DE1533506C3 - Mechanical unbalance vibration generator for generating elastic body vibrations - Google Patents

Description

The invention relates to a mechanical unbalance vibration generator for generating elastic body vibrations, which consists of a generator body in which the orbit is located for an unbalance rotor body forming bearing surface is located while with the unbalance rotor body a drive coupling is fixedly connected coaxially and a rotatable input coupling between the drive clutch and the drive motor of the generator are switched on.

The invention thus relates to the technical field of mechanical generation and transmission relatively high performance in terms of high-energy, high-frequency mechanical vibrations, in particular the generation and transmission of fast vibrations in mechanical vibration systems, which can be excited to resonance and which are made of elastically deformable, vibratory Elements exist.

For example, mechanical vibration generators are known from US Pat. No. 29 60 314, - at which an unbalance rotor is driven on a circular orbit, which is supported by brackets is connected to the generator body

U.S. Patent 2198148 also shows a vibration generator with a cylinder rotpr revolving on a cylindrical orbit, the has a smaller diameter than the orbit and is coupled to a motor via a flexible shaft is. The rotor and orbit are via a sun planetary gear tooth system each other in positive engagement. For coupling this freely oscillating vibration generator to a vibratory system, no precautions are taken, and the means by which the rotor can counteract its orbit is fixed, are for high speeds and thus high frequencies with accordingly not suitable for high energy.

In another unbalance vibration generator known from US Pat. No. 22 04472 After all, of the same type, no measures at all are provided, the runner against the orbit to press, so that during operation of external disturbances originating on the vibration system

Acting forces the tooth engagement between drive motor and rotor or between rotor and orbit, which is important for frequency maintenance and phase position, would break, so that under the conditions to which the invention is exposed in operation, significant disturbances occur.

The invention is therefore based on the object of a mechanical unbalance vibration generator of the type described above

In general, the orbit has a circular cross-section and is cylindrical in shape.

The generator according to the invention can be implemented in two different ways: It can be a 5 revolving unbalanced rotor may be present, the diameter of which is smaller than the diameter of a cylindrical orbit in which the rotor revolves; and second, an unbalance ring may be present be about to spin around

design that a cylindrical mandrel rotates even at high frequencies and uni. In both cases

if strong reaction disruptive forces act the rotor always winds the unbalance body a centrifugal force,

rests on the orbit and periodically revolves with the orbital teeth vector. This force can be used in

wheel remains in exact mesh, so that the force vector from the plane of the force vector in any direction

Required adjustments of the unbalance as a periodic, sinusoidal alternating force.

rotors with regard to frequency and phase angle. The first embodiment of the

enter visibly and precisely automatically. Generator is first paid attention.

The solution is done in such a way that the generator is a toTntnr and its orbit in such a way on one another planetary gear and the stationary gear are matched that the generator has a frequency internal gear whose diameter is larger than tion between its input and its 20 that of the planetary gear. The rotor generally has a role that performs at least one output frequency Rotor gear coaxially and opposite the rotor on a mandrel or an axis which consists of the rotatable with this sits on a common axis and emerges in the middle of the planetary gear, is freely rotatable. a stationary track gear with the orbit As I said, the planet gear is with the is coaxial, in which the rotor gear engages, -and 25 fixed internal gear, which is coaxial with the zydabei the width of the teeth of the interlocking Lindrian orbit and right next to it on gears on which is ordered in dynamic circulation conditions, engaged. The role runs on the surroundings common tooth pitch circle slightly below the track, and the planet gear rolls in the Indian Width of the tooth gaps, nenzahnrad from; Describe the role and planet gear

The rotor can have the shape of a ring, 30 so together a circular path, as if they were a single

which surrounds an axis, or it is located as an umpteen rotor. In general, however, takes place between

Role within an orbit in the generator body; the orbit and the roll or the ring and the axes are preferably circular in cross-section and are often cylindrical in shape.

The invention results in an improvement of the known vibration generators with far better ones Decoupling of the drive unit from the generator. The decoupling effect has its cause in

the roller, which rolls on its orbit, and the planet gear rolling in the internal gear, even if only slight relative movement.
The drive unit is usually connected to the input gear via at least one, but preferably via two universal joints.

The periodic output force of the generator occurs as a circular force vector, which is generated by the generator

the frequency increase. The improved building housing on that elastically oscillatable component way of the generator retains the desirable transmission with which the generator housing Properties of the known generators at, namely is connected. When applying the invention is the borrowed high output impedance when excited with low generator generally with an elastic riger impedance, relatively high performance, freely oscillating structures connected, the one full of relaxation Transmission, simplicity and low frequency range. The vibration genes sensitivity, long service life and the slope, rator with rotating mass is from its start the flank of the resonance bell curve tightly driven unit so that its output is halfway to fall into step of the resonance point. frequency falls within this resonance frequency range,

In addition, the translation options are thereby from the generator to the resonant circuit

improved (input frequency of the drive shaft to 5 ° good efficiency transfer vibration energy

Output frequency); the translation factor ins becomes. The generator is therefore exposed to a load.

Fast can be coupled much higher in a simple manner. During the work process, the

be elected than before. Change the impedance of the load, both

The vibration generator according to the invention in the direction of the active component as well as in direction a generator body; in this body 55 the reactive component of the impedance, storage areas represent an orbit; a change in a system of generator and Balancing rotor is used in this orbit in order to in Schwinger with a generator with orbiting to run around her. In addition, at least one with ground during operation is the load impedem Rotor coaxial gear, opposite that on danz, so the frequency changes automatically with it common shaft rotatable, at least one with the 60 and / or the phase position, so that a good energy rotor gear engaged second, fixed transition to the load is maintained. These Stationary gear in the generator body, a high frequency adjustment can be made in a generator frequency drive gear or clutch for the invention with one of the operating frequency of the load Rotor, which is rigidly linked to the rotor gear with a variable speed corresponding to the body and is coaxial with this, and a rotatable 65 follow. The resonance frequency of the entire Schwinres Input gear or a clutch, equalization system can shift, or the umlausig with the orbit and with the rotor drive fende gravity rotor can its relative position on gear in mesh, present. change the orbit (the phase angle), or

10

this can happen both. It can also (when working in the range of the resonance frequency) Adjust changes in the oscillation amplitude. Such changes, often sudden and very appear sharply, make small but significant position corrections between those in engagement Teeth of the spur and internal gears of the generator. It is for the good working of the Generator means that such corrections of the gear teeth are gentle and without sharp acceleration or delay. The load is often not linear, such as B. when drilling or other switching processes, so that non-linear secondary waves occur in the resonant circuit and also cause vibrations in the generator body. These secondary waves act instantaneously the gear teeth back with undesirable acceleration forces. Such conditions can lead to unpleasant irregularities in the generator.

