Gearwheel testing machine with gearwheel

Abstract

A gearwheel testing machine with a gearwheel, wherein the gearwheel engages with a pinion of the gearwheel testing machine, wherein the gearwheel testing machine has a plate on which a bearing housing is mounted which receives bearings for rotatably bearing a brake shaft, wherein the gearwheel is plugged onto the brake shaft and is connected to the brake shaft for conjoint rotation therewith, wherein a first clamping jaw is connected by a rotary joint to a second clamping jaw, wherein a screw part causes the first clamping jaw and the second clamping jaw to be pressed against the brake shaft.

Description

[0001] Gear testing machine with gear

[0002] Description:

[0003] The invention relates to a gear testing machine with a gear.

[0004] It is generally known that a gear testing machine with a gear is a device that must be supplied with electrical energy in order to enable the testing of the gear.

[0005] DE 102022 001 476 A1 discloses a gear testing machine as the closest prior art.

[0006] From DE 199 51 441 A1 a connecting part for a shaft with a braking effect is known.

[0007] A method for testing gears is known from DE 19 55 321 A.

[0008] A gear testing machine is known from US 1 911 435 A.

[0009] The invention is therefore based on the object of developing a gear testing machine with a gear, whereby fast and flexible operation should be possible.

[0010] According to the invention, the object is achieved in the gear testing machine with gear according to the features specified in claim 1.

[0011] Important features of the invention in the gear testing machine with gear are that the gear is in engagement with a pinion of the gear testing machine, wherein the gear testing machine has a plate on which a bearing housing is mounted, which accommodates bearings for the rotatable mounting of a brake shaft, in particular wherein the inner rings of the bearings are placed on the brake shaft, wherein the gear is placed on the brake shaft and is connected to the brake shaft in a rotationally fixed manner, in particular by means of a key connection, wherein a first clamping jaw is connected to a second clamping jaw via a rotary joint, wherein a pressing of the first clamping jaw and the second clamping jaw onto the brake shaft is effected by means of a screw part.

[0012] The advantage here is that the bearing housing can be mounted on the plate at a distance from the pinion's rotational axis that is adjusted to the size of the gear. The distance can therefore be adjusted to the size of the gear; the plate enables the provision of a hole pattern, whereby screws can be fastened in the differently arranged holes of the hole pattern, thus allowing different center distances to be provided quickly and flexibly. In addition, the clamping jaws allow adjustment to the diameter of the brake shaft. This means that shafts of different thicknesses can be used without the need for additional tools or assembly time to adapt to the diameter. The desired friction torque can be set quickly and easily using the screw part, because the clamping jaws are pressed onto the brake shaft when the screw part is actuated. The friction torque can be specified by the rotational position of the screw part.

[0013] In an advantageous embodiment, the pinion is driven by an electric motor of the gear testing machine via a gearbox of the gear testing machine. This allows for a reduction in the speed generated by the motor, thus allowing the load occurring during the intended use of the gear to be specified during the gear testing. After the test, the gear is installed in a gearbox, which is used in an electric drive. The load occurring there can therefore be specified and taken into account during the test.

[0014] In an advantageous embodiment, the gear unit is an angular gear unit, with the electric motor and the angular gear unit being arranged on the side of the plate facing away from the bearing housing. This is advantageous because the electric motor can be arranged below the plate. In an advantageous embodiment, the swivel joint, the first clamping jaw, and the second clamping jaw are arranged on the side of the plate facing away from the bearing housing. This is advantageous because no installation space is required on the upper side for this, thus providing more space for the differently spaced bearing housings.

[0015] In an advantageous embodiment, a bolt attached to the plate acts as a pivot joint, extending through a recess in the first clamping jaw and through a recess in the second clamping jaw. This allows for easy manufacture of the pivot joint.

[0016] In an advantageous embodiment, a limiting disc is attached to the brake shaft on the side of the gear axially facing away from the bearing housing, in particular for axially limiting the gear. This is advantageous in that the gear is secured against axial displacement.

