Pipe expanding machine

Abstract

The utility model discloses a pipe expanding machine, which belongs to the technical field of electric tools, and comprises a pipe expanding die, an ejector pin, a motor and a turning component, and the turning component comprises a moving part capable of moving back and forth, a transmission part capable of rotating forwards and reversely, and a rotating part driven by the transmission part capable of rotating reversely to rotate. A linkage structure is arranged between the moving part and the transmission part, and the linkage structure converts front-back linear motion of the moving part into circumferential rotation motion of the transmission part. A clutch structure is arranged between the transmission part and the rotating part and has an abutting state and a free state. The specific structure of the ejector pin is reasonably simplified, the movement load of the ejector pin is reduced, the driving effect of the ejector pin on the clamping jaw is improved, and the clamping jaw can smoothly intermittently rotate while the expansion effect of the clamping jaw is guaranteed.

Description

Technical Field

[0001] The utility model relates to the technical field of electric tools, in particular to a pipe expanding machine. Background Art

[0002] Pipe expanders are mainly used for connecting pipes. When in use, the end of the pipe is first expanded using the pipe expander, and then another pipe is inserted into the expanded end of the pipe, and then the two pipes are compressed by a crimping tool to complete the connection. In actual operation, in order to improve the expansion effect of the pipe, it is generally necessary to expand the end of the pipe multiple times. Usually, after each expansion action, the clamping claw is retracted and rotated to a certain angle, and then expanded again until the clamping claw rotates roughly one circle. In order to improve work efficiency, some existing pipe expanders are designed with a dial structure that can intermittently drive the clamping claw to rotate a certain angle after the expansion action is completed. However, the existing dial structure is generally driven directly by a push rod that moves back and forth to drive the clamping claw to retract and expand. The structure of the push rod is relatively complex and easily causes the push rod to be blocked, which is not conducive to improving the user experience. Utility Model Content

[0003] In order to solve the shortcomings and deficiencies in the above-mentioned prior art, the utility model provides a pipe expanding machine, which reasonably simplifies the specific structure of the ejector pin and reduces the motion load of the ejector pin, thereby improving the driving effect of the ejector pin on the clamping claw, ensuring the expansion effect of the clamping claw while allowing the clamping claw to rotate intermittently smoothly.

[0004] In order to achieve the above technical objectives, the present invention provides a pipe expanding machine, comprising:

[0005] The tube expansion die includes a plurality of circumferentially distributed and retractable claws;

[0006] The ejector pin moves forward and applies force to the jaws to open them, while the ejector pin moves backward and releases the jaws to close them.

[0007] The motor drives the ejector to move forward and backward through the transmission structure;

[0008] The pipe expander further includes a dial assembly for driving the jaws to intermittently rotate, the dial assembly including a moving part that can move forward and backward, a transmission part that can rotate forward and reverse, and a rotating part that is driven to rotate by the reverse rotating transmission part;

[0009] A linkage structure is provided between the moving part and the transmission part. The linkage structure converts the forward and backward linear motion of the moving part into the circumferential rotational motion of the transmission part. The moving part driven forward by the ejector pin drives the transmission part to rotate forward through the linkage structure. The moving part released by the ejector pin and moving backward drives the transmission part to rotate in the opposite direction through the linkage structure.

[0010] A clutch structure is provided between the transmission member and the rotating member. The clutch structure has an engaged state and a free state. The transmission member rotating in the forward direction rotates independently relative to the rotating member through the clutch structure in the free state. The transmission member rotating in the reverse direction drives the rotating member to rotate through the clutch structure in the engaged state. The rotating rotating member drives the claws of the pipe expansion mold to rotate.

[0011] Preferably, the transmission member is rotatably sleeved on the outside of the moving member, and the linkage structure is provided between the outer periphery of the moving member and the inner periphery of the transmission member.

[0012] Preferably, the linkage structure includes a linkage groove provided at one of the outer periphery of the moving part and the inner periphery of the transmission part, and a linkage part provided at the other part. The linkage groove is provided along the front-to-back direction and is at least partially inclined or bent relative to the front-to-back direction. A part of the linkage part is inserted into the linkage groove, and the moving part moving forward and backward drives the transmission part to rotate through the cooperation between the linkage groove and the linkage part.

[0013] Preferably, the ejector pin includes an ejector rod and a cone head, the ejector rod includes a rod body extending forward and backward, the cone head is connected to the front end of the rod body, the outer diameter of the rod body is smaller than the outer diameter of the cone head, and the movable part is sleeved on the outer periphery of the rod body.

[0014] Preferably, the movable member is sleeved on the outside of the ejector and is driven by the ejector to move forward. The dial assembly further includes a first elastic member with one end positioned and the other end in contact with the movable member. The first elastic member is configured to be deformed by force when the movable member is driven by the ejector to move forward, and to drive the movable member to move backward when the ejector moves backward.

[0015] Preferably, one of the inner peripheral wall of the movable member and the outer peripheral wall of the ejector pin is provided with a limiting groove extending forward and backward, and the other is provided with a limiting member inserted into the limiting groove, and the limiting member cooperates with the limiting groove to keep the movable member in linear motion.

[0016] Preferably, the rotating member can be rotatably sleeved on the outside of the transmission member, and the clutch structure includes a ratchet that can be rotatably arranged on the transmission member and a circle of convex teeth arranged on the inner circumferential wall of the rotating member. The transmission member rotating in the forward direction causes the ratchet to be resisted by the convex teeth and swing toward the center of the transmission member so that the ratchet and the convex teeth are in a free state. The transmission member rotating in the reverse direction causes the ratchet and the convex teeth to abut against each other so that the ratchet and the convex teeth are in an engaged state.

[0017] Preferably, the clutch structure further comprises a second elastic member with one end positioned and the other end in contact with the ratchet, and the second elastic member biases the ratchet toward the convex tooth.

[0018] Preferably, the transmission member is provided with a fixed boss, a positioning groove is provided on the side of the boss facing the ratchet, one end of the second elastic member extends into the positioning groove and abuts against the boss; and / or, the ratchet is provided with a boss protruding outward, the other end of the second elastic member is sleeved on the boss and abuts against the ratchet.

[0019] Preferably, the tube expansion mold further includes an annular seat, the rear end of each claw is connected to the annular seat, and an engaging structure is provided between the front end of the rotating member and the rear end of the claw, and the rotating rotating member drives the claw to rotate through the engaging structure.

