Double output heavy duty dynamic balancing machine gear box

Abstract

The utility model discloses a double output heavy load dynamic balancing machine gear box, specifically related to gear box technical field, including bottom plate, the bottom plate top is installed with installation box, the rear of inside installation box is provided with drive motor, the front of inside installation box is provided with electromagnetic clutch, the outside of electromagnetic clutch is provided with electromagnetic clutch protective cover, the front of right -hand member of bottom plate is provided with telescopic drive flange, the left end of telescopic drive flange is provided with dial, the front of auxiliary drive mechanism outer surface symmetry is installed with primary drive gear and secondary drive gear. The utility model discloses a double output heavy load dynamic balancing machine gear box, when using, electromagnetic clutch and double gear coordination have realized electromagnetic gear function, and two gears can be switched at will, do not interfere with each other, solve the problem that traditional head tank hangs single mode, convenient operation, adapt to different test scene demand.

Description

Technical Field

[0001] This utility model relates to the field of gearbox technology, and in particular to a dual-output heavy-duty dynamic balancing machine gearbox. Background Technology

[0002] As a core component of mechanical transmission systems, gearboxes are widely used in various mechanical equipment, especially in situations where it is necessary to change the transmission direction and adjust the torque. Dual-output gearboxes, due to their two output shafts, can drive multiple loads simultaneously (single-output shafts are mainly designed for easy gear shifting and have higher spindle precision). They have advantages such as high transmission efficiency and compact structure, and exhibit good applicability under heavy-load conditions.

[0003] In commercially available headstock applications, conventional headstock speed adjustment and gear shifting methods are relatively simple, making it difficult to meet the diverse speed range requirements of various tests. Furthermore, the operation is cumbersome, and the spindle accuracy is easily affected.

[0004] Some existing technologies lack gearbox structures that can achieve electromagnetic shifting, stepless speed regulation, and reasonable dual-gear matching to ensure spindle accuracy, thus addressing the above-mentioned problems. Therefore, it is necessary to develop a dual-output heavy-duty dynamic balancing machine gearbox to optimize the performance of the drive headstock on the market and meet the needs of testing and related industrial applications. Utility Model Content

[0005] The main objective of this invention is to provide a dual-output heavy-duty dynamic balancing machine gearbox, which can effectively solve the problem that some existing technologies lack a gearbox structure that can achieve electromagnetic shifting, stepless speed regulation, and reasonable dual-gear matching to ensure spindle accuracy.

[0006] To achieve the above objectives, the technical solution adopted by this utility model is as follows:

[0007] A dual-output heavy-duty dynamic balancing machine gearbox includes a base plate, a mounting box mounted on the top of the base plate, a drive motor disposed on the rear side inside the mounting box, an electromagnetic clutch disposed on the front side inside the mounting box, an electromagnetic clutch protective cover disposed on the outside of the electromagnetic clutch, a telescopic drive flange disposed on the front side of the right end of the base plate, a dial disposed on the left end of the telescopic drive flange, an auxiliary transmission mechanism disposed on the inner surface of the mounting box, and a primary drive gear and a secondary drive gear symmetrically mounted on the front side of the outer surface of the auxiliary transmission mechanism.

[0008] Preferably, the output end of the drive motor is connected to an electromagnetic clutch, and the electromagnetic clutch is adapted to and connected to the first-stage drive gear and the second-stage drive gear respectively through an auxiliary transmission mechanism.

[0009] Preferably, the primary drive gear and the secondary drive gear are connected to the telescopic drive flange via an auxiliary transmission mechanism.

[0010] Preferably, the electromagnetic clutch is used to control the power switching of the primary drive gear or the secondary drive gear, so as to realize the independent operation of the dual-speed transmission.

