Eccentric disk quenching fixture structure for electronic multi-arm

Abstract

An electronic multi-arm eccentric disk quenching fixture structure includes a dynamic pressure plate and a static pressure plate. An oil inlet hole is located at the center of the dynamic pressure plate, and an oil overflow hole is located at the center of the static pressure plate. Both the dynamic and static pressure plates have oil guiding and distributing mechanisms on their respective sides. An eccentric disk support plate limiting ring is fixed to the static pressure plate on the side facing the dynamic pressure plate. The eccentric disk support plate is located within the limiting ring and fixed to the static pressure plate on the same side. A clearance hole for the eccentric disk body boss is located at the center of the support plate. Oil guide grooves are formed on the support plate around the clearance hole, moving away from it. This design ensures the overall flatness of the eccentric disk, improves quenching efficiency, reduces workload, saves energy, and increases product yield.

Description

Technical Field

[0001] This invention belongs to the technical field of tooling and fixtures for textile component production, specifically relating to a fixture structure for quenching an eccentric disk of an electronic multi-arm. Background Technology

[0002] The aforementioned electronic dobby is a key mechanism among the five major motion mechanisms of a loom (shedding, weft insertion, beat-up, warp feeding, and take-up mechanisms). Its quality directly affects the shedding efficiency of the loom and the weaving quality of the fabric. The loom transmits power to the electronic dobby, causing the dobby's bevel gears to rotate synchronously and uniformly with the loom. Then, through a slider mechanism and a conjugate cam mechanism, the dobby's main shaft moves at a non-uniform speed, ultimately cooperating with the eccentric disc and heald lifting components to achieve the shedding motion of the loom's heald frames. Therefore, the eccentric disc is a component with extremely stringent technical requirements in the electronic dobby. Specifically, the wear resistance and machining precision of the eccentric disc directly affect the correctness of the shedding of the electronic dobby device in service. In view of this, improving the manufacturing precision and wear resistance of the eccentric disc is of positive significance for improving the overall performance of the electronic dobby shedding device.

[0003] Compared to a single rotary electronic heddle, 16 to 20 or even more eccentric discs are typically used. Since their working mechanism can be fully understood by reading patent documents such as CN1028119C (Control device for ultra-high speed rotary heddle lifting device), CN1057353C (Rotary heddle machine and loom equipped with the heddle mechanism), CN101709525B (Three-opening mechanism for rotary electronic heddle machine) and CN206545080U (Eccentric disc structure for rotary electronic heddle), the applicant will not elaborate further.

[0004] As is known in the industry, the shape of an eccentric disc is quite unique. It is generally flat but its thickness varies. For example, there are typically three specifications with varying thicknesses: 8.5mm thick, 2.5mm thin; 9.3mm thick, 3.3mm thin; and 9.4mm thick, 3.6mm thin. Furthermore, the shape of the eccentric disc is highly irregular. In actual use, the eccentric disc operates under extremely harsh conditions, often continuously for 24 hours a day without stopping, and needs to withstand asymmetrical load impacts from multiple arms for extended periods. Therefore, its wear resistance and hardness requirements are extremely stringent. In order to enable the eccentric disk to cope with the aforementioned harsh service environment and meet the service life requirements within a reasonable period of time, it is usually first forged from a GCr25 forging into a blank, and then the blank is machined. After the machining is completed, it is heated in a heating furnace to 840-850℃, and then quenched in a quenching medium such as oil without any restrictions (also known as "control"). After quenching, it is transferred to a tempering furnace and tempered at about 170-180℃ (commonly referred to in the industry as "low temperature tempering").

[0005] While the aforementioned quenching and tempering heat treatment methods can improve the wear resistance and hardness of the eccentric disk, as mentioned earlier, due to the eccentric disk's flat and highly irregular shape, significant planar deformation occurs after the heat treatment. Furthermore, the hardness after heat treatment is relatively high (HRC 58-62), making subsequent shaping measures difficult or even impossible to achieve for smoothing. During the tempering stage, the eccentric disk is first clamped using specialized tooling, and then tempered while still in this clamped state. However, because the tempering temperature is relatively low, around 170-180℃, the effect on surface flatness correction is far from ideal. Even after repeated clamping and tempering, the desired effect cannot be achieved, and the flatness failure rate detected in subsequent flatness tests remains consistently high. In particular, eccentric disks with unsatisfactory flatness cannot be used in electronic multi-arms. Undoubtedly, tempering an eccentric disc while it is clamped has at least the following drawbacks: First, repeated clamping and tempering affects tempering efficiency, which in turn affects the production efficiency of the eccentric disc; second, it causes energy waste; third, it increases the workload of on-line workers; and fourth, due to the high unevenness rate, the discs can only be discarded, resulting in resource waste.

