A gantry machining center head lifting mechanism

Abstract

This invention discloses a lifting mechanism for a gantry machining center, relating to the field of machining technology. It includes a saddle and a lifting ram slidably connected to the saddle, as well as a pair of connecting seats fixed to the outside of the saddle. Symmetrically fixed guide rails adapted to the connecting seats are mounted on the lifting ram. An anti-deviation mechanism is rotatably mounted on the connecting seats. The guide rails have limiting grooves through which the anti-deviation mechanism passes. A transmission rack meshing with the anti-deviation mechanism is symmetrically fixed to one side of the guide rail. A support mechanism is elastically slidably mounted on the saddle. Rotary lifting components, which respectively engage with the guide rails and the support mechanism, are rotatably mounted on the top of the connecting seats. This invention utilizes the continuous engagement between the transmission rack on the lifting ram and the anti-deviation mechanism mounted on the connecting seats to directly convert the eccentric torque into the rotational motion of the anti-deviation mechanism during ram lifting, thus counteracting lateral forces in real time and preventing excessive ram tilting.

Description

Technical Field

[0001] This invention relates to the field of machining technology, specifically to a head lifting mechanism for a gantry machining center. Background Technology

[0002] Gantry machining centers are high-performance, high-efficiency large CNC machine tools. They are designed specifically for machining large, heavy, complex three-dimensional curved surface parts that require high rigidity and high precision using a gantry frame structure. With their huge workspace, superior structural rigidity, and powerful cutting capabilities, they play an irreplaceable core role in heavy industries such as aerospace, energy, and mold manufacturing. They are key equipment for achieving efficient and high-precision manufacturing of large parts.

[0003] The existing patent application, with publication number CN110936210A and publication date of March 31, 2020, is titled "A Head Lifting Mechanism for a Gantry Machining Center." This patent includes a fixed connecting plate, with lifting adjustment mechanisms installed on both sides of the front wall of the fixed connecting plate. The adjusting blocks of the two lifting adjustment mechanisms are fixed to the lifting spindle housing. The lifting spindle housing is positioned between the two lifting adjustment mechanisms. An outer cover is fixed to the fixed connecting plate, with its front wall panel positioned in front of the fixed connecting plate. Two guide connecting plates are fixed to the lower rear wall of the front wall panel of the outer cover, and the lifting spindle housing is positioned between the two guide connecting plates. This invention provides auxiliary guidance for the lifting of the lifting spindle housing by setting two guide connecting plates on the outer cover, ensuring its lifting stability. Furthermore, the lifting of the lifting spindle housing is achieved through two lifting adjustment mechanisms, resulting in uniform force distribution, stable lifting, and good performance.

[0004] The aforementioned applications have shortcomings. When the ram of the fixed machine head is raised or lowered under heavy load or asymmetrical force, it is prone to lateral displacement or torsional deformation, which leads to accelerated wear of the guide rail, block jamming or even seizing, affecting positioning accuracy and equipment life. At the same time, when the ram changes from descending to ascending or brakes rapidly, due to the large structural inertia, the contact surface between the saddle and the ram is prone to instantaneous impact, which causes vibration and is transmitted to the workpiece surface, resulting in vibration marks or dimensional deviations on the machined surface. Existing guide rails mostly rely on local support from the slider. After long-term heavy load operation, the guide rails are prone to wear and sinking, lacking a dynamic compensation mechanism, which leads to an increase in the gap between the ram and the guide rail, and a significant decrease in repeatability positioning accuracy. Currently, the anti-deviation mechanism and support structure are mostly designed independently and cannot coordinate with each other according to load changes during the lifting and lowering operation. Moreover, there is no adaptive locking mechanism under abnormal working conditions, which poses a safety hazard. Summary of the Invention

