DE102006014237A1 - Gear twist action test stand has two transmission shafts and two reverse drive units forming a closed-circuit - Google Patents

Abstract

In a process to manufacture a gear assembly, the gear is tested on a twist test stand on which two or more gear assemblies are installed. The twist action is measured against distortion of the gear housing. The test stand has two transmission shafts and two reverse drive units forming a close-circuit in which the twist action is generated by one or both of the reverse-action units.

Description

The The invention relates to a stress test rig, a process for the production a gearbox and a gearbox.

Out the Internet site http://www.tri.fh-mannheim.de/fzg.htm is a Stress test rig known, with input shaft of the gear to be tested with the input shaft a first transmission is connected and the output shaft of the tested Gear is connected to the output shaft of the first transmission. The gearboxes are connected in parallel, so to speak. It is one of the Connecting shafts interrupted by means of a coupling. The tension is achieved in that by means of a lever arm, the first coupling half against the second coupling half is twisted and then the coupling is firmly connected. Thus is generates the tension within the test bench and at the beginning of their worth also known.

advantage The method is that a connected motor for driving the waves only the power loss of the test bench must apply and not the rated power or other high power levels. Consequently is the drive of the test bench inexpensive and easy to implement.

adversely is that the tension in the course of operation not adjustable or changeable is. For an adjustment would have the operation will be interrupted, the clutch will be opened and the lever arm attached with weights are used for resetting the tension.

Consequently is also an automated driving through of load cycles, that is predefinable Load conditions, not possible. In particular, there is no traversing of states in four-quadrant operation Executable with electric motors.

Out the publication Maschinenbau RUBIN 2004, page 72, "Caries prophylaxis for gear heavyweights" is known as a stress test rig, where an engine is a test gear drives, which is a transmission gear the test bench drives, whose output is connected to a generator, wherein the energy generated by this is supplied to the driving motor. In this way is from the electrical supply network also only to supply the low electrical power, the power loss the test bench total corresponds. However, a costly engine and a costly generator necessary in their rated power in the order of magnitude of the test gear lie. Furthermore is for the generator and the engine still each control electronics and a power electronics necessary, in particular corresponding power converter.

at another stress tester, such as on page 70, third column to page 71, first column, and the there Info 2 field is a similar one Arrangement as in the Internet page http://www.tri.fh-mannheim.de/fzg.htm where even a small motor to compensate for the power loss the test bench is necessary, but a hydraulically actuated tension clutch is provided.

adversely is in hydraulics that hydraulic oil can leak out and soiling may occur. Furthermore is the hydraulic tension clutch and also the hydraulic supply arrangement very elaborate and expensive.

From the DE 34 24 923 C2 a Verspannprüfstand is known in which the tension is introduced by means of a Verspannkupplung, wherein the coupling is opened for introducing the tension.

From the DE 31 00 848 C2 is a stress tester with a tensioning gear in a closed design known, comprising at least four transmissions. In this case, a coaxial transmission must be provided to generate the tension by pivoting the same gear.

From the US 3 122 643 is known a flexible wave testing apparatus comprising at least three gears. For specimens with large dimensions, especially transverse to the wave strands 17 and ( 37 . 41 . 43 . 45 . 47 . 48 ), is a complex redesign of the transmission ( 22 . 24 ) and ( 13 . 23 ) and the adjusting device ( 28 . 55 ) necessary, in particular to match the gear ratios of the transmission to each other.

From the DE 29 08 860 A1 is a closed tensioning gear for testing rotating mechanical transmission elements known which comprises at least four gear stages (see Fig.).

Of the The invention therefore has the object of developing a stress test stand, to make it easier and cheaper to design.

According to the invention Task at the stress test rig according to claim 1 or 14, in the method according to claim 25 and in the transmission according to the features indicated in claim 26 solved.

Important Features of the invention in the stress test stand are that this at least two deflection devices, wherein the tension by relative Twisting at least one of the deflection devices is generated. In particular, therefore, the invention is advantageous over the State of the art transmission stages can be saved. Thus, the Reduce production costs. Furthermore, it is advantageous that the Tension during the intended use of the stress test rig can be introduced.

