Crawler belt and crawler-type vehicle comprising crawler belt
By setting a shoulder at the connection end of the track hinge pin, the problem of pin wandering is solved, achieving high reliability and low-cost manufacturing of the track, which is suitable for heavy-duty applications.
Patent Information
- Application Number
- CN202380088067.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Priority Date
- 2022-12-22
- Filing Date
- 2023-12-21
- Publication Date
- 2025-09-19
AI Technical Summary
In existing tracked vehicles, the pin connections between track links are prone to axial displacement (pin wander), which can lead to compromised mechanical integrity, accelerated wear, and premature track failure. Existing solutions increase component and manufacturing process costs.
A shoulder is provided at the connecting end of the hinge pin, which abuts against the track link of the adjacent track module through the shoulder, thereby preventing or limiting axial displacement of the pin relative to the track link, simplifying the manufacturing process and reducing the impact of wear.
It effectively prevents pin wandering, improves track reliability and service life, reduces manufacturing costs, reduces displacement caused by wear, and is suitable for heavy-load applications.
Smart Images
Figure CN120677100A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to a crawler track for a tracked vehicle, such as a crawler truck, a tank, a bulldozer and other earth-moving machinery and heavy equipment.
[0002] In particular, the invention relates to a device for avoiding or reducing to a negligible extent the phenomenon known as "pin walking". Background Art
[0003] An articulated endless track 1' such as that used in a tractor, a bulldozer or other earth-moving machinery, a heavy equipment or a tank generally comprises a plurality of track modules 2', each track module 2' comprising a first and a second track link 3' arranged side by side, and a plurality of pin assemblies 9' which connect the first track link to the second track link 3' (see FIG. Figure 1 、 Figure 2 ).
[0004] Each pin assembly 9' includes a hinge pin 90' and a kingpin bushing 92'.
[0005] This is achieved by pressing the two opposite ends of each hinge pin 90' into two pin holes 300' machined at the ends of the track links 3' of the adjacent track modules 2' in a press-fit manner, thereby preventing the hinge pin 90' from rotating relative to the track links 3'; in this way, each hinge pin 90' connects the two track links 3' of the track module in the transverse direction.
[0006] Each end of the kingpin bushing 92 ′ is pressed into the bushing holes 310 ′ of the ends of two corresponding track links 3 ′ of the track module 2 ′ where the pin shaft assembly 9 ′ to which it belongs is located in a press-fit manner.
[0007] Since the hinge pin 90' passes through and exceeds its corresponding kingpin bushing 92' in the axial direction and can rotate relative to the bushing 92', each pin assembly 9' can achieve the connection and articulation movement of two adjacent track modules.
[0008] In certain applications of endless track chains such as earthmoving machinery, mining, heavy construction, demolition, waste handling, and forestry, the connection of the articulation pin 90' between two opposing track links 3' can lose structural integrity, causing the pin 90' to axially displace within the pin hole 300' of the track link.
[0009] This phenomenon, known in current technical terms as "pin walking", can have a critical impact on the mechanical integrity of the crawler track 1 ' and can even lead to its premature failure in certain circumstances.
[0010] Even if the hinge pin 90' has not completely come out of a pin hole 300', the axial displacement will reduce the contact surface between the pin end and the pin hole 300', thereby causing the pressure to be concentrated on a smaller contact surface, accelerating the wear of the pin end and the pin hole surface, and shortening the service life of the crawler 1' (see Figure 1 ).
[0011] In extreme cases, when the pin 90' is completely out of the pin hole 300', it still remains engaged with the other track links 3', thereby bearing the stress in a cantilever manner (see FIG. Figure 2 ), causing the entire crawler track 1' to be torn apart quickly.
[0012] A known solution for avoiding or limiting pin wandering is Figure 7 As shown: elastic snap rings 91 are installed at both ends of the hinge pin 90', just outside the respective pin holes 300'; when the pin moves, the snap rings 91 abut against the outside of the crawler link 3', thereby keeping the axial displacement of the pin 90' within a negligible range.
[0013] The inventors of the present invention point out that the first disadvantage of this structure is that each track module requires two additional elastic snap rings 91. Furthermore, each pin 90' must be machined with two annular grooves to accommodate the snap rings 91. These grooves must be machined using a dedicated turning tool separate from the one used to machine the pin's sides. In other words, this structure not only requires multiple additional components, but also requires an additional machining step for all pins 90 in the track, resulting in significant additional costs.