[0020] After adopting the above technical solution, the utility model has the following advantages:

[0021] 1. The pipe expander provided by the present invention comprises a rotating assembly for driving the intermittent rotation of the clamping claws, comprising a moving part, a transmission part, and a rotating part. A linkage structure is provided between the moving part and the transmission part, and a clutch structure is provided between the transmission part and the rotating part. When the moving part is driven forward by the ejector pin, the moving part drives the transmission part to rotate in the forward direction through the linkage structure. At this time, the clutch structure is in a free state, and the transmission part cannot drive the rotating part to rotate synchronously through the clutch structure. That is, the transmission part rotates independently relative to the rotating part, so that the rotating part does not rotate when the ejector pin moves forward to open the clamping claws to expand the end of the pipe, thereby ensuring the expansion effect of the clamping claws on the end of the pipe. When the ejector pin moves backward, the moving part is released, and the moving part released by the ejector pin moves backward. The moving part drives the transmission part to rotate in the opposite direction through the linkage structure. At this time, the clutch structure is in an engaged state. The transmission part rotating in the opposite direction can drive the rotating part to rotate synchronously in the opposite direction through the clutch structure. The rotating part rotating in the opposite direction drives the clamping claws to rotate circumferentially, thereby realizing the intermittent rotating drive of the clamping claws by the rotating assembly. The specific structure of the dial assembly is reasonably set so that the rotation of the transmission part is driven by the moving part through the linkage structure, rather than directly by the ejector pin. This can reasonably simplify the specific structure of the ejector pin and reduce the motion load of the ejector pin, thereby improving the driving effect of the ejector pin on the clamping claw, ensuring the expansion effect of the clamping claw while allowing the clamping claw to rotate intermittently smoothly.

[0022] In addition, since the intermittent rotation of the clamping jaw occurs during the period of the return stroke of the ejector pin, that is, the intermittent rotation of the clamping jaw occurs during the time interval between the two expansion actions of the clamping jaw, there is no need to set up an additional working time required for the dial assembly to drive the clamping jaw to rotate intermittently, which can effectively improve the working efficiency of the pipe expander.

[0023] 2. The transmission member is rotatably mounted on the outside of the moving member, and the linkage structure is preferably arranged between the outer periphery of the moving member and the inner periphery of the transmission member. The matching mode between the transmission member and the moving member and the setting position of the linkage structure are reasonably set to make the matching between the transmission member and the moving member more compact, improve the matching stability of the linkage structure, and thus improve the stability of the moving member driving the transmission member to rotate through the linkage structure.

[0024] 3. The linkage structure utilizes a linkage groove and a linkage member. Because at least a portion of the linkage groove is inclined or curved relative to the fore-aft direction, the forward-moving moving member can drive the transmission member in forward rotation through the linkage groove and the linkage member, while the backward-moving moving member can drive the transmission member in reverse rotation through the linkage groove and the linkage member. By rationally designing the specific coordination structure of the linkage structure, the mechanical coordination structure is used to smoothly convert the forward and backward linear motion of the moving member into the circumferential rotational motion of the transmission member.

[0025] 4. The ejector preferably adopts a structure in which an ejector rod and a cone head cooperate. The cone head is connected to the front end of the rod body. The outer diameter of the rod body is preferably smaller than that of the cone head. The movable member is preferably sleeved around the outer periphery of the rod body. Since the outer diameter of the rod body is smaller than that of the cone head, the outer periphery of the rod body provides adequate installation space for the toggle assembly, which can appropriately reduce the overall dimensions of the ejector, movable member, and transmission member, thereby facilitating appropriate control of the overall dimensions of the entire machine.

[0026] 5. The moving member is sleeved onto the exterior of the ejector pin. The pin drives the moving member forward, causing the first elastic member to deform under force. When the ejector pin moves backward, it releases the moving member, causing the first elastic member to recover its deformation and drive the moving member backward. Properly designating the driving force for the forward and backward movement of the moving member eliminates the need for a power transmission mechanism between the motor and the moving member, simplifying the structure of the tube expander.

[0027] When the ejector moves backward, the clamping jaws of the tube expansion mold are released. As the ejector moves backward, the clamping jaws gradually retract. The first elastic member drives the movable member backward as the ejector moves backward. The backward-moving movable member, through a linkage mechanism, drives the transmission member in the opposite direction to rotate. The reverse-rotating transmission member, through a clutch mechanism, drives the rotating member in the opposite direction to rotate. The reverse-rotating rotating member, in turn, drives the gradually retracting clamping jaws to rotate a certain angle. The clamping jaws complete intermittent rotation during the ejector's return stroke, eliminating the need for further rotation after the ejector has returned, improving the tube expander's operating efficiency.

[0028] 6. A limiting groove and a limiting member that cooperate with each other are set between the inner peripheral wall of the moving part and the outer peripheral wall of the ejector pin. The cooperation between the limiting groove and the limiting member enables the moving part to maintain linear motion when moving forward and backward, thereby avoiding the situation where the moving part moving backward rotates circumferentially and cannot smoothly drive the transmission part to rotate in the opposite direction through the linkage structure, and ensuring that the dial assembly can drive the clamping claw to rotate intermittently smoothly.

[0029] 7. The ratchet of the clutch structure is rotatably arranged on the transmission member, and the convex teeth of the clutch structure are arranged on the inner circumferential wall of the rotating member. When the transmission member rotates in the forward direction, the ratchet is resisted by the convex teeth and swings toward the center of the transmission member. The ratchet slips relative to the convex teeth, causing the clutch structure to be in a free state. The transmission member cannot drive the rotating member to rotate through the clutch structure in the free state, and thus cannot drive the claws of the pipe expansion mold to rotate, so that the claws will not rotate when the expanded pipe is opened, ensuring the expansion effect of the pipe expansion mold on the pipe. When the transmission member rotates in the reverse direction, the ratchet and the convex teeth are in contact, and the clutch structure is in an engaged state. The reverse rotating transmission member can drive the transmission member to rotate through the clutch structure in the engaged state, and the transmission member drives the retracted claws to rotate, so that the claws can rotate intermittently.

[0030] 8. When the ratchet is affected by the cam and swung toward the center of the transmission member and away from the cam, the second elastic member is deformed by force. When the cam releases the ratchet, the deformed second elastic member causes the ratchet to swing away from the center of the transmission member, allowing the ratchet to promptly and smoothly engage the cam when the transmission member rotates in the opposite direction. This allows the reverse-rotating transmission member to smoothly drive the rotating member to rotate through the engagement of the ratchet and cam.

[0031] 9. A boss is provided on the transmission member, and a positioning groove is provided on the boss. One end of the second elastic member extends into the positioning groove and contacts the boss, thereby maintaining a stable positioning of the one end of the second elastic member. A boss is provided on the ratchet, and the other end of the second elastic member is sleeved on the boss and contacts the ratchet, thereby maintaining a stable contact and fit between the other end of the second elastic member and the ratchet. The coordination structure between the second elastic member and other components is reasonably arranged so that the second elastic member can stably act on the ratchet, thereby ensuring the stability of the ratchet when it contacts the boss, and further ensuring the stability of the transmission member when the clutch structure in the contact state drives the rotating member to rotate.

