JP2017514070A - Torque limit system - Google Patents

Abstract

The present invention relates to torque transfer and torque limiting system technology and applications. The present invention uses a tolerance ring to protect machinery and drivetrains from damage due to mechanical overload and to control power transfer between a single power input shaft and one or more power output shafts. Related to providing an improved torque limiting system. The present invention relates to an automobile differential, which provides a differential limiting device when one wheel encounters a low traction situation, provides friction within the differential, No "slip or rotational difference can be limited and the rotational difference between the two power output shafts or drive shafts can be controlled. [Selection] Figure 3

Description

Cross-reference to related applications This application is a provisional application serial number 61 / 880,178 filed on September 20, 2013 entitled “Tolerance Ring / Differential Limiting Device Including Circumferential Clutch” and “Difference with Tolerance Ring”. Claims priority in connection with provisional application serial number 61 / 907,386, filed November 22, 2013, entitled “Motion Restriction Device”, and January 2014, entitled “Mechanical Locking System for Tolerance Rings” Claims priority in relation to provisional application serial number 61 / 927,111 filed on the 14th. The contents of which are incorporated herein by reference and are not admitted to be prior art with respect to the present invention by reference in this cross-reference section.

The present invention relates to torque limiting system technology, torque slip and torque limiting devices, and application to power delivery assemblies. The torque limiting device protects the mechanical device from damage due to mechanical overload, and can be used as a torque moving device and a torque limiting device in various assemblies.

Tolerance rings known in the art are devices that can provide torque transfer, axial holding, and radial load between mating cylindrical parts. When the tolerance ring is assembled with pressure between the aforementioned mating cylindrical parts, each corrugation provides a spring force to provide friction. The friction capacity of the tolerance ring is the resultant force of all corrugations and is the coefficient of friction of the mating parts.

Tolerance rings are cheap, light, simple and durable, and have many advantages such as rapid device assembly. Tolerance ring functions when a wide range of mating part materials and friction capacities are required There are limitations.

As is known in the art, a differential is a device that transfers rotational energy from a single power input source to two power output shafts or shafts. In land vehicles, a difference in rotation is created when the outer wheels need to bend much faster than the inner wheels when turning. However, when one wheel encounters a low traction situation such as mud, snow or ice, it controls the “undesirable” slip and the rotational difference between the wheels, thus limiting the “undesirable” movement difference Appropriate for differential assemblies.

As is well known in the art, differential limiting devices are expensive, complex and use viscous, locking devices, torque sensing gear systems, friction clutch plates or cones, or other means of limiting the difference in motion. Heavy and high friction loads can be a challenge.

Objects and features of the invention More specifically, the present invention relates to an industrial torque limiter and differential limiting device for land vehicles that provides friction torque to control wheel rotational differences. The main object and feature of the present invention is to provide a system that overcomes the above problems.

It is a further object and feature of the present invention to provide a predetermined amount of torque within the differential that resists relative movement of the output shaft to desirably distribute torque when friction is reduced on one output shaft or drive wheel. Provides a simple, durable, inexpensive means of using a tolerance ring as a fixed, variable, adjustable and active torque limiting assembly, independent between two drive shafts or two output shafts Is to provide a system that can rotate.

It is a further object and feature of the present invention to provide a differential limiter differential system that is versatile, simple, durable and inexpensive.
Using a tolerance ring to limit the movement of the torque when a predetermined threshold is exceeded, allowing independent rotation between the two drive shafts or output shafts;
Using a tolerance ring to provide a range of friction torque slip values that vary with the response of input energy to angular acceleration, allowing independent rotation between two drive shafts or output shafts;
Using a tolerance ring that improves existing functionality for torque detection and other types of limiting limiting differential limiting devices, allowing independent rotation between two drive shafts or output shafts;
Use a simple, durable, inexpensive means tolerance ring to increase the versatility and functionality of torque limiters and differential limiters in automotive and industrial drive lines, and between two drive shafts or output shafts To rotate independently,
Provide independent rotation between the two drive shafts or output shafts while providing minimal frictional load on the power source,
In a way that provides a long service life, with independent rotation between the two drive shafts or output shafts,
A method of adjusting the torque limiter as a function of one or more parameters, allowing independent rotation between the two drive shafts or output shafts,
Using a tolerance ring that functions durability and consistency in the elastic region of the material, allowing independent rotation between the two drive shafts or output shafts,
Has an axial groove structure that increases or decreases friction torque, or is fixed, variable, adjustable, and works durable under continuous torque slip operating conditions with active torque slip values .

It is a further object and feature of the present invention to provide a system with an axial groove with a mechanical force that can hold the corrugation in the groove and prevent rotation of the tolerance ring corrugation relative to the circumferential part. In particular, because the spring force and friction need not prevent destructive rotation of the aforementioned tolerance ring, the aforementioned groove is wider in the tolerance ring, ensuring a range of fixed and variable torque slip values previously unavailable. Can function.

Other objects and features of the present invention will become apparent with reference to the following description.

The drawings described herein are merely for the purpose of illustrating the features of existing selections, not all are feasible and are not intended to limit the range of existing content. It is also understood that all figures are shown larger for clarity.

FIG. 1 shows an exploded perspective view of an external corrugated tolerance ring associated with a prior art assembly. FIG. 2 illustrates an exploded perspective view of the internal corrugated tolerance ring associated with a prior art assembly. FIG. 3 illustrates an external corrugated tolerance ring in an exploded perspective view relevant to the present invention. FIG. 4 shows an internal corrugated tolerance ring in an exploded perspective view relevant to the present invention. FIG. 5 shows a part of a schematic diagram of one waveform structure of an external waveform tolerance ring of a fixed value torque limiter. FIG. 6 shows a graph relating to the performance limit of the fixed value torque limiter. FIG. 7 shows a graph related to the set use torque value of the fixed value torque limiter. FIG. 8 shows a portion of an angular cross-section of a complete variable value due to a response to an angular acceleration torque limiting assembly. FIG. 9 shows a close-up of a portion of the cross-sectional view of the variable values due to the response to the angular acceleration torque limiter, excluding the tolerance ring. FIG. 10 shows a perspective view of the outer cylindrical part of the variable value due to the response to the angular acceleration torque limiter, excluding the tolerance ring and the inner cylindrical part. FIG. 11 shows a portion of a schematic diagram of one waveform structure of a variable external waveform tolerance ring due to a response to an angular acceleration torque limiter. FIG. 12 shows a graph related to the performance limit of a variable due to a response to an angular acceleration torque limiter. FIG. 13 shows a graph related to the set use torque value of the variable due to the response to the angular acceleration torque limiter. FIG. 14 shows a part of an axial sectional view of the axial movement torque limiter. FIG. 15 shows a part of an annular sectional view of variables by means of an axial movement torque limiter. FIG. 16 shows a part of an axial sectional view of variables by an axial movement torque limiter. FIG. 17 shows a portion of a schematic diagram of one waveform structure of a bidirectional variable external waveform tolerance ring in response to an angular acceleration torque limiter. FIG. 18 shows a graph related to the performance limit of a bidirectional variable due to a response to the angular acceleration torque limiter. FIG. 19 shows a graph related to the setting use torque value of the bidirectional variable due to the response to the angular acceleration torque limiter. FIG. 20 shows a portion of a complete annular cross-sectional view of a complete circumferential variable value torque limiter. FIG. 21 shows a part of an annular sectional view of the drive ring of the circumferential variable value torque limiter. FIG. 22 shows a part of an axial sectional view of the drive ring of the circumferential variable value torque limiter. FIG. 23 shows a part of an annular cross-sectional view of a housing ring with a variable circumference by a torque limiter. FIG. 24 shows a part of an axial sectional view of the housing ring of the circumferential variable value torque limiter. FIG. 25 shows a part of an annular sectional view of the taper, brushing, and torque limiter. FIG. 26 shows a housing orthogonal view of the taper / brushing / torque limiter. FIG. 27 shows a part of an axial housing cross-sectional view of a taper, brushing and torque limiter. FIG. 28 shows a cross-sectional view of the active variable torque limiter. FIG. 29 shows an orthogonal view of the active variable torque limiter. FIG. 30 is a sectional view of the active variable torque limiter. FIG. 31 shows a functional block diagram of the active variable torque limiter. FIG. 32 shows a graph of the relationship between tolerance ring height, compression, ring stiffness and wear sensitivity. FIG. 33 shows a graph of the relationship between tolerance ring height, compression, ring stiffness and sensitivity to wear. FIG. 34 shows a graph of the relationship between tolerance ring height, compression, ring stiffness and wear sensitivity. FIG. 35 shows a portion of an annular cross-section of a differential limiting device for an angular acceleration internal friction device with variable values.

Detailed description of the best mode and preferred embodiments of the invention

The following description is provided to enable any person skilled in the art to make and use the invention and describes the best mode contemplated by the inventors in carrying out the invention. However, various modifications will still be readily apparent to those skilled in the art, since the generic principles of the present invention are defined herein to provide a torque limiting system in particular.

We describe herein a novel inventive combination of torque limiters that use tolerance rings that can be used as industrial torque limiters and can be applied to open differentials to limit rotational differences.