[0014] Furthermore, during operation, the snap ring 90 may contact and be worn by the rims of the idler wheels supporting the track above or below, and eventually become torn or damaged.
[0015] To avoid or limit pin wandering, another known solution is a pin retaining system manufactured by the applicant under the trade name BPR2 (registered trademark), such as Figure 8 As shown, the metal ring 93 is sheathed on the end of the hinge pin 90' by plastic deformation.
[0016] The metal ring 93 is press-fitted into an annular groove 95 which is provided partly on the hinge pin 90 ′ and partly in the pin hole 300 ′ on the track link 3 ′, thereby controlling the axial play of the joint connection within a specific predetermined range.
[0017] In this second solution, the metal ring is less subject to wear by the rollers than in the first known solution, but still suffers from the same other disadvantages as the retaining ring 91, namely the need for a large number of additional parts and dedicated manufacturing steps.
[0018] The object of the present invention is to overcome the shortcomings of the prior art and provide an endless crawler track for a vehicle in which pin migration is unlikely or relatively unlikely to occur. Summary of the Invention
[0019] According to a first aspect of the invention, this object is achieved by a crawler track having the features of the preamble of claim 1, characterized in that each connecting pin end is defined by a shoulder which abuts or is arranged to abut against a corresponding track link of an adjacent track module in order to prevent or limit axial displacement of the articulation pin relative to the track links of the adjacent track module.
[0020] This shoulder immediately stops the pin from wandering and only slightly reduces the contact surface between the two connecting pin ends and their corresponding pin connection seats without affecting the operation, strength and service life of the crawler track.
[0021] This shoulder allows the track to remain in normal operation longer until the pin is detected and repaired.
[0022] The shoulder structure is extremely simple and easy to manufacture (without changing the turning tool or additional processing steps), and can withstand extremely large axial thrust.
[0023] and Figure 7 and Figure 8 Unlike the existing structures shown, this shoulder adds only a very limited amount of cost to the manufacturing process: for example, it can be simply turned using the same turning tool used to machine both sides of the pin, without the need for special tools or additional components to be assembled in the endless track.
[0024] Furthermore, the effect of reducing or preventing pin wandering by the shoulder is not affected by the wear of the endless track in contact with the roller.
[0025] In the event of pin wandering, the shoulder can reliably limit the axial displacement of the pin to be equal to or less than the shoulder width, for example, equal to or less than 0.1-1 mm.
[0026] These advantages are particularly significant in heavy-duty applications such as mining, heavy construction, demolition and waste handling, typically in earthmoving machinery, heavy equipment and forestry.
[0027] According to a second aspect of the invention, this object is achieved by a tracked vehicle having the features of the first aspect of the invention.
[0028] Thanks to the advantages of the shoulders, the tracked vehicle has higher reliability and is less prone to failure.
[0029] In one embodiment of the crawler track of the present invention, the shoulder has a radial width between 0.1 and 1 mm.
[0030] In one embodiment of the crawler track of the present invention, the shoulder has a radial width between 0.3 and 0.8 mm.
[0031] Such a small width helps keep additive manufacturing costs low and simplifies the manufacturing process.
[0032] In a crawler embodiment of the present invention, the edge of the pin connection seat, that is, the part where the shoulder can abut, is basically not chamfered or has a circumferential chamfer, and its radial width or axial depth is preferably equal to or less than the radial width of the shoulder.
[0033] Designs with little or no chamfers reduce the amount of movement due to pin play.
[0034] In a crawler embodiment of the present invention, the edge of the pin connection seat, that is, the part where the shoulder can abut, has a basically rounded or smooth edge, and the average or maximum curvature radius of the edge in the axial section is preferably equal to or less than the radial width of the shoulder.
[0035] The small radius of curvature of this edge in the axial section also helps to reduce displacement caused by pin wandering.
[0036] In a specific embodiment of the crawler track of the present invention, each of the hinge pins is formed with an enlarged central section, which is located between the two connecting pin ends relative to the hinge pin axis; each of the shoulders is axially between the corresponding connecting pin end and the enlarged central section; and the average diameter or maximum diameter of the enlarged central section is significantly larger than the corresponding average diameter or maximum diameter of the connecting pin ends on the same hinge pin.
[0037] In one embodiment of the crawler track of the present invention, the average or maximum diameter of the enlarged central section and / or the connecting pin ends is 20-200 mm, or 30-150 mm.
