Wheel side reducer suitable for large horsepower heavy tractor

Abstract

The utility model discloses a kind of wheel edge speed reducer suitable for large horsepower heavy tractor, including wheel edge shell, wheel edge gear ring is sleeved in wheel edge shell. Wheel edge gear ring includes coaxial integration setting press mounting guide section, intermediate transition section and spline cooperation section from front to back along the axial direction. Press mounting guide section can press mount wheel edge gear ring to wheel edge shell. Annular groove is opened on the outside wall of intermediate transition section, intermediate transition section is coaxially connected with press mounting guide section and spline cooperation section. The outside wall of spline cooperation section is provided with gear ring outer spline, wheel edge shell is provided with inner spline, spline cooperation section and wheel edge shell are connected by gear ring outer spline and inner spline with spline interference fit. The device of the utility model adopts wheel edge output assembly based on double planetary gears, realizes two-stage transmission under the limitation of limited space size, successfully meets the requirement of 300 horsepower heavy tractor larger transmission ratio and higher power performance.

Description

Technical Field

[0001] This utility model belongs to the field of mechanical processing technology, and relates to speed reducers, specifically to a wheel-side speed reducer adapted to high-horsepower heavy-duty tractors. Background Technology

[0002] The tractor wheel-side reducer is an important component of the tractor drive axle. It is the last stage of reduction and torque amplification device in the tractor transmission system and serves as the direct drive unit for the tractor. Typically, tractors operate in environments such as farmland, where actual operating speeds are relatively low, and they require high power performance and good maneuverability. This necessitates a generally high overall gear ratio and a high ground clearance for the tractor transmission system.

[0003] For the entire drive system of a tractor, when a large low-gear overall gear ratio is used, the torque of structures such as the transmission and drive shaft will also increase accordingly; in order to ensure normal transmission, the structural dimensions of the parts will also increase accordingly. To avoid this situation, it is necessary to maximize the gear ratio distributed to the drive axle. At this time, this larger gear ratio will be mainly borne by the central final drive, which will also generate a large torque, resulting in a large mass and size of the drive axle system, which will not meet the passability requirements of high-horsepower tractors in the working environment. Therefore, in order to achieve a large gear ratio and high ground clearance in the transmission system of high-horsepower tractors, the drive axle is often designed as a two-stage reduction transmission system. That is, while maintaining a single-stage reduction in the central gear, a wheel-side reducer is added in the wheel hub. This not only meets the gear ratio matching of the entire system, but also further achieves the functions of deceleration and torque increase, further improving the driving force requirements of the tractor. However, the existing wheel-side reducers cannot achieve high power performance under the strict space constraints when meeting the drive axle reduction requirements of heavy tractors with more than 300 horsepower. Summary of the Invention

[0004] In view of the shortcomings of the existing technology, the purpose of this utility model is to provide a wheel-side reducer that is suitable for high-horsepower heavy tractors, so as to solve the technical problem that it is difficult to meet the drive axle reduction requirements of heavy tractors with more than 300 horsepower and achieve high power performance under strict space constraints.

[0005] To solve the above-mentioned technical problems, the present invention adopts the following technical solution:

[0006] A wheel-side reducer adapted to a high-horsepower heavy-duty tractor includes a wheel-side housing, wherein a wheel-side gear ring is fitted inside the wheel-side housing.

[0007] The aforementioned wheel-side gear ring includes, from front to back, a coaxially integrated press-fit guide section, an intermediate transition section, and a spline mating section.

[0008] The press-fit guide section can press the wheel-side gear ring into the wheel-side housing.

[0009] An annular groove is provided on the outer wall of the intermediate transition section, and the intermediate transition section coaxially connects the press-fit guide section and the spline mating section.

[0010] The outer wall of the spline mating section is provided with an external spline of the gear ring, and the wheel rim housing is provided with an internal spline. The spline mating section and the wheel rim housing are connected by an interference fit of the external spline of the gear ring and the internal spline.