[0006] Quenching an eccentric disc held in a quenching fixture on a pressure device such as a hydraulic press or similar machinery, while applying pressure and using oil as the quenching medium, can largely avoid the aforementioned shortcomings. This is because the eccentric disc is heated to a temperature of approximately 840-850℃ before quenching, which is highly beneficial for flattening the disc. However, the structural design of a quenching fixture for an eccentric disc, suitable for a hydraulic press and capable of reliably clamping the disc during quenching, requires ingenious design elements. This is because eccentric disc quenching fixtures fall under the category of tooling fixtures. Tooling fixtures are specialized equipment used to position workpieces during the manufacturing and / or subsequent processing of a product to achieve certain technological requirements. They also typically need to meet requirements such as no interference during workpiece processing (quenching) and ease of operation. Furthermore, because tooling fixtures have specific characteristics for processing a particular workpiece or product, they are usually not universally applicable and are often designed and manufactured by the workpiece or product manufacturer in a tailored manner. Based on these factors, no technical inspiration has been found in the publicly available patent and non-patent documents to date for a tooling fixture structure suitable for quenching an eccentric disk that has been processed and heated to 840-850°C in a heating furnace under a reliable clamping condition. The technical solution to be introduced below is produced in this context. Summary of the Invention

[0007] The objective of this invention is to provide an electronic multi-arm eccentric disk quenching fixture structure that can meet the requirements of cooperating with pressure equipment in the use state and the requirements of reliable clamping of eccentric disks in the quenching state, thereby improving the flatness of eccentric disks during the quenching stage, improving efficiency, saving energy consumption, reducing the labor intensity of workers, significantly improving the pass rate, and avoiding the waste of resources caused by the rejection of products due to insufficient flatness.

[0008] The present invention achieves its objective by providing a fixture structure for eccentric disk quenching of an electronic multi-arm, comprising a dynamic pressure plate and a static pressure plate. The dynamic and static pressure plates are vertically aligned and positioned on a pressure device during use. An oil inlet hole is located at the center of the dynamic pressure plate, and an oil overflow hole is located at the center of the static pressure plate. The oil inlet hole and overflow hole correspond to each other. An oil guiding and distributing mechanism communicating with the oil inlet hole is formed on the side of the dynamic pressure plate facing the static pressure plate, while an oil guiding and distributing mechanism communicating with the overflow hole is formed on the side of the static pressure plate facing the dynamic pressure plate. The dynamic and static pressure plate oil guiding and distributing mechanisms... The components correspond to each other; an eccentric disk bearing plate limiting ring and an eccentric disk bearing plate. The eccentric disk bearing plate limiting ring is fixed to the side of the static pressure plate facing the dynamic pressure plate. The eccentric disk bearing plate is located inside the eccentric disk bearing plate limiting ring and is also fixed to the side of the static pressure plate facing the dynamic pressure plate. An eccentric disk body boss clearance hole is opened at the center of the eccentric disk bearing plate, and the eccentric disk bearing plate is also fixed to the side of the static pressure plate facing the dynamic pressure plate. On the eccentric disk bearing plate and around the eccentric disk body boss clearance hole, radially spaced away from the eccentric disk body boss clearance hole, there are eccentric disk bearing plate oil guide grooves that penetrate the thickness direction of the eccentric disk bearing plate.

[0009] In a specific embodiment of the present invention, a dynamic pressure plate fixing flange extends outward from the side of the dynamic pressure plate facing upward and around the perimeter of the dynamic pressure plate, and a static pressure plate fixing flange extends outward from the side of the static pressure plate facing downward and around the perimeter of the static pressure plate. The dynamic pressure plate fixing flange and the static pressure plate fixing flange are fixed to the pressure equipment in the use state.

[0010] In another specific embodiment of the present invention, fastener insertion grooves for the dynamic pressure plate fixing flange are provided on the dynamic pressure plate fixing flange side and spaced apart around the dynamic pressure plate fixing flange side, and fastener insertion grooves for the static pressure plate fixing flange are provided on the static pressure plate fixing flange side and spaced apart around the static pressure plate fixing flange side. The dynamic pressure plate fixing flange side and the static pressure plate fixing flange side are fixed to the pressure device by fasteners at positions corresponding to the fastener insertion grooves for the dynamic pressure plate fixing flange side and the static pressure plate fixing flange side.

[0011] In another specific embodiment of the present invention, eccentric disk bearing plate limiting ring fixing screw holes and eccentric disk bearing plate fixing screw holes are provided at intervals on the side of the static pressure plate facing the dynamic pressure plate. Eccentric disk bearing plate limiting ring fixing holes are provided on the eccentric disk bearing plate limiting ring at positions corresponding to the eccentric disk bearing plate limiting ring fixing screw holes. The limiting ring fixing screw is screwed into the eccentric disk bearing plate limiting ring fixing screw hole at the position corresponding to the eccentric disk bearing plate limiting ring fixing hole to fix the eccentric disk bearing plate limiting ring to the side of the static pressure plate facing the dynamic pressure plate. Eccentric disk bearing plate fixing holes are provided on the eccentric disk bearing plate at positions corresponding to the eccentric disk bearing plate fixing screw holes. The eccentric disk bearing plate is fixed to the side of the static pressure plate facing the dynamic pressure plate by screwing into the eccentric disk bearing plate fixing screw hole at the position corresponding to the eccentric disk bearing plate fixing hole.

