Impact-resistant riveting driving structure

Abstract

The invention discloses an anti-impact riveting driving structure. Comprising a riveting working head and a riveting driving mechanism. The working head comprises a cylinder body, a hollow piston shaft and a rear end cover; the cylinder body and the rear end cover form a driven hydraulic cavity for the hollow piston shaft to move; the driving mechanism comprises a motor driving device and a driving oil cylinder driven by the motor driving device; the driving oil cylinder comprises a driving piston shaft and a driving hydraulic cavity formed by the driving piston shaft and a driving oil cylinder body; the motor driving device is a screw rod transmission mechanism and comprises a motor, a speed reducer driven by the motor and a driven screw rod which is driven by the motor and axially telescopically moves; the driven screw drives the driving piston shaft to move to provide driving hydraulic oil for the riveting working head; and the working head and the driving mechanism are axially mounted in a staggered manner. Riveting work is driven by the riveting screw and the driving oil cylinder and the hollow piston shaft which are arranged in a staggered mode, the cross sectional area of the driven hydraulic cavity and the cross sectional area of the driving hydraulic cavity are accurately set, vibration of a riveting work head is effectively reduced, and the service life of the riveting device is prolonged.

Description

Technical Field

[0001] The present invention belongs to the technical field of riveting device design, and relates to a riveting device with strong shock resistance, specifically an impact-resistant riveting drive structure. Background Art

[0002] The electric-hydraulic riveting gun is an efficient and portable riveting tool, which is widely used in various fields requiring riveting operations.

[0003] Chinese application CN115319009A discloses an electric-hydraulic riveting gun. In the electric-hydraulic riveting gun disclosed in this application, the riveting working head and the electric drive unit are in a front-back corresponding relationship, and the riveting working head is directly fixedly connected to the top surface of the hydraulic pump assembly, and the electric drive unit is directly fixedly connected to the back surface of the hydraulic pump assembly. When the riveting working head performs riveting work, vibrations in the front-back direction will be generated, and this vibration is easily transmitted to the hydraulic pump assembly and the electric drive unit, affecting the connection stability and airtightness of the hydraulic pump assembly and the electric drive unit, thereby affecting the overall service life of the riveting gun. Summary of the Invention

[0004] The purpose of the present invention is to provide an impact-resistant riveting drive structure. The present invention uses a riveting screw and a misaligned active oil cylinder and hollow piston shaft to drive the riveting work, effectively reducing the vibration of the riveting working head and improving the overall service life of the riveting device.

[0005] The present invention adopts the following solutions:

[0006] An impact-resistant riveting drive structure, comprising a riveting working head and a riveting drive mechanism; characterized in that:

[0007] The riveting working head includes a cylinder block, a hollow piston shaft and a rear end cover, and the cylinder block and the rear end cover form a driven hydraulic cavity for the hollow piston shaft to move.

[0008] The drive mechanism includes a motor drive device and an active oil cylinder driven by it; the active oil cylinder includes: an active piston shaft, an active hydraulic cavity formed by the active piston shaft and the active oil cylinder block; the motor drive device is a screw drive mechanism, including: a motor, a reducer driven by the motor and a driven screw that axially expands and contracts; one end of the driven screw is drivingly connected to the active piston shaft and drives the active piston shaft to move to provide drive hydraulic oil for the riveting working head.

[0009] The riveting working head is fixedly installed on the drive mechanism through a mounting seat, and the riveting working axis of the riveting working head composed of the cylinder block, the hollow piston shaft and the rear end cover is misaligned and installed axially with the drive mechanism axis.

[0010] Furthermore, the cross-sectional area of the driven hydraulic chamber is larger than that of the active hydraulic chamber. Preferably, the cross-sectional area of the driven hydraulic chamber is 1.12 times that of the active hydraulic chamber.

[0011] Furthermore, the cylinder block is provided with a first oil passage communicating with the front end of the driven hydraulic chamber and a second oil passage communicating with the rear end of the driven hydraulic chamber; the rear end of the cylinder block is connected to a mounting seat, and a first infusion passage communicating with the first oil passage and a second infusion passage communicating with the second oil passage are arranged in the mounting seat. A driving oil cylinder axially misaligned with the riveting working head is connected below the mounting seat, and a first driving oil passage communicating with the first infusion passage and a second driving oil passage communicating with the second infusion passage are arranged inside the driving oil cylinder.

[0012] Furthermore, the motor driving device includes a driving tube, and the driving tube includes a sealing joint. The sealing joint is hermetically connected to the driving oil cylinder and the driving piston shaft passes through the sealing joint. A driven screw is connected to one end of the driving piston shaft facing the driving tube. A driven gear is coaxially threadedly connected to the driven screw. A prism section with a prismatic outer surface is arranged at one end of the driven screw facing the driving piston shaft. A collar is sleeved on the prism section, and anti-rotation force arms extending along the radial direction of the collar are arranged on opposite sides of the collar. An activity groove extending along the axial direction of the driving tube is arranged on the side wall of the driving tube, and both ends of the anti-rotation force arm are limited and slid in the activity grooves on both sides. The driven gear is meshed with a driving gear, a speed reducer is coaxially connected to the driving gear, and a motor is coaxially connected to the speed reducer.

[0013] Furthermore, the driven screw adopts a ball screw, and position sensors are arranged through the driving tube at the head and tail ends of the activity groove.

[0014] Furthermore, rollers are sleeved on the ends of the anti-rotation force arms, and the rollers are limited and slid in the activity grooves.

[0015] Furthermore, two oil filling ports are arranged on the mounting seat. One of the oil filling ports communicates with the first infusion passage, and the other oil filling port communicates with the second infusion passage. Oil filling plugs are arranged on each oil filling port.

[0016] A buffer mechanism is arranged at the rear end of the riveting working head in the axial direction of the present invention.

