Stabilizing device of hydraulic hand riveter

Abstract

The utility model discloses a stabilizing device of a hydraulic hand riveter. The hydraulic hand riveter comprises a driver, a connecting rod and a piston. The piston is arranged on the connecting rod in a sliding and sleeving mode, and the connecting rod is fixedly connected with a rivet pulling screw. The driver drives the connecting rod to rotate in the piston, so that the rivet pulling screw is driven to rotate, and rivet pulling is completed. The stabilizing device comprises at least two bearings, and the at least two bearings are arranged between the piston and the connecting rod, fixedly installed at the two ends of the piston and fixedly support the connecting rod. The connecting rod of the hand riveter does not swing when rotating at a high speed, and the riveting process is more stable.

Description

Technical Field

[0001] The utility model relates to the field of rivet guns, in particular to a stabilizing device for a hydraulic rivet gun. Background Art

[0002] Rivet guns are used for fastening and riveting of various metal plates, pipes and other manufacturing industries. They are widely used in the riveting of electromechanical and light industrial products such as elevators, switches, instruments, furniture, and decorations. They can rivet products that do not require tapping internal threads or welding nuts.

[0003] A rivet gun typically consists of a piston, a connecting rod, and a driver. The piston fits over the connecting rod. The driver is connected to the connecting rod and drives it to rotate within the piston. During riveting, the driver must drive the connecting rod to rotate at high speeds. Currently, the connecting rods of rivet guns on the market are prone to wobbling at high speeds, compromising riveting quality. Utility Model Content

[0004] In view of the deficiencies in the prior art, the utility model provides a stabilizing device for a hydraulic rivet gun, so that the connecting rod of the rivet gun will not swing when rotating at high speed, and the riveting process is more stable.

[0005] The utility model is achieved through the following technical solutions:

[0006] A stabilizing device for a hydraulic rivet gun, the hydraulic rivet gun comprising a driver, a connecting rod and a piston, the piston being slidably sleeved on the connecting rod, the connecting rod being fixedly connected to a rivet screw, the driver driving the connecting rod to rotate in the piston, thereby driving the rivet screw to rotate, and characterized in that the stabilizing device comprises at least two bearings, and at least two bearings are arranged between the piston and the connecting rod, and at least two bearings are fixedly mounted at both ends of the piston and fixedly support the connecting rod.

[0007] Furthermore, the at least two bearings include a first bearing, which is a plane bearing and is accommodated at the upper end of the piston.

[0008] Furthermore, a first bearing groove is formed on the inner wall of the piston, the first bearing is accommodated in the first bearing groove, and the first inner ring of the first bearing fixes and supports the connecting rod to provide tension for the connecting rod.

[0009] Furthermore, the at least two bearings include a second bearing, which is a deep groove ball bearing and is accommodated in the upper end of the piston.

[0010] Furthermore, a second bearing groove is formed on the inner wall of the piston, and the second bearing is accommodated in the second bearing groove. The second inner ring of the second bearing fixedly supports the connecting rod to keep the connecting rod stable and prevent it from swinging.

[0011] Furthermore, it is characterized in that the first bearing groove is connected to the second bearing groove, and the first bearing is in abutment with the second bearing.

[0012] Furthermore, the at least two bearings include a third bearing, which is an angular contact ball bearing and is accommodated at the lower end of the piston.

[0013] Furthermore, a third bearing groove is provided on the inner wall of the piston, and a third ring groove is provided on the lower end of the connecting rod. The third bearing is accommodated in both the third bearing groove and the third ring groove, and the third inner ring of the third bearing fixes and supports the connecting rod to maintain the tension of the connecting rod.

[0014] Furthermore, the first groove surface of the third bearing groove is flush with the second end surface of the third annular groove, and the third bearing abuts against the first groove surface and the second end surface at the same time.

[0015] Furthermore, a first boss is provided at one end of the connecting rod, and a gasket is provided between the first boss and the first bearing. The gasket is sleeved on the connecting rod and has one end abutting against the first boss and the other end abutting against the first bearing.

[0016] Compared with the prior art, the advantages of the present invention are:

[0017] 1. By setting a deep groove ball bearing between the piston and the connecting rod, it can ensure that the connecting rod does not swing and the high-speed rotation is smoother.

[0018] 2. By setting a plane bearing between the piston and the connecting rod, a pulling force can be provided to the connecting rod, so that the connecting rod can maintain normal rotation and can also play a shock-absorbing role.