[0012] In another specific embodiment of the present invention, the eccentric disk bearing plate limiting ring is located at the circumferential edge of the surface of the static pressure plate facing the dynamic pressure plate. The outer diameter of the eccentric disk bearing plate is adapted to the inner diameter of the limiting ring cavity of the eccentric disk bearing plate limiting ring, and the outer circular surface of the eccentric disk bearing plate is in contact with the cavity wall of the limiting ring cavity.

[0013] In another specific embodiment of the present invention, the dynamic pressure plate oil guiding and distributing mechanism includes a dynamic pressure plate radial oil groove and a dynamic pressure plate annular oil groove. The dynamic pressure plate radial oil groove is arranged at intervals around the circumference of the dynamic pressure plate and extends from the edge of the oil inlet hole of the dynamic pressure plate to the edge of the dynamic pressure plate. The dynamic pressure plate annular oil groove is arranged at intervals around the circumference of the dynamic pressure plate. The dynamic pressure plate radial oil groove is interrupted by the dynamic pressure plate annular oil groove at the position located in the dynamic pressure plate annular oil groove and forms a cross-shaped interlacing relationship with the dynamic pressure plate annular oil groove.

[0014] In a further specific embodiment of the present invention, the hydrostatic plate oil guiding and distributing mechanism includes a hydrostatic plate radial oil groove and a hydrostatic plate annular oil groove. The hydrostatic plate radial oil groove is spaced apart around the circumference of the hydrostatic plate and extends from the edge of the hydrostatic plate overflow hole to the edge of the hydrostatic plate. The hydrostatic plate annular oil groove is spaced apart around the circumference of the hydrostatic plate. The hydrostatic plate radial oil groove is interrupted by the hydrostatic plate annular oil groove at the position located in the hydrostatic plate annular oil groove and forms a cross-shaped interlacing relationship with the hydrostatic plate annular oil groove.

[0015] In a further specific embodiment of the present invention, in the radial oil grooves of the dynamic pressure plate, the number of intersection points of each radial oil groove of the dynamic pressure plate that is broken by the annular oil groove of the dynamic pressure plate and forms a cross-shaped interlacing relationship with the annular oil groove of the dynamic pressure plate is equal to the number of annular oil grooves of the dynamic pressure plate.

[0016] In yet another specific embodiment of the present invention, in the radial oil grooves of the static pressure plate, the number of intersection points of each radial oil groove of the static pressure plate that is broken by the annular oil groove of the static pressure plate and forms a cross-shaped interlacing relationship with the annular oil groove of the static pressure plate is equal to the number of annular oil grooves of the static pressure plate.

[0017] In yet another specific embodiment of the present invention, the number of fastener insertion slots on the dynamic pressure plate fixing flange edge is four, equidistant from each other in the circumferential direction around the dynamic pressure plate fixing flange edge, and the shape of the fastener insertion slots on the dynamic pressure plate fixing flange edge is U-shaped with the slot opening communicating with the outside; the number of fastener insertion slots on the static pressure plate fixing flange edge is four, equidistant from each other in the circumferential direction around the static pressure plate fixing flange edge, and the shape of the fastener insertion slots on the static pressure plate fixing flange edge is U-shaped with the slot opening communicating with the outside; the pressure device is a hydraulic press.

[0018] The technical advantages of the solution provided by this invention are as follows: Due to the reasonable structure of the dynamic and static pressure plates, it can not only meet the requirements of cooperating with pressure equipment in the use state, but also meet the requirements of applying pressure from the dynamic pressure plate to the static pressure plate when the eccentric plate is placed on the eccentric plate bearing plate in the quenching state. This allows the eccentric plate to be reliably clamped, and the high-temperature oil used as the quenching medium is introduced from the oil inlet hole of the dynamic pressure plate and then sequentially led out through the oil guiding and distributing mechanism of the dynamic pressure plate, the oil guiding groove of the eccentric plate bearing plate, the oil overflow hole of the static pressure plate, and the oil guiding and distributing mechanism of the static pressure plate to complete the quenching. This can ensure the overall flatness of the eccentric plate and improve the quenching efficiency by eliminating the need for manual clamping, reducing the labor intensity of workers. Since only one quenching is required, it can save energy consumption and significantly improve the product qualification rate, avoiding the production of scrap due to insufficient flatness and preventing resource waste. Attached Figure Description

[0019] Figure 1 This is a structural diagram of an embodiment of the present invention;

[0020] Figure 2 for Figure 1 The diagram shows the eccentric disc bearing plate limiting ring and the eccentric disc bearing plate fixed to the side of the static pressure plate facing the dynamic pressure plate.