[0011] This utility model also has the following technical features:

[0012] Specifically, the wheel housing is also fitted with a plurality of double planetary gears. Each double planetary gear includes a sun gear input shaft meshing section and a gear ring meshing section that are coaxially integrated from back to front along the axial direction. The outer diameter of the sun gear input shaft meshing section is larger than the outer diameter of the gear ring meshing section.

[0013] Multiple gear ring meshing sections are also sleeved inside the wheel-side gear ring, and the wheel-side gear ring meshes with the gear ring meshing sections.

[0014] The rear axle main housing is fixed on the axial rear end face of the wheel housing. A sun gear input shaft is also inserted into the axial direction of the rear axle main housing. The sun gear integrated on the sun gear input shaft meshes with multiple sun gear input shaft meshing sections.

[0015] Specifically, a planetary carrier is also fitted inside the wheel housing. The planetary carrier includes a rear support and a front support arranged coaxially from back to front along the axial direction. The axial rear end face of the front support and the axial front end face of the rear support are integrally connected by multiple intermediate connecting columns. The multiple intermediate connecting columns are intermittently arranged along the circumference, and each intermediate connecting column is arranged along the axial direction.

[0016] The rear support has a circular cross-section and multiple axially penetrating planetary pin mounting holes are provided on the rear support. The multiple planetary pin mounting holes are arranged circumferentially.

[0017] The cross-section of the front support is also annular, and each planetary pin mounting hole extends axially through the front support. A planetary pin is coaxially mounted in each planetary pin mounting hole, and the planetary pins correspond one-to-one with the double planetary gears.

[0018] The multiple double planetary gears are axially mounted between the rear support and the front support.

[0019] The inner wall of the front support is also provided with splines along the circumferential direction, and the planetary carrier output shaft is also fitted inside the wheel rim housing. The axial rear end of the planetary carrier output shaft is connected to the front support by splines.

[0020] Specifically, the axial front end of the planetary carrier output shaft extends forward along the axial direction to the outside of the wheel edge housing, and an oil seal is also provided between the axial front end of the wheel edge housing and the planetary carrier output shaft.

[0021] The planetary carrier output shaft is also coaxially fitted with an oil seal cover, which is detachably connected to the wheel edge housing at the front end of the oil seal shaft.

[0022] Specifically, a first tapered roller bearing and a second tapered roller bearing are provided between the planetary carrier output shaft and the wheel housing, and the first tapered roller bearing and the second tapered roller bearing are respectively sleeved on the planetary carrier output shaft.

[0023] The planetary carrier output shaft is also provided with a round nut for pre-tightening the first tapered roller bearing and the second tapered roller bearing, and the round nut is also threadedly connected to the planetary carrier.

[0024] The planetary carrier is also equipped with a resilient cylindrical pin to prevent the round nut from rotating.

[0025] Specifically, a first cylindrical pin is installed on the end face of the axial rear end of the planetary carrier output shaft. The first cylindrical pin is located between the planetary carrier output shaft and the sun gear input shaft, and the axial rear end face of the first cylindrical pin is in contact with the axial front end face of the sun gear input shaft.

[0026] Specifically, a gap is formed between the planetary carrier and the planetary carrier output shaft, and a steel ball and a mating fastener screw are provided in the gap; the fastener screw is inserted into a threaded hole on the end face of the planetary carrier output shaft.

[0027] Specifically, the double planetary gear is also provided with an axially penetrating cylindrical roller bearing mounting hole, in which a cylindrical roller bearing is installed, and in which the axial intermediate section of the planetary pin is also coaxially installed.

[0028] The axial ends of the planetary pin are also mounted on the planet carrier through planetary pin mounting holes.

[0029] Specifically, two second cylindrical pins are symmetrically arranged circumferentially on the end face of the rear axle main housing.

[0030] Specifically, the wheel-side housing has multiple plugs arranged in a circumferential array.

