Differential transmission system of tension roller set of withdrawal and straightening machine

Abstract

The utility model discloses a tension roller group differential transmission system of a withdrawal and straightening machine, which relates to the technical field of strip steel processing, and particularly comprises an outlet tension roller group and an inlet tension roller group which are positioned at two ends of the withdrawal and straightening machine, and the side edges of the outlet tension roller group and the inlet tension roller group are respectively provided with a differential speed regulating mechanism; the device further comprises a curvature extending mechanism and a main power driving mechanism, the main power driving mechanism is in transmission connection with the two differential speed regulating mechanisms, and the curvature extending mechanism is in transmission connection with the main power driving mechanism. The differential speed regulating mechanisms are respectively arranged in the tension roller groups at the inlet and the outlet of the withdrawal and straightening machine, the curvature extension mechanism and the main power driving mechanism are arranged in a matched manner, and the transmission shafts are in transmission connection, so that the transmission system of the tension roller groups of the whole withdrawal and straightening machine can form a closed-loop system; the speed difference between the tension roller sets is constant, the tension can be stably controlled, and the tension and the ductility are reliably guaranteed.

Description

Technical Field

[0001] The utility model relates to the technical field of strip steel processing, in particular to a tension roller group differential transmission system of a straightening machine. Background Art

[0002] In the production and processing of strip steel, eliminating the internal stress of the strip steel is an extremely important link. At present, the tension required for the straightening machine to straighten the strip steel is achieved by increasing the tension between the inlet and outlet tension roller groups of the straightening machine; and the elongation of the strip steel is also obtained by controlling the speed difference between the inlet and outlet tension roller groups. The tension roller group is driven and controlled by the transmission system. The tension and speed provided play a decisive role in ensuring the stability of the tension and elongation of the strip steel during the straightening process.

[0003] The traditional tension roller drive form is an independent single-roller transmission, which will lead to unstable tension of the straightening machine and insufficient precision of strip elongation, making it difficult to ensure the quality of the strip.

[0004] Therefore, we designed a differential transmission system for the tension roller group of the straightening machine. Utility Model Content

[0005] In view of the deficiencies of the prior art pointed out in the above background technology, the utility model provides a tension roller group differential transmission system of a tension straightening machine.

[0006] The utility model discloses a tension roller group differential transmission system of a straightening machine, comprising an outlet tension roller group and an inlet tension roller group located at both ends of the straightening machine, wherein the sides of the outlet tension roller group and the inlet tension roller group are respectively provided with a set of differential speed regulating mechanisms; further comprising a curvature extension mechanism and a main power driving mechanism, wherein the main power driving mechanism is transmission-connected with the two sets of differential speed regulating mechanisms, and the curvature extension mechanism is transmission-connected with the main power driving mechanism.

[0007] Furthermore, the outlet tension roller group consists of an outlet tension roller A and an outlet tension roller B, and the inlet tension roller group consists of an inlet tension roller A and an inlet tension roller B.

[0008] Furthermore, the differential speed regulating mechanism corresponding to the outlet tension roller group is composed of a reduction box C, a motor C and a reduction box E, and the differential speed regulating mechanism corresponding to the inlet tension roller group is composed of a reduction box D, a motor C and a reduction box F.

[0009] Furthermore, the main power driving mechanism is composed of a motor B and a reduction box A, and the reduction box A has the same structure as the reduction boxes E and F.

[0010] Furthermore, the curvature extension mechanism is composed of a reduction box B and a motor A. The reduction box B has the same structure as the reduction box C and the reduction box D, and they are all ordinary three-stage gear reducers.

[0011] Furthermore, the reducer A includes gear A, gear B and a planetary gear mechanism. The planetary gear mechanism is composed of a ring gear, a sun gear and a planetary gear assembly. A tooth groove is provided around the circumference of the outer side of the ring gear. The gear A is meshed with the gear B for transmission. The gear B is meshed with the tooth groove on the outer side of the ring gear. The sun gear is located in the middle of the inner side of the ring gear. The planetary gears in the planetary gear assembly are distributed on the outer side of the sun gear and are meshed with the ring gear and the sun gear at the same time.

