Damping system and linear actuator
By using a pre-tensioned spring structure in conjunction with a stop surface in the linear actuator, the problem of load peaks in the linear actuator under vibration or impact is solved, achieving an effective damping effect, protecting critical components and maintaining the rigidity and precise positioning of the actuator.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- EWELLIX AB
- Filing Date
- 2022-07-26
- Publication Date
- 2026-07-31
AI Technical Summary
Linear actuators are prone to load peaks when subjected to vibration or shock, which shortens their service life. Existing damping systems cannot effectively buffer the force.
The spring structure with pretension is supported in the initial position by the first and second stop surfaces. When the rated force is exceeded, the spring structure is lifted off the stop surfaces to achieve a damping effect and protect the critical components of the linear actuator.
It effectively buffers loads exceeding the rated force, prevents oscillations and impacts on the linear actuator, protects key components such as support bearings and ball screws, and maintains the rigidity and precise positioning capability of the actuator.
Smart Images
Figure CN115681400B_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to a damping system for a linear actuator and a linear actuator. Background Technology
[0002] Linear actuators, which convert the rotational motion of a drive unit into translational motion, are frequently used to move machine components or equipment parts. In such cases, the forces acting on the linear actuator can sometimes cause load spikes, damaging the actuator. In particular, vibration or shock can have a long-term impact on the mechanism of the linear actuator, shortening its lifespan. Therefore, damping systems have been developed to buffer forces, thereby reducing the load on the linear actuator. Summary of the Invention
[0003] The objective of this invention is to further improve force buffering in linear actuators, particularly to provide a reliable reduction in the forces acting on the linear actuator without impairing the control operation of the actuator.
[0004] According to the independent claim, this task is solved by a damping system for a linear actuator and a linear actuator.
[0005] The preferred embodiments are the subject of the dependent claims and the description below.
[0006] According to a first aspect of the invention, a damping system for a linear actuator has a first component comprising a first axial stop surface and a second axial stop surface. The invention includes an elastic spring configuration that, in an initial position, stops axially on the first and second stop surfaces simultaneously under a predetermined pretension force. A second component is further provided, which is axially movably supported relative to the first component and configured to lift the spring configuration away from either the first or second stop surface upon axial movement relative to the first component.
[0007] The component in the sense of this invention preferably comprises at least one member. Preferably, the component is formed of multiple members. During normal operation of the actuator, the members are properly fixed relative to each other, for example, rigidly connected to each other, and can be moved relative to each other at most by using a tool (e.g., by screwing in threads and / or similar means). However, it is also possible for the component to comprise only a single member.
[0008] In this invention, "lifting away" is preferably understood as interrupting or canceling contact. In other words, when one component is lifted away from another component, the component is separated from the other component, thereby creating a gap between the components.
[0009] In the context of this invention, the axial stop surface is preferably a surface whose surface normal is parallel to the longitudinal axis and / or the direction of movement, and can stop on components, particularly on spring structures. Such an axial stop surface can be formed, for example, by a radial step or radial protrusion that extends into the spring travel of the spring structure.
[0010] An aspect of the invention is based on a means of loading a predetermined pretension force onto an elastic spring structure in a damping system for a linear actuator. Preferably, for this purpose, a first assembly comprising a first stop surface and a second stop surface is provided, and in an initial position, for example during normal operation of the linear actuator, the spring structure is supported on the first and second stop surfaces. For this purpose, the spring structure can be arranged, for example, such that in the initial position, it is loaded with a pretension force and contacts the first and second stop surfaces. A second assembly axially movable relative to the first assembly is appropriately provided to manipulate the spring structure at least in sections, for example, by compression. The damping system is advantageously configured in this case such that movement of the first assembly relative to the second assembly is only possible when the predetermined pretension force is overcome.
[0011] The predetermined pretension force is appropriately set such that the spring assembly can only be compressed by the second component and thus lifted off the first or second stop surface when the rated force of the linear actuator, such as the maximum allowable force, is exceeded. The spring assembly can be compressed by the second component, for example, in such a way that when an external force is applied to the first or second component, the axial end of the spring assembly loses contact with the first or second stop surface.
