Simulation device for simulating threaded joints in screw-driving tools

Abstract

To provide a cost effective simulation device for screw joint simulation of a screw driving tool.SOLUTION: A simulation device comprises measurement unit 13 for measuring torque M that a screw driving tool 2 coupled to a test connection unit 11 exerts onto the test connection unit 11 and for measuring an angle of rotation by which the test connection unit 11 coupled to the activated screw driving tool 2 rotates about a rotation axis Z. The simulation device 1 comprises a converter unit 14, and the converter unit 14 is mechanically connected to the test connection unit 11. The converter unit captures the torque M that the screw driving tool 2 coupled to the test connection unit 11 exerts onto the test connection unit 11, converts the torque into braking force F, and applies the braking force F to a brake unit 12.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a simulation device for threaded joint simulation of a screw-driving tool according to the preamble of the independent claim. The present invention also relates to a method for performing a threaded joint simulation of a screw-driving tool using a simulation device according to the preamble of the independent claim. [Background technology]

[0002] According to the guideline VDI / VDE 2647 of February 2013, a screwdrive tool is both a motor-driven screwdrive tool and a manually operated torque wrench. The screwdrive tool can be started, which causes it to rotate about its axis of rotation and thus exerts a torque on the connecting element.

[0003] The connecting elements are equipped with a screw thread and are bolts, nuts, etc. The connecting elements are used to connect components. The connection is made by a clamping force between the components. The clamping force ensures that the components can be used under maximum operating forces.

[0004] Thus, the torque exerted by the started screw-driving tool serves to generate a clamping force. For this purpose, the screw-driving tool increases the exerted torque over time and / or increases the exerted torque via the angle of rotation. The increase in the exerted torque is performed up to a nominal torque specific to the clamping force and / or up to a nominal angle of rotation specific to the clamping force. The nominal torque and / or the nominal angle of rotation can be predefined and set for the screw-driving tool. In the following, the nominal torque and / or the nominal angle of rotation are referred to as nominal values.

[0005] The screw-driven tool is equipped with an indicator system. As soon as the nominal value is reached, the application of torque by the screw-driven tool is stopped. The indicator system may operate according to different functional principles. For example, a click-type torque wrench automatically interrupts the application of torque once the nominal value is reached. An acoustic torque wrench automatically triggers an acoustic or optical signal once the nominal value is reached. The indication of the screw-driven tool displays the currently exerted torque and / or the current nominal angle of rotation on a scale or an electronic screen.

[0006] Screw-driven tools of the type mentioned above are used in many industrial manufacturing processes, the performance of which is tested at intervals to ensure that they actually achieve the nominal values ​​set.

[0007] For this purpose, the guideline VDI / VDE2647 of February 2013 specifies what should be tested and how. A performance test of a screw-driven tool is called a threaded joint simulation. The threaded joint simulation is performed using a simulation device which comprises a test connection element, a brake unit and a measurement unit. The screw-driven tool is coupled to the simulation device via the test connection element. The test connection element is capable of rotating about an axis of rotation. The brake unit and the test connection element are mechanically connected to one another. The measurement unit is arranged between the test connection element and the brake unit. The measurement unit comprises a torque transducer and a rotation angle transducer.

[0008] A screw drive tool coupled to the simulation device is actuated to exert a torque on the test connection element. The applied torque causes the test connection element to begin to rotate about the axis of rotation. A brake unit is actuated to brake the test connection element. The torque transducer measures the torque and the rotation angle transducer measures the rotation angle that the test connection element rotates about the axis of rotation.

[0009] Such a simulation device is known from WO 2016 / 103150 A1. The brake unit comprises a brake disc and brake pads. The brake disc is mechanically connected to the test connection element, whereas the brake pads are arranged stationary. The brake unit is hydraulically actuated and comprises a hydraulic pump and a brake piston. The hydraulic pump pumps brake fluid and acts against the brake piston, which acts in frictional engagement against the brake disc and brakes the test connection element.

[0010] Procurement and maintenance of hydraulic brake units of the type referred to above is expensive, and so are simulation devices. [Prior art documents] [Patent documents]

[0011] [Patent Document 1] International Publication No. 2016 / 103150A1 Summary of the Invention [Problem to be solved by the invention]

[0012] It is an object of the present invention to provide a cost-effective simulation device for threaded joint simulation of a screw driving tool. [Means for solving the problem]

[0013] This object is achieved by the mechanisms forming the features of the independent claims.

[0014] The present invention relates to a simulation device for threaded joint simulation of a screw-driving tool comprising a test connection unit capable of coupling a screw-driving tool to the simulation device, the screw-driving tool being capable of being started and coupled to the test connection unit in the started state, rotating the test connection unit about a rotation axis and exerting a torque on a test connection element, the screw-driving tool in the started state and coupled to the test connection unit comprising a measurement unit for measuring the torque exerted on the test connection unit and for measuring the angle of rotation the test connection unit rotates about the rotation axis when coupled to the started screw-driving tool, the simulation device comprising a converter unit, the converter unit being mechanically connected to the test connection unit, the converter unit being in the started state and capturing the torque exerted on the test connection unit by the screw-driving tool coupled to the test connection unit, converting said torque into a braking force and applying the braking force to the braking unit.

