Track design method

Abstract

This invention relates to a track design method, which includes: calculating the radial pressure P exerted on the pin sleeve (4) that is pressed into the pin sleeve hole (11) of the track link (1) and has an interference fit with the track link (1). max And the deformation a of the pin sleeve (4) is obtained by finite element analysis; the inner diameter of the end of the pin sleeve (4) inserted into the pin sleeve hole (11) and the outer diameter of the end of the pin shaft (3) sleeved in the pin sleeve (4) located in the pin sleeve hole (11) are designed such that the difference between the inner diameter and the outer diameter is not less than the deformation a, so as to avoid the pin shaft (3) sleeved in the pin sleeve (4) when the pin sleeve (4) is pressed into the pin sleeve hole (11) and deformed.

Description

Technical Field

[0001] This invention relates to the field of track design, and more specifically, to a track design method. Background Technology

[0002] As a core component of excavator track chassis, the reliability of track products directly affects the overall reliability and working efficiency of the machine. Abnormal wear of pins and bushings, leading to track elongation and breakage, is a major failure mode of track products. This failure mode is related to factors such as the pin bushing taper design, the coaxiality of the pins and bushings after track assembly, the amount of grease injected, the selection and sealing effect of the sealing rings, and the compatibility between the track product and the main chassis. Currently, research on the pin bushing taper design and sealing ring reliability testing of track products is not yet mature, and relevant product design and manufacturing standards are lacking. Surveys show that abnormal wear of track pins and bushings is always accompanied by abnormal track noise during installation and commissioning. Therefore, conducting research on the design and manufacturing methods of low-noise engineering track products is a necessary means to improve the reliability of track products. Summary of the Invention

[0003] The present invention aims to provide a track design method to improve the problem of high noise during operation of existing tracks.

[0004] According to one aspect of the present invention, the present invention provides a track design method, comprising:

[0005] Calculate the radial pressure P exerted on the pin bushing that is pressed into the pin bushing hole of the track link and has an interference fit with the track link. max And the deformation 'a' of the pin sleeve was obtained through finite element analysis;

[0006] The inner diameter of the end of the pin sleeve inserted into the pin sleeve hole and the outer diameter of the end of the pin shaft located inside the pin sleeve hole are designed such that the difference between the inner diameter and the outer diameter is not less than the deformation 'a', so as to avoid the pin shaft located inside the pin sleeve when the pin sleeve is pressed into the pin sleeve hole and deforms.

[0007] In some embodiments, calculating deformation includes:

[0008] Calculate the interference δ between the pin sleeve and the track link. max δ max =P max d(C1 / E1+C2 / E2),

[0009] in,

[0010] d is the nominal diameter of the pin sleeve.

[0011] C1 is the stiffness coefficient of the pin bushing.

[0012] C2 is the stiffness coefficient of the track link.

[0013] E1 is the elastic modulus of the pin sleeve.

[0014] E2 is the elastic modulus of the track link.

[0015] In some embodiments, the pressure P is calculated. max include:

[0016] Obtain the pressing force Fi required to press the pin sleeve into the pin sleeve hole of the track link;

[0017] Calculate pressure P max ,Fi=fπdlP max P max =Fi / fπdl,

[0018] f is the coefficient of friction between the pin sleeve and the track link;

[0019] d is the nominal diameter of the pin sleeve;

[0020] l represents the mating length between the pin sleeve and the track link.

[0021] In some embodiments, obtaining the pressure Fi includes:

[0022] Obtain the axial force on the pin sleeve under the ultimate load condition of the track, and use this axial force as the extrusion force F0 that the pin sleeve is pressed out of the pin sleeve hole.

[0023] Calculate the indentation force Fi, where F0 = (1.3ˉ1.5)Fi = (1.3ˉ1.5)fπdlP max ,Fi=F0 / (1.3ˉ1.5).

[0024] In some embodiments, the end of the central hole of the pin sleeve that is inserted into the pin sleeve hole is designed as a tapered hole to avoid the pin shaft sleeved in the pin sleeve when the pin sleeve is pressed into the pin sleeve hole and deforms. The inner diameter of the tapered hole gradually increases in the direction close to the end of the pin sleeve.