[0012] Furthermore, the motor B is the main power motor, and the output shaft of the motor B is transmission-connected to the central axis of the gear A in the reduction box A, the central axis of the sun gear in the planetary gear mechanism in the reduction box A is transmission-connected to the output shaft of the reduction box B, and the input shaft of the reduction box B is transmission-connected to the output shaft of the motor A, and the central axis of the gear B in the reduction box A and the center position of the planetary wheel bracket of the planetary wheel assembly in the reduction box A are respectively installed with a transmission shaft B and a transmission shaft D through a coupling.

[0013] Furthermore, the motors C in the two sets of differential speed regulating mechanisms are both AC variable frequency motors, and the motors C in the two sets of differential speed regulating mechanisms are respectively connected to the input shafts of the corresponding reducers C and D, and the output shafts of the reducers C and D are respectively connected to the central shafts of the sun gears in the planetary gear mechanisms in the reducers E and F. The ends of the central shafts of the gears A in the reducers E and F are respectively installed with transmission shafts A and transmission shafts C through couplings, and the transmission shafts A and B, as well as the transmission shafts C and D, are meshed and driven by bevel gears.

[0014] Furthermore, a transmission shaft E is installed on the shaft of the gear B in the reduction box E, and the end of the transmission shaft E is transmission-connected to the end of the outlet tension roller A through a coupling. A transmission shaft F is installed on the planetary gear bracket of the planetary gear assembly in the reduction box E, and the end of the transmission shaft F is transmission-connected to the end of the outlet tension roller B through a coupling.

[0015] Furthermore, a transmission shaft H is installed on the shaft of the gear B in the reduction box F, and the end of the transmission shaft H is connected to the end of the entrance tension roller B through a coupling. A transmission shaft G is installed on the planetary gear bracket of the planetary gear assembly in the reduction box F, and the end of the transmission shaft G is connected to the end of the entrance tension roller A through a coupling.

[0016] Compared with the prior art, the beneficial effects of the utility model are as follows:

[0017] The utility model arranges a set of differential speed regulating mechanisms inside the tension roller groups at the inlet and outlet of the tension straightening machine respectively to match and compensate the torque between the tension roller groups. When the factors such as the roller surface roughness or the roller diameter of the tension roller change, the rotation speed of the roller can be adjusted in real time through the real-time rotation speed regulation of the torque motor, so as to achieve the purpose of torque balance between the inlet and outlet tension rollers and improve the running stability of the tension straightening machine. At the same time, in conjunction with the curvature extension mechanism and the main power driving mechanism, the transmission connection is carried out through each transmission shaft, so that the transmission system of the tension roller group of the entire tension straightening machine can form a closed-loop system, so that the speed difference between the tension roller groups is constant, the tension can be stably controlled, and the tension and elongation are reliably guaranteed. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The drawings described herein are used to provide a further understanding of the present application and constitute a part of the present application. The illustrative embodiments of the present application and their descriptions are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0019] Figure 1 It is a schematic diagram of the structure of the utility model.

[0020] In the figure: 1. reduction box A; 101. gear A; 102. gear B; 103. ring gear; 104. sun gear; 105. planetary gear assembly; 2. reduction box B; 3. motor A; 4. motor B; 5. reduction box C; 6. reduction box D; 7. motor C; 8. reduction box E; 9. reduction box F; 10. transmission shaft A; 11. transmission shaft B; 12. transmission shaft C; 13. transmission shaft D; 14. transmission shaft E; 15. outlet tension roller A; 16. transmission shaft F; 17. outlet tension roller B; 18. transmission shaft G; 19. inlet tension roller A; 20. transmission shaft H; 21. inlet tension roller B. DETAILED DESCRIPTION

[0021] The following will disclose multiple embodiments of the utility model with diagrams. For the purpose of clear description, many physical details will be described together in the following description. However, it should be understood that these physical details should not be used to limit the utility model. In other words, in some embodiments of the utility model, these physical details are not necessary. In addition, for the purpose of simplifying the diagram, some conventional structures and components will be depicted in a simple schematic manner in the diagram.