[0019] 3. By setting an angular contact ball bearing between the piston and the connecting rod, it can ensure that the connecting rod does not swing and at the same time ensure the tension of the connecting rod. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 This is a left side view of a hydraulic rivet gun of the present utility model;

[0021] Figure 2 for Figure 1 Cross-sectional view along AA;

[0022] Figure 3 for Figure 2 Enlarged view of middle B;

[0023] Figure 4 This is an exploded view of the sealing device;

[0024] Figure 5 for Figure 2 Another enlarged view of middle B;

[0025] Figure 6This is an exploded view of the stabilization device;

[0026] Figure 7 This is the assembly drawing of the buffer device;

[0027] Figure 8 for Figure 2 Enlarged view of middle C;

[0028] Figure 9 This is an exploded view of the buffer device.

[0029] In the figure: 1, first seal assembly; 10, first main seal; 11, first secondary seal; 12, third seal; 2, second seal assembly; 20, second main seal; 21, second secondary seal; 3, third seal assembly; 30, first static seal; 31, second static seal; 4, piston; 40, first outer portion; 41, second outer portion; 43, first bearing groove; 44, second bearing groove; 45, third bearing groove; 450, first groove surface; 46 8. Second accommodating chamber; 49. Second annular groove; 5. Pressing ring; 52. Main body; 53. Second boss; 6. Cylinder body; 60. First inner wall; 61. Second inner wall; 68. First accommodating chamber; 69. First annular groove; 70. First guide element; 71. Second guide element; 72. Dustproof element; 80. Hydraulic oil pipe; 800. Oil chamber; 81. Driver; 82. Connecting rod; 820. First outer wall; 821. Second outer wall; 822. First end face; 8 23. Second end face; 825. First boss; 826. Third annular groove; 83. Rivet screw; 830. Connecting sleeve; 831. Pin; 832. Circlip; 833. Elastic member; 834. First through hole; 835. Waist-shaped through hole; 836. Arc-shaped groove; 837. Third boss; 838. Notch; 839. Third accommodating cavity; 84. First bearing; 840. First inner ring; 841. First outer ring; 845. Arc-shaped surface; 85. Second bearing; 850, second inner ring; 851, second outer ring; 86, third bearing; 860, third inner ring; 861, third outer ring; 87, gasket; 870, fourth boss; 88, limiter; 89, locking member; G, radial; 90, first groove; 91, second groove; 92, third groove; 93, fourth groove; 94, fifth groove; 95, sixth groove; 96, seventh groove; 97, eighth groove; 98, ninth groove; 99, tenth groove. DETAILED DESCRIPTION

[0030] The following is a further non-restrictive detailed description of the technical solution of the utility model in conjunction with the preferred embodiments and the accompanying drawings. In the description of the utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. In addition, the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" can explicitly or implicitly include at least one of the features. In the description of the utility model, the meaning of "multiple" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the utility model, and cannot be understood as limiting the utility model.

[0031] like Figure 1 and Figure 2 As shown, a hydraulic rivet gun according to one embodiment of the present invention includes a piston 4, a pressure ring 5, a cylinder body 6, a hydraulic oil pipe 80, a driver 81, a connecting rod 82 and a rivet screw 83. The connecting rod 82 is accommodated in the piston 4, and one end is connected to the driver 81, and the other end is connected to the rivet screw 83. The pressure ring 5 is sleeved on the piston 4 and is accommodated in the cylinder body 6 together with the piston 4. An oil circuit (not shown) is provided on the cylinder body 6, and the oil circuit is connected to the gap between the piston 4 and the pressure ring 5, and the hydraulic oil pipe 80 is installed in the oil circuit. The piston 4 is slidably accommodated in the cylinder body 6, and the pressure ring 5 is accommodated at one end of the cylinder body 6 and sleeved on the piston 4. An oil chamber 800 that can accommodate hydraulic oil is formed between the piston 4 and the pressure ring 5. The piston 4 is slidably sleeved on the connecting rod 82, and the connecting rod 82 is fixedly connected to the rivet screw 83. The driver 81 drives the connecting rod 82 to rotate in the piston 4, thereby driving the rivet screw 83 to rotate to complete the riveting.

[0032] The pressure ring 5 includes a body 52, the outer wall of the body 52 abuts the inner wall of the cylinder 6, and the inner wall of the body 52 abuts the outer wall of the piston 4. The pressure ring 5 also includes a second boss 53 protruding outward relative to the body 52, and the second boss 53 is fixedly connected to the bottom of the cylinder 6.