[0005] The purpose of this invention is to provide a lifting mechanism for the machine head of a gantry machining center to overcome the shortcomings of the prior art.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] A lifting mechanism for a gantry machining center includes a saddle and a lifting ram slidably connected to the saddle, as well as a pair of connecting seats fixed to the outside of the saddle. A guide rail adapted to the connecting seats is symmetrically fixedly connected to the lifting ram. An anti-deviation mechanism is rotatably mounted on the connecting seats. A limiting groove is provided through the guide rail for the anti-deviation mechanism to pass through. A transmission rack meshing with the anti-deviation mechanism is symmetrically fixedly connected to one side of the guide rail. A support mechanism is elastically slidably mounted on the saddle. Rotary lifting members, which respectively engage with the guide rail and the support mechanism, are rotatably mounted on the top of the connecting seats. When the lifting ram changes from lowering to raising, the anti-deviation mechanism drives the support mechanism to move downwards and allows the rotary lifting members to lift the guide rail. When the lifting ram descends, the anti-deviation mechanism drives the support mechanism to move upwards and locks the rotary lifting members when their rotational speed exceeds a threshold.

[0008] Preferably, a drive motor is fixedly connected to the top of the lifting ram, a transmission screw is installed on the output shaft of the drive motor, and a nut seat is fixedly connected to the outer side of the saddle between the two connecting seats, with the transmission screw threaded through the nut seat.

[0009] Preferably, the anti-deviation mechanism includes a connecting shaft that passes through the connecting seat, and both ends of the connecting shaft are fixedly connected to driven gears, which mesh with a transmission rack.

[0010] Preferably, the support mechanism includes a connecting frame that is elastically slidably connected to the saddle, a driven rack that meshes with the driven gear is fixedly connected to the bottom of the connecting frame, and toothed plates that are symmetrically fixedly connected to the connecting frame and are drivingly connected to the rotating lifting member.

[0011] Preferably, the rotating lifting component includes a lifting tooth column rotatably mounted on the top of the connecting seat, and an anti-disengagement toothed strip is fixedly embedded on the guide rail and meshes with one side of the lifting tooth column, while the other side of the lifting tooth column meshes with a toothed plate.

[0012] Preferably, the bottom of the toothed plate is fixedly connected to an abutment frame below the lifting tooth column, and centrifugal check components that cooperate with the abutment frame are installed on both sides of the lifting tooth column. When the rotation speed of the lifting tooth column exceeds the threshold, the abutment frame and the centrifugal check component engage with each other, forcing the lifting tooth column to stop rotating.

[0013] Preferably, the centrifugal check valve assembly includes a connecting ring fixed to one side of the lifting tooth column. The outer circumferential surface of the connecting ring has a plurality of grooves distributed in a ring. A pawl is elastically hinged in the groove. When the rotational speed of the lifting tooth column exceeds a threshold, the pawl flips outward under the action of centrifugal force, so that the abutment frame abuts against the pawl.

[0014] Preferably, a detection slider is vertically slidably installed inside the connecting seat. The detection slider is located in the limiting groove, and connecting rods are hinged to both sides of the detection slider at the eccentric points of the two driven gears on the connecting shaft.

[0015] Preferably, the detection slider has an air cavity inside, the connecting seat has a piston plate fixedly connected in the air cavity, and both sides of the detection slider have a number of heat dissipation grooves that communicate with the air cavity.

[0016] Preferably, air guide plates are installed on the outer sides of both connecting seats, and the top of the nut seat is located between the two air guide plates.

[0017] In the above technical solution, the transmission rack on the lifting ram continuously meshes with the anti-deviation mechanism installed through the connecting seat. During the lifting ram's movement, the eccentric torque is directly converted into the rotational motion of the anti-deviation mechanism, instantly offsetting the lateral force and preventing excessive tilting of the lifting ram. When the lifting ram changes from lowering to raising, the anti-deviation mechanism rotates to drive the support mechanism downwards, allowing the support mechanism to drive the rotating lifting component to abut and lift the guide rail, instantly filling the gap and bearing the load, avoiding impact vibration and reducing the lifting burden on the ram. When the ram descends, the anti-deviation mechanism reverses the drive of the support mechanism. When the mechanism moves upward and is detached from the load, if the ram falls due to stall and causes the rotating support component to rotate at an excessive speed, the support mechanism will immediately lock the rotating support component to prevent guide rail dislocation accidents. As a power transmission hub, it simultaneously receives the bidirectional force from the guide rail and the support mechanism, ensuring that the supporting force and anti-deviation force are applied synchronously to the load point of the guide rail. The limiting groove opened on the guide rail constrains the movement trajectory of the anti-deviation mechanism, making it always perpendicular to the guide rail plane, improving the anti-deviation load stiffness. The overspeed automatic locking mechanism prevents the ram from stalling and falling, avoiding equipment damage and personnel injury, and meets the safety standards for heavy equipment.