There are two basic types of automobile differentials: standard or “open” differentials and differential limiting devices. Both are well known in the art and have benefited from development for many years. Both functions are very simple. First, power is transmitted from a single power source to two drive shafts or output shafts. It then allows independent rotation or creates a rotational difference between the two drive shafts or output shafts. This difference in rotation occurs, for example, when the land vehicle turns and the outer wheels must bend much faster than the inner wheels.

“Open” differentials work well in most situations. However, when one wheel is buried in mud or on ice, the difference in the traction force between the drive main wheels causes the drive main wheels to slip and give no traction force. This is because the “open” differential provides an almost unlimited difference in motion, making the car move badly and transferring most of the output to the wheels with minimal traction.

Differential limiters are well known in the art and are relatively large, heavy, expensive and complex. However, the differential limiter is still very simple in function. The differential limiter limits the difference in rotation in various ways to provide motive force with the traction force impaired. The device is also a preferred option for all models due to safety and performance, but is excluded from the standard features due to cost.

Many existing industrial torque limiters are complex, large, heavy and expensive. Trelan rings are known in the art and provide simple and inexpensive torque transfer and limiting. The tolerance ring described above has a corrugated surface and a flat surface, with external or internal corrugations arranged in a circle in single or multiple rows, with uniform or varying heights and gradients, and a flat circumferential edge. Made of resilient metal or plastic, but not limited to, split or segmented ring shapes with various diameters. Torque limiting assemblies that use tolerance rings can limit the amount of torque that travels between the assemblies to a maximum. If the tolerance ring is arranged in a compressed manner, for example in the annular space between the shaft and the hole, the corrugated structure is compressed. The corrugated structure acts as a spring and provides a predetermined amount of friction torque to exert a radial force against the shaft and hole surfaces. More preferably, there is a linear relationship that determines the torque value between compression and friction. The rotation of the housing or shaft transmits a similar rotation to other shafts or housings. If the rotational force is applied so that the input torque is higher than a predetermined threshold, one will rotate relative to the other, i.e., cause slip.

When such slip occurs, the wavy surface slips before the flat surface. This is because at least one compression point of the wavy surface is smaller than the compression point of the flat surface. If such slips are repeated under working conditions, the corrugated structure will be worn away or damaged, or parts that are in contact with the corrugated structure will be damaged. Flat surface slips generally do not cause scuffing. Current methods include the attachment of soft materials that receive sufficient corrugations to score and grab the corrugations, but this is not a desirable solution for all situations and long-term performance. It is not considered.

For cylindrical parts that come into contact, problems associated with slippage of the wavy surface of the tolerance ring can primarily result in functional limitations due to low spring or resistance forces.

A further limitation is that the tolerance ring assembly described above is limited to one predetermined working torque slip value, which is set by design and manufacture, so that adjustments, wear, design changes and other factors are modified. Is difficult or impossible.

Extensive current research has little knowledge of how the tolerance ring works at low torque / torque slip values, and no system exists to address the problem.

The object of the present invention is to expand the versatility and functionality of the tolerance ring and provide a wide range of durable, inexpensive fixed, variable and adjustable differential limiters, fixed and adjustable To provide a wide range of durable and inexpensive devices that provide a variable torque limiter. Therefore, the present invention is needed.

FIG. 1 shows an external corrugated tolerance ring in an exploded perspective view of a common prior art assembly. FIG. 1 shows an external corrugated tolerance ring 1, an external cylindrical part 2 and an internal cylindrical part 3. When the torque limit of this assembly part is exceeded, either the outer cylindrical part 2 or the inner cylindrical part 3 slides on the other, and the corrugated structure of the external corrugated tolerance ring 1 slides on the outer cylindrical part 2 to obtain a predetermined torque value. It is understood to cause damage and rapid decline.

FIG. 2 illustrates an internal corrugated tolerance ring in an exploded perspective view of a common prior art assembly. FIG. 2 shows an inner corrugated tolerance ring 1 n, an outer cylindrical part 2 and an inner cylindrical part 3. When the torque limit of this assembly part is exceeded, either the outer cylindrical part 2 or the inner cylindrical part 3 slips on the other, and the corrugated structure of the internal corrugated tolerance ring 1n slides on the inner cylindrical part 3, and the predetermined torque value It is understood to cause damage and rapid decline.

FIG. 3 shows the external corrugated tolerance ring of the exploded perspective view assembly relevant to the present invention. FIG. 3 shows a preferred embodiment 50 of the present invention, an external corrugated tolerance ring 1, an external cylindrical part 2, an internal cylindrical part 3, and a constant value axial groove 4a. It is understood that either the outer cylindrical part 2 or the inner cylindrical part 3 slides relative to the other when the torque limit of this assembly part is exceeded. However, there is means for mechanically locking the corrugation of the external waveform tolerance ring 1 to the external cylindrical part 2 by one or more corrugations of the fixed value axial groove 4a, and the required internal cylindrical part 3 slides into the external cylindrical part 2, The external corrugated tolerance ring 1 remains mechanically locked to the external cylindrical part 2. Thus, a durable, simple and inexpensive torque limiting assembly is provided.

FIG. 4 shows an internal corrugated tolerance ring of the exploded perspective view assembly associated with the present invention. FIG. 4 shows an internal corrugated tolerance ring 1n, an external cylindrical part 2, an internal cylindrical part 3, and a constant value axial groove 4a. It is understood that either the outer cylindrical part 2 or the inner cylindrical part 3 slides relative to the other when the torque limit of this assembly is exceeded, so that the principles described above are applied.

It has been found that there are a number of ways to mechanically lock and restrict the tolerance ring using (but not limited to) keys, dowels, pins, and other means. One skilled in the art understands that the above-described shape is exemplary in nature and is not limiting. The constant value axial groove 4a of a given depth and design can be cut into the housing inner diameter or shaft outer surface by broaching, CNC or additive manufacturing, and other processes known in the art (but not limited thereto). it can. The principles of the present invention also apply to various types, shapes, and components of external or internal corrugated tolerance rings that rotate in any direction without limitation. More preferably, the principles of FIGS. 4 and 5 can be applied to all shapes, structures and materials of the tolerance ring without limitation.

By means of mechanically locking the corrugated surface of the ring to the desired part, damage can be prevented and the reliability and versatility of the tolerance ring assembly can be improved. For example, the present invention provides a system that is durable and allows a wide range of torque movement and slip values. This will be further explained in the content section.

5, 6, and 7 show two graphs of a preferred embodiment 50 of the present invention, a fixed value torque limiter, relating to a portion of the schematic and the set working torque slip value, function.

FIG. 5 further introduces the force Ft. This is a tangential force of the inner cylindrical part 3 with respect to the inner cylindrical part surface 3a. Preferably, constrained by the constant value axial groove 4a, in any rotational direction, on the inner cylindrical part surface 3a of the inner cylindrical part 3 by sliding and pushing on the external corrugated tolerance ring 1 based on the relative angular acceleration, As a result of being driven by the motive force, a force Ft is generated by the inner cylindrical part 3.

Since the force Ft is a force vector directed in a tangential direction with respect to the inner cylindrical part surface 3a of the inner cylindrical part 3 of a tangential force with respect to the inner cylindrical part surface 3a in FIG. The torque is replaced with the same torque as the Ft-fold radius of the tangential force with respect to the cylindrical part surface 3a.

FIG. 5 shows a part of a schematic diagram of one waveform structure of an external waveform tolerance ring of a fixed value torque limiter. 5 corresponds to compression of the outer corrugated tolerance ring 1, the outer cylindrical part 2, the constant value axial groove 4a, the inner cylindrical part 3, the inner cylindrical part surface 3a (the rotation direction 11 and the force Ft, the outer corrugated tolerance ring 1). Introducing the compression value standard 0-Y).

For FIG. 5, it is preferred that the constant value axial groove 4a provides a predetermined fixed invariant torque slip value based on the variable angular acceleration. Even if the angular acceleration of the inner cylindrical part 3 increases or decreases, the external waveform tolerance ring 1 can maintain a constant torque slip value. This is because neither the compression capacity nor the torque slip value can be changed. The external corrugated tolerance ring is mechanically locked in the groove by an alternative to corrugated structure. The preferred embodiment 50 preferably functions as a device that provides a constant torque slip value in any rotational direction based on all rotational conditions.

FIG. 6 shows a graph relating to the performance limit of the fixed value torque limiter. The aforementioned graph is directly related to FIG. The torque value standard 0-T is introduced. This shows a torque slip value related to compression of the compression value reference 0-Y, which corresponds to compression of the rotation direction 11 (not shown) and the external waveform tolerance ring 1.

For FIG. 6, it is preferable that the constant value axial direction 4a indicates a constant torque slip and compression value. This value cannot be changed when the angular acceleration of the inner cylindrical part increases or decreases because the compression capacity cannot be changed. This phenomenon can be explained by the following relationship: At 4a, the force Ft is equivalent to the force 4a. This relative parameter is important for the performance of the torque limiting system for the reasons described herein.

When the external corrugated tolerance ring 1 is mechanically locked to the external cylindrical part 2 by the constant value axial groove 4a, work without change due to various angular accelerations or loss of mechanical gripping force Based on the conditions, it is possible to reliably transmit a fixed predetermined torque slip value from zero to the maximum elastic value related to the external waveform tolerance ring 1. This should be done if a wide range of fixed constant torque slip values are required under continuous fixed value torque slip operating conditions and tolerance rings are required for durable functions. It is preferred that the form is particularly beneficial.

