coupling

Abstract

Clutch (10) for selectively preventing the rotational movement of a gear (12) about an axis, wherein the clutch (10) comprises: an actuator (20); a pivotably movable pawl (40), wherein the pawl (40) interacts with the gear (12); a plunger (24) which is radially movable within and through the actuator (20), wherein the plunger (24) is oriented perpendicular to the axis in order to control the pawl movement; a pair of axially spaced side walls (16, 18), each side wall (16; 18) comprising an opposing radially extending slot (52); a pawl push element (50) that is radially movable between the plunger (24) and the pawl (40), wherein the pawl push element (50) includes a pair of axially extending wing sections (54, 56), each wing section (54; 56) being slidably mounted in one of the opposing slots (52) to limit the movement of the pawl push element (50) to a purely radial movement; wherein axial and / or circumferential force loads, which are transmitted by the pawl (40) to the pawl push element (50), are not transmitted to the radially movable plunger (24).

Description

TECHNICAL AREA

[0001] The present disclosure relates to couplings, in particular sector couplings with pawls, which are used for the rotational control of gears.

[0002] DE 10 2017 104 173 A1 describes a coupling module with a pivotable pawl that can engage with a cam profile of a rotatable element. A radially adjustable cam is provided for pivoting the pawl, and this cam interacts directly with a heel of the pawl. A similar coupling system is also known from DE 11 2016 001 178 T5; however, instead of the cam, a radially adjustable and rotatable deflection lever is used.

[0003] DE 10 2017 212 571 B4 describes a freewheel clutch arrangement with a pivotable pressure rod that can be engaged or disengaged by ratchet teeth. A pivotable anchor, directly interacting with the pressure rod, is provided for actuating the pressure rod. BRIEF DESCRIPTION OF THE DRAWINGS

[0004] One or more embodiments of the disclosure are described below in conjunction with the accompanying drawings, wherein identical reference numerals refer to identical elements, and wherein: Fig. 1 is a perspective representation of an embodiment of a sector coupling shown in interaction with a gear and including a pair of side plates designed to support an actuator constructed according to an embodiment of this disclosure; Fig. Figure 2 is a partial side view of the same embodiment of the sector coupling. Fig. 1, wherein one of the side plates is removed to expose internal coupling structures which are positioned in an unlocked or free-running mode relative to the gear; Fig. Figure 3 is a similar partial side view of the same embodiment of the sector coupling of Fig. 1 and Fig. 2, but positioned in a locked mode relative to the gear; Fig. 4 is a cross-section of an inner section of the sector coupling along lines 4-4 of Fig. 3, wherein the section is constructed according to a disclosed embodiment; Fig. Figure 5 is a partial side view of an alternative embodiment of the sector coupling, also with a side plate removed to expose internal coupling structures positioned in an unlocked or free-running mode relative to the gear; Fig. Figure 6 shows a similar partial side view of the same embodiment of the sector coupling. Fig. 5, but positioned in a locked mode relative to the gear. Fig. Figure 7 shows a pair of sector couplings located in opposite orientations to provide additional functionality in yet another embodiment of this disclosure. DETAILED DESCRIPTION OF EXECUTION FORMS

[0005] A sector coupling described herein is designed to control the rotary motion of a component, such as a gear with a multitude of teeth, stops, or detents. Unlike other couplings, a sector coupling is designed to engage with a relatively limited angular range, or sector, of the 360° circumference of a rotating circular gear with which it interacts. Such a coupling can control the gear with only a single actuator and a single pawl. The gear and the pawl can each rotate or pivot about separate axes to selectively engage or disengage the gear, either allowing or preventing its rotary motion.

[0006] The pawl can be controlled by an actuator, which in turn can move a plunger to engage the gear or disengage the pawl from the gear. The embodiments of the clutch shown and described herein can be used in a wide range of applications that benefit from controlling gear movement by an actuator. Although the clutch can be used to control the movement of gears in vehicle transmissions, other applications involving selective control of gear rotation are also possible.