[0033] Specifically, the interior of the cylinder body 6 is through-formed and formed with a first accommodating chamber 68, and the piston 4 is accommodated in the first accommodating chamber 68 and abuts against the first inner wall 60 of the first accommodating chamber 68. A first annular groove 69 is provided on the first inner wall 60 of the first accommodating chamber 68, and a second annular groove 49 is provided on the outer wall of the piston 4. The body 52 is accommodated in both the first annular groove 69 and the second annular groove 49, and the inner wall of the body 52 abuts against the outer wall of the piston 4, and the inner wall of the body 52 abuts against the second inner wall 61 of the first annular groove 69. The second boss 52 is fixedly connected to the bottom of the cylinder body 6 by screws. The interior of the piston 4 is through-formed and formed with a second accommodating chamber 48, and the connecting rod 82 is accommodated in the second accommodating chamber 48, and the outer wall of the connecting rod 82 abuts against the inner wall of the second accommodating chamber 48.

[0034] The sealing device includes at least two sets of sealing assemblies, including a first sealing assembly 1 and a second sealing assembly 2. The first sealing assembly 1 is disposed between the piston 4 and the cylinder body 6. The first sealing assembly 1 is fixedly mounted on the piston 4 and abuts against the cylinder body 6, forming a first radial seal between the piston 4 and the cylinder body 6. The second sealing assembly 2 is disposed between the pressure ring 5 and the piston 4. The second sealing assembly 2 is fixedly embedded in the pressure ring 5 and abuts against the piston 4, forming a second radial seal between the pressure ring 5 and the piston 4. The at least two sets of sealing assemblies also include a third sealing assembly 3. The third sealing assembly 3 is disposed between the pressure ring 5 and the cylinder body 6. The third sealing assembly 3 is fixedly mounted on the pressure ring 5 and abuts against the cylinder body 6, forming a third radial seal between the pressure ring 5 and the cylinder body 6.

[0035] Specifically, the first sealing assembly 1 has an interference fit with both the piston 4 and the cylinder 6, with each having an interference margin of 0.1 to 0.6 mm. The second sealing assembly 2 has an interference fit with both the pressure ring 5 and the piston 4, with each having an interference margin of 0.1 to 0.4 mm. The third sealing assembly 3 has an interference fit with both the pressure ring 5 and the cylinder 6, with an interference margin of 0.1 to 0.3 mm. Each sealing assembly is composed of multiple sealing elements.

[0036] like Figures 3 to 4As shown, the first sealing assembly 1 includes a first main seal 10, which is a step seal ring. A first groove 90 is provided on the outer wall of the piston 4. The first main seal 10 is accommodated in the first groove 90 and simultaneously abuts against the inner wall of the first groove 90 and the inner wall of the cylinder 6, for sealing the high-pressure hydraulic oil. Specifically, the outer wall of the piston 4 includes a first outer portion 40 and a second outer portion 41. The first groove 90 is located at the lower end of the first outer portion 40 and is close to the oil chamber 800. The first main seal 10 has an interference fit with the inner wall of the first groove 90, and the interference amount is 0.6 mm. The first main seal 10 has an interference fit with the first inner wall 60 of the cylinder 6, and the interference amount is 0.6 mm. The first main seal 10 has an interference fit with the first inner wall 60 of the cylinder 6, and the interference amount is 0.6 mm. By positioning the first main seal 10 on the first outer portion 40 of the piston 4 and connecting it to the cylinder 6, the hydraulic riveter gun can withstand high pressure when subjected to high-pressure oil, increasing the pressure rating from 25 MPa to 40 MPa. The seal also serves as a primary seal, improving sealing effectiveness. Furthermore, the first main seal 10 is positioned close to the oil chamber 800, quickly preventing hydraulic oil from impacting the piston 4 and cylinder 6 during riveting, resulting in more timely and effective sealing.

[0037] The first sealing assembly 1 also includes a first secondary seal 11, which is a YX-type sealing ring. A second groove 91 is also provided on the outer wall of the piston 4. The first secondary seal 11 is accommodated in the second groove 91 and simultaneously abuts against the inner wall of the second groove 91 and the inner wall of the cylinder body 6, for sealing the low-pressure hydraulic oil. Specifically, the second groove 91 is located above the first groove 90. The first secondary seal 11 has an interference fit with the inner wall of the second groove 91, and the interference is 0.3 mm. The first secondary seal 11 has an interference fit with the first inner wall 60 of the cylinder body 6, and the interference is 0.3 mm. By arranging the first secondary seal 11 on the first outer portion 40 of the piston 4 and connecting it to the cylinder body 6, the hydraulic rivet gun can achieve a good sealing effect when dealing with low pressure.