[0031] Compared with the prior art, the present invention has the following beneficial technical effects:

[0032] (I) The device of this utility model adopts a wheel-side output assembly based on a double planetary gear, which realizes two-stage transmission under limited space constraints, successfully meeting the requirements of a large transmission ratio and high power performance of a 300-horsepower heavy tractor. Compared with the prior art, from the perspective of the assembly, the overall structure and transmission system of the 300-horsepower wheel-side output assembly are more reliable, and can undertake the speed reduction and torque increase function of heavy tractors with more than 300 horsepower. At the same time, its speed ratio is larger than that of 200 horsepower. From the perspective of the overall parts layout, the 300-horsepower wheel-side assembly has a higher space utilization rate, realizing two-stage transmission in basically the same space, and achieving a larger transmission speed ratio.

[0033] (II) The 300-horsepower wheel rim in this utility model needs to bear greater torque and bending moment than the 200-horsepower wheel rim in the prior art. The new wheel rim housing has higher strength and a new structure. It has a small module internal spline design inside, that is, a small module external spline design on the outer diameter of the wheel rim gear ring. The small module spline interference fit is adopted, and the wheel rim gear ring is pressed into the wheel rim housing by press fitting to realize the fixed connection between the two parts. The wheel rim gear ring and the wheel rim housing are connected by press fitting, which effectively saves space and realizes two-stage transmission in a limited space, while ensuring the strength of the overall transmission system.

[0034] (III) The device of this utility model uses a double planetary gear, which simplifies the complexity of the entire wheel-side output assembly during transmission, and uses fewer parts to achieve two-stage speed reduction at the wheel-side, effectively reducing the cost of parts and assembly.

[0035] (IV) The 300-horsepower planetary carrier in this utility model is different from the 200-horsepower three-jaw structure in the prior art. It adopts a structure in which the planetary carrier and planetary pins are separated. Its advantage is that the force is more reasonable during the gear meshing process in the power transmission process, which can extend the life of the double planetary gears. The planetary carrier in this utility model has higher strength than the three-jaw structure parts in the prior art, and can meet the needs of the wheel-side output assembly of 300 horsepower and above in the transmission process.

[0036] (V) The planetary carrier output shaft in this utility model device is changed to a split type, and the oil seal cover and the planetary carrier output shaft are divided into two parts. The advantage of this improvement is that it not only facilitates the assembly of the planetary carrier output shaft and makes it easier to control the position of the oil seal, but also facilitates the adjustment of the preload of the first tapered roller bearing and the second tapered roller bearing. Attached Figure Description

[0037] Figure 1 This is a partial structural diagram of the assembly between the wheel rim housing and the wheel rim gear ring in this utility model.

[0038] Figure 2 This is a partial structural diagram of the assembly between the planetary carrier output shaft and the oil seal cover in this utility model.

[0039] Figure 3 This is a schematic diagram of the power transmission and related components in this utility model.

[0040] Figure 4 This is a schematic diagram of the overall structure of the speed reducer in this utility model.

[0041] Figure 5 for Figure 4 A proportionally enlarged structural diagram of point A in the middle.

[0042] Figure 6 This is a schematic diagram of the assembly structure between the wheel-side gear ring, the double planetary gear, and the planetary carrier in this utility model.

[0043] The labels in the diagram represent the following: 1-Wheel rim housing, 2-Wheel rim gear ring, 3-Double planetary gear, 4-Rear axle main housing, 5-Sun gear input shaft, 6-Planet carrier, 7-Planet pin, 8-Planet carrier output shaft, 9-Oil seal, 10-Oil seal cover, 11-First tapered roller bearing, 12-Second tapered roller bearing, 13-Round nut, 14-Elastic cylindrical pin, 15-First cylindrical pin, 16-Steel ball, 17-Clamping screw, 18-Cylindrical roller bearing, 19-Second cylindrical pin, 20-Plug.

[0044] 201-Pressure fitting guide section, 202-Intermediate transition section, 203-Spline mating section.

