Dual-purpose stop pin and gearbox actuator using same

Abstract

A dual purpose detent pin and a transmission actuator using the same are provided. The dual purpose detent pin (106) includes two linearly reciprocating detent balls (108a, 108b) linearly reciprocable along a vertical axis (VA) and disposed at opposite ends of the dual purpose detent pin (106), first and second retaining structures (110a, 110b) for retaining the two linearly reciprocating detent balls (108a, 108b), respectively, and linearly reciprocable along the vertical axis (VA). The dual purpose detent pin (106) further includes a spring (112) in contact with both the first and second retaining structures (110a, 110b) and configured to allow predetermined range of linearly reciprocal opposite movement of at least one of the first and second retaining structures (110a, 110b) and at least one of the two linearly reciprocating detent balls (108a, 108b) along the vertical axis (VA).

Description

TECHNICAL FIELD

[0001] The present invention relates to a dual-purpose stop pin for use in a gearshift actuator. In particular, the present invention relates to a dual-purpose stop pin which not only prevents an undesired or unanticipated linear movement of a push rod within a gearshift actuator, but also prevents a relative movement between two push rods of a gearshift actuator. BACKGROUND

[0002] Stop pins are commonly used as part of a gearshift actuator. Some prior solutions related to conventional stop pins can be found in patent publications such as DE 9105258 U1, DE 102014213599 A1, DE 102015223036 A1, DE 19954386 A1, DE 20103393 U1, DE 4215187 A1, DE 19648856 A1 and DE 9319480 U1.

[0003] Pneumatic actuation gearshifts for commercial vehicles can comprise one or more pneumatic actuators which are cylindrical in shape. The pneumatic actuators comprise a piston and a connecting rod which is attached to the piston.

[0004] When the piston is linearly reciprocating within the pneumatic actuator, it causes the connecting rod to linearly reciprocate. The connecting rod is connected to gearshift shafts via downstream elements such as dog clutches or synchronizers on which a plurality of gears of the vehicle gearshift are arranged. However, from the perspective of the gearshift and / or gearshift actuator manufacturer, it must be prevented that any accidental or unanticipated movement of the connecting rod of any single pneumatic actuator, or a relative movement between the connecting rod(s) associated with different pneumatic actuators within the gearshift actuator, occurs. Thus, an accidental engagement or disengagement of gears within the gearshift does not occur.

[0005] Since there is a need for an alternative and / or further improvement of prior solutions, the present invention relates to such a failsafe element which is arranged within a gearshift actuator. SUMMARY

[0006] According to an embodiment of the present invention, a dual-purpose stop pin is disclosed. Within the scope of the present invention, the term "dual-purpose stop pin" can be understood as follows.

[0007] It is known to use stop pins to stop, suppress, or prohibit undesirable movement of corresponding shafts within a transmission actuator (see the Background section above). However, the dual-purpose stop pin of the present invention not only prevents movement of the individual shafts of the transmission actuator but also prevents "relative" movement of the first shaft of the transmission actuator relative to the second shaft of the transmission actuator. Further details and detailed technical benefits of having such a dual-purpose stop pin of the present invention will be explained in detail with reference to detailed embodiments.

[0008] Therefore, the dual-purpose stop pin of the present invention according to an embodiment includes two linearly reciprocating stop balls capable of linearly reciprocating along a vertical axis and disposed at opposite ends of the dual-purpose stop pin. In this respect, the "opposite ends" of the dual-purpose stop pin can refer to the vertical axis passing through the dual-purpose stop pin (e.g., see...). Figure 1a , 2 The vertical opposite side of the figure (VA) in figures 3 and 4.

[0009] The dual-purpose stop pin also includes first and second retaining structures, which are respectively used to retain two linearly reciprocating stop balls and are capable of linear reciprocating along a vertical axis. In an embodiment, the first and second retaining structures are capable of linearly reciprocating along a vertical axis together with the two linearly reciprocating stop balls.

[0010] Furthermore, the dual-purpose stop pin of this embodiment also includes a spring that simultaneously contacts the first and second retaining structures and is configured to allow at least one of the first and second retaining structures and at least one of the two linearly reciprocating stop balls to perform linearly reciprocating opposite movements within a predetermined range along the vertical axis.

[0011] The technical advantage of the dual-purpose stop pin according to this embodiment, as described above, is that a single stop pin is used to prevent accidental (linear) movement, either individually or relative to each other, of two shafts or shift levers, for example, provided in a gearbox actuator.

[0012] In real-world applications or use, as may become apparent in the discussion of further advantageous embodiments, the dual-purpose stop pin prevents the accidental engagement of the wrong gear in a vehicle transmission (i.e., a gear that the vehicle operator has not selected or does not intend to select), which is caused by movement in either direction of the shaft associated with, for example, two pneumatic actuators. Such accidental movement of the shaft or rod associated with the pneumatic actuator of the transmission can occur due to erroneous actuation of a solenoid valve that controls the flow of pressurized air into and out of the pneumatic actuator. Needless to say, as an element of the anti-misoperation design of the transmission actuator, such accidental movement of the shaft associated with the pneumatic actuator should be prevented. The dual-purpose stop pin according to the invention enables this anti-misoperation design according to embodiments of the invention.