[0017] In an advantageous embodiment, the pinion's rotational axis is aligned parallel to the brake shaft's rotational axis. The advantage here is that the pinion and gear can each be designed with spur gear teeth.

[0018] In an advantageous embodiment, the pinion's rotational axis and / or the brake shaft's rotational axis are aligned parallel to the normal direction of the flat plate. This allows for a simple and robust design of the gear testing machine.

[0019] In an advantageous embodiment, the screw part is arranged on the side of the plate facing away from the bearing housing. This is advantageous because the screw part and the friction torque generation can be located below the plate, thus saving installation space.

[0020] In an advantageous embodiment, the screw part protrudes through a recess in the second clamping jaw and is screwed into a threaded bore in the first clamping jaw having a threaded portion formed on the screw part. It is advantageous in this case that the screw part can be arranged diametrically opposite the rotary joint relative to the rotational axis of the gear. In an advantageous embodiment, the smallest internal diameter of the recess in the second clamping jaw is greater than the largest external diameter of the portion of the screw part located in the recess. It is advantageous in this case that there is play between the screw part and the second clamping jaw. Thus, the second clamping jaw is arranged to be pivotable relative to the first clamping jaw, even though the screw axis of the screw part is oriented tangentially. The opening angle or maximum pivoting angle depends on the play of the screw part in the tangentially continuous recess.

[0021] In an advantageous embodiment, the screw part has a shaft shoulder, wherein the largest outer diameter of the shaft shoulder is larger than the largest clear inner diameter of the recess of the second clamping jaw. This advantageously means that the screw part is axially limited and thus cannot migrate into the second clamping jaw. When the screw part is screwed into the threaded bore of the first clamping jaw, the shaft shoulder presses the second clamping jaw toward the first clamping jaw, so that the brake shaft is clamped between the two clamping jaws, in particular wherein the brake shaft is arranged between the swivel joint and the screw part.

[0022] In an advantageous embodiment, the screw part protrudes from the underside of the plate, in particular into the outer area of ​​the plate. The advantage here is that it is easy to operate because it protrudes into the outer area of ​​the device. For better grip, the screw part has a thickened portion that is provided with knurling on its outer circumference. This thickened portion is arranged in the area of ​​the screw part on the underside of the plate that protrudes into the outer area of ​​the plate. The thickened portion is thus easily accessible and can be designed in the shape of a wheel or disc, enabling simple and safe operation.

[0023] In an advantageous embodiment, the distance between the rotational axis of the pinion and the rotational axis of the gear is a first axis distance, wherein a further bearing housing is mounted on the plate, which accommodates further bearings for the rotatable mounting of a further brake shaft, in particular wherein the inner rings of the further bearings are placed on the further brake shaft, wherein a further gear is placed on the further brake shaft and connected to the further

[0024] Brake shaft is connected in a rotationally fixed manner, in particular by means of a further key connection, wherein a further first clamping jaw is connected to a further second clamping jaw via a further rotary joint, wherein a further screw part is used to press the further first clamping jaw and the further second clamping jaw against the further brake shaft, wherein the axial distance between the axis of rotation of the pinion and the axis of rotation of the further brake shaft and / or the axis of rotation of the further gear is greater than the first axial distance. The advantage here is that tests for different axial distances can be carried out with the same driving pinion.

[0025] In an advantageous embodiment, the first clamping jaw has a concave region which has contact areas which contact the brake shaft, wherein the contact areas press on the brake shaft, wherein the concave region is either composed of two flat surfaces whose normal directions are inclined to each other, i.e. have a non-zero angle to each other, or in the region of contact of the brake shaft with the first clamping jaw has a radius of curvature which is greater in magnitude than the outer radius of the brake shaft in this region,

[0026] Alternatively or additionally, the second clamping jaw has a second concave region which has second contact regions which contact the brake shaft, wherein the second contact regions press on the brake shaft, wherein the concave region is either composed of two second flat surfaces whose normal directions are inclined to one another, i.e. have a non-zero angle to one another, or has a second radius of curvature in the region of contact of the brake shaft with the second clamping jaw, which radius is greater in magnitude than the outer radius of the brake shaft in this region.