[0012] The pre-tensioned spring construction prevents unnecessary and potentially damaging oscillations in the damping system. Therefore, sensitive components of the linear actuator, such as support bearings, ball screws, ball nuts, and / or similar parts, are protected from excessive impacts or shocks. Simultaneously, the linear actuator maintains rigidity during normal operation, preferably up to rated force. Thus, despite the integrated damping from the linear actuator, machine components or equipment parts can be precisely positioned.
[0013] In a preferred embodiment, the damping system, particularly the first component and / or the spring structure and / or the second component, is configured such that, when the second component moves axially relative to the first component in a first direction, the second component lifts the spring structure away from the first stop surface, and when the second component moves axially relative to the first component in a second direction opposite to the first direction, the second component lifts the spring structure away from the second stop surface. For example, the first component and / or the spring structure and / or the second component may be arranged relative to each other in such a way that, depending on the direction of movement, the spring structure is lifted away from the first or second stop surface.
[0014] In another preferred embodiment, the second component has a third axial stop surface and a fourth axial stop surface. Preferably, the spring mechanism, in its initial position and under a predetermined pretension, is axially stopped at the third and fourth stop surfaces. The second component is preferably constructed such that the third or fourth stop surface lifts the spring mechanism away from the first or second stop surface, in which case, for example, at least segmental compression of the spring mechanism can be achieved. Reliable control of the spring mechanism can be achieved by means of the third and fourth axial stop surfaces.
[0015] In another preferred embodiment, in the initial position, the first stop surface is radially aligned with the third stop surface, and the second stop surface is radially aligned with the fourth stop surface. Specifically, the first and third stop surfaces, as well as the second and fourth stop surfaces, can each define a stop plane in the initial position. Therefore, the spring structure can be supported on all four stop surfaces. Thus, uniform load distribution on all stop surfaces can be achieved.
[0016] In another preferred embodiment, the first component has a fifth stop surface and a sixth stop surface. Preferably, the spring assembly is supported on the fifth and sixth stop surfaces with at least a predetermined pretension force. The second component is preferably constructed and / or arranged in such a way that the contact between the spring assembly and the fifth and sixth stop surfaces is not interrupted by movement of the second component. More precisely, the second component can be constructed and / or arranged such that the spring assembly is compressed relative to the fifth and sixth stop surfaces at least segmentally. Thus, the fifth and sixth stop surfaces can be used to adjust a predetermined spring force. The arrangement of the fifth and sixth stop surfaces also allows for a more compact design of the damping system.
[0017] In another preferred embodiment, the spring is configured to be spaced apart from the first or second stop surface in the load position, for example, when a force is applied to the first or second component.
[0018] The distance between the spring assembly, particularly the axial end of the spring assembly, and the first or second stop surface is adjusted by means of a second component, and this distance appropriately corresponds to the spring stroke of the spring assembly. Therefore, the spring assembly can reliably absorb loads acting on the damping system, such as those exceeding the rated force of the linear actuator.
[0019] In another preferred embodiment, the spring configuration has at least one, particularly rigid, support mechanism and at least one elastic spring mechanism.
[0020] The elastic spring mechanism is properly supported on at least one support mechanism, at least under a predetermined pretension force. In this case, the at least one support mechanism is preferably configured, and in particular, arranged accordingly, as a stop on a first or second stop surface. This allows for reliable axial fixation of the spring mechanism. Utilizing the flat surface, the at least one support mechanism can ensure a clearly defined stop on the stop surface, thereby ensuring good force transmission without force peaks.
[0021] In another preferred embodiment, the spring configuration has at least one spring mechanism configured as a disc spring assembly. The spring configuration may, for example, have four disc springs, layered into two assemblies. Preferably, the spring configuration has at least two, and more preferably four, such assemblies, which can be combined into one or two disc spring groups. With the aid of such disc spring assemblies, a high preload can be achieved even with a compact spring configuration.
[0022] In another preferred embodiment, the first and second stop surfaces are arranged opposite each other, i.e., facing each other. Preferably, the spring assembly is arranged between the first and second stop surfaces. Preferably, the third and fourth stop surfaces are also arranged opposite each other, with the spring assembly arranged between the third and fourth stop surfaces. This makes the spring assembly particularly compact in the axial direction. Therefore, a damping system can be used, for example, at the end of the thrust tube, particularly between the thrust tube and the connector.