[0015] The invention also relates to a method for performing a threaded joint simulation of a screw-driven tool using a simulation device according to the independent claims, the method comprising the following steps: in a first step a nominal value is set on the screw-driven tool, which is coupled to the simulation device via a test connection unit, in a third step the screw-driven tool is started, which rotates the test connection unit about its axis of rotation and exerts a torque on the test connection unit, in a third step the torque exerted by the screw-driven tool is captured by a converter unit and converted into a braking force, in a third step the braking force is applied by the converter unit to said braking unit.

[0016] Thus, in contrast to the prior art, such as that described in WO 2016 / 103150 A1, the simulation device according to the invention no longer requires a hydraulic brake unit, making the device cost-effective. Instead, the torque exerted by the screw-driven tool is received by a converter unit and converted into a brake force. This brake force is applied to the brake unit.

[0017] Further embodiments of the subject matter of the invention are claimed in the dependent claims.

[0018] In the following, the invention is explained in more detail, by way of example, with reference to the drawings. [Brief description of the drawings]

[0019] [Figure 1] FIG. 1 shows a longitudinal section of a simulation device 1 with a screw driving tool 2 coupled thereto. [Diagram 2] FIG. 2 is a longitudinal section according to FIG. 1, with the screw driving tool 2 and the holding unit 15 being actuated. [Figure 2a] FIG. 7 is an enlarged cross-sectional view of the holding unit 15 in the non-actuated state according to FIGS. 1, 5 and 6. [Figure 2b] FIG. 5 is an enlarged cross-sectional view of the actuated holding unit 15 according to FIGS. [Diagram 3] 3 is a longitudinal section according to FIG. 2, in which the converter unit 14 is in mechanical contact with the brake unit 12. FIG. [Figure 3a] FIG. 7 is a longitudinal section through the converter unit 14 according to FIGS. 1, 2 and 6, without mechanical contact with the brake unit 12. [Figure 3b] FIG. 6 is an enlarged cross-sectional view of the converter unit 14 according to FIGS. 3 to 5, which is in mechanical contact with the brake unit 12. [Figure 4] 3, in which the brake spring element 12.3 of the brake unit 12 is compressed by the converter unit 14. FIG. [Figure 4a]1 to 3 and 6 in an enlarged cross-sectional view of the brake spring element 12.3 of the brake unit 12 in the uncompressed state. [Figure 4b] 6 shows an enlarged cross-sectional view of the brake spring element 12.3 of the brake unit 12 in the compressed state according to FIGS. 4 and 5. FIG. [Diagram 5] FIG. 5 is a longitudinal section according to FIG. 4, without the screw driving tool 2 coupled thereto. [Figure 6] FIG. 6 is a longitudinal section according to FIG. 5 with the holding unit 15 stopped. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0020] Like reference numbers refer to like objects throughout the drawings.

[0021] Figures 1 to 6 show longitudinal sections through a preferred embodiment of a simulation device 1 for threaded joint simulation of a screw driving tool 2. The longitudinal sections are made along the axis of rotation Z. Figures 2a, 2b, 3a, 3b, 4a and 4d show enlarged cross-sections of Figures 1 to 6.

[0022] According to the guideline VDI / VDE 2647 of February 2013, the screw-driven tool 2 is a motor-driven screw-driven tool or a manually operated torque wrench. The screw-driven tool 2 can be started and, depending on the screw joint, the started screw-driven tool 2 rotates continuously and / or discontinuously about the axis of rotation Z and exerts a torque M.

[0023] In the course of the threaded joint simulation, the screw-driving tool 2 increases the applied torque M over time and / or increases the applied torque M via the angle of rotation. The increase in the applied torque M is performed up to a nominal torque and / or up to a nominal angle of rotation. The nominal torque and / or the nominal angle of rotation can be predefined and set for the screw-driving tool 2. In the following, the nominal torque and / or the nominal angle of rotation are also referred to as nominal value S.

[0024] The screw-driving tool 2 is equipped with an indicator system. During the threaded joint simulation, the screw-driving tool 2 stops applying torque as soon as the nominal value S is reached. The indicator system may operate according to different functional principles: The screw-driving tool 2 may be a click-type torque wrench that automatically releases itself when the nominal value is reached. The screw-driving tool 2 may also be an acoustic torque wrench that automatically triggers an acoustic or optical signal when the nominal value is reached. The screw-driving tool 2 may also be an indicating screw-driving tool, which displays the applied torque M on a scale or on an electronic screen.

[0025] The basic components of the simulation device 1 are a test connection unit 11 , a brake unit 12 , a measurement unit 13 , a converter unit 14 and a holding unit 15 .