[0013] According to an embodiment of the invention, when the spring is in its extended state, the first and second retaining structures are spaced apart by a predetermined gap. In this embodiment, the term "extended state" can be considered as the state in which the spring is subjected to a relatively small compressive force. Furthermore, in this illustrative embodiment, the predetermined gap may appear necessary to ensure that the two linearly reciprocating stop balls of the dual-purpose stop pin contact the outer surface of each shaft (regardless of the profile of the outer surface) and to prevent accidental (linear) movement of these shafts or relative movement of these shafts relative to each other. Since this contact with the outer surface of each shaft should not be lost even during gear shifting, i.e., the shafts do not move, the predetermined gap helps to maintain contact with the outer surface of the shafts, whether the spring is under tension or not. The predetermined gap between the first and second retaining structures is selected taking into account the operating conditions of the dual-purpose stop pin.

[0014] In one or more embodiments of the invention, the dual-purpose stop pin further includes an outer sleeve to orient or align the two linearly reciprocating stop balls, the first and second retaining structures, and the spring along a vertical axis. In the context of this embodiment, the sleeve can simply be configured along a vertical axis to retain the two linearly reciprocating stop balls and the first and second retaining structures.

[0015] In embodiments that are the same as or different from those discussed above, the dual-purpose stop pin is configured to prevent at least one of the two external shafts from horizontally moving along their respective transverse axes, based on the relative axial position of one of the external shafts along its transverse axis and relative to the axial position of the other external shaft along its transverse axis. Particularly advantageously, the dual-purpose stop pin described herein allows each of the two linearly reciprocating stop balls to selectively position itself in a suitable device disposed in the two external shafts, thereby preventing said horizontal movement of at least one of the two external shafts along their respective transverse axes.

[0016] In conjunction with the dual-purpose stop pin of the aforementioned embodiments discussed above, the relative axial position of one of the two external shafts relative to the other external shaft along its respective transverse axis, or the relative difference between the respective axial positions of these external shafts along their respective transverse axes, is related to the measured value of the physical distance between the corresponding bottom surfaces of the two external shafts.

[0017] According to another embodiment or in combination with one or more of the above embodiments, a transmission actuator is disclosed. The transmission actuator includes: a first outer shaft; a second outer shaft positioned parallel to the first outer shaft; and a locking mechanism configured to prevent unintended horizontal movement of each of the first and second outer shafts, and / or any relative unintended horizontal movement between the first and second outer shafts along their respective lateral axes, wherein the locking mechanism includes a dual-purpose stop pin as described in any one or more of the above embodiments.

[0018] According to the gearbox actuator of the embodiment discussed in the above context, each of the first and second outer shafts includes at least two peak-shaped portions and at least two valley-shaped portions on its outer surface. In the context of the first and second outer shafts, the term "outer surface" should be understood synonymously with "external surface" in accordance with various embodiments of the invention. One of the technical objectives of having peak-shaped and valley-shaped portions on the outer surface of the outer shaft is to simplify the rolling of the two linearly reciprocating stop balls, while the peak-shaped portions allow for smoother application of compressive force to the spring of the dual-purpose stop pin.

[0019] Continuing with this embodiment or in another alternative embodiment of the invention, the first peak-shaped portion of each of the first and second outer shafts is separated from the second peak-shaped portion of each of the first and second outer shafts by a first valley-shaped portion. As described above, this allows the stop ball to make smoother instantaneous movements, and furthermore, when the stop ball rolls along the outer surfaces of the first and second outer shafts or instantaneously contacts the peak-shaped and valley-shaped portions, it is complementary to the contour or shape of each of the stop balls.

[0020] Furthermore, in the same embodiment, optionally, the first diameter of each of the first and second outer shafts at the first peak portion is different from the second diameter of each of the first and second outer shafts at the second peak portion. The technical advantage of providing such different diameters at different portions of the first and second outer shafts is that the locking feature associated with the dual-purpose stop pin of the present invention can be achieved, because if the diameters at the respective portions of the first and second shafts are different, the predetermined gap or g0 between the first and second retaining structures can be reduced and / or increased (in a specific operating state of the gearbox actuator). For example, in a predetermined case, if the maximum diameter at the peak portion of the first outer shaft coincides with the maximum diameter at the peak portion of the second outer shaft (i.e., relative to their relative positions, e.g.) Figure 3 In P3), since the gap between the first and second retaining structures becomes "0mm" and the spring is fully compressed, the stop ball, which is in contact with the peaked portions of the first and second outer shafts, cannot roll further in at least one direction. Further details regarding this will be explained in conjunction with the description provided with reference to the accompanying drawings.

[0021] According to various embodiments of the invention, this embodiment further provides the option that the radius of curvature r0, r1, or r2 and / or depth / thickness t0, t1, t2 and / or the tilt angle θ0, θ1, θ2 of each of the at least two valley portions 116, 118 of each of the first outer shaft 102 and the second outer shaft 104 are different from or the same as the other. Various parameters for controlling the resistance to relative movement between shafts 102 and 104 and / or the respective linear movement of shafts 102 and 104 along their respective transverse axes LA1 and LA2 provide gearbox actuator designers with a wide range of choices to achieve optimal solutions. For example, by incorporating the varying diameters at different portions of the outer shaft, the variation in the radius of curvature at each of the at least two valley-shaped portions allows for specific design options (i.e., improved design freedom) to provide a locking feature between the two outer shafts of the gearbox actuator.

