Classifications

• • G—PHYSICS
  • G01—MEASURING; TESTING
  • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
  • G01M13/00—Testing of machine parts
  • G01M13/02—Gearings; Transmission mechanisms
  • G01M13/027—Test-benches with force-applying means, e.g. loading of drive shafts along several directions
• • G—PHYSICS
  • G01—MEASURING; TESTING
  • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
  • G01M13/00—Testing of machine parts
  • G01M13/02—Gearings; Transmission mechanisms
  • G01M13/021—Gearings

Definitions

• the invention relates to a toothed test stand according to the preamble of claim 1, a tooth sample according to the preamble of claim 23 and a method according to claim 24.
• FZG test stands In order to test the load capacity of the toothing of a gear wheel, so-called FZG test stands and pulsator test stands are known from the prior art.
• FZG test bench In a FZG test bench, the teeth of two gears are brought into engagement and braced against each other. The gears are regularly scaled down models of larger gears. This carries the risk that the results obtained can not be transferred 1: 1 to the larger gears.
• the tension and thus the simulated load is usually static. It is therefore not possible to test dynamic loads.
• the invention has for its object to test the load behavior of the toothing of a gear, bypassing the known from the prior art solutions inherent disadvantages. In particular, the validity of the results of the audit should be improved.
• the gearing dynamometer comprises a sample receiver, i. means for receiving a sample and a first load generator, i. a means for applying a load, in particular a mechanical load.
• the first load generator has at least one head for transmitting the load to the sample.
• the sample is a tooth sample. This comprises a, preferably exactly one, out of the gear or from the teeth of the gear tooth separated.
• the tooth may have been separated out of the gear by means of a method of the third main group of the DIN 8580 standard.
• the gear is preferably an internally or externally toothed cylindrical wheel. Its toothing can be designed as a straight toothing, but also as a helical toothing.
• the sample holder is designed according to the invention to receive the sample described, i. suitable to fix.
• the fixation is such that a load can be applied to a flank of the tooth.
• the load is applied to the head of the first load generator, which bears against the flank of the tooth. Over a corresponding contact surface of the head on the flank, the load is introduced into the flank.
• the load is a force that manifests itself as pressure in the contact surface.
• the force can be constant and / or variable over time.
• the invention makes it possible to directly test the teeth of a real gear without the production of miniaturized models. Since only a single tooth is tested, it is not necessary to completely clamp the gear in the test stand. This is an advantage, in particular in large gearboxes, such as wind power transmissions. In accordance with real stress situations, variable loads can also be simulated as a function of time.
• the tooth sample including the tooth and the head are preferably movable relative to each other.
• at least one actuator is accordingly provided to move the head of the first load generator and the tooth sample relative to each other.
• An actuator is an energy converter that converts a first form of energy - such as electrical energy - into a second form of energy - here: kinetic energy.
• a repeated meshing of intermeshing teeth is simulated in a further preferred development by an oscillating movement of the head and the tooth sample relative to each other.
• An oscillating movement is characterized by a repeated repetition of the direction of movement.
• the term oscillating movement is synonymous with a vibration.
• the actuator stimulates the head and the tooth sample to swing against each other.
• a corresponding preferred embodiment of the invention provides that the movement of the head and the tooth sample takes place relative to each other along or parallel to a mutual contact surface. One direction of this movement is orthogonal to a surface normal of this contact surface.
• the loading of the flank by the head takes place in a further preferred development at least partially in the direction of the above-mentioned surface norma. len.
• a non-zero direction vector of a corresponding force thus acts according to education in this direction.
• the head of the first load generator is clamped in a preferred development against the flank.
• a spring element is provided, which is braced against the head.
• the spring element between the head and a fixed means is braced.
• the fixed means is a component of the first load generator, which may be fixed approximately in the above-mentioned stationary structure.
• the relative mobility of the head of the first load generator and the tooth sample can be achieved by a movable head and / or a movable tooth sample.
• the head is movable and the tooth sample is stationary or rigid, i. without the possibility of relative movement, fixed in the sample holder. This implies that the sample holder is fixed or rigidly fixed.
• the above-mentioned actuator acts on the head of the first load generator.
• the movement of the head is along or parallel to the contact surface of the head and the flank.
• the relative mobility of the head and the load generator is achieved by a movable, preferably translationally movable, tooth sample.
• the above actuator acts on the tooth sample.
• the head In order for the head, while the tooth sample is moving, to bear permanently against the flank so that the load on the flank is permanently maintained by the head, the head is also movable in a further preferred development, preferably translationally. This allows the head to follow the movements of the flank.