[0026] The simulation device 1 comprises a housing 10. The housing 10 is made of several parts and comprises an upper housing part 10.1 and a housing bottom part 10.2. The housing end close to the screw-driving tool is arranged in the upper housing part 10.1 and the housing end remote from the screw-driving tool is arranged in the housing bottom part 10.2. The housing 10 is of hollow cylindrical shape and extends along a rotation axis Z. The housing 10 has a cavity. The cavity extends from the upper housing part 10.1 to the housing bottom part 10.2. The housing 10 performs several functions, for example it protects the basic components of the simulation device 1 from mechanical damage and furthermore gives the simulation device 1 mechanical stability against deflections along and twisting around the rotation axis Z during the threaded joint simulation.

[0027] The test connection unit 11 is designed to allow the coupling of a screw-driving tool 2 to the simulation device 1 for carrying out a threaded joint simulation. The test connection unit 11 is cylindrical in shape and extends along a rotation axis Z. The test connection unit 11 comprises a test connection element 11.1 and a rotating body 11.2. Preferably, the test connection element 11.1 and the rotating body 11.2 are manufactured in one piece. The test connection element 11.1 is arranged at the housing end of the upper housing part 10.1 close to the screw-driving tool. The test connection element 11.1 is accessible from the outside through an opening in the upper housing part 10.1. The test connection element 11.1 is formed according to standard specifications and is, for example, square in shape. The screw-driving tool 2 is coupled to the simulation device 1 via the test connection element 11.1. The coupling is releasable. The rotating body 11.2 is rotatably installed in a cavity of the upper housing part 10.1.

[0028] A brake unit 12 is arranged in the cavity of the upper housing part 10.1. The brake unit 12 comprises a number of brake plate elements 12.1, a brake piston 12.2 and a number of brake spring elements 12.3. The brake unit 12 has the function of decelerating the torque M exerted by the screw-driving tool 2 during the threaded joint simulation.

[0029] The brake plate element 12.1 is arranged closer to the screw-driven tool 2, and the brake piston 12.2 is arranged further away from the screw-driven tool 2 as seen along the axis of rotation Z. Preferably, said brake plate element 12.1 comprises a plurality of first brake plate elements mounted on the upper housing part 10.1 and a plurality of second brake plate elements mounted on the rotating body 11.2. The brake plate elements 12.1 are annular in shape. They are arranged alternately with each other along the axis of rotation Z. The brake piston 12.2 is arranged in the upper housing part 10.1. The brake piston 12.2 comprises an end remote from the screw-driven tool and an end close to the screw-driven tool. At the end close to the screw-driven tool, the brake piston 12.2 is in direct mechanical contact with the brake plate element 12.1. A braking force F can be applied to the brake piston 12.2 via the end remote from the screw-driven tool (see figures 3 and 4). A brake piston 12.2, to which a braking force F is applied, is movable along the axis of rotation Z in a direction towards the screw-driven tool 2. Said brake piston 12.2, to which a braking force F is applied, brings about a frictional engagement of the brake plate elements 12.1 with each other. The frictionally engaged brake plate elements 12.1 reduce the torque M exerted by the screw-driven tool 2.

[0030] The brake spring element 12.3 is arranged in a cavity of the housing pot 10.2 at the housing end remote from the screw-driven tool. The brake spring element 12.3 is fixed in the housing pot 12.2. Preferably, the brake spring element 12.3 is a disk spring. The brake spring element 12.3 is compressible along the axis of rotation Z. The number of brake spring elements 12.3 in the housing pot 10.2 and / or the hardness of the brake spring elements 12.3 vary depending on the nominal value S (nominal torque and / or nominal angle of rotation). The housing pot 10.2 is provided with a quick-release fastener, such as a bayonet lock, to allow a quick and easy exchange of the brake spring element 12.3.

[0031] A measuring unit 13 is arranged in the cavity of the upper housing part 10.1. The measuring unit 13 comprises a torque transducer and a rotation angle transducer. The torque transducer is designed to measure the torque M exerted by the screw driving tool 2 during the threaded joint simulation. The torque transducer is mounted on the rotating body 11.2. Preferably, the torque transducer is a strain gauge. The strain gauge detects the extension or compression of the rotating body 11.2 caused by the torque M. The rotation angle transducer is designed to measure the angle of rotation of the test connection unit 11 around the rotation axis Z during the threaded joint simulation. The rotation angle transducer comprises a sensor element and a measuring disc. The sensor element is mounted on the upper housing part 10.1 and the measuring disc is mounted on the rotating body 11.2. Preferably, the measuring disc comprises an angle mark and the sensor element detects the angle mark rotating around the rotation axis Z during the threaded joint simulation.

[0032] The main part of the converter unit 14 is arranged in the cavity of the upper housing part 10.1 and the smaller part is arranged in the cavity of the housing pot 10.2. The converter unit 14 comprises a spindle 14.1, a nut 14.2, a bush 14.3 and a return spring element 14.4. The converter unit 14 is mounted on the test connection unit 11. The function of the converter unit 14 is to capture the torque M exerted by the screw-driving tool 2 during the threaded joint simulation, convert it into a braking force F and apply the braking force F to the brake unit 12.