As is known in the art, since the mechanical force holding the tolerance ring corrugation of the axial groove 4a may be greater than the tangential force or the angular acceleration of the inner cylindrical part 3, the relationship is mf may be larger than the tangential force Ft. In particular, since there is no need to prevent relative rotation without the need for spring forces and / or friction, the axial groove 4a ensures a wider corrugated tolerance ring 1 in a wider range of torque slip values not previously available. Can function.

FIG. 7 shows a graph related to the set use torque value of the fixed value torque limiter. FIG. 7 further introduces and describes how torque slip values were generated by changing the tolerance ring over time, and after the set period and each relationship, first the assembly parts and the used torque value wtv (external waveform tolerance ring The concept of the set torque value itv (the torque value of the external waveform tolerance ring 1) when attached to the torque value of 1 is introduced.

The torque value reference 0-T and the compression value reference 0-Y are shown, the reference rx1k is introduced, and the rotation of the inner cylindrical part 3 is shown in 1000 units.

About FIG. 7, the line relevant to the change of a torque slip value is shown. In particular, FIG. 7 shows the torque slip and compression value starting from the set torque value itv and decreasing to the use torque value wtv. After reaching the use torque slip value, the tolerance ring functioning in the preferred embodiment 50 is shown to provide a very constant and reliable use torque slip value in continuous working conditions.

During testing on a lubrication tester that simulates the function of a differential limiter or torque limiter, it was found that the set torque value dropped significantly during the first 1000 revolutions. For example, the set torque value itv is 38 ft-lbs (11.6 m), and the use torque value wtv is 28 ft-lbs (8.5 m) at about 1000 revolutions. In this example, the average drop between the set torque value and the use torque value is about 25%. Thus, for the reasons described herein, this indicates the criticality of the torque limiting system settings and relative dimensions.

Thus, this test shows that tolerance rings used in similar installations and thousands of rotation cycles can provide a very constant and reliable use torque value wtv. Those skilled in the art understand that the above-described studies, shapes, and descriptions are exemplary in nature and unlimited.

Thus, the schematics and graphs of FIGS. 5, 6 and 7 are invariant when the system has mechanically locked one or more corrugated structures of the tolerance ring by the fixed value axial groove 4a and secured to the torque limiting device. A method for simply and reliably providing a reliable predetermined use torque slip value will be described.

It has been found that there are a number of ways to mechanically lock and restrict the tolerance ring using (but not limited to) keys, dowels, pins, and other means. One skilled in the art understands that the aforementioned shapes are exemplary in nature and unlimited. Fixed value axial grooves 4a of a given depth and design can be cut into the housing inner diameter or shaft outer surface by broaching, CNC or additive manufacturing, and other processes known in the art (but not limited thereto). it can. The principles of the present invention also apply to various types and shapes of external or internal corrugated tolerance rings and parts thereof, rotating in any direction without limitation. The principles of FIGS. 4 and 5 are preferably applicable without limitation to all shapes, structures and materials of the tolerance ring.

8, 9, and 10 show a portion of a cross-sectional angle view of a variable value in response to an angular acceleration torque limiting assembly and a perspective view.

FIG. 8 shows a portion of a cross-sectional view of a complete variable value due to a response to an angular acceleration torque limiting assembly. FIG. 8 shows an external corrugated tolerance ring 1, an external cylindrical part 2, an internal cylindrical part 3, a mechanical minimum down ramp stop 8, a down ramp 9, a mechanical maximum down ramp stop 10, a mechanical master corrugation It comprises a stop 10 a, both ends of the external waveform tolerance ring 1, one or more corrugation end stops 17, and a rotation direction 11. The preferred direction of rotation of the inner cylindrical part 2 is also shown.

FIG. 8 illustrates a preferred embodiment 100 that provides a predetermined fixed minimum torque slip value with a mechanical minimum downramp 8 in normal rotational conditions. When the angular acceleration of the inner cylindrical part 3 increases, it is preferable that the external waveform tolerance ring 1 reduces the down ramp 9 to decrease the clearance between the down ramp 9 and the inner cylindrical part 3 and increase the torque slip value.

Therefore, it is preferable that the compression process and the torque increase until the corrugation reaches the dynamic maximum down-ramp stop 10, which is the time when the torque slip threshold is reached. If angular acceleration continues, the preferred embodiment 100 preferably functions as a torque limiter to provide a predetermined maximum torque slip value. It is preferable that the external waveform tolerance ring 1 return to the mechanical minimum value down ramp stop 8 and the minimum torque slip value because the down ramp 9 has a side surface released by itself and the angular acceleration is stopped or rejected. If the inner cylindrical part 3 rotates in the opposite direction (not shown), the preferred embodiment 100 is similar to the predetermined minimum as produced by the mechanical minimum downramp stop 8 in normal relative rotation situations. Generate torque slip value.

Preferably, one or more corrugation end stops 17 are on the opposite side of the external waveform tolerance ring 1 to limit the maximum compression and maximum torque movement (predetermined maximum torque slip value) to a predetermined range. These relative parameters are important to the implementation of the torque limiting system for the reasons described herein.

FIG. 9 shows a close-up of a portion of the cross-sectional view of the variable values due to the response to the angular acceleration torque limiter, except for the tolerance ring. FIG. 9 shows a close-up of FIG. 8 without the external waveform tolerance ring 1. In this figure, the down lamp 9 is shown more clearly. This figure also preferably shows the outer cylindrical part 2, the inner cylindrical part 3, the mechanical minimum downramp stop 8, the downramp 9 and the mechanical maximum downramp stop 10 with the direction of rotation 11.

FIG. 10 shows a perspective view of the outer cylindrical part with variable values due to the response to the angular acceleration torque limiter, excluding the tolerance ring and the inner cylindrical part. FIG. 10 shows a perspective view of the outer cylindrical part 2 of FIG. 8 with the outer cylindrical part 2 alone and together with the downramp 9, the mechanical maximum downramp stop 10 and the mechanical master corrugation stop 10a.

Those skilled in the art will have unlimited variations in characteristics for the mechanical minimum downramp stop 8, downramp 9, mechanical maximum downramp stop 10, the relationship being long or short, linear, convex It is understood that including, but not limited to, stepped or abrupt, less or greater compression of concave surfaces.

Since the side of the down ramp allows compression in only one direction, it is preferred that embodiment 100 of the present invention be designed to rotate only in the counterclockwise direction. As one method, it is more preferable that the present invention 100 is configured to rotate the torque slip in either the counterclockwise direction or the clockwise direction (but not in both directions).

Both the outer cylindrical part 2 and the inner cylindrical part 3 are preferably constructed and arranged to slide and rotate in conjunction with each other in the same angular direction. These components are preferably constructed and arranged in a device, such as a differential, between the power supply and main wheels of the land vehicle. These parts are preferably constructed and arranged so that the angular acceleration itself can be shown as a suddenly accelerated rotational speed or as a tangential impact force.

The external corrugated tolerance ring 1 is in the housing bore and around the corresponding shaft, or in the groove in the housing bore or around the corresponding shaft, or in the groove in the housing bore and around the shaft, or in these recommended arrangements. It is preferably constructed and arranged in combination (but not limited to). The elements of the preferred embodiment 100 can be lubricated in any manner known in the art.

As mentioned above, the geometry of the present invention provides various torque slip values in only one direction and provides a fixed constant torque slip value in the other direction. With respect to land vehicles and other drive units, they can move forward or reverse.

Furthermore, since the above-described principle is applied, it is preferable that the embodiment 100 is configured with the internal waveform tolerance ring 1a (not shown) (but not limited thereto).

11, 12 and 13 show a part of the schematic diagram and two graphs relating to the setting use torque slip value of the variable value by the angular acceleration torque limiter, the preferred embodiment 100 of the present invention, and the function.

FIG. 11 shows a part of a schematic diagram of one corrugation of a variable external waveform tolerance ring due to a response to an angular acceleration torque limiter.

FIG. 11 shows an external corrugated tolerance ring 1, an external cylindrical part 2, an internal cylindrical part 3, an internal cylindrical part surface 3 a, a mechanical minimum value downramp stop 8, a downramp 9, a mechanical maximum value downramp stop 10, The compression value reference 0-Y, the force Ft, and the rotation direction 11 are shown.

In FIG. 11, it is preferred that the lowest value torque slip output be generated at the lowest value downramp stop 8 which produces a predetermined lowest torque slip value in normal relative rotational conditions. As the angular acceleration of the inner cylindrical part 3 increases, the outer corrugated tolerance ring 1 is inserted into the reduced clearance between the outer cylindrical part 2, the inner cylindrical part 3 and the inner cylindrical part surface 3a in the direction of rotation 11 of the downramp 9. Is done. This action causes compression and an increase in torque slip value. Thus, compression and torque are increased until the external waveform tolerance ring 1 is pushed by the mechanical maximum downramp stop 10, at which point the torque threshold is reached. If angular acceleration continues, the device preferably functions as a torque limiter and provides a predetermined maximum torque slip value. It is preferable that the external waveform tolerance ring 1 return to the mechanical minimum value down ramp stop 8 and the normal predetermined constant minimum torque slip value when the down ramp 9 has its own released side and the angular acceleration stops or rejects. . When the inner cylindrical part 3 rotates in the opposite direction (not shown), the preferred embodiment 100 is similar to the predetermined minimum as produced by the mechanical minimum downramp stop 8 in normal relative rotation situations. Generate torque slip value.

