DE1577072A1 - Method and device for producing a press fit - Google Patents

Description

Method and apparatus for making an interference fit The invention relates generally to the movement of two parts against each other along a common Contact surface (the sliding of two parts connected with a tight fit), whereby the Frictional force occurring at rest is great and must be overcome in order to achieve the To enable or facilitate relative movement. 'E.g. is at an embodiment of the invention a fast vibration generating machine present, with the help of which a bushing with a press fit in a hole leading to the Purpose in another machine part, such as a casting, is provided, press-fitted with the two parts having dimensions that result in an interference fit. In more general terms, 4 it often arises when assembling machine parts and the like. If an accurate and permanent connection is required that the individual parts be dimensioned so that their seat is too tight for them to be put together without difficulty could be so that they have to be pressed into one another with the application of force. It is Z. B. customary to slightly oversize bearing bushes so that they only pressed with considerable force into the bores of the receiving machine parts can be. Other areas of application are, without limiting the invention, pressing in a wedge, pressing on a cap, pushing a part into a groove, the insertion of an intermediate plate between two surfaces, a bolt in a bore, the pressing of a gear onto a shaft and the pressing in of iron cylinder liners in an aluminum engine block as well as the installation of conical parts, i.e. the entire area of connections in which with friction, Press fit dimensions or other seizure force worked will and that either with one of these measures alone or with several together. Of the For the sake of simplicity, the term friction mount or friction connection will always be used in the following spoken.

The main feature of the invention is therefore to be seen in the fact that two parts be joined together with an interference fit with their surfaces in contact slide against each other by adding vibrational energy to one or both parts, so that elastic vibrations at the contact surface in one or both parts are caused 'and thus the sliding is facilitated. An important consideration is the reflection of the vibration energy on the contact surface, which increases the size the friction is influenced.

The invention uses a number of principles of vibration theory, and to understand the basics of the theory of vibrations, which are used in the invention, To clarify, an explanation of these principles is now given.

When found, "elastic vibrations" mean rhythmic, elastic Deformations such as longitudinal vibrations, bending vibrations, circular movements or Torsional vibrations, etc. that are produced in a particular structure be or move through a medium with a certain speed of propagation spread out, whereby the frequency range in question is more than the frequency range of human hearing. In vibration systems with a few, concentrated ones Oscillating circuit sizes that are occasionally used and that will be discussed later elastic vibrations cannot propagate. In the mostly request Coming vibration systems, however, the vibrations spread with a certain Speed of propagation through the elastic media. When the vibrations Spread lengthways or in a medium that has evenly distributed constants like the modulus of elasticity and the mass or density, a longitudinal oscillation generate, is spoken of a vibration transmission. The description The mathematical formulas applied to the operations apply regardless of the amount of frequency, and the science concerned with such processes becomes vibration-free called. There are also oscillation systems in which the influences of density or let it appear concentrated at individual points, so that at one Point concentrated constants is spoken; can also be an elastically deformable Element can be concentrated at one point as such a point-like constant, so that the effect of their elasticity or stiffness on one Point focused. Fortunately, the elastic constants and their effects in the vibration systems in question with the constants and processes in Comparable to alternating current oscillating circuits. Both in vibration systems with concentrated Sizes as well as those with distributed sizes, the mass corresponds to an inductance (a coil); the elasticity of a capacitance (capacitor); the friction or purer Loss of energy in a resistor. In all applications of vibrations according to Invention it concerns stationary vibrations with a fixed amplitude value in contrast, for example, to decaying vibrations, such as those caused by impacts, e.g. hammer blows, go out. Because of the above-mentioned comparability, the elastic vibration systems with their masses, stiffness and their energy consumption as well as the vibration transmission properties are represented by equivalent circuit diagrams in which the individual functions are represented by known electrical formulas expressed, considered, modified the quantities and can be examined quantitatively. It is important to note; that for the transmission of vibrational energy into the contact surface or work zone between the two parts that are to be moved against each other, the peculiarities the elastic vibrations are necessary for the invention to take effect can. There are already other proposals known in which the individual parts be moved as a whole. However, such an approach does not have the advantages associated with the application of elastic vibrations according to the invention. Because the elastic vibrations from the mass and the elastic properties of the system to the same extent as the alternating current of an electrical oscillating circuit recognized by the inductance and capacitance and this can be mechanical Resonant circuits of greater efficiency can be built. The introduction of vibration impedance is of particular importance for understanding. The impedance is the ratio from the force of an oscillation to the resulting movement, comparable to the quotient of voltage and current. On the other hand, the impedance is also that product from the density of the medium and the rate of spread c the elastic oscillation. In the invention it is important to adjust the impedance to look at the ends, e.g. at the contact surface. When transmitting vibrational energy reflection can occur between two different media on a contact surface, which arises from the difference in impedances at the contact surface. Through this strong relative movement can occur on the contact surface, which is an advantage if there is a large friction coefficient of rest between the contact surfaces. The value the impedance is also important when considering optimization. If the impedance values are brought closer to each other, the transmission of vibrational energy is special effective. Vibrational energy of very high frequencies can affect the molecular or the crystalline structure of the oscillating system. Also arise at very high frequencies high acceleration values that are around 100,000 times greater than the acceleration due to gravity. That has to do with the fact that the acceleration with the square of the Frequency increases. By taking advantage of this dependency the acceleration from the square of the frequency can be achieved with the help of the oscillation system very great forces are exerted. The vibration system according to the invention is used such 'great forces and great total energy by using a vibration generator as disclosed in U.S. Patent 2,960,314. One of those Generator is a simple mechanical device. When using such a A vibration generator in the vibration system according to the invention is obtained particularly simple and cheap construction. Such a generator also offers the advantage that it adjusts to the resonance frequency of the oscillating circuit system and works in their vicinity, generally just below the resonance peak value, so that a considerable amplification of the vibrations occurs as a result of the resonance. Another feature of such oscillating circuits is that they are able to to store great forces if they have a high figure of merit. The quality factor is the ratio of the stored energy of an oscillation to the energy consumed Energy of a vibration. In other words, a vibrational system can do one has a high quality factor Q, on average, a large value of vibration energy save, with a certain, constant flow of energy must flow. The quality factor 6 @ is a numerical value for each resonant circuit from the Determine the ratio of the inductive reactance to the resistance value. With a high Resonant circuits equipped with a quality factor carry out considerable oscillatory movements.