[0027] The advantage here is that the brake shaft can be firmly pressed against the first and / or second clamping jaw, as the concave shape prevents the brake shaft from deflecting. The design with two flat surfaces ensures minimal abrasion of the brake pad on the clamping jaws. The design with the larger radius of curvature reliably achieves a very high friction torque.

[0028] Further advantages emerge from the dependent claims. The invention is not limited to the combination of features in the claims. Further possible combinations of claims and / or individual claim features and / or features of the description and / or the figures will become apparent to those skilled in the art, particularly from the problem and / or the problem posed by comparison with the prior art.

[0029] The invention will now be explained in more detail using schematic illustrations:

[0030] Figure 1 shows an oblique view of a gear testing machine according to the invention.

[0031] Figure 2 shows a side view of the testing machine.

[0032] Figure 3 shows a top view of the underside of the testing machine.

[0033] As shown in the figures, the testing machine allows testing gears arranged at different center distances from a pinion driven by an electric motor 9.

[0034] For this purpose, the testing machine has a plate 1, below which the electric motor 9 is arranged and drives a shaft via an angular gear, the axis of rotation of which is aligned parallel to the normal direction of the plate plane.

[0035] A pinion is connected to the shaft in a rotationally fixed manner or is integrally formed on the shaft.

[0036] Thus, the pinion of the electric motor 9 can be set in rotational motion.

[0037] The pinion is in engagement with a respective gear 4, which acts as the respective test object.

[0038] The respective gear 4 is connected in a rotationally fixed manner to a brake shaft 30, in particular by means of a key connection.

[0039] The respective axis of rotation of the respective gear 4 is aligned coaxially to the axis of rotation of the respective brake shaft 30 and parallel to the axis of rotation of the pinion.

[0040] The respective brake shaft 30 is rotatably mounted by means of bearings, in particular roller bearings, housed in a respective bearing housing 3. The respective bearing housing 3 is connected to the plate 1 via a connecting flange 8. For this purpose, the connecting flange 8 is preferably fastened to the plate 1 by means of screws extending through the plate 1 and / or screwed into a threaded bore in the plate 1.

[0041] The respective axis of rotation of the respective brake shaft 30 has different distances from the axis of rotation of the pinion.

[0042] A braking torque is introduced into the respective brake shaft 30 by pressing two clamping jaws (31, 32) onto the brake shaft 30.

[0043] For this purpose, the first 31 of the two clamping jaws and the second 32 of the two clamping jaws are connected to each other via a swivel joint which is arranged on the underside of the plate 1.

[0044] Thus, the two clamping jaws (31, 32) are arranged to be pivotable relative to each other, the pivot axis being the axis of rotation of the rotary joint.

[0045] A screw part 2 projects through the second clamping jaw 32 substantially diametrically opposite to the rotational axis of the brake shaft 30 and is screwed into a threaded hole in the first clamping jaw 31 by a threaded portion of the screw part. When screwing the first clamping jaw 31 into the threaded portion, a

[0046] 30 formed wave shoulder onto the first clamping jaw 31, so that the two clamping jaws 31 and 32 are pressed towards each other.

[0047] For the pivoting movement of the two clamping jaws 31 and 32, the screw part 2 protrudes through the second clamping jaw 32 with sufficient play.

[0048] While the screw part 2 is pushed deeper and deeper into the threaded hole of the first clamping jaw

[0049] 31 is screwed in, the shaft shoulder presses the second clamping jaw 32 closer to the first clamping jaw 31. By thus pressing together the two clamping jaws (31, 32), both clamping jaws (31, 32) are pressed onto the brake shaft 30 and thereby a corresponding braking torque is introduced into the brake shaft.