Under Deflection device is generally understood a device that includes at least one driving and one driven shaft, wherein a torque acting on the driving shaft to the transmitted abortive wave and vice versa, and wherein the transmitted torque at the abortive wave at least in the direction and point of attack - depending on Deflection device also in magnitude - different from the attacking torque.

at an advantageous embodiment connect the deflection the wave strands to a closed clamping circuit.

From The advantage here is that only one motor is necessary to drive the test bench is that supplies the power loss. Thus, the test bench economical executed. Furthermore is a twisting of the housing the deflecting device during of the operation easily possible. Only a twist, so tilt or similar movement, is necessary. Since the tipping force is simple and easily determinable, can be a costly Torque sensor omitted in the shaft train.

at In a further advantageous embodiment, the shaft strands are in at least a twisted position arranged in parallel. It is advantageous that the bracing test bench is space-saving buildable.

at a further advantageous embodiment comprises at least one Wave strand at least one variable-length Component, in particular the change in length along the axis of this Component takes place. The advantage here is that by the relative Turning a deflection at least one change in length the variable-length Component is effected. Thus, the bearing for the twisting movement is easy startable. In particular, no axial tensile forces act during rotation the wave strands.

at a further advantageous embodiment is the fulcrum for the rotation and / or the axis of rotation for the rotation of a shaft axis of a shaft of a deflection device is included, in particular in a input shaft or output shaft. Thus, advantageously, space can be saved.

Another Advantage of the invention is that, in contrast to the prior art short-building, rigid connecting shafts are used.

at An advantageous embodiment is a housing of a second transmission rotatably mounted. The advantage here is that a housing in this easy way to store and thus rotatable during operation is. This results in the advantages of the invention.

at An advantageous embodiment is a housing of a second transmission rotatably supported such that the axis of rotation parallel to the input shaft and / or Output shaft of one of the gear is aligned. Especially the input shafts and the output shafts are each about cardan shafts connected. In particular, the input shafts and the output shafts have flanges or couplings for connection to the cardan shafts. From The advantage is that for the invention suitable coupling devices for coupling the gear used are.

at According to an advantageous embodiment, the cardan shafts are constant velocity universal joint shafts. Alternatively, the propeller shafts are cardan shafts, with the input shafts and output shafts of the gear are aligned in parallel. If the cardan shafts are cardan shafts are input shafts and output shafts and Kardangelenkwellen align such that the rotation transmission runs uniformly, in particular by parallel aligned PTO shaft end pieces. It is advantageous that simple and inexpensive Components are usable.

at an advantageous embodiment is the rotation of an actuator executable. The advantage here is that during operation pretending and in conjunction with a sensor too allows a rules is.

at In an advantageous embodiment, the actuating element is a power actuator executed. The advantage here is that the asked force in direct connection with the tension in the clamping circuit of the test stand. Thus, the Can be specified by means of the power actuator in a simple manner.

In an advantageous embodiment, a sensor for determining the force of the power actuator is provided. The advantage here is that the determination of the Verspannmomentes is simple and inexpensive and thus allows a regulation of the Verspannmomentes to set values, in particular in particular to setpoints which can be changed during operation. Advantageously, so the tension during operation of the test bed is controlled or even regulated.

Vorteilig when using a sensor to determine the force in the force plate is that a torque sensor in the Wellnsträngen is dispensable. To this Way is inexpensive the tension can be determined.

hydraulic is advantageous dispensable.

at an advantageous embodiment of the stress test facility does not include only parallel shaft gear, such as helical gear. Of the closed clamping circuit of the stress test stand is made of angular gears, coaxial gearboxes, such as planetary gears and cycloid gears, and / or parallel shaft gears composable. Is an advantage in that they are combinable in a suitable manner and thus very extensive and complex testing tasks with accordingly constructed strands executable are. Depending on the tensioning circle, auxiliary gears are used to close the strand add.

