A clamping fixture for a centrifugal compressor guide vane

Abstract

This application relates to the field of machining technology, and in particular to a clamping fixture for a centrifugal compressor guide vane. The fixture includes a base plate, a drive device connected to the center of the base plate, and several equal-height blocks and displacement drive components arranged at intervals extending outwards from the drive device. The output end of the drive device simultaneously engages with the input ends of the multiple displacement drive components. Each displacement drive component includes a screw, one end of which is coaxially connected to a transmission unit, and the other end is connected to the base plate via a support unit. A slider is helically connected to the top of the screw, and its bottom is slidably connected to a slide rail. Several limiting parts are provided on the top of the slider along the screw axial direction, one of which is connected to a chuck. This application improves the versatility of the fixture by using equal-height blocks of varying lengths in conjunction with adjustable-position chucks. Furthermore, each chuck can synchronously move and clamp the workpiece under the action of the drive device, offering advantages such as compact structure, stable clamping, and high reliability.

Description

Technical Field

[0001] This application relates to the field of machining technology, and in particular to a clamping fixture for a centrifugal compressor guide vane. Background Technology

[0002] Centrifugal compressors are core power equipment in energy, chemical and other fields. The machining accuracy of their internal guide vanes directly affects airflow stability and overall compressor efficiency. These guide vanes are usually thin-walled, irregularly shaped structures, requiring precision milling and drilling of multiple dimensions (such as different diameters, heights, and blade angles) using a horizontal machining center. This places stringent requirements on the positioning accuracy, clamping stability, and model compatibility of the centrifugal compressor guide vane clamping fixtures.

[0003] In existing technologies, when machining multi-size centrifugal compressor guide vanes on horizontal machining centers, the conventional clamping method mainly involves pressing the upper end face of the guide vane while using chucks for circumferential clamping. However, this clamping method has many drawbacks in practical applications. On the one hand, the cover plate pressing the upper end face needs to be frequently disassembled, which not only increases manual workload and reduces production efficiency, but also easily affects the fit accuracy between the cover plate and the guide vane during frequent disassembly, and may also cause machining interference with the fixture, affecting the normal progress of machining. On the other hand, although the chucks used for circumferential clamping are common fixtures in the machining field and have a certain self-centering function, for workpieces like centrifugal compressor guide vanes that have extremely high precision requirements, existing toothed chucks are difficult to meet their precision requirements. Moreover, since the wall thickness of the guide vane is usually thin, if the clamping force is too large during the clamping process, it can easily cause the guide vane to deform, thereby seriously affecting its machining accuracy and quality. In addition, centrifugal compressor guide vanes come in a wide variety of models and sizes, while the existing fixtures are of a single size and cannot meet the processing requirements of most different models and sizes of guide vanes, which brings great inconvenience to production.

[0004] In view of the many problems existing in the above-mentioned clamping methods, in order to meet the high-precision and high-efficiency processing requirements of centrifugal compressor guide vanes, improve the flexibility and adaptability of production, and reduce production costs and manual workload, there is an urgent need for a new type of centrifugal compressor guide vane clamping fixture. Utility Model Content

[0005] The purpose of this application is to provide a centrifugal compressor guide clamping fixture to solve the problems in the prior art, such as low processing efficiency caused by frequent disassembly and assembly of the upper end face pressure plate and cover plate, easy interference between the pressure plate and the tool, low clamping accuracy and poor stability caused by insufficient precision of the peripheral toothed disc chuck, deformation of thin-walled workpieces caused by rigid clamping, and poor adaptability caused by the fixed fixture only being compatible with a few models and requiring frequent replacement and debugging.

[0006] The embodiments of this application can be implemented through the following technical solutions: A centrifugal compressor guide clamping fixture includes a fixture base plate, a drive device connected to the center of the fixture base plate, and several level blocks and displacement drive components. The level blocks and displacement drive components are arranged in a spaced manner extending outward from the drive device as the center. The output end of the drive device engages simultaneously with the input ends of multiple displacement drive components. Each displacement drive component includes a transmission part, a screw, a slider, and a support part. Along the axial direction of the screw, one end of the screw is coaxially connected to the transmission part, and the other end is connected to the tooling base plate through the support part. The slider is helically connected to the top of the screw, and the bottom of the slider is slidably connected to a slide rail on the tooling base plate. The top of the slider is provided with several limiting parts along the axial direction of the screw, and a pawl is connected to one of the limiting parts.