[0011] Preferably, the auxiliary transmission mechanism includes a first rotating shaft, a first pulley, a second pulley, a transmission belt, a second rotating shaft, and a bearing housing. The second rotating shaft is connected to a first-stage drive gear or a second-stage drive gear. The first pulley is fitted onto the first rotating shaft, the second pulley is fitted onto the left end of the second rotating shaft, the transmission belt is fitted between the first pulley and the second pulley, and the second rotating shaft is mounted on the inner surface of the mounting box via the bearing housing.

[0012] Preferably, the dial is used to assist in calibrating the installation and operating position of the telescopic drive flange, and a bracket is installed at the bottom of the telescopic drive flange.

[0013] Preferably, the transmission ratio of the first-stage drive gear is 1:2, and its maximum operating speed is 500 rpm; the transmission ratio of the second-stage drive gear is 1:1, and its maximum operating speed is 1000 rpm.

[0014] Compared with the prior art, the present invention has the following beneficial effects:

[0015] 1. This device achieves electromagnetic gear shifting function through the designed electromagnetic clutch (which works in conjunction with a dual-gear and a two-stage drive gear). It is easy to operate, and the two gears can be switched at will without interference. This solves the problem of the single gear shifting method of traditional headstock boxes, making it convenient to operate and adaptable to different test scenarios.

[0016] 2. Through the designed auxiliary transmission mechanism and its belt drive structure, this device achieves stable power transmission, reduces vibration interference from direct gear meshing, and further ensures the operating accuracy of the main shaft. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the overall structure of this utility model;

[0018] Figure 2 This is a schematic diagram of the local explosion effect structure of this utility model;

[0019] Figure 3 This is a partial structural diagram of the auxiliary transmission mechanism of this utility model;

[0020] Figure 4 This is a schematic diagram of the two-stage drive gear structure of this utility model.

[0021] In the diagram: 1. Drive motor; 2. Electromagnetic clutch; 3. Electromagnetic clutch protective cover; 4. First-stage drive gear; 5. Second-stage drive gear; 6. Telescopic drive flange; 7. Dial; 8. Base plate; 9. Mounting box; 10. Auxiliary transmission mechanism; 1001. Shaft 1; 1002. Pulley 1; 1003. Pulley 2; 1004. Transmission belt; 1005. Shaft 2; 1006. Bearing housing; 11. Bracket. Detailed Implementation

[0022] To make the technical means, creative features, objectives and effects of this utility model easier to understand, the present utility model will be further described below in conjunction with specific embodiments.

[0023] Example 1, as Figure 1 As shown, a dual-output heavy-duty dynamic balancing machine gearbox includes a base plate 8, a mounting box 9 mounted on the top of the base plate 8, a drive motor 1 located on the rear side inside the mounting box 9, an electromagnetic clutch 2 located on the front side inside the mounting box 9, an electromagnetic clutch protective cover 3 located on the outside of the electromagnetic clutch 2, a telescopic drive flange 6 located on the front side of the right end of the base plate 8, a dial 7 located on the left end of the telescopic drive flange 6, an auxiliary transmission mechanism 10 located on the inner surface of the mounting box 9, and a primary drive gear 4 and a secondary drive gear 5 symmetrically mounted on the front side of the outer surface of the auxiliary transmission mechanism 10.

[0024] In this embodiment, the drive motor 1 provides power output. By controlling the on / off state of the electromagnetic clutch 2, the power can be selectively transmitted to the primary drive gear 4 or the secondary drive gear 5. When the electromagnetic clutch 2 is engaged with the primary drive gear 4, the device operates at a transmission ratio of 1:2, with a maximum speed of 500 rpm. When the electromagnetic clutch 2 is engaged with the secondary drive gear 5, the device operates at a transmission ratio of 1:1, with a maximum speed of 1000 rpm.

[0025] For details, please refer to Figure 1 , Figure 2 and Figure 4 In this embodiment, the output end of the drive motor 1 is connected to the electromagnetic clutch 2, and the electromagnetic clutch 2 is adapted to and connected to the first-stage drive gear 4 and the second-stage drive gear 5 respectively through the auxiliary transmission mechanism 10.