It is a feature of the invention that these unpleasant influences are alleviated so that the operation of the generator becomes gentle.

In view of this feature (as far as the internal gear and the rotor gear are concerned) the Thickness of a tooth on the rotor gear that meshes with the fixed internal gear, not greater, but preferably less than the distance between two adjacent tooth flanks of the internal gear; exactly the same is the thickness of a tooth of the fixed internal gear with the spur-toothed rotor gear is in mesh, not greater, but preferably less than that Tooth flank spacing of adjacent teeth on the spur-toothed rotor gear, with thickness and spacing are measured on the common pitch circle when the generator is in operation.

As a result, the teeth on the two gears are designed so that the successive, im Engaging teeth on these two gears only touch one another with one flank are. You are preferably dimensioned so that under working conditions on at least one side still have a slight distance to the next tooth flank, so that only on one tooth pressure can be exerted on one tooth flank while the second tooth flank is depressurized. It is so to speak of a loose tooth game rather than a fixed one. In practice there is at least one little play between the opposing, non-driving tooth flanks of the face and Internal gears available for dynamic compensation. This is preferably done simply by teeth can also be used between rotor drive gear and input gear.

The invention results in a very effective generator-resonant circuit combination for mechanical vibrations. With the invention it is possible to have the unbalance mass on its orbit with such high frequency to drive that resonance vibrations with her in devices of considerable proportions can be generated. In such cases, part of the device is often used as a resonator educated. With the help of this improvement it is z. B. possible, an elastic rod at its resonance frequency to stimulate expansions and contractions, the resonance frequency being dependent on the speed of propagation depends on the vibration energy in the rod material. The resonance frequency is for most, with normal dimensions in the Technology related arrangements very high, so it means a great advantage that now with With the help of the invention, numerous such oscillatable systems are excited to resonate oscillations can be and that over a long period of time and without falling out of the generator with vibrations particularly high energy can be supplied.

It is also possible to combine two or more identical generators with one another. Very often two generators are used in pairs, those with the same frequency but in opposite directions Circulate direction.

In order to better understand the invention, a brief discussion of basic issues follows from FIG Oscillation theory and the names.

Vibration discussion

The expression "fast vibrations" denotes elastic vibrations, e.g. B. recurring elastic deformations in the longitudinal direction, as a bend, in a circular direction, as a twist or the like, which are generated in an arrangement or by a substance with a propagation speed of its own for this wander through. The vibrations propagate in the longitudinal direction of a body or generate them in a substance or a structure with evenly distributed elasticity and mass constants a longitudinal wave, so speaks longitudinal wave or sound wave transmission. They are also able to oscillate elastically Systems known in which the masses occur essentially concentrated, whereby one then of speaks punctiform constants; Another punctiform constant can be a concentrated, elastic be deformable element, which then has a locally localized spring action, the reciprocal of the

enough that the gear teeth thin and the gaps

between the teeth can be made large so that 55 represents stiffness. Elastic vibration systems

the desired backlash is present in the course of operation are comparable to alternating current oscillating circuits.

This backlash creates the generator-oscillator arrangement freed from destabilizing influences that occur in resonance conditions as a result of changes in the 'load impedance or non-linear Load or the like. Can occur. As has been pointed out, there is a general adaptation to such Influences reached, whereby the load of the gear teeth with the with the oscillation system related energy sources is reduced. Those in engagement with each other Teeth act like an insulator. This training of both distributed and concentrated systems The constants are the mass of the inductivity (of a coil), the elastic spring force a capacitance (capacitor) and the friction or other pure energy loss an ohmic To equate resistance.

As a result, elastic vibration systems are very easy to use with the formulas of electrical engineering too investigate.

The term vibration impedance is of paramount importance in this context. the Vibration impedance is the ratio of the in

a medium occurring vibrational force to the movement caused by it, what also the Corresponds to the ratio of voltage and current. However, the impedance is expressed by other values, also the product of the mean stiffness and the speed of propagation of the elastic Vibration. The transition across a contact area between two media or bodies can cause reflection arise, which is dependent on the impedance differences at the contact surfaces. So is the impedance is also of essential importance for the energy optimization of a vibration system. If the impedances are matched, the transmission of vibrational energy can be great effectively designed.

Resonant circuits can be very effectively designed so that they are able to deliver large forces when equipping them with a high Q factor. This quality factor Q is the quotient of the energy stored per oscillation to the energy consumed within this period. An oscillating circuit with a high quality factor Q is able to store considerable oscillation energy and energy is periodically added to and withdrawn from it. In relation to the resonant circuit sizes, j the quality factor Q is the quotient of the inductive reactance and the resistance. An oscillatable system equipped with a high quality factor Q is able to carry out considerable periodic oscillations.

The impedance in an elastic, oscillatable system is the complex quotient of the alternating force and the linear speed. This corresponds to the impedance in electrical systems. Of the the exact math expression for this impedance is:,

where M is the vibrating mass, C is the elastic spring constant (the reciprocal of the stiffness) and / is the vibration frequency.

The resistance is the real part R of the impedance and represents the energy loss, e.g. due to friction.

The reactance is the imaginary part of the impedance, which is calculated from the difference between the mass reactance and the spring reactance.

The mass reactance is the positive imaginary part of the impedance; he's using inductive reactance electrical circuits comparable.

The elastic spring reactance is the negative imaginary part of the impedance; it is with the capacitive one Reactance of electrical systems comparable.

There is resonance in the oscillating circuit when the reactance (the algebraic Sum of mass and spring reactance) becomes zero. Then the oscillation amplitude is only limited by the resistance and reaches a maximum. Under these conditions there is no energy used to overcome the inertia of mass parts.