It is of particular value to provide sufficiently excess capacitive heactance in such oscillating circuits so that the moment of inertia of necessarily added masses does not have an adverse effect on the operation of the oscillation system. For example, a vibration generator as it is generally used in the invention has a housing or a support structure in which the devices with the aid of which the alternating force is generated are accommodated. Such a support structure albeit has a low mass or an inertia torque. The moment of inertia can have a disadvantageous effect as it absorbs force and acts as a block impedance2; which consumes part of the alternating force for its own acceleration and deceleration. By using elastically oscillating components in the system, this effect of the mass and the associated mass reactance at resonance is counteracted by the opposite effect of the elastic reactance, if there is sufficient capacitance (elastic reactance) in the resonant circuit, through which the block impedance at the resonance frequency is tuned so that the alternating force, which is generated by the vibration generator, is fully effective for the work. In the following, the method according to the invention will now be considered again and, by way of example, the pressing of a bearing bush into a bore of a cast part with a press fit. This can be done in such a way that a hydraulic force is used to press on the bearing bush and at the same time either the bush or the casting Vibrations occur. There are many types of vibration possible, perhaps the simplest being the longitudinal vibration of the bushing with respect to the bore. The rest value of the friction is thereby switched off. Occasionally it happens that the effect of the cyclic contraction of the bushing also helps to facilitate the driving of the bushing. Many modifications are possible within the scope of the invention, some of which are reproduced here. However, if the bushing is excited to vibrate longitudinally, it is comparatively easy to insert it into the hole with a press fit. The supply of hydraulic pressure in the longitudinal direction of the bushing and at the same time the excitation to longitudinal vibrations can be carried out in such a way that a hydraulic ram engages two vibration nodes of a steel girder which lies transversely to the arrangement and in which bending vibrations are generated with the help of one or more vibration generators @ The steel girder is connected to the bearing bush in its center point, which oscillates transversely to its direction of extension, or slightly next to it, depending on which matching impedance or which oscillation amplitude is selected, so that the vibrations of the girder are transmitted to the bearing bush. By pre-printing the hydraulic ram, the vibrating carrier is also pre-pressed and the bearing bush, which vibrates in itself, is pressed into the bore of the casting. A special feature and a special advantage of generating seizure seats with the aid of rapid vibrations is to be seen in the fact that the press fit is stronger than one which is produced in a known manner. During the entire time during which the parts are pushed into one another, vibration energy must be supplied so that the parts cannot seize in an intermediate position, after which it is no longer possible to move them any further. A certain form of the method is that vibration energy of such strength and vibration amplitude is supplied that the dimensional changes occurring in the rhythm of the vibrations of one or both parts are so great that the press fit present in the rest state is in a sliding fit during part of an oscillation transformed so that the parts can be pushed together more easily. It is therefore the object of the invention to supply the area of the surfaces sliding into one another with vibration energy of such magnitude that a result as mentioned above is achieved. According to a further advantageous embodiment of the invention, the friction between two or more parts in contact is reduced in that vibrations of different amplitudes and / or phase positions are fed to them by giving the parts to be joined different impedance values. This condition can already be achieved in that the parts have different dimensions or consist of different materials. However, vibrations of different amplitudes or phase positions of the touching parts can also be generated by supplying the vibration energy at a specific point and with such a frequency that vibrations of different amplitudes develop and / or propagate. According to a further embodiment of the invention, different vibrations can be generated in the parts in contact with one another by utilizing the different damping properties in the material and by conveying the vibration energy to one or the other part over a longer or more strongly damped path. In a certain embodiment according to the invention, one of the two parts is therefore supplied with the vibrational energy through the other. The above-mentioned embodiment of the invention will now be discussed in more detail, in which a pressure ram of a hydraulic press is used. The vibrational energy is fed to the system between the pressure ram of the press and the part that is acted upon by the press. The implementation of the invention has proven to be very advantageous if the vibration energy is supplied at such a point and at such a frequency that the two parts to be pressed into one another are supplied with vibrations of different types and different speeds of movement. For example, vibrations can be supplied to one part, which act mainly radially to the bore, while the other part mainly carries out bending vibrations or mainly longitudinal vibrations. It is a feature of the invention that the friction is reduced as a result of the different propagation speeds of the different vibrations in the individual parts. It is therefore an object of the invention to reduce the force required to press fit two parts into one another by means of elastic vibrations which are not in phase with one another and which are applied to the two parts. A modification of the method according to the invention can be seen in the fact that the two parts to be pressed into one another vibrational energy is supplied, which originally generates the same vibrations, but that the speed of propagation of the elastic vibrations depends on the spatial dimensions of the two parts. Flexural vibrations and those that act in the circumferential direction are particularly suitable for this embodiment of the invention. The expression "elastic vibrations" is not intended to limit the invention to the transmission and propagation of vibrations, since in certain applications it is also used in vibration systems with concentrated constants. The propagation speed of vibrations is given by the formula c = f @ 1, where c is the propagation speed, f is the vibration frequency and A is the corresponding wavelength, the wavelength depending on the structure of the corresponding part. A very important embodiment of the invention makes use of the phenomenon of resonance, whereby the sliding friction between the two parts to be joined is caused by a special type of relative movement. Resonance can be generated either in one or in both parts . The invention is thus also characterized in that a frequency profile is selected which includes a specific frequency at which one of the parts is excited to self-oscillate. Another feature of the invention can be seen in the fact that frequencies are used at which one part acts more as an inductance, the other more as a capacitance "so that vibrations of different phase positions occur on their contact surface, whereby the sliding friction is reduced The following description of exemplary embodiments with reference to the figures of the drawing will further explain the invention. Figs. 1 and 2 show a device with the help of which Borehole samples from an earth borehole be taken; Fig. 3 is a longitudinal section along the line 3-3 in Figures 1 and 2; FIG. 4 is a section along line 4-4 of FIG Fig. 2; FIG. 5 shows a section along line 5-5 in FIG Fig. 4; 6 shows the diagram of a half-wave oscillation, as in the sample tube according to FIG is produced; 7 is a section along line 7-7 in FIG Fig. 9, which shows a preferred embodiment form of the invention and in the the diagram of a bending vibration is drawn; Fig. A horizontal section according to 8-t3 of Fig. 7; 9 is a section along the line 9-9 in FIG Fig. 7; 10 shows a section of an oscillatable Carrier according to FIG. 7 in an enlarged Scale; Fig.l0a the middle section of the vibratable Carrier from Fig. 7 in an enlarged scale stab together with the adapter and the already pressed workpieces; and 11 shows a cross section along the line 11-11 in Fig. 10. FIGS. 1-5 show an application form of the invention in which elongate parts are pushed into one another in close contact with their side walls. The elastic vibrations are transmitted in such a way that a vibration generator is rigidly coupled to