[0021] Figure 3 for Figure 1 and Figure 2 The diagram shows a detailed structural view of the dynamic pressure plate when rotated 180°.

[0022] Figure 4 This is a schematic diagram illustrating an application example of the present invention. Detailed Implementation

[0023] In order to better understand the technical essence and beneficial effects of the present invention, the applicant provides a detailed description below by way of embodiments. However, the description of the embodiments is not intended to limit the present invention. Any formal but not substantive equivalent transformations made based on the concept of the present invention should be considered within the scope of the present invention.

[0024] In the following description, all directional or orientational concepts such as up and down will be referred to as "up" or "down". Figure 1 The positional state shown is a baseline and therefore should not be construed as a specific limitation on the technical solution provided by this invention.

[0025] Please see Figure 1 and Figure 2 The diagram shows a circular or cylindrical dynamic pressure plate 1 and a similarly circular or cylindrical static pressure plate 2 (also referred to as a "pressure bearing plate," hereinafter the same). The dynamic pressure plate 1 and static pressure plate 2 are positioned vertically on the pressure equipment during operation. A dynamic pressure plate oil inlet 11 is located at the center of the dynamic pressure plate 1, and a static pressure plate oil overflow hole 21 is located at the center of the static pressure plate 2. The dynamic pressure plate oil inlet 11 and the static pressure plate oil overflow hole 21 correspond to each other. On the side of the dynamic pressure plate 1 facing the static pressure plate 2, a dynamic pressure plate oil guiding and separating mechanism 12 is formed, communicating with the aforementioned dynamic pressure plate oil inlet 11. On the side of the static pressure plate 2 facing the dynamic pressure plate 1, a static pressure plate oil guiding and separating mechanism 22 is formed, communicating with the aforementioned static pressure plate oil overflow hole 21. The dynamic and static pressure plate oil guiding and separating mechanisms... Structures 12 and 22 correspond to each other; an eccentric disk bearing plate limiting ring 3 and an eccentric disk bearing plate 4 are shown. The eccentric disk bearing plate limiting ring 3 is fixed to the side of the aforementioned static pressure plate 2 facing the aforementioned dynamic pressure plate 1. The eccentric disk bearing plate 4 is located inside the eccentric disk bearing plate limiting ring 3 and is also fixed to the side of the static pressure plate 2 facing the dynamic pressure plate 1. An eccentric disk body boss relief hole 41 is opened at the center of the eccentric disk bearing plate 4, and the eccentric disk bearing plate 4 is also fixed to the side of the static pressure plate 2 facing the dynamic pressure plate 1. On the eccentric disk bearing plate 4, and around the eccentric disk body boss relief hole 41, eccentric disk bearing plate oil guide grooves 42 are radially spaced in a direction away from the eccentric disk body boss relief hole 41, penetrating the thickness direction of the eccentric disk bearing plate 4.

[0026] A dynamic pressure plate fixing flange 13 extends outward from the side of the aforementioned dynamic pressure plate 1 facing upward and around the perimeter of the dynamic pressure plate 1. A static pressure plate fixing flange 23 extends outward from the side of the static pressure plate 2 facing downward and around the perimeter of the static pressure plate 2. The aforementioned dynamic pressure plate fixing flange 13 and static pressure plate fixing flange 23 are fixed to the aforementioned pressure equipment in the use state.

[0027] A fastener insertion groove 131 is provided on the aforementioned dynamic pressure plate fixing flange edge 13 and around the perimeter of the dynamic pressure plate fixing flange edge 13. A fastener insertion groove 231 is provided on the aforementioned static pressure plate fixing flange edge 23 and around the perimeter of the static pressure plate fixing flange edge 23. The dynamic pressure plate fixing flange edge 13 and the static pressure plate fixing flange edge 23 are fixed to the aforementioned pressure equipment by fasteners at positions corresponding to the fastener insertion grooves 131 and 231 of the dynamic pressure plate fixing flange edge and the static pressure plate fixing flange edge.

[0028] On the side of the aforementioned static pressure plate 2 facing the aforementioned dynamic pressure plate 1, there are eccentric plate bearing plate limiting ring fixing screw holes 24 and eccentric plate bearing plate fixing screw holes 25 spaced apart. On the aforementioned eccentric plate bearing plate limiting ring 3, there is an eccentric plate bearing plate limiting ring fixing hole 31 at the position corresponding to the eccentric plate bearing plate limiting ring fixing screw hole 24. The limiting ring fixing screw 311 is screwed into the eccentric plate bearing plate limiting ring fixing screw hole 24 at the position corresponding to the eccentric plate bearing plate limiting ring fixing hole 31, thereby fixing the eccentric plate bearing plate limiting ring 3 to the side of the static pressure plate 2 facing the dynamic pressure plate 1. On the aforementioned eccentric plate bearing plate 4, there is an eccentric plate bearing plate fixing hole 43 at the position corresponding to the aforementioned eccentric plate bearing plate fixing screw hole 25. The eccentric plate bearing plate 4 is screwed into the eccentric plate bearing plate fixing screw hole 25 at the position corresponding to the eccentric plate bearing plate fixing hole 43, thereby fixing the eccentric plate bearing plate 4 to the side of the static pressure plate 2 facing the dynamic pressure plate 1.