[0017] The beneficial effects of the present invention are as follows:

[0018] In the present invention, the riveting working head and the driving mechanism are arranged with a dislocation of the mounting base, and a buffer mechanism can be independently arranged at the rear end of the riveting working head. When the riveting working head works, the vibration in the front-rear direction is transmitted to the mounting base. Since the spatial arrangement of the mounting base and the active oil cylinder of the driving mechanism is set with a dislocation, the active oil cylinder of the driving mechanism and the like are perpendicular to the vibration direction generated by the riveting working head or not on the same axial line. During the process of the mounting base transmitting the vibration to the active oil cylinder, the vibration effect is weakened, reducing the vibration received by the active oil cylinder and the driving device, and prolonging the overall service life of the riveting gun.

[0019] Through the design of the dimensional relationship between the cross-sectional area of the driven hydraulic chamber and the cross-sectional area of the active hydraulic chamber in the present invention, the axial force of the driving device on the active piston shaft can be reduced.

[0020] The present invention further sets a buffer mechanism. After the shock absorption of the buffer structure, the vibration is transmitted to the mounting base, and finally the mounting base transmits the vibration to the active oil cylinder and other driving devices of the driving mechanism, which can further improve the shock absorption effect and protect the riveting device.

[0021] In the present invention, through the setting of a motor, a reducer, a driving gear, a driven gear, a driven screw, a prism section, and a rotation-preventing force arm, with the motor as the power source, after being decelerated by the reducer, the driving gear is driven to drive the driven gear to rotate. Since the driven screw is threadedly connected to the driven gear and a rotation-preventing force arm is arranged on the driven screw, during the process of the driven gear rotating around the axis of the driven screw, the driven screw does not rotate around its own axis and can only make a reciprocating motion along the axis of the driven screw, thereby driving the active piston shaft to make a reciprocating motion along the axis of the driven screw, so that the oil pressure at the front and rear ends in the active hydraulic chamber changes. Description of the Drawings

[0022] Figure 1 It is a three-dimensional structural schematic diagram of the riveting device according to the embodiment of the present invention;

[0023] Figure 2 It is a vertical sectional structural schematic diagram of the riveting device according to the embodiment of the present invention passing through the axis of the driven screw;

[0024] Figure 3 It is a horizontal sectional structural schematic diagram of the riveting device according to the embodiment of the present invention passing through the axis of the transition joint;

[0025] Figure 4 It is a vertical sectional structural schematic diagram of the riveting device according to the embodiment of the present invention passing through the axis of the first oil passage;

[0026] Figure 5 It is a vertical sectional structural schematic diagram of the riveting device according to the embodiment of the present invention passing through the axis of the second oil passage;

[0027] Figure 6 It is a structural schematic diagram of the active oil cylinder housing of the riveting device according to the embodiment of the present invention;

[0028] Figure 7 Schematic diagram of the oil distribution plate structure of the riveting device according to an embodiment of the present invention;

[0029] Figure 8 Schematic diagram of the collar structure of the riveting device according to an embodiment of the present invention;

[0030] Figure 9 Schematic diagram of the transition joint structure of the riveting device according to an embodiment of the present invention.

[0031] Reference numerals: 1, cylinder block; 2, hollow piston shaft; 3, rear end cover; 4, driven hydraulic cavity; 5, first oil circuit; 6, second oil circuit; 7, mounting seat; 8, first liquid delivery circuit; 9, second liquid delivery circuit; 10, active oil cylinder; 11, active piston shaft; 12, active hydraulic cavity; 13, first active oil circuit; 14, second active oil circuit; 15, buffer guide tube; 16, plugging plate; 17, mounting plate; 18, forward buffer ring; 19, reverse buffer ring; 20, annular retaining ring; 21, shaft circlip; 22, annular groove; 23, guide plate; 24, front guide ring; 25, rear guide ring; 26, transition joint; 27, axial oil passage; 28, radial oil passage; 29, sealing groove; 30, oil distribution plate; 31, limiting outer edge; 32, limiting groove; 33, sealing cavity; 34, drive tube; 35, sealing joint; 36, driven screw; 37, driven gear; 38, driving gear; 39, reducer; 40, motor; 41, collar; 42, anti-rotation force arm; 43, roller; 44, movable groove; 45, position sensor; 46, prism segment; 47, receiving groove; 48, plugging groove. Detailed implementation manners

[0032] The present invention will be further described below in conjunction with the detailed implementation manners. The detailed implementation manners are further explanations of the principles of the present invention and do not limit the present invention in any way. The technologies identical or similar to the present invention do not exceed the protection scope of the present invention.

[0033] In the description of the present invention, it should be noted that the orientation or positional relationship indicated by the terms "center", "upper", "lower", "left", "right", "vertical", "longitudinal", "lateral", "horizontal", "inner", "outer", "front", "rear", "top", "bottom", etc. is based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the invention product is usually placed during use. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present invention.

[0034] In the description of the present invention, it should also be noted that, unless otherwise clearly specified and defined, the terms "arranged", "provided with", "installed", "connected", and "coupled" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, and it can be the communication inside two components. For those of ordinary skill in the art, the specific meanings of the above terms in the present invention can be understood according to specific situations.

[0035] The following fully describes the anti-shock riveting device including a driving structure according to an embodiment of the present invention.