[0022] Example

[0023] In view of the problem that the current traditional tension roller drive form is an independent single roller transmission, which will lead to unstable tension of the straightening machine, insufficient elongation accuracy of the strip, and difficulty in ensuring the quality of the strip, we have developed a tension roller group differential transmission system for the straightening machine that can make the speed difference between the tension roller groups constant, the tension can be stably controlled, and the tension and elongation can be reliably guaranteed. The specific solution is as follows:

[0024] like Figure 1 As shown, the utility model discloses a tension roller group differential transmission system of a straightening machine, comprising an outlet tension roller group and an inlet tension roller group located at both ends of the straightening machine, specifically, the outlet tension roller group is composed of an outlet tension roller A15 and an outlet tension roller B17, and the inlet tension roller group is composed of an inlet tension roller A19 and an inlet tension roller B21; further, a set of differential speed regulating mechanisms are respectively arranged on the sides of the outlet tension roller group and the inlet tension roller group; specifically, the differential speed regulating mechanism corresponding to the outlet tension roller group is composed of a reduction box C5, a motor C7 and reduction box E8, and the differential speed regulating mechanism corresponding to the entrance tension roller group is composed of reduction box D6, motor C7 and reduction box F9. Among them, the motor C7 in the two sets of differential speed regulating mechanisms are AC variable frequency motors, and their main function is to match and compensate the torque between the tension roller groups. Through the differential speed regulating mechanism, when the factors such as the roller surface roughness or the roller diameter of the tension roller change, the speed of the tension roller can be adjusted in real time through the motor C7, so as to achieve the purpose of tension roller torque balance and make the system more stable.

[0025] Among them, the differential transmission system of the tension roller group of the straightening machine also includes a curvature extension mechanism and a main power driving mechanism, and the main power driving mechanism is transmission connected to the two sets of differential speed regulating mechanisms, and the curvature extension mechanism is transmission connected to the main power driving mechanism.

[0026] Specifically, the curvature extension mechanism is composed of a reduction box B2 and a motor A3, wherein the reduction box B2 has the same structure as the reduction box C5 and the reduction box D6, and they are all ordinary three-stage gear reducers.

[0027] In order to make the entire transmission system form a closed loop, the specific scheme is designed as follows:

[0028] Among them, the main power driving mechanism is composed of motor B4 and reduction box A1, and the reduction box A1 has the same structure as reduction box E8 and reduction box F9. Take reduction box A1 as an example: reduction box A1 includes gear A101, gear B102 and planetary gear mechanism inside, and the planetary gear mechanism is composed of ring gear 103, sun gear 104 and planetary gear assembly 105. The outer side of ring gear 103 is provided with tooth grooves around the circumference, gear A101 is meshed with gear B102 for transmission, gear B102 is meshed with the tooth groove on the outer side of ring gear 103, sun gear 104 is located in the middle of the inner side of ring gear 103, and the planetary gears in planetary gear assembly 105 are distributed on the outer side of sun gear 104 and are simultaneously connected with ring gear 103 and The sun gear 104 is meshed, wherein the motor B4 is the main power motor, which is used to uniformly drive the entire transmission system to operate. In order to achieve unified driving of the transmission system, the output shaft of the motor B4 is transmission-connected to the central axis of the gear A101 in the reduction box A1, and the central axis of the sun gear 104 in the planetary gear mechanism in the reduction box A1 is transmission-connected to the output shaft of the reduction box B2, and the input shaft of the reduction box B2 is transmission-connected to the output shaft of the motor A3. The central axis of the gear B102 in the reduction box A1 and the center position of the planetary wheel bracket of the planetary wheel assembly 105 in the reduction box A1 are respectively installed with the transmission shaft B11 and the transmission shaft D13 through the coupling.

[0029] The motor C7 in the two sets of differential speed regulating mechanisms is respectively connected to the input shafts of the corresponding reduction box C5 and reduction box D6, and the output shafts of the reduction box C5 and reduction box D6 are respectively connected to the central shaft of the sun gear 104 in the planetary gear mechanism in the reduction box E8 and reduction box F9, and the central shaft ends of the gear A101 in the reduction box E8 and reduction box F9 are respectively installed with the transmission shaft A10 and the transmission shaft C12 through couplings, wherein the transmission shaft A10 and the transmission shaft B11 as well as the transmission shaft C12 and the transmission shaft D13 are all driven by bevel gear meshing.