[0032] 10. An interlocking structure is provided between the front end of the rotating member and the rear end of the clamping jaws. The rotating member can drive the clamping jaws to rotate synchronously through the interlocking structure, so that the clamping jaws rotate a certain angle relative to the pipe after one expansion action is completed before the next expansion action. The reasonable arrangement of the matching structure between the rotating member and the clamping jaws ensures that the rotating member can smoothly and effectively drive the clamping jaws to rotate synchronously when rotating. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 This is a schematic diagram of the entire tube expanding machine of Example 1;

[0034] Figure 2 This is a partial structural diagram of the pipe expanding machine of Example 1 when the pipe expanding die is installed;

[0035] Figure 3 This is a partial structural diagram of the pipe expanding machine in Example 1 when the pipe expanding die is not installed;

[0036] Figure 4 This is a structural diagram of the tube expanding die in the tube expanding machine of Example 1;

[0037] Figure 5 1 is an axial cross-sectional view of a tube expanding die in a tube expanding machine according to Example 1;

[0038] Figure 6 This is a diagram showing the coordination structure of the cam and the rotating shaft in the pipe expanding machine of Example 1;

[0039] Figure 7 An exploded view of part of the structure of the pipe expander in Example 1;

[0040] Figure 8 This is a structural diagram of the moving parts in the pipe expanding machine of Example 1;

[0041] Figure 9 It is a side view of the moving parts in the pipe expander of Example 1;

[0042] Figure 10 This is a structural diagram of the transmission components in the pipe expanding machine of Example 1;

[0043] Figure 11 The structure of the rotating part in the pipe expanding machine of embodiment 1 Figure 1 ;

[0044] Figure 12 The structure of the rotating part in the pipe expanding machine of embodiment 1 Figure 2 ;

[0045] Figure 13 This is a diagram showing the coordination structure of the ejector pin, moving part, transmission part, rotating part, and clutch structure in the tube expanding machine of Example 1;

[0046] Figure 14 This is a diagram showing the coordination structure of the ejector pin, the moving part, and the transmission part in the tube expanding machine of Example 1;

[0047] Figure 15 This is a structural diagram of the rotating assembly in the pipe expanding machine of Example 1;

[0048] Figure 16 This is a partial structural diagram of the pipe expander in Example 1 when the ejector pin is not moving forward and the jaws are in a retracted state;

[0049] Figure 17 This is a partial structural diagram of the pipe expander in Example 1 when the ejector pin moves backward into position and the claws are in an open state.

[0050] In the figure, 100-tube expansion mold, 110-claw, 111-arc convex edge, 112-second protrusion, 120-annular seat, 121-annular groove, 130-gathering spring,

[0051] 200-thimble, 210-thrust rod, 211-rod body, 212-back plate, 213-lug, 220-cone head, 230-roller, 240-pin rod,

[0052] 310-motor, 320-reduction mechanism,

[0053] 400-turn assembly, 410-moving part, 411-flange, 420-transmission part, 421-pin, 422-boss, 4221-positioning groove, 423-protrusion, 430-rotating part, 431-first step surface, 432-second step surface, 433-first protrusion, 440-linkage structure, 441-linkage groove, 441a-front groove section, 441b-rear groove section, 441c-deformation groove section, 4 41d, 441d'-slot wall, 442-linkage member, 4421-pin, 450-clutch structure, 451-ratchet, 4511-convex column, 452-convex tooth, 453-second elastic member, 4531-second spring, 454-tooth groove, 461-limiting groove, 462-limiting member, 470-first elastic member, 471-first spring, 481-front gasket, 482-rear gasket, 490-bite structure,

[0054] 500- transmission structure, 510- rotating shaft, 520- cam, 521- pushing surface, 522- avoiding surface, 523- transition surface,

[0055] 600-case, 610-handle,

[0056] 700-return spring,

[0057] 810-front seat cover, 820-rear seat cover, 821-slide. DETAILED DESCRIPTION

[0058] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be understood that the following terms indicating orientations or positional relationships, such as "upper," "lower," "left," "right," "longitudinal," "lateral," "inner," "outer," "vertical," "horizontal," "top," and "bottom," are based solely on the orientations or positional relationships shown in the accompanying drawings and are intended solely for the purpose of facilitating and simplifying the description of the present invention. They do not indicate or imply that the device or element referred to must have a specific orientation or be constructed or operated in a specific orientation, and therefore should not be construed as limiting the present invention.

[0059] Example 1

[0060] Combine Figures 1 to 17 The first embodiment of the present invention provides a pipe expanding machine, comprising:

[0061] The tube expansion die 100 includes a plurality of circumferentially distributed and retractable claws 110;

[0062] The ejector pin 200 moves forward and applies force to the claw 110 to open the claw 110, while the ejector pin 200 moves backward and releases the claw 110 to close the claw 110.

[0063] The motor 310 drives the ejector 200 to move forward and backward through the transmission structure 500;

[0064] The pipe expander further includes a rotating assembly 400 for driving the jaws 110 to intermittently rotate. The rotating assembly 400 includes a moving member 410 that can move forward and backward, a transmission member 420 that can rotate forward and reverse, and a rotating member 430 that is driven to rotate by the reverse rotating transmission member 420.

[0065] A linkage structure 440 is provided between the moving member 410 and the transmission member 420. The linkage structure 440 converts the forward and backward linear motion of the moving member 410 into the circumferential rotational motion of the transmission member 420. The moving member 410, which is driven forward by the ejector 200, drives the transmission member 420 to rotate forward through the linkage structure 440. The moving member 410, which is released by the ejector 200 and moves backward, drives the transmission member 420 to rotate in the reverse direction through the linkage structure 440.

[0066] A clutch structure 450 is provided between the transmission member 420 and the rotating member 430. The clutch structure 450 has an engaged state and a free state. The transmission member 420 rotating in the forward direction rotates independently relative to the rotating member 430 through the clutch structure 450 in the free state. The transmission member 420 rotating in the reverse direction drives the rotating member 430 to rotate through the clutch structure 450 in the engaged state. The rotating rotating member 430 drives the claws 110 of the pipe expansion mold 100 to rotate.