[0038] In a specific embodiment of the crawler track of the present invention, the total axial length of one or more of the hinge pins is between 80-800 mm or 100-600 mm.
[0039] In a crawler track embodiment of the present invention, each connecting pin end of the hinge pin is assembled into a corresponding pin connection seat in the crawler link (3) of the adjacent crawler track module (2) by means of press fit, drive fit or force fit.
[0040] In one crawler track embodiment of the present invention, each of the hinge pins forms an enlarged central section disposed between two connecting pin ends.
[0041] In one crawler track embodiment of the present invention, one or both connecting pin ends and / or the enlarged central section of the hinge pin have a substantially cylindrical shape.
[0042] Those skilled in the art will more clearly understand the advantages that can be achieved by the present invention through the following detailed description of specific non-limiting embodiments in conjunction with the accompanying schematic diagrams. BRIEF DESCRIPTION OF THE DRAWINGS
[0043] Figure 1 shows a longitudinal section front view of a known endless track subject to pin wandering;
[0044] Figure 2 Shows Figure 1 A longitudinal cross-sectional front view of a known endless track shown in a condition of increased pin wander;
[0045] Figure 3 shows a longitudinal sectional front view of an endless crawler according to one embodiment of the present invention;
[0046] Figure 3A Shows Figure 3 Enlarged view of detail of endless track shown;
[0047] Figure 3B Shows Figure 3A A further enlargement of the detail of the endless track shown;
[0048] Figure 3C Shows Figure 3B A magnified view of the details;
[0049] Figure 4 shows a side view of a track link, viewed from a direction parallel to the axis of rotation of the hinge pin;
[0050] Figure 5 Shows Figure 3 a cross-section of the kingpin bushing in the track shown, the section being taken in an ideal plane passing through the longitudinal axis of the bushing;
[0051] Figure 6 Shows Figure 1 A side view of two track links in the crawler track shown, the two links being articulated with each other, viewed parallel to the axis of rotation of their articulation pins;
[0052] Figure 7 A cross-sectional view showing a known solution for preventing or limiting track pin wandering;
[0053] Figure 8 A cross-sectional view of another known solution for preventing or limiting track pin wandering is shown. DETAILED DESCRIPTION
[0054] Figures 3 to 6 The present invention relates to a crawler according to a specific embodiment.
[0055] The crawler track, generally designated 1, may be used on tracked vehicles such as crawlers, tanks, bulldozers and other earth-moving machinery and heavy equipment, such as those used in mining, heavy construction, demolition and waste disposal.
[0056] The crawler track 1 can be an endless crawler track, that is, a flexible closed ring structure that forms a self-closing loop.
[0057] Such tracked vehicles may be equipped with one or more wheels that roll along the track 1 when the vehicle is traveling or generally moving.
[0058] The crawler track 1 comprises a plurality of crawler track modules 2 which are interconnected and articulated to form a crawler track chain.
[0059] Each track module 2 includes first and second track links 3 arranged side by side, and a plurality of pin assemblies 9 for connecting the first track link 3 to the second track link 3 .
[0060] Each track link 3 may include a link body 11 and a track shoe 13, wherein the track shoe 13 is fixed to the link body (see FIG. Figure 4 ).
[0061] Each link body 11, or more broadly, the track link 3, forms a first end 30 and a second end 31, which are substantially disposed on opposite sides of the link body 11 or the track link 3; in this regard, the link body 11 and / or the track link 3 can have a substantially elongated structure ( Figure 4 ).
[0062] The first end portion 30 forms a pin connection seat 300 .
[0063] The second end portion 31 forms a bushing connection seat 310 .
[0064] The two opposite ends 30 , 31 may be provided in the form of holes of annular cross section.
[0065] Each pin assembly 9 includes a hinge pin 90 .
[0066] Each hinge pin 90 is provided with two connecting pin ends 94 , 96 at both ends thereof, and the two ends are arranged opposite to each other with respect to the middle area of the hinge pin 90 .
[0067] The connecting pin ends 94 , 96 are preferably coaxial with each other and with the longitudinal axis AX of the hinge pin 90 .
[0068] Each connecting pin end 94, 96 and / or the enlarged central section 98 of the pin may have a substantially cylindrical outer shape, for example.
[0069] One or more of the pinned ends 94, 96, or the enlarged central section 98, or the entire hinge pin 90 may have a substantially circular cross-section.