[0026] The electromagnetic clutch 2 is a conventional electromagnetic clutch that is compatible with the power of the drive motor 1 in the existing technology. It achieves rapid engagement and switching with the first-stage drive gear 4 or the second-stage drive gear 5 through circuit control. It has a fast response speed and is easy to operate.

[0027] The protective cover 3 is made of metal, which can effectively prevent dust and impurities from entering the electromagnetic clutch and ensure its operational stability.

[0028] Further reference Figure 1 and Figure 4 In this embodiment, the primary drive gear 4 and the secondary drive gear 5 are connected to the telescopic drive flange 6 via the auxiliary transmission mechanism 10.

[0029] Further reference Figure 2 and Figure 4 In this embodiment, the electromagnetic clutch 2 is used to control the power switching of the first-stage drive gear 4 or the second-stage drive gear 5, so as to realize the independent operation of the dual-speed transmission.

[0030] Further reference Figure 1 and Figure 4 In this embodiment, the dial 7 is used to assist in calibrating the installation and operating position of the telescopic drive flange 6, and a bracket 11 is installed at the bottom of the telescopic drive flange 6.

[0031] Further reference Figure 1 and Figure 4 In this embodiment, the transmission ratio of the first-stage drive gear 4 is 1:2, and its maximum operating speed is 500 rpm; the transmission ratio of the second-stage drive gear 5 is 1:1, and its maximum operating speed is 1000 rpm.

[0032] This embodiment achieves electromagnetic gear shifting by designing an electromagnetic clutch 2, which works in conjunction with a dual-gear primary drive gear 4 and a secondary drive gear 5. This makes operation convenient, and the two gears can be switched freely without interference. This solves the problem of the traditional headstock gear shifting method being too simplistic, making it easy to operate and adaptable to different test scenarios.

[0033] Example 2: Based on Example 1, this example adds an optimized structure for power transmission stability. By setting an auxiliary transmission mechanism 10, the transmission efficiency and stability of power from the gearbox to the telescopic drive flange 6 can be improved.

[0034] For details, please refer to Figure 1 , Figure 3 and Figure 4 In this embodiment, the auxiliary transmission mechanism 10 includes a first rotating shaft 1001, a first pulley 1002, a second pulley 1003, a transmission belt 1004, a second rotating shaft 1005, and a bearing seat 1006. The second rotating shaft 1005 is connected to the first-stage drive gear 4 or the second-stage drive gear 5. The first pulley 1002 is sleeved on the first rotating shaft 1001, the second pulley 1003 is sleeved on the left end of the second rotating shaft 1005, and the transmission belt 1004 is sleeved between the first pulley 1002 and the second pulley 1003. The second rotating shaft 1005 is mounted on the inner surface of the mounting box 9 through the bearing seat 1006.

[0035] This embodiment achieves stable power transmission through the designed auxiliary transmission mechanism 10 and its belt drive structure, reduces vibration interference from direct gear meshing transmission, and further ensures the operating accuracy of the main shaft telescopic drive flange.

[0036] Example 3

[0037] This embodiment adds an optimized structure for spindle accuracy calibration and speed range expansion based on embodiment one. Through the stepless speed regulation function of the dial 7 and the drive motor 1, the spindle accuracy and speed adaptability are improved.

[0038] Specifically, the dial 7 has precise graduations on its surface, and its central axis coincides with the central axis of the telescopic drive flange 6. During installation or debugging, the concentricity deviation of the telescopic drive flange 6 can be observed through the dial 7, which is convenient for calibration.

[0039] The drive motor 1 adopts the variable frequency speed control motor in the existing technology, which, together with the controller, can realize stepless speed regulation from 0 to the corresponding gear's highest speed;

[0040] Furthermore, the telescopic drive flange 6 adopts an axially fine-adjustable structural design, which, combined with the calibration function of the dial 7, can precisely adjust its connection position with the test workpiece to ensure clamping accuracy.