[0067] When the movable member 410 is driven by the ejector 200 to move forward, the movable member 410 drives the transmission member 420 to rotate forward through the linkage structure 440. At this time, the clutch structure 450 is in a free state, and the transmission member 420 cannot drive the rotating member 430 to rotate synchronously through the clutch structure 450. That is, the transmission member 420 rotates independently relative to the rotating member 430, so that the claw 110 does not rotate when the ejector 200 moves forward to open the claw 110 to expand the end of the pipe, thereby ensuring the expansion effect of the claw 110 on the end of the pipe. When the ejector pin 200 moves backward, the movable member 410 is released. The movable member 410 released by the ejector pin 200 moves backward. The movable member 410 drives the transmission member 420 to rotate in the opposite direction through the linkage structure 440. At this time, the clutch structure 450 is in an abutting state. The transmission member 420 rotating in the opposite direction can drive the rotating member 430 to rotate in the opposite direction synchronously through the clutch structure 450. The rotating member 430 rotating in the opposite direction drives the claw 110 to rotate circumferentially, thereby realizing the intermittent toggle drive of the toggle assembly 400 on the claw 110. The specific structure of the toggle assembly 400 is reasonably set so that the rotation of the transmission member 420 is driven by the movable member 410 through the linkage structure 440 rather than directly by the ejector pin 200. This can reasonably simplify the specific structure of the ejector pin 200 and reduce the motion load of the ejector pin 200, thereby improving the driving effect of the ejector pin 200 on the claw 110, ensuring the expansion effect of the claw 110, and allowing the claw 110 to rotate intermittently. Since the intermittent rotation of the clamping jaw 110 occurs during the period of the return stroke of the ejector pin 200, that is, the intermittent rotation of the clamping jaw 110 occurs during the time interval between two expansion actions of the clamping jaw 110, there is no need to set up an additional working time required for the dial assembly 400 to drive the clamping jaw 110 to perform intermittent rotation, which can effectively improve the working efficiency of the pipe expander.

[0068] In the description of this embodiment, the direction in which the ejector pin 200 moves toward the tube expanding die 100 to open the claws 110 is defined as the front direction, and the direction in which the ejector pin 200 moves away from the tube expanding die 100 to close the claws 110 is defined as the rear direction.

[0069] Combine Figure 4 、 Figure 5In this embodiment, the tube expansion die 100 further includes an annular seat 120, to which the rear end of each clamping jaw 110 is connected. Specifically, there are six clamping jaws 110, which are arranged in a circle along the circumference of the annular seat 120. A circle of annular grooves 121 is provided on the inner wall of the front end of the annular seat 120. The rear end of each clamping jaw 110 extends into the front end of the annular seat 120 and is provided with an outwardly protruding arcuate ridge 111. The arcuate ridge 111 is embedded in the annular groove 121 to connect the clamping jaw 110 to the annular seat 120. The cooperation between the arcuate ridge 111 and the annular groove 121 also limits the axial position of the clamping jaw 110. The outer wall of the curved ridge 111 is provided with an inwardly concave groove. A gathering spring 130 is provided at the rear end of the jaws 110, which engages with the curved ridge 111 to clamp each jaw 110. The gathering spring 130 is embedded in the groove of the curved ridge 111 of each jaw 110 and is also located within the annular groove 121 of the annular seat 120. The gathering spring 130 is annular in shape and applies a preload force to the jaws 110, causing them to be in a retracted state under normal conditions. In this retracted state, the jaws 110 are tightly gathered together, and the front ends of the jaws 110 form a tapered head with a maximum outer diameter of D1. When the ejector pin 200 moves forward, causing the jaws 110 to switch from the retracted state to the open state, a gap is created between adjacent jaws 110, and the gathering spring 130 is deformed under the force, causing the overall outer diameter of the jaws 110 to decrease to D2, where D2 is greater than D1. When the ejector pin 200 moves backward to release the jaws 110, the restoring springs 130 force the jaws 110 from the open state back to the closed state. As a preferred option for this embodiment, the tube expander can be equipped with multiple tube expanding dies 100 with different maximum outer diameters of the jaws 110 in the closed state, allowing the tube expander to expand pipes of varying diameters. It is understood that the number of jaws 110 in the tube expanding die 100 is not limited to six; other reasonable numbers, such as three, four, five, seven, or eight, may also be used.

[0070] Combine Figure 2 、 Figure 3 、 Figure 6The transmission structure 500 includes a rotating shaft 510 driven by the motor 310 and a cam 520 sleeved on the rotating shaft 510. The cam 520 is fixedly sleeved on the rotating shaft 510 or the cam 520 and the rotating shaft 510 are integrally formed. The rotating shaft 510 rotates with its own central axis as the rotation center line under the drive of the motor 310. When the motor 310 is working, the cam 520 is driven to rotate by the rotating shaft 510, and the rotating cam 520 drives the ejector 200 to move forward. In this embodiment, the motor 310 drives the rotating shaft 510 to rotate through the reduction mechanism 320. The rotating shaft 510 can be connected to the output shaft of the reduction mechanism 320 through a coupling. The output shaft of the reduction mechanism 320 can also directly serve as the rotating shaft 510. When the motor 310 is working, the rotating shaft 510 is driven to rotate with its own central axis as the rotation center line through the reduction mechanism 320. The rotating rotating shaft 510 drives the cam 520 to rotate synchronously. It is understandable that the reduction mechanism 320 may adopt a transmission structure that meets the reduction transmission requirements, such as a planetary gear structure.

[0071] Combine Figure 1 In this embodiment, the tube expander further includes a housing 600. To appropriately reduce the overall front-to-back dimensions of the tube expander, the axial direction of the motor 310 is preferably aligned with the axial direction of the rotating shaft 510. Furthermore, the axial direction of the rotating shaft 510 is preferably perpendicular to the axial direction of the ejector pin 200. That is, the ejector pin 200 is perpendicular to the rotating shaft 510 and the motor 310. The motor 310 and the reduction mechanism 320 are disposed within a handle 610 formed by the housing 600. Components such as the cam 520, the ejector pin 200, and the dial assembly 400 are disposed within the main cavity of the housing 600, resulting in the tube expander having a roughly pistol-shaped overall shape. The tube expander of this embodiment can utilize a battery pack to power various electrical components, or alternatively, utilize a power cord with a plug to connect to the mains electricity supply. Other structures of the tube expander can refer to existing technologies, such as a switch for controlling the start and stop of the housing 600, a control panel disposed within the housing 600, and a rotating shaft 510 rotatably mounted within the housing 600 via a bearing, and so on. These will not be described in detail here. Of course, the overall appearance of the tube expander is not limited to that shown above and in the accompanying drawings, and may also be configured in other reasonable styles.

[0072] Combine Figure 7As a preferred embodiment of this embodiment, ejector pin 200 includes an ejector pin 210 and a tapered head 220. Ejector pin 210 includes a rod portion 211 extending forward and backward. Tapered head 220 is connected to the front end of rod portion 211. Tapered head 220 is tapered, tapering from the front to the rear. The outer diameter of the rear end of tapered head 220 is larger than the outer diameter of rod portion 211. To reduce friction between cam 520 and ejector pin 200 when driving ejector pin 200 forward, a rotatable roller 230 is provided at the rear end of ejector pin 200. The outer circumference of cam 520 contacts roller 230, and the rotating cam 520 applies force to ejector pin 200 through roller 230, forcing ejector pin 200 to move forward. In this embodiment, the rear end of the rod body 211 is provided with a disc-shaped rear plate 212. The rear plate 212 is provided with two rearwardly protruding, oppositely disposed lugs 213. A roller 230 is rotatably mounted between the two lugs 213 via a pin 240. The axial direction of the pin 240 is preferably parallel to the axial direction of the rotating shaft 510, and the ends of the pin 240 are respectively inserted into the holes in the two lugs 213. Because the roller 230 can rotate circumferentially relative to the pin 240, the roller 230 effectively reduces the contact friction between the cam 520 and the ejector pin 200, allowing the cam 520 to smoothly drive the ejector pin 200 forward. In this embodiment, the cone head 220 and the rod body 211 are secured together via a threaded engagement. Of course, the cone head 220 and the rod body 211 can also be secured together via other means, or the cone head 220 and the rod body 211 can be integrally formed.