[0007] Now, referring to Fig. Figure 1 shows a first embodiment of a sector coupling 10, which is spatially fixed relative to and thus engages with a gear 12 oriented along a rotational axis aa. In at least one embodiment, the sector coupling 10 is fixed in an interactive gear element (not shown) that extends circumferentially around the gear 12. A gear, e.g., the gear 12, is defined here as a gear comprising at least one or more teeth 14. The sector coupling 10 includes a first side plate 16 (background) and a second side plate 18 (foreground), the first and second side plates being axially spaced apart, as shown.

[0008] Now, referring to Fig. Figure 2 shows an actuator 20, which is depicted here as an electromagnet, although other power sources, such as hydraulic pressure, can also be used to operate the actuator 20. The actuator includes an armature 22 and a plunger 24, which is designed to move back and forth under the influence of forces selectively exerted either by an electromagnetic field generated by the armature or by a plunger spring 26. For this purpose, the plunger spring 26 is held between a distal end 28 of the plunger 24 and an inner upper surface 38 of an actuator support block 36, which is secured between the first and second side plates 16, 18 by screws (not shown) extending through openings 34.The actuator support block 36 can be made of a non-conductive material, or, if desired for certain configurations, for example to allow flux to the electromagnet, it can alternatively be made at least partially of a conductive material. Ideally, the support block 36 is formed of a rigid material, such as a hard polymer, sufficient to minimize any deformations generated in a relatively harsh environment with high thermal loads and alternating mechanical forces, such as those found, for example, within vehicle transmissions.

[0009] Further referring to Fig. 2 A projection 30 is fixed to a proximal end 32 of the plunger 24. The projection 30 is designed to interact, at least indirectly, with a pawl 40, causing the pawl 40 to pivot axially extending support projections 42. This interaction causes the tip 44 of the pawl 40 to move whenever the plunger 24 interacts with the heel 46 of the pawl 40. It will be clear to those skilled in the art that, for the return movement, a pawl spring 48 exerts a relatively small force on the tip 44 of the pawl compared to the force of the interactive spring 28, which presses against the distal end 28 of the plunger 24.In the disclosed embodiment, whenever the armature 22 is electrically de-energized, the plunger spring 26 becomes effective to push the plunger downwards, overcoming an opposing force of the pawl spring 48 and causing the clutch to move into a free-running mode as shown. In this mode, the tip 44 is held out of engagement with the teeth 14, preventing any interaction with them. Thus, in a fail-safe mode, which is defined here as a mode in which no energy is supplied to the armature 22, the clutch can move into the free-running mode, which is shown in the diagram. Fig. As shown in diagram 2, move and remain in this state. Although the fail-safe mode is designed as described, it can alternatively be modified to allow a locked mode instead.

[0010] Now, referring to Fig. Figure 3 shows the actuator 20 in an energized state, and the sector clutch 10 is shown in a locked mode, in which the tip 44 of the pawl 40 is forced into engagement with a tooth 14 of the gear 12 by the force of the pawl spring 48. In an energized state, an electromagnetic field produced by the armature 22 causes the plunger 24 to be pulled upwards into the interior of the armature. The armature is designed to be strong enough to overcome the force of the plunger spring 26.

[0011] In the disclosed embodiment of the sector coupling 10 of Fig. 2 and Fig. 3. A pawl push element 50 is used to prevent the transmission of non-radial loads from the pawl 40 to the plunger 24. For this purpose, the projection 30, which is fixed to the proximal end of the plunger 24, is designed to interact only directly with the pawl push element 50. Now also with reference to Fig. Figure 4 shows a cross-section of the pawl push element, radially along lines 4-4 of Fig. 3 seen, a pair of first and second opposing wing sections 54, 56, which run radially within radially oriented slots 52 of the side plates 16, 18 (only in the first side plate 16 in Fig. 3 shown). The opposing wing sections 58 and 60 extend circumferentially between the first and second side plates 16, 18, or at right angles to the first and second wing sections 54, 56, thus forming a four-armed cross-section in the pawl thrust element 50, seen along its radial orientation ( Fig. 4) The four radially spaced wing sections 54, 56, 58, and 60 of the pawl thrust element 50 work together to ensure that no lateral loads exerted by the pawl 40 are transferred to the plunger 24. Since the wing sections of the floating pawl thrust element 50 are limited purely to radial movements, including those within the slots 52 of the first and second side plates 16, 18, neither the projection 30 nor the plunger 24 can be subjected to non-radial forces from the pawl 40.