[0022] According to one or more of the gearbox actuators discussed above, when the axial position of at least one of the first and second outer shafts changes relative to the other, the two linearly reciprocating stop balls of the dual-purpose stop pin are configured to make instantaneous contact, respectively, with at least one of the peak-shaped portions and at least one of the valley-shaped portions of the first and second outer shafts. This instantaneous contact between the two linearly reciprocating stop balls and the different curves of the outer surface of the shaft reduces the need for lubrication between the contact surface areas. Furthermore, in the same embodiment, the spring is compressed when at least one of the two linearly reciprocating stop balls moves from one of the valley-shaped portions of the first and second outer shafts toward or is located at one of the peak-shaped portions.

[0023] Furthermore, in the gearbox actuator according to one of the foregoing embodiments, the gap (g0, g1, g2, g3) between the first and second retaining structures of the dual-purpose stop pin varies depending on the relative positions of the first and second outer shafts. As will be understood within the scope of the invention, one of the technical advantages is that providing such a varying gap between the two retaining structures allows only a certain degree of compression of the spring between the two retaining structures, while compression beyond this gap would either prevent relative movement between the two outer shafts or allow such relative movement.

[0024] Furthermore, in the gearbox actuator of the aforementioned embodiment, when the first linearly reciprocating stop ball of the two linearly reciprocating stop balls initially engages with the second valley portion of the first outer shaft, and when the first outer shaft undergoes linear translational movement in a first direction parallel to the respective lateral axis, causing the first linearly reciprocating stop ball of the two linearly reciprocating stop balls to roll toward the first peak or first valley portion of the first outer shaft, the gap (g3) between the first and second retaining structures becomes "0 mm" (a zero-gap condition occurs). The technical purpose behind this configuration is to allow the designer to selectively prohibit relative movement between the two outer shafts only when the outer shaft causes a gear shift in the vehicle's transmission and prohibits any reverse movement. More precisely, the gap between these retaining structures is made "0 mm" only when it is necessary to prevent some linear translational movement between these shafts, by adjusting the curve profile along the outer surface of the outer shaft.

[0025] According to exemplary embodiments of the present invention, a vehicle transmission or gearbox includes a transmission actuator as explained in any of the above embodiments. In another embodiment of the invention, a commercial vehicle including the vehicle transmission is claimed. In yet another embodiment, the use of a dual-purpose stop pin as described below or a transmission actuator claimed and / or explained in the embodiments described below in a commercial vehicle transmission is claimed. Attached Figure Description

[0026] . Figure 1a A portion of a dual-purpose stop pin and gearbox actuator according to an embodiment of the present invention is shown;

[0027] . Figure 1b A cross-section of the second outer shaft of a gearbox actuator according to an embodiment of the present invention is shown; and

[0028] . Figures 2 to 4 The operation of a dual-purpose stop pin within a gearbox actuator is illustrated according to one or more embodiments of the present invention. Detailed Implementation

[0029] . Figure 1a A portion of the dual-purpose stop pin 106 and gearbox actuator 100 according to an embodiment of the present invention is shown.

[0030] At least in this embodiment, the gearbox actuator 100 includes a first outer shaft 102, a second outer shaft 104, and a locking mechanism (in... Figure 1a (Not shown in the image), the second outer shaft is positioned parallel to the first outer shaft 102, and the locking mechanism is configured to prevent accidental horizontal movement of each of the first and second outer shafts 102, 104 and / or any relative accidental horizontal movement between the first and second outer shafts 102, 104 along their respective transverse axes LA1, LA2. The locking mechanism includes a dual-purpose stop pin 106, which will be described in detail below.

[0031] According to one or more embodiments of the present invention, each of the first and second outer shafts 102, 104 includes at least two peak-shaped portions 115, 117 and at least two valley-shaped portions 116, 118 on its outer surface or outer surface 122. According to one embodiment, and which is also general to all embodiments of the invention, the outer surface 122 of the first outer shaft 102 and the shape of its peak-shaped and valley-shaped portions (e.g., designated 115, 116, 117, 118, 120) are identical to the shape of the outer surface 122 of the second outer shaft 102. Therefore, no different reference numerals are used for each of these elements designated on the outer shafts 102 and 104. It will be well understood that, according to a preferred embodiment, the outer surface 122 of the first outer shaft 102 need not have the same shape and features as the outer surface of the second outer shaft 104.

[0032] It should be noted that the shapes and features such as peak-shaped portions and valley-shaped portions 115, 116, 117, 118 and 120 on the outer surfaces 122 of the first and second outer shafts 102, 104 are equivalently configured together with the dual-purpose stop pin 106 to prevent accidental horizontal movement of each of the first and second outer shafts 102, 104 and / or any relative accidental horizontal movement between the first and second outer shafts 102, 104 along their respective transverse axes LA1, LA2.

[0033] You can also from Figure 1a It is found that the first peak-shaped portion 115 of each of the first and second outer shafts 102, 104 is separated from the second peak-shaped portion 117 of each of the first and second outer shafts 102, 104 by a first valley-shaped portion 116. Optionally, in this embodiment, the first diameter α1 or α4 of the shaft 102 or shaft 104 at the first peak-shaped portion 115 is different from the second diameter α2 or α5 of the shaft 102 or shaft 104 at the second peak-shaped portion 117.

[0034] In combining Figure 1b Among the other factors discussed, the diameter difference at specific locations along axes 102 and 104 causes spring 112 to compress and extend.