[0073] Combine Figure 6 The outer peripheral wall of the cam 520 is provided with a push surface 521, an avoidance surface 522 and a transition surface 523 which are sequentially distributed along the circumferential direction. Figure 6 Point E in the figure represents the proximal endpoint of the push surface 521, and point F represents the distal endpoint of the push surface 521. The push surface 521 extends from point E to point F along the involute, that is, the push surface 521 is roughly an involute arc surface. Point C represents the central axis of the rotating shaft 510, and ⊙D represents a circle with point C as the center and the distance between point C and point F as the radius. The radial distance between the push surface 521 and the contour line of ⊙D gradually decreases from point E to point F. Figure 6 Point G in the figure represents the dividing point between the avoidance surface 522 and the transition surface 523. One end of the avoidance surface 522 is smoothly connected to the distal end of the push surface 521, and the other end of the avoidance surface 522 is smoothly connected to the transition surface 523. The two ends of the transition surface 523 are smoothly connected to the proximal ends of the avoidance surface 522 and the push surface 521, respectively. The distance between each point on the avoidance surface 522 and point C is smaller than the distance between point F and point C. The distance between each point on the transition surface 523 and point C gradually increases from point G to point E. When the pipe expander is working, the motor 310 drives the cam 520 along Figure 6When the push surface 521 of the cam 520 contacts the roller 230, the cam 520 drives the ejector pin 200 forward through the contact between the push surface 521 and the roller 230. The forward movement of the ejector pin 200 causes each claw 110 to switch from the retracted state to the open state. When the cam 520 rotates until the avoidance surface 522 contacts the roller 230, the cam 520 releases the roller 230, and the ejector pin 210 can move backward to reset and release each claw 110. Under the action of the gathering spring 130, each claw 110 can switch from the open state to the retracted state.

[0074] To ensure that ejector pin 200 can promptly and smoothly move backward for reset when released by cam 520, a return spring 700 is sheathed around the exterior of ejector pin 200. Specifically, return spring 700 is sheathed around the rear end of rod body 211, with its front end positioned so that its rear end abuts against rear plate 212 of ejector pin 210. When ejector pin 200 moves forward, driven by cam 520, return spring 700 is compressed and elastically deformed. When the push surface 521 of cam 520 disengages from roller 230, releasing ejector pin 200, the return spring 700, having recovered its deformation, applies force to ejector pin 200, causing it to move backward for reset. Once ejector pin 200 has returned to its original position, the push surface 521 of cam 520 again contacts roller 230, driving ejector pin 200 forward through roller 230.

[0075] As a preferred solution of this embodiment, the dial assembly 400 is sleeved on the outside of the ejector pin 200. Specifically, the moving part 410 and the transmission part 420 of the dial assembly 400 are sleeved on the outer periphery of the rod body 211, and the rotating part 430 is sleeved on the outside of the transmission part 420 and the rear end of the cone head 220. The outer diameter difference between the rod body 211 and the cone head 220 is utilized to provide a certain installation space for the moving part 410 and the transmission part 420, which can reasonably reduce the external dimensions of the dial assembly 400 when it is sleeved on the outside of the ejector pin 200, thereby reasonably reducing the external dimensions of the main body of the pipe expander.

[0076] As a preferred embodiment of this embodiment, the moving member 410 is generally in the shape of a hollow cylinder and is mounted on the outside of the rod body 211 so as to be movable back and forth, with an appropriate gap between the moving member 410 and the rod body 211. The transmission member 420 is generally in the shape of a hollow disk and is mounted on the outside of the moving member 410 so as to be rotatable in the circumferential direction, with an appropriate gap between the transmission member 420 and the moving member 410. The linkage structure 440 is disposed between the outer periphery of the moving member 410 and the inner periphery of the transmission member 420.

[0077] Combine Figure 13 、 Figure 14In this embodiment, the linkage structure 440 includes a linkage groove 441 provided at one of the outer periphery of the moving member 410 and the inner periphery of the transmission member 420, and a linkage member 442 provided at the other. The linkage groove 441 is provided along the front-to-back direction and is at least partially inclined or curved relative to the front-to-back direction. A portion of the linkage member 442 is inserted into the linkage groove 441. The moving member 410 that moves forward and backward drives the transmission member 420 to rotate through the cooperation between the linkage groove 441 and the linkage member 442. Figure 8 、 Figure 10 Preferably, the linkage groove 441 is provided on the outer peripheral wall of the moving member 410 and is provided along the front-rear direction, the linkage member 442 is fixed on the transmission member 420 and protrudes toward the center of the transmission member 420, and the linkage member 442 is partially inserted into the linkage groove 441 toward the center of the transmission member 420. Figure 9 Specifically, the linkage groove 441 includes a front groove section 441a and a rear groove section 441b distributed front to back and staggered along the circumference of the moving part 410. The linkage groove 441 also includes a deformation groove section 441c arranged between the front groove section 441a and the rear groove section 441b. The two groove walls 441d of the deformation groove section 441c are inclined or curved relative to the front and rear directions. The front end of the deformation groove section 441c is smoothly connected to the front groove section 441a, and the rear end of the front groove section 441a is smoothly connected to the rear groove section 441b. Figure 9 The straight line L1 in the figure represents the approximate boundary between the front slot section 441a and the deformed slot section 441c, and the straight line L2 represents the approximate boundary between the deformed slot section 441c and the rear slot section 441b. The linkage member 442 can be a pin 4421. In order to reduce the thickness of the transmission member 420, a block-shaped protrusion 423 is provided on the rear surface of the transmission member 420. The end of the pin 4421 facing away from the center of the transmission member 420 is fixedly inserted into the protrusion 423. The end of the pin 4421 facing the center of the transmission member 420 protrudes from the inner peripheral wall of the transmission member 420 to form the linkage member 442. The transmission member 420 is sleeved on the outside of the moving member 410, and the end of the pin 4421 facing the center of the transmission member 420 is inserted into the linkage slot 441. When the moving member 410 moves forward, the linkage member 442 moves backward relative to the linkage groove 441, and the groove wall 441d of the deformed groove section 441c contacts the linkage member 442, causing the transmission member 420 to be forced to move along the Figure 10 When the moving member 410 moves backward, the linkage member 442 moves forward relative to the linkage groove 441, and the groove wall 441d' of the deformed groove section 441c contacts the linkage member 442, causing the transmission member 420 to be forced along Figure 10-α is rotated in the opposite direction. The specific matching structure of the linkage structure 440 is reasonably set, and the front and rear linear motion of the moving part 410 is smoothly converted into the circumferential rotation motion of the transmission part 420 by using a mechanical matching structure. As an alternative to this embodiment, the linkage part 442 can also adopt other reasonable components such as balls, small rollers to replace the pin 4421. As an alternative to this embodiment, the setting positions of the linkage groove 441 and the linkage part 442 can also be interchanged, and the linkage groove 441 is arranged on the inner peripheral wall of the transmission part 420, and the linkage part 442 is arranged on the moving part 410, and the linkage part 442 protrudes relative to the outer peripheral wall of the moving part 410 and cooperates with the linkage groove 441. As an optional solution of this embodiment, the deformation groove section 441c can be an oblique groove arranged with respect to the front and rear direction, or it can be an arc groove arranged with respect to the front and rear direction.