[0023] In another preferred embodiment, the first and second stop surfaces are oriented away from each other. Preferably, the first and second stop surfaces are arranged, particularly axially, between a first section and a second section of the spring structure. Preferably, the third and fourth stop surfaces are also oriented away from each other and are arranged between the first and second sections of the spring structure. In other words, the first and second stop surfaces—and, if necessary, the third and fourth stop surfaces—are surrounded (axially) by the spring structure. In this case, the first and second sections can each have at least one elastic spring mechanism, such as a disc spring assembly. With this orientation of the first and second stop surfaces, the pretension of the spring structure can be easily adjusted, for example, by a dedicated pretensioning mechanism. Furthermore, this allows the first and / or second components to be constructed compactly axially. Therefore, the use of a damping system becomes possible, for example, in the field of mechanisms for linear actuators that convert rotational motion into translational motion, particularly in lead screws or ball nuts.
[0024] In another preferred embodiment, a pretensioning mechanism is provided, which is configured to adjust a predetermined pretension force. The pretensioning mechanism may therefore have at least one pretensioning element, such as a safety nut or a slotted nut. This allows for flexible adjustment of the pretension force. In particular, the pretension force can be adjusted or readjusted according to use.
[0025] In another preferred embodiment, the pretensioning structure has a threaded mechanism through which the spring structure can be compressed or decompressed at least in sections.
[0026] In particular, at least one pretensioning element can be either screwed in or screwed out. This allows for simple and quick, yet also particularly precise, adjustment of the pretension force.
[0027] In another preferred embodiment, the distance between the first stop surface and the second stop surface can be varied, for example, by a threaded mechanism. Therefore, the predetermined pretension force can be adjusted particularly easily.
[0028] In another preferred embodiment, the second component and the spring assembly are arranged radially within the first component. In other words, the first component may radially surround the second component and the spring assembly. This allows for a particularly protected arrangement of the spring assembly and the second component.
[0029] The linear actuator according to a second aspect of the invention has a damping system according to a first aspect of the invention. The damping system is appropriately integrated into the power system of the linear actuator. In other words, the damping system is appropriately integrated into the linear actuator in such a way that the force flow generated during operation passes through the damping system. This prevents oscillation of the linear actuator and protects the mechanism of the linear actuator that converts rotational motion into translational motion from strong impacts or vibrations. Simultaneously, the linear actuator has high rigidity, thus allowing for accurate positioning even with heavy loads.
[0030] In a preferred embodiment, the predetermined preload is less than or equal to the rated force of the linear actuator. In this case, the rated force is preferably understood as the maximum force that the linear actuator is designed to apply. This avoids spring travel in the linear actuator's power system until the rated force is reached. In other words, high stiffness of the linear actuator can be ensured up to the rated force.
[0031] In another preferred embodiment, the linear actuator includes a ball screw, a ball nut effectively connected to the ball screw, and a safety nut connected to the ball nut, particularly via a spring mechanism. The spring mechanism is appropriately arranged, at least in sections, between the ball nut and the safety nut. This ensures that the safety nut is only effectively connected to the ball screw when the applied force exceeds a predetermined preload.
[0032] In another preferred embodiment, the linear actuator includes a ball screw, a ball nut effectively connected to the ball screw, and a nut housing in which the ball nut is axially movably arranged. In this case, the nut housing appropriately forms at least a portion of the first assembly.
[0033] In this case, the ball nut appropriately forms at least part of the second component. Thus, the ball nut, especially the ball that facilitates the effective connection between the ball screw and the ball nut, can effectively prevent overload.
[0034] In another preferred embodiment, the linear actuator includes a thrust tube and a connector. The damping system appropriately has a housing rigidly connected to the thrust tube, forming at least a portion of the first component. The connector appropriately forms at least a portion of or is at least rigidly connected to the second component. Overloads acting on the connector can be at least partially absorbed by the spring configuration before acting on the mechanism of the linear actuator through the thrust tube. Attached Figure Description
[0035] The invention is further described below with reference to the accompanying drawings. Elements with the same function are denoted by the same reference numerals throughout, as long as it is appropriate to use them. The invention is not limited to the embodiments shown in the drawings, nor is it limited in terms of functional features. The foregoing description and the following description of the drawings contain numerous features, some of which are generally reflected in various combinations in the dependent claims. However, those skilled in the art will also consider these features individually, as well as all other features disclosed in the foregoing and following description of the drawings, and combine them to form useful further combinations. In particular, all of the foregoing features can be combined individually and in any suitable combination with the damping system according to the first aspect of the invention and the linear actuator according to the second aspect of the invention.