[0035] The dual-purpose stop pin 106 of this embodiment includes two linearly reciprocating stop balls 108a and 108b, which are capable of linear reciprocating along the vertical axis VA and are located at opposite ends of the dual-purpose stop pin 106. The dual-purpose stop pin 106 also includes first and second retaining structures 110a and 110b, which are respectively used to retain the two linearly reciprocating stop balls 108a and 108b and are capable of linear reciprocating along the vertical axis VA. In this embodiment, the first and second retaining structures 110a and 110b are connected in series with the two linearly reciprocating stop balls 108a and 108b to allow linear reciprocating along the vertical axis VA.

[0036] Furthermore, the dual-purpose stop pin 106 of this embodiment also includes a spring 112 that contacts both the first and second retaining structures 110a and 110b, and is configured to allow at least one of the first and second retaining structures 110a and 110b and at least one of the two linearly reciprocating stop balls 108a and 108b to perform linearly reciprocating opposite movements along a predetermined range along the vertical axis VA. According to an embodiment, two springs may be provided between the first and second retaining structures 110a and 110b instead of a single spring. In a particular embodiment, a double-helix compression spring or a coil spring may be used between the first and second retaining structures 110a and 110b.

[0037] The technical advantage of the dual-purpose stop pin 106 according to the present embodiment as described above is that a single stop pin is used to prevent accidental (linear) movement of, for example, two shafts (108a and 108b) or shift levers (108a and 108b) provided in the gearbox actuator 100, either individually or relative to each other.

[0038] In real-world applications or use, as may become apparent in the discussion of further advantageous embodiments, the dual-purpose stop pin 106 prevents accidental engagement of the wrong gear in the vehicle transmission (i.e., a gear not selected by the vehicle operator), said accidental engagement of the wrong gear due to the shaft associated with, for example, two separate pneumatic actuators (e.g., similar to, in...). Figure 1a The movement of the shaft (shown by reference numerals 102 and 104 in the accompanying drawings) in any of its direction of movement (e.g., parallel to the transverse axis LA1 or LA2) is caused by movement. Such unintended movement of the shaft or rod associated with the pneumatic actuator of the gearbox may occur due to malfunction of a solenoid valve (not shown in any of the drawings), which controls the flow of pressurized air into and out of the pneumatic actuator (not shown in any of the drawings). Needless to say, as a gearbox actuator (at least a portion of which is in…) Figure 1aThe anti-misoperation design element (shown as "100" in the accompanying drawings) should prevent such accidental movement of the shaft associated with the pneumatic actuator. The dual-purpose stop pin 106 according to the invention enables this anti-misoperation design according to the present embodiment.

[0039] According to one or more embodiments of this application, the spring 112 may be a constant stiffness spring (stiffness is constant along the length of the spring) or a variable stiffness spring (stiffness varies along the length of the spring). For example, a spring with variable stiffness can provide the technical advantage that at one end of the dual-purpose stop pin 106 (e.g., along the length of the spring)... Figure 1a At one vertical end of axis 'VA', a connection is provided with the other end (e.g., along...). Figure 1a The other vertical end of the axis 'VA' in the middle is more or less compressed compared to the other vertical end.

[0040] Understandably, Figure 1a Only a portion of the transmission actuator 100 is shown. For example, just for clarity, it should be reiterated that shafts 102 and 104 are those shafts extending from pneumatic actuators used for shifting and selecting gears. For example, each of these pneumatic actuators may be a two- or three-cylinder unit, depending on the type of vehicle and / or vehicle transmission associated with these pneumatic actuators. However, it is clear that “accidental” actuation should not occur when a gear in the vehicle transmission is engaged and the driver or vehicle operator does not intend to change that gear.

[0041] Furthermore, according to this embodiment, when the spring 112 is in the extended state, the first and second retaining structures 110a and 110b are spaced apart by a predetermined gap (g0). For example, for illustrative purposes, it should be noted that the spring 112 is able to make the predetermined gap g0 according to this embodiment because the first and second linearly reciprocating stop balls 108a and 108b are positioned at the first and second valley portions 116 and 118 on at least the outer surface 122 of the first outer shaft 102. Due to the recesses at the first and second valley portions 116 and 118, it should be understood that the spring 112 is in the extended state.

[0042] In the same embodiment, the dual-purpose stop pin 106 also includes an outer sleeve 114 such that the two linearly reciprocating stop balls 108a, 108b, the first and second retaining structures 110a, 110b, and the spring 112 are oriented or aligned along a vertical axis (VA). For example, the outer sleeve 114 discussed in the context of this embodiment can simply be configured to hold the two linearly reciprocating stop balls 108a and 108b and the first and second retaining structures 110a and 110b along a vertical axis.

[0043] During use of the dual-purpose stop pin 106 in this embodiment, the dual-purpose stop pin 106 is configured to prevent at least one of the two external shafts 102, 104 from moving horizontally along their respective transverse axes LA1, LA2, based on the relative axial position of one of the two external shafts 102, 104 along its transverse axis LA1 and relative to the axial position of the other external shaft 102, 104 along its transverse axis LA2. For example, see the section being discussed to explain the present embodiment. Figure 1a In this configuration, the first bottom surface 102b of the first outer shaft 102 is directly aligned with the second bottom surface 104b of the second outer shaft 102. This indicates that the relative axial positions of the first outer shaft 102 and the second outer shaft 104 are aligned with each other. This relative axial position is... Figure 1a The text is incomplete and appears to be a fragment of a longer document. A more accurate translation would require the full context. Figure 1a The first linear reciprocating stop ball 108a shown is positioned at the second valley portion 118 of the first outer shaft 102, and the second linear reciprocating stop ball 108b is positioned at the second valley portion 118 of the second outer shaft 102.