[0018] It should be understood that the foregoing general description and the following detailed description are exemplary and illustrative only, and are not intended to limit this disclosure.

[0019] This application provides an overview of various implementations or examples of the technology described in this disclosure, and is not a full disclosure of the entire scope or all features of the disclosed technology. Attached Figure Description

[0020] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in this invention. For those skilled in the art, other drawings can be obtained based on these drawings.

[0021] Figure 1 This is a schematic diagram of the overall structure of the head lifting mechanism of a gantry machining center according to the present invention;

[0022] Figure 2 This is a schematic diagram of the overall structure of the head lifting mechanism of a gantry machining center according to the present invention;

[0023] Figure 3 This is a schematic diagram of the saddle and support mechanism in the head lifting mechanism of a gantry machining center according to the present invention;

[0024] Figure 4 This is a schematic diagram of the lifting slide in the lifting mechanism of the gantry machining center according to the present invention;

[0025] Figure 5 This is a schematic diagram of the support mechanism in the head lifting mechanism of a gantry machining center according to the present invention;

[0026] Figure 6 This is a schematic diagram of the connecting seat in the lifting mechanism of the head of a gantry machining center according to the present invention;

[0027] Figure 7 This is a transmission schematic diagram of the detection slider and anti-deviation mechanism in the head lifting mechanism of a gantry machining center according to the present invention;

[0028] Figure 8 This is a schematic diagram of the rotating support component and the centrifugal check component in the lifting mechanism of the head of a gantry machining center according to the present invention.

[0029] Explanation of reference numerals in the attached figures:

[0030] 1. Saddle; 101. Nut seat; 2. Lifting slide; 201. Drive motor; 202. Transmission screw; 3. Connecting seat; 4. Guide rail; 401. Limiting groove; 402. Transmission rack; 403. Anti-detachment rack; 5. Anti-deviation mechanism; 501. Connecting shaft; 502. Driven gear; 6. Support mechanism; 601. Connecting frame; 602. Driven rack; 603. Gear plate; 604. Abutment frame; 605. Connecting slider; 606. Top spring; 7. Rotating lifting component; 701. Lifting tooth column; 702. Fixed seat; 8. Centrifugal check valve assembly; 801. Connecting ring; 802. Groove; 803. Paw; 804. Torsion spring; 9. Detection slider; 901. Connecting rod; 902. Air chamber; 903. Piston plate; 904. Heat dissipation groove; 10. Air guide plate. Detailed Implementation

[0031] To make the objectives, technical solutions, and advantages of the embodiments of this disclosure clearer, the technical solutions of the embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this disclosure. All other embodiments obtained by those skilled in the art based on the described embodiments of this disclosure without creative effort are within the scope of protection of this disclosure.