Special elastic spring reactances can be introduced into the oscillating circuits, so that the Mass reactances, which are necessarily connected with the elements present in the resonant circuit are not to detune the oscillatable system too far from its resonance frequency, which then a large part of the supplied energy would be used to vibrate these masses offset. For example, the vibration generator itself is equipped with a generator body, which encloses the parts that generate the vibration force; however, this body is with a mass or lazy. This inertial mass could have a detrimental effect as a block impedance occur that are part of the periodically occurring

ίο Force expended in their acceleration and deceleration. Due to an elastically oscillatable structure (spring reactance) of the oscillatable system the effect of this mass (mass reactance) can be counteracted and even tuned in response to resonance will. In the case of resonance, the vibration generator can then use its force impulses without any deduction at the load that forms the resistance part of the impedance.

A resonant circuit can act as a coupling element between one with a high impedance Vibration generator and its load with low impedance for the purpose of impedance matching be inserted, the resonant circuit then serves as a transformer, where both by the effectiveness in the generator area as well as in the work area is designed as inexpensively as possible.

A resonance vibration system is generally used as the source for the vibration energy, which is an oscillatable element (elastic "resonance circuit) together with a Vibration generator with rotating mass (oscillator), the vibration generator with the rotating mass adapted to the resonance part of the system and then the composite system to the Load is adapted.

Such a composite system is more effective and particularly shows when during the work process as conditions change, greater persistence. With such an adapted arrangement the oscillator with the rotating mass can be dragged along by the load conditions, so that he always under his performance even with changed energy consumption due to the load submits favorable conditions. The oscillator automatically changes its phase angle and thus its Power factor when these values change in the impedance of the load.

The vibration generator with rotating mass also adapts to the imaginary part of the impedance during of the work process. For example, if the oscillation system decreases inductance or capacitance the oscillator reacts accordingly. This often happens because the operating frequency of the oscillator is changed automatically by acting back on its drive unit. Expressed differently this means that a change in the imaginary part of the impedance automatically shifts the Causes the resonance value of the entire oscillating circuit. This in turn attracts a frequency change of the vibration generator with rotating mass after it, which its drive unit with a certain Torque loaded. The frequency increase factor of the vibration generator according to the invention has an un- supportive.

In the drawing, various forms of the vibration generator according to the invention are shown. They are described in detail below.

In the F i g. 1 to 7 vibration generators are shown whose drive shaft is coaxial with the orbit runs. These generators can be designed in two different ways: Type 1 is the version with a low transmission factor, in which the frequency of the output oscillation the rotational frequency of the input shaft due to the practically given limitation of the gear wheel sizes and dimensions in a ratio of 1: 5 downwards and 5: 1 upwards, whereas type 2 is the embodiment with a high gear factor, at which the gear ratio of the output frequency the oscillation at the rotational frequency of the wave between the values 2 and theoretically infinite is, the latter in turn limited by the practical dimensioning options of the gears is.

Such vibration generators are either equipped with a roller on the inside a cylindrical orbit, or it has a ring around one in the center of the generator attached, cylindrical dome swirls. The fundamental difference between the two mentioned Types is that with the first, in the F i g. 1 to 4 with a low gear ratio the driving force is applied to the rotor at a point which is the point of contact of the The rotor is diametrically opposed with its orbit, while the second, in the F i g. 5 to 7 The type shown with a high gear ratio delivers the driving force to the rotor at one point which lies on the same side of the orbit center axis as the point of contact of the rotor with this orbit. In both types, the gear train consists of two sets of face-toothed ones and internally toothed wheels, the pitch circle diameter being the diameters of the orbit or the role (the mandrel and the ring) correspond, while the pitch circle diameter of the other Gear set can be varied according to the desired output frequency, this however, are limited in terms of their pitch circle diameter as well as that of the Orbit and the gear set belonging to the roller (the mandrel and the ring).

r _t = pitch circle radius of the gear belonging to the orbit,
r ₂ = pitch circle radius of the gear belonging to the motor,

_{r a} = pitch circle radius of the rotor drive gear, _{r i} = pitch circle radius of the input gear,
5 = Ratio between rotor (roller or ring) revolving around the orbit and input gear rotations. A negative value of this size indicates that the direction of rotation of the roller is opposite to the direction of rotation of the drive gear on the orbit.

The value S ₁ for type 1 of the vibration generator is expressed with the four radii by the following equation:

S ₂ =

- ^r l) (Ti - ^r i)

60

C -

r »r,

2'4

Ί'3

For type 2, the value of S ₂ is clear from the four radii as follows:

If the value for S is known, the input gear set can then be determined for the two types of oscillator when the dimensions of the orbit and the roller are determined.

There are different ways to accommodate the gears in a vibration generator, which is equipped with a revolving roller on a track, so that there are at least three different Types result in:

Arta: The drive power for the reel is fed to it from its ends, and the reel is a massive body;

Artb: The drive power is the role, which is hollow, in its center or in the vicinity of the Center fed by a shaft passing through the center of the roll;

Type c: The drive power is the role, which is a solid body, in its center, but from the outside over an internally toothed gear which surrounds the roller and is coaxial with the orbit.

Similar forms of variation are found in a ring-mandrel arrangement possible, but with the exception that the ring is naturally always hollow.

In the F i g. 1 to 4, a generator of type 1 is shown, the roller on the inside of a cylindrical Orbit expires. The generator has a housing 801, which consists of an intermediate part 811 and two end caps 821 and 831 and in which between the cap 831 and the central part 811 a spacer 841 is inserted, these parts all having a rectangular cross-section, as shown in FIGS. 1 and 2 can be seen. Parts 811 to 841 have bolts 861 and nuts 871 held together. The middle block 811 is penetrated by a bore 881, which another small piece into one end cap 821 and spacer 841 continues as best from FIG. 1 can be seen. In this bore 881 is a cylindrical orbit 891 made of hardened Steel used, in which there is also a cylindrical path bore 901. Between the one end of the orbit cylinder 891 and the inside of the intermediate piece 841 is an intermediate disk 911 inserted. A cylindrical unbalanced rotor 921 made of hardened material is inserted into the bore 901 Steel used, the diameter of which is slightly smaller than the inner diameter of the path bore 901 and its typical dimensions approximately as shown in FIG. 1 correspond to those shown. The role 921 runs in Inside the bore 901, which forms the support surface for the .Rolle, and its end faces are in very close proximity on the one hand to the intermediate disk 911 and on the other hand to the surface of the end cap 821. There can of course be a hardened between the end face of the roller 921 and the end cap 821 Intermediate disk can be inserted.

