Axial flow motor and displacement device for axial flow motor

Abstract

The present invention relates to an axial-flow motor (1) comprising: a stator (2); a first rotor body (31) disposed on a rotor shaft (3); a second rotor body (32) disposed on the rotor shaft (3); and a shifting device (4) disposed between and connected to the two rotor bodies (31, 32). According to the invention, the shifting device (4) comprises at least one spring device (40) acting on the first rotor body (31) and the second rotor body (32) to resist the magnetic attraction force (F_magnet) between the rotor bodies (31; 32) and the stator (2), wherein the spring device (40) is configured such that a spring force characteristic curve (K_spring force) higher than the magnetic force characteristic curve (K_magnetic force) is formed throughout the shifting path (V).

Description

Technical Field

[0001] This invention relates to an axial-flow motor, comprising: a stator; a first rotor body disposed on a rotor shaft; a second rotor body disposed on the rotor shaft; and a shifting device disposed between and connected to the two rotor bodies, wherein one of the two rotor bodies is disposed at an axial distance on one axial side of the stator to form a first air gap, and wherein the other rotor body is disposed at an axial distance on another axial side of the stator to form a second air gap, and wherein the axial distance between the rotor bodies axially disposed on the two sides and the stator can be changed along a shifting path by means of the shifting device according to the torque occurring between the rotor shaft and the rotor body. Furthermore, this invention also relates to a shifting device for an axial-flow motor. Background Technology

[0002] Axial flow motors are already well known in existing technology.

[0003] An axial-flow motor having a stator and a rotor is known in EP 2 985 893 A1, wherein the stator comprises at least two stator sections, and wherein the rotor is connected to a rotor shaft, wherein the rotor and / or the rotor shaft is rotatably mounted in bearings, and wherein the stator sections are arranged immovably relative to the bearings along the direction of rotor rotation. At least one stator section is arranged to be movable relative to the bearings in an axial or radial direction to adjust the width of the air gap between the rotor and the stator section. Summary of the Invention

[0004] The purpose of this invention is to provide an axial-flow motor with improved torque-related magnetic field amplification, and a shifting device for the axial-flow motor with improved torque-related magnetic field amplification effect.

[0005] The axial-flow motor according to the invention includes: a stator; a first rotor body disposed on a rotor shaft; a second rotor body disposed on the rotor shaft; and a shifting device disposed between and connected to the two rotor bodies. One of the two rotor bodies is disposed on one axial side of the stator at a certain axial distance, thereby forming a first air gap, and the other rotor body is disposed on another axial side at a certain axial distance, thereby forming a second air gap. By means of the shifting device, the axial distance between the rotor bodies axially disposed on the two sides and the stator can be changed along the shifting path according to the torque occurring between the rotor shaft and the rotor bodies, wherein, along the shifting path, the magnetic attraction between the corresponding rotor body and the stator maps a magnetic force characteristic curve. According to the invention, the shifting device includes at least one spring device acting on the first and second rotor bodies to resist the magnetic attraction between the rotor bodies and the stator, wherein the spring device is configured such that a spring force characteristic curve is formed that is higher than the magnetic force characteristic curve throughout the shifting path. Axial-flow motors are preferably designed as permanently excited synchronous machines used in drives for powering pneumatic motor vehicles. An advantage achieved by the design according to the invention is that it provides an axial-flow motor in which torque-related magnetic field enhancement is achieved using a structurally simple device. Another advantage of this design is that the enormous magnetic force that must be supported by external bearings in such a motor variant is greatly reduced by internal force support. This means that external storage can be designed with less expense (the warehouse can be smaller).

[0006] First, the various elements of the subject matter claimed in this invention will be described in the order in which they are mentioned in the group of claims, and then particularly preferred embodiments of the subject matter of this invention will be described.

[0007] In axial-flow electric motors (AFM), such as those in motor vehicles designed as axial-flow motors, the magnetic flux is axially directed in the direction of rotor rotation within the air gap between the stator and rotor. Different types of axial-flow motors exist. One known type is the so-called I-type arrangement, in which the rotors are axially arranged close to or between the two stators. Another known type is the so-called H-type arrangement, in which the two rotors are arranged on opposite axial sides of the stator.

[0008] The stator of an axial-flow motor has a stator body with multiple stator windings arranged circumferentially. Observed circumferentially, the stator body can be formed as a single piece or in segments. The stator body can be formed from a stator lamination core having multiple laminated plates. Alternatively, the stator body can also be formed from a compressed soft magnetic material, such as so-called SMC (soft magnetic compound) material.