at According to an advantageous embodiment, the transmission has the same transmission ratio. From The advantage here is that not only one but two at the same time Transmission are verifiable. This saves time during the exam the gearbox. Here is the direction of rotation of the shafts of the transmission of the strand allowed and to choose correctly from the expert.

basics Features of the manufacturing method are that the method at least The following steps are included: The gearbox is manufactured and checked afterwards, where to check a stress tester is used according to at least one of the preceding claims. Every transmission So is by means of the test bench checked. Advantageous Thus, the production of the transmission is overall more cost-effective, because the stress test economical and easier to execute is.

• – das Getriebe wird als vorläufige Variante konstruiert,
• – die vorläufige Variante wird hergestellt,
• – die hergestellte vorläufige Variante wird geprüft,
• – das Getriebe wird als verbesserte Variante konstruiert und hergestellt.

Alternatively, the manufacturing method has as essential features the following steps:

• - the gearbox is designed as a temporary variant,
• - the preliminary variant is produced,
• - the provisional variant produced is examined,
• - The gearbox is designed and manufactured as an improved version.

Advantageous So now is not every gear to check, but it suffices the test results as part of the construction of the improved variant. Thus, particularly robust gear with durable durable bearings and waves and gearing parts produced.

The The invention also relates to the products of said processes, ie accordingly manufactured gear.

Further Advantages emerge from the subclaims.

1

engine

2

first Gearbox, fixed

3

propeller shaft

4

propeller shaft

5

joint

6

second transmission

7

swiveling mounted mounting plate

8th

connection for tilting force actuator

20

first gear

21

second gear

22

Kippkraftsteller

30

engine

31

first angle gear

32

second angle gear

33

clutch

34

belt

35

third angle gear

36

fourth angle gear

40

axis of rotation the output shaft

41

first coaxial transmission

42

second coaxial transmission

43

lever

44

feast part

60

engine

61

first transmission

62

propeller shaft

63

 mounting plate

64

second transmission

65

wave

66

hollow shaft

67

shrink disc

68

connection for tilting force actuator

69

camp

The invention will now be explained in more detail with reference to figures:
In the 1 An example of an inventive stress test rig is shown.

The motor 1 is executable, for example, as an electric motor, which is powered by a converter. The motor 1 drives a first gearbox 2 which is fixedly mounted on the floor or a receiving plate. Internal combustion engines or other engines would be usable.

The input shaft of the first transmission is via a propeller shaft 3 connected to the input shaft of the second transmission.

The output shaft of the first transmission is via a propeller shaft 4 with the output shaft of the second transmission 6 connected.

A first shaft strand thus includes the propeller shaft 3 , a second shaft strand comprises the propeller shaft 4 ,

The second gear is on a receiving plate 7 mounted, which is rotatably mounted by means of a joint 5 , So there is at least one axis of rotation for the second transmission available, which is aligned parallel to the input shaft and output shaft of the first transmission.

The two gears ( 2 . 6 ) act as a deflection device and close the clamping circuit. The clamping circuit thus comprises the two gears ( 2 . 6 ) and the two wave strands.

The receiving plate 7 has a connection 8th for an actuating element, in particular a power actuator, on.

This drives the receiving plate 7 to rotate about said axis of rotation. In this way, the twist angle is generated. The rotation of the receiving plate and the connected housing of the second transmission creates a twist, so torsion, in the shaft train and thus in the Verspannkreis, which leads via the rigidity to a Verspanndrehmoment.

The Cardan shafts should be designed and mounted in such a way that transfer them uniformly.

When Cardan shafts can be provided with constant velocity universal joint shafts.

Alternatively, but also in 1 In this case, care must be taken that all four shaft axes of the transmission, that is, the two input shafts and output shafts, must be oriented in parallel in order to achieve uniformity. In particular, the Gelenkwellenendstücke are aligned in parallel or have the same amount of bending angles of the Gelenkwellenendstücke to the horizontal, the Gelenkwellenendstücke are provided in a plane.

