Differential for field monitoring radar antenna

Abstract

The utility model belongs to the technical field of differential mechanisms, and particularly relates to a differential mechanism for a field monitoring radar antenna, which comprises a driving part for providing driving force; the shell is used for installing the driving piece; the three-stage gear transmission structure is used for completing differential output of the driving force of the driving part through three-stage gear transmission; and the multiple hoisting assemblies can change the contact position between the hoisting machine and the shell through movement of the hoisting assemblies before the hoisting machine hoists and fixes the shell, so that the hook position and the contact position of the hoisting machine are kept consistent. The two-way screw rod drives the two moving parts to slide close to or far away from the third groove body by means of the two sections of threads with opposite rotating directions, and the two moving parts drive the two hanging rings to close to or far away from each other, so that the positions of the two hanging rings can be adjusted to the positions matched with the hooks, shell deviation caused by position difference is avoided, and the applicability of the device is improved.

Description

Technical Field

[0001] This utility model belongs to the field of differential technology, and in particular relates to a differential for field surveillance radar antennas. Background Technology

[0002] Differentials used in field surveillance radar antennas are typically used to adjust the movement of the antenna, enabling it to perform precise scanning or tracking in different directions.

[0003] When installing and fixing the differential for field surveillance radar antennas to the intended position, it is usually necessary to use a lifting ring installed on the differential housing for lifting before bolting to complete the installation and fixing. Since the lifting ring is fixed on the housing surface, its position cannot be changed. When the hook spacing of the crane and the lifting ring spacing are different, a certain offset will occur between the hooks. During subsequent installation and fixing, the position of the differential needs to be manually adjusted, which reduces the applicability of the device. Utility Model Content

[0004] The purpose of this invention is to provide a differential for field surveillance radar antennas to solve the problems mentioned in the background art, including:

[0005] A driving component, which provides driving force;

[0006] The housing, which is used to mount the drive components;

[0007] The three-stage gear transmission structure uses a three-stage gear transmission to achieve differential output of the driving force to the drive components;

[0008] Several lifting components are capable of changing the contact position between the crane and the outer shell by moving themselves before the crane lifts and fixes the outer shell, so that the position of the crane hook and the contact position are consistent.

[0009] Preferably, the outer shell has a plurality of third grooves, and part of the structure of the hoisting assembly is disposed in the third groove.

[0010] Preferably, the hoisting assembly includes:

[0011] A two-way lead screw, which is rotatably mounted in the third groove;

[0012] A rotating component that can drive a bidirectional lead screw to rotate;

[0013] Two movable parts are disposed within the third groove and are capable of sliding along the third groove; the two movable parts are threadedly connected to a bidirectional lead screw.

[0014] Two lifting rings are fixedly installed on two moving parts respectively.

[0015] Preferably, the outer shell has a plurality of fourth grooves, and the fourth grooves are internally connected to the third grooves.

[0016] Preferably, the hoisting assembly further includes:

[0017] Several protrusions are fixedly mounted on two movable parts, and a portion of the protrusions is disposed in the fourth groove, and the protrusions can slide along the fourth groove.

[0018] Preferably, the outer shell surface has a plurality of first grooves, and a plurality of bolts are disposed through the first grooves, the bolts being able to install and fix the outer shell in the position to be used.

[0019] Preferably, the outer shell surface has a plurality of second grooves.

[0020] Preferably, a plurality of first plates are detachably mounted on the surface of the outer casing, and the positions of the plurality of first plates correspond to the three-stage gear transmission structure.

[0021] Preferably, the driving component is a motor that conforms to IEC standards.

[0022] Preferably, the housing adopts an IEC standard interface.