[0025] In some embodiments, the length of the tapered hole is consistent with the length of the deformation of the pin sleeve.

[0026] In some embodiments, the coaxiality of the pin holes of the mounting pins or the pin holes of the mounting pins of two track links that are aligned along the length of the track is improved.

[0027] In some embodiments, the pitch of the track link is the distance between the center of the pin sleeve hole and the center of the pin shaft hole of the track link.

[0028] The pitch tolerance of the track link is ±0.1mm; or

[0029] The difference in pitch between two track links that are aligned along the length of the track is ≤0.05mm.

[0030] In some embodiments, the center height of the track link is the distance between the center of the pin hole or the center of the pin sleeve hole and the bolt hole surface of the track link.

[0031] The tolerance for the center height of the track link is ±0.2mm.

[0032] The difference in center height between two track links that are aligned along the length of the track is ≤0.2mm.

[0033] In some embodiments,

[0034] An oil injection head is configured to provide lubricating oil to a pin shaft and a pin sleeve fitted outside the pin shaft. The oil injection head is located at one end of the pin sleeve hole of the track link where the pin sleeve is installed. The oil injection head includes an oil injection head body, a first oil outlet located at the upper end of the oil injection head body to provide lubricating oil to the gap between the pin shaft and the pin sleeve, and a second oil outlet located at the lower end of the oil injection head body below the pin shaft and in the gap between the pin shaft and the pin sleeve to provide lubricating oil.

[0035] In some embodiments,

[0036] An oil passage is provided in the oil injection head body to provide lubricating oil to the first oil outlet and the second oil outlet;

[0037] An vent hole connected to the oil passage is provided on the oil injection head body.

[0038] In some embodiments, the track design method further includes a sealing component fitted between the pin and the track link, wherein,

[0039] If the tracks are driven under normal temperature conditions and the speed is less than 5 km / h, then a sealing ring made of polymer compound material should be selected.

[0040] If the track operating temperature is greater than 200℃, a sealed first disc spring is selected, and the cross-section of the first disc spring is V-shaped.

[0041] If the track travel speed is greater than 10km / h, a sealed second disc spring is selected, and the cross-section of the second disc spring is W-shaped;

[0042] If the track is a lubricated track link, select a combined sealing component, which includes a metal sealing ring and a polymer compound sealing ring connected to the metal sealing ring.

[0043] By applying the technical solution of this application, the difference between the inner diameter of the press-in end of the pin sleeve and the outer diameter of the pin shaft is not less than the deformation a, so as to avoid the pin shaft sleeved in the pin sleeve when the pin sleeve is pressed into the pin sleeve hole and deformed, which helps to reduce the noise caused by the mutual friction between the two.

[0044] Other features and advantages of the invention will become clear from the following detailed description of exemplary embodiments of the invention with reference to the accompanying drawings. Attached Figure Description

[0045] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0046] Figure 1 A schematic diagram of a track design method according to an embodiment of the present invention is shown;

[0047] Figure 2 A schematic diagram of the track structure according to an embodiment of the present invention is shown;

[0048] Figure 3 A schematic diagram of the pin sleeve structure of the track according to an embodiment of the present invention is shown;

[0049] Figure 4 A schematic diagram of the pin sleeve structure of the track according to an embodiment of the present invention is shown;

[0050] Figure 5 A schematic diagram of the track link of an embodiment of the present invention is shown;

[0051] Figure 6 A schematic diagram of the oiling head of the track according to an embodiment of the present invention is shown;

[0052] Figure 7 A cross-sectional schematic diagram of the oiling head of the track according to an embodiment of the present invention is shown;

[0053] Figure 8 A schematic diagram of the pin sleeve and track link of the track according to an embodiment of the present invention is shown;

[0054] Figure 9 A schematic diagram of the structure of an optional first sealing ring for the track according to an embodiment of the present invention is shown;