[0036] The anti-shock riveting device includes a riveting working head. The riveting working head includes a cylinder block 1, a hollow piston shaft 2, and a rear end cover 3. The cylinder block 1 and the rear end cover 3 form a driven hydraulic chamber 4 for the hollow piston shaft 2 to move. A first oil passage 5 communicating with the front end of the driven hydraulic chamber 4 and a second oil passage 6 communicating with the rear end of the driven hydraulic chamber 4 are arranged inside the cylinder block 1. The rear end of the cylinder block 1 is connected with a mounting seat 7. A first liquid delivery passage 8 communicating with the first oil passage 5 and a second liquid delivery passage 9 communicating with the second oil passage 6 are arranged inside the mounting seat 7. A driving oil cylinder 10 located outside the side of the riveting working head is arranged below the mounting seat 7. The axis of the riveting working head is arranged parallel to the driving oil cylinder 10. A driving piston shaft 11 and a driving hydraulic chamber 12 for the driving piston shaft 11 to move are arranged inside the driving oil cylinder 10. A first driving oil passage 13 communicating with the first liquid delivery passage 8 and a second driving oil passage 14 communicating with the second liquid delivery passage 9 are arranged in the driving oil cylinder 10 in a communicating manner. The driving piston shaft 11 is connected with a driving device. A buffer structure is also arranged at the rear end of the cylinder block 1 through the mounting seat 7.

[0037] The opening of the first driving oil passage 13 in the driving hydraulic chamber 12 is located at the rear end of the driving hydraulic chamber 12, and the opening of the second driving oil passage 14 in the driving hydraulic chamber 12 is located at the front end of the driving hydraulic chamber 12.

[0038] Through the settings of the mounting seat 7 and the buffer structure, when the riveting working head is working, the vibration in the front-back direction generated is first absorbed by the buffer structure and then transmitted to the mounting seat 7, and finally the mounting seat 7 transmits the vibration to the active oil cylinder 10. Since the spatial arrangement direction of the mounting seat 7 and the active oil cylinder 10 is perpendicular to the vibration direction generated by the riveting working head, during the process of the mounting seat 7 transmitting the vibration to the active oil cylinder 10, the vibration effect is further weakened, thereby reducing the vibration received by the active oil cylinder 10 and the driving device and extending the overall service life of the riveting gun; through the settings of the first liquid delivery path 8, the second liquid delivery path 9, the first active oil path 13, and the second active oil path 14, when the piston in the active oil cylinder 10 moves, the oil in the active hydraulic chamber 12 can enter and exit the driven hydraulic chamber 4, thereby driving the hollow piston shaft 2 to move back and forth; through hydraulic power transmission, the vibration generated during the riveting process can be effectively isolated, avoiding a large impact on the driving device.

[0039] The cross-sectional area of the driven hydraulic chamber 4 is larger than the cross-sectional area of the active hydraulic chamber 12. Preferably, the cross-sectional area of the driven hydraulic chamber 4 is 1.12 times that of the active hydraulic chamber 12. Through the design of the dimensional relationship between the cross-sectional area of the driven hydraulic chamber 4 and the cross-sectional area of the active hydraulic chamber 12, the axial force of the driving device on the active piston shaft 11 can be reduced, and at the same time, the riveting function design requirements of the riveting gun can be more accurately met, further enhancing the stability and the overall service life of the riveting gun.

[0040] In this embodiment, a buffer guide tube 15 is provided for supporting the riveting working head and providing sliding guidance for the riveting working head in the axial direction of the riveting working head. A sealing plate 16 for sealing the rear end of the rear end cover 3 is provided on the outer wall of the buffer guide tube 15. The mounting seat 7 includes a mounting plate 17 for the buffer guide tube 15 to pass through. In the state where the buffer guide tube 15 passes through the mounting plate 17, a retaining ring assembly is provided on the side of the buffer guide tube 15 facing away from the cylinder block 1. The buffer structure includes a forward buffer ring 18 located between the mounting plate 17 and the sealing plate 16 and a reverse buffer ring 19 located between the mounting plate 17 and the retaining ring assembly. The oil distribution plate 30 is provided with a sealing groove 48 for limiting and embedding the placement of the sealing plate 16 on the side facing the cylinder block. The materials of the forward buffer ring 18 and the reverse buffer ring 19 are both made of elastic energy-absorbing materials. Through the settings of the forward buffer ring 18 and the reverse buffer ring 19, the vibration in the front-back direction generated by the riveting working head can be absorbed and weakened.

[0041] The retaining ring assembly includes an annular retaining ring 20 and a shaft circlip 21. The inner diameter of the annular retaining ring 20 is equal to the outer diameter of the buffer guide tube 15. That is, in the state where the buffer guide tube 15 is fixed on the mounting plate 17, the outer diameter of the section of the buffer guide tube 15 where the annular retaining ring 20 is located. The outer diameter of the annular retaining ring 20 is greater than the outer diameter of the reverse buffer ring 18. The inner diameter of the shaft circlip 21 is less than the inner diameter of the annular retaining ring 20, and the outer diameter of the shaft circlip 21 is greater than the inner diameter of the annular retaining ring 20. An annular groove 22 for embedding the annular retaining ring 20 is provided on the buffer guide tube 15. The shaft circlip 21 is in a shape of a major arc. Through the setting of the annular groove 22, the shaft circlip 21 can be embedded, thereby playing a blocking role on the annular retaining ring 20; through the setting of the annular retaining ring 20, it can play a blocking role on the reverse buffer ring 19.

[0042] The mounting seat 7 is installed and fixed with a mounting plate 17 and a guide plate 23 for the buffer guide tube 15 to pass through. The mounting plate 17 is arranged between the cylinder block 1 and the guide plate 23. A front guide ring 24 for the buffer guide tube 15 to pass through is provided on the mounting plate 17. The inner diameter of the front guide ring 24 is equal to the outer diameter of the buffer guide tube 15. That is, in the state where the buffer guide tube 15 is fixed on the mounting plate 17, the outer diameter of the section where the front guide ring 24 is located. The thickness of the front guide ring 24 is greater than the thickness of the mounting plate 17; a rear guide ring 25 for the buffer guide tube 15 to pass through is provided on the guide plate 23. The inner diameter of the rear guide ring 25 is equal to the outer diameter of the buffer guide tube 15. That is, in the state where the buffer guide tube 15 is fixed on the guide plate 23, the outer diameter of the section where the rear guide ring 25 is located. The thickness of the rear guide ring 25 is greater than the thickness of the guide plate 23. The guide plate 23 and the mounting seat 7 are connected by bolts. The front guide ring 24 and the mounting plate 17 are connected by bolts. The rear guide ring 25 and the guide plate 23 are connected by bolts. Through the setting of the front guide ring 24 and the rear guide ring 25, it can play a guiding role in the axial movement of the buffer guide tube 15.