[0009] The rotor shaft is the shaft of the motor that is rotatably mounted, to which the rotor or rotor body is non-rotatably connected.

[0010] The rotor of an axial-flow motor can be designed, at least partially, as a stacked rotor. A stacked rotor is designed to be layered along the axial direction. The axial magnetic flux must overcome the adhesive or insulating layers between the stacked individual plates, which causes the magnetic circuit to experience shear (additional air gaps) and results in efficiency loss. Alternatively, the rotor of an axial-flow motor can also have a rotor carrier, which is correspondingly equipped with magnetic plates and / or SMC material and magnetic elements designed as permanent magnets.

[0011] Advantageous embodiments of the invention are described in detail in the dependent claims. Features listed individually in the dependent claims may be combined with each other in a technically meaningful manner and may define other embodiments of the invention. Furthermore, the features indicated in the claims are described and explained in more detail in the specification, in which other preferred embodiments of the invention are shown.

[0012] According to an advantageous embodiment of the invention, the spring device can be configured to include a first spring element and a second spring element, wherein the first spring element is designed as a leaf spring assembly and the second spring element is designed as a leaf spring. Therefore, a space-saving construction can be achieved advantageously.

[0013] According to another preferred further development of the invention, the first spring element and the second spring element can also be mechanically arranged in series and act in parallel such that, in the first displacement path segment, both the first spring element and the second spring element are at least partially but not completely compressed, and the first spring element remains fully compressed in the subsequent second displacement path segment. The advantage of this configuration is that it can produce a spring force characteristic curve that counteracts the magnetic attraction between the rotor and stator, thereby ensuring sufficient force to counteract the magnetic attraction throughout the displacement path.

[0014] Furthermore, according to the same advantageous embodiment of the invention, the shifting device may include the following:

[0015] - A spring device having a centrally arranged spring support member, visible along the axial range of the displacement device, supporting at least one first spring element on each axial side.

[0016] - Second spring elements, each axially located on two sides, act in parallel with the first spring element.

[0017] - First displacement elements, each axially located on two sides, are designed as supports for a first rotor body and a second rotor body, wherein the first displacement elements are arranged on a rotor shaft in a manner that allows axial displacement and limited rotation, while the rotor shaft is not arranged in a manner that allows axial displacement.

[0018] - Second displacement elements are axially located on two sides, and the second displacement elements are connected to the rotor shaft in a rotationally fixed and non-displaceable manner and cooperate with the corresponding first displacement elements.

[0019] Each first displacement element is axially supported against a first spring element and a second spring element, and at least one rolling element is arranged between the first and second displacement elements. The first displacement element has a first ramp element on its side facing the second displacement element, and the second displacement element has a second ramp element on its side facing the first displacement element. The first and second ramp elements are designed such that if the first displacement element rotates relative to the second displacement element, or if the second displacement element rotates relative to the first displacement element, the rotor body is axially displaced relative to the rotor shaft. The advantageous effect of this configuration is particularly due to its space-saving construction.

[0020] According to another particularly preferred embodiment of the invention, the first spring element can be designed to map a linear spring force characteristic curve and / or the second spring element can be designed to map a progressive spring force characteristic curve. Therefore, a characteristic curve that closely approximates the magnetic force characteristic curve can be generated using simple design methods, thereby avoiding excessive distance from the magnetic force characteristic curve throughout the displacement path. Correspondingly, approximating the magnetic force characteristic curve will result in a more complex and stable displacement device.

[0021] Furthermore, the invention can be further developed such that the shifting device is arranged in a floating manner on the rotor shaft, and the two rotor bodies are supported by each other via the shifting device. This avoids the need for support via additional bearings and makes further simplification of the construction possible.

[0022] In another preferred embodiment of the invention, the spring device may also be designed to map a spring force characteristic curve that is less than the function described below: F_magnet_limit = F_magnet + F_magnet_max * 0.3 over the entire displacement path. The value of F_magnet_max * 0.3 is particularly preferably in the range of up to 4000 N, especially in the range of 2500 N to 3500 N, and particularly around 3000 N. The distance from the magnetic force characteristic curve is not too large, and the construction does not correspondingly become more complex.

[0023] It is also advantageous to further develop the invention in the following manner: a stop device is provided between the first and second shifting elements, these stop devices being designed such that, under operating conditions where the torque between the rotor shaft and the rotor body exceeds a predetermined maximum shifting torque, the torque generated is transmitted via the stop device rather than via the corresponding first and second ramp devices of the first and second shifting elements. The advantage of this approach is that it prevents increased wear on the shifting elements and reliably transmits the maximum torque to the rotor shaft.