The unbalanced rotor 921 has a central bore 931 in which, rotatable relative to the roller, a Shaft or axle 941 is inserted, coaxially from the center of a spur-toothed gear 951, the rotor gear, protrudes. The roller 921 forms the rotor together with the shaft 941 and the gear 951 located on it. The gear 951, which is the position-determining gear, has a pitch circle diameter that is substantially

corresponds to the diameter of the roller 921. This gear 951 is with a fixed internal gear, the internal gear of the orbit 961, in engagement, which in the aforementioned intermediate piece 841 is molded. The pitch circle diameter of this internal gear is essentially the same the diameter of orbit hole 901.

In the axial direction, a cup 981 protrudes from the spur gear 951, which is designed as an internally toothed rotor drive gear 991 and meshes with a spur gear 1001 at the end of the drive shaft 1011, the latter being held rotatably in the hub 1021 of the end cap 831 coaxially to the orbit 901 . As shown in the figure, the input gear 1001 is slightly smaller in diameter than the rotor drive gear 991 and with the rotor drive gear 991 in the case of the one shown in FIG. 1 position of the parts to each other on its upper side in engagement. It should be noted that in this position, the rotor ze gear 951 is on the bottom in engagement with the gear of the orbit 961, in other words, at a point which, with respect to the main longitudinal axis of the vibration generator, the point of contact between the rotor drive gear 991 and Input gear 1001 is diametrically opposed. These positional relationships are characteristic of a type 1 generator. When the generator is in operation, the unbalance rotor 921 revolves on the orbit airfoil 901 and is in contact therewith due to its centrifugal force. If the generator is at a standstill or is just beginning to turn, the rotor 921 is pressed against the orbit by conical axle projections 1031 and 1041 connected to one another on the axle 941 and the gear wheel 1001, which is on the other side of the roller by projections 103Γ and 1041 'on the axis 941 and the end cap 821 also happens.

In FIG. 1 shows the radii r _x to r ₄ .

When the generator is in operation, the drive shaft 1011 rotates the input gear 1001, which is connected to the internally toothed Rötor drive gear 991 on one side, see above so that the gear 991 rotates. The rotor gear 951, which is made up of the drive gear 991 consists of one piece, rolls on the inside of the internal gear 961, with which it is in one place is in contact, which is diametrically opposite the point of contact between the gears 991 and 1001, from (the point of contact between the rotor and the orbit is also the point of contact between the gears 991 and 1001 diametrically opposite). The axis 941 and the Gravity rotor 921, which is located on the axis, thus rotate with one another, with the gravity rotor 921 rolls on the inside of the cylindrical support surface 901. The generator is located at full speed, the roller presses sufficiently with the centrifugal force caused by the rotation Pressure against the bearing surface 901, whereby good, non-slip contact is achieved. The rotor 921 runs essentially with on the cylindrical orbit 901 with the face-toothed Gear 951, which rolls in internal gear 961, rotates in unison. However, there is a need given that rotor 921 and gear 951 rotate slightly against each other, this is possible, since the rotor 921 is arranged freely rotatable on the axis 941.

The centrifugal force acts on the generator housing 801 and is made elastic by this on any transmit vibratory device on which the force is to act. About the attachment of the generator housing to be made possible on any device to which the circling output force is transmitted is to be, the generator housing can be designed as desired, such. B. with holes 1091 for Acceptance of machine screws, not shown.

The F i g. 5 and 6 show a modified embodiment of the in FIGS. 1 to 4 shown generator. This generator is largely the same as the one previously described. The rotor gear is However, not connected to a cup-shaped internal gear, but has a coaxial with it spur toothed gear 1121 on. This spur rotor drive gear 1121 is with an internal gear 1131 in engagement, which is molded into a cup 1141 at the end of the drive shaft 1011 is.

This generator works like the generator from FIGS. 1 to 4 with the only but essential one The difference is that the point of contact between the drive and input gears 1121 and 1131 is on the same side of the generator's longitudinal axis as the point of contact of the rotor and the orbit gear 951 or 961, or as of course the rotor 921 and the Orbit area 901 itself. The result of this is that the gear ratio is within the Transmission system can be very high, so that a strong increase in frequency can be achieved with this generator is.

Figure 7 is a side view of Figure 5, but shows a modified embodiment of the teeth of the gear 961. Also located in FIG. 7 the gears 951 and 961 mesh with one another on their upper side, whereas in FIG 5 are shown in a position in which they are in engagement with one another on their underside.

The gear 951 is equipped with special teeth 1201, between the tooth flanks 1211 especially shaped spaces 1221 lie. This gear has a special internal gear 961 in engagement, between its essentially semi-cylindrical teeth 1241 convex grooves 1231 are molded.

In the embodiment shown here, the gear 951 has one tooth less than that Gear 961, so that when teeth are in mesh on one side, the tooth flanks of the teeth on the slide along opposite sides. As a result, the staggered holding mandrels 1031 and 1041 can be omitted.

Another embodiment of the generator according to the invention is shown in FIG. 8 shown; it is one of the generators which, in principle, have already been shown on the basis of FIG. 1 have been described, so that a detailed description is not necessary here.