FIG. 12 shows a graph related to the performance limit of a variable due to a response to an angular acceleration torque limiter. FIG. 12 introduces a graph associated with the preferred embodiment 100 of the present invention. The graph of FIG. 12 is directly related to FIG. 11 and includes a point mechanical minimum downramp stop 8p, a line downramp 9p, a point mechanical minimum downramp stop 10p (mechanical minimum downramp stop 8, Introducing down ramp 9, which directly corresponds to mechanical maximum down ramp stop 10).

  Torque value standard 0-T, compression value standard 0-Y, point mechanical minimum value down ramp stop (including line) 8p, line down ramp 9p, point mechanical maximum value down ramp stop 10p, direction of rotation 11 Indicates.

  FIG. 12 shows that when the relative angular acceleration increases / decreases, the preferred embodiment 100 has operational limits of point dynamic minimum downramp stop 8p, line downramp 9l, point mechanical maximum downramp. It is more preferable to understand that it is defined by the stop 10p.

  In FIG. 12, the graph defines the direct relationship between compression and torque slip value variation. It shows how increases and decreases in compression and torque slip values are determined by the relative angular acceleration of the inner cylindrical part 3 and the operational limits of the preferred embodiment 100 are defined. More preferably, this relationship is as follows: At minimum mechanical ramp down stop 8, force Ft is less than or equal to F8, and at maximum mechanical down ramp stop 10, force Ft Is greater than or equal to F10. These relative parameters are important to the performance of the torque limiting system for the reasons described herein.

  FIG. 13 shows a graph related to the set use torque value of the variable due to the response to the angular acceleration torque limiter. More preferably, FIG. 13 is composed of a graph (representing torque value reference 0-T, compression value reference 0-Y, and scale Rx1k) directly related to FIG. Minimum mechanical down ramp / stop set torque value 8itv, Dynamic minimum down ramp / stop use torque value 8wtv (related to mechanical minimum down ramp / stop 8), Line down ramp 9itv and Line down ramp 9wtv (related to downramp 9), mechanical maximum value downramp / stop set torque value 10itv, mechanical minimum value downramp / stop set torque value 10wtv (related to maximum value downramp / stop 10) . Thus, the set working torque value, the mechanical minimum / maximum down ramp stop and down ramp are understood to correspond to the principles described in FIGS. 11 and 12 and herein.

  FIG. 13 shows two lines corresponding to the set use torque value of the preferred embodiment 100 and the set torque value (not shown) of the external waveform tolerance ring 1 (at zero rotation 8 itv, 9 itv, 10 itv). As the rotation increases, the set torque slip value begins to decrease with respect to the use torque values of 8 wtv, 9 wtv, and 10 wtv, and when the use torque value is achieved, the use torque value increases between torque and compression for thousands of rotations. Continue with minimal loss. These relative parameters are important to the performance of the torque limiting system for the reasons described herein.

  It shows that the preferred embodiment 100 can provide a very consistent and reliable use torque slip value. Those skilled in the art will appreciate that the foregoing research, shape, and description are exemplary in nature and do not limit the scope of the invention in any way.

  Those skilled in the art also understand that the above-described shapes are exemplary in nature and unlimited. Mechanical minimum downramp stop 8, downramp 9, mechanical maximum downramp stop 10 of a given depth and design can be achieved by broaching, CNC or additive manufacturing, or other processes known in the art. (But without limitation) can be cut into the housing inner diameter or shaft outer surface. The principles of the present invention also apply to various types and shapes of external or internal corrugated tolerance rings and parts thereof, rotating in any direction without limitation. More preferably, the principles of FIGS. 11, 12 and 13 can be applied to all shapes, structures and materials of the tolerance ring without limitation.

  14, 15, and 16 show a portion of a cross-sectional view of a preferred embodiment 600 that utilizes the principles of the preferred embodiment 100 of the present invention. This principle is adapted to provide compression and torque slip from axial movement of the outer cylindrical part.

  More preferably, the preferred embodiment 600 can utilize the principles described above to provide a pre-calculated actively changing torque slip value range.

  FIG. 14 shows a part of an axial sectional view of the torque limiter. The external waveform tolerance ring 1, the external compression part 2c, the internal cylindrical part 3, the internal cylindrical part surface 3a, the shaft compression groove 4b, the housing driving force mF, the external compression part stop 10x, and the shaft holding groove 4c are shown.

  FIG. 14 shows a preferred embodiment 600 configured to provide zero torque slip in a normal condition. The axial compression groove 4b can be interlocked with one or more corrugations of the external corrugated tolerance ring 1, and when the external compression component 2c is moved by the housing motive power mF, the external compression component 2c, the internal cylindrical component 3 and the internal cylindrical component surface 3a Decrease the dimension between them and increase the compression and torque slip values.

  Thus, it is more preferable that the compression and torque slip values increase until the aforementioned external compression component 2c reaches the external compression component stop 10x (which reaches the maximum torque slip target value at this point). Next, it is more preferred that the preferred embodiment 600 functions as a torque limiter to provide a predetermined maximum torque slip value. It is more preferable that the torque slip value returns to zero because the shaft compression groove 4a has a side surface that releases itself and / or the housing driving force mF stops or becomes negative. The shaft holding groove can mechanically limit unnecessary axial movement of the external corrugated tolerance ring 1.

  FIG. 15 shows a part of an annular sectional view of the torque limiter. A portion of a cross-sectional view of the above-described embodiment 600 (consisting of an external corrugated tolerance ring 1, an external compression component 2c, an internal cylindrical component 3, an internal cylindrical component surface 3a, and an axial compression groove 4b) is shown.

  As the foregoing principles apply, the preferred embodiment 600 is understood to function within a predetermined torque slip value without limitation. More preferably, it is understood that the driving force mF can be generated from any power source without limitation.

  This embodiment can have a performance range similar to that of FIGS. It is also preferred that one skilled in the art understand that the preferred embodiment 600 can be adapted to function without limitation in any of the applied embodiments of the invention.

  More preferably, those skilled in the art will understand that the foregoing description is exemplary in nature and not limiting.

  FIG. 16 shows a part of an axial sectional view of the torque limiter. An angled external waveform tolerance ring 1b, an external compression component 2c, an internal cylindrical component 3, an internal cylindrical component surface 3a, a shaft pressure groove 4b, a housing driving force mF, an external compression component stop 10x, and a shaft holding groove 4c are shown.

  FIG. 16 illustrates a preferred embodiment 600 of a shape that provides a zero torque slip value in a normal condition. The shaft compression groove 4b can be interlocked with one or more corrugations of the external waveform tolerance ring 1b inclined at an angle. When the external compression component 2c is operated by the housing driving force mF, the dimension between the external compression component 2c, the internal cylindrical component 3, and the internal cylindrical component surface 3a is reduced, and the compression and torque slip values are increased.

  Therefore, it is more preferable that the compression and torque slip value increase until the aforementioned external compression component 2c reaches the external compression component stop 10x (at this point, the maximum torque slip target value is reached). Next, it is more preferred that the preferred embodiment 600 functions as a torque limiter to provide a predetermined maximum torque slip value. It is more preferable that the torque slip value returns to zero because the shaft compression groove 4a has a side surface that releases itself and / or the housing driving force mF stops or becomes negative. The shaft retaining groove can mechanically limit unwanted axial movement of the angled external corrugated tolerance ring 1.

  Those skilled in the art understand that the above-described shapes are exemplary in nature and unlimited. The axial compression groove 4b of a given depth and design can be cut into the housing inner diameter or shaft outer surface by broaching, CNC or additive manufacturing, or other processes known in the art (but not limited thereto). The principles of the present invention also apply to various types, shapes, and components of external or internal corrugated tolerance rings that rotate in any direction without limitation. More preferably, the principles of FIGS. 14, 15 and 16 can be applied to all shapes, structures and materials of the tolerance ring without limitation.

  17, 18, and 19 show a portion of a schematic diagram and two graphs relating to setting and using torque slip values of variable values in response to the angular acceleration bidirectional torque limiter, preferred embodiment 150 of the present invention.

  Further, FIG. 17 shows a bidirectional variant of the preferred embodiment 100, FIG. 14 (its function described above in detail).

  Introduce negative dynamic maximum down-ramp stop-10, negative down-ramp-9, minimum equilibrium point eq. As the foregoing principles apply, these are to be interpreted as corresponding components necessary for the function of the preferred embodiment 150 to provide bi-directional variable torque values in response to angular acceleration torque limiters.

  One corrugation of the external waveform tolerance ring 1, external cylindrical part 2, internal cylindrical part 3, internal cylindrical part surface 3 a, negative mechanical maximum down ramp stop-10, negative down ramp -9, minimum equilibrium point A partial schematic diagram of eq, downramp 9, mechanical maximum downramp stop 10, compression criteria 0-Y, and force Ft is shown.