[0024] In another preferred embodiment of the invention, the first rotor body and the second rotor body can be rotatably coupled to each other such that there is no relative rotation between the first rotor body and the second rotor body during operation of the axial flow motor. Specifically, the frictional connection between the two rotor bodies is achieved via a displacement device arranged between the first rotor body and the second rotor body. In this way, the axial flow motor can always operate under optimal operating conditions. Furthermore, simple and cost-effective solutions have been found for connecting the rotor bodies on two sides. Alternatively, the rotational coupling can also be achieved via a form-fit connection—for example, by a connecting pin extending axially between the two rotor bodies.

[0025] Finally, the invention can also be implemented advantageously by providing a spring bearing ring between the first spring element and the second spring element, in each case. This is preferably designed so that torque can be transmitted between the first displacement element of the first rotor and the first displacement element of the second rotor solely by means of a frictional connection. In particular, when the installation space is limited, the spring bearing ring achieves optimal utilization of the leaf spring characteristics in terms of the required force (force-displacement characteristics).

[0026] At the start of the spring assembly's displacement, the leaf spring assemblies are used for a prolonged but almost constant increase on both sides. These leaf spring assemblies are self-limiting beyond a certain distance because they are compressed into a block. These leaf spring assemblies prevent overload through self-limitation. For the leaf springs to be able to connect to the same support component from both sides, these leaf springs must have identical geometry (distance between holes, thickness, mounting height, hole roundness, etc.). However, this is conditional on the leaf springs being oriented in opposite directions.

[0027] This means that when the spring changes its axial height during operation, the resulting radial paths must be of equal magnitude and in the same direction. Otherwise, the leaf spring will build up an internal torque that inhibits displacement and apply significant stress to the components. Additionally, the use of leaf springs provides the spring assembly itself with free centering.

[0028] Advantageously, the spring support of the spring assembly is designed as a sleeve with a radially outwardly projecting central annular collar at its axial center. This annular collar supports multiple individual leaf spring assemblies circumferentially distributed on two sides and acting axially, and these leaf springs consist of multiple individual leaf springs. Each of the individual leaf spring assemblies is fixedly attached to the annular collar with its free end, and each of the individual leaf spring assemblies is fixedly attached to a spring bearing ring with its other free end, which is axially spaced from the annular collar via the individual leaf spring assembly. Advantageously, the spring assembly is designed such that two spring bearing rings are arranged axially spaced from the annular collar and fixedly connected on both sides to the respective individual leaf spring assemblies, moving in the same direction of rotation throughout the displacement path without relative rotational offset. This forms a spring assembly that, due to its scissor-like structure, prevents relative torsion when compressed, and thus prevents radial tension between the two axially spaced spring bearing rings, and is then relaxed throughout the displacement path.

[0029] The first and second ramp elements are preferably designed such that, with the first and second shift elements not rotating relative to each other, the rotor body and stator are arranged at a predetermined maximum axial distance from each other. In the stationary position (maximum field strength position), the maximum distance (d) between the rotor body and stator is sized such that it consists of twice the distance of the air gap present at the maximum field strength (minimum air gap) plus the axial thickness of the permanent magnets arranged on the rotor body.

[0030] In a preferred development, the first shifting element has at least three first ramp elements, and the second shifting element has at least three second ramp elements arranged and configured to correspond to the first ramp elements, such that the optimized distribution of the axial force of the shifting device is ensured by arranging three support points distributed around the circumference.

[0031] The object of the present invention is also achieved by a shifting device for an axial-flow motor, the shifting device comprising the following:

[0032] - A centrally located spring support, as seen from the axial range of the displacement device, supports at least one first spring element on each axial side.

[0033] - Second spring elements, each axially located on two sides, act in parallel with the first spring element.

[0034] - First displacement elements, each axially located on two sides, are designed as supports for the first and second rotor bodies. These first displacement elements can be arranged on the rotor shaft in a manner that allows for axial displacement and limited rotation, whereas the rotor shaft is not arranged in a manner that allows for axial displacement.

[0035] - Second displacement elements are axially located on two sides, and the second displacement elements are connected to the rotor shaft in a rotationally fixed and non-displaceable manner and cooperate with the corresponding first displacement elements.