The main parts of the generator are the generator body 20 and a bushing 28 that defines the orbit for the runner /? represents. The runner is equipped with two face-toothed runner gears 42 and 46, those at the ends of the orbit

13 14

brought internal gears 30/31 in connection or just brought up to speed, and he hen. In this way, the two-seed generator is not exactly in a position to be in wheat of gears on the orbit and on rather the role because of their gravity against the Runner equipped. Orbit presses are conical on the shaft 37

On the rotor there is also an internal gear (rotor-5 mige warts 64 and 65, which against the

drive gear) 48 attached, which with a conical surfaces of truncated cones 66 and 67, which

Input gear 49 at the end of a cylindrical in the end cap 25 or the drive element

Drive assembly 50 molded coaxially to orbit 50, press,

bushing 28 is arranged, is engaged. It is very important that the generator is adequate

The rotor /? consists of a cylindrical roller io is lubricated, and since the possibilities of 32 with an axial bore 34 and is rotatable for lubrication are very diverse, only one axis 36, which passes through the bore 34, is shown a hose coupling screw 70, which is inserted . The axle 36 is in two parts and consists of a closed opening to which a lubricant of an inner shaft 37 with serrated teeth 38 on its hose can be connected. The lubricant outside and a concentrically surrounding medium spreads out inside the generator, and sleeve 39, in the inner surface of which also has a notch, in order to facilitate this expansion, bores are formed with toothing 40, which are toothed 71 in the gear 42 and in part 44 α of the cup 38 is in engagement. In this way, shaft 37-shaped gear 44 are provided. In the drive and sleeve 39, which together form the axis 36, element 50, a pierced mandrel 72 is inserted, protected from mutual rotation, but the parts through which the lubricant to the notches can twist with one another and in axial toothing 54, 55 headed wid. The oil mist can shift direction! Against each other. The axle arrangement escape via outlet openings 73,
opening 36 carries on one end of the sleeve part 39. An essential feature of the invention is the face-toothed gear 42, which can be seen with the internal tooth, that in cases in which the generator gear 30 is in engagement and a pitch circle diameter 25 is difficult Conditions works, ie with water, which is equal to the outer diameter of the high speed or high load (especially heavy roller 32, although this is not absolutely necessary when driving a resonance oscillation system). On the opposite end of the gear teeth of the externally toothed gearwheels axis 36, a cup-shaped part is formed on the shaft 37 and the internal gearwheels 42/30 and 46/31 are integrally formed on the Um-44, in the outer wall 45 of which a frontal 3 ° catch has play, as already stated toothed gear 46 with the same pitch circle diameter. became. With normal tooth dimensioning (involute knife as the gear 42 is incorporated, which th tooth shape) the teeth run when the Gerrit is in operation, the internal gear 31 is in mesh. The generator as a result of the centrifugal force, which occurs at the high wall 45 of the cup-shaped part 44, has frequencies to be generated, with closer flank contact also on its inner side, so that all games in radial 48, which are unilaterally in an external gear 49 are canceled at the direction; In addition, the end of a cylindrical drive body 50 is deformed and the rotor, which, as a result of the centrifugal force, engages with greater force, which is pressed coaxially with the orbit bushing 28 against the orbit bushing, is slightly deformed. The end plate 26 has a reinforced center, but is extremely elastic, so that the central section 26a is formed in which a bore of 4 ° teeth of the gears is unexpectedly deep into the intermediate 52, in which bearings to hold the intervening spaces penetrate the internal gears. Under the cylindrical drive part 50 are used. In these conditions, the teeth are in contact with each other, both the drive part is machined in its outer end section 53 on its front as well as on its rear side and push-notch teeth 54, into the arc-shaped ken like wedges in the spaces between the notch teeth of a drive head 56 at the end of the 45 Teeth of the internal gears, so that they engage as a result of the drive shaft 57, which generate particularly high frictional power sources, such as an electric motor, driven by any strong radial load, which can cause severe heating and die-off. The serrations 54 and 55 can bring about use and failure. In the form described, there is then an angle between there is also no play in the circumferential direction, so the generator axis and the drive axis 57 also allow the oscillator, which works with a resonant circuit while the device is in motion, not to move more car finds. If necessary, the drive shaft 57 can automatically adapt to the changes in load. Universal joints, which are not shown, equipped . These undesirable properties can be due to the. -. Way to prevent the teeth in their

The roller 32 of the rotor R sits on the outside 55 thickness to be dimensioned so that they are not wider than the sleeve 39 rotatable, and to reduce the contact surface than the distance between two adjacent teeth and thus the sliding friction to flank the associated internal gear and that Reduce, the sleeve 39 preferably also has the thickness of the teeth of the internal gear center on a rib 60 on which the roller rests with its not larger than the gap between two adjacent inner bores. The sliding friction teeth on the external gearwheel with full vibration between the end faces of the roller 32 and taking into account the centrifugal force. In this way, the gearwheel 42 on the one hand and the part 44 α of the enough that cup-shaped shaft extension 44 on the other hand comes into contact and preferably reduce the other, if these end faces of the roller 32 are formed from the neighboring surface of the other tooth, that it has with the parts 42 and 44 α only 65 of a small distance. They were connected to each other over a small ring area. Most successes achieved with the fact that between the back to press the roller on one side against the orbit flank of each tooth of the external gear and, when the generator is at rest, to press the front flank of the following tooth of the inner gear

There was a slight clearance between the gear wheel under operating conditions.

This means, of course, that the gaps are selected to be somewhat larger in the idle state, so that they are still present in the operating state when the centrifugal load presses the teeth of the internal gear between the teeth of the external gear. The outward displacement of the teeth of the internal gear is at the first moment when the generator starts to run, still limited by the contact of the roller 32 with the orbit 28, but this radial outward displacement decreases as a result of the tolerances in the arrangement and the deformation the role under the centrifugal force continues to increase under full working conditions. In FIG. 9 shows the preferred arrangement at Lauf in a somewhat exaggerated representation, a gap χ being present between the two teeth t and i . This is achieved in that when the generator is at a standstill, the teeth intermesh even less and leave an even larger gap χ between them. The teeth then penetrate further between one another under working conditions, but their shape is dimensioned from the outset in such a way that a gap * remains between the teeth, as shown in FIG. 9. Fig. 10 shows an also exaggerated picture of a somewhat modified form according to the invention; here a more common, ie wider, tooth is used, which, however, due to the appropriate dimensioning of the gravity roller and the orbit, penetrates less far between the outer teeth than is shown in FIG. 9 is the case. This means that there is also a gap χ here during the run.

In FIG. 11 is another embodiment of the .Generator according to type 1 shown. The generator has a housing 80 with two orbit rings 88 on both sides of a middle ring 89, in which the latter an internal gear 90 is located. The individual gears are arranged in the center plane of the generator, and the rotor is equipped with a pair of rollers.

