Staggered differential automatic right angle head

Abstract

The application discloses a staggered-tooth differential automatic right-angle head, which comprises a box body, a transmission shaft and a right-angle head main shaft arranged in the box body; a C-shaft indexing mechanism comprises a C-shaft positioning gear disc seat, a first indexing gear disc, a second indexing gear disc, an overrunning sleeve, a flange seat, an internal gear and an external gear; the external gear is always engaged with the first bevel gear; the C-shaft indexing mechanism adopts a staggered-tooth differential structure, which comprises two groups of gear disc pairs with different divisions, i.e., the C-shaft positioning gear disc seat, the first indexing gear disc and the second indexing gear disc; differential indexing is realized through differential motion of the two groups of gear disc pairs; the upper teeth of the first indexing gear disc can be engaged with the lower teeth of the C-shaft positioning gear disc seat, and the lower teeth of the first indexing gear disc can be engaged with the upper teeth of the second indexing gear disc; the number of the upper teeth of the first indexing gear disc is not equal to the number of the lower teeth of the first indexing gear disc. Through differential motion of the two groups of gear disc pairs with different divisions, the application realizes micro-angle indexing.

Description

Technical Field

[0001] This invention relates to the technical field of right-angle heads, and more particularly to an automatic right-angle head with staggered tooth differential. Background Technology

[0002] Right-angle heads are crucial components in machine tool processing, used for multi-axis machining of workpieces. Traditional right-angle heads have limitations in C-axis indexing accuracy, typically employing a single-tooth disc structure with limited indexing precision, making it difficult to meet high-precision machining requirements. Furthermore, traditional right-angle heads are prone to power transmission interruptions during indexing, affecting machining accuracy and efficiency. Existing right-angle heads suffer from the following problems: low indexing accuracy, limited indexing angle due to the single-tooth disc structure; discontinuous power transmission during indexing, easily leading to accuracy loss; low automation level and long changeover times; complex structure and difficult maintenance. Summary of the Invention

[0003] (a) Technical problems to be solved

[0004] The technical problem to be solved by the present invention is to provide an automatic right-angle head with staggered tooth differential. Its staggered tooth differential structure achieves micro-angle indexing through the differential motion of two sets of toothed disc pairs with different indexing, and the indexing accuracy is much higher than that of the traditional single toothed disc structure. The constant meshing of the external gear and the first bevel gear ensures the continuity of power transmission, avoids the accuracy loss caused by disengagement during indexing, eliminates power interruption during indexing, and ensures the stability of processing quality.

[0005] (II) Technical Solution

[0006] The solution adopted by the present invention to solve the above-mentioned technical problems is an automatic right-angle head for tooth misalignment, including a housing, a drive shaft arranged in the housing, and a right-angle head main shaft connected to the drive shaft; the drive shaft and the right-angle head main shaft are connected by a transmission mechanism; the housing includes an upper housing and a lower housing arranged vertically.

[0007] The top end of the drive shaft is provided with a main pull stud, which is connected to the machine tool spindle; the bottom end of the drive shaft is provided with a lower pressure cover, and a first spring is provided between the lower pressure cover and the drive shaft. The cooperation between the first spring and the lower pressure cover can compensate for the axial displacement of the drive shaft, avoid rigid collision between the machine tool spindle and the right-angle head, reduce impact load, extend the service life of the equipment, absorb assembly errors, and reduce vibration and noise.

[0008] The transmission mechanism includes a first bevel gear connected to the transmission shaft and a second bevel gear meshing with the first bevel gear, the second bevel gear being connected to the right-angle head spindle;

[0009] C-axis indexing mechanism is used to realize the indexing of right-angle head spindle on C-axis. It includes C-axis positioning gear plate seat, first indexing gear plate, second indexing gear plate, transition sleeve, flange seat, internal gear and external gear; the external gear is always meshed with the first bevel gear.

[0010] The C-axis indexing mechanism adopts a staggered tooth differential structure, which includes two sets of upper and lower indexed tooth disk pairs consisting of the C-axis positioning tooth disk seat, the first indexing tooth disk, and the second indexing tooth disk. The differential movement of the two sets of tooth disk pairs realizes the differential indexing. The upper teeth of the first indexing tooth disk can mesh with the lower teeth of the C-axis positioning tooth disk seat, and the lower teeth of the first indexing tooth disk can mesh with the upper teeth of the second indexing tooth disk. Furthermore, the number of upper teeth of the first indexing tooth disk is not equal to the number of lower teeth of the first indexing tooth disk.

[0011] In some embodiments, the first bevel gear is fixed to the C-axis bearing seat via a drive shaft bearing, an inner spacer, an outer spacer, a first pressure cover, a dustproof plate, and a second pressure cover. The C-axis bearing seat is centered on the C-axis positioning gear plate seat, which is centered on the upper housing. The second bevel gear is connected to the right-angle head spindle via a rectangular spline. The machine tool spindle power is transmitted to the first bevel gear connected to the drive shaft spline via the drive shaft. Through the meshing of the first and second bevel gears, the power is transmitted to the right-angle head spindle connected to the second bevel gear via the rectangular spline, thus completing the power transmission of the right-angle head.

[0012] In some embodiments, a sealing device is provided between the upper housing and the lower housing, the sealing device including an O-ring and a dust cover; the interior of the housing is filled with lubricating oil or grease.

[0013] Specifically, by employing a staggered tooth differential structure with two sets of gear pairs, the right-angle head can achieve micro-indexing that a single set of gear pairs cannot. Due to structural size limitations, the internal positioning gear size of the right-angle head cannot be made very large. The minimum indexing of the positioning gear in conventional accessory heads is only 1 division, and there are also issues with the reliability of the operation. By using two sets of gear pairs in combination, the gear positioning design becomes more flexible, easily achieving micro-indexing positioning, and improving the reliability of the operation.

[0014] Specifically, through a reasonable and compact structural design, the right-angle head of the present invention can realize the automatic exchange function with the slide. Based on the right-angle head of the present invention, the machine tool can continue to be equipped with other accessory heads with different functions, thus broadening the range of functions that the machine tool can be equipped with.

[0015] Using the above scheme, the staggered tooth differential structure achieves micro-angle indexing through the differential motion of two sets of toothed disk pairs with different indexing, and the indexing accuracy is much higher than that of the traditional single toothed disk structure; the constant meshing of the external gear and the first bevel gear ensures the continuity of power transmission, avoids the accuracy loss caused by disengagement during indexing, eliminates power interruption during indexing, and ensures the stability of machining quality.

[0016] In some embodiments, the number of teeth on the upper teeth of the first indexing gear is 144, and the number of teeth on the lower teeth of the first indexing gear is 150; so that the minimum indexing angle achieved by the differential motion of the two sets of gear pairs of the C-axis indexing mechanism is 360°÷144-360°÷150=0.1°.

[0017] By adopting the above scheme, the difference design between 144 teeth and 150 teeth can precisely control the minimum division angle to 0.1°, which meets the requirements of high-precision machining and is particularly suitable for high-end manufacturing fields such as aerospace and precision molds.

[0018] In some embodiments, the C-axis indexing mechanism further includes a first piston fixed to the first indexing gear and a second piston fixed to the second indexing gear; the second piston is disposed opposite to the first piston below; a first hydraulic cylinder is connected to the top of the first piston, a second hydraulic cylinder is connected between the first piston and the second piston, and a third hydraulic cylinder is connected to the bottom of the second indexing gear;

[0019] When pressurized oil is introduced into the first cylinder, the first piston pushes the second piston, the first indexing gear, the lower housing, and the flange seat downwards by a distance C, so that the lower teeth of the C-axis positioning gear seat disengage from the upper teeth of the first indexing gear, and the lower teeth of the first indexing gear and the upper teeth of the second indexing gear mesh. The internal gear fixed below the flange seat and the external gear fixed below the first bevel gear mesh. At this time, the machine tool spindle drives the transmission shaft to rotate clockwise, and the power can be transmitted to the internal gear through the first bevel gear and the external gear. The internal gear drives the flange seat, the lower housing, the second indexing gear, and the first indexing gear to rotate. After rotating to the required angle, pressurized oil is introduced into the third cylinder, and the second indexing gear, along with the lower housing, the flange seat, and the internal gear, pushes the first indexing gear to move upwards by a distance C, so that the upper teeth of the first indexing gear mesh with the lower teeth of the C-axis positioning gear seat. At this time, the first indexing operation is completed.

[0020] When the second cylinder receives pressurized oil, the first piston and the first indexing gear plate are subjected to an upward force, causing the upper teeth of the first indexing gear plate to mesh with the lower teeth of the C-axis positioning gear plate seat. Simultaneously, the second piston is subjected to a downward force, causing the second indexing gear plate, lower housing, flange seat, and internal gear to move downward a distance C, allowing the internal gear to mesh with the external gear fixed below the first bevel gear. At this time, the machine tool spindle drives the transmission shaft to rotate counterclockwise, transmitting power to the internal gear through the first bevel gear and external gear. The internal gear then drives the flange seat, lower housing, and second indexing gear plate to rotate. After rotating to the desired angle, the third cylinder receives pressurized oil, causing the second indexing gear plate to move upward a distance C along with the lower housing, flange seat, and internal gear, allowing the upper teeth of the second indexing gear plate to mesh with the lower teeth of the first indexing gear plate. This completes the second indexing operation.

[0021] Specifically, the upper teeth of the first indexing gear and the lower teeth of the C-axis positioning gear seat are end-face tooth structures, and the lower teeth of the first indexing gear and the upper teeth of the second indexing gear are end-face tooth structures; indexing control is achieved through the axial meshing and disengagement of the end-face teeth; the tooth ratio of the external gear to the internal gear is 1:1 to ensure angular accuracy during indexing; the external gear is fixed below the first bevel gear, and the internal gear is fixed below the flange seat.

[0022] In some embodiments, the first, second, and third cylinders are all double-acting cylinders, and the bidirectional movement of the first and second pistons is achieved by controlling the oil inlet and outlet; the distance C is 2-5 mm.

[0023] Indexing process: When the first cylinder is filled with pressurized oil, the first piston pushes the second piston, the first indexing gear, the lower housing and the flange seat to move downward by a distance C, realizing the first indexing operation; when the second cylinder is filled with pressurized oil, the second indexing operation is realized; when the third cylinder is filled with pressurized oil, the reset action after indexing is completed.

[0024] Using the above scheme, the coordinated action of the first, second, and third hydraulic cylinders realizes the automated process of disengagement, indexing, and re-engagement of the two sets of gear pairs, with high reliability; it enables indexing in both forward and reverse directions, expanding the processing range; and complex indexing actions can be achieved simply by controlling the hydraulic pressure.

[0025] In some embodiments, the top of the upper housing is connected to a female quick-change plug that mates with the female quick-change plug of the machine tool slide; a functional path for transmitting right-angle heads to achieve various automation functions.

[0026] Specifically, the transition sleeve is disposed between the C-axis positioning gear plate seat and the flange seat, and is used to transmit functional paths while realizing axial relative movement; the transition sleeve is provided with a sealing structure to ensure the sealing between each functional path.

[0027] By adopting the above solution, the female quick-change plug of the machine tool slide is matched with the male quick-change plug, so as to realize the rapid docking of the functional circuit (oil / gas / electric) and shorten the changeover time.

[0028] In some embodiments, the required functional paths of the right-angle head are introduced through the sub-quick-change plug to the C-axis positioning gear plate seat which is centered and connected to the upper housing, then through the transition sleeve which is centered and connected to the C-axis positioning gear plate seat to the flange seat, and then into the lower housing. Through the lower housing, the path enters the external cooling path, the nose gas seal, the cutting tool oil path, and the center air blowing path, providing power for the various automated functions of the right-angle head.

[0029] Specifically, the external cooling circuit and the central air blowing circuit ensure cooling and cleanliness during the machining process, the tool changing oil circuit enables automatic tool changing, and the nose air seal prevents cutting fluid and chips from entering the right-angle head spindle.

[0030] In some embodiments, the right-angle head spindle is provided with a coolant channel and a compressed air channel along its axial direction, which are connected to the external cooling circuit and the central air blowing circuit; the end of the right-angle head spindle is provided with a tool interface, which conforms to ISO or BT standards and has strong versatility.

[0031] By adopting the above scheme, the isolation transmission of multiple media (external cooling, gas sealing, etc.) is achieved through the centering connection module (C-axis positioning gear plate seat → transition sleeve → flange seat → lower housing), thus avoiding interference.

[0032] In some embodiments, the top of the upper housing is provided with several small pull studs. When the machine tool slide approaches the right-angle head, the pull head cylinder on the oil receiving plate of the machine tool slide pulls the small pull studs at the corresponding positions on the upper housing to complete the pull head action.

[0033] The drive shaft has a keyway at one end near the machine tool spindle. When the machine tool ram approaches the right-angle head, the end face key of the machine tool spindle is inserted into the keyway of the drive shaft to complete the gripping action.

[0034] In some embodiments, the number of small rivets is 4-8, which are evenly distributed on the top circumference of the upper housing.

[0035] Specifically, after the machine tool completes the gripper action, the end face key of the machine tool spindle is inserted into the keyway of the transmission shaft, the machine tool spindle baffle grips the main pull pin above the transmission shaft, and the centering sleeve on the transmission shaft is lifted by several small springs and contacts the inner hole of the machine tool spindle to achieve centering of the transmission shaft. The upper toothed chuck installed on the oil receiving pan meshes with the lower toothed chuck installed on the upper housing.

[0036] Using the above scheme, the small pull pin and the pull head cylinder work together to complete the coarse positioning; the end face key is inserted into the keyway to achieve precise positioning, ensuring the coaxiality of the drive shaft and the machine tool spindle; the small spring lifts the centering sleeve to absorb assembly errors and reduce vibration, and the dual positioning mechanism improves the reliability of the system.

[0037] In some embodiments, a spindle tool release mechanism is also included, which includes a spindle fixing assembly, a spindle tool pull assembly, and a spindle tool release assembly, for realizing automatic tool pull and automatic tool release.

[0038] In some embodiments, the spindle fixing assembly includes a front bearing housing and a front spindle bearing fixed in the front bearing housing, which are arranged axially spaced along the right-angle head spindle; and a rear bearing housing and a rear spindle bearing fixed in the rear bearing housing. Furthermore, the front bearing housing and the rear bearing housing are respectively placed at both ends of the second bevel gear to balance the radial load on the right-angle head spindle and extend the bearing life.

[0039] In some embodiments, the spindle broach assembly includes a pull rod assembly disposed within the right-angle head spindle. The pull rod assembly includes a broach pawl, a pull rod connected to the broach pawl, a washer disposed at the end of the pull rod away from the broach pawl, a disc spring connected to the washer, and a locking nut fixed to the tail of the pull rod. The disc spring is constrained by the washer and the limiting seat fixed to the tail of the right-angle head spindle, so that the disc spring is in a compressed state. When the right-angle head spindle grips the tool, the first step on the right side of the pull rod and the left end face of the washer are pulled out by a distance A. At this time, the tool is subjected to the reaction force of the disc spring compression force in the pull rod assembly, realizing the right-angle head broach action.

[0040] In some embodiments, the distance A is 3-8 mm, and the disc spring compression force of the pull rod assembly is 800-1500 N to ensure reliable clamping of the tool.

[0041] Using the above scheme, the compressed disc spring provides a constant pulling force to prevent the tool from loosening during machining and ensure reliable tool clamping; the setting of distance A ensures that the pulling force is linearly related to the deformation of the disc spring, and the clamping force is adjustable.

[0042] In some embodiments, the spindle tool release assembly includes a rear bearing housing, a spring housing, a plurality of second springs, a third piston, a tail end cap, and a stop block; the spring housing is disposed inside the rear bearing housing, the spring housing is disposed inside the spring housing, and the tail end cap is fixed to the outer end of the rear bearing housing; one end of the second spring is connected to the spring housing, and the other end is connected to the third piston.

[0043] The third piston and the impact block fixed on the right end of the third piston move to the left under the action of the impact oil in the impact oil circuit, so that the impact block moves to the left while facing the locking nut, and the impact action stops. At this time, the pull rod moves to the left with the pull pawl, the pull pawl opens, and the impact action is completed.

[0044] When the hydraulic pressure in the cutting tool oil circuit returns to zero, the pull rod assembly moves to the right under the compression force of the disc spring, pushing against the impact block seat and the third piston. After the pull rod assembly moves to its limit, several second springs in the spring seat push against the third piston and the impact block seat to continue moving to the right a distance B, so that the locking nut of the impact block seat and the pull rod assembly is pulled apart by a small distance, so that the two planes do not come into contact when the right-angle head spindle rotates.

[0045] In some embodiments, the distance B is 1-3 mm, and the spring force of the second spring is 200-500 N.

[0046] Working process: When gripping the tool, the compression force of the disc spring is transmitted to the tool clamping pawl through the pull rod, realizing tool clamping; when releasing the tool, the pressure of the tool release oil circuit pushes the third piston and the impact block seat to move to the left, the pull rod moves the tool clamping pawl to the left, the tool clamping pawl opens, and the tool release action is completed; when the oil pressure returns to zero, the second spring pushes the third piston and the impact block seat to move to the right by a distance B, avoiding friction during rotation.

[0047] Using the above scheme, the hydraulically driven impact block seat achieves rapid knife release; the second spring reserves a distance B when resetting to avoid friction between the locking nut and the impact block seat during rotation, thus protecting dynamic balance.

[0048] (III) Beneficial Effects

[0049] Compared with existing technologies, this invention designs an automatic right-angle head for tooth misalignment differentiation.

[0050] (1) This invention can be used on both vertical gantry machining centers and horizontal machining centers; the machine tool slide oil receiving plate is equipped with several pull head cylinders, and the corresponding position of the right-angle head housing is equipped with small pull pins. By pulling the small pull pins at the corresponding position through the pull head cylinders, the upper toothed plate on the oil receiving plate and the lower toothed plate on the right-angle head housing can be meshed, which can ensure the positioning accuracy of the right-angle head and withstand the machining resistance of the right-angle head; this structure can meet both vertical and horizontal use; one right-angle head can be used on two machine tools with different spindle machining directions, namely gantry machining centers and floor boring horizontal machining centers, which is a highlight of this invention;

[0051] (2) The toothed differential structure of the present invention achieves micro-angle indexing through differential motion of two sets of toothed disk pairs with different indexing, and the indexing accuracy is much higher than that of the traditional single toothed disk structure; the constant meshing of the external gear and the first bevel gear ensures the continuity of power transmission, avoids the accuracy loss caused by disengagement during indexing, eliminates power interruption during indexing, and ensures the stability of processing quality; moreover, the difference design between 144 teeth and 150 teeth precisely controls the minimum indexing angle to 0.1°, which meets the requirements of high-precision processing and is particularly suitable for high-end manufacturing fields such as aerospace and precision molds.

[0052] (3) The present invention can compensate for the axial displacement of the transmission shaft by cooperating with the first spring and the lower pressure cover, avoid rigid collision between the machine tool spindle and the right angle head, reduce impact load, extend the service life of the equipment, absorb assembly errors, and reduce vibration and noise;

[0053] (4) The present invention achieves an automated process of disengagement, indexing and re-engagement of two sets of gear disk pairs through the coordinated action of the first, second and third oil cylinders, which has high reliability; it realizes indexing in both forward and reverse directions, expanding the processing range; and it can realize complex indexing actions by only controlling the oil circuit pressure.

[0054] (5) The present invention achieves rapid docking of functional circuits (oil / gas / electric) by cooperating with the female quick-change plug of the machine tool slide; thus shortening the changeover time.

[0055] (6) The present invention achieves isolated transmission of multiple media (external cooling, gas sealing, etc.) through a centering connection module (C-axis positioning gear plate seat → transition sleeve → flange seat → lower housing) to avoid interference;

[0056] (7) The present invention completes coarse positioning by cooperating with the pull head cylinder; the end face key is inserted into the keyway to achieve precise positioning, ensuring the coaxiality of the drive shaft and the machine tool spindle; the small spring lifts the centering sleeve to absorb assembly errors and reduce vibration, and the dual positioning mechanism improves the reliability of the system.

[0057] (8) The present invention places the front bearing housing and the rear bearing housing at the two ends of the second bevel gear respectively, so as to balance the radial load of the right-angle head spindle and extend the bearing life;

[0058] (9) The present invention provides a constant pulling force through a compressed disc spring to prevent the tool from loosening during processing and ensure reliable tool clamping; the setting of distance A ensures that the pulling force is linearly related to the deformation of the disc spring, and the clamping force is adjustable;

[0059] (10) The present invention achieves rapid knife release by hydraulically driving the impact block seat; when the second spring is reset, a distance B is reserved to avoid friction between the locking nut and the impact block seat during rotation, thus protecting dynamic balance. Attached Figure Description

[0060] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0061] Figure 1 This is a cross-sectional schematic diagram of an automatic right-angle head for tooth misalignment according to the present invention;

[0062] Figure 2 for Figure 1 Enlarged view of point D;

[0063] Figure 3 for Figure 1 Enlarged diagram of point F in the middle.

[0064] The component names corresponding to the various labels in the figure are as follows: 100, drive shaft; 101, main pull pin; 102, lower pressure cover; 103, first spring; 104, keyway; 105, centering sleeve; 106, small spring; 200, right-angle head spindle; 201, limit seat; 300, upper housing; 301, quick-change plug; 302, small pull pin; 400, lower housing; 500, first bevel gear; 501, second bevel gear; 502, drive shaft bearing; 503, inner spacer; 504, outer spacer; 505, first pressure cover; 506, dustproof plate; 507, second pressure cover; 508, C-axis bearing seat; 600, C-axis indexing mechanism; 601, C-axis positioning gear seat; 602, first indexing gear. 603. Second indexing gear; 604. Transition sleeve; 605. Flange seat; 606. Internal gear; 607. External gear; 608. First piston; 609. Second piston; 610. First cylinder; 611. Second cylinder; 612. Third cylinder; 700. Front bearing seat; 701. Front bearing of spindle; 702. Rear bearing seat; 703. Rear bearing of spindle; 801. Cutting pawl; 802. Connecting rod; 8021. First step; 803. Washer; 804. Disc spring; 805. Locking nut; 900. Spring seat; 901. Second spring; 902. Third piston; 903. Tail end cap; 904. Impact block seat; 10. Nose end air seal; 20. Cutting tool oil passage; 30. Center air blowing passage. Detailed Implementation

[0065] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and should not be construed as limiting the scope of the invention.

[0066] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0067] The following specific examples illustrate the implementation of this application. Those skilled in the art can easily understand other advantages and effects of this application from the content disclosed in this specification. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. This application can also be implemented or applied through other different specific embodiments, and the details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of this application. It should be noted that, in the absence of conflict, the following embodiments and features in the embodiments can be combined with each other. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0068] It should be noted that the following description covers various aspects of embodiments within the scope of the appended claims. It will be apparent that the aspects described herein can be embodied in a wide variety of forms, and any particular structure and / or function described herein is merely illustrative. Based on this application, those skilled in the art will understand that one aspect described herein can be implemented independently of any other aspect, and two or more of these aspects can be combined in various ways. For example, any number and aspects set forth herein can be used to implement the device and / or practice the method. Additionally, this device and / or method can be implemented using structures and / or functionalities other than one or more of the aspects set forth herein.

[0069] It should also be noted that the illustrations provided in the following embodiments are only schematic representations of the basic concept of this application. The drawings only show the components related to this application and are not drawn according to the actual number, shape and size of the components in the actual implementation. In the actual implementation, the form, quantity and proportion of each component can be arbitrarily changed, and the layout of the components may also be more complex.

[0070] Additionally, specific details are provided in the following description to facilitate a thorough understanding of the examples. However, those skilled in the art will understand that practice can be carried out without these specific details.

[0071] The technical solutions provided by the various embodiments of this application are described below with reference to the accompanying drawings.

[0072] In the following examples, distance A is 3.2 mm; distance B is 1.5 mm; and distance C is 5 mm.

[0073] like Figures 1-3As shown, this invention provides an automatic right-angle head for tooth misalignment, including a housing, a drive shaft 100 arranged within the housing, and a right-angle head spindle 200 connected to the drive shaft 100; the drive shaft 100 and the right-angle head spindle 200 are connected by a transmission mechanism; the housing includes an upper housing 300 and a lower housing 400 arranged vertically; a main pull stud 101 is provided at the top of the drive shaft 100, and the main pull stud 101 is connected to the machine tool spindle (not shown in the figure); a lower pressure cover 102 is provided at the bottom of the drive shaft 100, and a first spring 103 is provided between the lower pressure cover 102 and the drive shaft 100. The cooperation between the first spring 103 and the lower pressure cover 102 can compensate for the axial displacement of the drive shaft 100, avoid rigid collision between the machine tool spindle and the right-angle head, reduce impact load, and extend the service life of the equipment. To absorb assembly errors and reduce vibration and noise, the transmission mechanism includes a first bevel gear 500 connected to the transmission shaft 100 and a second bevel gear 501 meshing with the first bevel gear 500. The second bevel gear 501 is connected to the right-angle head spindle 200. A C-axis indexing mechanism 600 is used to realize the indexing of the right-angle head spindle 200 on the C-axis. It includes a C-axis positioning gear plate seat 601, a first indexing gear plate 602, a second indexing gear plate 603, an adapter sleeve 604, a flange seat 605, an internal gear 606, and an external gear 607. The external gear 607 is always meshed with the first bevel gear 500. The C-axis... The indexing mechanism 600 adopts a staggered tooth differential structure, which includes two sets of upper and lower indexed tooth disk pairs composed of the C-axis positioning tooth disk seat 601, the first indexing tooth disk 602, and the second indexing tooth disk 603. The differential movement of the two sets of tooth disk pairs realizes the differential indexing. The upper teeth of the first indexing tooth disk 602 can mesh with the lower teeth of the C-axis positioning tooth disk seat 601, and the lower teeth of the first indexing tooth disk 602 can mesh with the upper teeth of the second indexing tooth disk 603. Furthermore, the number of teeth on the upper teeth of the first indexing tooth disk 602 is not equal to the number of teeth on the lower teeth of the first indexing tooth disk 602. In some embodiments, the first bevel gear 500 is fixed to the C-axis bearing seat 508 via a transmission shaft bearing 502, an inner spacer 503, an outer spacer 504, a first pressure cover 505, a dustproof plate 506, and a second pressure cover 507. The C-axis bearing seat 508 is centered on the C-axis positioning gear plate seat 601, and the C-axis positioning gear plate seat 601 is centered on the upper housing 300. The second bevel gear 501 is connected to the right-angle head spindle 200 via a rectangular spline. The power of the machine tool spindle is transmitted to the first bevel gear 500, which is splined to the transmission shaft 100, via the transmission shaft 100. Through the meshing of the first bevel gear 500 and the second bevel gear 501, the power is transmitted to the right-angle head spindle 200, which is rectangularly splined to the second bevel gear 501, thus completing the power transmission of the right-angle head.In some embodiments, a sealing device is provided between the upper housing 300 and the lower housing 400, the sealing device including an O-ring and a dust cover; the housing is filled with lubricating oil or grease. Using the above scheme, the staggered tooth differential structure achieves micro-angle indexing through the differential motion of two sets of toothed disc pairs with different indexing, resulting in indexing accuracy far exceeding that of traditional single-tooth disc structures; the constant meshing of the external gear 607 and the first bevel gear 500 ensures continuous power transmission, avoids accuracy loss due to disengagement during indexing, eliminates power interruption during indexing, and guarantees stable machining quality. In some embodiments, the upper teeth of the first indexing toothed disc 602 have 144 teeth, and the lower teeth of the first indexing toothed disc 602 have 150 teeth; so that the minimum indexing angle achieved by the differential motion of the two sets of toothed disc pairs of the C-axis indexing mechanism 600 is 360°÷144-360°÷150=0.1°. By adopting the above scheme, the difference design between 144 teeth and 150 teeth can precisely control the minimum division angle to 0.1°, which meets the requirements of high-precision machining and is particularly suitable for high-end manufacturing fields such as aerospace and precision molds.

[0074] In some embodiments, the C-axis indexing mechanism 600 further includes a first piston 608 fixed to the first indexing gear 602 and a second piston 609 fixed to the second indexing gear 603; the second piston 609 is disposed opposite to the first piston 608; a first hydraulic cylinder 610 is connected to the top of the first piston 608, a second hydraulic cylinder 611 is connected between the first piston 608 and the second piston 609, and a third hydraulic cylinder 612 is connected to the bottom of the second indexing gear 603; when pressurized oil is introduced into the first hydraulic cylinder 610, the first piston 608 pushes the second piston 609, the first indexing gear 602, the lower housing 400, and the flange. The flange seat 605 moves downward a distance C, causing the lower teeth of the C-axis positioning gear seat 601 to disengage from the upper teeth of the first indexing gear 602. The lower teeth of the first indexing gear 602 mesh with the upper teeth of the second indexing gear 603. The internal gear 606 fixed below the flange seat 605 and the external gear 607 fixed below the first bevel gear 500 mesh. At this time, the machine tool spindle drives the transmission shaft 100 to rotate clockwise. Power is transmitted to the internal gear 606 through the first bevel gear 500 and the external gear 607. The internal gear 606 drives the flange seat 605, the lower housing 400, the second indexing gear 603, and the first indexing gear 602 to rotate. After rotating to the desired angle, the third hydraulic cylinder 6... When pressurized oil is introduced into the second cylinder 611, the second indexing gear 603, along with the lower housing 400, flange seat 605, and internal gear 606, pushes the first indexing gear 602 upward by a distance C, so that the upper teeth of the first indexing gear 602 mesh with the lower teeth of the C-axis positioning gear seat 601, thus completing the first indexing operation. When pressurized oil is introduced into the second cylinder 611, the first piston 608 and the first indexing gear 602 are subjected to an upward force, so that the upper teeth of the first indexing gear 602 mesh with the lower teeth of the C-axis positioning gear seat 601. Simultaneously, the second piston 609 is subjected to a downward force, driving the second indexing gear 603, lower housing 400, flange seat 605, and internal gear 606 to move upward. The internal gear 606 moves downward a distance C so that the external gear 607 fixed below the first bevel gear 500 meshes. At this time, the machine tool spindle drives the transmission shaft 100 to rotate counterclockwise. The power is transmitted to the internal gear 606 through the first bevel gear 500 and the external gear 607. The internal gear 606 drives the flange seat 605, the lower housing 400 and the second indexing gear 603 to rotate. After rotating to the required angle, the third oil cylinder 612 injects pressurized oil, and the second indexing gear 603 moves upward a distance C with the lower housing 400, the flange seat 605 and the internal gear 606 so that the upper teeth of the second indexing gear 603 mesh with the lower teeth of the first indexing gear 602. At this time, the second indexing operation is completed.Specifically, the upper teeth of the first indexing gear 602 and the lower teeth of the C-axis positioning gear seat 601 have an end-face tooth structure, and the lower teeth of the first indexing gear 602 and the upper teeth of the second indexing gear 603 have an end-face tooth structure; indexing control is achieved through the axial meshing and disengagement of the end-face teeth; the tooth ratio of the external gear 607 to the internal gear 606 is 1:1 to ensure angular accuracy during indexing; the external gear 607 is fixed below the first bevel gear 500, and the internal gear 606 is fixed below the flange seat 605. In some embodiments, the first cylinder 610, the second cylinder 611, and the third cylinder 612 are all double-acting cylinders, and the bidirectional movement of the first piston 608 and the second piston 609 is achieved by controlling the oil inlet and outlet. Using the above scheme, the coordinated action of the first hydraulic cylinder 610, the second hydraulic cylinder 611, and the third hydraulic cylinder 612 realizes an automated process of disengagement, indexing, and re-engagement of the two sets of gear pairs, with high reliability; it enables indexing in both forward and reverse directions, expanding the processing range; and complex indexing actions can be achieved simply by controlling the hydraulic pressure. Indexing process: When pressurized oil is introduced into the first hydraulic cylinder 610, the first piston 608 pushes the second piston 609, the first indexing gear 602, the lower housing 400, and the flange seat 605 downwards by a distance C, realizing the first indexing operation; when pressurized oil is introduced into the second hydraulic cylinder 611, the second indexing operation is realized; when pressurized oil is introduced into the third hydraulic cylinder 612, the reset action after indexing is completed.

[0075] In some embodiments, the top of the upper housing 300 is connected to a female quick-change plug 301 that mates with a female quick-change plug (not shown) of the machine tool slide (not shown in the figure); this is used to transmit the functional paths of the right-angle head to achieve various automation functions. Specifically, the transition sleeve 604 is disposed between the C-axis positioning gear plate seat 601 and the flange seat 605, used to transmit the functional paths while realizing axial relative movement; the transition sleeve 604 has a sealing structure inside to ensure the sealing between the functional paths. Using the above scheme, the female quick-change plug 301 enables rapid docking of the functional paths (oil / gas / electric), shortening the changeover time. In some embodiments, the required functional paths of the right-angle head are introduced through the quick-change plug 301 to the C-axis positioning gear plate seat 601, which is centered and connected to the upper housing 300. Then, through the transition sleeve 604, which is centered and connected to the C-axis positioning gear plate seat 601, the path enters the flange seat 605, and then the lower housing 400. From the lower housing 400, the path enters the external cooling path (not shown in the figure), the nose gas seal 10, the tool changing oil path 20, and the center air blowing path 30, providing power for the various automated functions of the right-angle head. Specifically, the external cooling path and the center air blowing path 30 ensure cooling and cleanliness during the machining process; the tool changing oil path 20 enables automatic tool changing; and the nose gas seal 10 prevents cutting fluid and chips from entering the right-angle head spindle 200. In some embodiments, the right-angle head spindle 200 has an axially arranged coolant channel and a compressed air channel, which communicate with the external cooling path and the center air blowing path 30. The end of the right-angle head spindle 200 is provided with a tool interface conforming to ISO or BT standards. By adopting the above scheme, the isolation transmission of multiple media (external cooling, gas sealing, etc.) is achieved through the centering connection module (C-axis positioning gear plate seat 601 → transition sleeve 604 → flange seat 605 → lower housing 400), thus avoiding interference.

[0076] In some embodiments, the top of the upper housing 300 is provided with a plurality of small pull studs 302. When the machine tool ram (not shown in the figure) approaches the right-angle head, the pull cylinder (not shown in the figure) on the oil receiving plate of the machine tool ram pulls the small pull studs 302 at the corresponding positions on the upper housing 300, completing the pull action. The end of the transmission shaft 100 near the machine tool spindle is provided with a keyway 104. When the machine tool ram approaches the right-angle head, the end face key of the machine tool spindle is inserted into the keyway 104 of the transmission shaft 100, completing the gripping action. In some embodiments, the number of small pull studs 302 is 4, evenly distributed on the top circumference of the upper housing 300. Specifically, after the machine tool completes the gripper action, the end face key (not shown in the figure) of the machine tool spindle is inserted into the keyway 104 of the transmission shaft 100. The machine tool spindle baffle (not shown in the figure) grips the main pull stud 101 above the transmission shaft 100. The centering sleeve 105 on the transmission shaft 100 is lifted by several small springs 106 and contacts the inner hole of the machine tool spindle to achieve centering of the transmission shaft 100. The upper toothed chuck (not shown in the figure) installed on the oil receiving pan (not shown in the figure) meshes with the lower toothed chuck installed on the upper housing 300. Using the above scheme, the small pull stud 302 cooperates with the puller cylinder to complete coarse positioning; the end face key is inserted into the keyway 104 to achieve precise positioning, ensuring the coaxiality of the transmission shaft 100 and the machine tool spindle; the small springs 106 lift the centering sleeve 105 to absorb assembly errors and reduce vibration. The dual positioning mechanism improves the reliability of the system.

[0077] In some embodiments, a spindle pull-out mechanism is further included, which comprises a spindle fixing assembly, a spindle pull-out assembly, and a spindle release assembly, for realizing automatic pull-out and automatic release of the tool. In some embodiments, the spindle fixing assembly includes a front bearing housing 700 arranged axially along the right-angle head spindle 200 and a front spindle bearing 701 fixed in the front bearing housing 700, as well as a rear bearing housing 702 and a rear spindle bearing 703 fixed in the rear bearing housing 702; and the front bearing housing 700 and the rear bearing housing 702 are respectively positioned at both ends of the second bevel gear 501 to balance the radial load of the right-angle head spindle 200 and extend the bearing life. In some embodiments, the spindle broach assembly includes a pull rod assembly disposed within the right-angle head spindle 200. The pull rod assembly includes a broach pawl 801, a pull rod 802 connected to the broach pawl 801, a washer 803 disposed on one end of the pull rod 802 away from the broach pawl 801, a disc spring 804 connected to the washer 803, and a locking nut 805 fixed to the tail of the pull rod 802. The disc spring 804 is constrained by the washer 803 and the limiting seat 201 fixed to the tail of the right-angle head spindle 200, so that the disc spring 804 is in a compressed state. When the right-angle head spindle 200 grips the tool, the first step 8021 on the right side of the pull rod 802 and the left end face of the washer 803 are pulled out by a distance A. At this time, the tool is subjected to the reaction force of the compressive force of the disc spring 804 in the pull rod assembly, thereby realizing the right-angle head broach action. Using the above scheme, the compressed disc spring 804 provides a constant pulling force to prevent the tool from loosening during machining and ensure reliable tool clamping; the setting of distance A ensures that the pulling force is linearly related to the deformation of the disc spring 804, and the clamping force is adjustable.In some embodiments, the spindle tool release assembly includes a rear bearing housing 702, a spring seat 900, a plurality of second springs 901, a third piston 902, a tail end cap 903, and a stop block seat 904; the spring seat 900 is disposed inside the rear bearing housing 702, the second springs 901 are disposed inside the spring seat 900, and the tail end cap 903 is fixed to the outer end of the rear bearing housing 702; one end of each of the second springs 901 is connected to the spring seat 900, and the other end is connected to the third piston 902; the third piston 902 and the stop block seat 904 fixed to the right end of the third piston 902 move to the left under the action of the tool release oil in the tool release oil passage 20, so that the tool release assembly... The impact block 904 moves to the left while the locking nut 805 is being monitored, stopping the cutting action. At this time, the pull rod 802 moves to the left along with the pull pawl 801, opening the pull pawl 801 and completing the cutting action. When the hydraulic pressure in the cutting oil circuit 20 returns to zero, the pull rod assembly moves to the right under the compression force of the disc spring 804, pushing the impact block 904 and the third piston 902 together. After the pull rod assembly reaches its limit, several second springs 901 in the spring seat 900 push the third piston 902 and the impact block 904 to continue moving to the right a distance B, causing the impact block 904 and the locking nut 805 of the pull rod assembly to separate by a small distance, so that the two planes do not contact each other when the right-angle head spindle 200 rotates. Using the above scheme, the hydraulic pressure drives the impact block 904 to achieve rapid cutting; the second springs 901 leave a distance B when resetting to avoid friction between the locking nut 805 and the impact block 904 during rotation, protecting the dynamic balance. Working process: When gripping the tool, the compression force of the disc spring 804 is transmitted to the pull pawl 801 through the pull rod 802 to achieve tool clamping; when releasing the tool, the pressure of the tool release oil circuit 20 pushes the third piston 902 and the impact block seat 904 to move to the left, the pull rod 802 moves the pull pawl 801 to the left, the pull pawl 801 opens, and the tool release action is completed; when the oil pressure returns to zero, the second spring 901 pushes the third piston 902 and the impact block seat 904 to move to the right by a distance B to avoid friction during rotation.

[0078] The same or similar parts between the various embodiments in this specification can be referred to mutually. Each embodiment focuses on describing the differences from other embodiments.

[0079] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. An automatic right-angle head for tooth misalignment, characterized in that: It includes a housing, a drive shaft (100) arranged inside the housing, and a right-angle head spindle (200) connected to the drive shaft (100); the drive shaft (100) and the right-angle head spindle (200) are connected by a transmission mechanism; the housing includes an upper housing (300) and a lower housing (400) arranged vertically. The top end of the drive shaft (100) is provided with a main pull stud (101), which is connected to the machine tool spindle; the bottom end of the drive shaft (100) is provided with a lower pressure cover (102), and a first spring (103) is provided between the lower pressure cover (102) and the drive shaft (100). The transmission mechanism includes a first bevel gear (500) connected to the transmission shaft (100) and a second bevel gear (501) meshing with the first bevel gear (500), the second bevel gear (501) being connected to the right-angle head spindle (200); C-axis indexing mechanism (600) is used to realize the indexing of right-angle head spindle (200) on C-axis. It includes C-axis positioning gear plate seat (601), first indexing gear plate (602), second indexing gear plate (603), transition sleeve (604), flange seat (605), internal gear (606) and external gear (607); the external gear (607) is always meshed with the first bevel gear (500); The C-axis indexing mechanism (600) adopts a staggered tooth differential structure, which includes two sets of upper and lower tooth disk pairs with different indexing, consisting of the C-axis positioning tooth disk seat (601), the first indexing tooth disk (602), and the second indexing tooth disk (603). The differential movement of the two sets of tooth disk pairs realizes the differential indexing. The upper teeth of the first indexing tooth disk (602) can mesh with the lower teeth of the C-axis positioning tooth disk seat (601), and the lower teeth of the first indexing tooth disk (602) can mesh with the upper teeth of the second indexing tooth disk (603). Furthermore, the number of teeth on the upper teeth of the first indexing tooth disk (602) is not equal to the number of teeth on the lower teeth of the first indexing tooth disk (602). The C-axis indexing mechanism (600) further includes a first piston (608) fixed to the first indexing gear (602) and a second piston (609) fixed to the second indexing gear (603); the second piston (609) is disposed opposite to the first piston (608) below; a first hydraulic cylinder (610) is connected to the top of the first piston (608), a second hydraulic cylinder (611) is connected between the first piston (608) and the second piston (609), and a third hydraulic cylinder (612) is connected below the second indexing gear (603); It also includes a spindle tool release and pull mechanism, which includes a spindle fixing assembly, a spindle tool pull assembly, and a spindle tool release assembly, used to realize automatic tool pull and automatic tool release; The spindle broach assembly includes a pull rod assembly disposed within the right-angle head spindle (200). The pull rod assembly includes a broach pawl (801), a pull rod (802) connected to the broach pawl (801), a washer (803) disposed on the end of the pull rod (802) away from the broach pawl (801), a disc spring (804) connected to the washer (803), and a locking nut (805) fixed to the tail of the pull rod (802). The disc spring (804) The disc spring (804) is compressed between the pad (803) and the limiting seat (201) fixed on the tail of the right-angle head spindle (200). When the right-angle head spindle (200) grabs the tool, the first step (8021) on the right side of the pull rod (802) and the left end face of the pad (803) will be pulled out by a distance A. At this time, the tool will be subjected to the reaction force of the compression force of the disc spring (804) in the pull rod assembly, realizing the right-angle head pull action. The spindle tool release assembly includes a rear bearing housing (702), a spring seat (900), several second springs (901), a third piston (902), a tail end cap (903), and a stop block seat (904); the spring seat (900) is disposed inside the rear bearing housing (702), several second springs (901) are disposed inside the spring seat (900), and the tail end cap (903) is fixed to the outer end of the rear bearing housing (702); one end of the second spring (901) is connected to the spring seat (900), and the other end is connected to the third piston (902); The third piston (902) and the impact block seat (904) fixed on the right end of the third piston (902) move to the left under the action of the impact oil in the impact oil circuit (20), so that the impact block seat (904) pushes against the locking nut (805) and moves to the left, and the impact action stops. At this time, the pull rod (802) moves to the left with the pull claw (801), and the pull claw (801) opens to complete the impact action. When the oil pressure in the cutter oil circuit (20) returns to zero, the pull rod assembly moves to the right under the compression force of the disc spring (804), pushing against the impact block seat (904) and the third piston (902) together. After the pull rod assembly moves to its limit, several second springs (901) in the spring seat (900) push against the third piston (902) and the impact block seat (904) to continue moving to the right a distance B, so that the impact block seat (904) and the locking nut (805) of the pull rod assembly are pulled apart by a small distance, so that when the right-angle head spindle (200) rotates, the two planes do not come into contact.

2. The automatic right-angle head for tooth misalignment differential as described in claim 1, characterized in that: The first indexing gear (602) has 144 teeth on its upper teeth and 150 teeth on its lower teeth, so that the minimum indexing angle achieved by the differential motion of the two sets of gear pairs of the C-axis indexing mechanism (600) is 360°÷144-360°÷150=0.1°.

3. The automatic right-angle head for tooth misalignment differential as described in claim 1, characterized in that: When pressurized oil enters the first cylinder (610), the first piston (608) pushes the second piston (609), the first indexing gear (602), the lower housing (400), and the flange seat (605) to move downwards by a distance C, so that the lower teeth of the C-axis positioning gear seat (601) disengage from the upper teeth of the first indexing gear (602), and the lower teeth of the first indexing gear (602) mesh with the upper teeth of the second indexing gear (603). The internal gear (606) fixed below the flange seat (605) meshes with the external gear (607) fixed below the first bevel gear (500). At this time, the machine tool spindle drives the transmission shaft (100) to rotate clockwise, and the power... The first bevel gear (500) and the external gear (607) can transmit power to the internal gear (606). The internal gear (606) drives the flange seat (605), the lower housing (400), the second indexing gear (603), and the first indexing gear (602) to rotate. After rotating to the required angle, the third cylinder (612) injects pressurized oil. The second indexing gear (603) carries the lower housing (400), the flange seat (605), and the internal gear (606) to push the first indexing gear (602) to move upward a distance C, so that the upper teeth of the first indexing gear (602) mesh with the lower teeth of the C-axis positioning gear seat (601). At this time, the first indexing operation is completed. When the second cylinder (611) receives pressurized oil, the first piston (608) and the first indexing gear (602) are subjected to an upward force, causing the upper teeth of the first indexing gear (602) to mesh with the lower teeth of the C-axis positioning gear seat (601); and the second piston (609) is subjected to a downward force, causing the second indexing gear (603), the lower housing (400), the flange seat (605), and the internal gear (606) to move downward a distance C, so that the internal gear (606) meshes with the external gear (607) fixed below the first bevel gear (500); at this time, the machine tool spindle drives the transmission shaft (1 00) Rotate counterclockwise. Power is transmitted to the internal gear (606) through the first bevel gear (500) and the external gear (607). The internal gear (606) drives the flange seat (605), the lower housing (400) and the second indexing gear (603) to rotate. After rotating to the required angle, the third cylinder (612) injects pressurized oil. The second indexing gear (603) moves the lower housing (400), the flange seat (605) and the internal gear (606) upward by a distance C, so that the upper teeth of the second indexing gear (603) mesh with the lower teeth of the first indexing gear (602). At this time, the second indexing operation is completed.

4. The automatic right-angle head for tooth misalignment differential as described in claim 1, characterized in that: The top of the upper housing (300) is connected to a female quick-change plug (301) that mates with the female quick-change plug of the machine tool slide.

5. The automatic right-angle head for tooth misalignment differential as described in claim 4, characterized in that: The required functional paths of the right-angle head are introduced through the sub-quick-change plug (301) to the C-axis positioning gear plate seat (601) which is centered and connected to the upper housing (300), and then through the transition sleeve (604) which is centered and connected to the C-axis positioning gear plate seat (601) to the flange seat (605), and then into the lower housing (400). Through the lower housing (400), the path enters the external cooling path, the nose gas seal (10), the cutting tool oil path (20), and the center air blowing path (30), providing power for the various automated functions of the right-angle head.

6. The automatic right-angle head for tooth misalignment differential as described in claim 1, characterized in that: The top of the upper housing (300) is provided with several small pull studs (302). When the machine tool slide approaches the right angle head, the pull head cylinder on the oil receiving plate of the machine tool slide pulls the small pull studs (302) at the corresponding position on the upper housing (300) to complete the pull head action. The drive shaft (100) has a keyway (104) at one end near the machine tool spindle. When the machine tool ram approaches the right-angle head, the end face key of the machine tool spindle is inserted into the keyway (104) of the drive shaft (100) to complete the gripping action.

7. The automatic right-angle head for tooth misalignment differential as described in claim 1, characterized in that: The spindle fixing assembly includes a front bearing housing (700) and a front spindle bearing (701) fixed in the front bearing housing (700) and a rear bearing housing (702) and a rear spindle bearing (703) fixed in the rear bearing housing (702); and the front bearing housing (700) and the rear bearing housing (702) are respectively located at both ends of the second bevel gear (501).

Images