the pipe to be driven. Preferably, a standing longitudinal wave is generated in the part to be driven, specifically, if possible, a half-wave oscillation, as shown in FIG. N at st in the form of a diagram. This is a method with high impedance, because pe,, the oscillation impedance, is a maximum here. This type is particularly suitable for driving long shafts and tubes, which closely surround each other with their contact surfaces, into one another over greater distances, because when using the method with such a large impedance, the vibrations are particularly energetic and are not attenuated much. In addition, a certain elastic effect is achieved through the longitudinal oscillation, through which the circumferential dimensions change in the rhythm of the oscillations, especially in the area of the oscillation nodes. In the particular example shown here, a pipe is driven into a deep borehole in an earth .material, generally rock, which tightly encloses this pipe. However, it is also possible to proceed in the same way if a long shaft is to be pressed into a bore, a bushing or the like, which surrounds the shaft in a tightly fitting manner. Figures 1 and 2 together show a series of individual parts that are sunk on a rope 43 into a hole in the earth; the rope encloses an electrical line via which an electrical drive motor 41 is supplied with the required energy. The motor 41 can be any submersible electric motor, and its individual parts do not need to be explained further here. At the lower end of the arrangement shown in FIGS. 1 and 2 there is a thin-walled tube with a wall thickness of preferably 3 mm and an outer diameter of about 125 mm and a length of about 18 m. At the upper end of the tube 45, an internally threaded connection piece 47 is attached, which is screwed to a threaded pin 48 at the lower end of the vibration generator 49. The vibration generator 49 is designed in such a way that it generates longitudinal vibrations, torsional vibrations or also bending vibrations, depending on how the unbalanced bodies in the generator are set in phase with one another, and these vibrations are transmitted to the pipe 45 by the generator. In the example, longitudinal vibrations are used, and a vibration generator used for this purpose is described below. The upper end of the generator 49 is connected to the lower edge of a vibration energy storage device 50, which in turn hangs at its upper end on a submersible motor 41. Without going into too much detail, it should be mentioned here that a particularly high quality factor Q is generated with the device 50 in the oscillation circuit, as a result of which the oscillatable device is stabilized and operates with a particularly high degree of efficiency. The quality factor Q is a desired value in resonant circuits and represents the ratio of the energy that can be stored during a half-cycle to the energy loss occurring during this time. The quality factor a is roughly comparable to the flywheel effect and a high quality factor ensures stable and high-energy operation. Such a device prevents energy from being lost, so that all of the energy applied by the vibration generator can act on the workpiece. This is described in more detail below. In the particular exemplary embodiment, the oscillation generator 49 is driven by a submersible motor 41 via a long shaft which runs through the oscillatable device 50. The generator 49 has an operating frequency which is in the region of the resonance frequency of the oscillatable device 50, so that it is set into resonance. As a result, the generator 49 vibrates with a considerable amplitude, and this vibration is transmitted to the sample tube 45. A suitable embodiment of the vibration generator 49 is shown in FIGS. 4 and 5 and is described below. The generator 49 has a hollow housing 60 which can be divided into two halves in its longitudinal direction and is held together at point 61 by bolts. At its upper end it is connected to the vibratable tube 50 with screws of high tensile strength, as indicated in FIG. 2 at point 62. At its lower end, the generator is followed by the sleeve 48, which is rigidly connected to the generator housing with the screws indicated at 63 in FIG. 5. The generator housing 60 is closed at its lower end and provided with an inner cavity which is designed so that it can accommodate a plurality of rotating masses and bearings, as will now be described. The drive shaft 66 for the vibration generator extends from above into the housing 60 through a bore 65 in which the corresponding bearings are arranged, the bearings being braced and kept at a distance by bearing bushings and a clamping nut 67. The upper part of the clamping nut 67 is located in a recess at the lower end of the oscillating energy store 50. A bevel gear 68 is placed on the lower end of the drive shaft 66 and meshes with two further bevel gears 79. In addition, spur gear teeth 70 are applied to the hubs of the bevel gears 69, and the bevel and spur gears 69, 70 are rotatably arranged on a shaft 71 which is mounted in the generator housing so that the two groups of gears rotate in opposite directions. The gears 70 again mesh with face-toothed gears 72 which form a unit with further gears 73 below the shaft T1. The two gears 73 are. with a toothing 75 in engagement, which are connected to the unbalanced bodies 78, so that two unbalanced bodies seated on a common shaft 79 each rotate in opposite directions. The two unbalanced rotors are kept at a distance from each other by a hardened steel washer v0. Four pairs of such rotors 78 are arranged one above the other in the generator, and the associated gears 75 are each in mesh with one another. Lubrication takes place by filling a few cubic centimeters of oil into the interior of the generator housing. The unbalanced bodies 78a of all rotors of the vibration generator are set so that they are in the vertical direction;, ung in the same mode. It is now easy to see that the two rotors of each pair rotate in opposite directions, so that their sideways motion components cancel each other out. However, the vertical components of motion of all rotors are in phase and consequently add up. The unbalanced rotors 78a, which move synchronously in the vertical direction, emit an alternating force of considerable strength acting in the vertical direction to the generator housing 49 via the shafts 79. This alternating force acts on the lower end of the vibratory energy store 50 with the result that it is set into longitudinal vibrations. The vibrational energy storage 50 shown in particular in FIG. 3 consists mainly of a cylindrical rod O0 of a very elastic material such as steel, at the upper end of which a fastening flange 81 is formed, to which it is fastened by means of screws 82 at the lower end of the motor 41 , and further from a surrounding cylindrical housing 83 made of similar elastic material, which is fastened with its upper end to the upper end of the rod 80. For example, an annular flange 84 can be provided at the upper end of the rod 80, on which the slightly thickened upper end 85 of the jacket tube 83 rests, so that these two parts are connected by means of threaded bolts 86 which are screwed through the annular flange 84 into the jacket tube b5 . In this way, a rigid connection between the upper ends of the two parts 80 and 83 is established. The jacket tube ü3 has a lower end wall b7 which is provided with a cavity into which, as already mentioned, the clamping nut 67 engages. In addition, the end wall j'i 'is penetrated by a central bore 88 in the longitudinal direction, through which the drive shaft and its housing pass. The length of the vibratory energy store 50 is considerable, for example about 8 m. The cross-sectional areas of the hollow central rod 80 and the surrounding jacket tube 83 are preferably selected to be approximately the same. There is an annular gap between the two, and at the lower end of the rod 80 a pipe 89 is screwed on by means of a thread as an additional mass, for example about one meter in length 89 and the jacket tube 83 still has a gap. The benefits associated with the attachment of such a tube 89 will be better described later. The vibrational energy store 50 is in a certain sense comparable to a tuning fork, the inner and outer parts 80 and 83 representing the fork prongs which are rigidly connected to one another at the upper end. The prongs of a simple tuning fork, however, swing transversely to their direction of extension, whereas the "prongs" of this arrangement alternately elastically lengthen and shorten, this lengthening or shortening in the two prongs taking place in the opposite direction, so that the entire arrangement is dynamically neutral . With such a movement, the connection end remains essentially at rest, that is to say lies in the node of a standing quarter-wave oscillation. The lower ends of the prongs lie in the antinodes of the standing wave. Such a distribution of vibrations occurs when the entire arrangement is excited at its resonance frequency.