[0055] Figure 10 A schematic diagram of the optional second sealing ring for the track according to an embodiment of the present invention is shown;

[0056] Figure 11 A schematic diagram of the optional first disc spring of the track according to an embodiment of the present invention is shown;

[0057] Figure 12 A schematic diagram of the optional second disc spring of the track in an embodiment of the present invention is shown;

[0058] Figure 13A schematic diagram of an optional combined sealing component for a track according to an embodiment of the present invention is shown;

[0059] Figure 14 A comparative diagram of the clamping force test of the first and second sealing rings according to an embodiment of the present invention is shown; and

[0060] Figure 15 The results of dynamic running-in comparison of M-type sealing rings according to embodiments of the present invention are shown. Detailed Implementation

[0061] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0062] like Figure 2 As shown, the track includes multiple track link assemblies connected sequentially along its length. Each track link assembly includes two track links 1 arranged side by side along the width direction of the track. The first end of the track link 1 is provided with a pin sleeve hole 11 for mounting a pin sleeve 4, and the second end of the track link 1 is provided with a pin shaft hole 12 for mounting a pin shaft 3. One of two adjacent track link assemblies along the length direction of the track is a first track link assembly, and the other is a second track link assembly. The pin sleeve hole 11 at the first end of the first track link assembly and the pin shaft hole 12 of the second track link assembly are coaxial. The first ends of the two track links of the first track link assembly are located inside the second end of the second track link assembly.

[0063] The track also includes a pin sleeve 4 and a pin 3 passing through the pin sleeve 4. The two ends of the pin sleeve 4 are respectively installed in the pin sleeve holes 11 of the two track links 1 of the first track link assembly. The pin 3 passes through the inner hole of the pin sleeve 4, and the two ends of the pin 3 are respectively installed in the pin shaft holes 12 of the two track links 1 of the second track link assembly.

[0064] Figure 1 A flowchart of the track design method of this embodiment is shown, combined with Figure 1 As shown, in this embodiment, the track design method includes:

[0065] Calculate the radial pressure P exerted on the pin sleeve 4, which is pressed into the pin sleeve hole 11 of the track link 1 and has an interference fit with the track link 1. max And pin sleeve 4 under radial pressure P max The deformation variable a under the action of ;

[0066] The inner diameter of the end of the pin sleeve 4 inserted into the pin sleeve hole 11 is designed to be not less than the outer diameter of the end of the pin shaft 3 located in the pin sleeve hole 11. The difference between the inner diameter and the outer diameter is not less than the deformation a, so as to avoid the pin shaft 3 located in the pin sleeve 4 when the pin sleeve 4 is pressed into the pin sleeve hole 11 and deforms.

[0067] The calculation of deformation variables includes:

[0068] Calculate the interference δ between pin 4 and track link 1. max δ max =P max d(C1 / E1+C2 / E2),

[0069] in,

[0070] d is the nominal diameter of pin sleeve 4.

[0071] C1 is the stiffness coefficient of pin sleeve 4.

[0072] C2 is the stiffness coefficient of track link 1.

[0073] E1 is the elastic modulus of pin 4.

[0074] E2 is the elastic modulus of track link 1.

[0075] Calculate pressure P max include:

[0076] Obtain the pressing force Fi required to press the pin sleeve 4 into the pin sleeve hole 11 of the track link 1;

[0077] Calculate pressure P max ,Fi=fπdlP max P max =Fi / fπdl,

[0078] f is the coefficient of friction between pin 4 and track link 1;

[0079] d is the nominal diameter of pin sleeve 4;

[0080] l is the mating length between pin 4 and track link 1.

[0081] The characteristic feature is that obtaining the pressure Fi includes:

[0082] The force along the axial direction of the pin sleeve 4 under the ultimate load condition of the track is obtained, and this axial force is used as the extrusion force F0 of the pin sleeve 4 pressing out from the pin sleeve hole 11.

[0083] Calculate the indentation force Fi, where F0 = (1.3ˉ1.5)Fi = (1.3ˉ1.5)fπdlP max ,Fi=F0 / (1.3ˉ1.5).