[0036] Each first displacement element is supported abutting against a first spring element and a second spring element in the axial direction, and at least one rolling element is arranged between the first displacement element and the second displacement element. Furthermore, the first displacement element has a first ramp element on its side facing the second displacement element, and the second displacement element has a second ramp element on its side facing the first displacement element. The first and second ramp elements are designed such that if the first displacement element rotates relative to the second displacement element, or if the second displacement element rotates relative to the first displacement element, the rotor body is axially displaced relative to the rotor shaft.

[0037] Therefore, a compensating spring must be implemented using a spring device that is as close as possible to the magnetic force existing between the rotor and stator. The magnetic force changes according to the air gap, so the spring force must also change during the displacement.

[0038] To keep the forces acting on the displacement device as small as possible, the difference in forces between the two characteristics must be kept as small as possible. It must be ensured that the spring force is always greater than the magnetic force throughout the displacement path to set the air gap, thus maintaining preload on the displacement device.

[0039] The displacement itself is affected by the torque present in the axial-flow motor. The displacement generates an additional axial force via the ramp element of the displacement element, resulting in axial displacement of the rotor body. In the specific embodiment described below, a constant ramp gradient is achieved, and thus the two endpoint positions of the displacement are achieved. However, if the ramp gradient is designed to be variable in the angle of rotation, it is conceivable to achieve multiple intermediate layers.

[0040] In the initial and intermediate positions, the torque is supported by the ramp system, because otherwise displacement would not occur. However, in the high-torque end positions used in the motor, it is advantageous to provide an additional connection in the form of a stop between the ramp elements of the displacement element to support the high torque present. Attached Figure Description

[0041] The invention and its technical field will now be described in more detail with reference to the accompanying drawings. It should be noted that the invention is not intended to be limited by the exemplary embodiments shown. In particular, unless explicitly stated otherwise, aspects of the essential subject matter outlined in the drawings can be extracted and combined with other components and knowledge derived from this specification and / or the drawings. In particular, it should be noted that the drawings, and especially the scale shown, are merely illustrative. The same reference numerals indicate the same objects, and therefore, descriptions from other drawings may be used where applicable.

[0042] In the attached diagram:

[0043] Figure 1 The axial cross-section of the axial flow motor according to the present invention is shown in the schematic diagram.

[0044] Figure 2 This is a force-displacement diagram with magnetic force characteristic curves and spring force characteristic curves. The magnetic force characteristic curve shows the change of the magnetic force curve along the displacement path within the air gap, and the spring force characteristic curve shows the change of the spring force curve along the displacement path within the air gap and its cancellation with the magnetic force.

[0045] Figure 3 A schematic diagram shows an enlarged axial cross-section of the displacement device of an axial flow motor.

[0046] Figure 4 The rotor of the axial-flow motor according to the present invention is shown in a perspective view.

[0047] Figure 5 The displacement device of an axial flow motor is shown in an axial plan view, wherein the rotor body is mounted at the top and there is no rotor body at the bottom.

[0048] Figure 6A portion of the spring mechanism of the displacement device of an axial-flow motor is shown in a perspective view.

[0049] Figure 7 The first shifting element (bottom) and the second shifting element (top) of the shifting device are shown in an axial section (left) and a perspective view (right). Detailed Implementation

[0050] Figure 1 A schematic diagram shows the axial cross-section of an axial-flow motor 1 according to the present invention. The axial-flow motor 1, constructed in a so-called H-type arrangement, includes a stator 2 centrally arranged axially, a first rotor body 31 axially positioned to the left of the stator 2 and arranged on a rotor shaft 3, and a second rotor body 32 axially positioned to the right of the stator 2 and arranged on the rotor shaft 3. The two rotor bodies 31 and 32 are respectively arranged at an axial distance d from the stator 2, thereby forming a first air gap L1 and a second air gap L2. A displacement device 4 is arranged between the two rotor bodies 31 and 32, via which the two rotor bodies 31 and 32 are rotatably connected to each other, and via this displacement device, the two rotor bodies 31 and 32 can be reduced according to the torque generated between the rotor shaft 3 and the rotor bodies of the air gaps L1 and L2, and in order to amplify the magnetic field, the two rotor bodies can be synchronously displaced along the direction of the stator 2 without rotational offset relative to each other.

[0051] The shifting device 4 includes at least one spring device 40, which acts on the first rotor body 31 and the second rotor body 32 to resist the magnetic attraction F_magnet between the respective rotor bodies 31, 32 and the stator 2.

