provides the advantage of providing a relatively accurate centering of the damping mass. The configuration shown in FIG. 14 is also useful when the predicted load is relatively high between the damping mass and the housing such that a needle bearing is required.

Embodiments of the invention shown in FIGS. 15 and 16 are described in FIGS. 11, 12 and 13 excluding compensation masses that are separated from other viscous or other viscous fluids and damping masses that may be employed in each groove or path. It provides similar advantages described above in connection with the configuration.

In the various embodiments of the present invention described above, a rotating device that acts as a damper that is not tuned to torsion detection is not tuned for any particular frequency, but is well suited to compensate for vibrations that exceed 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 which opens 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 compensation masses 322 are located within the annular groove 330 and are arranged in a similar single annular row for a single annular thermal configuration. Compensation masses 332 disposed in the annular groove 330 preferably have the same weight and dimensions.

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 balancing device 320.

The balancing device 320 shown in FIG. 18 may be rotated to damp a particular torsional vibration frequency or a 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 properly 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, similar to 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, magneto or other rotating body). It can be seen that the through hole can be installed in the balancer. In addition, in each of the disclosed embodiments, the compensating 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 the translational vibration as well as the translational vibration. In the initial test, it was found that the balancer according to the 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 an environment of jet skis allows a user to operate jet skis for longer periods 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 balancing device according to the invention are also quite advantageous in that the dimensions are relatively small 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 balancing devices 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 fixed to the closed housing, the cover defining an annular hollow interior sealed by an interior wall and sealed from the outside; Means for mounting the housing on the rotating element; A dimension smaller than the inner wall which is positioned inside the hollow so as to be able to rotate freely inside the hollow interior and which borders the hollow interior such that there is a shear gap between the inner wall which borders the hollow and the outer circumferential surface of the torsional vibration damping mass An annular torsional vibration damping mass having an outer circumferential surface of which is installed at least one annular groove, A viscous fluid disposed inside the hollow, Positioned in the annular groove of the torsional vibration damping mass and taking a position to reduce the translational vibration in the rotating element while the torsional vibration damping mass rotates to reduce the torsional vibration in the hollow interior upon rotation of the torsional and translational vibration removing device. A torsional and translational vibration removing device comprising a plurality of translational vibration compensating masses freely moving in an annular groove of the torsional vibration damping mass to move into the annular groove of the torsional vibration damping mass. The torsional vibration damping mass according to claim 1, wherein the annular groove in the torsional vibration damping mass is a first annular groove and includes 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. Vibration elimination device. 3. The torsional and translational vibration removing device of claim 2, wherein the first and second annular grooves are equally spaced from the central plane of the housing. 3. The torsional and translational vibration removing device of claim 2, wherein the second annular groove is disposed radially outward 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 the weight 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 Torsional and translational vibration removing device comprising a plurality of translational vibration compensation masses disposed in the first annular groove of the torsional vibration damping mass, 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, A body having a hollow interior, An annular torsional vibration damping mass located within the hollow of the body for rotation within the hollow of the body; With 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 respective annular rows, 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 formed of the torsional vibration damping mass. A torsional and translational vibration removing device that moves into an annular groove and enters a position to reduce translational vibration. 11. The torsional and translational vibration removing device of claim 10, wherein the body is mounted on a rotating member. 12. A torsional and translational vibration removing device as recited in claim 11 including means for mounting a body on said rotating member. 12. The torsional vibration damping mass according to 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 formed by the wall portion of the torsional vibration damping mass. Spaced apart from the first annular groove, wherein the plurality of translational vibration compensating masses are disposed in a first annular groove of the torsional vibration damping mass and are located in a second annular groove of the torsional vibration damping mass. Torsional and translational vibration removing device comprising a mass. 14. The torsional and translational vibration removing device of claim 13, wherein the second annular groove is disposed radially outward of the first annular groove. 14. 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, The translational vibration compensating mass has a weight different from the weight of the plurality of translational vibration compensating masses in the second annular groove. 11. The hollow interior 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. 6. A torsional and translational vibration removing device disposed in a first annular groove of a torsional vibration compensating mass and comprising a plurality of translational vibration compensating masses disposed in a second annular groove and a plurality of translational vibration compensating masses disposed in a third annular groove. 11. A torsional and translational vibration removing device as recited in claim 10, comprising a pair of independent elastomeric elements located inside the hollow, the elastomeric elements being fixed to an annular torsional vibration compensating mass and fixed to an inner wall defining the hollow interior. 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, An 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, rotational reduction in the first hollow space of the annular torsional vibration damping mass reduces the torsional vibration while the translational vibration compensating mass is the second hollow space. Torsional and translational vibration removing device that moves into space and enters a position to reduce translational vibration. 21. The torsional and translational vibration removing device of claim 20, wherein the body is mounted to a rotating member. 23. A torsional and translational vibration removing device as recited in claim 21 including means for mounting a body on said rotating member. The body of claim 20, wherein the body comprises a third annular hollow space separated from the first hollow space by a wall of the body, the first hollow space being disposed 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 a third hollow space and arranged in respective annular rows. 24. The apparatus of claim 23, wherein the first hollow space is disposed radially outward of the third hollow space.