[0032] Please see Figure 1-8 This invention provides a gantry machining center head lifting mechanism, including a saddle 1 and a lifting slide 2 slidably connected to the saddle 1, and a pair of connecting seats 3 fixed to the outside of the saddle 1. A guide rail 4 adapted to the connecting seats 3 is symmetrically fixedly connected to the lifting slide 2. An anti-deviation mechanism 5 is rotatably mounted on the connecting seats 3. The guide rail 4 has a limiting groove 401 through which the anti-deviation mechanism 5 passes. A transmission rack 402 meshing with the anti-deviation mechanism 5 is symmetrically fixedly connected to one side of the guide rail 4. A support mechanism 6 is elastically slidably mounted on the saddle 1. A rotating lifting member 7, which is respectively driven and cooperates with the guide rail 4 and the support mechanism 6, is rotatably mounted on the top of the connecting seats 3. When the lifting slide 2 changes from lowering to raising, the anti-deviation mechanism 5 drives the support mechanism 6 to move down and allows the rotating lifting member 7 to lift the guide rail 4. When the lifting slide 2 descends, the anti-deviation mechanism 5 drives the support mechanism 6 to move up and locks the rotating lifting member 7 when its rotational speed exceeds a threshold.

[0033] Specifically, the lifting ram 2 is equipped with a machine head, and the saddle 1 serves as the connecting component between the gantry and the lifting ram 2. When the lifting ram 2 transitions from the descending state to the ascending state, as the lifting ram 2 rises, the anti-deviation mechanism 5 is driven counterclockwise by the transmission rack 402 on the guide rail 4 to rotate, thereby pushing the support mechanism 6 to move vertically downward on the saddle 1. This causes the rotating lifting component 7 to adjust and tighten against the guide rail 4 in real time, eliminating the gap between the guide rail 4 and the saddle 1, forming a rigid support, and allowing the rotating lifting component 7 to further engage and press against the guide rail 4. The anti-deviation mechanism 5 counteracts the lateral load moment in real time, improving the bending stiffness of the ram. The rotating lifting component 7 bears the load in advance, avoiding the impact vibration of the lifting ram 2 during the instant of rising when the motor starts, and reducing the load on the lifting system. During the descending phase of the lifting ram 2, the anti-deviation mechanism 5 is again driven clockwise by the transmission rack 402, driving the support mechanism 6 in the opposite direction. The system moves the support mechanism 6 and the rotating support component 7 to a certain height so that they can cooperate to release the support and reduce frictional resistance, allowing the lifting ram 2 to descend smoothly with the machine head. At the same time, if the lifting ram stalls and falls due to transmission failure, the transmission rack 402 will drive the rotating support component 7 and the anti-deviation mechanism 5 to rotate beyond the threshold speed. At this time, the support mechanism 6 limits and locks the high-speed rotating support component 7, forcing it to stop and keeping it in contact with the transmission rack 402, forming a mechanical lock to prevent the guide rail 4 from continuing to move downward, thus achieving dynamic locking and preventing the lifting ram 2 from derailing. No additional sensors are required, avoiding damage to the workpiece when the machine head falls at high speed. The system achieves triple protection of active anti-deviation, intelligent support, and fault self-locking through a purely mechanical structure, which is especially suitable for high-precision and high-safety lifting scenarios in heavy-duty gantry machining centers.

[0034] Compared with the prior art, the embodiment of the present invention continuously engages the transmission rack 402 on the lifting slide 2 with the anti-deviation mechanism 5 installed through the connecting seat 3. When the slide is raised or lowered, the eccentric torque is directly converted into the rotational motion of the anti-deviation mechanism 5, which cancels the lateral force in real time and prevents the slide from tilting excessively. When the slide changes from lowering to raising, the anti-deviation mechanism 5 rotates to drive the support mechanism 6 to move down, so that the support mechanism 6 drives the rotating lifting member 7 to abut and lift the guide rail 4, instantly filling the gap and bearing the load, avoiding impact vibration, and reducing the lifting burden of the lifting slide 2. When the slide is lowered, the anti-deviation mechanism 5 reverses the drive of the support mechanism 6. When mechanism 6 moves upward and is detached from the load, if the ram falls due to stall and causes the rotating support 7 to rotate at overspeed, the support mechanism 6 will immediately lock the rotating support 7 to prevent the guide rail 4 from dislodging. As a power transmission hub, it also receives the bidirectional force from the guide rail 4 and the support mechanism 6, ensuring that the supporting force and the anti-deviation force are applied synchronously to the load point of the guide rail 4. The limiting groove 401 opened on the guide rail 4 constrains the movement trajectory of the anti-deviation mechanism 5, making it always perpendicular to the plane of the guide rail 4, improving the anti-deviation load stiffness. The overspeed automatic locking mechanism prevents the ram from stalling and falling, avoiding equipment damage and personnel injury, and meets the safety standards for heavy equipment.