[0052] Figure 2 A force-displacement diagram is shown, which has magnetic force characteristic curve K_magnet force and spring force characteristic curve K_spring force. The magnetic force characteristic curve shows the change of magnetic force F_magnet along the displacement path in the air gaps L1 and L2, and the spring force characteristic curve K_spring force shows the change of spring force F_spring along the displacement path V in the air gaps L1 and L2. The spring force F_spring cancels out the magnetic force F_magnet.

[0053] The spring device 40 is configured such that a spring force characteristic curve K_spring force is formed, which extends along the entire displacement path V, wherein the spring force F_spring is higher than the magnetic force characteristic curve K_magnetic force.

[0054] like Figure 3As shown, the spring device 40 has first spring elements 41 and 42 and second spring elements 410 and 420 that act in parallel with the first spring elements. The first spring elements 41 and 42 are designed as leaf spring assemblies, and the second spring elements 410 and 420 are designed as leaf springs. Figure 2 and Figure 3 It is also clearly shown that the first spring elements 41, 42 and the second spring elements 410, 420 are mechanically arranged in series and act in parallel such that in the first displacement path segment x1 (see Figure 2 On the first spring element 41, 42 and the second spring element 410, 420 are both at least partially but not completely compressed, and the first spring element 41, 42 remain fully compressed within the second displacement path segment x2 following the first displacement path segment x1.

[0055] exist Figure 3 The displacement device 4, shown in detail in axial section, includes a spring device 40 having a centrally arranged spring support 400, visible in the axial direction of the displacement device 4, which axially supports the first spring elements 41; 42 on two sides in the form of leaf spring assemblies. Figure 6 As shown, the corresponding leaf spring assembly is divided into three independent leaf spring assemblies distributed around the circumference. These leaf spring assemblies are connected at their free ends by pins or rivets to a radially outwardly pointing annular collar 401 in the central portion of the sleeve-shaped spring support 400. Each individual leaf spring assembly is connected at its other free end by pins or rivets to spring support rings 71, 72 for receiving second spring elements 410, 420, designed as leaf springs. The inner diameter of the spring support ring is larger than the outer diameter of the sleeve of the spring support 400, such that the spring support 400 can be guided by the axial sleeve end of the spring support when the spring assembly 40 is compressed onto the sleeve portion of the spring support.

[0056] from Figure 3 and Figure 6 As can be clearly observed, the spring device 40 is configured such that the two spring support rings 71, 72 move in the same direction of rotation throughout the displacement path V without relative rotational offset. These two spring support rings are axially arranged at a certain distance from the annular collar 401 and are fixedly connected to corresponding individual leaf spring assemblies on both sides. For this purpose, the leaf springs 41a, 42a of the individual leaf spring assemblies have a longitudinal range in the form of arc segments when viewed from above (see below). Figure 6The leaf springs 41a and 42a are double-bent when viewed in a side view, such that one axial end of the leaf springs 41a and 42a has a different height than the other axial end. Therefore, the axial ends of the leaf springs 41a and 42a are connected to each other via a ramp-shaped connecting section. The leaf springs 41a and 42a of the leaf spring assemblies on the two axial sides of the annular collar 401 are bent out of the plane in different directions (see...). Figure 6 (See different side views of the leaf springs 41a and 42a below, with different curvatures). The individual leaf spring assemblies are arranged on the central annular collar 401 and the spring bearing ring 70 in a manner that creates a scissor mechanism. This is why the axially outward spring bearing rings do not twist or support each other when the spring assembly moves together or moves apart in the axial direction.