[0038] The first sealing assembly 1 also includes a third seal 12. A third groove 92 is also provided on the outer wall of the piston 4. The third seal 12 is accommodated in the third groove 92 and simultaneously abuts against the inner wall of the third groove 92 and the inner wall of the cylinder body 6 to seal the gas. Specifically, the third groove 92 is located above the second groove 91. The third seal 12 is an O-ring. The third seal 12 has an interference fit with the third groove 92, and the interference is 0.1 mm. The third seal 12 has an interference fit with the first inner wall 60 of the cylinder body 6, and the interference is 0.1 mm. By arranging the third seal 12 on the first outer portion 40 of the piston 4 and connecting it to the cylinder body 6, the hydraulic oil can be sealed while the gas can also be effectively sealed, and dustproofing can be achieved.

[0039] The first sealing assembly 1 is a plurality of sealing elements which are sleeved on the first outer portion 40 of the piston 4 and are distributed at a certain distance between each other. This can effectively seal the gap between the piston 4 and the cylinder body 6 layer by layer, thereby extending the service life of each sealing element, reducing the frequency of replacement of the sealing elements, and improving the sealing, stability and durability of the sealing device.

[0040] like Figures 3 to 4 As shown, the second sealing assembly 2 includes a second main seal 20, which is a step seal ring. A fourth groove 93 is provided on the inner side of the pressure ring 5. The second main seal 20 is accommodated in the fourth groove 93 and simultaneously abuts against the inner wall of the fourth groove 93 and the inner wall of the connecting rod 82, thereby sealing the high-pressure hydraulic oil. Specifically, the fourth groove 93 is located at the upper end of the inner wall of the body 52 and is close to the oil chamber 800. The second main seal 20 has an interference fit with the inner wall of the fourth groove 93, and the interference is 0.4 mm. The second main seal 20 has an interference fit with the second outer portion 41 of the piston 4, and the interference is 0.4 mm. By arranging the second main seal 20 on the inner side of the pressure ring 5 and connecting it to the piston 4, the hydraulic rivet gun can withstand high pressure when responding to the impact of high-pressure oil, and the pressure resistance level is increased from 25 MPa to 40 MPa. It also plays a major sealing role, thereby improving the sealing effect. Furthermore, the second main seal 20 is located close to the oil chamber 800 , which can quickly prevent the hydraulic oil from impacting the pressure ring 5 and the piston 4 during riveting, making the sealing more timely and effective.

[0041] The second sealing assembly 2 also includes a second secondary seal 21, which is a YX-type sealing ring. A fifth groove 94 is also provided on the inner side of the pressure ring 5. The second secondary seal 21 is accommodated in the fifth groove 94 and simultaneously abuts against the inner wall of the fifth groove 94 and the inner wall of the connecting rod 82 to seal the high-pressure hydraulic oil. Specifically, the fifth groove 94 is located below the fourth groove 93. The second sealing assembly 2 has an interference fit with the piston 4, and the interference is 0.1 to 0.4 mm. The second secondary seal 21 has an interference fit with the second outer portion 41 of the piston 4, and the interference is 0.1 mm. By arranging the second secondary seal 21 on the inner side of the pressure ring 5 and connecting it to the piston 4, a good sealing effect can be achieved when dealing with low pressure.

[0042] By embedding multiple sealing elements inside the pressure ring 5 and distributing a certain distance between each sealing element, the gap between the pressure ring 5 and the piston 4 can be effectively sealed layer by layer, thereby extending the life of each sealing element, reducing the frequency of sealing element replacement, and improving the sealing, stability and durability of the sealing device.

[0043] like Figures 3 to 4As shown, the third sealing assembly 3 includes a first static seal 30 and a second static seal 31. A sixth groove 95 and a seventh groove 96 are defined on the outer side of the pressure ring 5. The first static seal 30 is housed within the sixth groove 95 and abuts against both the inner wall of the sixth groove 95 and the inner wall of the cylinder body 6. The second static seal 31 is housed within the seventh groove 96 and abuts against both the inner wall of the seventh groove 96 and the inner wall of the cylinder body 6. Specifically, the sixth groove 95 is located at the upper end of the outer wall of the body 52, near the oil chamber 800. The first static seal 30 forms an interference fit with the inner wall of the sixth groove 95, with an interference fit of 0.3 mm. The first static seal 30 also forms an interference fit with the second inner wall 61 of the cylinder body 6, with an interference fit of 0.3 mm. The first static seal 30 is positioned near the top of the pressure ring 5, effectively preventing hydraulic oil from impacting the pressure ring 5 and cylinder body 6 during riveting, ensuring a more timely and effective seal. The seventh groove 96 is located below the sixth groove 95. The second static seal 31 forms an interference fit with the seventh groove 96, with an interference margin of 0.1 mm. It also forms an interference fit with the second inner wall 61 of the cylinder body 6, with an interference margin of 0.1 mm. The first and second static seals 30, 31 are O-rings. There is no relative motion between the pressure ring 5 and the cylinder body 6. The installation of the first and second static seals 30, 31 enhances the static sealing effect of the pressure ring 5 and the cylinder body 6 on the hydraulic oil. Furthermore, the structure is simple and easy to replace.