[0033] The spindle 14.1 is cylindrical in shape and extends along the axis of rotation Z. The nut 14.2 is hollow cylindrical in shape and is arranged on the circumference of the spindle 14.1. In a plane perpendicular to the axis of rotation Z, the nut 14.1 completely surrounds the circumference of the spindle 14.1. The spindle 14.1 and the nut 14.2 are connected to each other by a form fit. The form fit converts the rotational movement of the spindle 14.1 about the axis of rotation Z into a longitudinal movement of the nut 14.2 along the axis of rotation Z. Preferably, the spindle 14.1 and the nut 14.2 form a ball screw drive, a roller gear or the like. In such a case, the spindle 14.1 is a threaded spindle and the nut 14.2 is a threaded nut. A rolling element 14.5, such as a ball or a roller, creates a form fit between the threaded spindle and the threaded nut. In figures 1 to 6, the rolling element 14.5 is shown diagrammatically as a dashed circle. The screwed spindle is provided with a raceway on its circumference. The screwed nut is provided with a return path. A rolling element 14.5 runs in the raceway of the screwed spindle and in the return path of the screwed nut. The rolling element 14.5 converts the rotational movement of the screwed spindle about the axis of rotation Z into a movement of the screwed nut along the axis of rotation Z. The ball screw drive or roller gear drive is not self-locking, since the rotational friction of the rolling element 14.5 is very low.

[0034] The bush 14.3 is connected to the rotating body 11.2 by a mechanical connection 14.31. The mechanical connection 14.31 transmits the torque M exerted by the screw driving tool 2 from the rotating body 11.2 to the bush 14.3. Preferably, the mechanical connection 14.31 is a toothed system in which the bush 14.3 and the rotating body 11.2 are provided with teeth that engage with each other to form a toothed system.

[0035] The spindle 14.1 has an end that is positioned along the rotation axis Z close to the screw-driven tool. At the end close to the screw-driven tool, the spindle 14.1 is mounted to the bush 14.3 via another mechanical connection 14.11. The other mechanical connection 14.11 transmits the torque M exerted by the screw-driven tool 2 from the bush 14.3 to the spindle 14.1. Preferably, the other mechanical connection 14.11 is achieved by a feather-key screw connection. In such a case, a screw connects the spindle 14.1 and the bush 14.3 to each other and a feather key fixes this connection. The screw comprises a thread with a thread pitch. Under the action of the torque M exerted by the screw-driven tool 2 and depending on the thread pitch, the screw is movable along the rotation axis Z, leading to a longitudinal movement of the bush 14.3 away from the screw-driven tool 2 of less than / equal to 10 mm.

[0036] A return spring element 14.4 is arranged in the upper housing part 10.1. Preferably, an end of said return spring element 14.4 close to the screw-driving tool is in mechanical contact with the upper housing part 10.1, whereas an end of the return spring element 14.4 remote from the screw-driving tool is in mechanical contact with the nut 14.2.

[0037] Viewed along the axis of rotation Z, the nut 14.2 is arranged further away from the screw-driven tool 2 than the return spring element 14.4 and the brake piston 12.2. The nut 14.2 is provided at its end close to the screw-driven tool with a bearing and a pressure sleeve 14.21. The bearing serves to prevent the nut 14.1 from jamming during its movement along the axis of rotation Z, through which the rotating element 14.5 is interposed. The nut 14.2 is in mechanical contact with the return spring element 14.4 and the brake piston 12.2 by means of the pressure sleeve 14.21. For this purpose, the pressure sleeve 14.21 is provided with a contact surface extending in a plane perpendicular to the axis of rotation Z. The mechanical contact is made both with the return spring element 14.4 and with the brake piston 12.2.

[0038] A holding unit 15 is arranged in the housing 10. The holding unit 15 comprises a drive 15.1 and a holding element 15.2. The holding unit 15 is designed to hold the nut 14.2 for directional movement along the rotation axis Z in the direction towards the screw driving tool 2 along the rotation axis Z.

[0039] The drive 15.1 is mounted on the outside of the upper housing part 10.1. Preferably, the drive 15.1 is a solenoid. The drive 15.1 and the holding element 15.2 are mechanically connected to each other. The drive 15.1 and the holding element 15.2 extend along a radial axis X. The radial axis X is perpendicular to the axis of rotation Z. The holding element 15.2 projects through an outer opening of the housing 10 into the cavity of the housing 10. The holding element 15.2 is preferably provided with a feather key.

[0040] The holding unit 15 can be started and stopped. When the holding unit 15 is started, the drive 15.1 moves the holding element 15.2 between a rest position 15.2* and a holding position 15.2+. Figure 2a shows the holding element 15.2 in the rest position 15.2*. Figure 2b shows the holding element 15.2 with the drive 15.1 being moved along the radial axis X by a travel distance Δx towards the nut 14.2. The holding element 15.2 is then in the holding position 15.2+. In the holding position 15.2+, the holding element 15.2 is in direct mechanical contact with said nut 14.2. Preferably, the travel distance Δx along the radial axis X is less than / equal to 10 mm. The holding element 15.2, which is in mechanical contact with the nut 14.2 in the holding position 15.2+, holds the nut 14.2 by means of a form fit (see Figures 2 to 4).