In 1 the gears are exemplified as single-stage spur gear. But there are also transmissions with multiple stages usable.

at further embodiments of the invention are gearboxes with angular gear stages or planetary gear stages or Zyklogetriebestufen used, but the transmission must be combined with other transmissions suitable for closure of the clamping circuit.

In a further embodiment of the invention is in the region of the terminal 8th a load cell or a corresponding sensor provided. In this way, the determination of the force for lifting the receiving plate 7 allows.

There there is a clear relationship with the tensioning moment in the test bench, the tensioning moment can be determined from the force value.

through the sensor is an indication and / or regulation of the tension executable during the Operation.

In a further embodiment of the invention is used as an actuating element on the connection 8th a device that uses the weight of a mass to connect 8th deflects to generate the twist angle.

at a further embodiment of the invention the actuator comprises a spring with deflection for adjustment the spring force.

In a further embodiment of the invention, the terminal 8th connected to a hydraulic actuator, which includes a sensor as a hydraulic pressure sensor. Thus, a conclusion on the force and / or strain is possible from the pressure reading.

Advantageously, the Verspannmoment the test bench during operation can be changed easily and quickly by the tilting force adjuster on the connection 8th other heights, so other forces, sets.

In 2a and 2 B the operation of the arrangement is explained more clearly:

In 2a is the receiving plate 7 still parallel to the receiving plate of the first transmission 2 arranged. The first gear 20 and the second gear 21 are marked with black lines to mark their angle of rotation.

In 2 B has the power controller 22 a rotation of the receiving plate 7 caused by the angle α. Since you can imagine the gears of the first transmission as immutable, the rotational angle β for the second gear is present in this mental case. The rotation angle β is a function of the rotation angle α and the transmission ratio i:

als Verhältnis der Winkelgeschwindigkeiten des ersten Getriebes definiert, wenn dieses frei drehend verwendet wird. Das zweite Getriebe weist dasselbe Übersetzungsverhältnis auf.Here is the gear ratio

defined as the ratio of the angular speeds of the first gear when it is used freely rotating. The second transmission has the same transmission ratio.

For a one-step Helical gear is thus i <0. Positive i are known by a chain drive, as well as bicycles realizable. Alternatively, a gear with a straight Number of gear stages for realization vorsehbar.

The Rotation about the rotation angle β a measure of the generated Tensioning moment in the test bench, when the stiffness is known.

2a and 2 B serve for the theoretical explanation. In practice, the rotation will be distributed uniformly throughout the test stand, ie in the shafts of the first and second gears and in the propeller shafts.

3 shows the ratio of the rotation angles α and β as a function of i. It can be seen that for i = +1 the stress test rig according to the invention can not be used. Examples of such a case are a first and second gear with two identical, connected via a chain gears.

For very much small i, especially much smaller 1, are already the lowest Angle of rotation α causes large distortions in the strand in the test bench. At big Stiffness in the test bench and in the clamping circuit can then be with power controllers with small Hub, such as piezoelectric elements and the like, achieve large Verspannmomente in the test bench.

Of the transmission test bench is for All gear sizes advantageous usable, in particular from the field of nano-transmissions or micro-transmissions up to big ones Industrial gearboxes with a few megawatts of maximum transmittable power. Extremely advantageous the invention is applicable in the field of transmissions which more than 50kW maximum transferable Have performance. While In operation, various sizes are measurable, such as Noise, Temperature development and the like.

One Sensor for determining the force of the power actuator is provided for determining the tensioning moment.

In 4 another embodiment of the invention is shown. This drives the engine 30 over a belt 34 the first shaft of the stress test rig. In contrast to 1 where the tensioning circle consists of only two parallel shaft gears, the tensioning circle now comprises four gears, namely the first angular gear 31 which via the clutch 33 the second angular gear 32 drives, this via a cardan shaft with the fourth angular gear 36 connected via the other clutch 33 with the third angular gear 35 connected is. The cardan shaft 4 connects first with third gear ( 31 . 35 ). The first deflection device thus comprises in this embodiment, the transmission ( 31 . 32 ) and the clutch 33 , the second deflection device comprises the gears ( 35 . 36 ) and the other clutch 33 ,

The Product of translation numbers of the first and second gear is equal to the product of the gear ratios of the third and fourth gears or equal to its reciprocal.