  5A further relates to the symmetrical down-line bi-directional down-ramp side of down-ramp-9 and down-ramp 9 with respect to the clearance between the inner cylindrical part, the inner cylindrical part surface 3a, the inner cylindrical part 3 and the outer cylindrical part 2. FIG.

  FIG. 17 shows a part of a schematic diagram of one corrugation of a bi-directional variable external waveform tolerance ring in response to an angular acceleration torque limiter. FIG. 17 shows that the preferred embodiment 150 can provide a variable torque value in response to angular acceleration in both directions of rotation, such that the lowest value equilibrium point eq is relative rotation, so that the principles described above are applied. More preferably, it will be construed as explaining the state of zero. Further, the detailed discussion discussed above in FIGS. 14, 15, 16 applies. However, in the preferred embodiment 150, the force Ft and the associated rotational angular acceleration of the inner cylindrical part 3 are bidirectional.

  FIG. 18 shows a graph relating to the performance limit of the bidirectional variable due to the response to the angular acceleration torque limiter.

  Torque value standard 0-T, compression value standard 0-Y, negative mechanical maximum value stop-10, negative down ramp-9, minimum equilibrium point eq, down ramp 9, mechanical maximum value stop 10, rotational direction 11 is shown.

  With respect to FIG. 18, it is more preferred that the preferred embodiment 150 function in both directions of rotation and that the detailed discussion discussed above in FIGS. However, in the preferred embodiment 150, the force Ft and the associated rotational angular acceleration of the inner cylindrical part 3 are bidirectional. This event is explained by the following relationship: at -10 the force Ft is greater than or equal to F-10, at eq the force Ft is equal to Feq, and at the mechanical maximum downramp stop 10 the force Ft is greater than F10. Big or equivalent. These relative parameters are important to the performance of the torque limiting system for the reasons described herein.

  FIG. 19 shows a graph related to the set use torque value of the bidirectional variable according to the response to the angular acceleration torque limiter. The graph shown is directly related to FIG. Since the principle of the difference between the set torque slip value and the used torque slip value has been described in detail above, it is simply depicted in a graph.

  The graph of the setting torque slip value itv and the use torque slip value wtv (both are displayed with a line) is shown. These represent the set operating torque values associated with the preferred embodiment 150. Also, the difference between the setting and the long-term use torque slip value is about 25%. These relative parameters are important to the performance of the torque limiting system for reasons explained herein.

  It has been shown that the preferred embodiment 150 can provide very consistent and reliable variable values due to the response to the angular acceleration bidirectional torque limiter. Those skilled in the art understand that the above-described studies, shapes and descriptions are exemplary in nature and are not limiting.

  One skilled in the art understands that the aforementioned shape is exemplary in nature and is not limiting. Negative mechanical max stop -10, negative down ramp-9, minimum equilibrium point eq, down ramp 9, mechanical max stop 10 for a given depth and design are broaching, CNC or additive manufacturing, Other processes known in the art (but not limited to) can be cut into the housing inner diameter or shaft outer surface. The principles of the present invention also apply to various types, shapes, and components of external or internal corrugated tolerance rings that rotate in any direction without limitation. More preferably, the principles of FIGS. 17, 18 and 19 can be applied to all shapes, structures and materials of the tolerance ring without limitation.

  20, 21, 22, 23, 24 show a complete, partial or partial cross-sectional view of a circumferential variable value torque limiter 200 using a preferred embodiment 50 of the present invention.

  20, 21, 22, 23, 24 further illustrate a preferred embodiment 200 of the present invention, a torque limiting assembly when the inner circumference is adapted. This allows the compression / torque slip value of the preferred embodiment 50 to be adjusted to provide an adjustment of the associated travel torque for the requesting device.

  FIG. 20 shows a part of a complete annular cross-sectional view of a circumferential variable value angular torque limiter. External corrugated tolerance ring 1, external cylindrical part drive ring 2a, internal cylindrical part 3, internal cylindrical part surface 3a, one or more axial grooves 4a, external cylindrical drive ring 2b, internal cylindrical part 3, compression direction 11a, one It consists of the above holes 16, one or more screws 31, and one or more screw holes 31a.

  In FIG. 20, the fixed-value axial groove 4a is parallel to a predetermined depth and axial rotation of the design and is (but not limited to) broaching, CNC or additive manufacturing, other processes known in the art, It can be cut into the inner diameter of the outer cylindrical part drive ring 2a and is adapted to drive and engage one or more associated external corrugations of the outer corrugated tolerance ring 1. The outer cylindrical part drive ring 2a is in the form of a split ring having one or more pieces, provides a clamping force to the pieces, reduces the inner circumference of the outer cylindrical part drive ring 2a, and thereby adjusts one or more adjustment screws 31. It is more preferable that the diameter is reduced by the method.

  External cylindrical part drive ring 2a is flanged to external cylindrical drive ring 2b attached to one or more holes 16 with bolts (but not limited to) (not shown) differential limiters or industrial drive lines It is more preferable that the torque can be moved by other methods.

  FIG. 21 shows a part of an annular sectional view of the drive ring of the circumferential adjustment value torque limiter. In FIG. 21, an external cylindrical part drive ring 2a, an axial groove 4a (corresponding to one or more corrugations of the external waveform tolerance ring 1) (not shown), and an arrow in the compression direction 11a are shown.

  FIG. 22 shows a part of a sectional view of the drive ring of the circumferential adjustment value torque limiter. FIG. 22 shows an axial cross-sectional view of FIG. 2B1 along with an external cylindrical part drive ring 2a having one or more axial grooves 4a.

  FIG. 23 shows a part of an annular sectional view of the housing ring of the circumferential adjustment value torque limiter. In FIG. 23, the outer cylindrical drive ring 2b, the screw hole 31a, the adjusting screw 31, and one or more holes 16 are shown.

  FIG. 24 shows a part of an axial sectional view of the housing ring of the circumferential adjustment value torque limiter. FIG. 24 shows an axial cross section of the outer cylindrical part drive ring 2b and a screw hole 31a.

  More preferably, the embodiment 200 provides an adjusted torque slip value by changing the inner cylindrical diameter of the outer cylindrical part drive ring 2b and compression of the adjusting screw 31.

  More preferably, the axial groove 4a closely matches the contour and depth of the compression corrugation of the tolerance ring, but the thickness of the ring material utilized for the application is not limited. Thus, for example, a 0.020 inch (0.05 cm) material thickness ring can have a 0.020 inch deep groove and a 0.006 inch (0.015 cm) material thickness ring. Can have a groove depth of 0.006 inches. These relative dimensions are important to the performance of the torque limiting system for the reasons described herein. The axial grooves described above can be made by (but not limited to) CNC machining, additive manufacturing, molding, milling, or other processes known in the art, and FIGS. Any part of 22, 23, 24 can be used without limitation with metal, plastic, composite, or any material.

  More preferably, the preferred embodiment 200 of the present invention provides an accurate adjusted torque slip value that can compensate for different demands, changing situations or wear, and a very simple, inexpensive and reliable torque limiter.

  It is more preferred that those skilled in the art will interpret preferred embodiment 200 as configured above, or in conjunction with related embodiments of the present invention, to function with preferred embodiment 50. More preferably, embodiment 200 can be configured with a number of means including, but not limited to, an internal waveform tolerance ring (not shown) to apply the foregoing principles.

  One skilled in the art understands that the aforementioned shape is exemplary in nature and is not limiting. A constant value axial groove 4a of a predetermined depth and design is formed on the inner diameter of the outer cylindrical part drive ring 2a by broaching, CNC or additive manufacturing, and other processes known in the art (but not limited thereto). Can be cut. The principles of the present invention also apply to various types, shapes, and components of external or internal corrugated tolerance rings that rotate in any direction without limitation. More preferably, the principles of FIGS. 20, 21, 22, 23, 24 are applied without limitation to all shapes, structures and materials of the tolerance ring.

  FIGS. 25, 26, and 27 show a preferred embodiment 400 of the present invention, a taper brushing torque limiter, using a preferred embodiment 50 of the adjustment torque limiter.

  FIGS. 25, 26, and 27 are further known (known in the art) as taper brushing that can be configured to connect from a power source to a shaft, from a pulley to a shaft and / or other shapes, but not limited thereto. A type of compression type taper brushing is shown. In this taper brushing, there is a means for compressing to reduce the inside of the circumference diameter, or a means for enlarging to enlarge the outside of the circumference diameter (not shown), and a means for torque movement is more preferred. More preferably, taper brushing can be used in the present invention to accurately control compression so that torque slip can move torque. 25, 26 and 27 are examples, taper brushing with various means for expanding internal and external parts internally or externally, various types of equipment, and means for moving torque, so any type or shape More preferably, it is construed that it can be represented (without limitation).

  25, 26, and 27 more preferably show a portion of a cross-sectional view of an adjustment brushing that also functions as a torque slip assembly in accordance with a preferred embodiment 400 of the present invention.

  More preferably, adjustment brushing uses bolts, split rings, taper collars to provide compression of the internal compression ring, and further describes how compression is achieved and how torque is transferred.

  FIG. 25 shows a part of an annular sectional view of the taper, brushing, and torque limiter. The inner cylindrical part 3, the axial groove 4a, the divided taper thread housing 21, the housing slot 21a, the compression nut 34, the hole 16, and the outer corrugated tolerance ring 1 (not shown) are shown.