[0035] In a further embodiment of the present invention, a drive motor 201 is fixedly connected to the top of the lifting ram 2, and a transmission screw 202 is mounted on the output shaft of the drive motor 201. A nut seat 101 is fixedly connected to the outer side of the saddle 1 between two connecting seats 3. The transmission screw 202 is threaded through the nut seat 101. Specifically, the drive motor 201 is mounted on the top of the lifting ram 2, and the output shaft is connected to the transmission screw 202 through an interference fit. When the drive motor 201 is energized, it rotates clockwise, and the transmission screw 202 pushes the nut seat 101 to move upward relative to the saddle. The lifting ram 2 moves upward synchronously with the guide rail 4. The transmission rack 402 on the rail 4 drives the anti-deviation mechanism 5 to rotate counterclockwise. The anti-deviation mechanism 5 causes the support mechanism 6 to move down and triggers the rotating lifting component 7 to press against the guide rail 4 during the transition phase from descent to ascent. When the motor reverses and drives the lead screw to rotate counterclockwise, the lifting ram 2 moves down under the push of the transmission lead screw 202 and the gravity of the machine head. The transmission rack 402 drives the anti-deviation mechanism 5 to rotate clockwise, causing the support mechanism 6 to move up, so that the support mechanism 6 can reach the anti-return engagement position with the rotating lifting component 7. Even if the lead screw lifting system fails, the pure mechanical locking can still prevent the lifting ram 2 from falling continuously.

[0036] In a further embodiment of the present invention, the anti-deviation mechanism 5 includes a connecting shaft 501 that passes through the connecting seat 3. Both ends of the connecting shaft 501 are fixedly connected to driven gears 502. The driven gears 502 mesh with the transmission rack 402. Specifically, when the lifting slide 2 is raised and lowered under the drive of the transmission screw, if the lifting slide 2 deviates and fails to move vertically, its eccentric torque will be transmitted to the guide rail 4. The transmission rack 402 will press the driven gear 502 on one side, and the pressed driven gear 502 will drive the connecting shaft 501 to rotate. The shaft will drive the driven gear 502 on the other side to rotate in the opposite direction. The gear on the other side will apply a reverse thrust to the corresponding transmission rack 402. The reverse forces of the transmission racks 402 on both sides will form a couple, forcing the slide to return to a vertical posture and improving the bending stiffness of the system. At the same time, the forward and reverse rotation of the driven gears 502 will drive the support mechanism 6 to move up and down, so as to support the rotating lifting member 7 or prevent it from falling.

[0037] In a further embodiment of the present invention, the support mechanism 6 includes a connecting frame 601 elastically slidably connected to the saddle 1. A connecting slider 605 is fixedly connected to the back of the connecting frame 601. A guide groove matching the slider is vertically provided on the saddle 1. Top springs 606 are fixedly connected to the top and bottom of the connecting slider 605 in the guide groove. A driven rack 602 meshing with the driven gear 502 is fixedly connected to the bottom of the connecting frame 601. A toothed plate 603 symmetrically fixedly connected to the connecting frame 601 and drivingly connected to the rotating lifting member 7 is also fixedly connected. Specifically, the top spring 606 and the compression spring form a bidirectional elastic constraint on the connecting frame 601. When the lifting bolster 2 changes from descending to ascending, the driven gear 502 of the anti-deviation mechanism 5 starts to rotate counterclockwise, driving the driven rack 602 to move the connecting frame 601 downward, so that the connecting frame 601 compresses the bottom top spring 606. 06 Energy storage: The top spring 606 extends synchronously to release the pre-pressure. The toothed plate 603 on the connecting frame 601 then drives the rotating support 7 to press against the guide rail 4, which moves upward in real time. This allows the rotating support 7 to assist in lifting the lifting ram 2, reducing the force on the transmission screw 202. As the lifting ram 2 continues to rise, the driven rack 602 is completely below the driven gear 502. At this time, the driven gear 502 will not drag the connecting frame 601 down continuously, allowing the lifting ram 2 to operate normally during the continuous rising phase. During the falling phase of the lifting ram 2, the guide rail 4 drives the driven gear 502 to rotate clockwise, and the compression spring extends to provide upward assistance. The driven rack 602 pulls the connecting frame 601 upward, causing the toothed plate 603 to disengage from the rotating support 7, reducing the frictional resistance of the guide rail 4 and reducing the power consumption of the drive motor 201.