[0044] By setting up multiple sealing elements, the gaps between the piston and the cylinder body, the gaps between the piston and the pressure ring, and the gaps between the pressure ring and the cylinder body are effectively sealed layer by layer, thereby extending the life of each sealing element, reducing the replacement frequency of the sealing elements, and improving the sealing, stability and durability of the entire sealing device.

[0045] Further references Figure 3 and Figure 4 A first guide element 70 is also provided between the piston 4 and the cylinder body 6, and a second guide element 71 is also provided between the piston 4 and the pressure ring 5. Both the first guide element 70 and the second guide element 71 serve as guide strips. Specifically, an eighth groove 97 is provided on the first outer portion 40 of the piston 4. The first guide element 70 is received within the eighth groove 97 and abuts against the inner wall of the eighth groove 97. A clearance fit is formed between the first guide element 70 and the first inner wall 60 of the cylinder body 6. A ninth groove 98 is also provided on the inner side of the pressure ring 5. The second guide element 71 is received within the ninth groove 98 and abuts against the inner wall of the ninth groove 98. A clearance fit is formed between the second guide element 71 and the second outer portion 41 of the piston 4. Providing the first guide element 70 between the piston 4 and the cylinder body 6 effectively reduces friction between the two groups, extending their service life. Providing the second guide element 71 between the piston 4 and the pressure ring 5 effectively reduces friction between the two groups, extending their service life.

[0046] A dustproof element 72, a dustproof ring, is also provided between the piston 4 and the pressure ring 5. The dustproof element 72 is embedded in the pressure ring 5. A tenth groove 99 is defined on the inner side of the pressure ring 5. The dustproof element 72 is accommodated in the tenth groove 99 and engages with the second outer portion 41 of the piston 4. The placement of the dustproof element 72 between the pressure ring 5 and the piston 4 effectively prevents dust from entering the cylinder 6 and damaging the sealing element.

[0047] In addition, in order to ensure that the connecting rod does not swing when rotating at high speed during riveting, the hydraulic riveting gun of the present invention is also provided with a stabilizing device. Figure 5 and 6 As shown, the stabilizing device includes at least two bearings, and at least two bearings are arranged between the piston 4 and the connecting rod 82 , and at least two bearings are fixedly installed at both ends of the piston 4 and fixedly support the connecting rod 82 .

[0048] The at least two bearings include a first bearing 84, a planar bearing housed at the upper end of the piston 4. A first bearing groove 43 is defined in the inner wall of the piston 4. The first bearing 84 is accommodated within this groove, and the first inner ring 840 of the first bearing 84 securely supports the connecting rod 82, providing tension for the connecting rod 82. Specifically, the first outer ring 841 of the first bearing 84 abuts the sidewall of the first bearing groove 43, and the first inner ring 840 abuts the first outer wall 820 of the connecting rod 82. The provision of the first bearing 84 between the piston 4 and the connecting rod 82 provides tension for the connecting rod 82, enabling it to maintain normal rotation while also providing a shock-absorbing function.

[0049] The at least two bearings include a second bearing 85, a deep groove ball bearing housed at the upper end of the piston 4. A second bearing groove 44 is defined in the inner wall of the piston 4. The second bearing 85 is accommodated within this groove, and the second inner ring 850 of the second bearing 85 securely supports the connecting rod 82, preventing it from swinging. The first bearing groove 43 communicates with the second bearing groove 44, and the first bearing 84 abuts the second bearing 85. Specifically, the first bearing groove 43 is located above and communicates with the second bearing groove 44. The second outer ring 851 of the second bearing 85 abuts the sidewall of the second bearing groove 44, while the second inner ring 850 of the second bearing 85 abuts the first outer wall 820 of the connecting rod 82. The top of the second bearing 85 (not shown) abuts the bottom of the first bearing 84. By placing the second bearing 85 between the piston 4 and the connecting rod 82, the connecting rod 82 is prevented from swinging, ensuring smoother high-speed rotation.