  FIG. 26 shows an orthogonal view of the housing of the taper / brushing / torque limiter. A split tapered thread housing 21, an inner cylindrical part 3, a housing slot 21 a, a tapered thread 36 and a hole 16 are shown.

  FIG. 27 shows a part of an axial sectional view of the housing of the taper / brushing / torque limiter. A compression nut 34, a lock nut 35, a taper thread 36, an external corrugated tolerance ring 1, an internal cylindrical part 3, an axial groove 4 a, a split taper housing 21, and a hole 16 are shown.

  In FIGS. 25, 26, and 27, it is more preferable that the divided taper housing 21 is compressed in the circumferential direction by the compression nut 34 to reduce the internal diameter. More preferably, the compression of the external waveform tolerance ring 1 is reduced or expanded by the compression nut 34 and the torque slip value is controlled. More preferably, the split taper housing 21 can move the torque slip from the inner cylindrical part 3 by shaft drive with the power source through the flange 12. This flange may have other shapes (without limitation) and can be attached to a differential or industrial driveline with bolts (without limitation) in one or more holes 16 or other devices or shapes.

  Those skilled in the art understand that this compression taper bushing is suitable for functioning (without limitation) in any application embodiment of the present invention.

  Those of ordinary skill in the art will better understand that the foregoing description is exemplary in nature and is not limiting. One skilled in the art understands that the aforementioned shape is exemplary in nature and is not limiting. The constant value axial groove 4a of a given depth and design can be cut into the housing inner diameter or shaft outer surface by broaching, CNC or additive manufacturing, and other processes known in the art (but not limited thereto). it can. The principles of the present invention also apply to various types, shapes, and components of external or internal corrugated tolerance rings that rotate in any direction without limitation. More preferably, the principles of FIGS. 25, 26 and 27 can be applied to all shapes, structures and materials of the tolerance ring without limitation.

  More preferably, the preferred embodiment 400 of the present invention provides an accurate adjusted torque slip value that can compensate for changing requirements, circumstances or wear, and a very simple, inexpensive and reliable torque limiter.

  28, 29, and 30 show sectional views of the active variable torque limiter. A preferred embodiment 500 using a variant of the preferred embodiment 400, a fixed value torque limiter preferred embodiment 5. These embodiments provide an active system applied to a number of industrial and automotive devices, including differential limiting devices.

  FIG. 28 shows a cross-sectional view of the active variable torque limiter. Inner cylindrical part 3, axial groove 4a, split tapered smooth housing 21s, housing slot 21a, compression bearing 22, actuator arm 24, actuator 25, actuator arm pivot 26, external corrugated tolerance ring 1 (not shown) Yes.

  FIG. 29 shows an orthogonal view of the active variable torque limiter. A split tapered smooth housing 21s, a housing slot 21a, an inner cylindrical part 3 and a hole 16 are shown.

  FIG. 30 is a sectional view of the active variable torque limiter. Actuator 25, Actuator piston 25a, Actuator force aF, Compression bearing 22, Actuator arm 24, Actuator arm pivot 26, Internal cylindrical part 3, External corrugated tolerance ring 1, Compression collar 32, Belleville washer group 23, Space collar 18, Divided taper -The smooth housing 21s is shown.

  28, 29 and 30, the preferred embodiment 500 provides a predetermined friction torque value in a normal situation. It is more preferable that the hydraulic pump or other device (not shown) generates the actuator force aF by a signal from the ECU or the machine operating device when it is necessary to increase the friction torque or an unnecessary rotation difference is detected. . Actuator piston 25a is actuated by actuator force aF to actuate actuator arc 24 (turning actuator arm pivot 26), actuate compression collar 32 (similar to a car clutch disengagement bearing) and split taper. Operate the compression bearing 22 (with a tapered inner surface that releases itself against the tapered outer surface of the smooth housing 21s) to reduce the inner circumferential diameter of the split tapered housing 21s. This increases the compression of the external waveform tolerance ring 1. When the actuator force aF stops, the Bellville washer group 23 provides force against the self-releasing taper of the compression collar 32 and the preferred embodiment 500 returns to the predetermined friction torque. This embodiment can have performance limits similar to those of FIGS. 14, 15, and 16, and can be lubricated without limitation in a manner known in the art.

  Further, the preferred embodiment 500 provides a pre-calculated range of active torque slip variable values when the appropriate shape provides an active differential limiter, such that the principles described above are applied. More preferably, the active system has means for providing the actuator force aF without restriction.

  Moreover, it is more preferable if electric power can be provided to land vehicles without restriction. Furthermore, it is more preferable for those skilled in the art to understand that the preferred embodiment 500 can adapt the functions of the application embodiments of the present invention without limitation.

  One skilled in the art understands that the above-described configurations are exemplary in nature and are not limiting. The constant value axial groove 4a of a given depth and design can be cut into the housing inner diameter or shaft outer surface by broaching, CNC or additive manufacturing, and other processes known in the art (but not limited thereto). it can. The principles of the present invention also apply to various types, shapes, and components of external or internal corrugated tolerance rings that rotate in any direction without limitation. More preferably, the principles of FIGS. 28, 29 and 30 can be applied to all shapes, structures and materials of the tolerance ring without limitation.

FIG. 31 shows a block diagram of the active variable torque limiter function of FIGS.
1. 1. Detecting an increase in unnecessary radial speed rotation difference 2. Send a signal from the sensor to the actuator. 3. Actuator generates actuator force to move the actuator arm Actuate the actuator to move the compression collar against the tapered outer surface of the split taper smooth housing to reduce the inner circumferential diameter of the split taper housing
5. 5. Reduce the inner circumferential diameter of the split taper housing to increase the compression on the corrugated tolerance ring. Increase compression on the aforementioned waveform tolerance ring to increase at least one torque limit of the torque limit system

  FIGS. 32, 33 and 34 show three graphs relating to the relationship between tolerance ring height, compression, ring stiffness, and sensitivity to wear. Here, tr1, tr2, and tr3 represent the set torque slip values of the external waveform tolerance ring.

  FIG. 32 shows a graph relating the relationship of tolerance ring height, compression, ring stiffness, and sensitivity to wear. Two lines tr1 and tr2 are shown. Here, tr1 and tr2 are external corrugated tolerance rings with an uncompressed corrugation height of 0.050 inch (0.127 cm) and are located in similar devices with different diameter clearances. In the relevant test situation, tr1 yields 100 ft-lbs (30 m) at 10% or 0.005 inch (0.013 cm) compression and tr2 yields 50 ft-lbs at 10% or 0.005 inch (0.013 cm) compression. (15m) is produced. Therefore, tr1 is considered to be twice as stiff as tr2. Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  If tr1 produces a torque slip value of 50 ft-lbs (15 m) (0.0025 inch compression or 0.0064 cm compression) when tr1 is installed in the device, it is considered to be near the upper limit of elasticity. In that case, 0.001 inch (0.0025 cm) wear results in a loss of torque slip value of 40% (tr1 delta = (50-30) / 50 × 100 = 40%). Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  A wear of 0.001 inch (0.0025 cm) will result if a torque clearance value of 50 ft-lbs (15 m) (0.005 inch compression or 0.0127 cm compression) diameter clearance is produced when tr2 is installed in the device. This results in a 20% loss in torque slip value (tr2 delta = (50−40) / 50 × 100 = 20%). Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  In this example, with the same amount of wear (0.001 inch or 0.0025 cm), tr1 torque slip results in twice the loss compared to tr2. Therefore, it is preferable to select a tolerance ring in which the mounted torque slip value is at or near the upper limit of elasticity.

  FIG. 33 shows a graph of the relationship between tolerance ring height, compression, ring stiffness, and agility to wear. A graph of two lines, tr2 and tr3, is shown. Here, tr2 is an external waveform tolerance ring with an uncompressed corrugation height of 0.050 inch (0.127 cm), and tr3 is an external with an uncompressed corrugation height of 0.100 inch (0.254 cm). It is a waveform tolerance ring. They are similar devices but differ in diameter clearance. These relative parameters are important to the performance of the torque limiting system for the reasons described herein.