[0043] The buffer structure of this embodiment further includes two transition joints 26. The front and rear ends of each transition joint 26 are respectively embedded into the cylinder block 1 and the mounting seat 7. The front and rear ends of one transition joint 26 are respectively connected and communicated with the first oil circuit 5 and the first infusion circuit 8. The front and rear ends of the other transition joint 26 are respectively connected and communicated with the second oil circuit 6 and the second infusion circuit 9. Through the setting of the transition joint 26, the oil circuit inside the cylinder block 1 can be connected and communicated with the oil circuit inside the mounting seat 7.

[0044] An axial oil passage 27 extending along the axial direction of the adapter joint 26 and a radial oil passage 28 extending along the radial direction of the adapter joint 26 are provided inside the adapter joint 26. The axial oil passage 27 is communicated with the radial oil passage 28. One end of the axial oil passage 27 opens towards the cylinder block 1, and one end of the radial oil passage 28 opens towards the side wall of the adapter joint 26. A plurality of radial oil passages 28 are arranged around the axial oil passage. The axial oil passage 27 is used to communicate with the first oil passage 5 or the second oil passage 6, and the radial oil passage 28 is used to communicate with the first infusion passage 8 or the second infusion passage 9. Through the arrangement of the axial oil passage 27 and the radial oil passage 28, the axial oil passage 28 can be communicated with the first oil passage 5 or the second oil passage 6, and the radial oil passage 28 can be communicated with the first infusion passage 8 or the second infusion passage 9.

[0045] At the opening of the radial oil passage 27 on the side wall of the adapter joint 26, an annular sealing groove 29 for placing a sealing ring is respectively arranged on the front and rear sides along the axial direction of the adapter joint 26. Through the arrangement of the sealing groove 29, sealing rings can be arranged on the front and rear sides of the opening of the radial oil passage 27 on the adapter joint 26, so that a sealed space is formed between the two sealing rings, avoiding oil leakage near the opening of the radial oil passage 27 on the adapter joint 26.

[0046] The rear end of the cylinder block 1 is hermetically connected to an oil distribution plate 30. The transition joint 26 is made of an elastic material. A limiting outer edge is provided on the end face of the transition joint 26 facing the cylinder block. A limiting groove 32 for placing the limiting outer edge 31 is provided on the side of the oil distribution plate 30 facing away from the mounting seat 7. A sealing cavity 33 for placing a sealing ring corresponding to the axial oil passage 28 is provided at one end of the rear end cover 3 facing the oil distribution plate 30. The outer diameter of the sealing ring is smaller than the outer diameter of the limiting outer edge 31. A receiving groove 47 for receiving the transition joint 26 is provided on the mounting seat 7. When the riveting working head is in the working state, the length of the transition joint 26 in the receiving groove 47 is always less than the depth of the receiving groove 47. The openings of the first infusion passage 8 or the second infusion passage 9 on the side wall of the receiving groove 47 are always located between the two sealing grooves 29 on the transition joint 26 in the receiving groove 47. The oil distribution plate 30 is connected to the cylinder block 1 by bolts. The mounting seat 7 is provided with a vent hole at the bottom end of the sealing groove 29 for communicating the two sealing grooves 29 with the outside of the mounting seat 7. Through the setting of the vent hole, it is possible to prevent the transition joint 26 from forming a sealed cavity with the bottom end of the sealing groove 29, thereby avoiding the phenomenon that the movement of the transition joint 26 into the receiving groove 47 is hindered due to excessive pressure in the receiving groove 47. Through the design of the oil distribution plate 30 and the limiting outer edge 31, the transition joint 26 can be fixed on the cylinder block 1. At the same time, through the setting of the length of the receiving groove 47, the transition joint 26 has a margin for further in-depth movement in the receiving groove 47. When the riveting working head generates vibrations in the front-rear direction, the transition joint 26 can move back and forth in the receiving groove 47, thereby preventing the vibrations transmitted from the riveting working head to the transition joint 26 from being transmitted to the receiving groove 47. Through the design of the spatial position relationship between the opening position of the first infusion passage 8 or the second infusion passage 9 on the side wall of the receiving groove 47 and the two sealing grooves 29 on the transition joint 26 in the receiving groove 47, it is possible to ensure that when the transition joint 26 moves back and forth in the receiving groove 47, the radial oil passage 27 is always in communication with the first infusion passage 8 or the second infusion passage 9.

[0047] The driving device includes a driving pipe 34, and the driving pipe 34 includes a sealing joint 35. The sealing joint 35 is hermetically connected to the active oil cylinder 10, and the active piston shaft 11 penetrates through the sealing joint 35. A driven screw 36 is connected to one end of the active piston shaft 11 facing the driving pipe 34. A driven gear 37 is coaxially thread-connected to the driven screw 36. One end of the driven screw 36 facing the active piston shaft 11 is provided with a prism section 46 whose outer surface is prism-shaped. A collar 41 is sleeved on the prism section 46. Anti-rotation force arms 42 extending radially along the collar 41 are provided on opposite sides of the collar 41. A roller 43 is sleeved on the anti-rotation force arms 42. An activity groove 44 extending along the axial direction of the driving pipe 34 for placing the roller 43 is provided on the side wall of the driving pipe 34. The driven gear 37 is meshed with a driving gear 38. A speed reducer 39 is coaxially connected to the driving gear 38, and the speed reducer 39 is coaxially connected to a motor 40. At least two sealing rings are provided between the sealing joint 35 and the active piston shaft 11. The driven screw 36 and the driven gear 37 are coaxially arranged. The inner through hole of the collar 41 is prism-shaped with a shape and size corresponding to the outer surface of the prism section 46. Through the settings of the motor 40, the speed reducer 39, the driving gear 38, the driven gear 37, the driven screw 36, the prism section 37, and the anti-rotation force arms 42, with the motor 40 as the power source, after being decelerated by the speed reducer 39, the driving gear 38 is driven to drive the driven gear 37 to rotate. Since the driven screw 36 is thread-connected to the driven gear 37 and the anti-rotation force arms 42 are provided on the driven screw 36, during the rotation of the driven gear 37 around the axis of the driven screw 36, the driven screw 36 is rotationally limited and can only perform a reciprocating motion along the axis of the driven screw 36, thereby driving the active piston shaft 11 to perform a reciprocating motion along the axial direction of the driven screw 36, causing the oil pressures at the front and rear ends in the active hydraulic chamber 12 to change.