[0036] In the attached diagram:
[0037] Figure 1 An example of a damping system for a linear actuator in its initial position is shown. The damping system has a first component that includes two mutually facing stop surfaces for a spring configuration.
[0038] Figure 2 Show Figure 1 An example of a damping system at the first load position;
[0039] Figure 3 Show Figure 1 An example of a damping system in the second load position;
[0040] Figure 4An example of a damping system for a linear actuator in its initial position is shown. The damping system has a first component that includes two mutually opposing stop surfaces for a spring configuration.
[0041] Figure 5 An example of a damping system for a linear actuator is shown, the damping system having a second component that is rigidly connected to a spring configuration;
[0042] Figure 6 An example of a damping system for a linear actuator is shown, the damping system having a first component that includes a safety nut for the linear actuator;
[0043] Figure 7 Show Figure 6 An example of a damping system at the first load position; and
[0044] Figure 8 Show Figure 6 An example of a damping system in the second load position. Detailed Implementation
[0045] Figure 1 An example of a damping system 10 for a linear actuator in its initial position is shown. The damping system has a first component 20, which includes two opposing stop surfaces 20a, 20b for pre-tensioned, elastic spring structures 30. The damping system 10 also includes a second component 40, which is axially movably supported relative to the first component 20 and configured to lift the spring structures 30 from either the first stop surface 20a or the second stop surface 20b in the event of axial movement relative to the first component 20. For this purpose, the second component 40 has two opposing stop surfaces 40a, 40b.
[0046] In the example shown, the first component 20 is rigidly connected to the thrust tube 50 of the linear actuator, for example, screwed onto the thrust tube. The second component 40 is rigidly connected to the connector 51 of the linear actuator. This allows force flow from the connector 51 to the thrust tube 50, or vice versa, to be transmitted via the spring configuration 30, and protects the sensitive components of the linear actuator, such as the support bearings, ball screws, and / or ball nuts, from force peaks.
[0047] In order to enable precise positioning of the connector 51 by the linear movement of the thrust tube 50, the spring configuration 30 is appropriately loaded with a predetermined pretension force, which advantageously matches the rated force of the linear actuator, despite the presence of the damping system 10. When tension is applied to the connector 51, the spring configuration 30 is further compressed between the first stop surface 20a and the fourth stop surface 40b, or when pressure is applied to the connector 51, the spring configuration 30 is further compressed between the second stop surface 20b and the third stop surface 40a. Therefore, this compression only occurs when the applied force exceeds the rated force, which could potentially damage the components of the linear actuator.
[0048] For example, the spring assembly 30 has at least one elastic spring mechanism 31 and two support mechanisms 32, through which the spring mechanism 31 can be supported on a first stop surface 20a, a second stop surface 20b, a third stop surface 40a, and / or a fourth stop surface 40b. The spring mechanism 31 appropriately has at least one, in the illustrated example, four disc spring assemblies 33, each consisting of two layered disc springs; for clarity, only one disc spring assembly 33 is indicated by reference numerals. With the aid of such disc spring assemblies 33, a spring force of, for example, 70 kN to 90 kN can be achieved with a spring travel of 8 mm. If the spring mechanism 31 is clamped between the first stop surface 20a and the second stop surface 20b under a pretension force of, for example, 50 kN, then force impacts between 50 kN and 70 kN to 90 kN can be buffered by a relative movement of up to 3 mm between the first assembly 20 and the second assembly 40.
[0049] In the example shown, the pretension force can be adjusted by changing the distance between the first stop surface 20a and the second stop surface 20b. For this purpose, the first assembly 20 may include a length-adjustable housing 21 having a housing sleeve 22 with internal threads and a pretensioning element 23 with external threads. The pretensioning element 23 is suitably configured as a lock nut that at least partially closes the housing sleeve 22 at its axial end, i.e., on one side. The housing sleeve 22 has a first stop surface 20a, and the pretensioning element 23 has a second stop surface 20b. For example, the first stop surface 20a may be formed by the radially inner protrusion or axial side of the flange of the housing sleeve 22. The second stop surface 20b is suitably formed by the axial end face of the pretensioning element 23. The internal threads of the housing sleeve 22 and the external threads of the pretensioning element 23 can interact, thereby forming the threaded mechanism of the pretensioning configuration 11.