[0023] This application uses a wrench to rotate a rotating component, which drives a bidirectional lead screw to rotate. The bidirectional lead screw, through two threads with opposite directions, drives two moving parts to slide closer to or away from the third groove. The two moving parts drive two lifting rings closer to or away from each other, thereby allowing the position of the two lifting rings to be adjusted to the position of the matching hook, avoiding shell displacement caused by positional differences, and improving the applicability of the device. Attached Figure Description

[0024] Figure 1 This is an axial view of the present invention;

[0025] Figure 2 This is a bottom view of the present invention;

[0026] Figure 3 This is a right view of the present invention;

[0027] Figure 4 This is an internal sectional view of the present invention;

[0028] Figure 5 This is a partial exploded view of the present invention;

[0029] Figure 6 This utility model Figure 5 Enlarged structural diagram at point A in the middle;

[0030] Figure 7 This is a schematic diagram of the hoisting component structure of this utility model;

[0031] Figure 8 This is a structural diagram of the first stage gear of this utility model;

[0032] Figure 9 This is a structural diagram of the second-stage gear of this utility model;

[0033] Figure 10 This is a structural diagram of the third-stage gear of this utility model.

[0034] The markings in the diagram are as follows:

[0035] 100. Outer shell; 110. First groove; 120. Second groove; 130. First plate; 140. Third groove; 150. Fourth groove; 200. Drive component; 300. Three-stage gear transmission structure; 400. Lifting assembly; 410. Two-way lead screw; 420. Rotating component; 430. Moving component; 440. Lifting ring; 450. Protrusion. Detailed Implementation

[0036] The technical solutions of the embodiments of this application will be clearly described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application are within the scope of protection of this application.

[0037] In existing technology, when hoisting the differential of a field surveillance radar antenna, it is found that the differential will shift slightly when lifted by a crane, the cause of which is unknown. The installer needs to manually fine-tune the installation position of the differential. After long-term practice, it was discovered that the shift occurs when the position of the crane hook and the lifting ring 440 on the differential do not match. To solve this problem, this embodiment provides a differential for field surveillance radar antennas, such as... Figure 4 As shown, it includes: a housing 100 for mounting and fixing, a drive component 200 for providing driving force, a three-stage gear transmission structure 300 for generating differential speed, and several lifting components 400 capable of adjusting the lifting position.

[0038] like Figure 1 As shown, the outer shell 100 has a rectangular structure, as... Figure 1 and Figure 2As shown, the top and bottom edges of the outer casing 100 are provided with a plurality of first grooves 110. Each first groove 110 has a square structure, and at least one bolt is inserted through its interior. The bolt secures the outer casing 100 in its intended position. Furthermore, the first grooves 110 increase the contact area between the outer casing 100 and the outside environment, improving the heat dissipation effect of the device. The surface of the outer casing 100 is provided with a plurality of second grooves 120, which also increase the contact area between the outer casing 100 and the outside environment, further improving the heat dissipation effect of the device. The surface of the outer casing 100 is detachably mounted. There are several first plates 130, the positions of which correspond to the three-stage gear transmission structure 300. By disassembling the first plates 130, the three-stage gear transmission structure 300 can be quickly maintained. It is important to emphasize that the outer shell 100 adopts the IEC standard interface. If a non-standard interface is used, the motor can only be a non-standard motor of a specific brand and model customized by the turntable manufacturer, which has a long procurement cycle, high price, and the risk of being stuck. If the IEC standard interface is adopted, the motor and reducer are decoupled, and it can be adapted to any motor that conforms to the IEC standard at home and abroad, without the risk of production stoppage or being stuck.

[0039] like Figure 1 As shown, the drive unit 200 is bolted to the housing 100. The drive unit 200 is capable of providing driving force to the three-stage gear transmission structure 300, and is preferably a motor conforming to IEC standards.

[0040] like Figure 4 As shown, the three-stage gear transmission structure 300 is installed inside the housing 100. The differential output of driving force to the drive component 200 is achieved through the three-stage gear transmission. It is important to emphasize that the use of three-stage gears results in a more balanced load distribution between the tooth surfaces of each stage. The tooth surfaces are made of grade 5 high-precision gears with a hardness between 55-62 HRC. This high hardness reduces the load on the tooth surfaces, making the load more uniform and increasing the tooth surface hardness, thus making the gears more wear-resistant and extending their service life. Specifically:

[0041] like Figure 8 The diagram shows the structure of the first-stage gear. The first-stage gear is primarily for reduction. The first-stage gear pair is a helical cylindrical gear, belonging to the high-speed gear category. Due to the high rotational speed, involute cylindrical helical teeth are used to improve motion smoothness and reduce noise, thereby increasing the contact ratio. Because the reducer requires particularly high output torque, the gear design focuses on careful selection and design in terms of gear parameter calculations, materials, heat treatment, and manufacturing precision. The selections are as follows: Material: 20CrMnTi; Heat treatment: tempering, core hardness HRC28~32, carbonitriding of the teeth, tooth surface quenching: HRC55~60; Manufacturing precision: Grade 5.