[0041] During the rotational movement of the spindle 14.1 about the axis of rotation Z, this retention H achieved by the form fit prevents the nut 14.2 from moving along the axis of rotation Z in the direction away from the screw-driving tool 2. However, this retention H by the form fit allows the movement of the nut 14.2 along the axis of rotation Z in the direction towards the screw-driving tool 2. Figure 3a shows the nut 14.2 in a nut start position 14.2*. From the nut start position 14.2*, the nut 14.2 can advance by a nut stroke Δz1 along the axis of rotation Z, preferably less than / equal to 25 mm, in the direction towards the screw-driving tool 2. However, the movement of the nut 14.2 along the axis of rotation Z in the direction towards the screw-driving tool 2 is limited by the brake piston 12.2. The nut 14.2 advances by said nut stroke Δz1 along the axis of rotation Z and is then positioned in a nut end position 14.2+ relative to the return spring element 14.4 and relative to the brake piston 12.2. The pressure sleeve 14.21 compresses the return spring element 14.4 and exerts a braking force F on the brake piston 12.2.

[0042] The spindle 14.1 has an end facing away from the screw-driven tool along the rotation axis Z. At its end facing away from the screw-driven tool, the spindle 14.1 is provided with a spindle contact surface 14.12. Via the spindle contact surface 14.12, the spindle 14.1 is in direct mechanical contact with the brake spring element 12.3 in the housing pot 10.2. The spindle contact surface 14.12 extends in a plane perpendicular to the rotation axis Z.

[0043] Thus, when the nut 14.2 is in the nut end position 14.2+ and the screw-driving tool 2 continues to drive the spindle 14.1 to rotate about the rotation axis Z, said nut 14.2 and spindle 14.1 are mechanically loaded relative to each other. As shown in Figures 4a and 4b, the bushing 14.3 moves along the rotation axis Z away from the screw-driving tool 2 under the action of the torque M exerted by the screw-driving tool 2. As a result, the spindle 14.1, which is mechanically connected to said bushing 14.3, also moves along the rotation axis Z away from the screw-driving tool 2. The spindle contact surface 14.12 leaves the spindle start position 14.1* and moves along the rotation axis Z to the spindle end position 14.1+, resulting in compression of the brake spring element 12.3.

[0044] The nut 14.2 continues to exert a braking force F on the brake piston 12.2 even when the screw driving tool 2 is no longer exerting a torque M at the end of the threaded joint simulation (see FIG. 5). This is due to the fact that the nut 14.2 is still held by the holding unit 15 with a form fit H.

[0045] At the end of the threaded joint simulation, no further torque M can be exerted by the screw-driven tool 2. However, only after the stopping of the holding unit 15, when the holding element 15.2 is moved by the drive 15.1 from the holding position 15.2+ back to the rest position 15.2*, the nut 14.2 is no longer held by a form fit H. In this case, the brake spring element 12.3 will decompress and generate a spring force R. Said spring force R acts on the spindle 14.1 via the spindle contact surface 14.12. The bush 14.3 and the spindle 14.1 move along the rotation axis Z in the direction towards the screw-driven tool 2. The spindle contact surface 14.12 leaves the spindle end position 14.1+ and moves automatically along the rotation axis Z to the spindle start position 14.1+ (see Fig. 5 and Fig. 6). Further time-consuming measures for resetting the simulation device 1 are no longer necessary, making the procedure cost-effective.

[0046] When it is no longer held by the form fit H, the return spring element 14.4 decompresses and the return spring force RR resulting from this decompression causes the nut 14.2 to leave the nut end position 14.2+ and return automatically to the nut start position 14.2+ (see figures 5 and 6). Advantageously, the magnitude of this return spring force RR is selected such that the nut 14.2 under the action of the return spring force RR takes up the nut start position 14.2+ very quickly, making the procedure time-saving and economical.

[0047] Without the form-fit retention H, the frictional contact of the brake plate element 12.1 is released, allowing the brake piston 12.2 to move along the axis of rotation Z, away from the brake plate element 12.1.

[0048] Thus, a method for performing a threaded joint simulation of a screw driving tool 2 using the simulation device 1 comprises the following steps.

[0049] In a first step depicted in Fig. 1, a nominal value S is set for the screw-driving tool 2, which is coupled to the simulation device 1 via a test connection unit 11. The screw-driving tool 2 is not yet started, does not yet rotate about the rotation axis Z and does not yet exert any torque M. The holding element 15.2 is in a rest position 15.2* (see Fig. 2a). The nut 14.2 is in a nut start position 14.2* (see Fig. 3a). The spindle 14.1 is in a spindle start position 14.1* (see Fig. 4a).