The arrangement is also tuned to resonance when the two prongs 80 and 83 including the attached masses, on the one hand of the generator and on the other hand of the tube 89, are tuned to a quarter wavelength of the occurring frequency. It is known to any person skilled in the art that the tuning can be done in various ways, for example by changing the cross-section of one or both tines or by adding so-called concentrated masses to one tine, eg the tube 89. It should be noted that the outer tine is longer than the inner 80 and that at its lower end several concentrated masses are attached, which are composed of the lower end wall 87 and the generator housing 49. This gives the outer prong a much greater effective length than the inner prong if the additional tube 89 is left out of consideration. In order to match the inner prong 80 to the outer prong 83, the additional tube 89 is attached to the lower end of the inner prong, which means additional mass and also a considerable extension of the inner prong. The two prongs 80 and 83 are thus tuned to the same resonance frequency. This results in a greater effective length. The electric motor 41 can be a known motor, so that it is not necessary to explain it in more detail and to illustrate it. This motor is provided with a vertical output shaft 90 (see FIG. 3), the shaft end of which is equipped with internal teeth 91, into which the shaft end 93 of an elongated shaft 92, which is provided with corresponding teeth, engages. The shaft is guided in bearings which in turn are accommodated in a bearing holder 95 in a bore 96 in the upper part of the elastic rod 80. A bore 97, which is slightly smaller in diameter than the bore 96, extends through the part 80. A cone is attached to the lower end of the shaft 92 which engages in a conical connection 98 in the upper end of a tubular drive shaft 99 which extends through the bore 97 extends through to the lower end of the vibration energy store and is connected there to the drive shaft 66 of the vibration generator 49 (see FIG. 5). At the lower end of the shaft 99 there is a coupling 100, which in turn establishes the connection to the shaft 66 with a toothed tenon connection 101, 102. The generator housing 49 and likewise the shaft 66 oscillate back and forth in the longitudinal direction of the pipe, and the toothed pin connection between the drive shaft 66 and the tubular drive shaft 99 can compensate for this relative movement. On the bearing bush 95 (see Fig. 3) there is a short piece 45 of reduced diameter, which extends into the bore 97, and connected to this, a housing tube 106 extends through the entire length of the part 80 through for the Wave. The thin 107 that sit in this housing tube 1Q6 serve to keep the shaft 99 straight. The gauntlets are kept at a certain distance from one another by spacer sleeves 108. Sufficient space is provided between the housing tube 106 and the inner wall of the bore 97 in the rod 80 so that these parts do not touch when they vibrate against one another. The sample tube 45 is matched with its suspension to the suspension of the prongs 80 and 83 of the oscillating device 50 and is about 20 m long with the given dimensions of the oscillating device, which corresponds to half a wavelength at an operating frequency of about 133 Hz. In the present embodiment according to the drawing, the total length from the lower end of the housing 83 to the flange 84 is eight meters. If you consider that concentrated masses are attached to the lower ends of the two tuning fork prongs, the hang of the fork prongs correspond to a quarter wavelength at the operating frequency of 133 Hz. In other words, the effective length of the vibrational energy storage device 50 is half the length of the sample tube 45 the system operates at a frequency of around 133 Hz, oscillates. the housing of the vibration generator 49 as a result of the elastic displacements in the material and @ sends corresponding deformation waves through the sample tube 45. Since the sample tube is half a wavelength in length, a half-wave oscillation st is generated in it, with an antinode at both ends of the tube and in the center of which is a node. (see Fig. 6). The center of the tube is essentially still and only vibrates in the radial direction, which is related to the special type of longitudinal vibration, whereas the upper end swings back and forth in the vertical direction according to the generator movement and the lower end hits the ground S. from which a sample C is to be taken, with vibration energy being radiated to the ground below the pipe from its annular end cross-section. The operation of the entire device is now as follows: it is assumed that a hole has been drilled into the earth to a certain depth and that a layer sample of a few meters in length is to be taken below the end of the borehole, for which purpose the drill is pulled out of the borehole and the Device, as shown in FIGS. 1 and 2, is lowered into the borehole, namely hanging on the cable 43, until the lower end of the sample tube 45 rests with pressure against the borehole end. Current is now fed to the drive motor 41 via an electrical cable located within the support cable 43, which drives the shaft 99, which extends through the vibration energy store 50 and drives the shaft 66 of the vibration generator 49. It is necessary that the operating frequency be a resonance frequency of the energy storage device 50 and the sample tube 45. It is therefore necessary that the alternating current supplied to the drive motor 41 have the appropriate frequency, which is most easily achieved by driving a generator from a variable speed internal combustion engine. The vibration generator 49 emits an alternating force in the vertical direction with the predetermined resonance frequency of the system. The alternating force acts on the lower end of the jacket tube 83 of the vibration accumulator 50, so that tensile and pressure waves propagate through the jacket tube 83. The influence of the tensile and pressure waves on the connecting section of the jacket tube with the cylindrical rod 80 also generates the same tensile and pressure waves, but with opposite phase positions in the rod. If the frequency of the oscillations is the resonance frequency of the arrangement, the amplitudes of the oscillations are increased, and the condition is quickly reached in which longitudinal oscillations with opposite phase positions occur in the two prongs 80 and 83 . The arrangement in the longitudinal direction is therefore dynamically neutral. The entire vibratory device acts as an energy store with a high quality factor, which stabilizes the entire system in the event of a large vibration amplitude. The two prongs of the device absorb energy in periodic alternation and give it back to the system, as is clear from the explanations to any person skilled in the art. It is obvious that the vibration generator 49 has considerable energy consumption due to the reciprocating masses of its housing and other parts. A very important task of the energy storage device 50 is to "tune out" these oscillating masses of the generator housing, as a result of which the energy that would otherwise be lost is preserved. The mass is directly connected to the lower end of the tine 83 of the vibrating device 50 and forms a concentrated mass at the lower end of this vibrating tine. In this way, the mass is included in the oscillating system 80, 83 and balanced by the elastic components of the parts 80 and 83. By including the mass in the vibration system 80, 83, its resonance frequency is lowered. Since the mass is attached to the lower end of the prong 83, there is no longer any frequency equality with the inner prong 80, so that the sleeve 39, which serves as a balancing mass, has to be attached to it. If the balancing mass is not attached to the inner prong SO, the additional mass of the generator 49 on the outer prong 83 causes the vibration node to be moved from the junction of the two prongs 80 and 83 into the outer prong $ 3, which means that the junction is not is more at rest. The balancing mass 89 is chosen so large that the vibration node of the arrangement falls into the junction of the two parts 80 and 83. The lower end of the vibration generator 49 thus oscillates in the vertical direction with a considerable amplitude and transmits an alternating force of considerable strength to the upper end of the sample tube 45. As a result, a standing half-wave oscillation is generated in the sample tube, where the lower end of the tube, which is pressed against the ground with a certain pressure, vibrates against the ground. As already described, this oscillating movement of the lower edge of the pipe relative to the