[0029] At the edge of the aforementioned eccentric disk bearing plate limiting ring 3 located on the circumferential direction of the surface of the aforementioned static pressure plate 2 facing the aforementioned dynamic pressure plate 1, the outer diameter of the aforementioned eccentric disk bearing plate 4 is adapted to the inner diameter of the limiting ring cavity 32 of the eccentric disk bearing plate limiting ring 3, and the outer circular surface 44 of the eccentric disk bearing plate 4 is in contact with the limiting ring cavity wall 321 of the limiting ring cavity 32. Figure 2 Show).

[0030] exist Figure 1 and Figure 2 The diagram also shows an eccentric disk 5, with an eccentric disk body boss 51 formed in the middle of the downward-facing side of the eccentric disk 5. During quenching, the eccentric disk 5 is placed on the eccentric disk support plate 4, and the eccentric disk body boss 51 is aligned with the eccentric disk body boss clearance hole 41. Therefore, since the online operator does not need to clamp the eccentric disk 5 which is to be quenched in oil, the quenching efficiency can be improved, and the labor intensity of the workers can be significantly reduced.

[0031] Please pay attention. Figure 3 , Figure 3 In fact Figure 1 and Figure 2The diagram shows a view of the bottom of the dynamic pressure plate 1. The aforementioned dynamic pressure plate oil guiding and distributing mechanism 12 includes radial oil grooves 121 and annular oil grooves 122. The radial oil grooves 121 are spaced apart around the circumference of the dynamic pressure plate 1 and extend from the edge of the oil inlet hole 11 to the edge of the dynamic pressure plate 1. The annular oil grooves 122 are spaced apart around the circumference of the dynamic pressure plate 1. The radial oil grooves 121 are interrupted by the annular oil grooves 122 at positions located on the annular oil grooves 122 and form a cross-shaped interlacing relationship with the annular oil grooves 122.

[0032] Please pay attention. Figure 2 The aforementioned hydrostatic pressure plate oil guiding and distributing mechanism 22 includes a hydrostatic pressure plate radial oil groove 221 and a hydrostatic pressure plate annular oil groove 222. The hydrostatic pressure plate radial oil groove 221 is spaced around the circumference of the aforementioned hydrostatic pressure plate 2 and extends from the edge of the aforementioned hydrostatic pressure plate overflow hole 21 to the edge of the hydrostatic pressure plate 2. The hydrostatic pressure plate annular oil groove 222 is spaced around the circumference of the hydrostatic pressure plate 2. The aforementioned hydrostatic pressure plate radial oil groove 221 is interrupted by the hydrostatic pressure plate annular oil groove 222 at the position located at the position of the hydrostatic pressure plate annular oil groove 222 and forms a cross-shaped interlacing relationship with the hydrostatic pressure plate annular oil groove 222.

[0033] As can be seen from the applicant's description above: In the aforementioned radial oil grooves 121 of the dynamic pressure plate, the number of intersection points (i.e., breakpoints or disconnected parts) of each radial oil groove of the dynamic pressure plate that are broken by the aforementioned annular oil grooves 122 of the dynamic pressure plate and form a cross-shaped intersecting relationship with the annular oil grooves 122 of the dynamic pressure plate is equal to the number of annular oil grooves 122 of the dynamic pressure plate. Since there are three annular oil grooves 122 of the dynamic pressure plate in this embodiment, there are three intersection points between the radial oil grooves 121 of the dynamic pressure plate and the three annular oil grooves 122 of the dynamic pressure plate.

[0034] In the aforementioned radial oil grooves 221 of the static pressure plate, the number of intersection points of each radial oil groove of the static pressure plate that is broken by the aforementioned annular oil groove 222 of the static pressure plate and forms a cross-shaped interlacing relationship with the annular oil groove 222 of the static pressure plate is equal to the number of annular oil grooves 222 of the static pressure plate, as described above and will not be repeated.

[0035] Depend on Figure 1 and Figure 2As shown, the aforementioned dynamic pressure plate fixing flange edge fastener insertion groove 131 has four grooves (90° apart) that are equidistant from each other in the circumferential direction around the aforementioned dynamic pressure plate fixing flange edge 13, and the shape of the dynamic pressure plate fixing flange edge fastener insertion groove 131 is U-shaped with the groove opening communicating with the outside; the aforementioned static pressure plate fixing flange edge fastener insertion groove 231 has four grooves (90° apart) that are equidistant from each other in the circumferential direction around the aforementioned static pressure plate fixing flange edge 23, and the shape of the static pressure plate fixing flange edge fastener insertion groove 231 is U-shaped with the groove opening communicating with the outside; in this embodiment, the aforementioned pressure device is a hydraulic press 6, but it is not absolutely limited to a hydraulic press.