[0084] Combination Figure 3 As shown, the end of the center hole 41 of the pin sleeve 4 that is inserted into the pin sleeve hole is designed as a tapered hole so as to avoid the pin shaft 3 sleeved in the pin sleeve 4 when the pin sleeve 4 is pressed into the pin sleeve hole 11 and deformed. The inner diameter of the tapered hole gradually increases in the direction close to the end of the pin sleeve 4.

[0085] Combination Figure 3 and Figure 4 As shown, the length L1 of the tapered hole is consistent with the length b of the deformation of the pin sleeve 4.

[0086] Specifically, the track design method in this embodiment is as follows:

[0087] Step 1: Using multibody dynamics software such as RecurDyn, establish a model and perform full-condition system load analysis to determine the lateral limit load along the axial direction of the track assembly pin sleeve 4, which is taken as the maximum extrusion force F0 required for the interference fit of the pin sleeve 4. Based on F0 = (1.3~1.5)Fi = (1.3~1.5)fπdlP max The maximum radial pressure P was calculated. max .

[0088] According to δ max =P max d(C1 / E1+C2 / E2), calculate the maximum interference δ between pin 4 and track link 1. max .

[0089] in,

[0090] Fi represents the maximum axial clamping force required for the interference fit.

[0091] f: The coefficient of friction between pin 4 and track link 1;

[0092] d: Nominal diameter of pin sleeve 4 fit;

[0093] l: The mating length between pin sleeve 4 and track link 1;

[0094] C1: Stiffness coefficient of the enclosed pin sleeve;

[0095] C2: Stiffness coefficient of the containment link link;

[0096] E1: Elastic modulus of the material of the enclosed component;

[0097] E2: Elastic modulus of the encapsulating material;

[0098] Step 2 uses finite element analysis to simulate the actual press-fit process. Due to the interference fit between the track link and the pin sleeve 4, the inner hole of the pin sleeve 4 will shrink during press-fitting. Figure 3This diagram illustrates the deformation of a non-tapered pin sleeve during press-fitting. The dashed line represents the pin sleeve structure after press-fitting. To prevent interference between the inner hole of the pin sleeve and the outer diameter of the pin shaft during press-fitting, causing abnormal noise, a taper is designed at both ends of the inner hole of the pin sleeve. This ensures that the diameter of the press-fitting area of ​​the pin sleeve is essentially consistent with the diameter of the middle part of the pin sleeve after press-fitting. Figure 3 The maximum deformation 'a' shown is used as the size of the taper of the inner hole of pin sleeve 4. The distance 'b' from the starting point of the radial deformation of the inner hole of pin sleeve 4 to the end face of the pin sleeve is used as the length of the taper of the inner hole of pin sleeve. The structure of the taper pin sleeve is shown in [reference needed]. Figure 4 .

[0099] Step 2: Due to the interference fit between track link 1 and pin sleeve 4, the inner hole of pin sleeve 4 will shrink during press-fitting. To prevent interference between the inner hole 41 of pin sleeve 4 and the outer circle of pin shaft 3, causing abnormal noise, a taper is designed at both ends of the inner hole of pin sleeve. See the pin sleeve structure below. Figure 4 The actual press-fitting process was simulated by finite element analysis. The radial deformation result of the inner hole of pin sleeve 4 was extracted. The maximum deformation was used as the preliminary design dimension of the taper of the inner hole of pin sleeve 4, and the distance from the starting point of the radial deformation of the inner hole of pin sleeve 4 to the end face of pin sleeve 4 was used as the taper length of the inner hole of pin sleeve 4.

[0100] Interference fit is a key design element, directly affecting the magnitude of radial force and thus determining the deformation 'a'. Because the track link is not a thick-walled cylinder, the above formula cannot accurately describe the specific inner diameter reduction 'a', nor can it calculate the deformation length 'b' of the pin sleeve.

[0101] Therefore, the interference calculated in step 1 is used to design the model fit dimensions of the track link and pin sleeve. In step 2, the specific deformation a and deformation length b under the given interference are analyzed by simulation method.