[0050] The at least two bearings include a third bearing 86, an angular contact ball bearing housed at the lower end of the piston 4. A third bearing groove 45 is defined in the inner wall of the piston 4, and a third annular groove 826 is defined at the lower end of the connecting rod 82. The third bearing 86 is housed in both the third bearing groove 45 and the third annular groove 826. The third inner ring 860 of the third bearing 86 securely supports the connecting rod 82, maintaining tension on the connecting rod 82. The first groove surface 450 of the third bearing groove 45 is flush with the second end surface 823 of the third annular groove 826, and the third bearing 86 abuts both the first groove surface 450 and the second end surface 823. Specifically, the third outer ring 861 of the third bearing 86 abuts both the inner wall of the third bearing groove 45 and the second outer wall 821 of the third annular groove 826. The upper end surface of the third bearing 86 abuts both the first groove surface 450 and the second end surface 823. By providing the third bearing 86 between the piston 4 and the connecting rod 82 , it is possible to ensure that the connecting rod 82 does not swing, while ensuring the tension of the connecting rod 82 .

[0051] A first boss 825 is provided at one end of the connecting rod 82. A backing ring 87 is disposed between the first boss 825 and the first bearing 84. The backing ring is sleeved on the connecting rod 82, with one end abutting the first boss 825 and the other end abutting the first bearing 84. Specifically, the first boss 825 is provided at the upper end of the connecting rod 82, and a fourth boss 870 is provided at the lower end of the backing ring 87. The fourth boss 870 abuts both the first inner ring 840 and the top of the first bearing 84. The upper end surface of the backing ring 87 abuts the first end surface 822 of the first boss 825. The use of the backing ring 87 bridges the gap between the first bearing 84 and the connecting rod 82, making the relative movement between the piston 4 and the connecting rod 82 more stable and improving the sealing performance to prevent oil leakage.

[0052] The stabilizing device also includes a limiter 88 and a locking member 89, which are fixedly connected to each other and are both mounted on the connecting rod 82. Specifically, both the limiter 88 and the locking member 89 have internal threads, corresponding to external threads on the second outer wall 821 of the connecting rod 82. The limiter 88 is fixedly connected to the connecting rod 82 via threads and abuts against the third bottom portion 862 of the third bearing 86. The locking member 89 is fixedly connected to the connecting rod 82 via threads, and the locking member 89 and the limiter 88 are fixedly connected via screws. The limiter 88 limits the position of the third bearing 86, ensuring its proper operation.

[0053] The hydraulic rivet gun of the present invention is also provided with a buffer device. Figures 7 to 9As shown, the buffer device includes a rivet screw 83 and an elastic member 833. One end of the elastic member 833 is connected to the connecting rod 82 and the other end is connected to the rivet screw 83. The driver 81 drives the connecting rod 82 to rotate, thereby driving the elastic member 833 to rotate, and the elastic member 833 drives the rivet screw 83 to slide up and down. By providing the elastic member 833 between the connecting rod 82 and the rivet screw 83, the high-speed rotation of the connecting rod 82 driven by the driver 81 is buffered, thereby achieving deceleration and ensuring the quality of the rivet. In addition, by providing the elastic member 833 instead of the reducer, the structure is simple and the weight of the hydraulic rivet gun itself is reduced.

[0054] A third boss 837 is provided at one end of the connecting rod 82 near the buffer device. One end of the elastic member 833 is engaged with the third boss 837, and the other end is fixedly connected to the upper end surface of the rivet screw 83. A bolt 345 is fixedly connected to the bottom of the connecting rod 82, and the third boss 837 is mounted on the bolt 345. The upper end of the elastic member 833 is engaged between the third boss 837 and the lower end surface of the connecting rod 82. The buffer device also includes a connecting sleeve 830, in which the elastic member 833 is accommodated. One end of the connecting sleeve 830 is rotatably mounted on the connecting rod 82, and the other end is slidably mounted on the rivet screw 83. The third boss 837 is accommodated in the connecting sleeve 830. Specifically, the interior of the connecting sleeve 830 is through-connected to form a third accommodating cavity 839, and the elastic member 833 is accommodated in the third accommodating cavity 839. The third boss 837 is in the shape of an elongated strip, and arcuate surfaces 845 are provided at both ends thereof. The arcuate surfaces 845 abut against the inner wall of the connecting sleeve 830 .