[0036] Please see Figure 4 , Figure 4 The aforementioned hydraulic press 6 is shown. The front dynamic pressure plate 1 of the present invention is fixed to the hydraulic mold fixing seat 61 of the hydraulic press 6 (which can be referred to as the dynamic pressure plate fixing seat in this embodiment) at a position corresponding to the aforementioned dynamic pressure plate fixing flange fastener, such as dynamic pressure plate fastening bolt 1311. The static pressure plate 2 of the present invention is fixed to the hydraulic mold fixing platform 62 of the hydraulic press 6 (which can be referred to as the static pressure plate fixing platform in this embodiment) via static pressure plate fixing flange fastener, such as static pressure plate fastening bolt 2311. An oil-blocking ring 621 is fixed around the hydraulic mold fixing platform 62 to prevent quenching oil from escaping. Figure 4 As can be seen from the diagram, the aforementioned hydraulic mold fixing base 61, together with the dynamic pressure plate 1, is fixed to the lower end of the cylinder column 63 (also referred to as the "hydraulic column") of the hydraulic press 6. Figure 4 The diagram also shows a low-temperature quenching oil inlet 611, which communicates with the aforementioned dynamic pressure plate oil inlet hole 11 via a quenching oil channel 612 formed on the hydraulic mold fixing base 61. A quenching oil return pipe 6211 is provided on the aforementioned hydraulic mold fixing platform 62 at the position of the oil baffle ring 621. Figure 4 The image also shows a set of guide pillars 64 arranged in a grid (or square) shape for the hydraulic mold fixing base 61 to slide up and down. The set of guide pillars 64 is fixed between the top frame 65 of the hydraulic press 6 and the hydraulic mold fixing platform 62, which is formed on the top of the base 66.

[0037] In actual use, the aforementioned low-temperature quenching oil inlet 611 and quenching oil return pipe 6211 (also known as "high-temperature oil return pipe") are connected to a circulating pump (not shown in the figure) via pipelines. The circulating pump is connected to a quenching oil cooling container (cooling elements such as cooling coils can be installed inside the quenching oil cooling container). Under the operation of the circulating pump, low-temperature (approximately 40-50℃) quenching oil is introduced through pipelines from the low-temperature quenching oil inlet 611, through the oil inlet hole 11, the dynamic pressure plate oil guide and distribution mechanism 12, the eccentric plate bearing plate oil guide groove 42, the static pressure plate overflow hole 21, and the static pressure plate oil guide and distribution mechanism 22 into the hydraulic mold fixing platform 62 protected by the oil baffle ring 621. Then, through the quenching oil return pipe 6211, it is returned to the oil inlet of the circulating pump and introduced into the quenching oil cooling container, thus forming a circulating cooling and circulating supply of quenching oil.

[0038] When the eccentric disk 5 needs to be quenched, the online operator will press the eccentric disk 5, which has been heated to 840-850℃ by the heating furnace accompanying the hydraulic press 6, into place. Figure 2 The eccentric disc 5 is positioned as shown above and placed on the eccentric disc support plate 4 as described by the applicant. Under the operation of the hydraulic press 6, the oil cylinder 63 drives the hydraulic mold fixing seat 61 and the dynamic pressure plate 1 downward. Thus, the dynamic and static pressure plates 1 and 2 cooperate to reliably clamp the eccentric disc 5. Under clamping, the eccentric disc 5 is in a quenched state. In this state, the quenching can accurately reflect the technical effects recorded by the applicant in the above technical effects column. After quenching, the oil cylinder 63 reverses (moves upward), and the online operator removes the quenched eccentric disc 5 and transfers it to a tempering furnace, tempering box, or similar tempering device for tempering. During the tempering process, the eccentric discs can be stacked or laid flat one by one for tempering. The tempering temperature is approximately 170-180℃, and the tempering time is approximately 280-320 minutes.

[0039] The oil temperature for the aforementioned quenching, i.e., oil quenching, is 40-50℃. The clamping force of the hydraulic press 6 on the eccentric disc 5 during quenching is preferably 4-6 MPa, and the holding time is 60-100 seconds. The specific choice depends on the three common specifications of the eccentric disc, as mentioned by the applicant in the background section above: 8.5mm thick, 2.5mm thin; 9.3mm thick, 3.3mm thin; 9.4mm thick, 3.6mm thin. The lifting / lowering of the cylinder column 63 of the hydraulic press 6 is achieved by the online operator using the corresponding buttons on the hydraulic press electrical control box (not shown in the figure).