[0045] 301 - Sun gear input shaft meshing section, 302 - Gear ring meshing section.

[0046] 601-Rear support, 602-Front support, 603-Intermediate connecting column, 604-Planetary pin mounting hole.

[0047] The specific content of this utility model will be further explained in detail below with reference to the embodiments. Detailed Implementation

[0048] It should be noted that, unless otherwise specified, all equipment and components in this utility model are based on existing technologies. For example, the wheel rim housing uses a known wheel rim housing, and the elastic cylindrical pin uses a known elastic cylindrical pin.

[0049] In this utility model, "high horsepower" refers to 300 horsepower and above, and the wheel-side reducer adapted to high horsepower heavy tractors is a tractor wheel-side reducer with speed reduction and torque increase function adapted to heavy tractors with 300 horsepower and above.

[0050] Following the above technical solution, the following are specific embodiments of this utility model. It should be noted that this utility model is not limited to the following specific embodiments, and all equivalent modifications made based on the technical solution of this application fall within the protection scope of this utility model.

[0051] Example:

[0052] This embodiment provides a wheel-side reducer adapted to high-horsepower heavy-duty tractors, such as... Figure 1 As shown, it includes a wheel rim housing 1, and a wheel rim toothed ring 2 is fitted inside the wheel rim housing 1.

[0053] The gear ring 2 includes, from front to back, a coaxially integrated press-fit guide section 201, an intermediate transition section 202, and a spline mating section 203.

[0054] The press-fit guide section 201 can press the wheel-side gear ring 2 into the wheel-side housing 1.

[0055] An annular groove is provided on the outer wall of the intermediate transition section 202, and the intermediate transition section 202 coaxially connects the press-fit guide section 201 and the spline mating section 203.

[0056] The outer wall of the spline mating section 203 is provided with an external spline of the gear ring, and the wheel rim housing 1 is provided with an internal spline. The spline mating section 203 and the wheel rim housing 1 are connected by a spline interference fit through the external spline of the gear ring and the internal spline.

[0057] In this embodiment, the press-fitting of the wheel-side toothed ring 2 can increase the strength of the wheel-side housing 1 and the wheel-side toothed ring 2, save space, and improve space utilization.

[0058] In this embodiment, the advantages of processing the wheel rim housing 1 and the wheel rim gear ring 2 as two separate parts, i.e., the advantage of not designing them as a single part, are: reducing the difficulty of part processing, allowing the wheel rim gear ring 2 to be made of alloy materials, and increasing the service life of the wheel rim gear ring 2.

[0059] As a preferred embodiment of this invention, such as Figure 3 and Figure 4 As shown, a plurality of double planetary gears 3 are also fitted inside the wheel housing 1. Each double planetary gear 3 includes a sun gear input shaft meshing section 301 and a gear ring meshing section 302 that are coaxially integrated from back to front along the axial direction. The outer diameter of the sun gear input shaft meshing section 301 is larger than the outer diameter of the gear ring meshing section 302.

[0060] Multiple gear ring meshing sections 302 are also sleeved inside the wheel-side gear ring 2, and the wheel-side gear ring 2 meshes with the gear ring meshing sections 302.

[0061] The rear axle main housing 4 is fixed on the axial rear end face of the wheel housing 1. The sun gear input shaft 5 is also inserted in the axial direction of the rear axle main housing 4. The sun gear integrated on the sun gear input shaft 5 meshes with multiple sun gear input shaft meshing sections 301.

[0062] In this embodiment, the number of double planetary gears 3 is 3. The sun gear input shaft meshing section 301 and the gear ring meshing section 302 in the double planetary gears 3 are integrated, which reduces the assembly difficulty compared to splitting them into two parts.

[0063] In this embodiment, the rear axle main housing 4 and the wheel side housing 1 are fastened by bolts.