[0007] Furthermore, the contour block includes a first contour block and a second contour block. The length of the first contour block is greater than the length of the second contour block. The outer ends of both the first and second contour blocks are flush with the outer edge of the tooling base plate, and the inner ends are distributed in a stepped manner.

[0008] Furthermore, the first and second contour blocks are at the same height relative to the horizontal plane of the tooling base plate. The number of first contour blocks is three, and the three first contour blocks are arranged symmetrically, with their inner ends extending to the vicinity of the driving device.

[0009] Furthermore, a displacement driving component is provided between two adjacent first contour blocks, and a second contour block is provided between the displacement driving component and the first contour block.

[0010] Furthermore, the limiting part and the bottom of the claw are engaged by mutually cooperating grooves and protrusions, and the limiting part extends in the horizontal plane in a direction perpendicular to the screw axis.

[0011] Furthermore, along the axial direction of the screw, the two ends of the claw are respectively connected to a first claw head and a second claw head, wherein the first claw head is an arc-shaped structure with its center protruding outwards and facing away from the driving device, and the second claw head is an arc-shaped structure with its center concave inwards and facing towards the driving device.

[0012] Furthermore, a central hole is provided in the middle of the tooling base plate, and the driving end of the driving device passes through the central hole of the tooling base plate and protrudes from the upper surface of the tooling base plate. The driving end of the driving device is a driving bevel gear or a gear ring with helical teeth. The transmission part includes a bevel pinion. The driving end of the driving device and the bevel pinion are driven by meshing through the bevel tooth profile.

[0013] Furthermore, the transmission unit also includes a pinion shaft, the bevel pinion is fixedly connected to one end of the pinion shaft, and the other end of the pinion shaft is coaxially connected to one end of the screw via a coupling.

[0014] Furthermore, the end of the screw furthest from the coupling is connected to the support via a combination of tapered roller bearings and deep groove ball bearings.

[0015] Furthermore, a protective cover is provided on the outside of the screw, and the protective cover extends along the axial direction of the screw.

[0016] The centrifugal compressor guide clamping fixture provided in the embodiments of this application has at least the following beneficial effects: On the one hand, the device uses meshing bevel gears to enable the drive unit to simultaneously engage multiple displacement drive components, achieving synchronous movement of the jaws on all screws. This allows for rapid self-centering clamping and loosening of workpieces, eliminating the need for manual alignment, significantly shortening clamping and alignment time, effectively improving work efficiency, and reducing the labor intensity of operators.

[0017] On the other hand, through the reasonable circumferential arrangement of equal-height blocks of different lengths and displacement drive components centered on the drive device, and the design of chucks installed on different limit parts on the slider, it can meet the clamping requirements of products of various sizes and specifications. The tooling is highly versatile and can be adapted to various types of workpieces, significantly saving tooling manufacturing and storage costs.

[0018] In addition, one end of the screw in this application is connected to the drive device through the transmission part, and the other end is connected to the tooling base plate by the support part. The support part adopts a combination of tapered roller bearings and deep groove ball bearings to achieve a single-point support structure, making full use of the characteristics of bevel gear transmission. The structure is more compact. Combined with the sliding connection between the slider and the slide rail, the transmission characteristics are fully utilized to achieve a compact layout. While ensuring stable support and precise transmission, it saves installation space and improves the reliability of device operation. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the overall structure of a centrifugal compressor guide clamping fixture according to this application; Figure 2 This is a schematic diagram of the overall structure of a centrifugal compressor guide clamping fixture according to this application; Figure 3 for Figure 2 A magnified view of a portion of point I in the middle; Figure 4 for Figure 2 A schematic cross-sectional view along the AA direction.

[0020] Numbers in the diagram 1-Tooling base plate; 2-Elevation block; 21-First elevation block; 22-Second elevation block; 3-Drive device; 31-Drive bevel gear; 4-Displacement drive assembly; 40-Transmission part; 401-Bevel pinion; 402-Pinion shaft; 41-Screw; 42-Coupling; 43-Slider; 430-Nut; 431-Limiting part; 44-Support part; 45-Slide rail; 5-Claw; 51-First claw head; 52-Second claw head; 6-Guard cover. Detailed Implementation

[0021] The present application will now be further described based on preferred embodiments and with reference to the accompanying drawings.