[0044] According to this embodiment, the relative axial position of one of the two external shafts (i.e., the first external shaft 102) relative to the other external shaft (i.e., the second external shaft 104) along its respective transverse axis LA1 or LA2, or the relative difference between the respective axial positions of these external shafts along their respective transverse axes LA1, LA2, is related to the measured value of the physical distance between the corresponding bottom surfaces 102b, 104b of the two external shafts 102, 104.

[0045] In real-time gearbox applications, such as Figure 1a The relative position P0 shown, and the positions of the first and second linear reciprocating stop balls 108a and 108b at the second valley portion 118 of the first and second outer shafts, can indicate the "neutral" gear position. Therefore, when the vehicle transmission or gearbox is engaged in neutral (in which state the engine transmission output is not transmitted to the driven shaft within the gearbox), the relative position, referred to as P0, of the first and second outer shafts 102 and 104 of the pneumatic actuator (not shown) is observed.

[0046] .exist Figure 2 , Figure 3 , Figure 4 Explain other possible positions and relative positions P1, P2, and P3 within the context.

[0047] Furthermore, when the axial position of at least one of the first and second outer shafts 102, 104 changes relative to the other of the first and second outer shafts 102, 104, the two linearly reciprocating stop balls 108a, 108b of the dual-purpose stop pin 106 are configured to momentarily contact at least one of the peak portions 115, 117 and at least one of the valley portions 116, 118 of the first and second outer shafts 102, 104, respectively, and wherein the spring 112 is compressed when at least one of the two linearly reciprocating stop balls 108a, 108b moves from one of the valley portions of the first and second outer shafts 102, 104 toward or is in one of the peak portions 115, 117. The technical objective of achieving this momentary contact with the peak and valley portions of the first and second outer shafts 102, 104 will be achieved by combining... Figure 2 , Figure 3 and Figure 4 The explanation provided becomes obvious.

[0048] In the same embodiment, the gap g0 between the first and second retaining structures 110a and 110b of the dual-purpose stop pin 106 is shown (see [link]). Figure 1a The gap g0 depends on the relative positions of the first and second outer shafts 102 and 104. As will be understood within the scope of the invention, one of the technical advantages is that providing this varying gap between the two retaining structures 102 and 104 allows only a certain degree of compression of the spring 112 between the two retaining structures 102 and 104, while compression (of the spring 112) exceeding a certain gap threshold will either prevent relative movement between the two outer shafts 102 and 104 or allow said relative movement.

[0049] The working principle of this invention will be explained by using... Figure 1a The interpretation will be based on publicly available information. However, it should be noted that when providing information related to... Figure 1b , Figure 2 , Figure 3 and Figure 4 The working principle will become more obvious when explained.

[0050] .from Figure 1aAs can be seen, the first and second outer shafts 102 and 104 are positioned parallel to each other, as representatively shown by means of the transverse axes LA1 and LA2. Each of the first and second outer shafts 102 and 104 is connected to two pneumatic actuators (not shown in the figures). Each of the two pneumatic actuators can be used for a separate purpose. For example, one of the two pneumatic actuators could be a first "shift" actuator dedicated to shifting between second and third gears (e.g., responsible for shifting; not shown in the figures), while the other of the two pneumatic actuators could be a second "shift" actuator (not shown in the figures) responsible for shifting between first and reverse gears.

[0051] Therefore, by using the dual-purpose stop pin 106 according to the invention, a mechanical interlock system (or simply a locking system) is implemented between the first shift actuator responsible for first gear and reverse gear and the second shift actuator responsible for shifting between second and third gear. This mechanical interlock system (or locking system) allows for some movement of the relative gear positions of the engaged gears, but prevents the actuator responsible for engaging first gear and reverse gear from causing any movement of the shaft during the engagement of second or third gear.

[0052] It is understood that one of the technical advantages of the dual-purpose stop pin 106 according to the present invention is that it can prevent not only undesired linear movement within a single shaft, but also undesired relative linear movement between two shafts. In this way, accidental or undesirable engagement or alteration of the gear position is prevented in a mis-prevention manner.

[0053] In addition, to achieve the aforementioned effects or technical advantages, the following list of non-exclusive parameters may also be carefully considered in other aspects:

[0054] The diameter (d) of the stop balls 108a and 108b;

[0055] The diameters of the first and second outer shafts 102 and 104 at the peak portions 115 and 117, namely, α1, α2, α4, and α5;

[0056] The radii of curvature (e.g., at the peak portions (115, 117) and valley portions (116, 118, 120) Figure 1b (r0, r1, r2);

[0057] The diameters (α0, α3) of the first and second outer shafts 102 and 104;

[0058] The thickness of the trough-shaped portion at points 116, 118, and 120 (t0, t1, t2);

[0059] The gap between the first and second retaining structures 110a and 110b.

[0060] Further details regarding the parameters associated with implementing the locking mechanism as described above are in the section on... Figure 1b This will become obvious in the discussion.