[0050] In a second step depicted in Fig. 2, the screw-driving tool 2 is started. Shortly after the start of the screw-driving tool 2 (within 2 seconds), the holding unit 15 is started and the holding element 15.2 is moved by the drive 15.1 to the holding position 15.2+ and the nut 14.2 is held H in the nut start position 14.2* by means of a form fit (see also Fig. 2b and Fig. 3a). The spindle 14.1 is still in the spindle start position 14.1* (see Fig. 4a).

[0051] In a third step depicted in FIG. 3, the started screw-driving tool 2 rotates about the axis of rotation Z and exerts a torque M. The test connection element 11.1 coupled to the screw-driving tool 2 transmits the rotational movement about the axis of rotation Z to said bush 14.3 via the rotor 11.2. The torque M is received by the converter unit 14 via the mechanical connection 14.31. The rotational movement about the axis of rotation Z is transmitted from the bush 14.3 to the spindle 14.1. The rotational movement of the spindle 14.1 about the axis of rotation Z results in a movement of the nut 14.2 along the axis of rotation Z. The converter unit 14 converts the exerted torque M. A movement of the nut 14.2 along the axis of rotation Z away from the screw-driving tool 2 is prevented by the H that holds the nut 14.2 by means of a form fit. The nut 14.2 thus performs a movement along the axis of rotation Z towards the screw-driving tool 2. The nut 14.2 leaves the nut start position 14.1* and moves along the axis of rotation Z to a nut end position 14.2+ (see Fig. 3a and Fig. 3b). The nut 14.2 in the nut end position 14.2+ converts the applied torque M into a braking force F. The applied torque M is thus converted into a braking force F by the converter unit 14. The nut 14.2 in the nut end position 14.2+ compresses the return spring element 14.4. The nut 14.2 in the nut end position 14.2+ applies a braking force F to the brake piston 12.2. The converter unit 14 thus applies a braking force F to the brake unit 12. The brake piston 12.2 to which the braking force F is applied can move along the axis of rotation Z, resulting in frictional contact between the brake plate elements 12.1. The brake plate elements 12.1 reduce the torque M applied by the screw driving tool 2. The measuring unit 13 measures the torque M exerted by the screw driving tool 2 and the angle of rotation through which the test connection unit 11 rotates about the rotation axis Z. The holding element 15.2 remains in the holding position 15.2+ (see FIG. 2b). The spindle 14.1 is still in the spindle start position 14.1*.

[0052] In a fourth step depicted in Fig. 4, the screw-driving tool 2 further increases the exerted torque M until the set nominal value S is reached. The screw-driving tool 2 continues to rotate the spindle 14.1 around the rotation axis Z. Since the nut 14.2 is in the nut end position 14.2+, the nut 14.2 and the spindle 14.1 are mechanically loaded against each other. As a result of this mechanical loading, the bush 14.3 moves the spindle 14.1 from the spindle start position 14.1* to the spindle end position 14.1+ and compresses the brake spring element 12.3 (see Fig. 4a and Fig. 4b). The measuring unit 13 measures the torque M exerted by the screw-driving tool 2 and the angle of rotation through which the test connection unit 11 rotates around the rotation axis Z.

[0053] In a fifth step depicted in Fig. 5, the screw-driving tool 2 has achieved the set nominal value S and stops the rotational movement about the rotation axis Z of the test connection unit 11 and the exertion of the torque M. The coupling of the screw-driving tool 2 to the test connection element 11.1 is released. The screw-driving tool 2 is removed from the simulation device 1. The holding element 15.2 remains in the holding position 15.2+ (see Fig. 2b). The nut 14.2 remains in the nut end position 14.2+ (see Fig. 3b).

[0054] In a sixth step depicted in FIG. 6, the holding unit 15 is stopped and the holding element 15.2 is moved by the drive 15.1 from the holding position 15.2+ back to the rest position 15.2. The nut 14.2 is no longer held by form-fit H. Without such form-fit holding H, the return spring element 14.4 decompresses and exerts a return spring force RR along the rotation axis Z on the nut 14.2, which is moved to the nut start position 14.2+ (see FIG. 5 and FIG. 6). Without such form-fit holding H, the frictional contact between the brake disc elements 12.1 is released, causing the brake piston 12.2 to move along the rotation axis Z away from the brake disc element 12.1 (see FIG. 5 and FIG. 6). At the same time, the brake spring element 12.3 decompresses, resulting in a spring force R. This spring force R urges the bush 14.3 and the spindle 14.1 back along the axis of rotation Z from the spindle end position 14.1+ to the spindle start position 14.1*, which the bush 14.3 and the spindle 14.1 have reached in the representation shown in FIG. [Explanation of symbols]