[0078] In order to improve the stability of the circumferential rotation of the transmission member 420 driven by the moving member 410 through the linkage structure 440, two groups of linkage structures 440 are evenly spaced along the circumference of the moving member 410. That is, two linkage grooves 441 are provided and evenly spaced along the circumference on the outer peripheral wall of the moving member 410, and two linkage members 442 are provided and evenly spaced along the circumference on the inner periphery of the transmission member 420. Of course, the number of linkage structures 440 is not limited to two groups, and can also be set to one, three, four, or other reasonable numbers.

[0079] Combine Figure 7 、 Figure 16 In this embodiment, when the ejector pin 200 is driven by the cam 520 to move forward, the rear plate 212 of the ejector pin 200 contacts the rear end face of the moving member 410, causing the moving member 410 to be forced to move forward. In order to allow the moving member 410 that is moving forward to smoothly move backward and reset when the ejector pin 200 moves backward, the dial assembly 400 also includes a first elastic member 470 with a positioning setting at one end and the other end in contact with the moving member 410. The first elastic member 470 is configured to deform when the moving member 410 is driven by the ejector pin 200 to move forward, and to drive the moving member 410 to move backward when the ejector pin 200 moves backward. As a preferred solution of this embodiment, the first elastic member 470 adopts a first spring 471, and a circle of first step surface 431 is provided on the inner peripheral wall of the front part of the rotating member 430, combined with Figure 11, the front end of the first spring 471 is against the first step surface 431 to realize positioning setting. The front end of the moving member 410 is provided with a circle of flange 411 extending radially outward, and the rear end of the first spring 471 is against the flange 411 to realize contact with the moving member 410. When the moving member 410 is driven by the ejector pin 200 to move forward, the first spring 471 is compressed. When the return spring 700 that restores the deformation drives the ejector pin 200 to move backward for reset, the ejector pin 200 releases the moving member 410, and the first spring 471 that restores the deformation applies force to the moving member 410 so that the moving member 410 is forced to move backward for reset.

[0080] The first spring 471 and the return spring 700 are distributed front to back and are respectively used to drive the movable member 410 and the ejector pin 200 to move backward and reset. That is, two different springs are used to drive the movable member 410 and the ejector pin 200 to reset, which can appropriately reduce the load borne by the two springs, thereby extending the service life of the springs, ensuring that the movable member 410 and the ejector pin 200 can move backward and into place when the tube expander is working, and ensuring the working performance stability of the tube expander.

[0081] Combine Figure 13In order to make the movable member 410 move only forward and backward, a limiting structure is provided between the ejector pin 200 and the movable member 410. One of the inner peripheral wall of the movable member 410 and the outer peripheral wall of the ejector pin 200 is provided with a limiting groove 461 extending forward and backward, and the other is provided with a limiting member 462 inserted into the limiting groove 461. The limiting member 462 cooperates with the limiting groove 461 to keep the movable member 410 in linear motion. Specifically in the present embodiment, the limiting groove 461 is provided on the inner peripheral wall of the movable member 410 and extends in the forward and backward direction. The limiting member 462 is fixed to the rod body 211 of the ejector pin 200. The end of the limiting member 462 protrudes from the outer peripheral wall of the rod body 211 and is inserted into the limiting groove 461. Through the cooperation of the limiting member 462 and the limiting groove 461, the movable member 410 is circumferentially limited, thereby preventing the movable member 410 from rotating circumferentially when moving forward and backward. The limiting member 462 preferably adopts a rod-shaped member, and both ends of the limiting member 462 protrude from the outer peripheral wall of the rod body 211. Two limiting grooves 461 uniformly spaced along the circumference are provided on the inner wall of the movable member 410. The two ends of the limiting member 462 are respectively inserted into the two limiting grooves 461, thereby improving the effect of the limiting member 462 and the limiting groove 461 cooperating to limit the movable member 410 in the circumferential direction. As an alternative to the present embodiment, the limiting member 462 can also be replaced by components such as balls. As an alternative to the present embodiment, the setting positions of the limiting groove 461 and the limiting member 462 can be interchangeable, with the limiting groove 461 being located on the outer peripheral wall of the rod body 211 and the limiting member 462 being located on the movable member 410, and the part of the limiting member 462 protruding relative to the inner peripheral wall of the movable member 410 and cooperating with the limiting groove 461. As an alternative to this embodiment, the number of the limiting grooves 461 can also be set to one, three, four or other reasonable numbers, and the number of the limiting members 462 is determined according to the number of the limiting grooves 461.