[0012] Now, referring to Fig. Figure 5 shows a second embodiment of a sector coupling 110. In the descriptions of additional embodiments given herein, all reference numerals are analogous to those of previously described embodiments. Thus, in each newly introduced embodiment, elements similar to those of the previously introduced embodiments have similar reference numerals, but with a preceding multiple of one hundred for differentiation. For example, the pawl-push element 50 of the first embodiment becomes a pawl-push element 150 in the second embodiment, etc.

[0013] Thus, in the second embodiment of the sector coupling 110, a pawl push element 150 rests against a tip 144 instead of against a heel 146. Also in this second embodiment, the pawl spring 148 presses against the heel 146 of the pawl 140 instead of against the tip 144. Fig. Figure 5 shows the clutch in a free-running mode in which an actuator 120 has been de-energized, similarly to the fail-safe mode described in relation to the first embodiment of Fig. 2 was described. It will be clear to those skilled in the art that, apart from the exception described, the sector coupling 110 is in every respect analogous to the first embodiment ( Fig. 2) is.

[0014] In Fig. Figure 6 shows the second embodiment of the sector clutch 110 in a locked mode, with the tip 144 shown in engagement with a tooth 114 of a gear 112. In this mode, the armature 120 is energized, and thus the force of the plunger spring (not shown) acts to overcome the lesser force of the pawl spring 148, analogous to the state of the clutch as described in relation to the first embodiment.

[0015] Finally, with reference to Fig. 7, a double sector coupling arrangement, provides a third embodiment that offers additional functionality. Thus, the sector couplings 210 and 310, which are shown here angularly adjacent to each other for common interaction with the gear 212, provide additional operating modes besides a one-way freewheeling mode and a one-way locking mode provided by the first two embodiments of the sector coupling. The double sector coupling arrangement offers four different states or modes: 1) unhindered rotation; 2) fully locked rotation; 3) rotation only in one direction, clockwise; and 4) rotation only in one direction, counterclockwise. The respective dual actuators 220 and 320 of the couplings 210 and 310 can be selectively controlled to selectively allow the rotation of the gear 212 to permit each of the four states, as will be readily apparent to those skilled in the art.

[0016] As an example, the clutch 210 can be a transmission clutch designed to actuate a primary pawl 240 associated only with forward movements of a vehicle, while the clutch 310 can actuate a secondary pawl, e.g. pawl 340, to allow only reverse movements of the same vehicle.

[0017] It should be clear that the foregoing description encompasses only a few embodiments of the disclosure. However, the disclosure is not limited to the specific disclosed embodiment(s). For example, it is conceivable that other embodiments or configurations might employ only axial movements of the pawl push element, although only the radial movement of the pawl push element 50, 150, 250, 350 has been shown and described herein. Furthermore, the statements contained in the description relate only to the specific embodiments and should not be interpreted as limiting the scope of the disclosure or the definitions of terms used in the claims, except where a term or phrase may be expressly defined.Numerous other embodiments, variations and modifications of the disclosed embodiment(s) will be clear to the person skilled in the art and are intended to fall within the spirit and scope of the attached claims.

[0018] The terms “e.g.,” “for example,” “approximately,” and “similar,” and the verbs “comprise,” “have,” “include,” and their concrete verbal forms, as used in this revelation, in conjunction with a list of one or more components or other points, are to be interpreted as non-exclusive and open-ended; this means that the list should not be interpreted as exhaustive or as excluding other additional components or points. All terms are always to be interpreted in their broadest possible sense, unless they are used in a context that requires a different interpretation.