[0064] As a preferred embodiment, a planetary carrier 6 is also fitted inside the wheel housing 1. The planetary carrier 6 includes a rear support 601 and a front support 602 arranged coaxially from back to front along the axial direction. The axial rear end face of the front support 602 and the axial front end face of the rear support 601 are integrally connected by a plurality of intermediate connecting columns 603. The plurality of intermediate connecting columns 603 are intermittently arranged along the circumference, and each intermediate connecting column 603 is arranged along the axial direction.

[0065] The rear support 601 has a circular cross-section and multiple axially penetrating planetary pin mounting holes 604 are provided on the rear support 601. The multiple planetary pin mounting holes 604 are arranged circumferentially.

[0066] like Figure 6 As shown, the cross-section of the front support 602 is also annular. Each planetary pin mounting hole 604 also extends through the front support 602 along the axial direction. Each planetary pin mounting hole 604 contains a planetary pin 7 coaxially mounted. The planetary pin 7 corresponds one-to-one with the double planetary gear 3.

[0067] Multiple double planetary gears 3 are axially mounted between the rear support 601 and the front support 602.

[0068] The inner wall of the front support 602 is also provided with splines along the circumferential direction, and the planetary carrier output shaft 8 is also fitted inside the wheel housing 1. The axial rear end of the planetary carrier output shaft 8 is connected to the front support 602 by splines.

[0069] As a preferred embodiment of this invention, such as Figure 2 As shown, the axial front end of the planetary carrier output shaft 8 extends forward along the axial direction to the outside of the wheel housing 1, and an oil seal 9 is also provided between the axial front end of the wheel housing 1 and the planetary carrier output shaft 8.

[0070] An oil seal cover 10 is also coaxially mounted on the planetary carrier output shaft 8. The oil seal cover 10 is detachably connected to the wheel edge housing 1 at the front end of the oil seal 9.

[0071] In this embodiment, oil seal 9 is a box-type combination oil seal, which improves the sealing effect of the entire reducer. The box-type combination oil seal adopts a commonly used box-type combination oil seal known in the art.

[0072] As a preferred embodiment, a first tapered roller bearing 11 and a second tapered roller bearing 12 are further provided between the planetary carrier output shaft 8 and the wheel housing 1, and the first tapered roller bearing 11 and the second tapered roller bearing 12 are respectively sleeved on the planetary carrier output shaft 8.

[0073] The planetary carrier output shaft 8 is also provided with a round nut 13 for pre-tightening the first tapered roller bearing 11 and the second tapered roller bearing 12. The round nut 13 is also threadedly connected to the planetary carrier 6.

[0074] The planetary carrier 6 is also fitted with a flexible cylindrical pin 14 to prevent the round nut 13 from rotating.

[0075] In this embodiment, a first tapered roller bearing 11 and a second tapered roller bearing 12 are provided between the planetary carrier output shaft 8 and the wheel housing 1 to ensure the reliability of the planetary carrier output shaft 8 during the output process.

[0076] In this embodiment, a round nut 13 for pre-tightening the first tapered roller bearing 11 and the second tapered roller bearing 12 is installed on the planetary carrier output shaft 8, and the preload of the two tapered roller bearings is tested by testing the wheel-side drag torque. Installing the round nut 13 can provide preload to the two tapered roller bearings, effectively ensuring the service life of the two tapered roller bearings and the axial clearance of the planetary carrier output shaft 8.

[0077] In this embodiment, an elastic cylindrical pin 14 is inserted into the planetary carrier 6. The elastic cylindrical pin 14 prevents the round nut 13 from loosening due to vibration during operation, thereby improving the stability of providing preload to the two tapered roller bearings.

[0078] As a preferred embodiment of this invention, such as Figure 5 As shown, a first cylindrical pin 15 is installed on the end face of the axial rear end of the planetary carrier output shaft 8. The first cylindrical pin 15 is located between the planetary carrier output shaft 8 and the sun gear input shaft 5, and the axial rear end face of the first cylindrical pin 15 is in contact with the axial front end face of the sun gear input shaft 5.