[0050] The screw part 2, as well as the electric motor 9 and the clamping jaws (31, 32), are arranged below the table 1. Since each bearing housing 3 accommodates bearings which rotatably support a respective brake shaft 30, the brake shaft 30 protrudes at the bottom, where the clamping jaws (31, 32) are pressed against the brake shaft 30.

[0051] The bearing housings 3 are arranged on the upper side of the plate 1, i.e. on the side of the plate 1 facing away from the motor 9.

[0052] To stabilize the pinion and the shaft driven by the electric motor 9 via the angular gear, a mandrel 20 can be moved towards the shaft and pressed against it by means of a linear axis 7.

[0053] The direction of movement of linear axis 7 is parallel to the pinion's rotational axis. The linear movement can be performed manually using a lever or with a motor.

[0054] Different center distances are achieved by varying the distances between the bearing housings and the rotational axis of the rotor shaft.

[0055] Respective limiting discs (5, 6) axially secure the respective gear on the respective brake shaft 30, in particular against axial displacement. The limiting discs (5, 6) are attached to the respective brake shaft 30 by means of a centrally arranged screw.

[0056] Each of the two clamping jaws (31, 32) has a concave area composed of two flat surfaces arranged at an angle to one another, which is pressed against the brake shaft 30.

[0057] Preferably, the side of the limiting disc facing the gear, in particular a flat end face of the gear, is concave, so that the contact surface between the limiting disc and the gear, in particular the end face of the gear, is a circular ring. In this way, the gear is axially limited by the limiting disc, but the pressure surface is well-defined, in contrast to the flat design of the limiting disc on its side facing the gear. With a flat design, the maximum radius of the contact surface depends on the manufacturing quality of the flat surface. In particular, with a concave deviation, the contact surface can be extremely small radially, and thus the gear is insufficiently fixed and executes a wobbling movement.

[0058] Preferably, the side of the limiting disc facing the gear, in particular the flat face of the gear, is designed to be concave such that the axial distance between the limiting disc and the gear, in particular the flat face of the gear, decreases monotonically, in particular strictly monotonically, with increasing radius, particularly radially within the contact surface. Tilting of the gear is thus avoided as best as possible.

[0059] In further embodiments according to the invention, the clamping jaws 31 and 32 are each designed with a differently shaped, concave region. The respective concave region is designed as a curved surface, in particular a cylindrical surface, whose radius of curvature is larger than the outer radius of the brake shaft 30. In particular, this results in line contact.

[0060] In further embodiments according to the invention, the clamping jaws 31 and 32 are coated or formed with a non-metallic brake lining, in particular such that metal and synthetic resin act as friction partners and not two metallic friction partners.

[0061] Alternatively, a non-metallic ring is placed on a protruding area on the underside of the plate 1, with the clamping jaws 31 and 32 pressing on the ring.

[0062] List of reference symbols

[0063] 1 plate 2 screw part

[0064] 3 bearing housings

[0065] 4 gear

[0066] 5 Handrail

[0067] 6 Limiting disc 7 Linear axis, especially lifting axis

[0068] 8 Connecting flange

[0069] 9 Electric motor with angle gear

[0070] 20 thorn

[0071] 30 Brake shaft 31 First clamping jaw

[0072] 32 second clamping jaw

[0073] 33 Swivel joint

Claims

Patent claims:

1. Gear testing machine with gear, wherein the gear is in engagement with a pinion of the gear testing machine, characterized in that the gear testing machine has a plate on which a bearing housing is mounted, which accommodates bearings for the rotatable mounting of a brake shaft, in particular wherein the inner rings of the bearings are placed on the brake shaft, wherein the gear is placed on the brake shaft and is connected to the brake shaft in a rotationally fixed manner, in particular by means of a key connection, wherein a first clamping jaw is connected to a second clamping jaw via a rotary joint, wherein the first clamping jaw and the second clamping jaw are pressed against the brake shaft by means of a screw part.