[0055] The buffer device also includes a pin 831. The rivet screw 83 is provided with a first through-hole 834, and the connecting sleeve 830 is provided with a pair of waist-shaped through-holes 835 symmetrically arranged along the axis of the rivet screw 83. The pin 831 is received in the first through-hole 834, with its ends respectively received in the pair of waist-shaped through-holes 835. The pin 831 and the rivet screw 83 are loosely fitted. When the elastic member 833 drives the rivet screw 83 to slide up and down within the connecting sleeve 830, the latch 831, driven by the rivet screw 83, can slide within the waist-shaped through-holes 835. The distance the rivet screw 83 slides within the connecting sleeve 830 is equal to the distance the latch 831 slides within the waist-shaped through-holes 835. When the rivet screw 83 is withdrawn, the pin 831 and the rivet screw 83 are able to move simultaneously under the action of the elastic member 833, buffering the rapid movement of the driver 81 and the connecting rod 82, ensuring smoother withdrawal of the rivet screw 83. At the same time, when the rivet gun rotates, there will be a downward pressure on the rivet. By inserting the pin 831 into the rivet screw 83, and accommodating the two ends of the pin 831 in the waist-shaped through hole 835 of the connecting sleeve 830, the pin 831 presses against the waist-shaped through hole 835, thereby ensuring the downward pressure of the rivet screw 83.

[0056] The buffer device also includes a retaining spring 832, which is mounted on the connecting sleeve 830 and connected to the pin 831. The pin 831 has arcuate slots 836 at both ends, into which the retaining spring 832 is removably engaged. The retaining spring 832 is made of spring steel and has a notch 838 for removal. When either end of the pin 831 is within the notch 838, the retaining spring 832 can be removed from the pin 831. The retaining spring 832 prevents the pin 831 from being ejected from the rivet screw 83 when the rivet screw 83 rotates, ensuring smooth riveting.

[0057] During operation, the driver 81 and the connecting rod 82 rotate at high speed, driving the rivet screw 83 to rotate into the rivet (not shown in the figure), and then the hydraulic oil is pressurized by the supercharger (not shown in the figure) and quickly rushes into the hydraulic oil pipe 80, pushing the piston 4 to move axially. The piston 4 drives the connecting rod 82 and the rivet screw 83 to move axially, completing the riveting process.

[0058] The present invention utilizes a first main seal 10 disposed on the first outer portion 40 of the piston 4 and connected to the cylinder body 6, and a second main seal 20 disposed on the inner side of the pressure ring 5 and connected to the piston 4. These seals can withstand high pressures when exposed to high-pressure oil, increasing the pressure rating from 25 MPa to 40 MPa, and provide a primary seal with excellent sealing performance. A first secondary seal 11 disposed on the first outer portion 40 of the piston 4 and connected to the cylinder body 6, and a second secondary seal 21 disposed on the inner side of the pressure ring 5 and connected to the piston 4, provide an excellent seal when exposed to low pressures. A third seal 12 disposed on the first outer portion 40 of the piston 4 and connected to the cylinder body 6 simultaneously seals hydraulic oil and gas, and provides a dust-proof function. The first and second static seals 30, 31, which are sleeved on the pressure ring 5 and abut against the cylinder body 6, improve the static sealing performance between the pressure ring 5 and the cylinder body 6, while maintaining a simple structure and ease of replacement. By arranging the first main seal 10, the second main seal 20, and the first static seal 30 close to the oil chamber 800, sealing is more immediate and effective. By providing multiple sealing elements, the gaps between the piston and cylinder body, the gaps between the piston and the pressure ring, and the gaps between the pressure ring and the cylinder body are effectively sealed layer by layer, extending the life of each sealing element, reducing the frequency of sealing element replacement, and improving the sealing performance, stability, and durability of the entire sealing device. By providing a first guide element 70 between the piston 4 and the cylinder body 6, and a second guide element 71 between the piston 4 and the pressure ring 5, friction between the piston 4 and the cylinder body 6, and between the piston 4 and the pressure ring 5 is prevented, protecting the cylinder body 6, piston 4, and the pressure ring 5 from damage. The provision of a dustproof element 72 prevents dust from entering the cylinder body and damaging the sealing elements, thereby extending the service life of the sealing elements.

[0059] The present invention also provides a second bearing 85 between the piston 4 and the connecting rod 82, preventing the connecting rod 82 from swinging and ensuring smoother high-speed rotation. A first bearing 84 between the piston 4 and the connecting rod 82 provides tension to the connecting rod 82, maintaining normal rotation and providing shock absorption. A third bearing 86 between the piston 4 and the connecting rod 82 prevents the connecting rod 82 from swinging while maintaining tension.