[0038] In a further embodiment of the present invention, the rotating lifting member 7 includes a lifting toothed column 701 rotatably mounted on the top of the connecting seat 3. The lifting toothed column 701 is fixedly mounted on the top of the connecting seat 3 via a fixing seat 702. An anti-disengagement toothed strip 403 that meshes with one side of the lifting toothed column 701 is fixedly embedded on the guide rail 4. The other side of the lifting toothed column 701 meshes with a toothed plate 603. Specifically, the lifting slide 2 moves upward to lower the support mechanism 6. During the downward movement of the support mechanism 6, the toothed plate 603 pushes the lifting toothed column 701 to rotate counterclockwise, allowing the lifting toothed column 701 to rotate counterclockwise. The teeth of the lifting pinion 701 are embedded in the root of the anti-detachment rack 403, making hard contact and pressing against the guide rail 4. The anti-detachment rack 403 transmits the vertical load of the lifting ram 2 to the connecting seat 3, eliminating the screw drive backlash, bearing part of the weight of the lifting ram 2 and the machine head, and extending the service life of the drive motor 201 and the transmission screw 202. The lifting pinion 701 and the anti-detachment rack 403 mesh when the lifting ram 2 changes from the lowering state to the raising state, reducing the vibration generated during the switching process and ensuring the stability of the machine head during its initial rising stage.

[0039] In a further embodiment of the present invention, a contact frame 604 is fixedly connected to the bottom of the toothed plate 603 below the lifting toothed column 701. Centrifugal check valve components 8 that cooperate with the contact frame 604 are installed on both sides of the lifting toothed column 701. When the rotational speed of the lifting toothed column 701 exceeds a threshold, the contact frame 604 and the centrifugal check valve components 8 engage with each other, forcing the lifting toothed column 701 to stop rotating. Specifically, during the descent of the lifting slide 2, the connecting frame 601 will move upward, thereby allowing the contact frame 604 to reach a position where it can contact the toothed column 701. The height at which the centrifugal check assembly 8 is engaged is determined by the meshing of the lifting pinion 701 and the transmission rack 402 on the guide rail 4. When the lifting ram 2 falls rapidly, the transmission rack 402 drives the lifting pinion 701 to rotate at high speed. At this time, the centrifugal check assembly 8 unfolds under the action of centrifugal force. Then, the lifting pinion 701 is prevented from continuing to rotate by the limiting of the centrifugal check assembly 8 by the abutment frame 604, thereby preventing the lifting ram 2 from falling further and avoiding damage to the workpiece caused by the falling of the machine head.