[0042] like Figure 9 The diagram shows the structure of the second-stage gear. The main function of the second-stage gear pair is to reduce and amplify the output torque of the first-stage gear pair. Simultaneously, it needs to reverse the force transmission direction of the first-stage gear pair by 90° before outputting it to the third-stage gear pair. Under the condition of meeting the usage requirements, a spiral bevel gear pair (arc teeth) is most suitable for the intermediate stage of the reducer (because it has high transmission efficiency, smooth transmission, large transmitted torque, and small transmission ratio). Since the reducer requires a particularly large output torque, the gear design focuses on careful selection and design in terms of gear parameter calculation, materials, heat treatment, and manufacturing precision. The selections are as follows: Material: 20CrMnTi; Heat treatment: tempering, core hardness HRC28~32, carbonitriding of the teeth, tooth surface quenching: HRC58~62; Manufacturing precision: Grade 5.

[0043] like Figure 10 The diagram shows the structure of the third-stage gear. The third-stage gear is primarily for speed reduction, with a lower speed and higher torque. To improve tooth surface strength, a large module is used. To improve motion smoothness and reduce noise, involute cylindrical helical gears are used to increase contact ratio. The third-stage gear pair is the output stage of the reducer, employing a helical cylindrical gear pair for transmission. The output shaft features a large-diameter design to accommodate a large through-hole, facilitating the installation of antenna waveguides. Because the reducer requires exceptionally high output torque, the gear design emphasizes careful selection of gear parameters, materials, heat treatment, and manufacturing precision. The selections are as follows: Material: 20CrMnTi; Heat treatment: tempering, core hardness HRC28~32, carbonitriding of teeth, tooth surface quenching: HRC58~62; Manufacturing precision: Grade 5.

[0044] Based on the reducer's technical specifications and torque transmission characteristics, a three-stage reduction structure is adopted to reduce the load on each gear tooth surface and improve gear life. The first-stage gears are cylindrical teeth, completing the first-stage reduction; the second-stage gears are bevel teeth, completing the second-stage reduction and 90° reversal; and the third-stage gears are cylindrical teeth, completing the third-stage reduction. To improve contact ratio, enhance motion smoothness, and reduce noise, all gears are helical teeth. Through this three-stage transmission mechanism, the horizontal input power from the motor is ultimately converted into vertical output.

[0045] like Figure 4 As shown, two lifting assemblies 400 are respectively installed at symmetrical positions on the top of the outer casing 100. Before the crane lifts and secures the outer casing 100, they can change the contact position between the crane and the outer casing 100 by moving themselves, ensuring that the hook position of the crane and the contact position remain consistent. Specifically, as shown... Figure 6As shown, the top of the outer casing 100 has a third groove 140, which is rectangular. A portion of the lifting assembly 400 is housed within the third groove 140. The lifting assembly 400 includes: a double-acting screw 410, a rotating component 420, two moving components 430, and two lifting rings 440. The double-acting screw 410 is a long rod with two opposing threads on its surface. It is rotatably mounted within the third groove 140 via bearings. The double-acting screw 410 penetrates the outer casing 100. When the double-acting screw 410 rotates, it drives the two moving components 430 to slide closer to or further away from the third groove 140 via the opposing threads. The rotating component 420 is preferably a hexagonal socket head cap, bolt head, etc. Rotating the rotating component 420 with a wrench drives the double-acting screw 410 to rotate. The two moving components 430 are cylindrical. The body is set inside the third groove 140 and can slide along the third groove 140. The two moving parts 430 and the bidirectional lead screw 410 are threadedly connected. When the two moving parts 430 slide closer or further away along the third groove 140, they can synchronously drive the two lifting rings 440 closer or further away, so that the position of the two lifting rings 440 can be adjusted to the position of the matching hook, avoiding the displacement of the outer shell 100 caused by the position difference. The two lifting rings 440 are circular and can accommodate the hook. They are fixedly installed on the two moving parts 430 respectively.

