A shift transmission for a cotton picker spindle

Abstract

The application discloses a shift gearbox for a cotton picker picking spindle, which is provided with a three-in-one sun gear, a power cut-off brake, a high-speed clutch and a planetary transmission structure in transmission connection with the three-in-one sun gear on a power input shaft, and a low-speed brake capable of switching the transmission state of the high-speed clutch. The shift gearbox of the application realizes the switching of the transmission state among the high-speed clutch, the planetary transmission structure and the low-speed brake in a more compact manner through the three-in-one sun gear structure, can transmit greater torque, and can directly cut off the input power through the power cut-off brake, so that the system transmission efficiency and light weight are improved.

Description

Technical Field

[0001] This application relates to the field of cotton harvesting equipment, and more specifically to a shift gearbox for cotton harvester spindles. Background Technology

[0002] In recent years, with rising labor costs, cotton harvesting has largely been replaced by machines. The advantages of cotton harvesters—high efficiency and relatively low cost compared to manual labor—are becoming increasingly apparent. The gearbox is a key transmission component of the cotton harvester spindle. Currently, domestic cotton harvesters cannot achieve the function of shifting gears while operating, which seriously affects the fuel economy of cotton harvesters, provides a poor driving experience for operators, severely impacts work efficiency, and is one of the key factors contributing to the high cost of cotton harvesters.

[0003] Existing hydraulic shift transmissions either require both the hydraulic actuator and the hydraulic clutch to be engaged, or they require separate braking systems on the output shafts of the differential lock.

[0004] For designs requiring both the hydraulic actuator and hydraulic clutch to be engaged, the brake is directly bolted to the housing. Hydraulic pressure locks the outer brake drum to the intermediate brake drum, which is then fixed to the planetary gear carrier. Further hydraulic pressure locks the inner drum to the intermediate drum, restricting the rotation of the output transmission gears. This hydraulic control method generates significant friction between the brake drum layers, makes the hydraulic control system complex, and generates considerable heat during braking, affecting the lifespan of each brake drum layer.

[0005] For schemes that require the installation of braking systems on the left and right output shafts of the differential lock, the mechanical structure is complex and requires the reservation of assembly space for the brakes on both sides, which is not conducive to system integration and miniaturization.

[0006] Furthermore, when the gearbox switches between high and low speeds, constraints are generated between the planetary carrier and the sun gear, and between the planetary carrier and the stationary housing. During this process, unbalanced axial forces are generated on the output gears due to gear constraints, which can damage the transmission system and affect its transmission efficiency. Summary of the Invention

[0007] This application addresses the shortcomings of existing technologies by providing a shift gearbox for cotton harvester spindles. Based on a three-section sun gear, this application offers a shift gearbox with a more compact overall structure and greater torque transmission. It can cut off input power, more flexibly and efficiently improve system transmission efficiency, and achieve lightweighting of the cotton harvester spindle transmission system. The specific technical solution adopted in this application is as follows.

[0008] First, to achieve the above objectives, a shift gearbox for a cotton harvester spindle is proposed. The shift gearbox is positioned in the transmission path between the power output mechanism and the cotton harvester spindle, and includes: a power input shaft, one end of which is connected to the power output mechanism of the cotton harvester to receive driving torque; a triple-spindle sun gear, which is bearing-connected to the power input shaft and has a brake external spline, an output gear, and a transmission gear integrated as a single unit; a power cut-off brake, which restricts the rotation of the triple-spindle sun gear when coupled with the brake external spline, and allows the triple-spindle sun gear to output torque from the power input shaft when the coupling with the brake external spline is released; and a high-speed clutch, which, in the first fluid... In the first hydraulic state, the power input shaft is coupled with the power transmission, driving the planetary transmission structure and the high-speed clutch, which are mounted on the power input shaft, to operate synchronously. The planetary transmission structure is synchronously connected to the power input shaft, driving the output gear to output the torque of the power input shaft. The low-speed brake, in the second hydraulic state, is coupled with the high-speed clutch to restrict the transmission between the high-speed clutch and the power input shaft. The high-speed clutch remains synchronized with the planetary transmission structure, causing the planetary transmission structure to switch to a configuration where the planetary gears inside it couple the transmission gears of the three-linked sun gear on the power input shaft. The planetary gears drive the output gear to reduce speed and output torque. The first hydraulic state and the second hydraulic state are triggered independently.

[0009] Optionally, in any of the above-described shift gearboxes for cotton picker spindles, when the first hydraulic state is deactivated, the high-speed clutch is decoupled from the power input shaft, and the operating states between the power input shaft and the high-speed clutch, and between the power input shaft and the planetary transmission structure, are independent of each other.

[0010] Optionally, in the shift gearbox for cotton picker spindles as described above, when the second hydraulic state is deactivated, the low-speed brake is decoupled from the high-speed clutch, and the operating states of the power input shaft and the low-speed brake are independent of each other.