[0055] 1. Simulation device 2 Screwdriver tools 10.1 Upper housing part 10.2 Housing Bottom 11 Test Connection Unit 11.1 Test Connection Elements 11.2 Solids of revolution 12 Brake unit 12.1 Brake plate elements 12.2 Brake piston 12.3 Brake Spring Elements 13 Measurement Units 14 Converter unit 14.1 Spindle 14.1* Spindle start position 14.1+ spindle end position 14.11 Alternative Mechanical Connections 14.12 Spindle Contact Surface 14.2 Nuts 14.2* Nut starting position 14.2+ Nut End Position 14.21 Pressure sleeve 14.3 Bush 14.31 Mechanical connections 14.4 Return Spring Elements 14.5 Rotation elements 15 Holding Unit 15.1 Drive 15.2 Holding Elements 15.2* Rest position 15.2+ Holding position Δx Travel distance Δz1 Nut stroke Δz2 Bush stroke F Brake force H Form-fit retention M Torque R Spring force RR Return spring force S Nominal value X radial axis Z Rotation Axis

Claims

1. A simulation device (1) for simulating a threaded joint of a screw driving tool (2), comprising: a test connection unit (11) capable of coupling the screw driving tool (2) to the simulation device (1), the screw driving tool (2) being capable of being actuated and coupled to the test connection unit (11) in the actuated state, rotating the test connection unit (11) about a rotation axis (Z) and exerting a torque (M) on the test connection unit (11); a measuring unit (13) for measuring the torque (M) exerted on the test connection unit (11) by the screw driving tool (2) in the actuated state and coupled to the test connection unit (11) and for measuring the angle of rotation rotated around the rotation axis (Z) by the actuated screw driving tool (2) in the coupled state, A simulation device (1) comprising a brake unit (12) for slowing down the torque (M) exerted on the test connection unit (11) by the screw driving tool (2) in the started state and coupled to the test connection unit (11), The simulation device (1) comprises a converter unit (14), the converter unit (14) being mechanically connected to the test connection unit (11), the converter unit (14) being in the started state, capturing the torque (M) exerted on the test connection unit (11) by the screw driving tool (2) coupled to the test connection unit (11), converting the torque into a braking force (F), applying the braking force (F) to the brake unit (12), and controlling the converter unit (14) to detect the torque (M) and the braking force (F) applied to the brake unit (12). The test connection unit (11) comprises a spindle (14.1) and a nut (14.2), the spindle (14.1) and the nut (14.2) being connected to each other via a form fit, by which a rotational movement of the spindle (14.1) about the axis of rotation (Z) is converted into a longitudinal movement of the nut (14.2) along the axis of rotation (Z), and the nut (14.2), which is moved along the axis of rotation (Z), is in the actuated state and is coupled to the test connection unit (11). a torque (M) applied by the screw-driving tool (2) to the test connection unit (11) being converted into a braking force (F) and applying the braking force (F) to the brake unit (12); the converter unit (14) comprises a rotating element (14.5); the spindle (14.1) is a threaded spindle; the nut (14.2) is a threaded nut; the rotating element (14.5) forms the shape fit between the threaded spindle (14.1) and the threaded nut (14.2); and said rolling element (14.5) converts the rotational movement of said threaded spindle (14.1) around said axis of rotation (Z) into the longitudinal movement of said threaded nut (14.2) along said axis of rotation (Z), said rolling elements (14,5) being balls or rollers so as to generate said form fit between said threaded spindle (14,1) and said threaded nut (14,2), and said rolling elements (14,5) being balls or rollers so as to generate said form fit between said threaded spindle (14,1), said threaded nut (14,2) and said intermediate rolling elements (14,5) forms a ball screw drive or roller gear drive, which is not self-locking, and the balls or rollers convert the rotational movement of the threaded spindle (14, 1) about the axis of rotation (Z) into a movement of the threaded nut (14, 2) along the axis of rotation (Z) due to the extremely low rotational friction of the balls or rollers.

2. 2. The simulation device (1) according to claim 1, characterized in that the simulation device (1) comprises a holding unit (15), which can be actuated, and the actuated holding unit (15) holds (H) the nut (14.2) by means of a form-fit, and the holding (H) by form-fit only allows a longitudinal movement of the nut (14.2) along the rotation axis (Z) in a direction towards the screw-driving tool (2) from a nut start position (14.2*) to a nut end position (14.2+).

3. 3. The simulation device (1) according to claim 2, characterized in that the brake unit (12) comprises a plurality of brake plate elements (12.1) and a brake piston (12.2), the nut (14.2) being moved longitudinally to the nut end position (14.2+) applies the brake force (F) to the brake piston (12.2), and the brake piston (12.2) to which the brake force (F) is applied brings about frictional engagement of the brake plate elements (12.1) with each other.

4. 3. The simulation device (1) according to claim 2, characterized in that the converter unit (14) comprises a return spring element (14.4) and that the nut (14.2) moved longitudinally to the nut end position (14.2+) compresses the return spring element (14.4).