  The tr2 related test yields 50 ft-lbs (15 m) at 10% or 0.005 inch (0.0127 cm) compression, and tr3 produces 50 ft-lbs (15 m) at 10% or 0.010 inch (0.0254 cm) compression. Produced. A wear of 0.001 inch (0.0025 cm) will result if a torque clearance value of 50 ft-lbs (15 m) (0.0025 inch compression or 0.0064 cm compression) is produced when tr2 is installed in the device. This results in a 20% loss in torque slip value (tr2 delta = (50−40) / 50 × 100 = 20%). A wear of 0.001 inch (0.0025 cm) is torque when a torque clearance value of 50 ft-lbs (15 m) (0.010 inch or 0.0254 cm compression) is produced when tr3 is installed in the device. This results in a 10% loss in the slip value (tr3 delta = (50−45) / 50 × 100 = 10%). In this example, a torque slip of tr2 with the same amount of wear (0.001 inch or 0.0025 cm) results in twice the loss compared to tr3. Therefore, it is preferable to select a tolerance ring with the highest possible corrugation. Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  FIG. 34 shows a graph of the relationship between tolerance ring height, compression, ring stiffness, and agility to wear. A graph of two lines, tr1 and tr3, is shown. Here, tr1 is an external waveform tolerance ring with an uncompressed corrugation height of 0.050 inch (0.127 cm) and tr3 is an external waveform tolerance with an uncompressed corrugation height of 0.100 inch (0.254 cm). It is a ring. They are similar devices but differ in diameter clearance. In this example, the ring tr1 in FIG. 1A is compared with the ring tr3 in FIG. 1B. Here, tr1 yields 100 ft-lbs (30 m) at 10% or 0.005 inch (0.013 cm) compression and tr3 50 ft-lbs (15 m) at 10% or 0.010 inch (0.0254 cm) compression. Produce. Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  If tr1 produces a torque slip value of 50 ft-lbs (15 m) (0.0025 inch compression or 0.0064 cm compression) when tr1 is installed in the device, it is considered to be near the upper limit of elasticity. In that case, 0.001 inch (0.0025 cm) wear results in a loss of torque slip value of 40% (tr1 delta = (50-30) / 50 × 100 = 40%). Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  A wear of 0.001 inch (0.0025 cm) is torque when a torque clearance value of 50 ft-lbs (15 m) (0.010 inch or 0.0254 cm compression) is produced when tr3 is installed in the device. This results in a 10% loss in the slip value (tr3 delta = (50−45) / 50 × 100 = 10%). In this example, a torque slip of tr1 with the same amount of wear (0.001 inch or 0.0025 cm) results in a four-fold loss compared to tr3. Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  Thus, the beneficial effect of Examples 1 and 2 is an additive. The torque slip value mounted on the tolerance ring is preferably the upper limit value of elasticity or a value close thereto, and the height of the corrugation of the tolerance ring is preferably as high as possible.

  Thus, these results indicate the criticality and relative dimensions of the torque limiting system shape for the reasons described herein.

  FIG. 35 shows a portion of an annular cross-sectional view of a differential limiting device in response to an angular acceleration internal friction device with variable values.

  FIG. 35 shows a preferred embodiment 300 of the present invention, a differential limiting device using the preferred embodiment 100 as a friction device inside the differential. In particular, this embodiment provides a differential limiting device that is efficient and inexpensive and requires only a small addition in size, complexity, cost, or weight.

  The preferred embodiment 300 can be applied to many types of devices and automobiles, including associated front-wheel drive differentials, front-wheel drive center differentials, rear-wheel drive rear accelerators, or any land vehicle associated without limitation. Can be placed anywhere.

  The preferred embodiment 100 functionality is described in detail in FIGS. 8, 9, 10, 11, 12, 13, 14, 15, 16 described above. It also provides a predetermined invariable minimum torque slip value in normal road conditions, allowing easy rotation differences. When the traction force is lost, the torque slip value is increased during the angular acceleration, and the torque slip value is increased to provide power to the automobile. As angular acceleration continues, it produces a fixed maximum torque slip value. When the torque slip value is decreased, the angular acceleration stops or becomes negative, so that it returns to the invariable minimum torque slip value and the fixed invariant minimum torque slip value proceeds in the opposite direction. All of these limit unnecessary rotation differences under adverse conditions and provide traction.

  FIG. 35 further shows a portion of a cross-sectional view of the differential limiting device automobile differential. More preferably, the differential housing 47 is securely attached to the accelerator or transaxle housing (not shown), but is also attached to the automobile. Differential housing 47 is prime mover, drive train (not shown), primary bearing 56, side bearing cap (not shown), secondary bearing 57, side bearing cap (not shown), external waveform tolerance ring More preferably, it is configured to rotate in response to the rotational torque received from the mechanical minimum downramp stop 8, downramp 9, and mechanical maximum downramp stop 10.

  More preferably, the primary gear 48 is disposed in the differential housing 47, the primary gear 48 is rotationally fixed to the primary output shaft 50, and the secondary gear 49 is disposed in the differential housing 47. . More preferably, the secondary gear 49 is rotated and fixed to the secondary output shaft 51, and one or more differential pinion gears 52 on the pinion shaft 54 are safely fixed to the differential housing 47. preferable. More preferably, the above-described pinion gear is arranged between the primary side gear 48 and the secondary side gear 49 to enable a difference in rotation.

  More preferably, the primary gear 48 and the secondary gear 49 are shaped so as to hold a friction region with an increased circumferential diameter, a primary gear friction region 48a, and a secondary gear friction region 49a. As is known in the art, the increased circumferential diameter and region provides increased torque slip due to reduced wear due to the larger pressure region.

  More preferably, one or more external corrugated tolerance rings 1 are arranged in each friction region between the primary gear 48, the secondary gear 49 and the differential housing 47. Therefore, the external waveform tolerance ring 1 is disposed between the circumference of the primary side gear 48 and the differential housing 47, and the other external waveform tolerance ring 1 is located near the circumference of the secondary side gear 49. Between the differential housings 47.

  More preferably, the preferred embodiment 300 is directly related to the preferred embodiment 100 of the present invention. It is also preferred that it is understood that the preferred embodiment 300 can be adapted to function without limitation the application embodiments of the present invention.

  One skilled in the art understands that the aforementioned shape is exemplary in nature and is not limiting. The preferred embodiment 100 described above holds a mechanical minimum downramp stop 8, downramp 9, mechanical maximum downramp stop 10 of a predetermined depth and design, broaching, CNC or additive manufacturing, Other processes known in the art (but without limitation) can be cut into the housing inner diameter or shaft outer surface. The principles of the present invention also apply to various types, shapes, and components of external or internal corrugated tolerance rings that rotate in any direction without limitation. Further, it is more preferable that power transmission can be provided to land vehicles without limitation.

  Those of ordinary skill in the art will appreciate that the foregoing description is exemplary in nature and does not limit the scope of the invention in any way.

List of elements

40 Preferred Embodiment 40
Fixed value torque limiter
Screw, key, pin, stop
Unused 50 preferred embodiment 50
Fixed Value Torque Limiter 100 Preferred Embodiment 100
One Variable Value Torque Limiter 150 Preferred Embodiment 150
Two Variable Value Torque Limiter 200 Preferred Embodiment 200
E-ring (50,
100 and 150)
300 Preferred Embodiment 300
LSD (100)
400 Preferred Embodiment 400
Tapered bushing (50)
500 Preferred Embodiment 500
Active (50)
600 Preferred Embodiment 600
Active (synchronized with axis)
DESCRIPTION OF SYMBOLS 1 External waveform tolerance ring 1n Internal waveform tolerance ring 1a Spherical external waveform tolerance ring 1b Angle external waveform tolerance ring 2 External cylindrical component 2a External cylindrical component drive ring 2b Housing ring 2c External compression component 3 Internal cylindrical component 3a Internal cylindrical component surface 4a Constant Value axial groove 4b Fixed value axial lamp 4c Shaft holding groove 8 Mechanical minimum value Down lamp / stop-8 Negative minimum value down lamp / stop 8itv Set torque value 8wtv Operating torque value 9 Down lamp-9 Negative down lamp 9itv set torque value 9wtv use torque value 10 mechanical maximum value down ramp stop-10 negative maximum value down ramp stop 10itv set torque value 10wtv use torque value 10a housing corrugation stop 10b housing 11 Rolling direction 11a Compressive force direction arrow 11b Actuator force 16 Hole 17 Corrugation stop 18 Spacer collar 21 Divided taper thread housing 21a Housing slot 21s Divided taper smooth housing 22 Compression bearing 23 Belleville washer group 24 Actuator arm 25 Actuator 25a Actuator piston 26 Actuator arm pivot 31 Adjustment screw 31a Screw hole 32 Compression collar 34 Compression nut 35 Lock nut 36 Taper thread 47 Differential housing 48 Primary gear 48a Primary gear friction area 49 Secondary gear 49a Secondary gear friction region 50 Primary output shaft 51 Secondary output shaft 52 Differential pinio Gear 54 Pinion shaft 56 Side bearing 57 Side bearing eq Minimum equilibrium point itv Setting torque value wtv Operating torque value OT Torque value reference OY Compression value reference rx1k Reference 8itv Dynamic minimum value Downramp setting torque value 8wtv Dynamic Minimum value for ramp down use torque value 9itv Down ramp set torque value 9wtv Use down ramp torque value 10itv Maximum dynamic value Down ramp set torque value 10wtv Maximum dynamic value Down ramp set torque value Ft Tangent force tr1 Tolerance ring 1 (FIG. 6)
tr2 Tolerance ring 2 (Fig. 6)
tr3 Tolerance ring 3 (Fig. 6)

Claims (20)