[0050] The damping system 10 is preferably connected to the thrust tube 50 via a pretensioning element 23, particularly a locking nut, for example, screwed onto the thrust tube 50.
[0051] To accommodate changes in pretension force and possible compression or relaxation of the spring mechanism 31, the second component 40 includes a protruding bolt 41 and a retaining mechanism 42, for example in the form of a slotted nut, which can be variably positioned axially on the bolt 41. The axial side of the bolt flange can form a third stop surface 40a, while the axial end face of the retaining mechanism 42 appropriately forms a fourth stop surface 40b. Therefore, the distance between the third stop surface 40a and the fourth stop surface 40b can be adjusted similarly to the pretensioning structure 11 on the first component 20. In particular, the distance between the third stop surface 40a and the fourth stop surface 40b can be adjusted such that, in the initial position shown, the first stop surface 20a and the third stop surface 40a, as well as the second stop surface 20b and the fourth stop surface 40b, are aligned with each other. This prevents axial clearance in the second component 40 and / or the spring mechanism 30 in the initial position.
[0052] Figure 2 Show Figure 1 An example of the damping system 10 in the first load position is shown, where pressure exceeding the pretension force acts on the connector 51 (shown only partially). In this case, the third stop surface 40a of the second component 40 lifts the spring structure 30 away from the first stop surface 20a of the first component 20. This causes a force flow from the connector 51 through the third stop surface 40a, through the spring structure 30, and further through the second stop surface 20b to the first component 20, thereby applying force to the thrust tube 50. Due to the deflection of the second component 40 relative to the first component 20, the fourth stop surface 40b also lifts away from the spring structure 30 in this case. Gaps are created between the first stop surface 20a and the spring structure 30, and between the fourth stop surface 40b and the spring structure 30, respectively, with dimensions appropriately matching the spring travel of the spring structure 30.
[0053] Figure 3 Show Figure 1 An example of the damping system 10 in the second load position.
[0054] In the second load position, a tension exceeding a predetermined preload is applied to the connector 51 (shown only partially). In this case, the fourth stop surface 40b of the second assembly 40 lifts the spring structure 30 away from the second stop surface 20b of the first assembly 20. This causes a force flow from the thrust tube 50 through the first stop surface 20a, through the spring structure 30, and further through the fourth stop surface 40b to the second assembly 40, and thus to the connector 51. Due to the deflection of the second assembly 40 relative to the first assembly 20, the third stop surface 40b also lifts away from the spring structure 30 in this case. Gaps are created between the second stop surface 20b and the spring structure 30, and between the third stop surface 40a and the spring structure 30, respectively, with dimensions appropriately matching the spring travel of the spring structure 30.
[0055] Figure 4 An example of a damping system 10 for a linear actuator in its initial position is shown. The damping system has a first component 20 including two opposing stop surfaces 20a, 20b for a spring assembly 30. The damping system 10 also includes a second component 40 axially movably supported relative to the first component 20 and configured to lift the spring assembly 30 away from either the first stop surface 20a or the second stop surface 20b in the event of axial movement relative to the first component 20. For this purpose, the second component 40 has two opposing stop surfaces 40a, 40b.
[0056] In the example shown, the first component 20 includes a rotor 52, which is part of the drive mechanism of the linear actuator, and includes a nut housing 53 rigidly connected thereto, for example, tightened. The nut housing 53 is rotatably supported in the housing of the linear actuator (not shown) by a bearing 54 and is simultaneously axially fixed.
[0057] The second component 40 is at least partially formed by a ball nut 56, which is axially movably arranged on the rotor 52 within the nut housing 53. The ball nut 56 is effectively connected to the ball screw 57 of the linear actuator via balls. This allows the force flow from the ball screw 57 to the nut housing 53—and through the bearing 54 to the linear actuator housing—or the opposite force flow, to be guided by the spring configuration 30, and prevents force peaks from occurring in the sensitive components of the linear actuator, such as the bearing 54, the ball screw 57, and / or the ball nut 56.