In an alternative embodiment of the invention, instead of the couplings 33 in 4 provided variable-length shafts. Thus, the stress test rig can be adapted without costly redesigns to different dimensions of specimens, especially to large dimensions transverse to the shaft direction.

6 shows as another embodiment of the invention a stress test rig. An engine 60 drives a first gearbox via a shaft 61 on, which is firmly mounted. The driving shaft of the first gearbox 61 is over a propeller shaft 62 with the driving shaft of a second transmission 62 connected. The PTO shaft 62 is advantageously designed as a variable-length universal joint shaft.

The second transmission 62 is on a receiving plate 63 assembled. The receiving plate 63 has funds 68 for connecting a tilting force plate, not shown.

The driven-side shaft of the second transmission 64 is about a wave 65 with the output-side shaft of the first transmission 61 connected. Thus, the two gears each act as a deflection device. The first shaft train comprises the propeller shaft 62 , the second shaft train includes the shaft 65 , The clamping circuit thus comprises the two deflection devices and two shaft strands and is thus closed.

The output-side shafts of the transmission are advantageous as hollow shafts 66 formed, and the connection between the hollow shaft 66 and wave 65 via shrink discs 67 ,

The wave 65 is still in such a camp 69 stored that the receiving plate 63 with the housing of the second transmission 64 around the shaft 65 is pivotable or rotatable. Advantageously, this pivoting takes place by actuating one on the means 68 attacking Kippkraftstellers. By pivoting according to the invention torsion in the strand of waves ( 62 . 65 ) and gears ( 61 . 64 ) and thus introduced into the Verspannkreis.

Thus, the transmission 64 even during engine operation 60 pivotable.

In an embodiment according to the invention, at least one transmission ( 61 . 63 ) the device to be tested.

In another embodiment of the invention, the propeller shaft 62 the device to be tested. Thus not only gears but also drive shafts can be tested.

In an alternative embodiment of the invention, the device to be tested in the the propeller shaft 62 or in the the shaft 65 integrated shaft.

In 5a another embodiment of the invention is shown. In a shaft train, which is essentially the first shaft train of the 4 corresponds, two coaxial transmission, such as planetary gear or Zyklogetriebe interposed. A first deflection device comprises the gears ( 31 . 36 ), a second deflection device comprises the transmission ( 32 . 35 ).

The first coaxial transmission 41 is firmly mounted. The second coaxial transmission 42 is rotatably mounted with its housing in the fixed part 44 , The associated axis of rotation is the axis of rotation 40 the output shaft of the second coaxial transmission.

In 5b is a section outlined by the area of the lever 43 , which is fixed to the housing of the second coaxial transmission 42 connected is. Now if the power plate 22 the lever 43 pushes upwards, the housing of the gearbox leads 42 a rotation about the axis of rotation of its output shaft. Thus, distortion is brought into the strand and in turn is even regulated if appropriate sensors are provided.

So is the tension in coaxial and in other transmissions by means Rotation of the housing producible and even during of operation.

In an alternative embodiment of the invention between the gears ( 36 . 31 ) and between the gears ( 32 . 35 ) in 5a each variable-length waves provided, the change in length is synchronously vornehmbar. Thus, the stress test rig without costly redesigns to different dimensions of specimens ( 42 . 44 ) to adjust.

In an alternative embodiment of the invention is between the gears ( 36 . 31 ) and between the gears ( 32 . 35 ) in 5a each provided a releasable coupling. Thus, in the stress test rig, the wave strands can easily move away from one another, in particular for the exchange of the test specimens ( 41 . 42 ).