[0011] Optionally, in any of the above-described gearboxes for cotton harvester spindles, the high-speed clutch includes: a spline sleeve fixedly connected to the power input shaft and rotating synchronously with it; a high-speed clutch pressure plate movably disposed outside the spline sleeve, the outer periphery of the high-speed clutch pressure plate having a coupling protrusion extending radially therefrom; and a high-speed clutch friction plate, the inner periphery of which has a first toothed structure coupled to the outer peripheral surface of the spline sleeve, the first toothed structure being movably disposed outside the spline sleeve, the high-speed clutch friction plate and the high-speed clutch pressure plate being alternately arranged; the high-speed clutch... The high-speed clutch housing is disposed outside the high-speed clutch pressure plate and the high-speed clutch friction plate, and a first sliding groove parallel to the power input shaft is provided on the high-speed clutch housing, in which the coupling protrusion is accommodated; a first piston ring is disposed between the bottom of the high-speed clutch housing and the high-speed clutch pressure plate, for supplying hydraulic pressure, so as to drive the high-speed clutch friction plate and the high-speed clutch pressure plate to move along the first sliding groove toward the spline sleeve in the first hydraulic state, so that the inner ring of the high-speed clutch pressure plate is coupled with the outer circumference of the spline sleeve, and the high-speed clutch pressure plate, spline sleeve, high-speed clutch housing and power input shaft operate synchronously.

[0012] Optionally, in the shift gearbox for cotton picker spindles as described above, the high-speed clutch housing is fixedly connected to the planetary carrier of the planetary transmission structure and maintains synchronous rotation; the planetary gear is disposed in the planetary carrier and is drively connected between the power input shaft and the transmission gear of the triple sun gear.

[0013] Optionally, in the shift gearbox for cotton picker spindle removal as described above, the power cut-off brake is located at one end of the power input shaft, and the low-speed brake is located at the other end of the power input shaft. Both the power cut-off brake and the low-speed brake are connected to the gearbox housing. The actuating components in the power cut-off brake and the low-speed brake slide axially along the power input shaft to switch their coupling states.

[0014] Optionally, in the shift gearbox for cotton harvester spindles as described above, the triple sun gear, planetary transmission structure, and high-speed clutch are arranged along the power input shaft between the power cut-off brake and the low-speed brake; wherein the triple sun gear is arranged along the power input shaft near the power cut-off brake; the high-speed clutch is arranged along the power input shaft near the low-speed brake; the planetary transmission structure is arranged between the triple sun gear and the high-speed clutch; and the power cut-off brake, triple sun gear, planetary transmission structure, high-speed clutch, and low-speed brake are all coaxially arranged with the power input shaft.

[0015] Optionally, in the shift gearbox for cotton harvester spindles as described above, the low-speed brake includes: a low-speed brake housing fixedly connected to the gearbox housing, wherein a second groove parallel to the power input shaft is provided inside the low-speed brake housing; a second pressure plate movably disposed between the low-speed brake housing and the power input shaft, wherein a brake cam is formed on the outer periphery of the second pressure plate extending radially therefrom; a second friction plate movably disposed between the low-speed brake housing and the power input shaft, alternating with the second pressure plate; and a second piston ring disposed between the bottom of the low-speed brake housing and the second pressure plate, for supplying hydraulic pressure to drive the brake cam and the second friction plate to move along the second groove toward the high-speed clutch under a second hydraulic pressure state, thereby tightly coupling the second pressure plate and the second friction plate with the bottom of the high-speed clutch housing, maintaining coupling between the high-speed clutch, the second pressure plate, the second friction plate, and the low-speed brake housing, and maintaining synchronous fixation with the gearbox housing.

[0016] Optionally, in the shift gearbox for cotton picker spindles as described above, the low-speed brake further includes a shim and a disc spring between the second pressure plate and the bottom surface of the high-speed clutch housing; the inner ring of the second pressure plate and the second friction plate is further provided with inner and outer ring needle roller bearings, which are located on the outer periphery of the power input shaft, between the power input shaft and the second pressure plate and the second friction plate.

[0017] Optionally, in the shift gearbox for cotton harvester spindles as described above, the power cut-off brake includes: a first pressure plate and a first friction plate alternately arranged along the axial direction of the brake external spline; the first pressure plate and the first friction plate are movably disposed outside the brake external spline, a fixing protrusion is formed on the outer periphery of the first pressure plate extending radially therefrom, and a second toothed structure coupled to the outer peripheral surface of the brake external spline is provided on the inner periphery of the first friction plate along its radial direction; when the second toothed structure is coupled to the outer peripheral surface of the brake external spline, the fixing protrusion keeps the first pressure plate and the gearbox housing synchronously fixed.

[0018] Beneficial effects

[0019] This application provides a shift gearbox for cotton harvester spindles, which has a triple-sun gear, a power cut-off brake, a high-speed clutch and a planetary transmission structure connected to the triple-sun gear on the power input shaft, and a low-speed brake capable of switching the high-speed clutch transmission state. The shift gearbox of this application, through the triple-sun gear structure, achieves switching between the high-speed clutch, planetary transmission structure, and low-speed brake in a more compact manner, enabling the transmission of greater torque. It can also directly cut off the input power through the power cut-off brake, achieving the goals of improving system transmission efficiency and weight reduction.