[0058] In the example shown, the spring assembly 30 has two elastic spring mechanisms 31a and 31b, each consisting of three disc spring assemblies 33, each disc spring assembly 33 comprising two layered disc springs. For clarity, only one disc spring assembly 33 is labeled with reference numerals. The first spring mechanism 31a is axially supported on the fifth stop surface 20c of the first assembly 20 by means of its end facing away from the first stop surface 20a and the third stop surface 40a. The second spring mechanism 31a is appropriately axially supported on the sixth stop surface 20d of the first assembly 20 by means of its end facing away from the second stop surface 20b and the fourth stop surface 40b. In this case, both spring mechanisms 31a and 31b are supported not only on the fifth stop surface 20c or the sixth stop surface 20d, but also preferably on the fifth stop surface 20c or the sixth stop surface 20d, in which the second assembly 40 is deflected relative to the first assembly 20, and the first spring mechanism 31a or the second spring mechanism 31b is even more strongly compressed.
[0059] Figure 5 An example of a damping system 10 for a linear actuator is shown, the damping system having a second component 40 rigidly connected to a spring configuration 30. The damping system 10 also has a first component 20 including two stop surfaces 20a, 20b, the second component 40 being axially movably supported relative to the first component. The second component 40 is at least partially formed by the thrust tube 50 of the linear actuator.
[0060] In the example shown, the first component 20 includes a nut housing 53 for a ball nut 56 of a linear actuator, the ball nut being effectively connected to a ball screw 57 via balls. The nut housing 53 extends radially inward at its end. The axial side of the flange forms a first stop surface 20a in this case.
[0061] The first component 20 preferably also includes a pretensioning element 23, in this example in the form of a slotted nut, which is screwed into the nut housing 53 through its internal threads. In this case, the slotted nut can serve as a locking nut, at least partially closing the nut housing 53 axially on one side. The axial side of the pretensioning element 23 forms a second stop surface 20b. The nut housing 53, together with the pretensioning element 23, forms a pretensioning structure 11 with a threaded mechanism for setting a predetermined pretension force on the spring structure 30.
[0062] In addition to the elastic spring mechanism 31, which takes the form of three disc spring assemblies 33, each consisting of two disc springs, the spring configuration 30 also includes a support mechanism 32 on which the spring mechanism 31 can be supported under a predetermined pretension. The support mechanism 32 is configured as a safety nut 58, which, in the event of impaired interaction between the ball screw 57 and the ball nut 56, such as in the event of ball failure, can interact with the ball screw 57 to prevent uncontrolled axial movement of the ball screw 57 relative to the ball nut 56 or the nut housing 53.
[0063] If the pressure load acting on the thrust tube 50 exceeds the rated force of the linear actuator, there is a risk of damage, such as damage to the balls or damage to the bearings of the nut housing 53 (not shown) (see Figure 4 Therefore, the pretension force is preferably set to be substantially the same as the rated force. When the pressure load on the thrust tube 50 exceeds the predetermined pretension force, the spring configuration 30 can now be compressed, thus allowing the safety nut 58 to be effectively connected to the ball screw 57. Therefore, overload, particularly overload of the balls, can be avoided.
[0064] Figure 6 An example of a damping system 10 for a linear actuator is shown. The damping system has a first component 20, which includes a safety nut 58 for the linear actuator and four stop surfaces 20a, 20b, 20c, and 20d. The damping system 10 also includes a spring structure 30 consisting of two spring mechanisms 31a and 31b, and a second component 40 consisting of two stop surfaces 40a and 40b. In this example, the damping system 10 is in an initial position, in which the spring structure 30 is stopped on the mutually aligned first stop surfaces 20a and 40a, and on the mutually aligned second stop surfaces 20b and 40b.
[0065] In addition to the safety nut 58, the first assembly 20 also includes a nut housing 53 and a pretensioning element 23, wherein the safety nut 58 and the pretensioning element 23 are screwed into the nut housing 53 at opposite ends. The axial side of the pretensioning element 23 forms a fifth stop surface 20c in this configuration, and the axial end face of the safety nut 58 forms a sixth stop surface 20d. The spring configuration 30 is arranged in sections between the fifth stop surface 20c and the first stop surface 20a, and between the second stop surface 20b and the sixth stop surface 20d of the first assembly 20.