2. Gear testing machine according to claim 1, characterized in that the pinion is or can be driven by an electric motor of the gear testing machine via a gear of the gear testing machine.

3. Gear testing machine according to one of the preceding claims, characterized in that the gear is an angular gear, wherein the electric motor and the angular gear are arranged on the side of the plate facing away from the bearing housing.

4. Gear testing machine according to one of the preceding claims, characterized in that the rotary joint, the first clamping jaw and the second clamping jaw are arranged on the side of the plate facing away from the bearing housing.

5. Gear testing machine according to one of the preceding claims, characterized in that a bolt fastened to the plate projects through a recess of the first clamping jaw and through a recess of the second clamping jaw as a pivot joint.

6. Gear testing machine according to one of the preceding claims, characterized in that a limiting disc is fastened to the brake shaft on the side of the gear axially remote from the bearing housing, in particular for axially limiting the gear, in particular wherein the side of the limiting disc facing the gear is concave, in particular so that the contact surface between the limiting disc and the gear, in particular the end face of the gear, is a circular ring.

7. Gear testing machine according to one of the preceding claims, characterized in that the axis of rotation of the pinion is aligned parallel to the axis of rotation of the brake shaft.

8. Gear testing machine according to one of the preceding claims, characterized in that the axis of rotation of the pinion and / or the axis of rotation of the brake shaft is aligned parallel to the normal direction of the flat plate.

9. Gear testing machine according to one of the preceding claims, characterized in that the screw part is arranged on the side of the plate facing away from the bearing housing.

10. Gear testing machine according to one of the preceding claims, characterized in that the screw part projects through a recess of the second clamping jaw and is screwed into a threaded bore of the first clamping jaw with a threaded area formed on the screw part.

11. Gear testing machine according to one of the preceding claims, characterized in that the smallest clear diameter of the recess of the second clamping jaw is larger than the largest outer diameter of the area of ​​the screw part located in the recess.

12. Gear testing machine according to one of the preceding claims, characterized in that the screw part has a shaft shoulder, wherein the largest outer diameter of the shaft shoulder is larger than the largest clear inner diameter of the recess of the second clamping jaw.

13. Gear testing machine according to one of the preceding claims, characterized in that the screw part protrudes, in particular on the underside of the plate, in particular protrudes into the outer environment of the plate.

14. Gear testing machine according to one of the preceding claims, characterized in that the distance between the rotational axis of the pinion and the rotational axis of the gear is a first axial distance, wherein a further bearing housing is mounted on the plate, which accommodates further bearings for the rotatable mounting of a further brake shaft, in particular wherein the inner rings of the further bearings are placed on the further brake shaft, wherein a further gear is placed on the further brake shaft and is connected in a rotationally fixed manner to the further brake shaft, in particular by means of a further key connection, wherein a further first clamping jaw is connected to a further second clamping jaw via a further rotary joint, wherein a further screw part is used to press the further first clamping jaw and the further second clamping jaw against the further brake shaft,wherein the center distance between the axis of rotation of the pinion and the axis of rotation of the further brake shaft and / or the axis of rotation of the further gear is greater than the first center distance.

15. Gear testing machine according to one of the preceding claims, characterized in that the first clamping jaw has a concave region which has contact areas that contact the brake shaft, wherein the contact areas press on the brake shaft, wherein the concave region is either composed of two flat surfaces whose normal directions are inclined to one another, i.e., have a non-zero angle to one another, or has a radius of curvature in the region of contact of the brake shaft with the first clamping jaw which is greater in magnitude than the outer radius of the brake shaft in this region, and / or that the second clamping jaw has a second concave region which has second contact areas that contact the brake shaft, wherein the second contact areas press on the brake shaft, wherein the concave region is either composed of two second flat surfaces,whose normal directions are inclined to each other, i.e. have a non-vanishing angle to each other, or in the area of ​​contact of the brake shaft with the second clamping jaw has a second radius of curvature which is greater in magnitude than the outer radius of the brake shaft in this area.

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