[0046] To prevent the weight on the lifting ring 440 from being applied to the double-acting lead screw 410 during lifting, thus avoiding deformation of the double-acting lead screw 410, a further solution is as follows: Figure 6 As shown, the outer casing 100 has several fourth grooves 150, which are internally connected to the third groove 140. The hoisting assembly 400 also includes several protrusions 450, which are cylindrical and are fixedly mounted on two moving parts 430. Parts of the protrusions 450 are located inside the fourth grooves 150 and can slide along the fourth grooves 150. When the lifting ring 440 is under force, the weight is sequentially transferred to the moving parts 430 and the protrusions 450. The protrusions 450 are supported by the fourth grooves 150, which prevents the weight from being transferred to the bidirectional lead screw 410 and increases the stability of the device.

[0047] The embodiments of this application have been described above with reference to the accompanying drawings. Unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other. This application is not limited to the specific embodiments described above. The specific embodiments described above are merely illustrative and not restrictive. Those skilled in the art can make many other forms under the guidance of this application without departing from the spirit and scope of the claims, and all of these forms are within the protection scope of this application.

Claims

1. A differential for a phased-array radar antenna, characterized in that, include: Drive element (200), which is used to provide driving force; Housing (100) for mounting drive unit (200); The three-stage gear transmission structure (300) completes the differential output of the driving force to the drive unit (200) through the three-stage gear transmission; Several lifting components (400) are capable of changing the contact position between the crane and the housing (100) by moving themselves before the crane lifts and fixes the housing (100), so that the hook position of the crane and the contact position are consistent.

2. The differential for a field monitor radar antenna of claim 1, wherein, The outer shell (100) has a plurality of third grooves (140), and part of the structure of the hoisting assembly (400) is disposed in the third grooves (140).

3. The differential for a field monitor radar antenna of claim 2, wherein, The hoisting assembly (400) includes: A two-way lead screw (410) is rotatably mounted in a third groove (140); The rotating component (420) can drive the bidirectional lead screw (410) to rotate; Two movable parts (430) are disposed in the third groove (140) and are slidable along the third groove (140), the two movable parts (430) and the bidirectional lead screw (410) are threadedly connected; Two lifting rings (440) are fixedly mounted on two movable parts (430).

4. The differential for a field monitor radar antenna of claim 3, wherein, The outer shell (100) has a plurality of fourth grooves (150), and the fourth grooves (150) are internally connected to the third grooves (140).

5. The differential for a field monitor radar antenna of claim 4, wherein, The hoisting assembly (400) also includes: Several protrusions (450) are fixedly mounted on two movable parts (430), and a portion of the protrusions (450) is disposed in the fourth groove (150). The protrusions (450) can slide along the fourth groove (150).

6. The differential for a phased monopulse radar antenna of claim 1, wherein, The outer shell (100) has a plurality of first grooves (110) on its surface. A plurality of bolts are inserted through the first grooves (110) and the bolts can install and fix the outer shell (100) in the position to be used.

7. The differential for a field monitor radar antenna of claim 1, wherein, The outer shell (100) has a plurality of second grooves (120) on its surface.

8. The differential for a field monitor radar antenna of claim 1, wherein, The outer shell (100) has several first plates (130) detachably mounted on its surface, and the positions of the several first plates (130) correspond to the three-stage gear transmission structure (300).

9. The differential for a field monitor radar antenna of claim 1, wherein, The drive unit (200) is a motor that conforms to IEC standards.

10. The differential for a phased monopulse radar antenna of claim 1, wherein, The housing (100) adopts an IEC standard interface.

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