[0061] Typically, when the vehicle operator requests a gear shift, one of the first and second outer shafts 102 and 104 moves along their respective lateral axes LA1 and LA2, respectively. According to this embodiment, the engaged gear is neutral, and the relative positions of shafts 102 and 104 reflect the alignment of the bottom surfaces 102b and 104b of the first and second shafts 102 and 104 relative to each other. Figure 1a The center is indicated by P0. At this relative position in neutral, the first and second linearly reciprocating stop balls 108a and 108b are positioned at the valley portion 118 (see [reference]). Figure 1a Therefore, when a gear change occurs, one or both stop balls 108a and 108b roll along the outer surface 122 and compress spring 112 as they move toward at least one of the peak portions 115, 117. However, the compression of spring 112 is limited, occurring within a gap (e.g., see g0) between the first and second retaining structures 110a and 110b. This gap between the first and second retaining structures 110a and 110b is carefully designed so that there is no relative movement between the first and second outer shafts 102 and 104 (e.g., see g0). Figure 4 ).

[0062] . Figure 1b A cross-section of the second outer shaft 104 of the gearbox actuator 100 according to an embodiment of the present invention is shown.

[0063] In particular, Figure 1a Part of "1b" in Figure 1b The images are shown in an enlarged view. It can be noted that the valley-shaped portions 116, 118, and 120, and the peak-shaped portions 115 and 117 are shown in an enlarged view. It should be noted that this is merely an illustrative example.

[0064] .according to Figure 1b The disclosed embodiment only shows the second outer shaft 104. Figure 1a Part 1b. However, it must be understood that similar parameters will also appear in the design of the corresponding section at the first outer shaft 102. In other words, the parameters discussed herein apply not only to the second outer shaft 104, but also to the first outer shaft 102 within the scope of this application.

[0065] .from Figure 1bIt can be seen that each valley segment 116, 118, and 120 is shown to have a unique radius r0, r1, and r2, but at least two valley segments 116, 118, and 120 may have radii that are different from each other. The radius of each of the valley segments 116, 118, and 120 directly or indirectly, and at least to some extent, helps to determine whether linear movement of one of the axes 102 and 104 or relative movement of that axis with respect to the other axis is permitted or should be locked.

[0066] Furthermore, in Figure 1b In this context, the tilt angles θ0, θ1, θ2, θ3, θ4, and θ5 of the relatively inclined surfaces 116.1, 116.2, 118.1, 118.2, 120.1, and 120.2 are respectively associated with each of the valley portions 116, 118, and 120. The tilt angles θ0, θ1, θ2, θ3, θ4, and θ5 are illustrated with reference to the horizontal surface or outer surface 122.1 of the second axis 104 as a horizontal line / plane. As from... Figure 1b As can be interpreted, the tilt angle of each of the opposing surfaces of the valley portions 116, 118, and 120 has a direct influence, for example, on the depth or thickness (t0, t1, t2) relative to surface 122.1 at the valley portions 116, 118, and 120. By controlling each or one or more of these parameters (including the tilt angle, radius of curvature, and thickness of the opposing tilted surfaces), the invention provides, in the exemplary description, precise control or anti-misoperation measures to prevent one or more of the stop balls 108a and 108b from moving from one of the valley portions 118 (e.g., t0, t1, t2). Figure 1a (As shown) Roll to another valley-shaped section (see...) Figure 2 and Figure 3 ) or does not roll to another valley (see Figure 4 ).

[0067] Furthermore, this embodiment provides the option that the radius of curvature r0, r1, or r2 and / or depth / thickness t0, t1, t2 and / or the tilt angle θ0, θ1, θ2 of each of the at least two valley portions 116, 118 of each of the first and second outer shafts 102, 104 are different from or the same as the other. Such a variety of parameters for controlling the inhibition of relative movement between shafts 102 and 104 and / or the respective linear movement of shafts 102 and 104 along their respective transverse axes LA1 and LA2 provides gearbox actuator designers with a wide range of choices to achieve the optimal solution.

[0068] . Figures 2 to 4The operation of a dual-purpose stop pin within a gearbox actuator 100 according to one or more embodiments of the present invention is illustrated.

[0069] According to the embodiment, Figure 2 The instantaneous movement of the second external shaft 104, indicated by the arrow "M," is shown, while the first external shaft 102 is stationary or immobile at that point. Due to the movement of the second external shaft 104 along the transverse axis LA2 in the direction "M," the second external shaft 104 compresses the spring 112 due to the linear reciprocating stop ball 108b moving linearly upward along the vertical axis VA. To illustrate the movement of the second linear reciprocating stop ball 108b along the vertical axis VA, the upward direction... Figure 2 The arrow "U" is used to clearly indicate the actual meaning of "upward direction". According to the present invention, the upward direction "U" can be understood as a direction that starts from the second outer axis 104 and points towards the first outer axis 102, while being perpendicular to the transverse axis LA2 or LA1. Therefore, when a gear shift occurs, the second linear reciprocating stop ball 108 is indicated as "midway" by the movement of the second outer axis 104.

[0070] It should be noted that at this stage, with Figure 1a Compared to the gap "g0", the gap "g1" between the first and second retaining structures 110a and 110b is smaller in size (millimeters "mm"), but not exactly "zero" or 0 millimeters. This state will effectively allow the second outer shaft 104 to move further along axis LA2 in the direction "M". Figure 3 The location of the action is shown or indicated, wherein the second linear reciprocating stop ball 108b is positioned at the first valley-shaped portion 116 of the second outer shaft 104. It is also noteworthy that... Figure 2 The relative horizontal position P1 between the first and second outer shafts 102 and 104 is in Figure 3 The relative horizontal position P2 has been changed to the updated position. In other words, simply by comparing the axis in... Figure 2 and Figure 3 The relative positions of the two outer shafts 102 and 104, and the distance between the bottom surfaces 102b and 104b, increase due to the horizontal movement of the second outer shaft 104.