[0030] In addition, a transmission shaft E14 is installed on the shaft of the gear B102 in the reduction box E8, and the end of the transmission shaft E14 is connected to the end of the outlet tension roller A15 through a coupling. A transmission shaft F16 is installed at the center position of the planetary wheel bracket of the planetary wheel assembly 105 in the reduction box E8, and the end of the transmission shaft F16 is connected to the end of the outlet tension roller B17 through a coupling. In addition, a transmission shaft H20 is installed on the shaft of the gear B102 in the reduction box F9, and the end of the transmission shaft H20 is connected to the end of the inlet tension roller B21 through a coupling. A transmission shaft G18 is installed at the center position of the planetary wheel bracket of the planetary wheel assembly 105 in the reduction box F9, and the end of the transmission shaft G18 is connected to the end of the inlet tension roller A19 through a coupling.

[0031] To further explain, the export tension roller A15 and the export tension roller B17 are the roller groups for main power output. The power output by the export tension roller B17 drives the planetary wheel carrier in the planetary wheel assembly 105 inside the reduction box E8 through the transmission shaft F16, and the power output by the export tension roller A15 drives the gear B102 inside the reduction box E8 to rotate through the transmission shaft E14, so that part of its power is used to drive the ring gear 103 in the planetary gear assembly inside the reduction box E8 to rotate, and finally the sun gear 104 inside the reduction box E8 is output to the reduction box C5, and finally drives the motor C7. The other part of the power output by the export tension roller A15 is fed back to the gear B102 in the reduction box A1 through the transmission shaft A10 and the transmission shaft B11 to merge with the power output by the motor B4.

[0032] The power output by motor A3 drives the sun gear 104 in reduction box A1 through reduction box B2. It should be noted that: the power required by motor A3 is relatively small, and generally only a direction is required for the sun gear 104 in reduction box A1. At the same time, it should be emphasized that when there is no need to adjust the elongation rate and the torque and speed of the inlet and outlet tension roller groups, the motor A3 and the motor C7 are in the power generation state. When the tension balance and elongation of the inlet and outlet roller groups need to be adjusted, the motor A3 and the two motors C7 work according to actual needs, and the power output speed and torque of the planetary gear assembly 105 inside the corresponding reduction box can be adjusted through the reduction box B2, reduction box C5, or reduction box D6 set at the corresponding position.

[0033] After the power fed back by motor B4 and the outlet tension roller A15 merge, it drives the ring gear 103 in the planetary gear mechanism inside the reduction box A1 to rotate, and the power is output through the planetary wheel carrier in the planetary wheel assembly 105, and is input into the reduction box F9 after cooperation with the transmission shaft C12 and the transmission shaft D13. Part of the power drives the inlet tension roller B21 through the gear B102 inside the reduction box F9 and the transmission shaft H20, and the other part of the power is input into the ring gear 103 inside the reduction box F9 through the gear B102 in the reduction box F9 to drive it to rotate; and the output power of motor C7 connected to the reduction box D6 drives the sun gear 104 inside the reduction box F9 after passing through the reduction box D6, and its power is output through the planetary wheel carrier in the planetary wheel assembly 105, and drives the inlet tension roller A19 through the transmission shaft G18, thus completing the closed-loop design of the entire power transmission system.

[0034] The above description is only an embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent substitution, improvement, etc. made within the spirit and principle of the present invention shall be included in the scope of the claims of the present invention.

Claims

1. A tension roller differential transmission system for a tension straightening machine, comprising an outlet tension roller group and an inlet tension roller group located at both ends of the tension straightening machine, characterized in that: The sides of the outlet tension roller group and the inlet tension roller group are each provided with a set of differential speed regulating mechanisms; It also includes a curvature extension mechanism and a main power driving mechanism. The main power driving mechanism is transmission-connected with two sets of differential speed regulating mechanisms, and the curvature extension mechanism is transmission-connected with the main power driving mechanism.

2. A tension roller differential transmission system for a straightening machine according to claim 1, characterized in that: The exit tension roller group is composed of an exit tension roller A (15) and an exit tension roller B (17), and the entrance tension roller group is composed of an entrance tension roller A (19) and an entrance tension roller B (21).