• the direction of movement of the head should be anti-parallel to a surface normal of the contact surface between the head and the flank. This creates a condition in the direction of the Agility of the head on the force applied over the head on the tooth to load the flank of the tooth.
• the movements of the tooth sample and the head are relative to a fixed structure, such as a housing of the gear dynamometer.
• a fixed structure such as a housing of the gear dynamometer.
• the tooth sample and / or the head are fixed, for example in the stationary structure, that movements are possible exclusively in the directions mentioned.
• the tooth sample is preferably clamped symmetrically in the tooth tester. This means that a plane with respect to which the tooth is symmetrical and the direction of movement of the tooth sample are aligned parallel to each other. With respect to the gear from which the tooth sample has been separated, the direction of movement of the tooth sample moves preferably radially, i. orthogonal to a rotation axis or central axis of the gear. This corresponds to a central axis of the tooth sample.
• the head is rotationally symmetrical in a further preferred development.
• the head may be formed as a cylindrical roller. This results in a linear contact between the head and the flank of the tooth. Accordingly, the head applies a line load to the flank of the tooth.
• a rotatably mounted further development of the head. This allows a rolling movement of the head on the flank of the tooth.
• the rolling movement of the head corresponds to a rolling tooth engagement occurring during involute toothings.
• An axis of rotation of the rotatably mounted head can be crossed relative to at least one flank line of the tooth flank. This means that the axis of rotation and the flank line are skewed.
• the entanglement of the axis of rotation relative to the flank line is preferably such that the axis of rotation is rotated from a parallel course to the flank line about a surface normal of the contact surface of the head and the flank of the tooth.
• the first load generator has, in a preferred development, at least two heads of the type described above, which rest on the same flank of the tooth and in each case apply a load to the flank.
• the two heads are spatially separated from each other and touch the flank of the tooth in spatially separated contact surfaces. The loads applied by the heads to the flank of the tooth are thus spatially separated from each other.
• the use of two heads makes it possible to selectively bring about a bending stress of the tooth with one of the heads, while the other - the tooth root nearer head causes a weakening of the surface of the tooth by the pressure stress. Based on this, the fatigue strength of the tooth can be determined both in terms of pressure and bending. Both factors are known as causes of failure.
• the at least two heads are each movable in a direction which is anti-parallel to a surface normal of a contact surface of the respective head and the flank of the tooth.
• each of the heads is braced against the flank.
• spring elements may be provided, which are each braced between the heads and the fixed structure.
• the heads are rotationally symmetrical or formed as a roller and rotatably supported. In order to simulate specific sliding, the axes of rotation of the two heads can be entangled with respect to at least one flank line of the flank of the tooth.
• the second head of the tooth dynamometer may have a second load generator. This loads the tooth together with the first load generator and causes a bending moment.
• the bending moment pulsates in a preferred embodiment, i.
• the bending moment can be described as periodic or nonperiodic, damped or undamped, linear or nonlinear oscillation function.
• the bending moment or a vector of the bending moment is directed orthogonal to a surface normal of the flank.
• the surface normal preferably runs through the contact surface of the head and the flank.
• the bending moment with respect to the above-mentioned gear can extend axially in a preferred embodiment.
• the pulsating bending moment completes a zero crossing in a further preferred development.
• a zero crossing is equivalent to a sign change.
• the bending moment changes its direction.
• the tooth sample comprises one, preferably exactly one, tooth of a toothed wheel and a shaft for fixing in the sample receptacle of the tooth test bench described above.
• the shaft can be configured at least partially parallelepiped or cylindrical.
• a method according to the invention for checking the toothing of a toothed wheel comprises the following steps:
• the method step of testing comprises a partial step of clamping the tooth into the tooth test bench and a partial step of loading the tooth by means of the tooth test bench.
• the tooth is clamped in the tooth test bench, where it is fixed in the sample holder.
• the load on the tooth is such that a load is applied to a flank of the tooth by the head or heads of the gear test bench.
• FIG. 2 shows a gearing test stand with a load generator
• 3 is a partial view of a clamped tooth sample.
• Fig. 7 a test cycle
• Fig. 1 1 a gear with internal teeth
• Fig. 12 is a Zahnahnungsprüfstand with two load generators.
• the gear 101 shown in Figure 1 is clamped between two punches 103 of a conventional Pulsatorprüfstands for the purpose of simulating a dynamic load situation.
• the punches 103 engage in the toothing of the gear 101 and apply a load.
• Conventional Pulsatorprüfconstruction have a number of disadvantages, which can be avoided with the Veriereungsprüfstand 201 shown in FIG.
• a tooth sample to be tested 203 is clamped.
• the tooth sample 203 is characterized in that it is not a model produced for the purpose of the test but has been extracted from a usable toothed wheel.
• the tooth sample 203 comprises a shaft 205 and two tooth flanks 207.
• the tooth 205 is clamped in a sample receptacle 209 with the shaft 205.
• the sample holder 209 guides the tooth sample 203 in the vertical direction.