[0057] First displacement elements 51 and 52, designed as support members for the first rotor body 31 and the second rotor body 32 respectively, are axially outwardly adjacent to second spring elements 410 and 420 on both sides. The first displacement elements 51 and 52 are arranged, or can be arranged, on the rotor shaft 3 in a limited range in a manner that allows for axial displacement and rotatability. The rotor shaft is not arranged in a manner that allows for axial displacement (not within...). Figure 3(As shown in the diagram). The second shifting elements 61 and 62 are axially adjacent to the corresponding first shifting elements 51 and 52 on their two outward-facing sides. These two second shifting elements are connected to or can be connected to the rotor shaft 3 in a rotationally fixed and displaceable manner and cooperate with the corresponding first shifting elements 51 and 52. In this case, each first shifting element 51 and 52 is supported axially inward against the first spring elements 41 and 42 and the second spring elements 410 and 420 in the direction of the central ring collar 401. Three rolling elements 7, designed as ball bearings, are arranged between the first shifting elements 51 and 52 and the second shifting elements 61 and 62. The first shifting elements 51 and 52 have a total of three first ramp elements 510 and 520 on their sides facing the second shifting elements 61 and 62, and the second shifting elements 61 and 62 have a total of three second ramp elements 610 and 620 corresponding to the first ramp elements 51 and 52 on their sides facing the first shifting elements 51 and 52. The first ramp elements 510, 520 and the second ramp elements 610, 620 are designed such that if the first shifting elements 51, 52 rotate relative to the second shifting elements 61, 62, or if the second shifting element rotates relative to the first shifting element, the rotor bodies 31, 32 are axially displaced inward relative to the rotor shaft 3, thereby correspondingly reducing the existing air gaps L1, L2. In a preferred illustrated embodiment, the first ramp elements 510, 520 and the second ramp elements 610, 620 are each designed in pairs, such that the rotation and associated axial displacement of the shifting elements 51, 52; 61, 62 against each other, or the rotation and associated axial displacement of the rotor bodies 31, 32, are guaranteed in different rotational directions of the motor 1.

[0058] The displacement device 4 shown is arranged in a floating manner on the rotor shaft 3, wherein the two rotor bodies 31, 32 are supported by each other via the displacement device 4.

[0059] One of the two second shifting elements 61 and 62 can also be designed as an integral part of the rotor shaft 3, rather than as a separate component. Figure 3 In the example shown, this would be the second shifting element 62 shown on the right, which can be designed as an integral part of the rotor shaft 3. The rotor shaft 3 shown here is composed of two parts and can be mounted on the upper left side via separate radially widened bearing receiving extensions to form a unified rotor shaft 3, wherein the bearing receiving extensions are axially formed on both sides. As part of the assembly of the rotor shaft 3, a first rotor shaft portion with an integral bearing receiving extension (formed here on the upper right side) can be provided, and then the shifting device 4 and the remaining separate parts of the shifting device are mounted on the rotor shaft 3, and then the second rotor shaft portion designed as a bearing receiving extension is used to complete the process.

[0060] Figure 3 , Figure 4 , Figure 5 and Figure 7 As shown, stop devices 500 and 600 are provided between the first shifting elements 51, 52 and the second shifting elements 61, 62. These stop devices are designed such that, in an operating condition where the torque between the rotor shaft 3 and the rotor body 31, 32 exceeds a predetermined maximum displacement torque, the torque generated is transmitted via the stop devices 500 and 600 instead of via the corresponding first ramp devices 510 and 520 of the first shifting elements 51, 52 and the second ramp devices 610 and 620 of the second shifting elements 61, 62. The stop devices 500 and 600 are designed as radially outward-pointing annular sections. In this case, the stop portion may have a buffer device (not shown) to ensure a smoother stop when moving to the operating position with maximum torque. The buffer device may be formed by, for example, an arranged elastomeric element or spring element, or by the finite stiffness in the geometry of the stop devices 500 and 600.

[0061] like Figure 1 As shown, the first ramp elements 510, 520 and the second ramp elements 610, 620 are designed such that, with the first shifting elements 51, 52 and the second shifting elements 61, 62 not rotating about each other, the rotor bodies 31, 32 and the stator 2 are arranged at a predetermined maximum axial distance from each other.

[0062] This invention is not limited to the embodiments shown in the accompanying drawings. Therefore, the above description should be considered explanatory rather than restrictive. The following claims should be understood to mean that the described features are present in at least one embodiment of the invention. This does not exclude the presence of other features. Where the claims and foregoing description define "first" and "second" features, this designation is used to distinguish two features of the same kind in the absence of an established priority order.

[0063] List of reference numerals

[0064] 1. Axial flow motor

[0065] 2. Stator

[0066] 3. Rotor shaft

[0067] 4. Shifting device

[0068] 7 Rolling elements

[0069] 31 First rotor body

[0070] 32 Second rotor body

[0071] 40 Spring device

[0072] 41, 42 First spring element

[0073] 41a and 42a leaf springs

[0074] 410, 420 Second spring element

[0075] 51, 52 First shifting element

[0076] 61, 62 Second shifting elements

[0077] 500 (stop device for the first shifting element)

[0078] 600 (stop device for the second shifting element)

[0079] 70 Spring Bearing Ring

[0080] d Axial distance

[0081] L1, L2 air gap

[0082] V shift path

[0083] X1 First shift path segment

[0084] X2 Second shift path segment.