[0040] In a further embodiment of the present invention, the centrifugal check valve assembly 8 includes a connecting ring 801 fixed to one side of the lifting gear column 701. A plurality of grooves 802 are circumferentially distributed on the outer circumferential surface of the connecting ring 801. A pawl 803 is elastically hinged within each groove 802. A torsion spring 804 is installed between the pawl 803 and the groove 802. When the rotational speed of the lifting gear column 701 exceeds a threshold, the pawl 803 flips outward under centrifugal force, causing the abutment frame 604 to abut against the pawl 803. Specifically, under normal operating conditions, the transmission rack 402 on the guide rail 4 drives the lifting gear column 701 to rotate normally. The preload of the torsion spring 804 is greater than the centrifugal force, and the pawl 803 is tightly pressed against the inner wall of the groove 802. With the claw tip retracted, even if the abutment frame 604 is in a position to cooperate with the centrifugal check component 8, the two have zero contact, and the lifting slide 2 can move freely. When the lifting slide 2 falls rapidly, the transmission rack 402 drives the lifting pinion 701 to rotate at high speed. The centrifugal force of the pawl 803 is greater than the preload of the torsion spring 804. The pawl 803 rotates outward around the pin axis, and the claw tip protrudes from the connecting ring 801. At this time, the abutment frame 604 will collide with the claw tip of the pawl 803. The support mechanism 6 restricts the rotation of the lifting pinion 701. The lifting pinion 701 bites the transmission rack 402 in the opposite direction to prevent the guide rail 4 from falling continuously and avoid the lifting slide 2 from falling accidentally with the machine head.

[0041] In a further embodiment of the present invention, a detection slider 9 is vertically slidably installed inside the connecting seat 3. The detection slider 9 is located within the limiting groove 401, and connecting rods 901 are hinged to the two eccentric points of the two driven gears 502 on the connecting shaft 501 on both sides of the detection slider 9. Specifically, when the lifting slide 2 does not deviate from the limiting groove 401 and is not twisted, the lifting movement of the slide 2 drives the driven gears 502 to rotate. The driven gears 502 then pull the detection slider 9 along the limiting groove 401 through the connecting rods 901. If the lifting slide 2 deviates or the limiting slide 401 deforms, the groove wall of the limiting slide 401 will squeeze the detection slider 9, causing the movement resistance of the detection slider 9 to increase sharply. The obstructed slider will forcibly brake the driven gear 502 through the connecting rod 901, thereby using the meshing of the driven gear 502 and the transmission rack 402 to instantly lock the guide rail 4. The drive motor 201 will stop in time after receiving the torque change, so as to quickly eliminate the hidden dangers in subsequent operation and ensure that the core components are not greatly damaged.

[0042] In a further embodiment of the present invention, an air cavity 902 is provided inside the detection slider 9, and a piston plate 903 located in the air cavity 902 is fixedly connected inside the connecting seat 3. Several heat dissipation grooves 904 connected to the air cavity 902 are vertically provided on both sides of the detection slider 9. Specifically, during the normal lifting and lowering process of the lifting slide 2, the driven gear 502 drives the detection slider 9 to move up and down along the limiting slide groove 401 through the connecting rod 901. The piston plate 903 squeezes out the gas in the air cavity 902 and blows it to the guide rail 4 through the multiple heat dissipation grooves 904, thereby reducing the heat of the guide rail 4 itself, and offsetting thermal deformation in real time, making the connection between the lifting slide 2 and the saddle 1 more stable and reliable.

[0043] In a further embodiment of the present invention, air guide plates 10 are installed on the outer sides of both connecting seats 3, and the top of the nut seat 101 is located between the two air guide plates 10. Specifically, the air guide plates 10 on both sides guide the airflow blown out of the air chamber 902 to the nut seat 101, so that the temperature of the nut seat 101 remains stable under the influence of continuous forced convection. At the same time, it can also blow off the cutting chips on the nut seat 101, so as to avoid the accumulation of chips on the nut seat 101 and affect the transmission accuracy and stability of the transmission screw 202.

[0044] The foregoing has only described certain exemplary embodiments of the present invention by way of illustration. Undoubtedly, those skilled in the art can modify the described embodiments in various ways without departing from the spirit and scope of the present invention. Therefore, the foregoing drawings and descriptions are illustrative in nature and should not be construed as limiting the scope of protection of the claims of the present invention.