[0102] Design process:

[0103] Step 1 uses the lateral ultimate load determined by dynamic software as the maximum output force F0.

[0104] The output force is calculated from the input force: Fi = F0 / (1.3 ~ 1.5)

[0105] The radial pressure P on the pin sleeve is calculated from the extrusion force. max =Fi / fπdl

[0106] The interference fit is calculated from the radial pressure.

[0107] δ max =P max d(C1 / E1+C2 / E2)

[0108] The purpose of step 1 is to calculate a reasonable interference fit and determine the model fit dimensions, preparing for the analysis in step 2. It is not necessary to calculate the deformation 'a' using theoretical formulas.

[0109] Step 2 uses the interference calculated in Step 1 to design the model fit dimensions of the track link and pin sleeve, and imports the model into ANSYS for finite element analysis to calculate the deformation a and deformation length b of the pin sleeve under the interference.

[0110] Step 3: To ensure the coaxiality of the pin assembly, the pitch L and center height H dimensions need to be precisely controlled during the machining of the track links. Maintaining consistency in the pitch and center height of the left and right track links within the same batch is especially important when machining on multi-station roughing and finishing boring machines. Specifically,

[0111] 1. The machining tolerance for the pitch of the left and right track links of the track is ±0.1 mm, and the pitch difference is ≤0.05 mm;

[0112] 2. When roughing and finishing the pin mounting holes and pin sleeve mounting holes of the track links, the bolt hole surface of the track link is used as the positioning reference. The machining tolerance of the center height H of the left and right track links of the track is ±0.2, that is, the upper and lower deviations are 0.2mm, and the center height H difference is ≤0.2mm. See the track link structure below. Figure 5 .

[0113] Step 4: To ensure sufficient grease between the track pins and bushings, use a dual-nozzle grease injector 6 (see...). Figure 6 and 7 During installation, the two grease nozzles should be positioned at the top and bottom respectively to prevent the grease from failing to fully fill the upper surface of the pin due to gravity. When the ambient temperature is below 5℃, an insulation device should be added to the outer surface of the grease container to ensure grease flowability. The type of grease should be selected based on the ambient temperature of the host machine. Ordinary lithium-based grease is suitable for temperatures from -20℃ to 120℃. When the ambient temperature is above 120℃, a high-temperature grease should be used; when the ambient temperature is below -20℃, a low-temperature grease should be used to ensure effective lubrication between the bushings.

[0114] Combination Figure 6 and Figure 7 As shown, the oil filling head 6 in this embodiment includes an oil filling head body 61, a first oil outlet 66 located at the upper end of the oil filling head body 61 to provide lubricating oil to the gap between the pin 3 and the pin sleeve, and a second oil outlet 63 located at the lower end of the oil filling head body 61 below the pin 3 and in the gap between the pin sleeve and the pin 4 to provide lubricating oil.

[0115] The oil filling head body 61 is provided with an oil passage that communicates with the first oil outlet 66 and the second oil outlet 63 to provide lubricating oil to the first oil outlet 66 and the second oil outlet 63.

[0116] The oil filling head body 61 is also provided with a vent 65 communicating with the oil passage. In some embodiments, the oil filling head body 61 is also provided with an inner sealing ring 62 and an outer sealing ring 64.

[0117] Step 5: Select the appropriate sealing ring 2 between the pin sleeve 4 and the track link 1 based on different working conditions and main machine model (see...). Figure 8 ). Figure 9 The first sealing ring of type M shown and Figure 10 The M-type second sealing ring 2 shown is suitable for excavators and other mainframes operating at normal temperatures with a travel speed not exceeding 5 km / h. The first and second sealing rings of the M-type are made of polymer compounds, preferably polyurethane. This material makes the sealing ring 2 easily compressible. After compression, the sealing ring 2 fits tightly against the bottom of the countersunk hole of the track link 1 and the end of the pin sleeve 4, resulting in a good sealing effect. However, its high-temperature resistance and wear resistance are relatively poor.