[0048] The driven screw 36 is a ball screw. Position sensors 45 are provided through the driving pipe 34 at the head and tail ends of the activity groove 44. The position sensors 45 are electrically connected to the motor 40. Through the setting of the position sensors 45, the position of the collar 41 in the driving pipe 34 can be detected. When the collar 41 reaches the end of the activity groove 44, the position sensors 45 transmit a signal indicating arrival to the motor 40, preventing the motor 40 from continuing to drive the driven screw 36 to move in the original direction and thus generating an ineffective load.

[0049] The mounting seat 7 is connected to the outer wall of the active oil cylinder 10 by bolts. Two oil replenishing ports are provided on the mounting seat 7. One of the oil replenishing ports is communicated with the first liquid delivery path 8, and the other oil replenishing port is communicated with the second liquid delivery path 9. Oil replenishing plugs are provided on each oil replenishing port. Through the setting of the oil replenishing ports, when the oil volume in the driven hydraulic chamber 4 or the active hydraulic chamber 12 is lost as the piston moves, oil can be replenished through the oil replenishing ports.

[0050] Embodiment 1

[0051] An impact-resistant riveting device according to this embodiment is as follows Figure 1 , Figure 2 shown, including a riveting working head, which includes a cylinder block 1, a hollow piston shaft 2, and a rear end cover 3. The cylinder block 1 and the rear end cover 3 form a driven hydraulic chamber 4 for the hollow piston shaft 2 to move.

[0052] As Figure 3 shown, a first oil passage 5 connected to the front end of the driven hydraulic chamber 4 and a second oil passage 6 connected to the rear end of the driven hydraulic chamber 4 are arranged inside the cylinder block 1, and a mounting seat 7 is connected to the rear end of the cylinder block 1.

[0053] As Figure 2 , Figure 3 , Figure 4 , Figure 5 , Figure 6 shown, a first infusion passage 8 connected to the first oil passage 5 and a second infusion passage 9 connected to the second oil passage 6 are arranged inside the mounting seat 7. A driving oil cylinder 10 located outside the side of the riveting working head is arranged below the mounting seat 7. A driving piston shaft 11 and a driving hydraulic chamber 12 for the driving piston shaft 11 to move are arranged inside the driving oil cylinder 10; a first driving oil passage 13 connected to the first infusion passage 8 and a second driving oil passage 14 connected to the second infusion passage 9 are arranged in the driving oil cylinder 10 in a communicating manner. The driving piston shaft 11 is connected with a driving device, and a buffer structure is arranged between the mounting seat 7 and the cylinder block 1. The opening of the first driving oil passage 13 in the driving hydraulic chamber 12 is located at the rear end of the driving hydraulic chamber 12, and the opening of the second driving oil passage 14 in the driving hydraulic chamber 12 is located at the front end of the driving hydraulic chamber 12. The outer walls of the mounting seat 7 and the driving oil cylinder 10 are connected by bolts. Two oil filling ports are arranged on the mounting seat 7. One oil filling port is connected to the first infusion passage 8, and the other oil filling port is connected to the second infusion passage 9. An oil filling plug is arranged on each oil filling port. Through the arrangement of the oil filling ports, when the oil quantity in the driven hydraulic chamber 4 or the driving hydraulic chamber 12 is lost as the piston moves, the oil can be supplemented through the oil filling ports.

[0054] As Figure 1 , Figure 2 , Figure 3 , Figure 4As shown, through the setting of the mounting seat 7 and the buffer structure, when the riveting working head works, the vibration in the front-back direction generated is first damped by the buffer structure and then transmitted to the mounting seat 7, and finally the mounting seat 7 transmits the vibration to the driving oil cylinder 10. Since the spatial arrangement direction of the mounting seat 7 and the driving oil cylinder 10 is perpendicular to the vibration direction generated by the riveting working head, during the process of the mounting seat 7 transmitting the vibration to the driving oil cylinder 10, the vibration effect is further weakened, thereby reducing the vibration received by the driving oil cylinder 10 and the driving device and prolonging the overall service life of the riveting gun; through the setting of the first liquid delivery path 8, the second liquid delivery path 9, the first active oil path 13, and the second active oil path 14, when the piston in the driving oil cylinder 10 moves, the oil in the active hydraulic cavity 12 can enter and exit the driven hydraulic cavity 4, thereby driving the hollow piston shaft 2 to move back and forth; through hydraulic power transmission, the vibration generated during the riveting process can be effectively isolated, avoiding a large impact on the driving device.

[0055] As Figure 2 shown, the cross-sectional area of the driven hydraulic cavity 4 is larger than that of the active hydraulic cavity 12. Its function is that through the design of the size relationship between the cross-sectional area of the driven hydraulic cavity 4 and the cross-sectional area of the active hydraulic cavity 12, the axial force of the driving device on the active piston shaft 11 can be reduced.