Claims

1. A gantry machining center head lifting mechanism, comprising a saddle (1) and a lifting ram (2) in sliding connection with the saddle (1), characterized in that, Also include: A pair of connecting seat (3) is fixed to the outside of the saddle (1), the lifting ram (2) is symmetrically fixed and connected with the connecting seat (3) is matched with the guide rail (4); Anti deviation mechanism (5), rotating through the installation on the connecting seat (3), the guide rail (4) is provided with a limiting sliding slot (401) for the anti deviation mechanism (5) to pass through, the guide rail (4) is symmetrically fixed and connected with the transmission rack (402) engaged with the anti deviation mechanism (5); Supporting mechanism (6), which is elastically slidingly installed on the saddle (1), the connecting seat (3) is rotatably installed on the top of the connecting seat (3), respectively with the guide rail and the supporting mechanism transmission matching rotating lifting piece (7); When the lifting ram (2) is turned from descending to ascending, the anti deviation mechanism (5) drives the supporting mechanism (6) to move down and let the rotating lifting piece (7) lift the guide rail (4), when the lifting ram (2) is lowered, the anti deviation mechanism (5) drives the supporting mechanism (6) to move up and lock the rotating lifting piece (7) when the rotating speed of the rotating lifting piece (7) exceeds the threshold value; The anti deviation mechanism (5) includes a connecting shaft (501) penetrating the connecting seat (3), both ends of the connecting shaft (501) are fixedly connected with the driven gear (502), and the driven gear (502) is engaged with the transmission rack (402); The supporting mechanism (6) includes a connecting frame (601) elastically slidingly connected with the saddle (1), the bottom of the connecting frame (601) is fixedly connected with the driven gear (602) engaged with the driven gear (502), and the connecting frame (601) is symmetrically fixedly connected with the gear plate (603) drivingly connected with the rotating lifting piece (7); The rotating lifting piece (7) includes a lifting tooth column (701) rotatably installed on the top of the connecting seat (3), the guide rail (4) is fixedly embedded with the anti falling rack (403) engaged with one side of the lifting tooth column (701), the other side of the lifting tooth column (701) is engaged with the gear plate (603), the bottom of the gear plate (603) is fixedly connected with the abutting frame (604) below the lifting tooth column (701), and the lifting tooth column (701) is provided with a centrifugal check assembly (8) matched with the abutting frame (604) on both sides, when the rotating speed of the lifting tooth column (701) exceeds the threshold value, the abutting frame (604) and the centrifugal check assembly (8) are clamped with each other, so that the lifting tooth column (701) is forced to stop rotating; The centrifugal check assembly (8) includes a connecting ring (801) fixed to one side of the lifting tooth column (701), a plurality of grooves (802) are annularly distributed on the outer circumferential surface of the connecting ring (801), and the grooves (802) are elastically hinged with the pawl (803), when the rotating speed of the lifting tooth column (701) exceeds the threshold value, the pawl (803) is turned outward under the action of centrifugal force, so that the abutting frame (604) and the pawl (803) are abutted.

2. The gantry machining center head lifting mechanism according to claim 1, characterized in that, The lifting ram (2) top fixedly connected with a drive motor (201), the drive motor (201) output shaft is provided with a transmission screw (202), the saddle (1) outside between two connecting seat (3) fixedly connected with nut seat (101), the transmission screw (202) thread penetrates nut seat (101).

3. The gantry machining center head lifting mechanism according to claim 1, characterized in that, The connecting seat (3) is vertically slidably installed with a detection slider (9), the detection slider (9) is located in the limiting sliding slot (401), and the detection slider (9) is hinged with a connecting rod (901) on both sides of the eccentric point of the two driven gears (502) on the connecting shaft (501).

4. The gantry machining center head lifting mechanism according to claim 3, characterized in that, The detection slider (9) is internally provided with an air cavity (902), the connecting seat (3) is fixedly connected with a piston plate (903) in the air cavity (902), and the detection slider (9) is vertically provided with a plurality of heat dissipation grooves (904) on both sides and in communication with the air cavity (902).

5. The gantry machining center head lifting mechanism according to claim 2, wherein, Both sides of the two connecting seat (3) are provided with a baffle (10), and the nut seat (101) top is between the two baffles (10).

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