[0118] Figure 11 The first disc spring shown can be used for sealing in environments with high temperatures up to 200°C. Figure 11 The cross-section of the first disc spring shown is V-shaped; Figure 12 The second disc spring shown is suitable for bulldozers and other vehicles with travel speeds exceeding 10 km / h, such as... Figure 12 As shown, the cross-section of the second disc spring is W-shaped.

[0119] The first and second disc springs are made of metal materials 60Si2MnA or 50CrVA, which can withstand high-temperature environments or temperature rise caused by high-speed friction.

[0120] Figure 13 The combined seal shown is used for lubricating the track chains and is widely used on bulldozers to significantly extend the service life of the tracks. Figure 13 As shown, the combined sealing component includes a metal sealing ring and a polymer compound sealing ring connected to the metal sealing ring.

[0121] Using a sealing ring durability test bench and axial reciprocating loading, the reliability of the sealing ring is rapidly verified. By comparing the difference between the compressive force and the restoring force at the same distance, the sealing performance and free movement capability of the sealing ring are verified. Figure 14 The figures represent a comparison of the clamping force tests for two types of M-shaped seals (the left and right figures correspond to the first and second sealing rings, respectively). The horizontal axis represents the compression recovery distance, and the vertical axis represents the clamping force value. The upper line is the compression curve, and the lower line is the recovery curve. By selecting a compression distance value, such as 2.9 mm in the figure, two clamping force values ​​can be obtained. The difference can be referred to the length of the red arrow in the figure. The shorter the arrow length, the better the sealing performance and free movement performance of the seal.

[0122] Using a sealing ring durability testing rig, dynamic testing and verification of sealing ring reliability are achieved through compression-recovery-compression axial loading and rotation angle. By comparing the attenuation of compression force and recovery force, the design rationality and service life of the dynamic sealing ring are quickly verified. The method involves loading the sealing ring sample into the actuating chamber according to the assembly design requirements, applying hydraulic loading to ensure the surface pressure meets the specified range, and then adding mud to the actuating chamber after assembly to simulate actual working conditions, followed by continuous operation for a specified duration. Figure 15 The image shows the results of dynamic running-in comparison of the M-type sealing ring. The reliability of the sealing ring under dynamic conditions is tested. The dynamic reliability of the sealing ring is determined based on the changes in the dynamic test decay curve, the leakage of lithium-based grease at the end of the test, and the wear and deformation of the seal. The smoother the decay, the more reliable the sealing ring is in dynamic use.

[0123] Step 6: Collect the load spectrum of the excavator under various working conditions by using various pressure sensors installed on the excavator, calibrate the simulated load spectrum in the multibody dynamics model, and then import it into the track assembly running-in test bench to verify whether there is abnormal noise from the track. After running continuously for a specified period of time, disassemble the track to detect and analyze the wear amount and wear uniformity of the pins and bushings.

[0124] The above are merely exemplary embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the protection scope of the present invention.

Claims

1. A track design method, characterized in that, include: Calculate the radial pressure P exerted on the pin sleeve (4) that is pressed into the pin sleeve hole (11) of the track link (1) and has an interference fit with the track link (1). max And the deformation a of pin sleeve (4) was obtained through finite element analysis; The inner diameter of the end of the pin sleeve (4) inserted into the pin sleeve hole (11) is designed to be equal to the outer diameter of the end of the pin shaft (3) sleeved in the pin sleeve (4) located in the pin sleeve hole (11). The difference between the inner diameter and the outer diameter is not less than the deformation a, so as to avoid the pin shaft (3) sleeved in the pin sleeve (4) from deforming when the pin sleeve (4) is pressed into the pin sleeve hole (11). The end of the center hole (41) of the pin sleeve (4) that is inserted into the pin sleeve hole is designed as a tapered hole so as to avoid the pin shaft (3) sleeved in the pin sleeve (4) when the pin sleeve (4) is pressed into the pin sleeve hole (11) and deformed. The inner diameter of the tapered hole gradually increases in the direction close to the end of the pin sleeve (4).