On the drive shaft 94, a drive gear 95 is attached, which is on one side with a slightly larger internal rotor drive gear 96 is engaged. The internal gear 96 is located on the Inner surface of a cylindrical gear ring 97, the cylinder outer surface with teeth of a gear 98, which mesh on one side with a 5 "internal gear 90 of the orbit.

A pair of unbalance rollers 100 with coaxial inner bores 101 surround the drive shaft 94 and lie on either side of the input gear 95. These rollers 100 roll on the inner surface of the orbit rings 88 from. Your sides facing the ring 97 and the gear 95 are offset, like this is indicated at 102 so that it can be rotated, i.e. rotated. H. Slidably displaceable, sit within the ring 97. The rollers 100, the gear wheel 97 and the external gear wheel 98 are coaxial with one another. Of the The outer diameter of the rollers 100 is approximately equal to the pitch circle diameter of the gear wheel 98.

The diameter of the gear 98 is slightly smaller than the pitch circle diameter of the internal gear 90. When using involute teeth, the gears can only mesh with one another when they are moved parallel to their axis, however, they are once with each other when engaged, they can no longer be separated from one another in the radial direction. That has to The result that the gear 98 rolls in the internal gear without it being able to separate from this, so that on guide elements for this gear, such as the elements 1031/1041 in the generator according to FIG. 1 can be dispensed with.

In operation, the rollers 100 can rotate slowly with respect to the gear ring 97, and thus also opposite the gear 98 which meshes with the internal gear 90; this is made possible by the Slidable connection of the rollers 100 on the ring 97 allows.

For high loads or special conditions with resonance of the connected oscillating circuit the generator gear 98 is also provided with teeth that when they mesh between the teeth of the internal gear 90, even when running, a gap between the back flank of each tooth of the Release gear 98 and the leading edge of the following tooth of the inner gear.

Another embodiment of this type of generator, but which is still further elaborated, is shown in Figs. Only those parts are described here in which this example differs from the already described differs. In the socket 116 are two cylindrical, in the axial direction with a press fit Separate, hardened orbit rings 120 are used, between which an internal orbit gear 122 is inserted, the pitch circle diameter of which is approximately the inner diameter of the orbit rings 120 corresponds. The internal gear 122 is non-rotatably connected to the bush 116 by means of a key, as shown at 123. The rotor consists of two cylindrical rollers 125 with large Mass and a gear sleeve 126 on which they are rotatably seated with respect to this. The gear sleeve 126 carries a rotor gear 128 in its center, which sits between the two rollers 125 and with the internal gear 122 is engaged. The pitch circle diameter of this rotor gear 128 is approximately the same the diameter of the rollers 125.

The gear sleeve 126 carries two internal gears as rotor drive gears on its inside 130, which are in mesh with smaller-diameter gears 132 on the drive shaft 133, soft rotates coaxially with the cylindrical orbit 120.

Gear 128 and heavy rollers 125 must be against internal gear 122 and orbit rings, respectively 120 can be printed when the generator is rotated slowly. In addition For this purpose, the central section of the drive shaft 133 is provided with a cylindrical surface 160 which unrolls a cylindrical roller 161, which has stub axles protruding on both sides, which carry needle bearings 162 on which two rollers 163 are rotatably mounted, these rollers with their Circumferential surfaces on the inside of the gear sleeve 126 run. Between the rollers 163 and the There is a clearance gap between shaft 133, as well as between roller 161 and gear sleeve 126. Thus, this roller arrangement holds the gear sleeve 126 on an eccentric path with the shaft 133, see above that the heavy rollers 125 on the gear sleeve are constantly against the inner surface of the orbit rings 120 must be pressed.

Here, too, there is backlash between the teeth of gear 128 and internal gear 122 kept under running when particularly difficult working conditions are to be expected.

Embodiments of the type 2 generator will now be described, with which more powerful Frequency increase can be achieved than with type 1 generators. These generators too can be equipped with corresponding backlash in the circumferential direction, as already shown in Connection with the generators according to type 1 was shown. In Fig. 14, with the number 200 very generally the generator housing with end faces 201 and 202 referred to, in which a transverse bore 204 is introduced from the end face 201 to close to the other end face 202, whereas from on the second side a counterbore 206 is made up to the bore 204, so that a support shoulder 207 is created. An end plate 208 is screwed against the end face 202 of the housing 200, which s ° is equipped with a hub part 209, in the bearing and other parts to be described later are used.

In the middle section of the bore 204, a sleeve 210 is used, which is press fit on its inside two spaced apart, hardened orbit rings 212 receives, between which there is an internal gear 214 which is secured against rotation with respect to the sleeve 210 with a wedge 215 is set. The orbit rings 212 and the sleeve 210 are between two side rings 217 and 217

218, the latter pressing against the shoulder 207, while the former by a retaining ring

219, which by means of screw bolts 220, which penetrate an end plate 229 and the retaining ring 219 and in the housing are screwed in and pressed against the ring 217. The holes 224 in the immediate Proximity of the surface of the orbits make oil or oil mist easily can escape between the heavy rollers and the orbit rings 212.

the already mentioned hub 209 of the end plate contains a bearing arrangement 225 in which a serrated Sleeve 226 rotates coaxially with orbit 212. The one protruding into the generator housing inner end of this socket is designed as an input gear 228, which has a smaller diameter Rotor gear 229 is engaged. The rotor gear 229 is on one end of a sleeve 230 of an axle arrangement, which is designated as a whole by 231. This axis arrangement also contains an external gear sleeve 232; the sleeves 230 and 232 can be axially opposite one another move, but are prevented by a spline 234 from opposing each other twist. The gear sleeve 232 rests with one end on the gear 229 and is on the opposite End clamped by a flange ring 235 of a cylindrical retaining bolt 236, the sliding is inserted into the sleeve 230. The bolt 236 is penetrated by a screw 238, which in the hub of gear 229 is screwed in, thereby holding the entire assembly together will. The hub of the gear 229 continues to the outside in a protrusion 239 on her The outer surface of a further lug 228 a molded into the hub of the internal gear 228 is in contact will. With the help of these two lugs, the rollers 242 are pressed against the orbit rings 212, when the generator has stopped or is just starting to turn.