[0071] For example, according to an embodiment, relative movement of shafts 102 and 104 can result in a gear shift from second to third gear in a transmission (not shown in the figures). However, it should be noted that during such a shift, the first outer shaft 102 travels along... Figure 4 Movement in the "M" direction shown should stop.

[0072] This is like Figure 4The implementation shown prevents the first outer shaft 102 from moving "M" along the transverse axis LA1 because when the first linear reciprocating ball 108a moves instantaneously from the second valley portion 118 to the first valley portion 116, the gap g3 has already become "0mm" (see [reference]). Figure 4 The instantaneous contact point at which the first linear reciprocating ball 108a stops rolling is at... Figure 4 The figure is marked with 400.

[0073] Alternatively, in this embodiment, when the first linearly reciprocating stop ball (i.e., 108a of balls 108a and 108b) initially engages with the second valley portion 118 of the first external shaft 102, and when the first external shaft 102 undergoes a linear translational movement in a first direction M parallel to the respective transverse axis LA1 such that the first linearly reciprocating stop ball (i.e., 108a) rolls toward the first peak portion 115 or the first valley portion 116 of the first external shaft 102, the gap (g3) between the first and second retaining structures 110a and 110b becomes “0 mm” or a gapless condition occurs.

[0074] Due to the above-described operating scheme or sequence, the dual-purpose stop pin 106 of the present invention (as part of the gearbox actuator 100 or its locking mechanism) prevents each of the first and second external shafts 102, 104 from undergoing unintended horizontal movement and / or any unintended relative horizontal movement between the first and second external shafts 102, 104 along their respective transverse axes LA1, LA2.

[0075] According to an embodiment, a commercial vehicle including the vehicle transmission is disclosed. Furthermore, the use of a dual-purpose stop pin 106 or a transmission actuator in a commercial vehicle (not shown in any of the figures) is disclosed.

[0076] List of reference numerals (part of the instruction manual)

[0077] 100-Gearbox Actuator

[0078] 102-First outer shaft

[0079] 102b - First bottom surface of the first outer shaft 102

[0080] 104 - Second outer shaft

[0081] 104b - Second bottom surface of the second outer shaft 104

[0082] 106-Dual-purpose stop pin

[0083] 108a and 108b - First and second linear reciprocating stop balls

[0084] 110a and 110b - First and second retaining structures

[0085] 112-Spring

[0086] 114-Outer Sleeve

[0087] 115, 117 - Peak-like portions (or the first and second peak-like portions)

[0088] 116, 118, 120 - Valley-like portions (or respectively the first, second, and third valley-like portions)

[0089] 116.1, 116.2 - Relative inclined surfaces of the valley-shaped portions 116

[0090] 118.1, 118.2 - Relative inclined surfaces of the valley-shaped portion 118

[0091] 120.1, 120.2 - Relative inclined surfaces of the valley-shaped portion 120

[0092] 122 - The outer surface or outer surface of the first outer shaft 102

[0093] 122.1 - The outer surface or horizontal surface of the second outer shaft 104

[0094] 400-in Figure 4 The middle indicates the point of instantaneous contact stop of the first linear reciprocating ball 108a.

[0095] 1b - from Figure 1a This part, in Figure 1b Shown in magnified form

[0096] α0, α1, α3, α4, α5 - Diameters of corresponding portions of the first and second outer shafts 102 and 104

[0097] θ0, θ3 - Inclination angles of surfaces 116.1 and 116.2 relative to surface 122.1

[0098] θ1, θ4 - Inclination angles of surfaces 118.1 and 118.2 relative to surface 122.1

[0099] θ2, θ5 - Inclination angles of surfaces 120.1 and 120.2 relative to surface 112.1

[0100] P0 - relative position, i.e., relative to Figure 1a Indicator of the distance between the first and second bottom surfaces 102b and 104b

[0101] P1 - Relative position, i.e., relative toFigure 2 Indicator of the distance between the first and second bottom surfaces 102b and 104b

[0102] P2 - Relative position, i.e., relative to Figure 3 Indicator of the distance between the first and second bottom surfaces 102b and 104b

[0103] P3 - Relative position, i.e., relative to Figure 4 Indicator of the distance between the first and second bottom surfaces 102b and 104b

[0104] VA - along the vertical axis of the dual-purpose stop pin 106

[0105] g0, g1, g2, g3- are respectively Figure 1a , Figure 2 , Figure 3 , Figure 4 The gap between the first and second retaining structures 110a and 110b

[0106] LA1 and LA2 are the transverse axes along axes 102 and 104, respectively.

[0107] t0, t1, t2- Figure 1b The thickness shown in the figure

[0108] r0, r1, r2- Figure 1b The radius of curvature shown in the figure

[0109] U - refers to an upward arrow marker relative to axis 'VA'.

[0110] M - An arrow mark present on the shaft (102 or 104) indicating the direction of the shaft's movement.