[0082] Combine Figure 16 The rotating member 430 is sleeved on the outside of the transmission member 420 and the rear end of the cone head 220. There is an appropriate gap between the rotating member 430 and the transmission member 420, and there is also an appropriate gap between the rotating member 430 and the rear end of the cone head 220. Figure 15The clutch structure 450 includes a ratchet 451 rotatably provided on the transmission member 420 and a circle of convex teeth 452 provided on the inner circumferential wall of the rotating member 430. The transmission member 420 rotating in the forward direction causes the ratchet 451 to be resisted by the convex teeth 452 and to swing toward the center of the transmission member 420 so that the ratchet 451 and the convex teeth 452 are in a free state. The transmission member 420 rotating in the reverse direction causes the ratchet 451 to abut against the convex teeth 452 so that the ratchet 451 and the convex teeth 452 are in a contact state. Furthermore, the clutch structure 450 also includes a second elastic member 453 with one end positioned and the other end in contact with the ratchet 451. The second elastic member 453 is configured to deform when the ratchet 451 is forced to swing toward the center of the transmission member 420, and to drive the ratchet 451 to swing away from the center of the transmission member 420 when the ratchet 451 is released. Figure 10 、 Figure 13 Specifically, the ratchet tooth 451 is rotatably mounted on the rear surface of the transmission member 420 via a pin 421. The ratchet tooth 451's swinging plane is perpendicular to the front-to-back direction. The second elastic member 453 is preferably a second spring 4531. A fixed boss 422 is provided on the rear surface of the transmission member 420. A positioning groove 4221 is provided on the side of the boss 422 facing the ratchet tooth 451. One end of the second spring 4531 extends into the positioning groove 4221 and abuts against the boss 422 to achieve positioning. The ratchet tooth 451 is provided with a boss 4511 that protrudes outward toward the boss 422. The other end of the second spring 4531 is sleeved on the boss 4511 and abuts against the ratchet tooth 451, placing the second spring 4531 in a compressed state. The positioning groove 4221 and the boss 4511 ensure the structural stability of the second spring 4531, allowing it to effectively act on the ratchet tooth 451. The protruding teeth 452 are arranged on the inner peripheral wall of the rear end of the rotating member 430. A tooth groove 454 is formed between adjacent protruding teeth 452 for the ratchet teeth 451 to be embedded in and abut against the protruding teeth 452. Figure 11 A second step surface 432 is provided on the inner circumferential wall of the rotating member 430, which is located at the front end of the protruding tooth 452 and behind the first step surface 431. The transmission member 420 rests on the second step surface 432 through the front gasket 481, and the flange 411 on the moving member 410 is located in front of the front gasket 481.

[0083] Combine Figure 13The second spring 4531 in a compressed state pushes the ratchet 451 against the convex tooth 452. When the transmission member 420 rotates forward along the direction indicated by α, the ratchet 451 is resisted by the convex tooth 452, overcoming the pre-tightening force of the second spring 4531 and swinging toward the center of the transmission member 420. The ratchet 451 slips relative to the convex tooth 452. At this time, the clutch structure 450 is in a free state, and the transmission member 420 cannot drive the rotating member 430 to rotate synchronously through the free clutch structure 450, thereby unable to drive the claw 110 of the pipe expansion mold 100 to rotate, so that the claw 110 does not rotate when the expanded pipe is opened. When the transmission member 420 rotates in the opposite direction along the direction indicated by -α, the ratchet 451 is embedded in the tooth groove 454 under the preload force of the second spring 4531 and abuts against a certain convex tooth 452. At this time, the clutch structure 450 is in an abutting state. The transmission member 420 rotating in the opposite direction can drive the transmission member 420 to rotate synchronously through the clutch structure 450 in the abutting state. The transmission member 420 drives the claw 110 released by the ejector pin 200 to rotate, so that the claw 110 can rotate intermittently.

[0084] To ensure the structural stability of the ratchet 451, a rear washer 482 is provided behind the transmission member 420. The front end of the return spring 700 abuts against the rear washer 482 to achieve positioning. Simultaneously, the rear washer 482 remains stable in its forward and backward motion under the elastic force of the return spring 700, with the ratchet 451 located between the rear washer and the transmission member 420. To prevent the rear washer 482 from pressing against the ratchet 451 and interfering with its swinging motion, and to reduce the rotational interference of the rear washer 482 with the transmission member 420, the thickness of the boss 422 protruding rearward from the transmission member 420 is slightly greater than the thickness of the ratchet 451. Under the elastic force of the return spring 700, the rear washer 482 only contacts the boss 422, thereby reducing the contact area between the rear washer 482 and the transmission member 420 and preventing the rear washer 482 from contacting the ratchet 451.

[0085] As a preferred solution of this embodiment, two groups of linkage structures 440 and two groups of clutch structures 450 are each provided, and the two groups of linkage structures 440 and the two groups of clutch structures 450 are evenly spaced and staggered along the circumference. Of course, the linkage structures 440 and the clutch structures 450 can also be provided as one group, three groups, or other reasonable numbers.

[0086] Combine Figure 4 、 Figure 12An engaging structure 490 is provided between the front end of the rotating member 430 and the rear end of the clamping jaws 110. The rotating rotating member 430 drives the clamping jaws 110 to rotate via the engaging structure 490. Specifically, a plurality of first protrusions 433 spaced circumferentially are provided on the front end surface of the rotating member 430, and a plurality of second protrusions 112 spaced circumferentially are provided on the annular rear end surface formed by the combination of the clamping jaws 110. When the tube expansion die 100 is installed on the front end of the tube expansion machine, the first protrusions 433 and the second protrusions 112 are embedded in and engaged with each other to form the engaging structure 490. The rotating member 430, which is driven to rotate by the transmission member 420 via the clutch structure 450, drives the clamping jaws 110 to rotate synchronously via the engaging structure 490.

[0087] Combine Figure 2 、 Figure 3 The tube expander also includes a front cover 810 and a rear cover 820 for mounting the ejector pin 200 and the rotating assembly 400. The front cover 810 is fixed within the housing 600, with its front end extending forward from the housing 600. The front cover 810 is sleeved over the outer periphery of the front portion of the rotating member 430, with a certain gap between the front cover 810 and the rotating member 430 to prevent the front cover 810 from interfering with the rotation of the rotating member 430. The outer peripheral wall of the front end of the front cover 810 is provided with an external thread, and the inner peripheral wall of the annular seat 120 in the tube expansion mold 100 is provided with an internal thread. The annular seat 120 is detachably fixedly connected to the front end of the front cover 810 through the cooperation of the internal and external threads. The jaws 110 are opened by the ejector pin 200 and can be rotated by the rotating member 430. A rear cover 820 is fixed to the rear end of the housing 600 and fits over the rear end of the ejector pin 200. A certain gap exists between the rear cover 820 and the rear end of the ejector pin 200 to prevent the rear cover 820 from interfering with the forward and backward movement of the ejector pin 200. To ensure the stability of the ejector pin 200's movement, a slide groove 821 extending in the forward and backward direction is provided on the rear cover 820. The two ends of the pin 240 protrude from the lug 213 and are inserted into the slide groove 821. The cooperation between the pin 240 and the slide groove 821 circumferentially restrains the ejector pin 200, preventing it from rotating circumferentially during its forward and backward movement. This, in turn, prevents the ejector pin 200 from rotating circumferentially when the movable member 410 is driven forward and backward by the linkage structure 440.