[0079] In this embodiment, the axial rear end of the planetary carrier output shaft 8 is the input end of the planetary carrier output shaft 8.

[0080] In this embodiment, a first cylindrical pin 15 is fixed on the end face of the input end of the planetary carrier output shaft 8. The end face of the first cylindrical pin 15 is in contact with the end face of the sun gear input shaft 5. This effectively reduces the risk of damage to the planetary carrier output shaft 8. At the same time, the oil groove on the first cylindrical pin 15 can effectively lubricate, which also reduces the labor and time costs of replacing parts and ensures the accuracy, transmission efficiency and service life of the reducer during use.

[0081] As a preferred embodiment, a gap is formed between the planetary carrier 6 and the planetary carrier output shaft 8, and a steel ball 16 and a fastening screw 17 that cooperates with it are provided in the gap; the fastening screw 17 is inserted into the threaded hole on the end face of the planetary carrier output shaft 8.

[0082] In this embodiment, the axial gap between the planetary carrier 6 and the planetary carrier output shaft 8 is filled by the engagement of the fastening screw 17 and the steel ball 16. According to actual needs, the distance between the planetary carrier output shaft 8 and the planetary carrier 6 can be adjusted by tightening or loosening the fastening screw 17 to meet the degree of freedom of the planetary carrier 6, thereby further improving the reliability of the entire reducer.

[0083] As a preferred embodiment, the double planetary gear 3 is also provided with an axially penetrating cylindrical roller bearing mounting hole, in which a cylindrical roller bearing 18 is installed, and the axial intermediate section of the planetary pin 7 is also coaxially installed in the cylindrical roller bearing 18.

[0084] The two ends of the planetary pin 7 are also mounted on the planet carrier 6 through the planetary pin mounting holes 604.

[0085] In this embodiment, the double planetary gear 3, the cylindrical roller bearing 18, the planetary pin 7, and the planetary carrier 6 constitute the planetary carrier assembly.

[0086] In this embodiment, the planetary carrier assembly is installed inside the wheel housing 1. The planetary carrier 6 and the planetary carrier output shaft 8 transmit power via a spline, and the steel ball 16 is lifted by tightening the locking screw 17. In this embodiment, the locking screw 17 is a hexagonal conical locking screw, which is a commonly known type of hexagonal conical locking screw in the art. The axial position and clearance of the planetary carrier assembly on the planetary carrier output shaft 8 are adjusted by the steel ball 16.

[0087] In this embodiment, the cylindrical roller bearing 18 further ensures the transmission effect.

[0088] In this embodiment, the cylindrical roller bearing 18 is a double-row cylindrical roller bearing, which is a commonly used double-row cylindrical roller bearing known in the art.

[0089] As a preferred embodiment, two second cylindrical pins 19 are symmetrically arranged on the end face of the rear axle main housing 4 in the circumferential direction.

[0090] In this embodiment, two second cylindrical pins 19 are arranged circumferentially on the end face of the rear axle main housing 4, that is, the two second cylindrical pins 19 are arranged symmetrically; when the rear axle main housing 4 is assembled with the wheel-side gear ring 2, the second cylindrical pins 19 play a good guiding role, which facilitates the assembly of the rear axle main housing 4 and the wheel-side gear ring 2.

[0091] As a preferred embodiment, the wheel housing 1 has a plurality of plugs 20 arranged in a circumferential direction.

[0092] In this embodiment, a wheel housing 1 is fitted on the planetary carrier output shaft 8, and multiple plugs 20 are installed on the wheel housing 1 to improve the sealing performance of the overall structure.

[0093] The installation process of the device in this embodiment includes the following steps:

[0094] Step 1: Press the wheel-side toothed ring 2 into the wheel-side housing 1 using a press to fix the two parts together.

[0095] Step two: Hoist the planetary carrier output shaft 8 onto the tooling bracket, place the oil seal 9 into the shaft end, and press it into place using a press. Then, heat-install the inner rings of the first tapered roller bearing 11 and the second tapered roller bearing 12 respectively.