[0040] In summary, the technical solution provided by this invention makes up for the shortcomings of the prior art, successfully completes the invention task, and accurately realizes the technical effects described by the applicant in the above technical effects column.

Claims

1. A fixture structure for quenching an eccentric disk in an electronic multi-arm system, characterized in that: The utility model discloses a dynamic pressure plate (1) and a static pressure plate (2) are included, the dynamic pressure plate (1) and static pressure plate (2) are arranged in pressure equipment in use state correspondingly, the dynamic pressure plate (1) is provided with a dynamic pressure plate oil hole (11) in the central position, the static pressure plate (2) is provided with a static pressure plate overflow oil hole (21) in the central position, the dynamic pressure plate oil hole (11) and static pressure plate overflow oil hole (21) correspond to each other, the dynamic pressure plate (1) is provided with a dynamic pressure plate oil guide and oil separation mechanism (12) with the dynamic pressure plate oil hole (11) on the side towards static pressure plate (2), and the static pressure plate (2) is provided with a static pressure plate oil guide and oil separation mechanism (22) with the static pressure plate overflow oil hole (21) on the side towards dynamic pressure plate (1), and the dynamic pressure plate oil guide and oil separation mechanism (12) and static pressure plate oil guide and oil separation mechanism (22) correspond to each other, an eccentric disc bearing disc limiting ring (3) and an eccentric disc bearing disc (4), the eccentric disc bearing disc limiting ring (3) is fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), the eccentric disc bearing disc (4) is located in the eccentric disc bearing disc limiting ring (3) and is also fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), the eccentric disc bearing disc (4) is provided with an eccentric disc body boss relief hole (41) in the central position, and the eccentric disc bearing disc (4) is also fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), and the eccentric disc bearing disc (4) is provided with an eccentric disc bearing disc oil guide groove (42) penetrating the thickness direction of eccentric disc bearing disc (4) around the eccentric disc body boss relief hole (41) and spaced apart in the direction away from the eccentric disc body boss relief hole (41) in the radiation state.

2. The jig structure for eccentric disc quenching of an electronic multi-arm according to claim 1, characterized by: The utility model discloses a dynamic pressure plate (1) and a static pressure plate (2) are included, the dynamic pressure plate (1) and static pressure plate (2) are arranged in pressure equipment in use state correspondingly, the dynamic pressure plate (1) is provided with a dynamic pressure plate oil hole (11) in the central position, the static pressure plate (2) is provided with a static pressure plate overflow oil hole (21) in the central position, the dynamic pressure plate oil hole (11) and static pressure plate overflow oil hole (21) correspond to each other, the dynamic pressure plate (1) is provided with a dynamic pressure plate oil guide and oil separation mechanism (12) with the dynamic pressure plate oil hole (11) on the side towards static pressure plate (2), and the static pressure plate (2) is provided with a static pressure plate oil guide and oil separation mechanism (22) with the static pressure plate overflow oil hole (21) on the side towards dynamic pressure plate (1), and the dynamic pressure plate oil guide and oil separation mechanism (12) and static pressure plate oil guide and oil separation mechanism (22) correspond to each other, an eccentric disc bearing disc limiting ring (3) and an eccentric disc bearing disc (4), the eccentric disc bearing disc limiting ring (3) is fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), the eccentric disc bearing disc (4) is located in the eccentric disc bearing disc limiting ring (3) and is also fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), the eccentric disc bearing disc (4) is provided with an eccentric disc body boss relief hole (41) in the central position, and the eccentric disc bearing disc (4) is also fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), and the eccentric disc bearing disc (4) is provided with an eccentric disc bearing disc oil guide groove (42) penetrating the thickness direction of eccentric disc bearing disc (4) around the eccentric disc body boss relief hole (41) and spaced apart in the direction away from the eccentric disc body boss relief hole (41) in the radiation state.

3. The jig structure for eccentric disc quenching of an electronic multi-arm according to claim 2, characterized by: The utility model discloses a dynamic pressure plate (1) and a static pressure plate (2) are included, the dynamic pressure plate (1) and static pressure plate (2) are arranged in pressure equipment in use state correspondingly, the dynamic pressure plate (1) is provided with a dynamic pressure plate oil hole (11) in the central position, the static pressure plate (2) is provided with a static pressure plate overflow oil hole (21) in the central position, the dynamic pressure plate oil hole (11) and static pressure plate overflow oil hole (21) correspond to each other, the dynamic pressure plate (1) is provided with a dynamic pressure plate oil guide and oil separation mechanism (12) with the dynamic pressure plate oil hole (11) on the side towards static pressure plate (2), and the static pressure plate (2) is provided with a static pressure plate oil guide and oil separation mechanism (22) with the static pressure plate overflow oil hole (21) on the side towards dynamic pressure plate (1), and the dynamic pressure plate oil guide and oil separation mechanism (12) and static pressure plate oil guide and oil separation mechanism (22) correspond to each other, an eccentric disc bearing disc limiting ring (3) and an eccentric disc bearing disc (4), the eccentric disc bearing disc limiting ring (3) is fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), the eccentric disc bearing disc (4) is located in the eccentric disc bearing disc limiting ring (3) and is also fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), the eccentric disc bearing disc (4) is provided with an eccentric disc body boss relief hole (41) in the central position, and the eccentric disc bearing disc (4) is also fixed on the side of static pressure plate (2) towards dynamic pressure plate (1), and the eccentric disc bearing disc (4) is provided with an eccentric disc bearing disc oil guide groove (42) penetrating the thickness direction of eccentric disc bearing disc (4) around the eccentric disc body boss relief hole (41) and spaced apart in the direction away from the eccentric disc body boss relief hole (41) in the radiation state.