ground makes it locally flowable, so that a soil sample is separated from the surrounding soil material and fills the pipe when it is lowered. It will be understood that the assembly is supported on the ground, at least in part, so that the downward force on the earth material comes about through it; moreover, it will be understood that the whole assembly is slowly lowered as the sampling proceeds. The longitudinal oscillation not only influences the soil material at the end face of the pipe, but the oscillations of the pipe walls also contribute to the reduction of friction with the soil sample in the pipe, which makes it easier to penetrate the pipe. This reduces the frictional resistance of the sample in the pipe, which in turn facilitates the penetration of the soil samples into the pipe at its lower opening. With suitable modifications of the device, aas method can also be used to drive a shaft or a pipe into a second pipe which tightly encloses this or, which is the same, to insert a shaft into a bore with a press fit. In the following, reference is made to FIGS. 7 to 11, in which a hydraulic press of known design is shown, in which devices for generating vibrations according to the invention are inserted, it being shown on the basis of these representations how a bushing is inserted into a bore a housing or a frame, preferably a casting. The frame of the. hydraulic press is indicated generally at 120 and consists of a pair of vertical supports or columns 121 which stand on a foundation B and at their upper. End are connected to one another by a bow 122 (see Fig. 7). The connecting arch 122 is connected in the middle with a transverse arch 123 which connects two frame supports 124 and 125 which are also erected on the foundation B to one another. A hydraulic ram 126 protrudes through an AnguB 127, which is attached to the underside of the head piece of the press, which is formed by the crossed arched parts 122 and 123; the associated hydraulic cylinder is (not shown) inside the arch 122, which can be provided on its upper side with an extension 122a so that the cylinder is given the necessary length, and in which the known control elements of a hydraulic cylinder are accommodated so that the The punch 126 can be pre-pressed with a certain pressure and then retracted again; these parts are omitted from the drawing for the sake of simplicity, since they are known to any person skilled in the art. At the bottom of the press, on the foundation B, there is a horizontal clamping plate 130, on which a cylinder housing or other machine part 131 rests as a typical example, which has a top surface 132 with a downward-facing annular flange or sprue 133 which forms a cylindrical bore 134. Eik @? .f = .. s, 135, which has a likewise cylindrical wall 136 with a flange 137 at the upper end, the outer diameter of the cylindrical wall 136 being dimensioned so that it forms a press fit with the inner diameter of the bore 134, which tight is that it is difficult to press the socket into the Jie bore even when considerable pressure is applied. Between the columns 121 and above the bushing 135 there is a horizontal, elastically oscillatable support 140 made of highly elastic material such as steel and the dimensions of which are chosen approximately in relation to the bushing as shown in the figures. This carrier is excited to elastic bending vibrations in the vertical direction, and the vibrations of the carrier are transmitted to the socket with the aid of an adapter 141. In the case shown, the adapter piece can be a steel disk, the lower surface of which rests on the flange 137 of the bushing 135 and on the upper side of which tabs 142 are formed in pairs that accommodate the oscillating carrier 140 between them, to which they are connected by bolts 143 are. As can be clearly seen here, the bolts 143 penetrate the carrier 140 at certain points, namely at a distance of approximately a quarter of the length between the center of the carrier and its end from the center. The adapter can be connected to the carrier at different points, for example also to the center point, which each has a different effect. Occasionally it is advantageous to place the connection points close to the vibration nodes still to be described, and this is the case when vibrations with high energy but very small amplitudes are required. The vibrations which are caused in the carrier 140 are standing bending vibrations, as is shown in a diagram at W on the upper side of FIG. In this a-diagram, the distances a mean the oscillation amplitude at the corresponding points of the carrier 140. The carrier therefore also vibrates. lowest amplitude in the two nodes N and with the highest amplitude in the areas of the antinodes V at the two ends of the beam and in the area of the antinode Vt in the center of the beam. The adapter is connected to the support 140 at two symmetrical points with respect to the standing wave, namely at points where the oscillation amplitude is still considerable, but smaller than in the antinode in the center of the support: such a position of the connection points has proven to be advantageous proven, but in other cases other connection points can be advantageous if other oscillation amplitudes or impedances are selected. The flexural vibrations can be generated in the carrier 140 in various ways; a very simple mechanical vibration generator for generating the vibrations is described in more detail below. The nodes of vibration are approximately a quarter of the total length of the beam from the end of the beam, and these points are preferably used to attach the beam. For this purpose, bolts 145 are passed through the carrier, and these bolts pass through brackets 140, which enclose the carrier on both sides and are attached to the ends of a support beam 148, which is located close above the swingable carrier 140 . The support beam 148 also serves the task of keeping the vibrations of the carrier 140 away from the frame of the press, since it is connected to the carrier 140 in its vibration node by the bolts 145. The support beam 148 is again suspended at its ends with vertical bolts 149, which penetrate bores 150 in support arms 151 which, in turn, are fastened to the columns 121 of the press. The guide pins 149 enable the support beam to be freely movable in the vertical direction; they are equipped with heads 152 at their upper ends, so that when the support beam moves downward, they compress a spiral compression spring placed between these heads and the support arms 151 on the bolts. So that the bolts 149 and also the springs 153 can be long enough, they stick with their upper ends in Aashöhlungen of the connecting arc 122. The spring constant of the springs 153 is chosen large enough so that they the support beam 148 and the swingable carrier 140 in their Hold the uppermost layer, as shown in FIG. 7, the support beam 148 then resting against the underside of the support arms 151 as long as it is not pressed downwards by the hydraulic ram 126. In the support beam 148, a seat 165 for the hydraulic ram 126 is formed on its upper side, in which the ram engages when it is pushed down and presses the carrier 148 and the oscillating carrier 140 and the adapter 141 down onto the socket 135, so that it fits into the Bore 134 is pressed in. The path of the ram 126 must of course be sufficient for the bush 135 ′ to be able to be pressed completely into the bore 134. The devices with which the stationary bending vibrations according to diagram W are generated in the vibrating beam 140 consist in the example shown here of simple, air-driven vibration generators 158 which are embedded in the ends of the beam 140. The-Fig. 10 and 11 show one end of the carrier 1 # 0 with an embedded vibration generator, it being seen that the carrier end is hollowed out from the end face, as shown at 159, and that this hollow is penetrated transversely by a sleeve 160. The sleeve 160 extends parallel to the pin 145 in the nodes and is inserted tightly in the Trägerwandung 161 on one side of the cavity 159, it whereas in the other wall 162 of the cavity is screwed, as shown in FIG. 11 clearly understood . One side of the necks is closed, and an air line 164 is screwed into the other. A ring 165 surrounds the sleeve 160, the inner diameter of the ring being slightly larger than the outer diameter of the sleeve 160 and the ring having approximately the dimensions as shown in FIG. The sleeve 160 is penetrated by tangentially directed bores or air outlet nozzles 166, through which the air flows out against the inner surface of the ring 165, so that it is driven in a centrifugal orbital movement around the sleeve 160 in the direction of the arrow in FIG. 10. So that the ring does