The gear sleeve 232 is equipped with a rotor gear 240 in its center, the diameter of which is slightly smaller than the orbit internal gear 214 with which it is engaged. The roles 242 are rotatably mounted on the gear sleeve 232, on both sides of the gear 240, so that they orbiting on the orbit rings 212. The input internal gear 228 and the rotor drive gear 229 are in mesh with one another on the same side of the generator center axis as the rotor gear 240 and orbit gear 214. This arrangement is similar to that of the previous ones in contrast to the generators described.

The pitch circle diameter of the internal gear 214 is preferably equal to the internal diameter of the orbit 212, while the pitch circle diameter of the rotor gear 240 is equal to the outer diameter of the heavy rollers 242 is. Whenever the expected load is very high, you should the dimensions and shape of the gear teeth are chosen so that even at high Centrifugal force is the force caused by the rollers and internal gear 214 from the orbit fingers 212 is recorded.

The gear sleeve 226 itself is via the spline 243, which is via arcuate spline teeth

244 of the drive end of the drive shaft 245 is driven in rotation, the drive shaft 245 is driven by any power source. The end cap 246 is on the Front face of the hub 209 fastens and holds the bearings 225, while also in an annular groove a seal 247 is inserted, one of which is the drive shaft

245 surrounding sleeve 248 is sealed to the outside.

Different running between the rollers 242 and the roller gear 240 can be achieved by relative movement be balanced between the rollers and the hub 232. During operation acts on the generator housing 200 a rotating force, which of course acts on all parts that are connected to the housing are, also acts. The forces are symmetrical with respect to the generator center plane distributed. The generator is therefore suitable for delivering very high output forces.

In FIG. 15 shows a gear arrangement including a reduction gear between the input shaft and generator. The generator is of type 2. The generator housing 250 is divided in its center into two halves 250 α and 250 b , which are equipped with a mutually coaxial bore 251 and 252 with orbit sleeves 253 inserted therein. The two housing halves 250 a and 250 b are provided from their common center plane concentrically to the orbit bore 251 with further bores, so that they contain an inner cavity 255 of cylindrical shape for receiving certain gears. The cavity 255 continues at its upper end, as indicated at 256, this part of the cavity being located in an extension 257 of the housing which receives the reduction gear.

The input gear is labeled 260 and is in the center of the housing cavity 255, i.e. in the center of the generator. For that purpose it works

Ring gear 260 on a ball bearing 262 of large diameter with preferably small balls, wherein the outer ring of the ball bearing 262 is held in a cylindrical flange 264 which is attached to a

Gear 302 located on the shaft is engaged, and the inner surface 307 of the ring 304 next to the internal gear 306 has a diameter that is approximately that of the pitch circle diameter of the inner tooth

vibration displaced on the body 301 and thus on any device with which this body is connected.

■ In the F i g. 17 shows a similar ring mandrel generator, but in the type 2 version. A shaft 320 protruding from an elastically oscillatable body 321 is on its outer surface End equipped with a toothing 322. Around

Ring 265 and two corresponding to a ring pair 265, 266 straight 306. The surface 307 runs on the listening rings with internal toothing molded cylindrical surface of the shaft 300 um, while the is. The pitch circle diameter of the internal gears gear 306 is on the gear 302, which with 265 and 266 correspond approximately to the inner diameter of the shaft 300 is connected, rolls off. The shape and ser of the orbit sleeves 253. These internal gears- the dimensions of the teeth of the gears are like this of the 265 and 266 are chosen with slightly smaller rotor teeth that for the teeth of the gear 302 in the Gears 270 engaged, the gevon on the inner ends of the gaps of the gear 306 in the axial direction Gear sleeves 271 are attached, which ensures that there is no clearance.

Represent the outer parts of an Aohs arrangement 272. The ring 304 sits on a cup base 308

inner parts of this axle arrangement are shafts which are coaxial with a stub shaft with the rotoran-274, the drive gear 310 protrudes in the sleeves 271 so as to be slidable in the axial direction. The gear 310 are used, which are, however, against each other by a key in turn with an internal gear 312 in a wedge toothing, which is indicated at 276, against handle, the axis of which is aligned with the shaft 300 and Rotating against each other are secured. The shaft that is driven by the drive shaft 314. 274 stand on either side of a rotor drive gear. In operation, shaft 314 drives the input gear 278, which is in the space between the two-wheel 312, so that the rotor drive gear the rotor gears 270 is, the gear 310 rotates and with it together the cup base 278 meshed with input internal gear 260 308 of internal gear 306. The rotor gear is. then rolls on orbit gear 302

The input internal gear 260 is through a, and the ring 304 swirls around the shaft 300 and the bearing 262 encompassing, radial wall with the * 5 generates a centrifugal force that is connected to the shaft gear 280, which acts with the pinion 281 300 . The shaft 300 is thus connected to a Taumeide transmission input. The pinion sits
on a shaft 282 which is held in bearings 284.
The orbital caves are through on both sides
End plates 286 completed, which at the Ge 3 °
housing halves 250 α and 250 b are screwed and
V-shaped annular channels 288, in which conical lugs 290 at the ends of the shafts 274
be guided.

The mode of operation corresponds essentially to that of this gearwheel and the adjacent surface of the nigen of the models already presented, with the axis 320 rotating a heavy ring which has an input power via the shaft 282 and the meshing teeth as the rotor gearwheel 324; diebeindlichen gears 281 and 280 of the center plane ser ring corresponds exactly to the heavy ring 304 of the generator and is thus supplied to the internal gear 306 according to FIG. The input gear 40 324 is molded onto a cup base 325, from which the rotor drive gear 278 rotates, chemically opposite the ring, a concentric internal gear 324 with which the rotor gears 270 and the roller 324 are also rotated so that on that stands out. A rotating force acts with the internal gear 326 of the input generator housing 250. gear wheel 328 in engagement, the diameter of which is somewhat. The gear wheel 278 is in this embodiment 45 smaller than that of the internal gear and which is fixed to a relatively large size with respect to the internal gear of a drive shaft 329, which is connected to the 260, which leads to a considerable increase in frequency
leads. A relatively small input gear
281 works on a gear 280 with large

Diameter; such an arrangement is the internal gear 324 via an internal gear 326 for a 5 ° Energy supply to the input shaft is driven with high, which is its drive from a Speed suitable. Spur gear 328 experiences on a shaft 329, which with the