• the shaft 205 has an upwardly open blind bore with an internal thread 21 1. Via the internal thread 21 1, the tooth sample 203 can be connected to an actuator, not shown in FIG. 2, which moves the tooth sample 203 up and down.
• the toothing test stand 201 has a load generator 213.
• a rotatably mounted roller 215 of the load generator 213 is in contact with the flank 207.
• the roller 215 is biased.
• a force F of the spring 213 acts in the horizontal direction on the roller 215 and presses against the flank 207th
• a housing 219 encapsulates the components of the gear bench.
• the housing 219 of the load generator 213 is fixed. Furthermore, the housing 219 forms the sample receptacle 209. Inside the housing 219 is an oil bath 221, in which the flank 207 of the tooth sample 203 and the roller 215 of the load generator 213 are immersed. Oil bath 221 simulates the oil lubrication present in a real gearbox.
• FIG. A view of the tooth sample 203 from below is shown in FIG. Here it can be seen that it is a section of a helical gearing.
• the force F which acts on the flank 207 of the tooth sample 203 for testing purposes, must correspond be aligned obliquely. This is achieved by a corresponding oblique orientation of the load generator 213, as shown in Fig. 4.
• a major axis 401 along which the roller 215 is slidable and in which direction a force can be applied, is orthogonal to the flank 207 of the tooth sample 203.
• the flank 207 runs anti-parallel to a major axis 403 of the gear test bench 201.
• the main axis 403 is aligned parallel to a rotation axis of the gear 101 from which the tooth sample 203 has been cut out.
• the main axis 401 of the load generator 213 and the main axis 403 of the toothed test stand 203 are thus not orthogonal to one another.
• the direction of the perspective shown in FIG. 5 corresponds to the direction of the force F applied by the load generator 213. From this perspective, an entanglement of an axis of rotation 501 of the roller 215 of the load generator 213 with respect to an engagement line 503 can be seen.
• the engagement line 503 denotes a region in which the flank 207 of the tooth sample 203 is loaded by the roller 215. In particular, there is a contact between the roller 215 and the flank 207 along the engagement line 503.
• the axis of rotation 501 of the roller 215 and the engagement line 503 are anti-parallel. This causes a so-called "specific sliding" of the roller 215.
• the roller 215 moves not only rolling but also sliding over the surface of the flank 207. This can simulate real prevailing load conditions exactly.
• FIGS. 6a and 6b The resulting force relationships are illustrated in FIGS. 6a and 6b.
• a first component of a force F applied to the flank 207 by the load generator 213 acts in the flank as a normal force Fn perpendicular to the flank 207.
• a second component of the force F is perpendicular to Fn.
• Fig. 7 illustrates the force F, which is applied by the roller 215 on the flank 207 of the tooth sample 203, over time. Also shown is a test load 701, which is applied in the idle state by the spring 21 7. By the Up and down movement of the tooth sample 203 describes the force F a fluctuating around the test load 701 around periodic course.
• rollers 215 are also entangled with respect to their engagement lines in a two-fold embodiment in order to simulate specific sliding.
• the gear 101 from which the tooth sample 203 has been cut out may be an internally toothed or externally toothed gear 101.
• FIG. 10 illustrates an externally toothed gear 101.
• the tooth sample 203 is cut out of the gear 101 along a first cutting surface 1001 and a second cutting surface 1003.
• the first cut surface 1001 and the second cut surface 1003 are parallel to each other.
• FIG. 1 1 illustrates an internally toothed gear 101.
• the tooth sample 203 is cut out of the gear 101.
• the first cut surface 1001 and the second cut surface 1003 are parallel to each other.
• the toothing test stand 1201 shown in FIG. 12 has, in addition to a first load generator 1203, a second load generator 1205.
• the first load generator 1203 applies a load to the flank 207 of the tooth sample 203 via a roller 1207. This load is applied by a spring 1209.
• the tooth sample 203 is fixed in place in an equally stationary sample receptacle 121 1.
• the first load generator 1203 movable.
• the first load generator 1203 may be orthogonal to a force passing over the Roller 1207 is applied to the flank 207 of the tooth sample 203, are pivoted. As a result, the roller 1207 rolls on the flank 207. In this case, a force applied by the spring 1209 permanently acts on the roller 1207.
• the first load generator 1203 is pivoted by means of an actuator, not shown in FIG. 12, which is connected to the first load generator 1203 via a first coupling rod 1213.
• the second load generator 1205 engages a head of the tooth sample 203 and exerts a pulsating tensile force.
• the second load generator 1205 is suspended linearly movable.
• the second load generator 1205 is connected to a further actuator, not shown in FIG. 12.
• the tensile force applied by the second load generator 1205 manifests itself in the tooth sample 203 as a pulsating bending moment whose vector is orthogonal to the image plane of FIG. 12. This bending moment corresponds to a structural load of the tooth sample 203. Together with the superficially acting load applied by the roller 1207, it is thus possible to realistically simulate the loading situation which is effective during a real tooth engagement.

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ID=60515369

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• 2016
  • 2016-12-09 DE DE102016224629.1A patent/DE102016224629A1/de not_active Withdrawn
• 2017
  • 2017-11-24 EP EP17807809.3A patent/EP3551987A1/de not_active Withdrawn
  • 2017-11-24 CN CN201780070542.8A patent/CN110140039A/zh active Pending
  • 2017-11-24 US US16/466,691 patent/US20200064224A1/en not_active Abandoned
  • 2017-11-24 WO PCT/EP2017/080347 patent/WO2018104077A1/de unknown

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