[0020] In this application, the planetary transmission structure housing is fixedly connected to the high-speed clutch housing. The transmission mode between the high-speed clutch and the planetary transmission structure can be switched by the different sliding states of the pressure plate inside the high-speed clutch under hydraulic oil. On the one hand, the nested transmission system with coaxial arrangement between the two, in conjunction with the triple sun gear, compresses the transmission distance and improves the transmission efficiency. On the other hand, the planet carrier, planetary gears and triple sun gear can be directly locked into one unit by the coupling of the high-speed clutch pressure plate, realizing the direct output of the driving torque of the power input shaft and improving the maximum speed output of the spindle.

[0021] In the triple sun gear of this application, the output gear and the transmission gear can be realized through two sets of helical gears with opposite rotation directions. This allows for the transmission of large torque while simultaneously counteracting the axial force applied to the triple sun gear, effectively preventing damage to the transmission system. Therefore, in the shift gearbox of this application, the triple sun gear is only subjected to radial force. When selecting bearings to match it, only bearings subjected to radial force need to be considered. The bearing connection between the triple sun gear and the power input shaft is directly achieved through double-row cylindrical roller bearings and needle roller bearings without inner or outer rings, effectively reducing bearing usage costs.

[0022] Furthermore, this application improves the structure of the friction plate in the high-speed clutch. By adding grooves connecting to the inner ring on the front and rear friction end faces of the high-speed clutch friction plate, an oil guide passage connecting to the first tooth structure on the outer peripheral surface of the spline sleeve can be formed when the high-speed clutch is engaged, thereby increasing the amount of hydraulic oil on the front and rear friction end faces of the friction plate. The addition of crisscrossing grooves ensures sufficient oil intake and increases the contact area between the oil and the friction plate. The mesh-like slotting method allows the hydraulic oil to quickly reach all directions, thereby effectively increasing the amount of oil entering the friction plate and the hydraulic oil flow rate, further reducing the surface temperature of the high-speed clutch friction plate, reducing the temperature of the friction plate during gear shifting, and reducing drag torque loss. This allows the oil to enter and exit quickly, ultimately improving the lifespan of the friction plate and even the gearbox.

[0023] Other features and advantages of this application will be set forth in the following description, and will be apparent in part from the description, or may be learned by practicing this application. Attached Figure Description

[0024] The accompanying drawings are provided to further illustrate the present application and form part of the specification. Together with the embodiments of the present application, they serve to explain the present application but do not constitute a limitation thereof. In the drawings:

[0025] Figure 1 This is an exploded view of the shift gearbox used in the cotton harvester spindle removal mechanism of the present invention.

[0026] Figure 2This is a cross-sectional view of the shift gearbox of the present invention.

[0027] Figure 3 This is a schematic diagram illustrating the low-speed power transmission principle of the shift gearbox of the present invention.

[0028] Figure 4 This is a schematic diagram illustrating the power transmission principle of the high-speed gearbox of the present invention.

[0029] Figure 5 This is a schematic diagram of the triple sun gear used in this invention.

[0030] Figure 6 This is a schematic diagram of the structure of the high-speed clutch friction plate used in this invention;

[0031] Figure 7 This is a schematic diagram showing the assembly state of the high-speed clutch friction plate in the shift gearbox of the present invention.

[0032] In the diagram, 1 represents the first pressure plate; 2 represents the first friction plate; 3 represents the double-row cylindrical roller bearing; 4 represents the triple sun gear; 41 represents the brake external spline; 42 represents the output gear; 43 represents the transmission gear; 5 represents the power input shaft; 6 represents the needle roller bearing without inner and outer rings; 7 represents the spline sleeve; 8 represents the high-speed clutch pressure plate; 9 represents the high-speed clutch friction plate; 10 represents the first piston ring; 11 represents the high-speed clutch housing; 12 represents the gasket; 13 represents the needle roller bearing with inner and outer rings; 14 represents the disc spring; 15 represents the second pressure plate; 16 represents the second friction plate; 17 represents the release plate; 18 represents the second piston ring; 19 represents the low-speed brake housing; 20 represents the stop pin; 21 represents the planetary gear shaft; 22 represents the thrust washer; 23 represents the ball bearing; 24 represents the spacer ring; 25 represents the planetary carrier; 26 represents the planetary gear; and 27 represents the hexagonal bolt. Detailed Implementation

[0033] To make the objectives and technical solutions of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this application. All other embodiments obtained by those skilled in the art based on the described embodiments of this application without creative effort are within the scope of protection of this application.

[0034] Those skilled in the art will understand that, unless otherwise defined, all terms used herein (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains. It should also be understood that terms such as those defined in general dictionaries should be understood to have the meaning consistent with their meaning in the context of the prior art, and should not be interpreted in an idealized or overly formal sense unless defined as herein.

[0035] In this application, "inner" and "outer" refer to the direction from the outer wall of the gearbox to the center of the internal power input shaft, relative to the gearbox itself, and vice versa; rather than a specific limitation on the device mechanism of this application.