4. The jig structure for eccentric disc quenching of an electronic multi-arm according to claim 1, characterized by: The eccentric disc bearing disc limiting ring (3) is located at the edge of the circumferential direction of the side surface of the static pressure disc (2) towards the dynamic pressure disc (1), the outer diameter of the eccentric disc bearing disc (4) is adapted to the inner diameter of the limiting ring cavity (32) of the eccentric disc bearing disc limiting ring (3), and the bearing disc outer cylindrical surface (44) of the eccentric disc bearing disc (4) is in contact with the limiting ring cavity cavity wall (321) of the limiting ring cavity (32).

5. The jig structure for eccentric disc quenching of an electronic multi-joint according to claim 1 or 4, characterized by: The dynamic pressure disc oil guide and oil distribution mechanism (12) comprises a dynamic pressure disc radial oil groove (121) and a dynamic pressure disc annular oil groove (122), the dynamic pressure disc radial oil groove (121) is arranged at intervals around the circumferential direction of the dynamic pressure disc (1) and extends from the edge of the dynamic pressure disc oil guide hole (11) to the edge of the dynamic pressure disc (1), and the dynamic pressure disc annular oil groove (122) is arranged at intervals around the circumferential direction of the dynamic pressure disc (1), the dynamic pressure disc radial oil groove (121) is disconnected by the dynamic pressure disc annular oil groove (122) at the position of the dynamic pressure disc annular oil groove (122) and forms a cross-shaped staggered relationship with the dynamic pressure disc annular oil groove (122).

6. The jig structure for eccentric disc quenching of an electronic multi-joint according to claim 1, characterized by: The static pressure disc oil guide and oil distribution mechanism (22) comprises a static pressure disc radial oil groove (221) and a static pressure disc annular oil groove (222), the static pressure disc radial oil groove (221) is arranged at intervals around the circumferential direction of the static pressure disc (2) and extends from the edge of the static pressure disc oil overflow hole (21) to the edge of the static pressure disc (2), and the static pressure disc annular oil groove (222) is arranged at intervals around the circumferential direction of the static pressure disc (2), the static pressure disc radial oil groove (221) is disconnected by the static pressure disc annular oil groove (222) at the position of the static pressure disc annular oil groove (222) and forms a cross-shaped staggered relationship with the static pressure disc annular oil groove (222).

7. The jig structure for eccentric disc quenching of an electronic multi-arm according to claim 1, characterized by: ​ 8. The jig structure for eccentric disc quenching of an electronic multi-arm according to claim 6, characterized by: In the dynamic pressure disc radial oil groove (121), the number of the cross points where each dynamic pressure disc radial oil groove is disconnected by the dynamic pressure disc annular oil groove (122) and forms a cross-shaped interlaced relationship with the dynamic pressure disc annular oil groove (122) is equal to the number of the dynamic pressure disc annular oil groove (122).

9. The jig structure for eccentric disc quenching of an electronic multi-arm according to claim 7, characterized by: In the static pressure disc radial oil groove (221), the number of the cross points where each static pressure disc radial oil groove is disconnected by the static pressure disc annular oil groove (222) and forms a cross-shaped interlaced relationship with the static pressure disc annular oil groove (222) is equal to the number of the static pressure disc annular oil groove (222).

10. The jig structure for eccentric disc quenching of an electronic multi-arm according to claim 3, characterized by: The number of the dynamic pressure disc fixed flange edge fastener probe-in grooves (131) is four which are equally spaced around the circumferential direction of the dynamic pressure disc fixed flange edge (13), and the shape of the dynamic pressure disc fixed flange edge fastener probe-in grooves (131) is a U-shaped notch which is open to the outside; the number of the static pressure disc fixed flange edge fastener probe-in grooves (231) is four which are equally spaced around the circumferential direction of the static pressure disc fixed flange edge (23), and the shape of the static pressure disc fixed flange edge fastener probe-in grooves (231) is a U-shaped notch which is open to the outside; the pressure equipment is a hydraulic press (6).

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