There are now two vibration generators with axis 320 running coaxially. This becomes the common one Ring-mandrel arrangement, namely one after the generator according to FIG. 17 to a generator after Type 1 and one according to type 2 are described, whereby to- 55 Type 2, whose frequency translation factor is higher next may be the generator shown in FIG. 16.

is described according to type 1. At 300 there is a wave. In FIGS. 18 to 25 the different ones

denotes, which emerges from a partially illustrated, ela translation options of the individual generator table oscillatable body 301, which is shown in an overview. There are two more likely to vibrate. On the ^{60 generators shown with outer orbits at the end of this shaft 300, an orbital gear wheel} and rollers and two generators with a ring 302 are fastened, the pitch circle diameter of which in a we-mandrel arrangement, and this for each type of generator, is essentially the diameter of the shaft 300. so that together there are eight generators, speaks. A vortex ring 304 is fitted onto the shaft. The main difference is that it is replaced so that it can rotate about shaft 300. ⁶ 5th version, which has a small transmission factor. The ring 304 has a slightly larger diameter, the driving force of the ring or the roller. ser on than the shaft 300. It is supplied with an inner rotor at a point which, with respect to the gate gear 306, which is on the axis of the orbit, the point of contact between

Axis 320 is coaxial.

The operation is exactly the same as that of the generator of FIG. 16, with the exception that

Ring or roller and orbit are diametrically opposite, whereas in the second version with high transmission factor the driving force of the ring or the roller on the same side of the axis is supplied on which the ring or roller is in contact with the orbit.

FIGS. 18 and 19 show a generator with a roller revolving in a circular path, the input gear of which is a spur gear. is; the two gear sets (orbit gear rj / rotor gear r ₂ and rotor _{drive gear r 3} / input _{gear r 4} ) mesh with each other at points which are opposite to each other with respect to the central axis.

The F i g. 22 and 23 also relate to a roller orbit arrangement in which the input gear is an internal gear; the two gear sets are connected to each other at points in the Engagement that lie on the same side with respect to the central axis.

Figures 20 and 21 show a ring-mandrel-arrangement, whose input gear is an internal gear; the two gear sets are with respect to the central axis engaged with each other on the same side.

In the F i g. 24 and 25 a ring-mandrel arrangement is shown, the input gear of which is a spur gear; the two gear sets are in mesh with one another at points which are mutually related with respect to the central axis opposite.

From the description it appears that the generators shown in FIGS. 8 and 11 not only Generators of type 1 are, rather, generators as they are in the illustration according to FIG. 18 are shown. The first generator mentioned has a speed ratio of about 2, the the second of about 1: 3. The type 2 generator according to FIG. 14 translates the frequency roughly in proportion 7: 1. The generator according to FIG. 15, which is also a type 2 generator, is reduced in size Input gear initially the speed in the ratio 2: 1, whereas the transmission ratio of The input gear is measured at about 1:30 a.m., resulting in a total gear ratio of 1:15 quickly results. A very strong increase in frequency can thus be achieved. In this It should also be mentioned that in type 2 generators, the frequency transformation ratio approaches infinity when the internal gear 260 has a diameter that is close to the diameter of the internal gears 265 and 266.

In addition 9 sheets of drawings

Claims (7)

Patent claims: 1. Mechanical unbalance vibration generator for generating elastic body vibrations, which consists of a generator body in which there is a bearing surface forming the orbit for an unbalance rotor body, while a drive coupling is firmly connected to the unbalance rotor body and a rotatable input coupling between the drive coupling and the The drive motor of the generator is switched on, characterized in that the generator rotor and its orbit are matched to one another in such a way that the generator carries out a frequency increase between its input and output frequency, with at least one rotor gear (951) being coaxial and opposite to the rotor (921 ) rotatably sits on this on a common axis ^ao (941) and a stationary track gear (961) is coaxial with the orbit (901)) in which the rotor gear (9Sl) engages, and the width of the teeth of the intermeshing gears on the at dynamic circulation - * 5 conditions common tooth pitch circle is slightly below the width of the tooth gaps. 2. Vibration generator according to claim 1, characterized in that the rotor (921), we! - ' rather rolls on the orbit (991), has a smaller outer diameter than the diameter of the orbit, the rotor gear (951) is a planetary gear and the Orbit gear (961) as an internal gear mii larger diameter surrounds the planetary gear (951), and the rotor drive gear (911) is an internal gear and the input gear (1001) is a spur gear, which is connected to the internal gear is engaged on a line that is relative to the Umlaufbalinachss of the line of contact between the rotor (921) and the orbit (901) is opposite (Fig. 1). 3. Vibration generator according to claim 1, characterized in that the rotor (921), which rolls on the orbit (901), has a smaller outer diameter than the diameter of the orbit, the rotor gear (9Sl) is a planetary gear and that Orbit gear (961) as an internal gear with a larger diameter, the planetary gear (951) surrounds and the rotor drive gear (1121) a spur gear and the input gear (1131) is an internal gear that meshes with the spur gear on a line that is relative to the axis of rotation is on the same side as the contact line of the rotor (921) with orbit (901) (Fig. 5). 4. Vibration generator according to claim 2 or 3, characterized in that the rotor has a freely _{rotatable roller (921) around a mandrel (941) which protrudes in the axis So direction VOm 1} planet gear (951). 5. Vibration generator according to claim 4, characterized in that the mandrel (36) has a Sleeve (39) which surrounds an inner shaft (37) concentrically and with the shaft (37) via a Splines (38/49) is connected (Fig. 8). 6. Vibration generator according to one of the preceding claims, characterized in that the rotor on at least one side with a lug located on its axis (1031; 64, 65) and the generator body on at least one side with a second lug located on its axis (1041 ; 66, 67), both of which are preferably conical in outline. 7. Vibration generator according to one of the preceding claims, characterized in that the tooth thickness of the teeth (t) of a spur gear engaging in an internally toothed gear is not larger and preferably smaller than the distance between the tooth flanks of the teeth (i) of the internal gear and the tooth thickness of the Teeth (z) of the internal gear is not larger and preferably smaller than the distance between the tooth flanks of the spur gear teeth (f), the tooth thickness and the distances being measured on the pitch circles which coincide with the working conditions.