3. A tension roller differential transmission system for a straightening machine according to claim 2, characterized in that: The differential speed regulating mechanism corresponding to the outlet tension roller group is composed of a reduction box C (5), a motor C (7) and a reduction box E (8), and the differential speed regulating mechanism corresponding to the inlet tension roller group is composed of a reduction box D (6), a motor C (7) and a reduction box F (9).

4. A tension roller differential transmission system for a straightening machine according to claim 1, characterized in that: The main power driving mechanism is composed of a motor B (4) and a reduction box A (1), and the reduction box A (1) has the same structure as the reduction box E (8) and the reduction box F (9).

5. The differential transmission system of the tension roller group of the straightening machine according to claim 1 is characterized in that: The curvature extension mechanism is composed of a reduction box B (2) and a motor A (3). The reduction box B (2) has the same structure as the reduction box C (5) and the reduction box D (6), and they are all ordinary three-stage gear reducers.

6. A tension roller differential transmission system for a tension straightening machine according to claim 4, characterized in that: The reduction box A (1) comprises a gear A (101), a gear B (102) and a planetary gear mechanism, wherein the planetary gear mechanism is composed of a ring gear (103), a sun gear (104) and a planetary gear assembly (105), wherein a tooth groove is arranged around the circumference of the outer side of the ring gear (103), wherein the gear A (101) meshes with the gear B (102) for transmission, wherein the gear B (102) meshes with the tooth groove on the outer side of the ring gear (103), wherein the sun gear (104) is located in the middle of the inner side of the ring gear (103), and wherein the planetary gears in the planetary gear assembly (105) are distributed on the outer side of the sun gear (104) and mesh with the ring gear (103) and the sun gear (104) at the same time.

7. A tension roller differential transmission system for a tension straightening machine according to claim 4, characterized in that: The motor B (4) is a main power motor, and the output shaft of the motor B (4) is drivingly connected to the gear A (101) in the reduction box A (1), the sun gear (104) in the planetary gear mechanism in the reduction box A (1) is drivingly connected to the output shaft of the reduction box B (2), and the input shaft of the reduction box B (2) is drivingly connected to the output shaft of the motor A (3), and the gear B (102) in the reduction box A (1) and the planetary wheel bracket of the planetary wheel assembly (105) in the reduction box A (1) are respectively installed with a transmission shaft B (11) and a transmission shaft D (13) through a coupling.

8. The differential transmission system of the tension roller group of the straightening machine according to claim 3 is characterized in that: The motors C (7) in the two sets of differential speed regulating mechanisms are both AC variable frequency motors. The motors C (7) in the two sets of differential speed regulating mechanisms are respectively connected to the input shafts of the corresponding reduction box C (5) and the reduction box D (6). The output shafts of the reduction box C (5) and the reduction box D (6) are respectively connected to the sun gear (104) in the planetary gear mechanism in the reduction box E (8) and the reduction box F (9). The gears A (101) in the reduction box E (8) and the reduction box F (9) are respectively installed with the transmission shaft A (10) and the transmission shaft C (12) through couplings. The transmission shaft A (10) and the transmission shaft B (11) as well as the transmission shaft C (12) and the transmission shaft D (13) are meshed and driven by bevel gears.

9. The differential transmission system of the tension roller group of the straightening machine according to claim 3 is characterized in that: A transmission shaft E (14) is mounted on the shaft of the gear B (102) in the reduction box E (8), and the end of the transmission shaft E (14) is transmission-connected to the end of the outlet tension roller A (15) via a coupling. A transmission shaft F (16) is mounted on the planetary gear support of the planetary gear assembly (105) in the reduction box E (8), and the end of the transmission shaft F (16) is transmission-connected to the end of the outlet tension roller B (17) via a coupling.

10. The differential transmission system of the tension roller group of the straightening machine according to claim 3 is characterized in that: A transmission shaft H (20) is mounted on the shaft of the gear B (102) in the reduction box F (9), and the end of the transmission shaft H (20) is transmission-connected to the end of the entrance tension roller B (21) via a coupling. A transmission shaft G (18) is mounted on the planetary gear support of the planetary gear assembly (105) in the reduction box F (9), and the end of the transmission shaft G (18) is transmission-connected to the end of the entrance tension roller A (19) via a coupling.

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