[0056] As Figure 2 , Figure 4 , Figure 5 shown, the riveting working head includes a guide tube 15 for supporting the riveting working head and providing sliding guidance for the riveting working head in the axial direction of the riveting working head. A sealing plate 16 for sealing the rear end of the rear end cover 3 is arranged on the outer wall of the buffer guide tube 15. The mounting seat 7 includes a mounting plate 17 for the buffer guide tube 15 to pass through. In the state where the buffer guide tube 15 passes through the mounting plate 17, a retaining ring assembly is arranged on the side of the buffer guide tube 15 facing away from the cylinder block 1 and located on the mounting plate 17.

[0057] As Figure 1 , Figure 2 , Figure 4 , Figure 5 shown, the buffer structure includes a forward buffer ring 18 located between the mounting plate 17 and the sealing plate 16 and a reverse buffer ring 19 located between the mounting plate 17 and the retaining ring assembly. The oil distribution plate 30 is provided with a sealing groove 48 for placing the sealing plate 16 on the side facing the cylinder block 1. The materials of the forward buffer ring 18 and the reverse buffer ring 19 both adopt elastic energy-absorbing materials. Its function is that through the setting of the forward buffer ring 18 and the reverse buffer ring 19, the vibration in the front-back direction generated by the riveting working head can be absorbed and weakened.

[0058] As Figure 1 , Figure 2 , Figure 4 , Figure 5As shown, the retaining ring assembly includes an annular retaining ring 20 and a shaft circlip 21; the inner diameter of the annular retaining ring 20 is equal to the outer diameter of the buffer guide tube 15, that is, in the state where the buffer guide tube 15 is fixed to the mounting seat 7, the outer diameter of the section of the guide tube 15 where the annular retaining ring 20 is located; the outer diameter of the annular retaining ring 20 is greater than the outer diameter of the reverse buffer ring 19, the inner diameter of the shaft circlip 21 is less than the inner diameter of the annular retaining ring 20, the outer diameter of the shaft circlip 21 is greater than the inner diameter of the annular retaining ring 20, and an annular groove 22 for embedding the annular retaining ring 20 is provided on the guide tube 15. The shaft circlip 21 is in the shape of a superior arc. Through the setting of the annular groove 22, the shaft circlip 21 can be embedded, thereby playing a blocking role on the annular retaining ring 20; through the setting of the annular retaining ring 20, it can play a blocking role on the reverse buffer ring 19.

[0059] As Figure 1 , Figure 4 , Figure 5 shown, the mounting seat 7 includes a guide plate 23 for the buffer guide tube 15 to pass through, a mounting plate 17 is arranged between the cylinder block 1 and the guide plate 23, a front guide ring 24 for the buffer guide tube 15 to pass through is connected and arranged on the mounting plate 17, the inner diameter of the front guide ring 24 is equal to the outer diameter of the buffer guide tube 15, that is, in the state where the buffer guide tube 15 is fixed to the mounting seat 7, the outer diameter of the section where the front guide ring 24 is located, the thickness of the front guide ring 24 is greater than the thickness of the mounting plate 17, a rear guide ring 25 for the buffer guide tube 15 to pass through is connected to the guide plate 23, the inner diameter of the rear guide ring 25 is equal to the outer diameter of the buffer guide tube 15, that is, in the state where the buffer guide tube 15 is fixed to the mounting seat 7, the outer diameter of the section where the rear guide ring 25 is located, the thickness of the rear guide ring 25 is greater than the thickness of the guide plate 23. The guide plate 23 and the mounting seat 7 are connected by bolts, the front guide ring 24 and the mounting plate 17 are connected by bolts, and the rear guide ring 25 and the guide plate 23 are connected by bolts. Through the setting of the front guide ring 24 and the rear guide ring 25, it can play a guiding role in the axial movement of the buffer guide tube 15.

[0060] As Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 5 shown, the buffer structure further includes two transition joints 26, the front and rear ends of each transition joint 26 are respectively embedded into the cylinder block 1 and the mounting seat 7, the front and rear ends of one transition joint 26 are respectively communicated with the first oil passage 5 and the first infusion passage 8, and the front and rear ends of the other transition joint 26 are respectively communicated with the second oil passage 6 and the second infusion passage 9. Its function is that through the setting of the transition oil passage, the oil passage inside the cylinder block 1 can be communicated with the oil passage inside the mounting seat 7.

[0061] As Figure 9As shown, an axial oil passage 27 extending along the axis of the adapter 26 and a radial oil passage 28 extending along the radius of the adapter 26 are provided inside the adapter 26. The axial oil passage 27 is in communication with the radial oil passage 28. One end of the axial oil passage 27 opens towards the cylinder block 1, and one end of the radial oil passage 28 opens towards the side wall of the adapter 26. A plurality of radial oil passages 28 are arranged around the axial oil passage 27. The axial oil passage 27 is used to communicate with the first oil passage 5 or the second oil passage 6, and the radial oil passage 28 is used to communicate with the first infusion passage 8 or the second infusion passage 9. Its function is that through the arrangement of the axial oil passage 27 and the radial oil passage 28, the axial oil passage 27 can be communicated with the first oil passage 5 or the second oil passage 6, and the radial oil passage 28 can be communicated with the first infusion passage 8 or the second infusion passage 9.

[0062] As Figure 9 shown, at the opening of the radial oil passage 28 on the side wall of the adapter 26, an annular sealing groove 29 for placing a sealing ring is provided on each of the front and rear sides along the axis of the adapter 26. Its function is that through the arrangement of the sealing groove 29, sealing rings can be provided on the front and rear sides of the opening of the radial oil passage 28 on the adapter 26, so as to form a sealed space between the two sealing rings and prevent oil leakage near the opening of the radial oil passage 28 on the adapter 26.

