Paver electric drive device and paver

Abstract

The utility model discloses a paving machine electric drive transmission device and paving machine, including motor, connecting disc, speed reducer casing, primary planetary carrier assembly, secondary planetary carrier assembly and output shaft, the motor is connected with the front end of speed reducer casing through connecting disc, the spline shaft of motor is engaged with primary planetary carrier assembly to realize first stage transmission, primary planetary carrier assembly is connected with secondary planetary carrier assembly to realize second stage transmission, the front end of secondary planetary carrier assembly is connected with output shaft, and the sprocket for connecting work device of output shaft end is used. The utility model discloses an integrated design of motor and speed reducer replaces traditional structure, reduces no -load loss, promotes energy efficiency, realizes more accurate control and faster response speed, and reduces maintenance cost.

Description

Technical Field

[0001] This utility model relates to an electric drive transmission device for a paver and a paver, belonging to the field of power devices for engineering machinery. Background Technology

[0002] In the field of construction machinery, the material conveying and distributing systems of pavers mostly adopt internal combustion engine drive, with power transmission relying on a combination of hydraulic pump, hydraulic motor, and reducer. However, this traditional structure has many limitations: on the one hand, the hydraulic system needs to continuously run the pump to maintain pressure, resulting in high energy consumption even during standby or low load, and issues such as oil flow resistance, leakage, and mechanical friction lead to significant energy loss and low energy efficiency; on the other hand, the hydraulic system is affected by oil temperature and pressure fluctuations, limiting control accuracy and response speed, making it difficult to meet the precise control requirements of paver operation.

[0003] Meanwhile, with the deepening of the national green development policy and increasingly stringent environmental protection requirements, the risk of oil leakage and pollution inherent in traditional hydraulic drive modes contradicts the trend of green transformation. Furthermore, the combined structure of hydraulic pumps, hydraulic motors, and reducers involves numerous components, not only occupying a large space but also increasing maintenance costs, thus hindering the development of pavers towards intelligence and information technology. Summary of the Invention

[0004] To address the problems existing in the prior art, this utility model provides an electric drive transmission device for a paver and a paver. By integrating the motor and reducer into a design that replaces the traditional structure, it reduces no-load losses, improves energy efficiency, achieves more precise control and faster response speed, and reduces maintenance costs.

[0005] To achieve the above objectives, this utility model employs an electric drive transmission device for a paver, comprising a motor, a connecting disc, a reducer housing, a primary planetary carrier assembly, a secondary planetary carrier assembly, and an output shaft; the motor is connected to the front end of the reducer housing via the connecting disc, the splined shaft of the motor meshes with the primary planetary carrier assembly to achieve the first stage of transmission, the primary planetary carrier assembly is connected to the secondary planetary carrier assembly to achieve the second stage of transmission, the secondary planetary carrier assembly is connected to the front end of the output shaft, and the end of the output shaft is used to connect to the sprocket of the working device.

[0006] As an improvement, the connecting disc is provided with multiple O-rings for sealing.

[0007] As an improvement, the end of the reducer housing is connected to the output end cover by bolts, and the output end cover is provided with a lip seal and an O-ring for sealing.

[0008] As an improvement, the middle section of the output shaft is provided with bearing I and bearing II. Bearing I is fixed by a nut and washer I, and bearing II is adjacent to the output end cover. A spacer and multiple adjusting shims are provided between bearing I and bearing II to adjust the gap between the two bearings.

[0009] As an improvement, the reducer housing is provided with a nameplate, oil level indicator and vent cap; the location for adding lubricating oil on the reducer housing is provided with a screw plug and washer II to achieve sealing; the bottom of the reducer housing is provided with a magnetic screw plug and washer II to adsorb metal wear particles in the lubricating oil.