[0060] The utility model provides an elastic member 833 between the connecting rod 82 and the rivet screw 83 to buffer the high-speed rotation of the connecting rod 82 driven by the driver 81, thereby achieving deceleration and ensuring the quality of the rivet. In addition, by providing the elastic member 833 instead of the reducer, the structure is simple and the weight of the hydraulic rivet gun itself is reduced. By inserting the pin rod 831 into the rivet screw 83, and accommodating both ends of the pin rod 831 in the waist-shaped through hole 835 of the connecting sleeve 830, when the rivet screw 83 is withdrawn, the pin rod 831 and the rivet screw 83 can move simultaneously under the action of the elastic member 833, thereby buffering the rapid movement of the driver 81 and the connecting rod 82, and making the rivet screw 83 withdrawn more smoothly. When the rivet gun is rotated, there is a downward pressure on the rivet. By inserting the pin 831 into the rivet screw 83, and accommodating both ends of the pin 831 in the waist-shaped through hole 835 of the connecting sleeve 830, the pin 831 presses against the waist-shaped through hole 835, thereby ensuring the downward pressure of the rivet screw 83. The provision of the retaining spring 832 can prevent the pin 831 from being thrown out of the rivet screw 83 when the rivet screw 83 rotates, thereby ensuring the smooth progress of the riveting work.

[0061] The above embodiments merely illustrate several implementations of the present invention. While the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the present invention. It should be noted that a person skilled in the art would be able to make numerous variations and improvements without departing from the concept of the present invention, all of which fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be determined by the appended claims.

Claims

1. A stabilizing device for a hydraulic rivet gun, comprising a driver (81), a connecting rod (82) and a piston (4), wherein the piston (4) is slidably sleeved on the connecting rod (82), and the connecting rod (82) is fixedly connected to a rivet screw (83), and the driver (81) drives the connecting rod (82) to rotate in the piston (4), thereby driving the rivet screw (83) to rotate, characterized in that: The stabilizing device comprises at least two bearings, and the at least two bearings are arranged between the piston (4) and the connecting rod (82). The at least two bearings are fixedly mounted on both ends of the piston (4) and fixedly support the connecting rod (82).

2. The stabilizing device of the hydraulic rivet gun according to claim 1, characterized in that: The at least two bearings include a first bearing (84), which is a plane bearing and is accommodated at the upper end of the piston (4).

3. The stabilizing device of the hydraulic rivet gun according to claim 2, characterized in that: A first bearing groove (43) is formed on the inner wall of the piston (4), the first bearing (84) is accommodated in the first bearing groove (43), and the first inner ring (840) of the first bearing (84) fixedly supports the connecting rod (82) to provide tension for the connecting rod (82).

4. The stabilizing device of the hydraulic rivet gun according to claim 3, characterized in that: The at least two bearings include a second bearing (85), which is a deep groove ball bearing and is accommodated at the upper end of the piston (4).

5. The stabilizing device of the hydraulic rivet gun according to claim 4, characterized in that: A second bearing groove (44) is provided on the inner wall of the piston (4), the second bearing (85) is accommodated in the second bearing groove (44), and the second inner ring (850) of the second bearing (85) fixedly supports the connecting rod (82) to keep the connecting rod (82) stable and prevent it from swinging.

6. The stabilizing device of the hydraulic rivet gun according to claim 5, characterized in that: The first bearing groove (43) is communicated with the second bearing groove (44), and the first bearing (84) is in contact with the second bearing (85).

7. The stabilizing device of the hydraulic rivet gun according to claim 1, characterized in that: The at least two bearings include a third bearing (86), which is an angular contact ball bearing and is received at the lower end of the piston (4).

8. The stabilizing device of the hydraulic rivet gun according to claim 7, characterized in that: A third bearing groove (45) is provided on the inner wall of the piston (4), and a third annular groove (826) is provided on the lower end of the connecting rod (82). The third bearing (86) is accommodated in both the third bearing groove (45) and the third annular groove (826), and a third inner ring (860) of the third bearing (86) fixedly supports the connecting rod (82) to maintain the tension of the connecting rod (82).

9. The stabilizing device of the hydraulic rivet gun according to claim 8, characterized in that: The first groove surface (450) of the third bearing groove (45) is flush with the second end surface (823) of the third annular groove (826), and the third bearing (86) abuts against the first groove surface (450) and the second end surface (823) at the same time.

10. The stabilizing device of the hydraulic rivet gun according to claim 2, characterized in that: A first boss (825) is provided at one end of the connecting rod (82), and a backing ring (87) is provided between the first boss (825) and the first bearing (84). The backing ring is sleeved on the connecting rod (82) and has one end abutting against the first boss (825) and the other end abutting against the first bearing (84).

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