[0041] The drive motor 1 supports stepless speed regulation and can be used with a dual-gear structure to achieve a wider range of speed adjustment.

[0042] The controller in this solution can be a frequency converter that is compatible with the drive motor 1 in the prior art, which can be used to control the rotation speed of the drive motor 1. Since it is a very mature product in the prior art, it will not be described in detail in this application.

[0043] It should be noted that the specific installation method, circuit connection method and control method of the drive motor 1 used in this utility model are all conventional designs, and will not be described in detail in this utility model.

[0044] The foregoing has shown and described the basic principles, main features, and advantages of this utility model. Those skilled in the art should understand that this utility model is not limited to the above embodiments. The embodiments and descriptions in the specification are merely illustrative of the principles of this utility model. Various changes and modifications can be made to this utility model without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claims. The scope of protection of this utility model is defined by the appended claims and their equivalents.

Claims

1. A dual-output heavy-duty dynamic balancing machine gearbox, comprising a base plate (8), characterized in that: The mounting box (9) is installed on the top of the base plate (8). A drive motor (1) is installed on the rear side inside the mounting box (9). An electromagnetic clutch (2) is installed on the front side inside the mounting box (9). An electromagnetic clutch protective cover (3) is installed on the outside of the electromagnetic clutch (2). A telescopic drive flange (6) is installed on the front side of the right end of the base plate (8). A dial (7) is installed on the left end of the telescopic drive flange (6). An auxiliary transmission mechanism (10) is installed on the inner surface of the mounting box (9). A first-stage drive gear (4) and a second-stage drive gear (5) are symmetrically installed on the front side of the outer surface of the auxiliary transmission mechanism (10).

2. The dual-output heavy-duty dynamic balancing machine gearbox according to claim 1, characterized in that: The output end of the drive motor (1) is connected to the electromagnetic clutch (2), and the electromagnetic clutch (2) is adapted to and connected to the first-stage drive gear (4) and the second-stage drive gear (5) respectively through the auxiliary transmission mechanism (10).

3. The dual-output heavy-duty dynamic balancing machine gearbox according to claim 1, characterized in that: The primary drive gear (4) and the secondary drive gear (5) are connected to the telescopic drive flange (6) via an auxiliary transmission mechanism (10).

4. The dual-output heavy-duty dynamic balancing machine gearbox according to claim 1, characterized in that: The electromagnetic clutch (2) is used to control the power switching of the first-stage drive gear (4) or the second-stage drive gear (5) to achieve independent operation of the dual-speed transmission.

5. The dual-output heavy-duty dynamic balancing machine gearbox according to claim 1, characterized in that: The auxiliary transmission mechanism (10) includes a first rotating shaft (1001), a first pulley (1002), a second pulley (1003), a transmission belt (1004), a second rotating shaft (1005), and a bearing seat (1006). The second rotating shaft (1005) is connected to a first-stage drive gear (4) or a second-stage drive gear (5). The first pulley (1002) is sleeved on the first rotating shaft (1001). The second pulley (1003) is sleeved on the left end of the second rotating shaft (1005). The transmission belt (1004) is sleeved between the first pulley (1002) and the second pulley (1003). The second rotating shaft (1005) is mounted on the inner surface of the mounting box (9) through the bearing seat (1006).

6. The dual-output heavy-duty dynamic balancing machine gearbox according to claim 1, characterized in that: The dial (7) is used to assist in calibrating the installation and operation position of the telescopic drive flange (6), and a bracket (11) is installed at the bottom of the telescopic drive flange (6).

7. The dual-output heavy-duty dynamic balancing machine gearbox according to claim 1, characterized in that: The transmission ratio of the first-stage drive gear (4) is 1:2, and its maximum operating speed is 500 rpm. The transmission ratio of the second-stage drive gear (5) is 1:1, and its maximum operating speed is 1000 rpm.

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