[0022] Furthermore, for ease of understanding, various components on the drawings have been enlarged or reduced, but this is not intended to limit the scope of protection of this application.

[0023] Singular forms of words also include plural meanings, and vice versa.

[0024] In the description of the embodiments of this application, it should be noted that if terms such as "upper," "lower," "inner," or "outer" are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship commonly used when the product of this application is in use, they are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on this application. In addition, in the description of this application, in order to distinguish different units, the terms "first," "second," etc. are used in this specification, but these are not limited by the manufacturing order, nor should they be construed as indicating or implying relative importance. Their names may differ in the detailed description and claims of this application.

[0025] The vocabulary used in this specification is for illustrative purposes and is not intended to limit the scope of this application. It should also be noted that, unless otherwise expressly specified and limited, the terms "set," "connected," and "linked" 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, a direct connection, or an indirect connection via an intermediate medium; or they can refer to the internal communication between two components. Those skilled in the art will understand the specific meaning of these terms in this application.

[0026] like Figure 1 , Figure 2 As shown, a centrifugal compressor guide clamping fixture includes a fixture base plate 1. A drive device 3 is connected to the center of the fixture base plate 1. Several equal-height blocks 2 and displacement drive components 4 are connected to the fixture base plate 1 in a radial arrangement centered on the drive device 3. The several displacement drive components 4 are arranged circumferentially along the drive device 3. An equal-height block 2 is provided between every two displacement drive components 4. The planetary carrier is connected to the top of the drive device 3 through the equal-height blocks 2. The several displacement drive components 4 are connected to jaws 5, so that the planetary carrier is located at the clamping center of the several jaws 5.

[0027] In some preferred embodiments, the displacement driving assembly 4 includes a transmission part 40, a screw 41, a slider 43, and a support part 44. Along the axial direction of the screw 41, one end of the screw 41 is coaxially connected to the transmission part 40, and the other end is connected to the tooling base plate 1 through the support part 44. The slider 43 is connected to the top of the screw 41 through a nut 430, and the bottom of the slider 43 is slidably connected to the slide rail 45 of the tooling base plate 1. The top of the slider 43 is provided with a plurality of limiting parts 431 radially along the tooling base plate 1. The claw 5 can be selectively connected to any of the limiting parts 431. By adjusting the connection position of each claw 5 with the corresponding displacement driving assembly 4, the clamping point can be flexibly adjusted to meet the clamping requirements of different specifications of guide tubes.

[0028] In some preferred embodiments, the output end of the drive device 3 engages simultaneously with the input ends of the multiple displacement drive components 4. During operation, the drive device 3 synchronously drives each of the transmission parts 40 to rotate the screw 41, thereby causing the slider 43 to move linearly along the slide rail 45 until all the chucks 5 synchronously press against the planetary carrier surface, achieving precise and stable clamping.

[0029] In some preferred embodiments, the leveling block 2 includes a first leveling block 21 and a second leveling block 22. The length of the first leveling block 21 is greater than the length of the second leveling block 22. The outer ends (the ends away from the driving device 3) of the first leveling block 21 and the second leveling block 22 are flush with the outer circumference of the tooling base plate 1, while the inner ends are distributed in a stepped manner due to the difference in length. The stepped layout of the support points is achieved through the difference in length. Combined with the clamping action of the claw 5, a multi-dimensional balanced force structure is formed, which improves the clamping stability and positioning accuracy.

[0030] In some preferred embodiments, the first leveling block 21 and the second leveling block 22 are at the same height relative to the horizontal plane of the tooling base plate 1. There are three first leveling blocks 21, which are symmetrically arranged, with their inner ends extending to the periphery near the drive device 3. A displacement drive assembly 4 is provided between two adjacent first leveling blocks 21. There are six second leveling blocks 22, which are symmetrically distributed on the outer side, with their inner ends closer to the edge of the tooling base plate than the first leveling blocks 21. Each of the claws 5 has one second leveling block 22 on each side, so that the three symmetrically distributed first leveling blocks 21 form a stable central support triangle. Together with the second leveling blocks 22 distributed on both sides of the displacement drive assembly 4, multiple sets of evenly distributed support points are constructed at a uniform height to ensure that the planetary carrier is clamped in a balanced manner and to avoid local stress concentration.