[0010] As an improvement, the first-stage planetary carrier assembly includes a first-stage sun gear, three first-stage planet gears, a first-stage planetary carrier, a roller bearing without an outer ring I, and a retaining ring I;

[0011] The first-stage sun gear is arranged in the middle of the first-stage planetary gear carrier, and the three first-stage planetary gears mesh with the first-stage sun gear respectively; the outer ringless roller bearing I is installed in the first-stage planetary gear to support the radial load of the first-stage planetary gear; the retaining ring I is installed on the outer ringless roller bearing I to restrict the axial movement of the outer ringless roller bearing I.

[0012] The inner ring of the first-stage planetary gear carrier is tightly fitted with the gasket I.

[0013] As an improvement, the secondary planetary carrier assembly includes a secondary sun gear, four secondary planet gears, a secondary planetary carrier, a roller bearing without an outer ring II, and a retaining ring II;

[0014] The secondary sun gear is arranged in the middle of the secondary planetary gear carrier, and the four secondary planetary gears mesh with the secondary sun gear respectively; the outer ringless roller bearing II is installed in the secondary planetary gear to support the radial load of the secondary planetary gear; the retaining ring II is installed on the outer ringless roller bearing II to restrict the axial movement of the outer ringless roller bearing II.

[0015] The inner ring of the secondary planetary gear carrier is tightly fitted with the gasket II.

[0016] In a second aspect, this utility model also provides a paver, on which the aforementioned paver electric drive transmission device is installed.

[0017] Compared with the prior art, the beneficial effects of this utility model are:

[0018] (1) Reduce no-load loss and improve energy efficiency. The energy consumption of the motor is significantly reduced when it is in standby or low load state, while the traditional hydraulic system needs to keep the pump running continuously to maintain pressure, and additional energy loss occurs due to oil flow resistance, leakage and mechanical friction; at the same time, the motor and reducer adopt a coaxial integrated design, eliminating the need for couplings and other connecting structures, reducing rotational inertia and mechanical loss.

[0019] (2) Compact structure and high cost performance. The integrated design of the motor and reducer allows most of the heat generated by the high-speed rotation of the reducer gears to be discharged through the motor heat dissipation channel, eliminating the need for an additional independent heat dissipation system. This effectively simplifies the structure and achieves a compact layout while improving cost performance.

[0020] (3) Simplified component configuration and saved installation space. Compared with the traditional combination of hydraulic pump + motor, the motor drive scheme reduces the number of working parts; and the coaxial integration design of motor and reducer greatly shortens the axial length, further simplifying the overall structure and saving space for the overall layout.

[0021] (4) High control precision and fast response speed. The motor can achieve high-precision control of speed, position and torque through the encoder, while the hydraulic system is easily affected by oil temperature and pressure fluctuations, resulting in low control precision and slow response. This device has a significant advantage in control performance.

[0022] (5) Green and environmentally friendly, with no risk of oil pollution. The use of an electric motor drive system avoids pollution problems caused by hydraulic oil leakage, which is in line with the development trend of green transformation of equipment and meets environmental protection requirements. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0024] Figure 1 This is a schematic diagram of the structure of this utility model;

[0025] Figure 2 This is a schematic diagram of the exploded structure of this utility model;

[0026] Figure 3 This is a schematic diagram of the structure of the first-stage planetary carrier assembly of this utility model;

[0027] Figure 4 This is a schematic diagram of the structure of the secondary planetary carrier assembly of this utility model;

[0028] In the diagram: 1. Motor; 2. O-ring I; 3. Screw; 4. Connecting disc; 5. O-ring II; 6. First-stage planetary carrier assembly; 7. Second-stage planetary carrier assembly; 8. Nut; 9. Washer I; 10. Bearing I; 11. Adjusting shim I; 12. Adjusting shim II; 13. Adjusting shim III; 14. Spacer; 15. Nameplate; 16. Washer II; 17. Plug; 18. Gearbox housing; 19. Vent cap; 20. Output shaft; 21. Bearing II. 22. Lip seal; 23. O-ring III; 24. Output end cap; 25. Bolt; 26. Oil level indicator; 27. Magnetic plug; 28. Retaining ring I; 29. ​​Roller bearing without outer ring I; 30. First-stage sun gear; 31. First-stage planetary gears; 32. Washer I; 33. First-stage planetary gear carrier; 34. Retaining ring II; 35. Second-stage sun gear; 36. Roller bearing without outer ring II; 37. Washer II; 38. Second-stage planetary gears; 39. Second-stage planetary gear carrier. Detailed Implementation

[0029] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of this application will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the embodiments and specific features in the embodiments are detailed descriptions of the technical solutions of this application, rather than limitations thereof. In the absence of conflict, the embodiments and technical features in the embodiments can be combined with each other.