[0070] Each connecting pin end 94 , 96 of the hinge pin 90 is mounted in a corresponding pin connection seat 300 of the track link 3 of the adjacent track module 2 , for example, by press fit, drive fit or force fit.
[0071] Each kingpin bushing 92 ends at two axially opposed connecting bushing ends 922 ( Figure 5 ).
[0072] Each connecting bushing end 922 is installed in a corresponding bushing connection seat 310 of the track link 3 of the track module 2 to which it belongs, for example, by means of press fit, drive fit or force fit.
[0073] The kingpin bushing 92 has a substantially tubular shape, with a length covering at least 0.4 times the total axial length of the hinge pin 90 and accommodating at least a portion of the hinge pin 90 , thereby connecting and articulating the track module 2 containing the pin assembly 9 with the adjacent track module 2 .
[0074] For example, Figure 6 As shown, each pin assembly 9 allows the track links 3 of two adjacent track modules 2 to rotate relative to each other about the longitudinal axis AX of the common hinge pin 90 (see FIG. Figure 6 ).
[0075] The length of the kingpin bushing 92 covers a portion of the total axial length of the hinge pin 90 , preferably 0.4-0.8 times, 0.5-0.7 times, or 0.6-0.7 times.
[0076] Preferably, the kingpin bushing 92 covers at least half or 0.6 times the total axial length of the hinge pin 90 .
[0077] Preferably, the kingpin bushing 92 accommodates at least the enlarged central section 98 of its corresponding hinge pin 90 .
[0078] According to one aspect of the present invention, the connecting pin end 94, 96 of each hinge pin is defined by a shoulder 940 that abuts or is configured to abut a corresponding adjacent / subsequent track link 3, such as against an edge of a corresponding pin connection seat 300, to prevent or limit axial displacement of the hinge pin 90 relative to the track link 3 to which it is connected (see Figure 3B 、 3C ).
[0079] The shoulder 940 has a radial width WSD, preferably between 0.1-1 mm, more preferably 0.3-0.8 mm, 0.4-0.7 mm, 0.4-0.6 mm, for example about 0.5 mm.
[0080] Advantageously, the edge of the pin connection seat 300 against which the shoulder 940 abuts is substantially unchamfered or has a circumferential chamfer, and its radial width or axial depth is preferably equal to or less than the radial width WSD of the shoulder 940 .
[0081] Similarly, if the edge of the pin connection seat 300 against which the shoulder 940 abuts is a rounded or smooth edge, the average or maximum radius of curvature in its axial cross section is preferably equal to or smaller than the radial width WSD of the shoulder 940 .
[0082] This arrangement of the edge of the pin connection seat 300 can limit the maximum axial displacement of the pin 90 through the shoulder 940 when the press-fit connection between the pin 90 and the seat 300 becomes loose (for example, due to wear).
[0083] The shoulder 940 can be obtained, for example, by turning.
[0084] The turning operation to machine the shoulder 940 can be performed simultaneously with the machining of the hinge pin 90 without requiring additional manufacturing steps or tool changes.
[0085] Each hinge pin 90 forms an enlarged central section 98 , which is located axially between the two connecting pin ends 94 , 96 .
[0086] Each shoulder 940 is axially disposed between the corresponding connecting pin end 94 , 96 and the central section 98 .
[0087] The enlarged central section 98 may extend over a portion of the total axial length of the hinge pin 90 , such as 0.4-0.95 times, 0.4-0.9 times, 0.4-0.8 times, 0.5-0.7 times, or 0.6-0.7 times.
[0088] Preferably, enlarged central section 98 has substantially the same overall length as kingpin bushing 92 .
[0089] Preferably, the average or maximum diameter of the enlarged central section 98 is significantly larger than the average or maximum diameter of the connecting pin ends 94 , 96 of the same hinge pin 90 .
[0090] Preferably, the average or maximum diameter of the central section 98 is between 20-200 mm, or between 20-150 mm, 30-70 mm, 70-110 mm, or 110-150 mm.
[0091] Preferably, the average or maximum diameter of the connecting pin ends 94, 96 is between 20-200 mm, or between 20-150 mm, 30-70 mm, 70-110 mm, or 110-150 mm.
[0092] The central section 98 and the connecting pin ends 94 , 96 may have a substantially constant diameter throughout their respective axial lengths.