[0063] As Figure 1 、 Figure 2 、 Figure 3 、 Figure 4 、 Figure 5 、 Figure 7As shown, a oil distribution plate 30 is hermetically connected to the rear end of the cylinder block 1. The transition joint 26 is made of an elastic material. A limiting outer edge 31 is provided on the end face of the transition joint 26 facing the cylinder block 1. A limiting groove 32 for placing the limiting outer edge 31 is provided on the side of the oil distribution plate 30 facing away from the mounting seat 7. A sealing cavity 33 for placing a sealing ring corresponding to the axial oil passage 27 is provided at one end of the rear end cover 3 facing the oil distribution plate 30. The outer diameter of the sealing ring is smaller than the outer diameter of the limiting outer edge 31. A receiving groove 47 for receiving the transition joint 26 is provided on the mounting seat 7. When the riveting working head is in the working state, the length of the transition joint 26 in the receiving groove 47 is always less than the depth of the receiving groove 47. The openings of the first infusion path 8 or the second infusion path 9 on the side wall of the receiving groove 47 are always located between the two sealing grooves 29 on the transition joint 26 in the receiving groove 47. The oil distribution plate 30 and the cylinder block 1 are connected by bolts. Its function is that through the design of the oil distribution plate 30 and the limiting outer edge 31, the transition joint 26 can be fixed on the cylinder block 1. At the same time, through the setting of the length of the receiving groove 47, the transition joint 26 has a margin for further moving deeper in the receiving groove 47. When the riveting working head generates vibrations in the front and back directions, the transition joint 26 can move back and forth in the receiving groove 47, thereby avoiding the vibrations transmitted from the riveting working head to the transition joint 26 being transmitted to the receiving groove 47. Through the design of the spatial position relationship between the opening position of the first infusion path 8 or the second infusion path 9 on the side wall of the receiving groove 47 and the two sealing grooves 29 on the transition joint 26 in the receiving groove 47, when the transition joint 26 moves back and forth in the receiving groove 47, the radial oil passage 28 can always be kept in communication with the first infusion path 8 or the second infusion path 9.

[0064] As Figure 2 , Figure 4 , Figure 5 , Figure 8 shown, the driving device includes a driving pipe 34. The driving pipe 34 includes a sealing joint 35. The sealing joint 35 is hermetically connected to the active oil cylinder 10 and the active piston shaft 11 passes through the sealing joint 35. A driven screw 36 is connected to one end of the active piston shaft 11 facing the driving pipe 34. A driven gear 37 is coaxially threadedly connected to the driven screw 36. A prism section 46 with a prismatic outer surface is provided at one end of the driven screw 36 facing the active piston shaft 11. A collar 41 is sleeved on the prism section 46. As Figure 8As shown in the figure, anti-rotation force arms 42 extending radially along the collar 41 are provided on opposite sides of the collar 41. Rollers 43 are sleeved on the anti-rotation force arms 42. An activity groove 44 extending axially along the drive tube 34 for placing the rollers 43 is provided on the side wall of the drive tube 34. The driven gear 37 is meshed and connected with a driving gear 38. A speed reducer 39 is coaxially connected to the driving gear 38, and a motor 40 is coaxially connected to the speed reducer 39. Through the arrangement of the rollers 43, it is convenient for the anti-rotation force arms 42 on the collar 41 to move in the activity groove 44. At least two sealing rings are provided between the sealing joint 35 and the active piston shaft 11. The driven screw 36 is coaxially arranged with the driven gear 37. The internal through hole of the collar 41 is in a prismatic shape corresponding to the outer surface of the prism section 46. The speed reducer 39 and the motor 40 are prior arts and will not be elaborated here. Their function is that, through the arrangements of the motor 40, the speed reducer 39, the driving gear 38, the driven gear 37, the driven screw 36, the prism section 46, and the anti-rotation force arms 42, with the motor 40 as the power source, after being decelerated by the speed reducer 39, the driving gear 38 is driven to drive the driven gear 37 to rotate. Since the driven screw 36 is threadedly connected to the driven gear 37 and the anti-rotation force arms 42 are provided on the driven screw 36, during the rotation of the driven gear 37 around the axis of the driven screw 36, the driven screw 36 does not rotate around its own axis and can only make a reciprocating motion along the axis of the driven screw 36, thereby driving the active piston shaft 11 to make a reciprocating motion along the axis of the driven screw 36, so that the oil pressures at the front and rear ends in the active hydraulic chamber 12 change.

[0065] As Figure 2 , Figure 4 , Figure 5 shown, the driven screw 36 adopts a ball screw. Position sensors 45 are penetrated and arranged at the head and tail ends of the activity groove 44 on the drive tube 34. The position sensors 45 are electrically connected to the motor 40. Their function is that, through the arrangement of the position sensors 45, the position of the collar 41 in the drive tube 34 can be detected. When the collar 41 reaches the end of the activity groove 44, the position sensors 45 transmit the in-place signal to the motor 40, avoiding the motor 40 from continuing to drive the driven screw 36 to move in the original direction, thereby generating an ineffective load.

[0066] The working principle of this embodiment is described as follows: In this embodiment, the motor 40 is used as the power source to drive the active piston shaft 11 to move reciprocally. During the process that the forward rotation of the motor 40 drives the active piston shaft 11 to move away from the driven gear 37 in the active hydraulic chamber 12, the hydraulic oil at the front end of the active hydraulic chamber 12 sequentially passes through the second active oil path 14, the second liquid delivery path 9, the radial oil passage 28, the axial oil passage 27, and the second oil path 6 and enters the rear end of the driven hydraulic chamber 4, pushing the hollow piston shaft 2 to move forward. The hydraulic oil at the front end of the driven hydraulic chamber 4 is extruded by the hollow piston shaft 2 and sequentially passes through the first oil path 5, the axial oil passage 27, the radial oil passage 28, the first liquid delivery path 8, and the first active oil path 13 and enters the rear end of the active hydraulic chamber 12. During the process that the reverse rotation of the motor 40 drives the active piston shaft 11 to move towards the driven gear 37 in the active hydraulic chamber 12, the moving route of the hydraulic oil is opposite to the above route.