Claims

1. An axial-flow motor (1), comprising - Stator (2), - First rotor body (31), the first rotor body is arranged on rotor shaft (3), - and a second rotor body (32), the second rotor body being arranged on the rotor shaft (3), - and a shifting device (4), which is arranged between and connected to the two rotor bodies (31, 32). in, One of the two rotor bodies (31; 32) is arranged on one axial side of the stator (2) with an axial distance (d) to form a first air gap (L1), and the other rotor body (32; 31) is arranged on the other side with an axial distance (d) to form a second air gap (L2), and the axial distance (d) between the rotor bodies (31, 32) arranged on the two sides and the stator (2) can be changed on the displacement path (V) by means of the displacement device (4) according to the torque generated between the rotor shaft (3) and the rotor bodies (31, 32), wherein the magnetic attraction force (F_magnet) between the corresponding rotor bodies (31; 32) and the stator (2) maps a magnetic force characteristic curve (K_magnetic force) on the displacement path (V), characterized in that The displacement device (4) includes at least one spring device (40) acting on the first rotor body (31) and the second rotor body (32) to resist the magnetic attraction (F_magnet) between the rotor body (31; 32) and the stator (2), wherein the spring device (40) is configured such that a spring force characteristic curve (K_spring force) is formed, which is higher than the magnetic force characteristic curve (K_magnetic force) over the entire displacement path (V); the spring device (40) includes a first spring element (41, 42) and a second spring element (410, 420), wherein the first spring element (41, 42) is designed as a leaf spring assembly having a plurality of leaf springs (41a, 42a), and wherein the second spring element (410, 420) is designed as a leaf spring.

2. The axial flow motor (1) according to claim 1, characterized in that... The first spring element (41, 42) and the second spring element (410, 420) are mechanically arranged in series and act in parallel such that on the first displacement path portion (x1), the first spring element (41, 42) and the second spring element (410, 420) are at least partially but not completely compressed, and the first spring element (41, 42) remains fully compressed in the second displacement path portion (x2) following the first displacement path portion (x1).

3. The axial flow motor (1) according to claim 1, characterized in that... The shifting device (4) includes: - A centrally located spring support (400) is visible from the axial range of the displacement device (4), the spring support supporting at least one first spring element (41; 42) on each axial side. - Second spring elements (410; 420) are axially located on two sides, and the second spring elements act in parallel with the first spring elements (41; 42). - First displacement elements (51, 52) are axially located on two sides, each designed as a support for the first rotor body (31) and the second rotor body (32), wherein the first displacement elements (51, 52) are arranged on the rotor shaft (3) in a manner that allows axial displacement and limited rotation, while the rotor shaft is not arranged in a manner that allows axial displacement. - Second displacement elements (61; 62) are axially located on two sides, respectively, and are connected to the rotor shaft (3) in a rotationally fixed and non-displaceable manner, and cooperate with the corresponding first displacement elements (51; 52). Each of the first shifting elements (51, 52) is supported abutting against the first spring element (41, 42) and the second spring element (410, 420) in the axial direction, and at least one rolling element (7) is arranged between the first shifting element (51, 52) and the second shifting element (61, 62), and the first shifting element (51, 52) has a first ramp element (510, 520) on the side of the first shifting element facing the second shifting element (61, 62), and the second shifting element (61, 62) The second shifting element has a second ramp element (610, 620) on the side facing the first shifting element (51, 52), wherein the first ramp element (510, 520) and the second ramp element (610, 620) are designed such that if the first shifting element (51, 52) rotates relative to the second shifting element (61, 62), or the second shifting element (61, 62) rotates relative to the first shifting element (51, 52), the rotor body (31, 32) is axially displaced relative to the rotor shaft (3).

4. The axial flow motor (1) according to claim 1, characterized in that... The first spring element (41, 42) is designed to map a linear spring force characteristic curve and / or the second spring element (51, 52) is designed to map a progressive spring force characteristic curve.

5. The axial-flow motor (1) according to claim 4, characterized in that... The shifting device (4) is arranged in a floating manner on the rotor shaft (3), and the two rotor bodies (31, 32) are supported by each other via the shifting device.

6. The axial-flow motor (1) according to any one of the preceding claims, characterized in that... The spring device (40) is designed to map a spring force characteristic curve that is below the function: F_magnet_limit = F_magnet + F_magnet_maximum * 0.3 over the entire displacement path.