[0036] The terms "front" and "rear" as used in this application refer to the direction from the power cut-off brake to the low-speed brake when the user is facing the gearbox itself, which is the rear direction, and the direction from the low-speed brake housing to the first pressure plate, which is the front direction, rather than a specific limitation on the device mechanism of this application.

[0037] The term "connection" as used in this application can mean a direct connection between components or an indirect connection between components through other components.

[0038] Figure 1 According to this application, a shift gearbox for a cotton harvester spindle is provided. It is positioned in the transmission path between the power output mechanism and the cotton harvester spindle, and features a two-speed power shift mechanism. This mechanism is compact, transmits high power, and can also perform power splitting. The two-speed power shift mechanism works in conjunction with a clutch and brake within the gearbox to achieve different gear ratios, thereby changing the transmission ratio and obtaining a wide speed range, enabling the cotton harvester to meet various operating conditions.

[0039] Specifically, the shift gearbox includes Figure 1 as well as Figure 2 Shown:

[0040] The power input shaft 5 has one end connected to the power output mechanism of the cotton harvester for transmission, and receives the driving torque.

[0041] The triple sun gear 4 is connected to the power input shaft 5 bearing and has a brake external spline 41, an output gear 42 and a transmission gear 43 connected as a whole.

[0042] The power cut-off brake consists of a first pressure plate 1 and a first friction plate 2, which are sleeved on the outer periphery of the brake external spline 41 at the front end of the triple sun gear 4. It is used to restrict the rotation of the triple sun gear 4 by coupling the first pressure plate 1 with the brake external spline 41 and by using the convex limiting structure of the outer ring of the first pressure plate 1. When the coupling with the brake external spline is removed, the triple sun gear 4 is driven by the power input shaft 5 to output torque.

[0043] The high-speed clutch mainly consists of a splined sleeve 7, a high-speed clutch pressure plate 8, a high-speed clutch friction plate 9, a first piston ring 10, and a high-speed clutch housing 11. In the first hydraulic state, the high-speed clutch is coupled to the power input shaft 5 via the high-speed clutch pressure plate 8, and through its high-speed clutch housing 11, drives the planetary transmission structure sleeved on the power input shaft 5 to operate synchronously with the high-speed clutch. This ensures that the planetary transmission structure is synchronously connected to the power input shaft 5 and operates according to... Figure 4 The output gear 42 is driven to output torque to the power input shaft 5 in the manner shown; when the first hydraulic state is removed, the high-speed clutch is decoupled from the power input shaft 5, and the operating states between the power input shaft 5 and the high-speed clutch, and between the power input shaft 5 and the planetary transmission structure are independent of each other.

[0044] The low-speed brake mainly consists of a washer 12, inner and outer ring needle roller bearings 13, a disc spring 14, a second pressure plate 15, a second friction plate 16, a release plate 17, a second piston ring 18, and a low-speed brake housing 19. The second pressure plate 15 of the low-speed brake is coupled to the low-speed brake housing 19 and the high-speed clutch under a second hydraulic state. Figure 3 The method shown achieves power output through the output gear on the triple sun gear, restricting the transmission between the high-speed clutch and the power input shaft 5. This allows the high-speed clutch to restrict the planetary transmission structure to remain synchronized with it, causing the planetary transmission structure to switch to coupling the transmission gear 43 of the triple sun gear 4 on the power input shaft 5 with its internal planetary gear 26. The planetary gear 26 drives the output gear 42 to reduce the output torque. When the second hydraulic state is revoked, the low-speed brake is decoupled from the high-speed clutch, and the operating states of the power input shaft 5 and the low-speed brake are independent of each other.

[0045] In this application, the first hydraulic state and the second hydraulic state can be independently triggered by the first piston ring 10 and the second piston ring 18 in the high-speed clutch and the low-speed brake, respectively, to achieve power output at different gears. When the low-speed brake is adjusted to the braking state by hydraulic oil, and the high-speed clutch is adjusted to the state that limits the planetary transmission structure to maintain synchronous operation with the high-speed clutch by hydraulic oil, there is partial coupling between the power input shaft 5 and the output gear 42. In the second hydraulic state, the low-speed brake is coupled to the high-speed clutch housing 11.

[0046] For details, please refer to the following: Figure 5 As shown, in the shift gearbox of this application, the brake external spline 41 of the triple sun gear 4 can be provided with a toothed structure parallel to the axis of the power input shaft 5. This toothed structure is slidably connected to the inner circumference of the first friction plate 2, and can restrict the rotation of the brake external spline 41 by coupling the outer convex limiting structure of the outer ring of the first pressure plate 1 with the sliding groove on the inner wall of the shift gearbox, thereby cutting off the power output of the gearbox. The output gear 42 and the transmission gear 43 can be configured as two sets of helical gears with opposite directions of rotation. In the triple sun gear 4, a double row cylindrical roller bearing 3 can be provided between the inner ring of the output gear 42 and the power input shaft 5, and a needle roller bearing without inner and outer rings 6 can be provided between the transmission gear 43 and the power input shaft 5. Because the output gear 42 and the transmission gear 43 rotate in opposite directions, their axial forces can cancel each other out, effectively avoiding damage to the transmission system from a single axial force. This allows the triple sun gear to be subjected only to radial force, and when selecting bearings to match it, only bearings subjected to radial force need to be considered. The bearing connection between the triple sun gear and the power input shaft is achieved directly through double-row cylindrical roller bearings and needle roller bearings without inner or outer rings, effectively reducing bearing usage costs. Specifically... Figure 6 For example, the output gear 42 and the transmission gear 43 of this triple sun gear are coaxially driven. The shaft diameter at the transmission gear 43 can be denoted as d1, and the shaft diameter at the output gear 42 can be denoted as d2. The input torque of the shaft is T, the helix angle of the transmission gear 43 is β, and the helix angle of the output gear 42 is β'. Decomposing the forces acting on the helical gears, the radial force F1 at the transmission gear 43 and the radial force F2 at the output gear 42 are respectively:

[0047]

[0048]

[0049] To eliminate the harmful effects of axial forces on the shaft, the two axial forces should cancel each other out, therefore the following conditions must be met:

[0050] F1 = F2

[0051] Right now:

[0052]

[0053] Therefore, the helix angles of the two helical gears should satisfy:

[0054]

[0055] In addition, the external spline at the front end of the aforementioned triple sun gear 4 can also be configured to cooperate with the first pressure plate and the first friction plate to achieve the function of cutting off power. The aforementioned triple sun gear 4 uses helical gear transmission, which not only can transmit large torque, but also reduces the number of gear teeth compared with spur gear transmission, making the overall structure more compact, greatly optimizing the transmission route, and improving transmission efficiency. At the same time, it further reduces the size of the gearbox, achieving the goal of lightweighting, and also plays a certain role in optimizing energy conservation and emission reduction.

[0056] In a more specific implementation, the high-speed clutch of this application may be configured to include:

[0057] The spline sleeve 7 is fixedly connected to the power input shaft 5 and rotates synchronously with the power input shaft 5;

[0058] The high-speed clutch pressure plate 8 is movably disposed outside the spline sleeve 7. The outer periphery of the high-speed clutch pressure plate 8 extends radially to form a coupling protrusion. The inner periphery of the high-speed clutch friction plate 9 is provided with a first tooth structure coupled to the outer periphery of the spline sleeve 7. Both the high-speed clutch pressure plate 8 and the high-speed clutch friction plate 9 can slide back and forth along the first tooth structure on the outer surface of the spline sleeve. The inner periphery of the friction plate 9 is provided with a first tooth structure coupled to the outer periphery of the spline sleeve 7. The high-speed clutch pressure plate 8 only has a protrusion on its outer periphery and no tooth structure on its inner periphery. The high-speed clutch pressure plate 8 only moves axially along the slide groove of the high-speed clutch housing 11 under the action of hydraulic oil to press the friction plate.

[0059] A high-speed clutch friction plate 9 is movably disposed outside the spline sleeve 7 and alternately arranged with the high-speed clutch pressure plate 8; the high-speed clutch friction plate 9 may preferably be configured to have Figure 6 The groove structure shown can be set to a depth of 2mm. The grooves on the front and rear friction end faces of the high-speed clutch friction plate can be directly connected to the grooves on the toothed coupling surface of the inner ring of the friction plate and the spline sleeve 7 through the annular plane that directly contacts the high-speed clutch pressure plate 8. The 2mm deep grooves can form an oil guide passage connecting to the first toothed structure on the outer circumference of the spline sleeve when the high-speed clutch is engaged, thereby guiding the hydraulic oil on the first toothed structure on the outer circumference of the spline sleeve to the friction contact surface, increasing the amount of hydraulic oil on the front and rear friction end faces of the friction plate. By increasing the cross-shaped grooves, sufficient oil intake is ensured, and the contact area between the oil and the friction plate is increased. The mesh-like groove method allows the hydraulic oil to quickly reach all directions, thereby effectively increasing the amount of oil entering the friction plate and the pressure oil flow rate, further reducing the surface temperature of the high-speed clutch friction plate, reducing the temperature of the friction plate during gear shifting, and reducing drag torque loss. This allows the oil to achieve the purpose of fast inflow and fast outflow, ultimately improving the life of the friction plate and even the gearbox.

[0060] The high-speed clutch housing 11 is disposed outside the high-speed clutch pressure plate 8 and the high-speed clutch friction plate 9, and the high-speed clutch housing 11 is provided with a first sliding groove parallel to the power input shaft 5. The coupling protrusion is accommodated in the first sliding groove. The high-speed clutch housing 11 is fixedly connected to the planet carrier 25 of the planetary transmission structure and maintains synchronous rotation.

[0061] The first piston ring 10 is disposed between the bottom of the high-speed clutch housing 11 and the high-speed clutch pressure plate 8. It is used to supply hydraulic pressure to drive the high-speed clutch friction plate 9 and the high-speed clutch pressure plate 8 to move along the first slide groove toward the spline sleeve 7 under the first hydraulic pressure state, so that the inner ring of the high-speed clutch pressure plate 8 is coupled with the outer periphery of the spline sleeve 7, and the high-speed clutch pressure plate 8, spline sleeve 7, high-speed clutch housing 11 and power input shaft 5 operate synchronously.

[0062] The low-speed brake can be configured in the following ways:

[0063] The low-speed brake housing 19 is fixedly connected to the gearbox housing, and a second sliding groove parallel to the power input shaft 5 is provided inside the low-speed brake housing 19.

[0064] The second pressure plate 15 is movably disposed between the low-speed brake housing 19 and the power input shaft 5, and the outer periphery of the second pressure plate 15 extends radially therein to form brake pads.

[0065] The second friction plate 16 is movably disposed between the low-speed brake housing 19 and the power input shaft 5, and is alternately arranged with the second pressure plate 15;

[0066] The second piston ring 18 is disposed between the bottom of the low-speed brake housing 19 and the second pressure plate 15. It is used to supply hydraulic pressure to drive the brake cam and the second friction plate 16 to move along the second groove toward the high-speed clutch in the second hydraulic state. This makes the second pressure plate 15 and the second friction plate 16 tightly coupled with the bottom of the high-speed clutch housing 11, keeping the high-speed clutch, the second pressure plate 15, the second friction plate 16 coupled with the low-speed brake housing 19, and keeping them synchronously fixed with the gearbox housing.

[0067] In this application, the triple sun gear 4, planetary transmission structure, and high-speed clutch can be referred to... Figure 7As shown, the power input shaft 5 is positioned between the power cut-off brake and the low-speed brake. Specifically, the triple-sun gear 4 is positioned near the power cut-off brake along the power input shaft 5; the high-speed clutch is positioned near the low-speed brake along the power input shaft 5; and the planetary transmission structure is positioned between the triple-sun gear 4 and the high-speed clutch. Furthermore, the power cut-off brake, triple-sun gear 4, planetary transmission structure, high-speed clutch, and low-speed brake are all coaxially mounted on the power input shaft 5. Therefore, this application can adjust the transmission mode of the planetary gears 26 within the planetary carrier 25 by adjusting the coupling state of the pressure plates in the high-speed clutch, thereby adjusting the transmission ratio between the power input shaft 5 and the transmission gears 43 of the triple-sun gear 4, achieving transmissions with different speed ratios.

[0068] The planetary transmission structure can be composed of a stop pin 20, a planetary gear shaft 21, a thrust washer 22, a ball bearing 23, a spacer ring 24, a planetary carrier 25, planetary gears 26, and hexagonal bolts 27. The high-speed clutch is composed of a spline sleeve 7, a high-speed clutch pressure plate 8, and a high-speed clutch friction plate 9. The low-speed brake is composed of a disc spring 14, a second pressure plate 15, a second friction plate 16, a release plate 17, a second piston ring 18, and a low-speed brake housing 19. The power input shaft 5 is connected to the triple sun gear 4, planetary gears 26, and spline sleeve 7. The planetary carrier 25 of the transmission gear set is connected to the housing of the high-speed clutch as a whole by hexagonal bolts 27. The first piston ring 10 inputs hydraulic oil to push the high-speed clutch pressure plate 8 and the high-speed clutch friction plate 9 toward the front opening of the high-speed clutch housing 11, so that the high-speed clutch housing is connected to the planetary carrier 25 and maintains synchronous driving state. The release disc 17 is bolted to the low-speed brake housing, preventing the pressure plate from exiting the low-speed brake housing 19. Thus, the high-speed clutch and planetary system are connected as a single unit, directly transmitting power from the input shaft to the high-speed clutch via the spline sleeve 7. The high-speed clutch housing then synchronously drives the planetary transmission structure to output power to the triple sun gear 4, ensuring that the triple sun gear operates synchronously with the power input shaft.

[0069] The low-speed brake includes a disc spring 14, a second pressure plate 15, a second friction plate 16, and a second piston ring 18. A gasket 12 and the disc spring 14 are disposed between the second pressure plate 15 and the bottom surface of the high-speed clutch housing 11. The inner rings of the second pressure plate 15 and the second friction plate 16 are also provided with inner and outer ring needle roller bearings 13, which are located on the outer periphery of the power input shaft 5, between the power input shaft 5 and the second pressure plate 15 and the second friction plate 16. It is mainly fixed to the gearbox housing via a release disc 17 and the low-speed brake housing 19, so that when the second piston ring 18 is filled with hydraulic pressure, the disc spring 14 and the second pressure plate 15 are pushed forward along the axis of the low-speed brake housing 19, causing the second pressure plate 15 to abut against the high-speed clutch housing. The low-speed brake housing 19, which is stationary in the gearbox housing, restricts the operation of the high-speed clutch, thus achieving braking.

[0070] The planetary gear shaft 21 is mounted on the planetary carrier 25. To prevent the planetary gear shaft 21 from falling onto the planetary carrier 25 during operation, a stop pin 20 is installed. The planetary gear 26 is mounted on the planetary gear shaft 21 via balls 23. At the same time, thrust washers 22 are installed on both sides of the planetary gear 26, and the balls 23 are separated by a spacer ring 24.

[0071] In a preferred embodiment, the shift gearbox has a power cut-off brake located at one end of the power input shaft 5 and a low-speed brake located at the other end of the power input shaft 5. Both the power cut-off brake and the low-speed brake are connected to the gearbox housing. The actuating components in the power cut-off brake and the low-speed brake slide axially along the power input shaft 5 to switch their coupling states.

[0072] During high-speed power transmission, the high-speed clutch pressure plate 8 and high-speed clutch friction plate 9 of the high-speed clutch are driven forward by the hydraulic oil injected by the first piston ring 10, locking the high-speed clutch pressure plate 8, high-speed clutch housing, spline sleeve 7 and planetary carrier 25 into one unit, so that the planetary carrier 25 keeps rotating in the same direction as the input shaft 5. At the same time, the gear on the input shaft 5 meshes with the planetary gear 26, causing the planetary gear 26 to rotate in the opposite direction. At this time, the entire planetary gear set is connected to the input shaft 5 as one unit, which is equivalent to the power being directly output from the triple sun gear 4.

[0073] When the transmission is in low gear, the disc spring 14, the second pressure plate 15, and the second friction plate 16 of the low-speed brake are driven by the hydraulic oil injected by the second piston ring 18, move forward and tightly engage with the high-speed clutch housing, restricting the high-speed clutch and the planetary carrier 25 connected to the front end of its housing to stop rotating. At this time, the input power is transmitted from the input shaft 5 to the planetary gear 26, and then the planetary gear 26 is reduced and transmitted to the transmission gear 43 at the rear end of the triple sun gear 4, driving the output gear 42 to achieve a two-stage reduction fixed-axis gear transmission.

[0074] The gear is in neutral when the high-speed clutches 8, 9, and 10 and the low-speed brakes 14, 15, 16, and 18 are not engaged.

[0075] In a more specific implementation, the power cut-off brake can be arranged with a set of first pressure plates 1 and first friction plates 2 alternately along the axial direction of the brake external spline 41;

[0076] The first pressure plate 1 and the first friction plate 2 are movably disposed outside the brake external spline 41. The outer periphery of the first pressure plate 1 extends radially to form a fixed protrusion, and the inner periphery of the friction plate 2 is provided with a second tooth structure coupled to the outer peripheral surface of the brake external spline 41.

[0077] When the bottom of the brake is filled with oil, the piston pushes the pressure plate to move towards the power input end. The first pressure plate 1 and the first friction plate 2 move axially under the action of hydraulic oil, pressing the friction plate. When the second tooth structure distributed radially on the inner circumference of the friction plate 2 is coupled with the outer circumferential surface of the brake spline 41, the triple gear 4 is braked, realizing the function of cutting off the power. The fixed protrusion keeps the first pressure plate 1 and the gearbox housing synchronously fixed.

[0078] The above are merely embodiments of this application, and their descriptions are quite specific and detailed, but they should not be construed as limiting the scope of this patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application.

Claims

1. A shift transmission for a cotton picker spindle characterized by, The shift gearbox is arranged in the transmission path between the power output mechanism and the cotton picker spindle, comprising: a power input shaft (5) having one end connected with the power output mechanism of the cotton picker to receive driving torque; A triple sun gear (4) is connected with the power input shaft (5) through a bearing, and has a brake outer spline (41), an output gear (42) and a transmission gear (43) connected as a whole; A power cut-off brake is arranged to limit the rotation of the triple sun gear (4) when coupled with the brake outer spline (41), and to make the triple sun gear (4) driven by the power input shaft (5) to output torque when decoupled from the brake outer spline; A high-speed clutch is coupled with the power input shaft (5) to drive the planetary transmission structure and the high-speed clutch to rotate synchronously in a first hydraulic state, the planetary transmission structure is connected with the power input shaft (5) synchronously to drive the output gear (42) to output torque of the power input shaft (5); A low-speed brake is coupled with the high-speed clutch to limit the transmission between the high-speed clutch and the power input shaft (5) in a second hydraulic state, the high-speed clutch is kept synchronous with the planetary transmission structure, so that the planetary transmission structure is switched to be coupled with the transmission gear (43) of the triple sun gear (4) on the power input shaft (5) through the planetary gear (26) to drive the output gear (42) to output torque at a reduced speed; The first hydraulic state and the second hydraulic state are triggered independently.

2. The shift transmission for a cotton picker spindle as claimed in claim 1, wherein, When the first hydraulic state is cancelled, the coupling between the high-speed clutch and the power input shaft (5) is cancelled, and the operating states of the power input shaft (5) and the high-speed clutch are independent of each other.

3. The shift transmission for a cotton picker spindle as claimed in claim 1, wherein, When the second hydraulic state is cancelled, the coupling between the low-speed brake and the high-speed clutch is cancelled, and the operating states of the power input shaft (5) and the low-speed brake are independent of each other.