[0093] The total axial length of the one or more hinge pins 90 is preferably between 80-800 mm, or between 100-200 mm, 200-300 mm, 300-400 mm, 400-500 mm or 500-600 mm.
[0094] The maximum radial thickness WBS of the wall of the kingpin bushing 92 is, for example, 5-50 mm, and the minimum radial thickness is, for example, 5-20 mm.
[0095] Advantageously, the kingpin bushing 92 may have an enlarged midsection 920 and two connected bushing ends 922 having an average or maximum diameter that is smaller than the midsection.
[0096] The enlarged middle section 920 is used to engage with a driving sprocket (not shown) that drives the endless track and is used to withstand the wear of the driving sprocket during operation.
[0097] Each connecting bushing end 922 is separated from the mid-section by a shoulder 924 .
[0098] The shoulder 924 can abut against the edge of the corresponding larger size connecting seat 310 in the crawler link 3 (see Figure 3A ).
[0099] Preferably, the axial end surface of each connecting bushing end portion 922 abuts against the bottom of the shallow groove 301 in the axial direction, and the shallow groove forms one of the edges of the smaller connecting seat 300 .
[0100] In the assembled track 1, each articulation pin 90 is basically and preferably coaxial with its corresponding kingpin bushing 92, and with the following structures: the holes into which the ends 94, 96 of the corresponding pin 90 are inserted, or other pin connection seats 300, bushing connection seats 310; the longitudinal axis AX of the articulation pin 90 is preferably basically perpendicular or, more generally speaking, transverse to the forward direction of the track 1, and / or the ideal plane in which the two track links 3 of the corresponding track module 2 are located.
[0101] The hinge pin 90 , the kingpin bushing 92 , the link body 11 , the track shoe 13 and other components of the crawler track 1 are preferably made of steel or other metal materials.
[0102] A possible example of operation of the crawler track 1 is described below.
[0103] As mentioned above, under normal working conditions, the connecting pin ends 94, 96 of each hinge pin 90 and its corresponding pin connecting seat 300 form an integral structure, for example, by press fit, drive fit or force fit, and these pin connecting seats 300 are processed in the two track links 3 of the track module adjacent to the track module to which the hinge pin 90 belongs.
[0104] The connecting bushing end 922 of each kingpin bushing 92 forms an integral structure with its corresponding bushing connecting seat 310, and these bushing connecting seats 310 are assembled in the same two track links 3 as the track module to which the kingpin bushing 92 belongs, for example, by press fit, drive fit or force fit.
[0105] As previously mentioned, the hinge pin 90 passes through and extends beyond its corresponding kingpin bushing 92 in the axial direction, or longitudinal direction, and because it can rotate relative to the bushing 92, the hinge pin hinges the track module 2 to which it belongs to the adjacent track module 2 so that the two can rotate relative to each other around the pin axis AX.
[0106] Under normal operating conditions, the axial displacement between two adjacent track modules 2 along the pin axis AX may be, for example, a few tenths of a millimeter, such as 0.1 mm, 0.2 mm or 0.4 mm.
[0107] Under abnormal operating conditions, the two pin connection ends 94 , 96 of the hinge pin 90 may become loose and may be displaced relative to their respective connection seats 300 or even detached.
[0108] Initially, the articulation pin 90 may begin to move axially, but then its shoulder 940 will, after a very short axial displacement—for example, only 0.1–0.8 mm—come into contact with the edge of the pin connection seat 300, while the connecting pin end 94 or 96 remains inserted, thereby immediately preventing the pin from wandering; the contact area between the two connecting pin ends 94, 96 and their respective pin connection seats 300 is only slightly reduced, which has no effect on the operation, strength and service life of the crawler track 1.
[0109] The crawler track 1 can still maintain normal operation for a considerable period of time until the pin 90 is detected to be disconnected from the seat 300 and repaired.
[0110] The shoulder 940 is a very simple and strong limit structure that can withstand extremely strong axial thrust.
[0111] and Figure 7 、 Figure 8Unlike the prior art solutions shown, the shoulder 940 of this solution can be formed by simple turning and can be completed using the same tool as the side processing of the pin 90; neither special turning tools nor additional components need to be assembled in the endless track.
[0112] Furthermore, the effect of reducing or preventing pin wandering by the shoulder 940 is not affected by the wear of the track-roller contact.
[0113] Through the above structural design, in the case of pin wandering, the axial displacement of the pin 90 can be reliably limited to be equal to or less than the radial width WSD of the shoulder 940, for example, 0.1-1 mm.