A torque limiting assembly comprising:
A central element defined by a circular cross section and an outer wall,
An intermediate ring element surrounding the central element within a central hole formed therein, the intermediate ring element being defined by a generally circular cross section, an inner wall, and an outer wall;
An outer element surrounding an intermediate ring element within a generally circular hole formed therein, wherein the hole is defined by an inner wall, and the outer element is further defined by an outer wall;
The central element, the intermediate ring element and the outer element are a matched set selected from a group defined by an inner spline set and an outer spline set;
The internal spline set is
A central element outer wall defined by a plurality of flutes spaced apart near the periphery,
An intermediate element inner wall defined by a plurality of domes projecting therefrom, wherein the dome is configured to be in a longitudinal groove in the central element outer wall, and an outer element defined by a smooth surface Including inner walls,
The external spline set is
A central element outer wall defined by a smooth surface;
An intermediate element outer wall defined by a plurality of domes projecting therefrom at spaced intervals near the periphery, and an outer element defined by a plurality of flutes configured therein such that said dome projecting from the intermediate element outer wall is present Including inner walls,
Torque limiting assembly. At least one said longitudinal groove is
First and second longitudinal sidewalls extending from opposite ends of the groove and ending with first and second stop portions, defining first and second relatively unequal heights; A second longitudinal side wall,
An uppermost wall extending between the first stop portion and the second stop portion,
The torque limiting assembly according to claim 1, wherein: At least one said longitudinal groove is
First and second longitudinal sidewalls extending from opposite ends of the groove and ending with first and second stop portions;
A top wall extending from between the first stop portion and the second stop portion, wherein the top wall defines a generally arcuate shape, wherein it is defined by the top wall. The midpoint includes a top wall defining a distance further from a line interconnecting opposite ends in at least one of the side walls than the distance between the stop portion and the end,
The torque limiting assembly according to claim 1, wherein: 4. The torque limiting assembly of claim 3, wherein the top wall is defined by flat ramp portions extending from each of the stop portions, the ramp portions intersecting each other at an intermediate point. . The outer element further includes at least one longitudinal gap defining a width extending from between the inner and outer walls;
The torque limiting assembly further includes a gap adjustment structure for changing the width of each gap.
The torque limiting assembly according to claim 2, wherein: The gap adjustment structure
An encapsulating ring surrounding the external element and one or more adjusting screws, each threadedly engaged with a threaded hole formed in the encapsulating ring, thereby reducing or allowing the gap width to be responsive Including one or more adjusting screws, rotatable to add or reduce compressive force at the external element to expand,
6. A torque limiting assembly according to claim 5, wherein: The gap adjustment structure
Said outer element defining a longitudinally oriented conical outer wall further defined by threads formed therein;
One or more screw nuts that engage the outer wall thread, whereby at least one rotation of the screw nut adds or reduces compressive force to the outer wall, reducing or expanding the gap width for application Including one or more screw nuts,
6. A torque limiting assembly according to claim 5, wherein: The gap adjustment structure
An outer element defining a longitudinally oriented conical outer wall,
One or more colorings that mesh with the outer wall of the outer element, and one or more colorings along the longitudinal direction of the conical outer wall with respect to the outer wall to reduce or enlarge the gap width in a responsive manner An actuator arm configured to urge the compression force to be added or reduced,
6. A torque limiting assembly according to claim 5, wherein: The torque limiting assembly according to claim 1, wherein the inner wall of the outer element defines a surface inclined along the transverse direction, the transverse direction being oriented perpendicular to the longitudinal direction. 10. The torque limiting assembly of claim 9, wherein the dome defines an elongated shape oriented along the transverse direction. A differential assembly comprising:
A rotatable input shaft assembly,
A first rotatable output shaft assembly mechanically connected to the input shaft assembly, whereby rotation of the input shaft assembly is a first rotatable force at the first output shaft assembly. A first rotatable output shaft assembly,
A second rotatable output shaft assembly mechanically connected to the input shaft assembly, whereby rotation of the input shaft assembly is a second rotatable force at the second output shaft assembly. A second rotatable output shaft assembly,
A first torque control element associated with the first output shaft assembly that provides a force against the first rotatable force in response to the rotational speed of the first output shaft assembly. A second torque control element associated with the first torque control element and the second output shaft assembly, wherein the first torque control element is responsive to the rotational speed of the second output shaft assembly; A second torque control element configured to impart a force against the two rotatable forces;
Differential assembly. Each of the first and second rotatable output shaft assemblies includes:
A central element defined by a circular cross section and an outer wall and an intermediate ring element surrounding the central element within a central hole formed therein, usually defined by a circular cross section, an inner wall and an outer wall Defining an intermediate ring element,
The differential assembly further includes a housing element mechanically connected to the input shaft, the housing element surrounding the intermediate ring elements of both output shaft assemblies, each of which is generally circular formed by the housing elements. In the hole, which is defined by the inner wall,
Wherein the central element, the intermediate ring element, and the housing element are a matched set selected from a group defined by an inner spline set and an outer spline set;
Internal spline set
A central element outer wall defined by a plurality of flutes spaced apart near the periphery,
An intermediate element inner wall defined by a plurality of elongate domes protruding therefrom, wherein the dome is configured to reside in a longitudinal groove in the central element outer wall, and a housing defined by a smooth surface Including element inner walls,
External spline set
A central element outer wall defined by a smooth surface;
An intermediate element outer wall defined by a plurality of elongate domes projecting therefrom at spaced intervals near the periphery, and a plurality of flutes configured to have the elongate dome protruding from the intermediate element outer wall therein Including an inner wall of the housing element,
The differential assembly according to claim 11, wherein: Each of the first and second rotatable output shaft assemblies includes:
A central element mechanically connected to the input shaft assembly, the central element being defined by a circular cross section and an outer wall;
An intermediate ring element surrounding the central element within a central hole formed therein, the intermediate ring element being defined by a generally circular cross section, an inner wall and an outer wall;
Defining an outer element surrounding an intermediate ring element within a generally circular hole formed therein, wherein the hole is defined by an inner wall and the outer element is further defined by an outer wall. ,
The central element, the intermediate ring element and the outer element are a matched set selected from a group defined by an inner spline set and an outer spline set;
Internal spline set
A central element outer wall defined by a plurality of flutes spaced apart near the periphery,
An intermediate element inner wall defined by a plurality of elongate domes protruding therefrom, wherein the dome is configured to reside in a longitudinal groove in the central element outer wall, and an exterior defined by a smooth surface Including element inner walls,
External spline set
A central element outer wall defined by a smooth surface;
An intermediate element outer wall defined by a plurality of elongate domes projecting therefrom at spaced intervals near the periphery, and a plurality of flutes configured to have the elongate dome protruding from the intermediate element outer wall therein Including the inner wall of the external element,
The differential assembly according to claim 11, wherein: An improved torque ring assembly comprising:
A central element defined by the outer wall,
An intermediate ring element surrounding the central element within a central hole formed therein, the intermediate ring element defined by an inner wall and an outer wall;
An outer element surrounding an intermediate ring element therein within a hole formed therein, wherein the hole is defined by an inner wall, and the outer element is further defined by an outer wall;

The central element, the intermediate ring element and the outer element are an alignment set selected from the group defined by an inner grooved set and an outer grooved set;
Inside grooved set
A central element outer wall defined by a plurality of flutes spaced apart near the periphery,
An intermediate element inner wall defined by a plurality of domes projecting therefrom, wherein the dome is configured to be present in a longitudinal groove in the outer wall of the central element and is further defined by a cross-section typically in the form of a teardrop An inner element inner wall, and an inner element inner wall defined by a smooth surface,
The outer grooved set
A central element outer wall defined by a smooth surface;
An intermediate element outer wall defined by a plurality of domes projecting therefrom at spaced intervals near the periphery, wherein the dome is further defined by a cross-section generally in the form of a teardrop; and
An outer element inner wall defined by a plurality of flutes configured to have the dome projecting from an intermediate element outer wall therein,
Improved torque ring assembly. The improved torque ring assembly of claim 14, wherein the inner wall of the outer element defines a surface that is inclined along a transverse direction, the transverse direction being oriented perpendicular to the longitudinal direction. The improved torque ring assembly of claim 15, wherein the dome defines an elongated shape oriented along the transverse direction. At least one longitudinal groove
First and second longitudinal sidewalls extending from opposite ends of the groove and ending with first and second stop portions, defining first and second relatively unequal heights; A second longitudinal side wall,
An uppermost wall extending between the first stop portion and the second stop portion,
Wherein the outer element further includes at least one longitudinal gap defining a width extending from between the inner wall and the outer wall;
The torque ring assembly further includes a gap adjustment structure for changing a width of each gap.
The improved torque ring assembly according to claim 14, wherein: The gap adjustment structure
An encapsulating ring surrounding the external element and one or more adjusting screws, each threadedly engaged with a threaded hole formed in the encapsulating ring, thereby reducing or allowing the gap width to be responsive Including one or more adjusting screws, rotatable to add or reduce compressive force at the external element to expand,
The improved torque ring assembly of claim 17, wherein: The gap adjustment structure
Said outer element defining a longitudinally oriented conical outer wall further defined by threads formed therein;
One or more screw nuts that engage the outer wall thread, whereby at least one rotation of the screw nut adds or reduces compressive force to the outer wall, reducing or expanding the gap width for application Including one or more screw nuts,
The improved torque ring assembly of claim 17, wherein: The gap adjustment structure
Said outer element defining a longitudinally oriented conical outer wall;
One or more colorings that mesh with the outer wall of the outer element, and one or more colorings along the longitudinal direction of the conical outer wall with respect to the outer wall to reduce or enlarge the gap width in a responsive manner An actuator element configured to encourage the compression force to be added or reduced,
The improved torque ring assembly of claim 17, wherein: