Hydraulic nut for assembling conical hole bearing

Abstract

The application discloses a hydraulic nut for assembling a conical hole bearing, and relates to the field of assembling equipment.The hydraulic nut is used for mounting the conical hole bearing on a shaft neck, and comprises a nut body, a connecting piece, an anti-withdrawal pin, a nut piston and a push ring.An annular groove is arranged on one side of the nut body, and the nut piston is slidably arranged in the annular groove, so that the nut body and the nut piston are axially overlapped, the overall axial dimension is significantly compressed under the premise of not reducing the effective thread length and the end face bearing area of the connecting piece, the compactness and the bearing capacity are considered, the anti-rotation section is abutted against the nut body, the axial bearing pressure effect is achieved, the anti-rotation section of the connecting piece is matched with the matching section on the back side of the nut body, the circumferential anti-rotation effect is achieved, and the anti-withdrawal pin achieves the axial anti-withdrawal effect.Three functions of the axial bearing pressure, the circumferential anti-rotation and the axial anti-withdrawal are distributed to independent structural units to bear, and stress concentration and micro-motion wear hidden dangers caused by the composite load are effectively eliminated.

Description

Technical Field

[0001] This application relates to the field of assembly equipment, and more particularly to a hydraulic nut for assembling tapered bore bearings. Background Technology

[0002] Hydraulic nuts are core specialized hydraulic tools for the installation, disassembly, and pre-tightening adjustment of large interference fit components. They use high-pressure hydraulic oil to drive the piston of the hydraulic nut to generate axial displacement, applying a stable and controllable axial thrust to the component to be assembled, thereby achieving high-precision, low-damage interference fit assembly. For details, please refer to the paper "Application of Hydraulic Nuts in Assembly Technology of Tapered Bore Rolling Bearings" published by Wang Yanpeng et al.

[0003] The existing hydraulic nuts have the following problems: 1. In order to facilitate quick adaptation to specific journal specifications, existing hydraulic nuts have a replaceable threaded connector on one side of their axial direction. The threaded connector is threaded to the journal. This axial series structure inevitably increases the overall axial dimension and requires space conditions to be met before it can be used. If the axial length of the threaded connector is reduced to gain space, the effective thread engagement length and bearing area will be reduced simultaneously, which can easily lead to thread shear failure under ultra-high pressure. 2. In the existing solution, the three functions of axial bearing, circumferential anti-rotation and axial anti-disengagement are undertaken by the same position. This position is in a composite load field of tension, compression, shear and alternating vibration, which can easily induce fretting wear and local yielding at the contact interface, causing potential reliability risks to the structure. 3. The existing solution only focuses on the adaptation design when different journal specifications change, and ignores the adaptation design when the bearing inner ring end face size changes. Utility Model Content

[0004] This application provides a hydraulic nut for assembling tapered bore bearings to solve the above-mentioned technical problems.

[0005] This application provides a hydraulic nut for assembling tapered bore bearings, including a nut body, a connecting member, an anti-disengagement pin, a nut piston, and a push ring. The first axial end face of the nut body is provided with an annular groove around its axis, and the second axial end face of the nut body is provided with a mating section. The connecting member includes a threaded section and an anti-rotation section coaxially connected. The threaded section is coaxially sleeved and threadedly connected to an external journal, and the anti-rotation section is sleeved on the mating section to restrict the mating section from rotating around its own axis. The anti-rotation section abuts against the second axial end face of the nut body. The anti-disengagement pin connects the mating section and the threaded section to restrict the nut body and the threaded section from axially disengaging. The nut piston is slidably disposed in the annular groove along the axial direction, forming an annular oil cavity between the nut piston and the annular groove. A high-pressure oil inlet channel disposed in the nut body is connected to the annular oil cavity and an external hydraulic source. The push ring is disposed on the side of the nut piston away from the nut body through a quick-release structure for contacting the tapered bore bearing.

[0006] Preferably, the mating section is provided with a keyway, and the anti-rotation section is provided with a spline. The spline is located in the keyway to restrict the mating section from rotating around its own axis.

[0007] Preferably, multiple keyways are spaced apart around the axial direction, and splines are set in one-to-one correspondence with keyways.

[0008] Preferably, a tapered head is provided at the end of the mating section facing the threaded section.

[0009] Preferably, the axial length of the anti-rotation section is greater than the length of the mating section, so that the fourth axial end face of the anti-rotation section can fit against the second axial end face (103) of the nut body.

[0010] Preferably, the second axial end face of the nut body is provided with an annular mounting groove, and a pressure-bearing pad ring is coaxially provided in the annular mounting groove, the pressure-bearing pad ring being in contact with the fourth axial end face of the anti-rotation section.

[0011] Preferably, the anti-loosening pin is configured as a quick-release pin with a steel ball spring at one end; along the axial direction, both the mating section and the threaded section of the nut body are provided with pin holes, and the mating section is also provided with a radial locking hole that connects to the pin hole in the radial direction. The anti-loosening pin is set in the pin holes of the mating section and the threaded section, and the steel ball on the anti-loosening pin protrudes into the radial locking hole to restrict the axial position of the mating section and the threaded section.

[0012] Preferably, the inner diameter of the radial lock hole is larger than the outer diameter of the steel ball.

[0013] Preferably, the pin hole provided on the threaded section is a waist-shaped hole, and the length direction of the waist-shaped hole is consistent with the circumferential direction of the threaded section.

[0014] Preferably, the quick-release structure includes a locating pin disposed on the push ring; the fifth axial end face of the nut piston is provided with a tapered hole, a rotary guide groove, and a locating hole that cooperate with the locating pin, the large end of the tapered hole faces the locating pin, the length direction of the rotary guide groove is consistent with the circumferential direction of the nut piston, and the two ends of the length direction of the rotary guide groove are respectively connected to the tapered hole and the locating hole; the length of the locating pin is configured as H1, the depth of the tapered hole and the rotary guide groove is configured as H2, and the depth of the locating hole is configured as H3, where H2 < H1 < H3.

[0015] The hydraulic nut of this application has at least the following beneficial effects: (1) The hydraulic nut of this application has an annular groove on one side of the nut body, and the nut piston is slidably disposed in the annular groove, so that the nut body and the nut piston overlap at least partially in the axial direction. Without reducing the effective thread length and end face bearing area of ​​the connector, the overall axial dimension is significantly compressed, taking into account both compactness and bearing capacity. It is especially suitable for heavy-duty assembly scenarios where axial space is severely limited. On the other hand, the anti-rotation section abuts against the second axial end face of the nut body in the axial direction, playing an axial bearing role. The anti-rotation section of the connector cooperates with the mating section on the back side of the nut body to play a circumferential anti-rotation role. The anti-disengagement pin connects the mating section and the threaded section respectively to play an axial anti-disengagement role. This application effectively eliminates the stress concentration and fretting wear hazards caused by the composite load by distributing the three functions of axial bearing, circumferential anti-rotation and axial anti-disengagement to independent structural units. The push ring set at the front end of the nut piston is installed through a quick-release structure and can be quickly replaced to adapt to the changes in the end face size of different bearing inner rings.

[0016] (2) This application differs from the paper "Application of Hydraulic Nut in Assembly Technology of Tapered Bore Rolling Bearing" as follows: 1. The connecting parts are designed in a two-section design. The threaded section can quickly match journals of different specifications. The anti-rotation section is used to restrict the rotation of the nut body and the mating section on the back side of the nut body. At the same time, the end face of the anti-rotation section is in contact with the back side of the nut body to play an axial bearing role. It should be noted that there is no independent end face bearing structure in the paper. The load is borne by the thread interface. That is, the hydraulic nut in the paper is directly threaded to the journal, while in this application it is connected to the journal through the threaded section; 2. The push ring and nut piston of this application adopt a split quick-release design, which can be quickly replaced according to the bearing specifications. Furthermore, a quick-release structure is designed to realize the quick disassembly and assembly of the push ring. Attached Figure Description

[0017] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this application. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings: Figure 1 This is a cross-sectional view of the hydraulic nut of this application. Figure 1 ; Figure 2 This is a cross-sectional view of the hydraulic nut of this application. Figure 2 ; Figure 3 This is an exploded view of the connector and nut body of this application; Figure 4 These are front views of the push ring and nut piston of this application, (A) representing the front view of the nut piston and (B) representing the front view of the push ring; Figure 5The diagram shows the process of assembling the push ring onto the nut piston. (A) shows a schematic diagram after the locating pin is inserted into the tapered hole, (B) shows a schematic diagram after the locating pin moves into the rotary guide groove, and (C) shows a schematic diagram after the locating pin is inserted into the locating hole. The annotations in the attached figures are explained as follows: 100. Nut body; 101. First axial end face; 102. Annular groove; 103. Second axial end face; 104. Mating section; 105. High-pressure oil inlet channel; 106. Third axial end face; 107. Keyway; 108. Conical head; 109. Annular mounting groove; 1010. Pressure bearing ring; 200. Connector; 201. Threaded section; 202. Anti-rotation section; 203. Spline; 204. Fourth axial end face; 300. Anti-detachment pin; 301. Pin hole; 302. Radial locking hole; 303. Steel ball; 400. Nut piston; 401. Tapered hole; 402. Rotary guide groove; 403. Positioning hole; 404. Fifth axial end face; 500, push ring; 501, positioning pin; 600, journal; 700. Bearings. Detailed Implementation

[0018] The features and exemplary embodiments of various aspects of this application will be described in detail below. To make the objectives, technical solutions, and advantages of this application clearer, the application will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are only intended to explain this application and not to limit it. For those skilled in the art, this application can be implemented without some of these specific details. The following description of the embodiments is merely to provide a better understanding of this application by illustrating examples.

[0019] It should be noted that, in this document, relational terms such as "first" and "second" are used merely to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising..." does not exclude the presence of additional identical elements in the process, method, article, or apparatus that includes the element.

[0020] like Figure 1 As shown, this embodiment discloses a hydraulic nut for assembling a tapered bore bearing 700, used to install the tapered bore bearing 700 (hereinafter referred to as the bearing) onto a journal 600. The hydraulic nut includes a nut body 100, a connector 200, an anti-disengagement pin 300, a nut piston 400, and a push ring 500.

[0021] like Figure 2 As shown, the nut body 100 is an annular structure, which is coaxially sleeved on the journal 600. The two end faces of the nut body 100 perpendicular to the axial direction are respectively configured as a first axial end face 101 and a second axial end face 103. The first axial end face 101 is provided with an annular groove 102, which is configured as a groove formed around the axial direction and has a rectangular cross-sectional shape. The second axial end face 103 is coaxially provided with a mating section 104.

[0022] like Figure 2 and Figure 3 As shown, the mating section 104 is integrally formed with the nut body 100. The mating section 104 is cylindrical in shape. A keyway 107 is provided on the outer circumferential surface of the mating section 104. The length direction of the keyway 107 is parallel to the axial direction. Preferably, there are multiple keyways 107, which are arranged at equal intervals around the axial direction.

[0023] like Figure 2 and Figure 3 As shown, in this embodiment, a tapered head 108 is provided at one end of the mating section 104 facing the connector 200. The small end of the tapered head 108 faces the connector 200 and serves as a guide so that the mating section 104 can be quickly and coaxially inserted with the anti-rotation section 202 of the connector 200. More preferably, the anti-rotation section 202 is provided with an inner tapered surface that slides with the tapered head 108.

[0024] like Figure 2 and Figure 3As shown, the connector 200 includes a threaded section 201 and an anti-rotation section 202 arranged sequentially along the axial direction. The threaded section 201 and the anti-rotation section 202 are integrally formed and both are made of metal. The threaded section 201 is coaxially sleeved on the journal 600 and threadedly connected to the journal 600. The anti-rotation section 202 is coaxially arranged on the side of the threaded section 201 facing the nut body 100. The anti-rotation section 202 is cylindrical in shape, with an inner diameter larger than the outer diameter of the mating section 104. The inner circumferential surface of the anti-rotation section 202 is provided with... There is a spline 203, the length direction of the spline 203 is parallel to the axial direction. Preferably, the number of splines 203 corresponds one-to-one with the number of keyways 107 on the mating section 104. During installation, the tapered head 108 of the mating section 104 faces the anti-rotation section 202 and is coaxially inserted into the anti-rotation section 202. During insertion, the keyways 107 and splines 203 are aligned one-to-one, so that the splines 203 can slide into the keyways 107, thereby restricting relative rotation between the mating section 104 and the anti-rotation section 202.

[0025] like Figure 2 and Figure 3 As shown, the fourth axial end face 204 (the end face perpendicular to the axial direction) of the anti-rotation section 202 abuts against the second axial end face 103 of the nut body 100 to provide axial bearing. To ensure that the fourth axial end face 204 of the anti-rotation section 202 can still make contact with the second axial end face 103 even in the event of machining errors or other fitting errors, the axial length of the anti-rotation section 202 is designed to be greater than the axial length of the fitting section 104. Since the axial length of the anti-rotation section 202 is greater than that of the fitting section 104, there is a compensating gap H in the axial direction between the third axial end face 106 of the tapered head 108 of the fitting section 104 and the inner end face of the threaded section 201. This compensating gap H can achieve physical isolation between the fitting section 104 and the threaded section 201, ensuring that the axial main load transmission path formed by the anti-rotation section 202 and the nut body 100 is preferentially established.

[0026] like Figure 2 As shown, the anti-rotation section 202 can directly abut against the second axial end face 103 of the nut body 100, or it can indirectly abut against it through other components. In this embodiment, preferably, the second axial end face 103 of the nut body 100 is provided with an annular mounting groove 109, which coaxially surrounds the outside of the mating section 104. A pressure-bearing washer 1010 is detachably provided in the annular mounting groove 109. After the pressure-bearing washer 1010 is installed in the annular mounting groove 109, the end face of the pressure-bearing washer 1010 is flush with the second axial end face 103, and the fourth axial end face 204 of the anti-rotation section 202 abuts against the end face of the pressure-bearing washer 1010. In this embodiment, by designing the pressure-bearing washer 1010 to directly contact the anti-rotation section 202, it plays a role in axial bearing. The pressure-bearing washer 1010 can be quickly replaced according to the wear condition without replacing the entire nut body 100.

[0027] In this preferred embodiment, the pressure-bearing ring 1010 adopts a two-layer structure stacked along the axial direction. The layer facing the anti-rotation section 202 is a high-hardness wear-resistant layer to resist repeated contact wear. The layer facing the nut body 100 is a plastic adaptive layer. The yield strength of this plastic adaptive layer is lower than that of the nut body 100. When assembly misalignment occurs, the local plastic deformation of the plastic adaptive layer achieves end-face stress homogenization, protecting the nut body 100 from crushing and wear. The specific material of the high-hardness wear-resistant layer can be selected from carburized and quenched steel, nitrided steel, or cemented carbide, etc., and the specific material of the plastic adaptive layer can be selected from aluminum alloy.

[0028] like Figure 2 As shown, the anti-loosening pin 300 is used to limit the relative axial position of the mating section 104 on the back side of the nut body 100 and the threaded section 201 of the connector 200. The anti-loosening pin 300 is configured as a quick-release pin with a steel ball spring in the prior art. In order to facilitate understanding of the solution of this embodiment, the quick-release pin with a steel ball spring is briefly introduced below. The quick-release pin is cylindrical in shape. A radially recessed groove is provided at the end of the quick-release pin. A spring and a steel ball 303 are provided in the groove. When the steel ball 303 is subjected to an external force and the external force is sufficient to overcome the work done by the spring, the steel ball 303 can retract into the groove.

[0029] The specific installation method of quick-release pins is as follows: Figure 2 As shown, both the mating section 104 and the threaded section 201 are provided with pin holes 301. The pin holes 301 on the threaded section 201 are through holes along the axial direction, while the pin holes 301 on the mating section 104 are blind holes along the axial direction. The pin holes 301 on the mating section 104 and the threaded section 201 are correspondingly arranged in the axial direction. Furthermore, the mating section 104 is also provided with a radial locking hole 302 that communicates with the pin holes 301 inside the mating section 104 along the radial direction. When a quick-release pin needs to be installed, the quick-release pin passes through the pin holes 301 of the threaded section 201 and the mating section 104 in sequence along the axial direction. During this process, the steel ball 303 is restricted by the inner wall of the pin hole 301 and remains in a retracted state. When the steel ball 303 at the end of the quick-release pin moves to the position of the pin hole 302, the quick-release pin will automatically retract. When the ball is within the radial locking hole 302, under the action of the spring, some of the steel balls 303 pop out and extend into the radial locking hole 302. The outer circumferential surface of the steel ball 303 can abut against the inner circumferential surface of the radial locking hole 302, thereby restricting the quick release pin from axial withdrawal to a certain extent, and thus restricting the axial position of the mating section 104 and the threaded section 201. Since the mating section 104 and the threaded section 201 are not subjected to a large axial separation force, it is only necessary to restrict their relative position by means of the spring. When the quick release pin needs to be removed, pull the quick release pin with force so that the steel ball 303 contacts the inner circumferential surface of the radial locking hole 302 and the force is sufficient to overcome the work done by the spring, so that the steel ball 303 can retract back into the groove.

[0030] Preferred, such as Figure 2 As shown, the inner diameter of the radial locking hole 302 is larger than the outer diameter of the steel ball 303. When the steel ball 303 is inserted into the radial locking hole 302, there is a margin of movement between the hole wall and the steel ball 303. When the connector 200 has a slight displacement tendency under the action of axial force, the steel ball 303 can float axially in the radial locking hole 302, which blocks the axial force from being transmitted to the pin through the steel ball 303 from the geometric structure, thus avoiding stress on the quick-release pin.

[0031] Preferred, such as Figure 3 As shown, the pin hole 301 on the threaded section 201 is machined into an oblong hole. The length direction of the oblong hole is consistent with the circumferential direction of the threaded section 201. When the mating section 104 and the threaded section 201 are misaligned by a small angle in the circumferential direction, the anti-disengagement pin 300 can also move within the range of the oblong hole to a suitable position to align with and insert into the pin hole 301 on the mating section 104. This design can improve the flexibility of the structure. On the other hand, the oblong hole design can also prevent the anti-disengagement pin 300 from being subjected to shearing force due to the slight circumferential rotation of the mating section 104 during operation.

[0032] like Figure 2 As shown, at least a portion of the nut piston 400 is coaxially slidably disposed within the annular groove 102 of the nut body 100. This portion of the nut piston 400 disposed within the annular groove 102 forms a sealed annular oil cavity with the inner circumferential surface of the annular groove 102. A high-pressure oil inlet channel 105 is also provided within the nut body 100. One end of the high-pressure oil inlet channel 105 communicates with the annular oil cavity, and the other end communicates with an external hydraulic source. When the external hydraulic source inputs high-pressure oil into the annular oil cavity, the nut piston 400 is driven axially, thereby causing the bearing 700 to move relative to the journal 600, thus assembling the bearing 700. Preferably, a sealing ring is provided on this portion of the nut piston 400 disposed within the annular groove 102. This sealing ring contacts the inner circumferential surface of the annular groove 102 to achieve a sliding seal between the nut piston 400 and the annular groove 102.

[0033] In this embodiment, the overall axial dimension is significantly compressed without reducing the effective thread length by using a nested arrangement of the nut body 100 and the nut piston 400.

[0034] like Figure 2 As shown, the push ring 500 is set on the side of the nut piston 400 away from the nut body 100 through a quick-release structure. The push ring 500 and the nut piston 400 are coaxially arranged. The push ring 500 can be quickly replaced through the quick-release structure. Different specifications of push ring 500 can correspond to different specifications of bearing 700 inner ring end face size. All different specifications of push ring 500 are detachably connected to the nut piston 400 through the quick-release structure.

[0035] like Figure 4 As shown, the quick-release structure includes a circular positioning pin 501, which is fixedly set on the side of the push ring 500 facing the nut piston 400. The positioning pin 501 is parallel to the axial direction. The fifth axial end face of the nut piston 400 facing the push ring 500 is provided with a tapered hole 401, a rotary guide groove 402, and a positioning hole 403 that cooperate with the positioning pin 501. The positioning hole 403, the tapered hole 401, and the rotary guide groove 402 are on the same arc line, and the depth direction is all configured in the axial direction. The large end of the tapered hole 401 faces the positioning pin 501. The rotary guide groove 402 is an arc-shaped groove whose length direction (i.e., arc direction) is configured in the circumferential direction of the nut piston 400. The two ends of the rotary guide groove 402 in the length direction are respectively connected to the tapered hole 401 and the positioning hole 403. The positioning hole 403 can be clearance-fitted with the positioning pin 501.

[0036] In this embodiment, as Figure 4 As shown, there are multiple positioning pins 501, which are evenly spaced along the circumference of the push ring 500. This embodiment illustrates three positioning pins 501, each of which is provided with a conical hole 401, a rotary guide groove 402, and a positioning hole 403 that cooperate with it.

[0037] In this embodiment, the axial length of the positioning pin 501 is configured as H1, the depth of the tapered hole 401 and the rotary guide groove 402 are both configured as H2, and the depth of the positioning hole 403 is configured as H3.

[0038] When installing the push ring 500, the locating pin 501 is aligned one-to-one with the tapered hole 401. Since the larger end of the tapered hole 401 faces the locating pin 501, it can play a guiding and positioning role. The locating pin 501 is inserted axially into the tapered hole 401. Figure 5 As shown in (A), since the length of the locating pin 501 is greater than the depth of the tapered hole 401, there is a gap between the axial end face of the push ring 500 and the fifth axial end face 404 of the nut piston 400 after the locating pin 501 touches the bottom. After the locating pin 501 touches the bottom, the push ring 500 rotates circumferentially, and the locating pin 501 moves from the tapered hole 401 into the rotary guide groove 402, as shown in (A). Figure 5 As shown in (B), the positioning pin 501 is guided from the tapered hole 401 to the positioning hole 403 by the rotating guide groove 402, and the length of the positioning pin 501 is also greater than the depth of the rotating guide groove 402. Therefore, during rotation, the axial end face of the push ring 500 and the fifth axial end face 404 of the nut piston 400 remain in a non-fitted state. When the positioning pin 501 rotates into the positioning hole 403, it axially pushes the push ring 500, and the positioning pin 501 is pushed into the positioning hole 403, as shown in (B). Figure 5As shown in (C), since the length of the positioning pin 501 is less than the depth of the positioning hole 403, the positioning pin 501 can be fully inserted into the positioning hole 403 so that the axial end face of the push ring 500 fits against the fifth axial end face 404 of the nut piston 400, ensuring uniform force distribution.

[0039] In this embodiment, the push ring 500 can be quickly disassembled and installed without the aid of tools by means of the above method, and the difficulty of drilling and installation can be reduced by the guiding effect of the tapered hole 401 and the rotary guide groove 402.

[0040] More preferably, the outer diameter of the locating pin 501 is configured as D1, the inner diameter of the large port of the tapered hole 401 is 1.2 to 3 times that of D1, the inner diameter of the small port of the tapered hole 401 and the inner width of the rotary guide groove 402 are 1.05 to 1.2 times that of D1, and the inner diameter of the locating hole 403 is 1.01 to 1.1 times that of D1.

[0041] The assembly process in this embodiment is as follows: Based on the specifications of journal 600 and the inner ring end face dimensions of bearing 700, select the corresponding specifications for connector 200 and push ring 500. Install the selected push ring 500 on the front end of nut piston 400. Then, align the anti-rotation section 202 of connector 200 with the mating section 104 on the back of nut body 100. Insert the tapered head 108 of mating section 104 into anti-rotation section 202 first, and then rotate nut body 100 so that the pin hole 301 on mating section 104 is axially aligned or nearly aligned with the pin hole 301 on threaded section 201. Align the keyway 107 on the upper part with the spline 203 on the inner side of the anti-rotation section 202, and then push the mating section 104 into the anti-rotation section 202 along the axial direction until the fourth axial end face 204 of the anti-rotation section 202 abuts against the pressure washer ring 1010 on the back side of the nut body 100. Then, insert the anti-disengagement pin 300 from the rightmost end of the connector 200 into the pin hole 301 of the thread section 201 and the mating section 104 along the axial direction. When the steel ball 303 on the anti-disengagement pin 300 is aligned with the radial locking hole 302, it springs in and locks, completing the axial anti-disengagement locking. At this time, the hydraulic nut assembly is completed. The hydraulic nut is fitted onto the journal 600, the hydraulic nut is rotated as a whole, and tightened onto the journal 600 through the threaded section 201 of the connector 200. During the tightening process, the push ring 500 gradually approaches the bearing 700 or fits against the inner ring end face of the bearing 700 along the axial direction. The pipeline and connector of the external hydraulic source (such as a hydraulic pump station) are connected to the high-pressure oil inlet channel 105. High-pressure oil is injected into the annular oil chamber through the high-pressure oil inlet channel 105, which pushes the nut piston 400 to produce axial displacement. The nut piston 400 drives the push ring 500 to push the bearing 700 to move axially along the journal 600 until the preset interference fit is achieved.

[0042] When it is necessary to replace the thrust ring 500 or the connector 200, first remove the hydraulic pressure, pull out the anti-disengagement pin 300 (it can be pulled out by hand or with the help of a tool), remove the mating section 104 from the anti-rotation section 202, and then unscrew the connector 200 from the journal 600. Then, select and replace the parts of the corresponding specifications according to the actual needs and assemble them in the above manner.

[0043] The working principle of this embodiment is as follows: Circumferential anti-rotation path: achieved by spline 203 and keyway 107, which can transmit circumferential torque and provide radial coaxial positioning. The meshing length is designed based on the maximum transmitted torque. Spline 203 does not participate in the transmission of axial load. Axial bearing path: It is achieved through the anti-rotation section 202 and the bearing washer ring 1010 set on the back side of the nut body 100. The fourth axial end face 204 of the anti-rotation section 202 is in contact with the bearing washer ring 1010, forming the only transmission path of the axial main reaction force, which bears all the axial main load generated during the hydraulic assembly process. In the working state, the high-pressure hydraulic oil drives the hydraulic nut piston 400 to generate axial thrust. This thrust is transmitted to the inner ring end face of the bearing 700 through the push ring 500. The reaction force of the thrust on the bearing 700 is transmitted to the internal thread of the thread section 201 through the journal 600, and then transmitted to the nut body 100 through the fourth axial end face 204 of the mating section 104 and the bearing washer ring 1010, forming an axial load closed loop.

[0044] Axial anti-detachment path: achieved through the cooperation of anti-detachment pin 300 and radial locking hole 302.

[0045] The above description is merely a specific implementation of this application. Those skilled in the art will clearly understand that, for the sake of convenience and brevity, the specific working processes of the systems, modules, and units described above can be referred to the corresponding processes in the foregoing method embodiments, and will not be repeated here. It should be understood that the protection scope of this application is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in this application, and these modifications or substitutions should all be covered within the protection scope of this application.

Claims

1. A hydraulic nut for assembling tapered bore bearings, characterized in that, include: The nut body (100) has an annular groove (102) around its axis on its first axial end face (101) and a mating section (104) on its second axial end face (103). The connector (200) includes a threaded section (201) and an anti-rotation section (202) that are coaxially connected. The threaded section (201) is coaxially sleeved and threadedly connected to the external journal (600). The anti-rotation section (202) is sleeved on the mating section (104) and is used to restrict the mating section (104) from rotating around its own axis. The anti-rotation section (202) abuts against the second axial end face (103) of the nut body (100). Anti-disengagement pin (300), connecting mating section (104) and threaded section (201), used to prevent the nut body (100) and threaded section (201) from disengaging axially; The nut piston (400) is axially slidably disposed in the annular groove (102), and an annular oil cavity is formed between the nut piston (400) and the annular groove (102). The high-pressure oil inlet channel (105) disposed in the nut body (100) is connected to the annular oil cavity and the external hydraulic source respectively. The push ring (500) is located on the side of the nut piston (400) away from the nut body (100) via a quick-release structure and is used to contact the tapered bore bearing (700).

2. The hydraulic nut according to claim 1, characterized in that, The mating section (104) is provided with a keyway (107), and the anti-rotation section (202) is provided with a spline (203). The spline (203) is located in the keyway (107) to restrict the mating section (104) from rotating around its own axis.

3. The hydraulic nut according to claim 2, characterized in that, Multiple keyways (107) are spaced apart around the axial direction, and the spline (203) is arranged in a one-to-one correspondence with the keyway (107).

4. The hydraulic nut according to claim 3, characterized in that, A tapered head (108) is provided at one end of the mating section (104) facing the threaded section (201).

5. The hydraulic nut according to claim 4, characterized in that, The axial length of the anti-rotation section (202) is greater than the length of the mating section (104) so ​​that the fourth axial end face (204) of the anti-rotation section (202) can fit against the second axial end face (103) of the nut body (100).

6. The hydraulic nut according to claim 5, characterized in that, The second axial end face (103) of the nut body (100) is provided with an annular mounting groove (109), and a pressure-bearing pad ring (1010) is coaxially provided in the annular mounting groove (109). The pressure-bearing pad ring (1010) fits against the fourth axial end face (204) of the anti-rotation section (202).

7. The hydraulic nut according to claim 1, characterized in that, The anti-detachment pin (300) is configured as a quick-release pin with a steel ball spring at one end; Along the axial direction, the mating section (104) and the threaded section (201) of the nut body (100) are provided with pin holes (301). The mating section (104) is also provided with a radial locking hole (302) that connects to the pin hole (301) in the radial direction. The anti-detachment pin (300) is provided in the pin holes (301) of the mating section (104) and the threaded section (201). The steel ball (303) on the anti-detachment pin (300) protrudes into the radial locking hole (302) to restrict the axial position of the mating section (104) and the threaded section (201).

8. The hydraulic nut according to claim 7, characterized in that, The inner diameter of the radial lock hole (302) is larger than the outer diameter of the steel ball (303).

9. The hydraulic nut according to claim 7, characterized in that, The pin hole (301) provided on the threaded section (201) is a waist-shaped hole, and the length direction of the waist-shaped hole is consistent with the circumferential direction of the threaded section (201).

10. The hydraulic nut according to claim 1, characterized in that, The quick-release structure includes a positioning pin (501) set on the push ring (500); the fifth axial end face (404) of the nut piston (400) is provided with a tapered hole (401), a rotary guide groove (402) and a positioning hole (403) that cooperate with the positioning pin (501). The large end of the tapered hole (401) faces the positioning pin (501). The length direction of the rotary guide groove (402) is consistent with the circumferential direction of the nut piston (400). The two ends of the length direction of the rotary guide groove (402) are respectively connected to the tapered hole (401) and the positioning hole (403). The length of the locating pin (501) is configured as H1, the depth of the tapered hole (401) and the rotary guide groove (402) are both configured as H2, and the depth of the locating hole (403) is configured as H3, where H2 < H1 < H3.

Images