not move laterally with respect to the air nozzles, bead edges 168 are formed on the outer surface of the sleeve, between which the ring 165 runs with little axial play. The ring thickness is selected so that the ring 165 just does not touch the inner wall of the cavity 159, as can be seen from FIG. 11. The ring exerts a centrifugal force on the sleeve 160, the direction of which is perpendicular to the axis of the sleeve and rotates around it. Such a force arises in both ends of the girder, and this force can be thought of as being composed of components in the axial direction of the girder and perpendicular to the girder axis. The tangentially directed air nozzles 116 of the sleeves 160 of the generators are positioned in opposite directions to one another, so that the two rings 165 in the two carrier ends run in opposite directions to one another. The advantage of this measure will now be explained in more detail. It is assumed that the standing bending vibration W is caused by a vibration generator 158 at one end of the beam. The air pressure of the oscillation generator is influenced in such a way that the ring 165 swirls around the sleeve 160 at a frequency that is in the range of the resonance frequency of the elastic carrier 140 with respect to its flexural oscillations, preferably the fundamental wave oscillation, as shown in FIG. 7 in diagram W. is shown. The standing wave shows two nodes N, the distance from the ends of the beam about a quarter of a wavelength, and antinodes V at the ends of the beam and an antinode V 'in the center of the beam, as already explained earlier. From the basics of vibration theory it can be seen that such a standing wave is created by the propagation of vibrations in the carrier 140, which emanate from a vibration generator which is accommodated in one end of the carrier, since the. Waves are reflected at the second end of the carrier and as a result of the superposition of the forward and return waves, a flexural oscillation with oscillation nodes and antinodes is caused. The free end of the support, on which a vibration bulge is formed, is a suitable point with a suitable impedance for arranging a vibration generator 158. The quarter-wavelength points, in which the impedance of the oscillation system is very high, but the oscillation amplitudes are very small, are particularly suitable for fastening the carrier. When the vibration generator 158 is driven by the air so that it operates in the resonance range of the standing wave, it falls into step on the lower side of the resonance curve, so that a stable operation is ensured. Further discussion of this phenomenon is given in US Pat. No. 2,960,314. If two vibration generators 158 are used, one of which is inserted in each end of the carrier, these two generators synchronize themselves, since each of the generators strives to generate a standing wave in the carrier when it is in the resonance range of the Carrier arrives. The two waves emanating from the generators automatically come into phase and synchronize the two rotating rings. So it happens that the rings move in a vertical direction in unison, which creates a flexural vibration of twice the strength compared to that generated by a single generator. is quite desirable. Since the rings rotate in the opposite direction to one another, they move in opposite directions to one another in the longitudinal direction of the carrier, so that the forces in the longitudinal direction of the carrier cancel one another out. In no case, however, do the circumferential frequencies of the rings fall within the range of the resonance frequency of a longitudinal oscillation in the carrier, so that there is no risk of a longitudinal oscillation of considerable amplitude being generated in the carrier. The flexural oscillation of the beam 140 causes a considerable movement in the vertical direction between the oscillation nodes N, namely the amplitude is proportional to the distance a in the diagram W. The amplitude increases from the value zero in the oscillation nodes to its maximum Vt in the oscillation antinode. The carrier 140 is connected to the adapter 141 which is intended to act on the workpiece 135 at a point at which the impedance and thus also the vibration force and the vibration amplitude is adapted to the corresponding workpiece. In the example shown, two points are selected as connection points, which are approximately halfway between your antinode V 'and the oscillation node N, i.e. points with a relatively high impedance at which no significant oscillation amplitude occurs. In the case of a carrier 140 of approximately 600 mm in length, the oscillation amplitude at the connecting bolts 143 is approximately in the order of magnitude of 0.75 mm. The aim is to produce the carrier 14-0 from a material with a high quality factor Q so that it is able to store a considerable amount of vibration energy, as already explained in more detail at the beginning of the description. Then the carrier also serves as part of the vibration generator. The carrier 140 is designed to have sufficient elastic reactance to balance the mass reactances in the system at the operating frequency. The press 120 also has a clamping device for the casting or any other workpiece 131 into which the bushing 145 is to be pressed, and this clamping device preferably contains a further vibration system which can either cooperate with the first vibration system or also on its own can act. As shown here, the upper end of the casting 131 is caught by an adjustable jaw 1B0 which is brought into the desired position with a ball joint 1211 at the end of a screw spindle 12-2. The screw spindle 182 is guided through a nut in the frame 124 of the press and can be rotated by a toggle 184 so that the jaw is pressed against the workpiece. Opposite the jaw 130, the casting 131 is touched by an adapter 185 which is similar to the adapter 141, with the exception that the surface abutting the casting is provided with a cavity 166 and that in the case shown here the jaw is centered a vibrating beam is connected. The carrier designated by 188 is mounted in the vertical direction and its shape corresponds exactly to the carrier 140 already explained. The carrier 188 is provided with suspensions and a hydraulic ram, as was already explained for the previous section for the carrier 140. The adapter 185 can also be connected to the carrier at two divergent points that are distant from the center of the carrier and its nodes of vibration, as shown between the adapter 141 and the carrier 140, but in the example shown here is the adapter connected to the carrier in its center with the aid of two tabs 190 which grip the carrier laterally and are penetrated by a bolt 191 inserted through the carrier. The bolt 191 thus connects the adapter to the carrier in an antinode, so that a maximum of oscillation amplitude is transmitted. Such a fastening 4 can also be made between the adapter 141 and the carrier 140, and it is to be preferred if a particularly large amplitude is desired. The two-point attachment between the carrier and the adapter is selected when a lower amplitude of the oscillation with a high oscillation force is desired, which requires attachment in points with higher impedance, i.e. closer to the oscillation nodes. The carrier 1'ö has exactly like äer, `.L'r@ger 140 nodes of vibration which are displaced inwards from its ends by about a quarter of the length of the carrier, and the carrier is exactly like the carrier 140 in these points by bolts 195 , which are passed through tabs 195, which are located on a support beam 197, which serves as a vibration isolator, held. The support beam is in turn seated on ends of bolts 198, which are passed through support arms 199 and 200, the bolts having screw heads 201 at their other ends, so that a coil compression spring 201 is clamped between the support arms 199 and 200 and the bolt heads. In the stand 125, the press frame forms a downward-facing, horizontal surface 204 to which a support arm 199 is attached, whereas the second support arm 200 rests on the foundation B. A hydraulic ram 210 emerges with a horizontal axis from a cylinder sprue 211 on the frame part 125, which is directed at the center of the oscillating beam 188, and within the cylinder sprue 211 and the frame part 125 there is a corresponding hydraulic cylinder (not shown) and associated valve parts and the like attached, by means of which the ram 210 is actuated and moved back and forth, as is well known. A seat 213 for the punch 210 is mounted in the support beam 197, and when the punch engages in this seat, the support beam 197, the swingable carrier 188 and the adapter piece 185 are pressed against the workpiece 131.