2. The track design method according to claim 1, characterized in that, Calculating the deformation includes: Calculate the interference δ between the pin sleeve (4) and the track link (1). max δ max =P max d(C1 / E1+C2 / E2), in, d is the nominal diameter of the pin sleeve (4). C1 is the stiffness coefficient of the pin sleeve (4). C2 is the stiffness coefficient of the track link (1). E1 is the elastic modulus of the pin sleeve (4). E2 is the elastic modulus of the track link (1).

3. The track design method according to claim 1, characterized in that, Calculate the pressure P max include: Obtain the pressing force Fi required for the pin sleeve (4) to be pressed into the pin sleeve hole (11) of the track link (1); Calculate the pressure P max ,Fi=fπdlP max P max = Fi / fπdl, f is the coefficient of friction between the pin sleeve (4) and the track link (1); d is the nominal diameter of the pin sleeve (4); l is the mating length between the pin sleeve (4) and the track link (1).

4. The track design method according to claim 3, characterized in that, Obtaining the pressure Fi includes: The force along the axial direction of the pin sleeve (4) under the ultimate load condition of the track is obtained, and the axial force is used as the extrusion force F0 of the pin sleeve (4) pressing out of the pin sleeve hole (11). Calculate the indentation force Fi, where F0 = (1.3~1.5)Fi = (1.3~1.5) fπdlP max ,Fi = F0 / (1.3~1.5).

5. The track design method according to claim 1, characterized in that, The length (L1) of the tapered hole is consistent with the length (b) of the deformed pin sleeve (4).

6. The track design method according to claim 1, characterized in that, Improve the coaxiality of the pin holes (12) for mounting the pin shaft (3) or the pin holes (11) for mounting the pin sleeve (4) of the two track links (1) that are aligned along the length direction of the track.

7. The track design method according to claim 6, characterized in that, The pitch (L) of the track link (1) is the distance between the center of the pin sleeve hole (11) and the center of the pin shaft hole (12) of the track link (1). The pitch tolerance of the track link (1) is ±0.1 mm; or The difference in pitch (L) between two track links (1) that are aligned along the length of the track is ≤0.05mm.

8. The track design method according to claim 6, characterized in that, The center height (H) of the track link (1) is the distance between the center of the pin hole (12) or the center of the pin sleeve hole (11) and the bolt hole surface (13) of the track link (1). The tolerance for the center height of the track link (1) is ±0.2mm; The difference in center height (H) between two track links (1) that are aligned along the length of the track is ≤0.2mm.

9. The track design method according to claim 1, characterized in that, An oiling head (6) is configured to provide lubricating oil to the pin (3) and the pin sleeve (4) sleeved outside the pin (3). The oiling head (6) is located at one end of the pin sleeve hole (11) of the mounting pin sleeve (4) of the track link (1). The oiling head (6) includes an oiling head body (61), a first oil outlet (66) located at the upper end of the oiling head body (61) to provide lubricating oil to the gap between the pin (3) and the pin sleeve above, and a second oil outlet (63) located at the lower end of the oiling head body (61) to provide lubricating oil to the gap between the pin (3) and the pin sleeve (4) below.

10. The track design method according to claim 9, characterized in that, The oil injection head body (61) is provided with an oil passage that communicates with the first oil outlet (66) and the second oil outlet (63) to provide lubricating oil to the first oil outlet (66) and the second oil outlet (63); An exhaust port (65) communicating with the oil passage is provided on the oil injection head body (61).

11. The track design method according to claim 1, characterized in that, It also includes a sealing component (2) fitted between the pin (3) and the track link (1), wherein, If the track is driven under normal temperature conditions and the speed is less than 5 km / h, a sealing ring made of polymer compound material shall be selected. If the operating temperature of the track is greater than 200℃, a sealed first disc spring is selected, and the cross-section of the first disc spring is V-shaped. If the track travel speed is greater than 10km / h, a sealed second disc spring is selected, and the cross-section of the second disc spring is W-shaped. If the track is a lubricated track link, a combined sealing component is selected, which includes a metal sealing ring and a polymer compound sealing ring connected to the metal sealing ring.

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