Claims

1. A gearbox actuator (100), comprising: First outer axis (102); The second external shaft (104) is positioned parallel to the first external shaft (102); as well as A locking mechanism is configured to prevent unintended horizontal movement of each of the first external shaft (102) and the second external shaft (104) along their respective transverse axes (LA1, LA2), and / or any relative unintended horizontal movement between the first external shaft (102) and the second external shaft (104) along their respective transverse axes (LA1, LA2). The locking mechanism includes a dual-purpose stop pin (106), which comprises: Two linearly reciprocating stop balls (108a, 108b), which are capable of linear reciprocating along the vertical axis (VA) and are located at opposite ends of the dual-purpose stop pin (106), A first retaining structure (110a) and a second retaining structure (110b) are respectively used to retain the two linearly reciprocating stop balls (108a, 108b) and to enable linear reciprocating motion along the vertical axis (VA). The dual-purpose stop pin (106) also includes: A spring (112) is in contact with both the first retaining structure (110a) and the second retaining structure (110b), and is configured to allow at least one of the first retaining structure (110a) and the second retaining structure (110b) and at least one of the two linearly reciprocating stop balls (108a, 108b) to perform linearly reciprocating opposite movements within a predetermined range along the vertical axis (VA). Each of the first outer shaft (102) and the second outer shaft (104) includes at least two peak-shaped portions (115, 117) and at least two valley-shaped portions (116, 118) on its outer surface (122). The feature is that the first peak-shaped portion (115) of each of the first outer shaft (102) and the second outer shaft (104) is separated from the second peak-shaped portion (117) of each of the first outer shaft (102) and the second outer shaft (104) by a first valley-shaped portion (116), and The first diameter (α1, α4) of each of the first outer shafts (102) and the second outer shaft (104) at the first peak portion (115) is different from the second diameter (α2, α5) of each of the first outer shafts (102) and the second outer shaft (104) at the second peak portion (117).

2. The gearbox actuator (100) according to claim 1, wherein, When the spring (112) is in the extended state, the first retaining structure (110a) and the second retaining structure (110b) are separated by a predetermined gap (g0).

3. The gearbox actuator (100) according to claim 1 or claim 2, wherein, The dual-purpose stop pin (106) also includes an outer sleeve (114) to orient or align the two linearly reciprocating stop balls (108a, 108b), the first retaining structure (110a) and the second retaining structure (110b), and the spring (112) along the vertical axis (VA).

4. The gearbox actuator (100) according to claim 1 or claim 2, wherein, The dual-purpose stop pin (106) is configured to prevent at least one of the two external shafts (102, 104) from moving horizontally along their respective transverse axes (LA1, LA2) depending on the relative axial position of one of the two external shafts (102, 104) along its transverse axis (LA1) with respect to the axial position of the other of the two external shafts (102, 104) along its transverse axis (LA2).

5. The gearbox actuator (100) according to claim 4, wherein, The relative axial position of one of the two external shafts (102, 104) relative to the other external shaft along its respective transverse axis (LA1, LA2), or the relative difference between the respective axial positions of the two external shafts along their respective transverse axes (LA1, LA2), is related to the measured physical distance (P0; P1; P2; P3) between the corresponding bottom surfaces (102b, 104b) of the two external shafts (102, 104).

6. The gearbox actuator according to claim 1, wherein, The radius of curvature (r0, r1, r2) and / or depth / thickness (t0, t1, t2) and / or tilt angle (θ0, θ1, θ2, θ3, θ4, θ5) of each of the at least two valley portions (116, 118) of each of the first outer shaft (102) and the second outer shaft (104) is different from or the same as the other.

7. The gearbox actuator according to claim 1, wherein, The two linearly reciprocating stop balls (108a, 108b) of the dual-purpose stop pin (106) are configured to momentarily contact at least one peak-shaped portion (115, 117) and at least one valley-shaped portion (116, 118) of the first external shaft (102) and the second external shaft (104) respectively, when the axial position of at least one of the first external shaft (102) and the second external shaft (104) changes relative to the other external shaft (104). The spring (112) is compressed when at least one of the two linearly reciprocating stop balls (108a, 108b) moves from one of the valley portions of the first outer shaft (102) and the second outer shaft (104) toward one of the peak portions (115, 117) of the first outer shaft (102) and the second outer shaft (104), or is located at one of the peak portions (115, 117) of the first outer shaft (102) and the second outer shaft (104).

8. The gearbox actuator according to any one of claims 1, 6, and 7, wherein, The gaps (g0, g1, g2, g3) between the first retaining structure (110a) and the second retaining structure (110b) of the dual-purpose stop pin (106) change depending on the relative positions of the first external shaft (102) and the second external shaft (104).

9. The gearbox actuator according to claim 8, wherein, When the first linear reciprocating stop ball (108a) of the two linear reciprocating stop balls (108a, 108b) initially engages with the second valley-shaped portion (118) of the first outer shaft (102), and When the first external shaft (102) undergoes a linear translational motion in a first direction (M) parallel to the corresponding transverse axis (LA1), causing the first linear reciprocating stop ball (108a) of the two linear reciprocating stop balls (108a, 108b) to roll toward the first peak-shaped portion (115) or the first valley-shaped portion (116) of the first external shaft (102), The gap (g3) between the first retaining structure (110a) and the second retaining structure (110b) becomes "0mm", that is, a gapless situation occurs.

10. A vehicle transmission or gearbox, the vehicle transmission or gearbox comprising a transmission actuator according to any one of claims 1 to 9.

11. A commercial vehicle comprising a vehicle transmission or gearbox as claimed in claim 10.

12. The use of a transmission actuator according to any one of claims 1 to 9 in a vehicle transmission of a commercial vehicle.

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