[0088] Combine Figure 16 、 Figure 17When the pipe needs to be expanded, the pipe expansion die 100 of appropriate size is selected according to the inner diameter of the pipe and installed at the front end of the pipe expansion machine by cooperating with the front seat sleeve 810. When the pipe expander is working, the motor 310 drives the ejector pin 200 through the rotating shaft 510 and the cam 520 to overcome the preload force of the return spring 700 and move forward. The forward-moving ejector pin 200 causes the claws 110 to open outward through the cone head 220 and compress the return spring 700. The opened claws 110 force the ends of the pipe fittings to open. At the same time, the forward-moving ejector pin 200 drives the moving part 410 to overcome the preload force of the first spring 471 and move forward. The forward-moving moving part 410 drives the transmission part 420 to rotate forward through the linkage structure 440 and compresses the first spring 471. At this time, the clutch structure 450 is in a free state, and the transmission part 420 cannot drive the rotating part 430 to rotate synchronously through the clutch structure 450, so that the claws 110 will not rotate circumferentially during the expansion action. After the ejector 200 moves forward into position, the cam 520 releases the ejector 200, and the return spring 700 that restores the deformation drives the ejector 200 to move backward and reset. The backward moving ejector 200 releases the moving member 410 and each claw 110, and each claw 110 gradually retracts under the action of the gathering spring 130. The first spring 471 that restores the deformation drives the moving member 410 to move backward and reset. The backward moving member 410 drives the transmission member 420 to rotate in the opposite direction through the linkage structure 440. At this time, the clutch structure 450 is in an engaged state, and the reverse rotating transmission member 420 drives the rotating member 430 to rotate synchronously through the engaged clutch structure 450. The rotating member 430 drives the claws 110 to rotate synchronously through the bite structure 490, so that each claw 110 rotates a certain angle relative to the expanded pipe. When the ejector pin 200 moves backward to its proper position, the cam 520 can drive the ejector pin 200 to move forward again to open the claws 110 for tube expansion.

[0089] When the claw 110 is stuck and cannot be driven by the rotating member 430 to rotate smoothly, the rotating member 430 and the transmission member 420 cannot rotate circumferentially when the ejector 200 moves backward. In this case, the moving member 410 driven by the first spring 471 to move backward cannot rotate smoothly through the linkage structure 440. The moving member 410 encounters resistance and cannot move backward smoothly for restoration. Since the limiting groove 461 is a straight groove extending in the front-to-back direction, the ejector 200 can still move backward smoothly for restoration under the drive of the reset spring 700.

[0090] In this embodiment, since the rotation of the rotating part 430 is driven by the movable part 410 moving back and forth through the transmission part 420, the rotational power of the rotating part 430 does not directly come from the motor 310, so when the rotating part 430 is blocked, it will not cause the load of the motor 310 to increase, which is beneficial to ensuring the service life of the motor 310.

[0091] In addition to the above preferred embodiments, the present invention has other implementation methods. Those skilled in the art can make various changes and modifications based on the present invention. As long as they do not depart from the spirit of the present invention, they should all fall within the scope defined in the claims of the present invention.

Claims

1. A pipe expanding machine comprising: The tube expansion die includes a plurality of circumferentially distributed and retractable claws; The ejector pin moves forward and applies force to the jaws to open them, while the ejector pin moves backward and releases the jaws to close them. The motor drives the ejector to move forward and backward through the transmission structure; The pipe expander is characterized in that the pipe expander further comprises a dial assembly for driving the jaws to intermittently rotate, the dial assembly comprising a moving part capable of moving forward and backward, a transmission part capable of rotating forward and reversely, and a rotating part driven to rotate by the reversely rotating transmission part; A linkage structure is provided between the moving part and the transmission part. The linkage structure converts the forward and backward linear motion of the moving part into the circumferential rotational motion of the transmission part. The moving part driven forward by the ejector pin drives the transmission part to rotate forward through the linkage structure. The moving part released by the ejector pin and moving backward drives the transmission part to rotate in the opposite direction through the linkage structure. A clutch structure is provided between the transmission member and the rotating member. The clutch structure has an engaged state and a free state. The transmission member rotating in the forward direction rotates independently relative to the rotating member through the clutch structure in the free state. The transmission member rotating in the reverse direction drives the rotating member to rotate through the clutch structure in the engaged state. The rotating rotating member drives the claws of the pipe expansion mold to rotate.

2. A pipe expanding machine according to claim 1, characterized in that: The transmission member is rotatably sleeved on the outside of the moving member, and the linkage structure is arranged between the outer periphery of the moving member and the inner periphery of the transmission member.

3. The pipe expanding machine according to claim 2, characterized in that: The linkage structure includes a linkage groove provided at one of the outer periphery of the moving part and the inner periphery of the transmission part, and a linkage part provided at the other part. The linkage groove is provided along the front-to-back direction and is at least partially inclined or curved relative to the front-to-back direction. A part of the linkage part is inserted into the linkage groove, and the moving part moving forward and backward drives the transmission part to rotate through the cooperation between the linkage groove and the linkage part.

4. The pipe expanding machine according to claim 2, characterized in that: The ejector pin includes an ejector rod and a cone head. The ejector rod includes a rod body extending forward and backward. The cone head is connected to the front end of the rod body. The outer diameter of the rod body is smaller than that of the cone head. The moving part is sleeved on the outer periphery of the rod body.

5. The pipe expanding machine according to claim 1, characterized in that: The moving part is sleeved on the outside of the ejector and is driven by the ejector to move forward. The rotating assembly also includes a first elastic part with one end positioned and the other end in contact with the moving part. The first elastic part is configured to be deformed by force when the moving part is driven by the ejector to move forward, and to drive the moving part to move backward when the ejector moves backward.

6. The pipe expanding machine according to claim 5, characterized in that: One of the inner peripheral wall of the moving part and the outer peripheral wall of the ejector pin is provided with a limiting groove extending forward and backward, and the other is provided with a limiting part inserted into the limiting groove. The limiting part cooperates with the limiting groove to keep the moving part moving linearly.

7. The pipe expanding machine according to claim 1, characterized in that: The rotating member can be rotatably sleeved on the outside of the transmission member, and the clutch structure includes a ratchet that can be rotatably arranged on the transmission member and a circle of convex teeth arranged on the inner circumferential wall of the rotating member. The transmission member rotating in the forward direction causes the ratchet to be resisted by the convex teeth and swing toward the center of the transmission member so that the ratchet and the convex teeth are in a free state. The transmission member rotating in the reverse direction causes the ratchet and the convex teeth to abut against each other so that the ratchet and the convex teeth are in an abutting state.

8. The pipe expanding machine according to claim 7, characterized in that: The clutch structure further comprises a second elastic member with one end positioned and the other end in contact with the ratchet, and the second elastic member biases the ratchet toward the convex tooth.

9. The pipe expanding machine according to claim 8, characterized in that: The transmission member is provided with a fixed boss, and a positioning groove is provided on the side of the boss facing the ratchet, and one end of the second elastic member extends into the positioning groove and contacts the boss; and / or, the ratchet is provided with a boss protruding outward, and the other end of the second elastic member is sleeved on the boss and contacts the ratchet.

10. The pipe expanding machine according to claim 1, characterized in that: The tube expansion mold also includes an annular seat, the rear end of each claw is connected to the annular seat, and an engaging structure is provided between the front end of the rotating member and the rear end of the claw. The rotating rotating member drives the claw to rotate through the engaging structure.

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