With the help of this arrangement a hydraulic jig the workpiece 131 into which a bushing 145 is to be pressed can be clamped while the bushing is pressed downwards via the oscillating beam 140 and vibrates is moved.

The oscillating beam 188, however, is also equipped with oscillation generators 220 fitted at one or both ends, these vibration generators can be exactly the same as in the ends of the oscillating beam 140 and preferably to the resonance frequency of the carrier 188 for its standing bending vibration be matched so that the casting or any other workpiece 131 is also is vibrated while the sleeve 145 vibrates downward is pressed. The pressing of the bushing 145 into the workpiece 131 is thereby repeated relieved.

However, such a press also makes it possible to produce parts with horizontal Insertion direction to be pressed together. Then only the clamping plate 180 and the adapter 185 with the oscillatable carrier pressed towards one another, what happens with the help of the hydraulic ram 210, while the oscillatable Carrier 188 vibrates with a standing resonance wave.

The invention will now be further described, assuming that the workpiece 131 is clamped with the aid of the hydraulic ram 210, without the oscillating beam 188 being set in oscillation. The vibration generators 158 are driven so that in the oscillating beam 140 a standing bending oscillation is generated, and the hydraulic ram is pushed out so far that it against the support beam 148 is pressed, on which the swing beam 140 and the adapter 141 sitting, which in turn again against the top. the Bush 137 presses, which is placed exactly concentrically on the bore 134 in the workpiece 131 is. In general, the adapter 141 is held slightly above the socket, so that it does not touch the socket until it is slightly behind by the punch 126 is pressed down. In any case, the stamp is pressed down until the Adapter 141, which is suspended from the swing beam, with pressure on the Workpiece acts, and the punch is pressed downwards until the bushing 135 is pressed completely into the bore 134. As a result of the rhythm of the vibrations alternating pressing force, which is generated by the 'oscillating beam, is pressed in into the bore 134 with little effort, even with a tight press fit. With particularly firm Press-in with the aid of the method according to the invention is still a press fit possible, while it can no longer be carried out with simple pressure.

In order to be able to understand the invention better, the processes involved in the vibrations must be discussed in more detail. A whole series of vibration phenomena play a role in the invention, since their meaning changes within the broad scope of the invention, the example shown in FIGS. 7 to 11 should be considered here. The socket 135 and the casting or the like. 131 which is to receive the socket 135 are complex structures with distributed constants. That means that their mass is distributed and that their walls have a certain elastic stiffness. The whole structure can oscillate elastically in itself, with resonance or not with resonance. In general there is a whole range of resonance frequencies and also several possibilities to generate a standing wave, which depends on where and with what frequency the alternating force acts. In the example described here, the casting 131 receives the vibration energy via the bush 1, 5, which is pressed into the casting with the aid of an alternating force superimposed on a one-dimensional force. The bush itself is caused to vibrate in the vertical direction by the adapter 141 and can itself perform elastic vibrations. As already mentioned, the adapter with the vibrating beam is attached to certain points on the carrier selected according to their impedance, the attachment being designed so that elastic vibrations can be transmitted so that the vibrations are transferred from the vibrating beam via the adapter to the workpiece will. It's going ok. So the oscillation energy from the oscillation generators 15 $ to the bphwing support 140 and from this via the adapter 141 to the workpiece, which here is the socket 135, and to the part 131 via and thus also on its parting surface. If the adapter is roughly rigid, the impedance value on its underside is equal to the impedance value of the oscillatable carrier at the point or locations at which the adapter is connected to the carrier. The vibrations are directed essentially perpendicularly, so that longitudinal vibrations are exerted on the bushing with a high impedance value. The socket 135 has an impedance value of approximately the same order of magnitude. The vibrations imparted to the bushing preferably travel through it in the longitudinal direction and produce elastic expansions and compressions, as indicated by the dash-dotted line 135a in FIG. 10a. It is also possible for elastic forces acting in the radial direction to occur, in particular if the adapter piece bends somewhat elastically, so that in general the bushing oscillates elastically both in the longitudinal direction and in the radial direction. With a suitable adjustment of the oscillation frequency to the dimensions of the bushing and the vibration characteristic resonance vibrations 133 of the workpiece 131 can be caused in the bushing, which are then substantially increased, and such a procedure represents an application of the invention. These vibrations now call in the cylindrical sprue vibrations in the longitudinal direction as well as in the transverse direction, as shown, for example, by the dash-dotted * lines 131a in FIG. 10a. The transverse expansion can also occur at the top of the bore and all of these oscillatory motions create small but effective changes in the dimensions of the bore 134 into which the bushing is inserted. Resonance vibrations can also occur in the workpiece 131, so that the vibration amplitudes are thereby increased. Longitudinal vibrations in the bushing cause elastic deformations, the bushing also contracting in the rhythm of the vibrations, so that its seat in the bore 134 becomes looser as a result. In general, the vibrations of the cylinder sprue 133 acting in the radial direction are not of the same amplitude as those of the bushing, and they also generally do not have the same phase position, so that the contact pressure between the bushing and the bore wall is lower in the rhythm of the vibrations . It should also be considered that, especially at the first moment of the press-fit, as shown in FIG Pressure waves that reach the lower end of the socket are reflected there. In this initial stage, the lower end of the bushing has a large oscillation range with respect to part 131. This helps that this part easily penetrates the workpiece 131 so that the bushing can be pressed in without having to overcome the resting value of friction. If the socket then penetrated a short distance into the bore 134, two further impedance mismatches result, as a result of which strong reflection occurs again in the socket. The first mismatch results from the fact that the lower end of the bushing is gripped in the bore of the workpiece 131, whereas the section above remains free, so that it can execute elastic vibrations. The second point of mismatch. is the contact surface between the lower, already inserted bushing section and the cylinder wall of the workpiece 131. Here too, due to the relatively large play, vibrational energy waves are reflected, which results in strong relative movements between the bushing and the workpiece 131 towards the outside expresses. This contributes to the fact that the parts move easily against each other and thereby the friction is reduced, which is particularly important for the press-fit process. The phenomena just described are based on the mismatch in the contact zone, as a result of which vibration energy is reflected, which leads to a greater vibration amplitude in the socket than in the workpiece 131. The relative movement between the bush 135 and the chewing part 131 can, however, also be brought about in another way than by a phase shift of the vibrations in these parts. The oscillatable system, consisting of the oscillating support, the adapter and the bushing 135, has a resonance frequency which is essentially determined by the mass and the elastic constant of the oscillating support. The workpiece 131 can be influenced in a simple manner in such a way that its resonance frequency deviates significantly from that of the oscillatable carrier. At the working frequency, is carrier, the vibration of the workpiece 131 is very much out of phase with that of the carrier. This means that a strong relative movement occurs between the bushing 135 and the workpiece 131.