[0096] Step 3: Install the outer rings of the first tapered roller bearing 11 and the second tapered roller bearing 12 onto the wheel housing 1.

[0097] Step 4: Install 3 plugs 20 on the wheel housing 1, hoist the wheel housing 1 and lower it onto the planetary carrier output shaft 8, heat-install the second tapered roller bearing 12, install it in place, and tighten the round nut 13.

[0098] Step 5: Hammer the first cylindrical pin 15 onto the axial rear end of the planetary carrier output shaft 8. Apply 5-6 turns of thread-locking adhesive to the tail of the fastening screw 17 and tighten the fastening screw 17. Apply grease to the steel ball 16 and place it into the ball hole on the planetary carrier output shaft 8. Hammer the elastic cylindrical pin 14 onto the planetary carrier 6. Use a planetary carrier lifting fixture to lift the planetary carrier assembly and lower it into the axial rear end of the planetary carrier output shaft 8, i.e., the spline end of the planetary carrier output shaft 8. At this point, the wheel-side output assembly is formed.

[0099] Step 6: Measure the axial runout of the planetary carrier assembly on the planetary carrier output shaft 8, and adjust the fastening screw 17 to meet the axial runout requirements.

[0100] Step 7: Finally, use bolts to connect the wheel-side output assembly and the rear axle main housing 4 together.

[0101] The working principle of the device in this embodiment is as follows:

[0102] like Figure 3 As shown, power is input from the sun gear input shaft 5. Through the meshing between the sun gear integrated on the sun gear input shaft 5 and the sun gear input shaft meshing section 301 of the multiple double planetary gears 3, the power is transmitted from the sun gear input shaft 5 to the double planetary gears 3. Since the planetary pin 7 and the planet carrier 6 are fixedly connected, the gear ring meshing section 302 of the double planetary gear 3 meshes with the wheel edge gear ring 2. The wheel edge gear ring 2 is press-fitted to the wheel edge housing 1, that is, the wheel edge gear ring 2 is stationary and will not rotate. Therefore, the power is transmitted from the double planetary gear 3 to the planet carrier 6. The planet carrier 6 and the planet carrier output shaft 8 are connected by a spline, and the power is finally transmitted to the planet carrier output shaft 8, realizing the speed reduction and torque increase function.

Claims

1. A wheel-side reducer adapted to a high-horsepower heavy-duty tractor, comprising a wheel-side housing (1), wherein a wheel-side gear ring (2) is sleeved inside the wheel-side housing (1); characterized in that: The wheel-side gear ring (2) includes, from front to back, a press-fit guide section (201), an intermediate transition section (202), and a spline mating section (203) that are coaxially integrated; The press-fit guide section (201) can press the wheel-side toothed ring (2) into the wheel-side housing (1); An annular groove is provided on the outer side wall of the intermediate transition section (202), and the intermediate transition section (202) coaxially connects the press-fit guide section (201) and the spline mating section (203); The outer wall of the spline mating section (203) is provided with an external spline of the gear ring, and the wheel rim housing (1) is provided with an internal spline. The spline mating section (203) and the wheel rim housing (1) are connected by a spline interference fit through the external spline of the gear ring and the internal spline.

2. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 1, characterized in that, The wheel housing (1) is also fitted with a plurality of double planetary gears (3). Each double planetary gear (3) includes a sun gear input shaft meshing section (301) and a gear ring meshing section (302) that are coaxially integrated from back to front. The outer diameter of the sun gear input shaft meshing section (301) is larger than the outer diameter of the gear ring meshing section (302). Multiple gear ring meshing sections (302) are also sleeved inside the wheel-side gear ring (2), and the wheel-side gear ring (2) meshes with the gear ring meshing sections (302); The rear axle main housing (4) is fixed on the axial rear end face of the wheel housing (1). The rear axle main housing (4) is also inserted in the axial direction of the rear axle main housing (4). The sun gear input shaft (5) is integrally set on the sun gear input shaft (5) and meshes with multiple sun gear input shaft meshing sections (301).

3. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 2, characterized in that, The wheel housing (1) is also fitted with a planetary carrier (6). The planetary carrier (6) includes a rear support (601) and a front support (602) arranged coaxially from back to front along the axial direction. The axial rear end face of the front support (602) and the axial front end face of the rear support (601) are integrally connected by multiple intermediate connecting columns (603). The multiple intermediate connecting columns (603) are intermittently arranged along the circumferential direction, and each intermediate connecting column (603) is arranged along the axial direction. The rear support (601) has a circular cross-section and multiple axially penetrating planetary pin mounting holes (604) are provided on the rear support (601). The multiple planetary pin mounting holes (604) are arranged circumferentially. The cross-section of the front support (602) is also annular. Each planetary pin mounting hole (604) also passes through the front support (602) along the axial direction. Each planetary pin mounting hole (604) is coaxially mounted with a planetary pin (7). The planetary pin (7) and the double planetary gear (3) correspond one-to-one. The plurality of double planetary gears (3) are axially mounted between the rear support (601) and the front support (602); The inner wall of the front support (602) is also provided with splines along the circumferential direction, and the planetary carrier output shaft (8) is also sleeved inside the wheel housing (1). The axial rear end of the planetary carrier output shaft (8) and the front support (602) are connected by splines.

4. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 3, characterized in that, The axial front end of the planetary carrier output shaft (8) extends forward along the axial direction to the outside of the wheel edge housing (1), and an oil seal (9) is also provided between the axial front end of the wheel edge housing (1) and the planetary carrier output shaft (8). The planetary carrier output shaft (8) is also coaxially fitted with an oil seal cover (10), and the oil seal cover (10) is detachably connected to the wheel edge housing (1) at the front end of the oil seal (9).

5. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 3, characterized in that, A first tapered roller bearing (11) and a second tapered roller bearing (12) are also provided between the planetary carrier output shaft (8) and the wheel housing (1). The first tapered roller bearing (11) and the second tapered roller bearing (12) are respectively sleeved on the planetary carrier output shaft (8). The planetary carrier output shaft (8) is also provided with a round nut (13) for pre-tightening the first tapered roller bearing (11) and the second tapered roller bearing (12), and the round nut (13) is also threadedly connected to the planetary carrier (6). The planetary carrier (6) is also provided with an elastic cylindrical pin (14) to prevent the round nut (13) from rotating.

6. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 3, characterized in that, A first cylindrical pin (15) is installed on the end face of the axial rear end of the planetary carrier output shaft (8). The first cylindrical pin (15) is located between the planetary carrier output shaft (8) and the sun gear input shaft (5). The axial rear end face of the first cylindrical pin (15) is in contact with the axial front end face of the sun gear input shaft (5).

7. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 3, characterized in that, A gap is formed between the planetary carrier (6) and the planetary carrier output shaft (8), and a steel ball (16) and a fastening screw (17) that cooperates with it are provided in the gap; the fastening screw (17) is inserted into the threaded hole on the end face of the planetary carrier output shaft (8).

8. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 3, characterized in that, The double planetary gear (3) is also provided with an axially through cylindrical roller bearing mounting hole, and a cylindrical roller bearing (18) is installed in the cylindrical roller bearing mounting hole. The axial middle section of the planetary pin (7) is also coaxially installed in the cylindrical roller bearing (18). The two ends of the planetary pin (7) are also mounted on the planet carrier (6) through planetary pin mounting holes (604).

9. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 3, characterized in that, Two second cylindrical pins (19) are symmetrically arranged on the end face of the rear axle main housing (4) in the circumferential direction.

10. The wheel-side reducer adapted for high-horsepower heavy-duty tractors as described in claim 3, characterized in that, The wheel-side housing (1) has multiple plugs (20) arranged in a circumferential direction.

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