5. 3. Simulation device (1) according to claim 2, characterized in that the nut (14.2) and the spindle (14.1) being moved longitudinally to the nut end position (14.2+) are loaded relative to each other during a rotational movement of the spindle (14.1) about the rotation axis (Z), the spindle (14.1) moving longitudinally along the rotation axis (Z) from a spindle start position (14.1*) to a spindle end position (14.1+), the brake unit (12) comprises a plurality of brake spring elements 12.3, and the spindle (14.1) being moved longitudinally along the rotation axis (Z) to the spindle end position (14.1+) compresses the brake spring elements (12.3).

6. 6. Simulation device (1) according to claim 5, characterized in that the brake spring elements (12.3) are arranged in a housing pot (10.2) and the number of brake spring elements (12.3) arranged in the housing pot (10.2) varies depending on the torque (M) exerted by the started screw-driven tool (2) up to a predefined nominal torque and / or a nominal angle of rotation and / or the hardness of the brake spring elements (12.3) arranged in the housing pot (10.2) varies depending on the torque (M) exerted by the started screw-driven tool (2) up to a predefined nominal torque and / or a nominal angle of rotation.

7. 6. The simulation device (1) according to claim 5, characterized in that the brake spring element (12.3) is arranged in a housing pot (10.2), and that the housing pot (10.2) can be opened by means of a quick release mechanism, and that the brake spring element (12.3) can be replaced in the opened housing pot (10.2).

8. A method for performing a threaded joint simulation of a screw driving tool (2) using a simulation device (1) according to any one of claims 1 to 7, comprising: In a first step, the screw driving tool (2) is coupled to the simulation device (1) via the test connection unit (11), in a second step, the screw-driving tool (2) is started, and the started screw-driving tool (2) rotates the test connection unit (11) about the rotation axis (Z) and exerts a torque (M) on the test connection unit (11); In a third step, the torque (M) exerted by the screw driving tool (2) is captured by a converter unit (14) and converted into a braking force (F); and A method according to claim 1, characterized in that in the third step, the braking force (F) is applied to the braking unit (12) by the converter unit (14).

9. 9. The method according to claim 8, characterized in that the converter unit (14) comprises a spindle (14.1) and a nut (14.2), the spindle (14.1) and the nut (14.2) being connected to one another via a form fit, and in the third step, by means of the form fit, a rotational movement of the spindle (14.1) about the axis of rotation (Z) is converted into a longitudinal movement of the nut (14.2) along the axis of rotation (Z) from a nut start position (14.2*) to a nut end position (14.2+), and in the third step, the torque (M) exerted by the screw driving tool (2) is converted into the braking force (F) by the nut (14.2) being moved longitudinally to the nut end position (14.2+).

10. 10. The method according to claim 9, characterized in that the simulation device (1) comprises a holding unit (15), which is activated in the second step, the nut (14.2) is form-fittingly held (H) by the activated holding unit (15), and the form-fitting holding (H) only allows a longitudinal movement of the nut (14.2) along the rotation axis (Z) in a direction towards the screw-driving tool (2) from the nut start position (14.2*) to the nut end position (14.2+).

11. 11. The method according to claim 10, characterized in that the brake unit (12) comprises a plurality of brake plate elements (12.1) and a brake piston (12.2), and that in the third step, the nut (14.2) moved in the longitudinal direction to the nut end position (14.2+) applies the braking force (F) to the brake piston (12.2), and that in the third step, the brake piston (12.2) to which the braking force (F) is applied brings about frictional engagement of the brake plate elements (12.1) with each other.

12. The converter unit (14) comprises a return spring element (14.4), which in the third step is compressed by the nut (14.2) being moved longitudinally to the nut end position (14.2+); in a sixth step, the holding unit (15) is stopped, the stopped holding unit (15) no longer holding (H) the nut (14.2) by form-fitting; 11. The method according to claim 10, characterized in that, in the absence of the retention (H) of the nut (14.2), the compressed return spring element (14.4) is decompressed and a return spring force (RR) generated by the decompressed return spring element (14.4) is exerted on the nut (14.2), and in the sixth step the nut (14.2) is moved along the rotation axis (Z) from the nut end position (14.2+) to the nut start position (14.2*) by the return spring force (RR).

13. the nut (14.2) and the spindle (14.1) being moved longitudinally to the nut end position (14.2+), are loaded against each other during the rotational movement of the spindle (14.1) about the axis of rotation (Z), and the spindle (14.1) is moved longitudinally along the axis of rotation (Z) from a spindle start position (14.1*) to a spindle end position (14.1+), the brake unit (12) comprises a plurality of brake spring elements (12.3), and the spindle (14.1) compresses the brake spring elements (12.3); in a sixth step, 11. The method according to claim 10, characterized in that the screw-driving tool (2) is stopped and a torque (M) is no longer exerted by the stopped screw-driving tool (2), that in the absence of the retention (H) of the nut (14.2) by form-fit, the brake spring element (12.3) decompresses and the decompressed spring element (12.3) exerts a spring force (R), and that in the sixth step the spindle (14.1) is moved along the rotation axis (Z) by a return spring force (R) from the spindle end position (14.1+) to the spindle start position (14.1*).

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