Claims

[1] Coupling (10) for selectively preventing the rotational movement of a gear (12) about an axis, wherein the coupling (10) comprises: an actuator (20); a pivotably movable pawl (40), wherein the pawl (40) interacts with the gear (12); a plunger (24) which is radially movable within and through the actuator (20), wherein the plunger (24) is oriented perpendicular to the axis in order to control the pawl movement; a pair of axially spaced side walls (16, 18), each side wall (16; 18) comprising an opposing radially extending slot (52); a pawl push element (50) that is radially movable between the plunger (24) and the pawl (40), wherein the pawl push element (50) includes a pair of axially extending wing sections (54, 56), each wing section (54; 56) being slidably mounted in one of the opposing slots (52) to limit the movement of the pawl push element (50) to a purely radial movement; wherein axial and / or circumferential force loads, which are transmitted by the pawl (40) to the pawl push element (50), are not transmitted to the radially movable plunger (24). [2] Clutch (10) according to claim 1, wherein the plunger (24) has radially spaced proximal and distal ends (32; 28), wherein a projection (30) is located at its proximal end (32), wherein the projection (30) is in direct contact with and moves the pawl push element (50). [3] Coupling (10) according to claim 1, wherein the pawl push element (50) has a four-armed cross-section. [4] Coupling (10) according to claim 1, wherein the pawl push element (50) is configured to float radially between the projection (30) and the pawl (40). [5] Coupling (10) according to claim 1, wherein the coupling (10) is a sector coupling (10) and each pawl (40) includes a heel (46) and a tip (44). [6] Clutch (110) according to claim 1, further comprising a spring (148) which is biased against a heel (146) of the pawl (140), and wherein the pawl push element (150) biases a tip (144) of the pawl (140). [7] Clutch (10) according to claim 1, further comprising a spring (48) which is biased against a tip (44) of the pawl (40), and wherein the pawl push element (50) biases a heel (46) of the pawl (40). [8] A pawl push element (50) for a clutch (10) designed to selectively prevent the rotational movement of a gear (12), the pawl push element (50) comprising: a cross-shaped element suitable for being inserted radially between a control plunger (24) of the clutch (10) and a pivotable pawl (40) of the clutch (10), wherein the element is limited to an exclusively radial movement within the clutch (10). [9] Pawl push element (50) according to claim 8, wherein the control plunger (24) has radially spaced proximal and distal ends (32; 28), wherein a projection (30) is located at its proximal end (32), wherein the projection (30) is in direct contact with the pawl push element (50) and moves it. [10] Latch push element (50) according to claim 8, further comprising a four-armed cross-section. [11] Pawl push element (50) according to claim 8, which is further configured to float radially between the projection (30) and the pawl (40). [12] Pawl push element (50) according to claim 8, wherein the coupling (10) is a sector coupling (10) and each pawl (40) includes a heel (46) and a tip (44). [13] Pawl push element (150) according to claim 8, wherein the clutch (110) further comprises a spring (148) which is biased against a heel (146) of the pawl (140), and wherein the pawl push element (150) biases the tip (144) of the pawl (140). [14] Pawl push element (50) according to claim 8, wherein the clutch (10) further comprises a spring (48) which is biased against a tip (44) of the pawl (40), and wherein the pawl push element (50) biases the heel (46) of the pawl (40). [15] Method for manufacturing a sector coupling (10) for selectively preventing the rotational movement of a gear (12) about an axis; the method comprising the following steps: Forming an actuator support block (36), and installing an actuator (20) in the support block (36); Forming a pair of axially spaced side walls (16, 18), each having a slot (52) oriented radially with respect to the axis; Securing the side walls (16, 18) to the support block (36); Forming a pivotably movable pawl (40) for interaction with teeth (14) on the gear (12), wherein the pawl (40) has axial ends (42) which are pivotably anchored in each side wall (16, 18); Forming a radially movable plunger (24) which is oriented perpendicular to the axis, wherein the plunger (24) is suitable for controlling the pawl movement; Securing the plunger (24) to the actuator (20); Forming a pawl push element (50) designed to float radially between the plunger (24) and the pawl (40), wherein the pawl push element (50) includes a pair of axially extending wing sections (54, 56), each wing section (54; 56) being slidably mounted in one of the opposing slots (52) to allow movement of the pawl push element (50); wherein axial and / or circumferential force loads, which are transmitted by the pawl (40) to the pawl push element (50), are not transmitted to the radially movable plunger (24).

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