4. The shift transmission for a cotton picker spindle as claimed in claim 3, wherein, The high-speed clutch comprises: a spline sleeve (7) fixedly connected with the power input shaft (5) and kept synchronous with the power input shaft (5); A high-speed clutch pressure plate (8) is movably arranged outside the spline sleeve (7), and the outer periphery of the high-speed clutch pressure plate (8) is formed with a coupling tab in the radial direction thereof; A high-speed clutch friction plate (9) is movably arranged outside the spline sleeve (7) with a first tooth structure coupled with the outer periphery of the spline sleeve (7) arranged in the radial direction thereof, and the high-speed clutch friction plate (9) and the high-speed clutch pressure plate (8) are arranged alternately; A high-speed clutch housing (11) is arranged outside the high-speed clutch pressure plate (8) and the high-speed clutch friction plate (9), and the high-speed clutch housing (11) is provided with a first sliding groove parallel to the power input shaft (5), and the coupling tab is accommodated in the first sliding groove. The first piston ring (10) is arranged between the bottom of the high-speed clutch housing (11) and the high-speed clutch pressure plate (8) to supply hydraulic pressure to drive the high-speed clutch friction plate (9) and the high-speed clutch pressure plate (8) to move along the first sliding groove to the spline sleeve (7) in the first hydraulic state, so that the inner ring of the high-speed clutch pressure plate (8) is coupled with the outer periphery of the spline sleeve (7), and the high-speed clutch pressure plate (8), the spline sleeve (7), the high-speed clutch housing (11) and the power input shaft (5) are kept synchronous operation.

5. The shift transmission for a cotton picker spindle as claimed in claim 4, wherein, The high-speed clutch housing (11) is fixedly connected with the planet carrier (25) of the planetary transmission structure and kept synchronous rotation; the planetary gear (26) is arranged in the planet carrier (25) and is drivingly connected between the power input shaft (5) and the transmission gear (43) of the triple sun gear (4).

6. The shift transmission for a cotton picker spindle as claimed in claim 3, wherein, The power cut-off brake is arranged at one end of the power input shaft (5), and the low-speed brake is arranged at the other end of the power input shaft (5), both of which are connected with the gearbox of the shift transmission, and the action components in the power cut-off brake and the low-speed brake respectively slide along the power input shaft (5) to switch the coupling state.

7. The shift transmission for a cotton picker spindle as claimed in claim 6, wherein, The triple sun gear (4), the planetary transmission structure and the high-speed clutch are arranged along the power input shaft (5) between the power cut-off brake and the low-speed brake; The triple sun gear (4) is arranged near the power cut-off brake along the power input shaft (5); The high-speed clutch is arranged near the low-speed brake along the power input shaft (5); The planetary transmission structure is arranged between the triple sun gear (4) and the high-speed clutch; The power cut-off brake, the triple sun gear (4), the planetary transmission structure, the high-speed clutch and the low-speed brake are coaxially arranged with the power input shaft (5).

8. The shift transmission for a cotton picker spindle as claimed in claim 3, wherein, The low-speed brake comprises a low-speed brake housing (19) fixedly connected with the gearbox of the shift transmission, and a second sliding groove parallel to the power input shaft (5) is arranged in the low-speed brake housing (19); A second pressure plate (15) is movably arranged between the low-speed brake housing (19) and the power input shaft (5), and a brake tab is formed on the outer periphery of the second pressure plate (15) in the radial direction thereof; A second friction plate (16) is movably arranged between the low-speed brake housing (19) and the power input shaft (5) and is alternately arranged with the second pressure plate (15); A second piston ring (18) is arranged between the bottom of the low-speed brake housing (19) and the second pressure plate (15) to supply hydraulic pressure to drive the brake tab and the second friction plate (16) to move along the second sliding groove to the high-speed clutch in the second hydraulic state, so that the second pressure plate (15) and the second friction plate (16) are tightly coupled with the bottom of the high-speed clutch housing (11), the high-speed clutch, the second pressure plate (15), the second friction plate (16) and the low-speed brake housing (19) are kept coupled, and the gearbox of the shift transmission is kept synchronous fixed.

9. The shift transmission for a cotton picker spindle as claimed in claim 8, wherein, The low-speed brake further comprises a gasket (12) and a butterfly spring (14) between the second pressure plate (15) and the bottom surface of the high-speed clutch housing (11); The inner ring of the second pressure plate (15) and the second friction plate (16) further comprises an inner-outer ring needle bearing (13) arranged on the outer periphery of the power input shaft (5) between the power input shaft (5) and the second pressure plate (15) and the second friction plate (16).

10. The shift transmission for a cotton picker spindle as claimed in claim 3, wherein, The power cut-off brake comprises a first pressure plate (1) and a first friction plate (2) alternately arranged along the brake outer spline (41) in the axial direction; The first pressure plate (1) and the first friction plate (2) are movably arranged outside the brake outer spline (41), the outer periphery of the first pressure plate (1) is formed with a fixed tab extending in the radial direction thereof, and the inner periphery of the first friction plate (2) is provided with a second toothed structure coupled to the outer peripheral surface of the brake outer spline (41); When the second toothed structure is coupled to the outer peripheral surface of the brake outer spline (41), the fixed tab keeps the first pressure plate (1) and the gear box body of the gear shift transmission synchronously fixed.

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