[0066] The safety nut 58 and nut housing 53, as well as the pretensioning element 23 and nut housing 53, respectively form a pretensioning structure 11, which allows the spring structure 30 to be loaded with a predetermined pretension force. By screwing the pretensioning element 23 into the nut housing 53, the pretension force of the first segment 34a of the spring structure 30, including the first spring mechanism 31a, is increased, or decreased by unscrewing the nut housing. Similarly, by screwing the safety nut 58 into the nut housing 53, the pretension force of the second segment 34b of the spring structure 30, including the second spring mechanism 31b, is increased, or decreased by unscrewing the nut housing.
[0067] The second component 40 has a ball nut 56 axially movably supported in a nut housing 53, which is effectively connected to the ball screw 57 of the linear actuator via balls. The axial end face or front face of the ball nut 56 forms a third stop surface 40a and a fourth stop surface 40b. Thus, during operation of the linear actuator, the rotational motion of the ball screw 57 is converted into the translational motion of the ball nut 56. A force corresponding to this motion, not exceeding a predetermined pre-tension, is transmitted via the spring configuration 30 to the first component 20, and further, for example, to components rigidly connected to the first component 20, such as the thrust tube 50 screwed into the safety nut 58. In this way, for example, machine components connected to the thrust tube 50 can be precisely positioned.
[0068] The pretension of the spring configuration 30 is preferably set to be substantially equal to or higher than the rated force of the linear actuator. Therefore, in cases where the tensile or compressive load on the thrust tube 50 exceeds the predetermined pretension, such as due to load peaks caused by impacts, the spring configuration 30 can compress in one of sections 34a and 34b, resulting in effective connection between the safety nut 58 and the ball screw 57. These conditions... Figure 7 and Figure 8 As shown in the image.
[0069] Figure 7 Show Figure 6 In an example of the damping system 10 in a first load position, a tension exceeding a predetermined pretension of the spring configuration 30 acts on the thrust tube 50. In this case, the tension acts on a first section 34a of the spring configuration 30 via the fifth stop surface 20c of the first assembly 20, in which the spring configuration is supported on the third stop surface 40a of the second assembly 40 and is correspondingly compressed. Therefore, the second assembly 40 lifts the first section 34a of the spring configuration 30 away from the first stop surface 20a.
[0070] Compression of the spring assembly 30 in the first section 34a causes axial displacement of the first component 20 relative to the second component 40. This effectively connects the safety nut 58 to the ball screw 57 and prevents the load on the effective connection between the ball nut 56 and the ball screw 57, especially the load on the effective connection between the balls, from increasing in a manner far exceeding the predetermined pretension.
[0071] Figure 8 Show Figure 6 An example of the damping system 10 in the second load position is shown, where pressure exceeding a predetermined pretension force of the spring configuration 30 acts on the thrust tube 50. In this case, the pressure acts through the sixth stop surface 20d of the first assembly 20 on the second section 34b of the spring configuration 30, in which the spring configuration is supported on the fourth stop surface 40b of the second assembly 40 and is correspondingly compressed. Therefore, the second assembly 40 lifts the second section 34b of the spring configuration 30 away from the second stop surface 20b.
[0072] Compression of the spring assembly 30 in the second section 34b causes axial displacement of the first component 20 relative to the second component 40. This effectively connects the safety nut 58 to the ball screw 57 and prevents the load on the effective connection between the ball nut 56 and the ball screw 57, especially the load on the effective connection between the balls, from increasing in a manner far exceeding the predetermined pretension.