[0067] This embodiment eliminates the piston pump composed of an oil suction check valve, a pressure oil check valve, and a pressure oil plunger in the conventional hydraulic system, does not require a direction control valve with a complex structure and high cost, and can also omit the pressure limiting valve of the hydraulic system, making the structure of the power part simpler;

[0068] Since components such as the direction control valve sensitive to hydraulic oil are removed from the hydraulic power part, the requirements for the quality and viscosity of the hydraulic oil are reduced, and it can be applied under a wider ambient temperature condition. While for the conventional hydraulic system, the viscosity of the hydraulic oil at high temperature and the oil suction capacity of the piston pump at low temperature must be considered. For this kind of structure, as long as the hydraulic oil still has good fluidity, it can work normally; when the oil volume in the cavity is sufficient, complex maintenance work such as replacing the hydraulic oil does not need to be considered, and only replenishment is needed after the hydraulic oil is consumed;

[0069] Due to the use of the equal volume principle, it is not necessary to supply oil to the fuel tank additionally during each stroke. At the same time, for this kind of equal volume structure, the hydraulic oil only moves in the connected cavities along their respective pipelines, generating less heat, and there is no need to particularly dissipate heat from the hydraulic system.

Claims

1. An impact-resistant riveting drive structure, comprising a riveting working head and a riveting drive mechanism; characterized in that: The riveting working head includes a cylinder block (1), a hollow piston shaft (2) and a rear end cover (3), and the cylinder block (1) and the rear end cover (3) form a driven hydraulic cavity (4) for the hollow piston shaft (2) to move. The drive mechanism includes a motor drive device and a driven hydraulic cylinder (10) driven by it. The driven hydraulic cylinder (10) includes: a driven piston shaft (11), and a driven hydraulic cavity (12) formed by the driven piston shaft (11) and the cylinder block of the driven hydraulic cylinder (10); the motor drive device is a screw drive mechanism, including: a motor (40), a reducer (39) driven by the motor (40) and a driven screw (36) that axially expands and contracts; one end of the driven screw (36) is drivingly connected to the driven piston shaft (11) and drives the driven piston shaft (11) to move to provide drive hydraulic oil for the riveting working head. The riveting working head is fixedly installed on the drive mechanism through a mounting seat (7), and the riveting working axis of the riveting working head composed of the cylinder block (1), the hollow piston shaft (2) and the rear end cover (3) is installed in a misaligned manner with the axis of the drive mechanism.

2. The anti-impact riveting driving structure according to claim 1, wherein: The cross-sectional area of the driven hydraulic cavity (4) is larger than the cross-sectional area of the driven hydraulic cavity (12).

3. The anti-impact riveting drive structure according to claim 2, characterized in that: The cross-sectional area of the driven hydraulic cavity (4) is 1.12 times that of the driven hydraulic cavity (12).

4. The anti-impact riveting driving structure according to claim 2, characterized in that: The cylinder block (1) is provided with a first oil passage (5) communicating with the front end of the driven hydraulic cavity (4) and a second oil passage (6) communicating with the rear end of the driven hydraulic cavity (4); the rear end of the cylinder block (1) is connected to the mounting seat (7), and the mounting seat (7) is provided with a first infusion passage (8) communicating with the first oil passage (5) and a second infusion passage (9) communicating with the second oil passage (6). The mounting seat (7) is connected to a driven hydraulic cylinder (10) arranged in a misaligned manner with the axis of the riveting working head below. The inside of the driven hydraulic cylinder (10) is connected and provided with a first driven oil passage (13) communicating with the first infusion passage (8) and a second driven oil passage (14) communicating with the second infusion passage (9).

5. The anti-impact riveting drive structure according to claim 4, characterized in that: The motor driving device includes a driving pipe (34). The driving pipe (34) includes a sealing joint (35). The sealing joint (35) is hermetically connected to the driving oil cylinder (10), and the driving piston shaft (11) passes through the sealing joint (35). One end of the driving piston shaft (11) facing the driving pipe (34) is connected with a driven screw rod (36). A driven gear (37) is coaxially threadedly connected to the driven screw rod (36). One end of the driven screw rod (36) facing the driving piston shaft (11) is provided with a prism section (46) whose outer surface is prism-shaped. A collar (41) is sleeved on the prism section (46). Anti-rotation force arms (42) extending radially along the collar (41) are arranged on opposite sides of the collar (41). An activity groove (44) extending axially along the driving pipe (34) is provided on the side wall of the driving pipe (34). The two ends of the anti-rotation force arm (42) are respectively limited and slide in the activity grooves (44) on both sides. The driven gear (37) is meshed and connected with a driving gear (38). A speed reducer (39) is coaxially connected to the driving gear (38), and the speed reducer (39) is coaxially connected to a motor (40).

6. The anti-impact riveting drive structure according to claim 5, characterized in that: The driven screw rod (36) adopts a ball screw, and position sensors (45) are arranged through the driving pipe (34) at the head and tail ends of the activity groove (44).

7. The anti-impact riveting driving structure according to claim 5, characterized in that: Rollers (43) are sleeved on the ends of the anti-rotation force arms (42), and the rollers (43) are limited and slide in the activity grooves (44).

8. The anti-impact riveting driving structure according to claim 5, characterized in that: Two oil filling ports are arranged on the mounting seat (7). Among them, one oil filling port is communicated with the first liquid delivery path (8), and the other oil filling port is communicated with the second liquid delivery path (9). Oil filling plugs are arranged on each oil filling port.

9. The impact-resistant riveting driving structure according to claim 5, wherein: A buffer mechanism is arranged at the rear end of the riveting working head axially.

Images