Relative movement between the bushing and the workpiece 131 is also caused by damping. The source of the vibrations lies in the vibrating beam 14-0, and these vibrations become especially at the junction on their way of propagation strongly damped between bushing and workpiece 131.

There are also differences in impedance and thus increased relative movement due to different materials, so that when choosing the materials, e.g. Bronze for the bushing and steel for the casting, corresponding differences in the acoustic impedance are present at the contact points.

The case is now considered in which the vibrating beam 188 is also excited, so that the workpiece 131 is vibrated in the lateral direction. In this way, an elliptical vibration can be generated in the workpiece 131, so that the case occurs that a type of vibration is generated in one of the two parts to be joined which is completely different from that in the other part. The propagation speeds of the various types of vibration differ. Relatively large differences in the vibrations are achieved, so that the friction on the contact surfaces is considerably reduced. Phase inequality is also obtained in this way. With such a drive system it can also be achieved that one of the parts is only excited by one vibration source and the other is excited by a second vibration source that is completely separate from it.

The system contained in FIGS. 7 to 11 also includes that the difference in the dimensions or the physical properties of the the two parts to be united have different propagation velocities of the elastic Results in vibrations. E.g. the longitudinal vibrations propagate in the socket at a different speed than the bending and radial vibrations in part 133.

This also includes the fact that one part shows a more inductive and another part a more capacitive behavior - at the operating frequency. In the example shown here, the casting 131 is more flexible than the bushing 135 or the system connected to it. This promotes the occurrence of out-of-phase vibrations, which contributes to a reduction in the friction between the two parts. It goes without saying that the invention can also be carried out if only the oscillating beam 188 and through it the part 131 are excited, for example to stretch vibrations, while the bush 135 is merely pressed downwards. The only difference is that the source of the vibrations is connected to part 131 instead of to part 135 as before. Both oscillating beams can be excited simultaneously or alternately. If they are excited simultaneously, the same frequencies can be generated in both, especially if the material and the dimensions of the supports are the same, so that their resonance frequencies are the same or very close to one another. By changing the dimensions or choosing a different material, e.g. steel and hard aluminum, different resonance frequencies can be achieved. The oscillations can be in common mode with one another, although it is generally advantageous to have a small phase difference, which is due to the different dimensions. If, however, vibrations of different frequencies are generated, there are already large differences and thus differential movements. It is therefore possible to find out the most favorable mode of operation for the process.

Claims (3)

Patent claims are, with reduced friction on the contact surface, characterized in that a vibration is caused in at least one of the parts, which also affects the contact surface, so that the friction on the contact surface is reduced, and that a force in the direction of the Parts acts, in which the parts are shifted against each other, and with such a size that the friction reduced by the vibration is overcome. 2. The method according to claim 1, characterized in that that the magnitude and direction of the supplied vibration is chosen so that in at least one of the parts connected with a press fit one in the rhythm of the vibrations recurring dimensional change occurs. 3. The method according to claim 1, characterized in that vibrations are generated on both sides of the contact surface in both parts. Method according to claim 3 ,. characterized in that the vibrations generated in the two parts have different amplitudes. 5. The method according to claim 4, characterized in that the vibrations with one amplitude are generated in one of the parts and the vibrations with the lower amplitude reach the second part by transmission via the interface with damping. b. Method according to Claim 3, characterized in that the type of vibration is different in both parts. 7. The method according to claim 3, characterized in that there is a phase difference between the two oscillations. Method according to Claim 3, characterized in that the mode of vibration is the same in both parts and that the propagation speeds are different as a result of different dimensions of the parts. .9. Method according to one of Claims 1 to 8, characterized in that the vibrations are generated at a frequency at which they are amplified in the parts. 10. The method according to any one of claims 1 to 9, characterized in that a vibration is generated with a frequency at which a certain vibration distribution occurs in the part. 11. The method according to claims 9 or 10, characterized in that the parts are excited with their resonance frequency. 12. The method according to claim 3, characterized in that an oscillation is generated which generates an inductive behavior in one part and a capacitive behavior in the other part, whereby relative movement occurs at the separating surfaces. 13. The method according to any one of the preceding claims, characterized in that the vibrations propagate through one of the parts and are reflected on the parting surface. 14. A method for driving a bushing or the like. In a bore with a press fit, characterized in that vibrations are generated in the bushing and that at the same time a force acts on the bushing which drives the bushing into the bore. 15. Device for carrying out the method according to claims 1 to 14, characterized by holding elements with which the parts (131, 135) can move along one another on their contact surface, means (14;), 1138) which are connected to the parts (135, 131) are coupled in terms of vibration to generate vibrations in the parts in the area of the contact surfaces and a device (12ö, 127) for supplying a one-dimensional thrust force to a part (135) in order to push the part along the contact surface. lt ;. Device according to claim 15, characterized in that the means (14G) for generating vibrations and the device (12b) for supplying the thrust force are connected to the same part (135) and that the means (140) for generating vibrations are connected between the part (135) and the thrust feeder (126) are attached. 17. The device according to claim 15 or 16, characterized in that the means for generating vibrations are an elastically oscillatable carrier (140) (188) and vibration generators (158, 220), which in the carrier (140, 188) are a standing bending vibration with zones of high and low impedance, the vibration generators (158, 220) attack at points of low impedance, devices (148, 149, 151) for carrying the carrier at points of high impedance and connecting means (141) for the vibration coupling of a point of the Carrier with a certain oscillation amplitude to the part (135). 18. The device according to claim 17, characterized in that the bending vibrations in the carrier have at least two vibration nodes and three antinodes, including an antinode in the center of the carrier (14G), and that the vibration generator (158) engages in an antinode, that the thrust supply ( 126, 148) engages two vibration nodes and that adapter members (141) touch the part and are connected to the carrier (140) at two points which are between the antinode in the center and the vibration node. 19: - Device according to claim 17, characterized in that the bending vibrations in the carrier (188) have at most two vibration nodes and three antinodes, including an antinode in the center of the carrier Q88) that the vibration generator (220) engages in one of the antinodes that the thrust supply (210, 197) engages in two vibration nodes and that an adapter (1851, which is in contact with the part (131), is attached approximately in the center of the support (188).