[0031] In some preferred embodiments, the limiting part 431 and the bottom of the claw 5 are engaged by a groove and a protrusion that cooperate with each other. Preferably, the limiting part 431 is a claw groove. The limiting part 431 extends in the horizontal plane in a direction perpendicular to the axis of the screw 41. The bottom of the claw 5 is provided with a protrusion structure that cooperates with the claw groove. When the claw 5 is subjected to radial force, the direction of force transmission is consistent with the extension direction of the claw groove. The load can be dispersed through the large-area contact between the groove wall and the protrusion structure, which can effectively prevent the claw 5 from loosening or shifting when subjected to force.

[0032] In some preferred embodiments, along the axial direction of the screw 41, the two ends of the jaws 5 are respectively connected to a first jaw head 51 and a second jaw head 52. The first jaw head 51 is an arc-shaped structure with its center protruding outwards, facing away from the driving device 3. The second jaw head 52 is an arc-shaped structure with its center concave inwards, facing towards the driving device 3. When "internal support positioning" of the planetary carrier is required, multiple jaws 5 simultaneously move towards the center of the tooling, and the protruding arc surface of the first jaw head 51 interacts with the inner wall of the planetary carrier's bore. The cavity walls fit tightly together, and the planetary carrier is supported by radial outward support force to achieve precise positioning of the inner reference of the workpiece. When the planetary carrier needs to be "externally clamped and positioned", multiple jaws 5 move towards the center of the tooling at the same time. The concave arc surface of the second jaw head 52 wraps around the outer contour of the planetary carrier, and the planetary carrier is clamped by radial inward clamping force, which directly acts on the outer reference surface of the workpiece. This allows a single jaw 5 to cover the two core clamping scenarios of the planetary carrier without the need for frequent replacement of jaw components, which greatly improves the versatility and clamping efficiency of the tooling.

[0033] In some preferred embodiments, such as Figure 3As shown, the tooling base plate 1 has a central hole that runs vertically through the middle. The driving end of the driving device 3 passes through the central hole of the tooling base plate 1 and protrudes from the upper surface of the tooling base plate 1. The driving end of the driving device 3 is a driving bevel gear 31. The transmission part 40 includes a bevel pinion 401. The driving bevel gear 31 and the bevel pinion 401 mesh with each other through the conical tooth profile. When the driving device 3 is started, the rotational motion of the driving bevel gear 31 can be converted into the synchronous rotation of multiple bevel pinions 401 through gear meshing, thereby driving each screw 41 to drive the pawl 5 on the slider 43 to achieve radial linkage. Preferably, the driving bevel gear 31 can be replaced with a gear ring with helical teeth on the upper surface.

[0034] In some preferred embodiments, such as Figure 3 As shown, the transmission unit 40 also includes a pinion shaft 402. The bevel pinion 401 is fixedly connected to one end of the pinion shaft 402. The other end of the pinion shaft 402 is coaxially connected to the screw 41 through the coupling 42. The two ends of the coupling 42 are respectively connected to the screw 41 and the pinion shaft 402 through keys to transmit torque, ensuring efficient power transmission from the bevel pinion 401 to the screw 41.

[0035] In some preferred embodiments, to further improve the coaxiality of the transmission, positioning holes (usually mating boss and concave hole structures) are provided on the opposite end faces of the screw 41 and the pinion shaft 402. During assembly, the pre-positioning of the two is achieved by the precise fitting of the positioning holes.

[0036] In some preferred embodiments, such as Figure 4 As shown, the end of the screw 41 furthest from the coupling 42 is connected to the support 44 via a combination of tapered roller bearings and deep groove ball bearings, forming a unique single-point cantilever support structure. Conventional single-point support structures are prone to deflection or vibration under stress due to the superposition of radial force and torque, resulting in insufficient support stability. In this design, the tapered roller bearings can simultaneously bear radial and axial forces, while the deep groove ball bearings assist in bearing the radial force. The combination of the two bearings can completely offset the compound force generated by gear meshing, forming a self-balancing force system.