7. The axial-flow motor (1) according to claim 3, characterized in that... A stop device (500, 600) is provided between the first shifting element (51, 52) and the second shifting element (61, 62). The stop device is designed such that when the torque between the rotor shaft (3) and the rotor body (31, 32) is higher than a predetermined maximum shifting torque, the torque generated is transmitted via the stop device (500, 600) instead of via the corresponding first ramp element (510, 520) and second ramp element (610, 620) of the first shifting element (51, 52) and the second shifting element (61, 62).

8. The axial-flow motor (1) according to any one of claims 1 to 5, characterized in that... The first rotor body (31) and the second rotor body (32) are rotatably connected to each other such that no relative rotation occurs between the first rotor body (31) and the second rotor body (32) during operation of the axial flow motor (1), wherein the frictional connection between the two rotor bodies (31; 32) is achieved via the shifting device (4) arranged between the first rotor body (31) and the second rotor body (32).

9. The axial-flow motor (1) according to any one of claims 1 to 5, characterized in that... A spring bearing ring (70) is provided between the first spring element (41; 42) and the second spring element (410; 420) in their respective cases.

10. The axial-flow motor (1) according to claim 9, characterized in that... The spring support (400) is designed as a sleeve having a radially outwardly projecting central annular collar (401) in the axial center of the sleeve, wherein the annular collar (401) supports a plurality of individual leaf spring assemblies circumferentially distributed on both sides and acting in the axial direction, wherein each of the individual leaf spring assemblies is fixedly attached to the annular collar (401) with its free end, and wherein each of the individual leaf spring assemblies is fixedly attached to the spring bearing ring (70) with its other free end, the spring bearing ring being axially spaced from the annular collar (401) via the individual leaf spring assemblies.

11. The axial-flow motor (1) according to claim 10, characterized in that... The spring assembly (40) is configured such that the two spring bearing rings (70) move in the same direction of rotation along the entire displacement path (V) and do not rotate relative to each other. The two spring bearing rings are axially arranged at a distance from the annular collar (401) and are fixedly connected to the respective individual leaf spring assemblies on both sides.

12. The axial-flow motor (1) according to claim 3, characterized in that... The first ramp element (510, 520) and the second ramp element (610, 620) are designed such that, in a state where the first shift element (51, 52) and the second shift element (61, 62) do not rotate about each other, the rotor body (31, 32) and the stator (2) are arranged at a predetermined maximum axial distance from each other.

13. The axial-flow motor (1) according to claim 12, characterized in that... The first shifting element (51, 52) has at least three first ramp elements (510, 520), and the second shifting element (61, 62) has at least three second ramp elements (610, 620) arranged and formed to correspond to the first ramp elements (510, 520).

14. A shifting device (4) for an axial-flow motor (1), the shifting device comprising: - A centrally arranged spring support (400) is observed in the axial range of the shifting device (4), which supports at least one first spring element (41, 42) on each axial side, the first spring element (41, 42) being designed as a leaf spring assembly having a plurality of leaf springs (41a, 42a). - Second spring elements (410, 420) are axially located on two sides, and the second spring elements act in parallel with the first spring element (41). The second spring elements (410, 420) are designed as leaf springs. - First displacement elements (51, 52) are axially located on two sides, and the first displacement elements are designed as supports for the first rotor body (31) and the second rotor body (32), wherein, The first displacement elements (51, 52) are arranged on the rotor shaft (3) in a manner that allows for axial displacement and limited rotation, while the rotor shaft is not arranged in a manner that allows for axial displacement. - Second shifting elements (61; 62) are axially located on two sides, and the second shifting elements are rotatably fixed and non-displaceable to the rotor shaft (3) and cooperate with the corresponding first shifting elements (51; 52). Each of the first shifting elements (51, 52) is supported abutting against the first spring element (41, 42) and the second spring element (410, 420) in the axial direction, and at least one rolling element (7) is arranged between the first shifting element (51, 52) and the second shifting element (61, 62), and the first shifting element (51, 52) has a first ramp element (510, 520) on the side of the first shifting element facing the second shifting element (61, 62), and the second shifting element (61, 62) The second shifting element has a second ramp element (610, 620) on the side facing the first shifting element (51, 52), wherein the first ramp element (510, 520) and the second ramp element (610, 620) are designed such that if the first shifting element (51, 52) rotates relative to the second shifting element (61, 62), or if the second shifting element (61, 62) rotates relative to the first shifting element (51, 52), the rotor body (31, 32) is axially displaced relative to the rotor shaft (3).

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