[0073] List of reference numerals
[0074] 10 Damping System
[0075] 11 Pre-tensioned structure
[0076] 20 First Component
[0077] 20a First stop surface
[0078] 20b Second stop face
[0079] 20c Fifth stop face
[0080] 20d Sixth Stop Face
[0081] 21. Shell
[0082] 22 Housing sleeve
[0083] 23 Pretensioning element
[0084] 30 Spring Construction
[0085] 31 Spring Mechanism
[0086] 31a First Spring Mechanism
[0087] 31b Second Spring Mechanism
[0088] 32 Supporting Institutions
[0089] 33 Disc Spring Assembly
[0090] 34a First Section
[0091] 34b Second Section
[0092] 40 Second Component
[0093] 40a Third stop surface
[0094] 40b Fourth stop face
[0095] 41 bolts
[0096] 42 Security agencies
[0097] 50 thrust tube
[0098] 51 Connector
[0099] 52 rotors
[0100] 53 Nut housing
[0101] 54 bearing
[0102] 56 Ball Nuts
[0103] 57 Ball Screw
[0104] 58 Safety Nuts
Claims
1. A damping system (10) for a linear actuator, the damping system having a first component (20) including a first axial stop surface (20a) and a second axial stop surface (20b). Its features are, An elastic spring structure (30) that, in its initial position, is axially stopped on the first and second axial stop surfaces (20a, 20b) under a predetermined pretension force, and The second component (40) is axially movably supported relative to the first component (20) and is configured to lift the spring structure (30) from the first axial stop surface (20a) or from the second axial stop surface (20b) in the event of axial movement relative to the first component (20), wherein the second component (40) has a third axial stop surface (40a) and a fourth axial stop surface (40b), wherein the spring structure (30) is axially stopped on the third stop surface (40a) and the fourth stop surface (40b) in the initial position under the action of a predetermined pretension force.
2. The damping system (10) according to claim 1. Its features are, In the initial position, the first axial stop surface (20a) is radially aligned with the third stop surface (40a), and the second axial stop surface (20b) is radially aligned with the fourth stop surface (40b).
3. The damping system (10) according to claim 1. Its features are, The first component (20) has a fifth stop surface (20c) and a sixth stop surface (20d), on which the spring structure (30) is supported at least by the predetermined pretension force.
4. The damping system (10) according to claim 1. Its features are, The spring configuration (30) is spaced apart from the first or second axial stop surface (20a, 20b) in the load position.
5. The damping system (10) according to claim 1. Its features are, The spring structure (30) has at least one support mechanism (32) and at least one elastic spring mechanism (31; 31a, 31b), the spring mechanism being supported on the at least one support mechanism (32) at least under the action of the predetermined pretension force, wherein the at least one support mechanism (32) is configured to stop on the first or second axial stop surface (20a, 20b).
6. The damping system (10) according to claim 1. Its features are, The spring structure (30) has at least one spring mechanism (31; 31a, 31b) configured as a disc spring assembly (33).
7. The damping system (10) according to claim 1. Its features are, The first axial stop surface (20a) and the second axial stop surface (20b) are arranged opposite each other, and the spring structure (30) is arranged between the first axial stop surface (20a) and the second axial stop surface (20b).
8. The damping system (10) according to claim 1. Its features are, The first axial stop surface (20a) and the second axial stop surface (20b) are oriented in opposite directions to each other and are arranged between the first section (34a) and the second section (34b) of the spring structure (30).
9. The damping system (10) according to claim 1. Its features A pre-tensioning structure (11) is configured to adjust the predetermined pre-tension force.
10. The damping system (10) according to claim 1. Its features are, The pretensioning structure (11) has a threaded mechanism, through which the spring structure (30) can be compressed or decompressed at least in sections.
11. The damping system (10) according to claim 1. Its features are, The distance between the first axial stop surface (20a) and the second axial stop surface (20b) is variable.
12. The damping system (10) according to claim 1. Its features are, The second component (40) and the spring structure (30) are arranged radially within the first component (20).
13. A linear actuator (10) having a damping system (10) according to any one of the preceding claims.
14. The linear actuator according to claim 13, Its features are, The predetermined pretension force is less than or equal to the rated force of the linear actuator.
15. The linear actuator according to claim 13, Its features The ball screw (57), the ball nut (56) effectively connected to the ball screw (57), and the safety nut (58) connected to the ball nut (56), wherein the spring structure (30) is arranged at least in sections between the ball nut (56) and the safety nut (58).
16. The linear actuator according to claim 13, Its features The ball screw (57), the ball nut (56) effectively connected to the ball screw (57), and the nut housing (53), the ball nut (56) being axially movable in the nut housing, the nut housing (53) forming at least a portion of the first component (20), and the ball nut (56) forming at least a portion of the second component (40).
17. The linear actuator according to claim 13, Its features are, The thrust tube (50) and connector (51) wherein the damping system (10) has a housing (21) rigidly connected to the thrust tube (50), the housing forming at least a portion of the first component (20), and the connector (51) forming at least a portion of the second component (40) or being rigidly connected to the second component (40).