[0037] In some preferred embodiments, the screw 41 is further covered with a protective cover 6, which extends along the axial direction of the screw 41. Preferably, the protective cover 6 adopts a segmented telescopic structure, which is divided into a fixed section and a movable section along the axial direction of the screw 41. The two ends of the fixed section are respectively sealed and connected to the transmission part 40 and the support part 44. The movable section is nested inside the fixed section and rigidly connected to the outer wall of the slider 43. When the slider 43 moves radially along the screw 41, the movable section extends and retracts synchronously with the slider 43, thereby achieving gapless protection throughout the process and avoiding interference with the movement of the slider 43.

[0038] The specific embodiments of this application have been described in detail above. For those skilled in the art, several improvements and modifications can be made to this application without departing from the principle of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A centrifugal compressor guide vane clamping fixture, comprising a fixture base plate (1), characterized in that: The tooling base plate (1) is connected to a driving device (3), a number of contour blocks (2) and a displacement driving assembly (4) at the center. The contour blocks (2) and the displacement driving assembly (4) are arranged in a way that extends outward from the driving device (3) and are spaced apart. The output end of the drive device (3) engages simultaneously with the input ends of multiple displacement drive components (4). The displacement drive component (4) includes a transmission part (40), a screw (41), a slider (43), and a support part (44). Along the axial direction of the screw (41), one end of the screw (41) is coaxially connected to the transmission part (40), and the other end is connected to the tooling base plate (1) through the support part (44). The slider (43) is spirally connected to the top of the screw (41), and the bottom of the slider (43) is slidably connected to the slide rail (45) on the tooling base plate (1). The top of the slider (43) is provided with several limiting parts (431) along the axial direction of the screw (41), and a pawl (5) is connected to one of the limiting parts (431).

2. The centrifugal compressor guide clamping fixture according to claim 1, characterized in that: The contour block (2) includes a first contour block (21) and a second contour block (22). The length of the first contour block (21) is greater than the length of the second contour block (22). The outer ends of the first contour block (21) and the second contour block (22) are flush with the outer edge of the tooling base plate (1), and the inner ends are distributed in a stepped manner.

3. The centrifugal compressor guide clamping fixture according to claim 2, characterized in that: The first contour block (21) and the second contour block (22) are at the same height relative to the horizontal plane of the tooling base plate (1). The number of the first contour blocks (21) is three, and the three first contour blocks (21) are arranged symmetrically, with their inner ends extending to the adjacent drive device (3).

4. The centrifugal compressor guide clamping fixture according to claim 3, characterized in that: A displacement driving component (4) is provided between two adjacent first contour blocks (21), and a second contour block (22) is provided between the displacement driving component (4) and the first contour block (21).

5. The centrifugal compressor guide clamping fixture according to claim 1, characterized in that: The bottom of the limiting part (431) and the claw (5) are engaged by a groove and a protrusion that cooperate with each other. The limiting part (431) extends in the horizontal plane in a direction perpendicular to the axis of the screw (41).

6. The centrifugal compressor guide clamping fixture according to claim 1, characterized in that: Along the axial direction of the screw (41), the two ends of the claw (5) are respectively connected to a first claw head (51) and a second claw head (52). The first claw head (51) is an arc-shaped structure with its center protruding outwards and facing away from the driving device (3). The second claw head (52) is an arc-shaped structure with its center concave inwards and facing towards the driving device (3).

7. The centrifugal compressor guide clamping fixture according to claim 1, characterized in that: The tooling base plate (1) has a central hole that runs vertically through the middle. The driving end of the driving device (3) passes through the central hole of the tooling base plate (1) and protrudes from the upper surface of the tooling base plate (1). The driving end of the driving device (3) is a drive bevel gear (31) or a gear ring with helical teeth. The transmission part (40) includes a bevel pinion (401). The driving end of the driving device (3) and the bevel pinion (401) are driven by meshing through the bevel tooth profile.

8. The centrifugal compressor guide clamping fixture according to claim 7, characterized in that: The transmission unit (40) also includes a pinion shaft (402), the bevel pinion (401) is fixedly connected to one end of the pinion shaft (402), and the other end of the pinion shaft (402) is coaxially connected to one end of the screw (41) through a coupling (42).

9. The centrifugal compressor guide clamping fixture according to claim 8, characterized in that: The end of the screw (41) away from the coupling (42) is connected to the support (44) by a combination of tapered roller bearings and deep groove ball bearings.

10. The centrifugal compressor guide clamping fixture according to claim 1, characterized in that: The screw (41) is also covered with a protective cover (6), which extends along the axial direction of the screw (41).

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