[0114] These advantages are particularly evident in heavy-duty applications such as mining, heavy construction, demolition, waste handling, and general earthmoving, heavy equipment, and forestry machinery.
[0115] The foregoing embodiments may be modified in various ways without departing from the scope of the present invention.
[0116] All construction details may be replaced by technically equivalent elements.
[0117] Expressions similar to “A includes B, C, D” or “A consists of B, C, D” should be understood to cover and disclose the specific case of “A only consists of B, C, D”.
Claims
1. A crawler track (1) comprising a plurality of crawler track modules (2) which are interconnected and articulated to form a crawler track chain, wherein: Each track module (2) comprises first and second track links (3) arranged side by side, and a plurality of pin assemblies (9) for connecting the first track link (3) to the second track link (3), wherein: - Each track link (3) has a first end (30) and an opposite second end (31); - the first end (30) forms a pin connection seat (300); - the second end (31) forms a bushing connection seat (310); – Each pin assembly (9) comprises a hinge pin (90) and a kingpin bushing (92); - Each hinge pin (90) is provided with two oppositely disposed connecting pin ends (94, 96) at its two ends; - Each connecting pin end (94, 96) of the hinge pin (90) is assembled in a corresponding pin connection seat (300) in the crawler link (3) of the adjacent crawler module (2); - Each kingpin bushing (92) is provided with two connecting bushing ends (922) arranged axially opposite to each other at its two ends; - Each connecting bushing end (922) of the kingpin bushing (92) is assembled in a corresponding bushing fitting hole (310) in the crawler link (3) of the crawler module (2) to which it belongs; - the kingpin bushing (92) has a substantially tubular structure, an axial extension length of which is at least 0.4 times the axial length of the hinge pin (90), and covers at least a portion of the hinge pin (90) so as to connect and articulate the track module (2) to which the hinge pin (90) belongs with an adjacent track module (2); Its characteristics are: Each connecting pin end (94, 96) is defined by a shoulder (940) that abuts or is configured to abut against a corresponding track link (3) of an adjacent track module (2) to prevent or limit axial displacement of the hinge pin (90) relative to the track link (3) of the adjacent track module (2).
2. The crawler track according to claim 1, wherein the radial width of the shoulder (940) is between 0.1 and 1 mm.
3. The crawler track of claim 2, wherein the radial width of the shoulder (940) is between 0.3 and 0.8 mm.
4. A crawler according to any of the preceding claims, wherein the edge of the pin connection seat (300) against which the shoulder (940) can abut is substantially unchamfered, or the radial width or axial depth of its circumferential chamfer is preferably equal to or less than the radial width (WSD) of the shoulder (940).
5. A crawler according to any one of the preceding claims, wherein the edge of the pin connection seat (300) is a substantially rounded or smooth edge, and the average or maximum radius of curvature on its axial cross section is preferably equal to or less than the radial width (WSD) of the shoulder (940).
6. A crawler according to any of the preceding claims, wherein each articulation pin (90) has an enlarged central section (98) which is arranged between the two connecting pin ends (94, 96) relative to the axis (AX) of the articulation pin (90), each of the shoulders (940) being axially located between the corresponding connecting pin end (94, 96) and the enlarged central section (98), the average or maximum diameter of the central section (98) being significantly larger than the average or maximum diameter of the connecting pin ends (94, 96) of the same articulation pin (90).
7. The crawler track of claim 6, wherein the average or maximum diameter of the enlarged central section (98) and / or the connecting pin ends (94, 96) is between 20-200 mm or 30-150 mm.
8. A crawler track according to any preceding claim, wherein the total axial length of the one or more hinge pins (90) is between 80-800 mm or 100-600 mm.
9. A crawler track according to any of the preceding claims, wherein each connecting pin end (94, 96) of the hinge pin (90) is assembled in a corresponding pin connection seat (300) in the crawler link (3) of the adjacent crawler module (2) by means of a press fit, a drive fit or a force fit.
10. A crawler track according to any preceding claim, wherein each said hinge pin (90) forms an enlarged central section (98) disposed axially between two connecting pin ends (94, 96).
11. The crawler track of claim 10, wherein one or both connecting pin ends (94, 96) and / or the enlarged central section (98) of the hinge pin (90) have a substantially cylindrical shape.
12. A tracked vehicle comprising one or more tracks (1) according to any one of the preceding claims.