Claims (26)

Stress test rig, comprising, two shafting and two deflection devices in a tension circle, in which the Tension by relative rotation of at least one of the deflection devices is produced. Stress test rig according to at least one of the preceding claims, characterized that the deflecting the shaft strands to a closed Connect the clamping circuit. Stress test rig according to at least one of the preceding claims, characterized that the wave strands are arranged in parallel in at least one twisting position. Stress test rig according to at least one of the preceding claims, characterized that at least one shaft strand at least one variable-length Component, in particular the change in length along the axis of this Component takes place. Stress test rig according to at least one of the preceding claims, characterized that the relative rotation of the one deflecting device at least a change in length the variable-length Component causes. Stress test rig according to at least one of the preceding claims, characterized that the fulcrum for the twisting and / or the axis of rotation for the rotation of a shaft axis a shaft of a deflection device is included, in particular a input shaft or output shaft. Stress test rig according to at least one of the preceding claims, characterized in that the pivot point for the rotation and / or the rotation axis for the twisting except half of the housing of the deflection device is provided or at least not included in the shaft axis of a shaft of a deflection device. Stress test rig according to at least one of the preceding claims, characterized that the input shafts and the output shafts of the deflecting devices each via cardan shafts in particular, wherein the input shafts and the output shafts each have flanges or couplings for connection to the Propeller shafts. Stress test rig according to at least one of the preceding claims, characterized that at least one of the propeller shafts a variable-length propeller shaft, in particular a cardan shaft, is. Stress test rig according to at least one of the preceding claims, characterized that the cardan shafts are cardan shafts, wherein the input shafts and output shafts of the deflecting devices are aligned in parallel. Stress test rig according to at least one of the preceding claims, characterized that the cardan shafts are cardan shafts, wherein input shafts and output shafts and cardan shafts are aligned in such a way that the rotary transmission uniform runs, in particular by parallel aligned Gelenkwellenendstücke or equal in magnitude bending angle the propeller shaft end pieces against the horizontal, the Gelenkwellenendstücke in one Level are provided. Stress test rig according to at least one of the preceding claims, characterized that the cardan shafts are constant velocity universal joint shafts. Stress test rig according to at least one of the preceding claims, characterized in that at least one deflecting device comprises a test object, in particular a test transmission, includes. Stress test rig, full at least two wave strands and two deflection devices in a tension circle, in which the Deflection devices each comprise at least one variable-length component, with which the spatial Distance of the wave strands changeable to each other is. Stress test rig according to claim 14, characterized in that the axes of the change in length Stand perpendicular to the axes of the wave strands. Stress test rig according to claim 14 or 15, characterized in that at least in one of the wave strands at least one gear, in particular a coaxial, provided is, wherein the tension generated by relative rotation of the transmission housing becomes. Stress test rig according to at least one of the claims 1 to 16, characterized in that in at least one shaft train a test object, in particular a test gear, is provided. Stress test rig according to at least one of the claims 1 to 17, characterized in that the rotation of an actuating element executable is. Stress test rig according to at least one of the claims 1 to 18, characterized in that the actuating element with a Transmission, in particular a test gear, solvable connected is. Stress test rig according to at least one of the claims 1 to 19, characterized in that the actuating element as a power actuator is executed. Stress test rig according to at least one of the claims 1 to 20, characterized in that a sensor for determining the force of the power actuator is provided, in particular for determination the tensioning moment. Stress test rig according to at least one of the claims 1 to 21, characterized in that the tension during the Operation of the test bench controllable or even controllable. Stress test rig according to at least one of the claims 1 to 22, characterized in that the closed clamping circuit the stress test rig angular drives, coaxial transmissions, such as planetary gears and Zyklogetrieben, and / or parallel shaft gear composed is. Stress test rig according to at least one of the claims 1 to 23, characterized in that the transmission ratios the transmission multiplied by one, in particular in pairs. Method for producing a transmission, characterized in that - in a first method step, the gear forth - and in a second process step, the transmission is checked thereafter, wherein for testing a stress test stand is used according to at least one of claims 1 to 24. Transmission, characterized in that the transmission prepared by a method according to claim 25