[0030] like Figures 1-4 As shown, an electric drive transmission device for a paver includes a motor 1, a connecting plate 4, a reducer housing 18, a primary planetary carrier assembly 6, a secondary planetary carrier assembly 7, and an output shaft 20.

[0031] The motor 1 is connected to the front end of the reducer housing 18 via the connecting plate 4 and fixed with screws 3 to form a coaxial structure. The splined shaft of the motor 1 is directly embedded in the first-stage sun gear 30 of the first-stage planetary carrier assembly 6 for meshing. The first-stage reduction is completed through the meshing of the evenly distributed first-stage planetary gears 31 and the first-stage sun gear 30. The output end of the first-stage planetary carrier assembly 6 is rigidly connected to the second-stage sun gear 35 of the second-stage planetary carrier assembly 7. The second-stage reduction is achieved through the second-stage planetary gear 38. The two-stage transmission ratio is optimized and matched to meet the low speed and high torque requirements of the paving device. The output end of the second-stage planetary carrier assembly 7 is connected to the front end of the output shaft 20 via a key to transmit power. The end of the output shaft 20 is provided with a flange structure adapted to the sprocket of the paving device to realize direct power output.

[0032] In some embodiments, such as Figure 2As shown, the connecting disc 4 is sealed using O-ring I 2 and O-ring II 5. O-ring I 2 is used to seal the connecting disc 4 and the motor 1, and O-ring II 5 is used to seal the connecting disc 4 and the reducer housing 18. This improves the sealing performance of the connection surfaces between the connecting disc 4 and the motor 1, and between the connecting disc 4 and the reducer housing 18. It can effectively prevent liquids, gases or dust from leaking through the gaps, avoid the overall sealing performance degradation caused by the failure of a single seal, and significantly reduce the risk of internal components of the equipment being corroded by external impurities or internal media leaking out.

[0033] In some embodiments, such as Figure 2 As shown, the end of the reducer housing 18 is connected to the output end cover 24 by bolts 25, and the output end cover 24 is sealed with a lip seal 22 and an O-ring Ⅲ 23. On the one hand, the bolt connection ensures a stable connection between the reducer housing 18 and the output end cover 24, and is easy to disassemble and assemble, facilitating quick opening of the end cover for internal component inspection or replacement during later maintenance, thus meeting the regular maintenance needs after frequent paver operation; on the other hand, the lip seal 22 and the O-ring Ⅲ 23 form a double seal, which can effectively prevent external dust, mud and other impurities from entering the reducer (avoiding wear on gears, bearings and other components), and also prevent internal lubricating oil leakage. This ensures the stable operation of the transmission system in the harsh environment of paving operations (high vibration, multiple pollutants), significantly reduces the risk of failure due to seal failure, and simplifies the maintenance process and reduces downtime losses.

[0034] In some embodiments, such as Figure 2 As shown, the middle section of the output shaft 20 is provided with bearing I10 and bearing II21. Through the dual support of bearing I10 and bearing II21, the radial load of the middle section of the output shaft 20 can be effectively distributed, reducing swaying and vibration during high-speed rotation and ensuring the smoothness of power transmission. The bearing I10 is fixed by nut 8 and washer I9. The bearing II21 is close to the output end cover 24. A spacer 14 and adjusting shims I11, II12 and III13 are provided between the bearing I10 and bearing II21. By fixing bearing I10 with nut and washer, and combining bearing II21 close to the output end cover 24, the axial displacement of the bearing can be precisely limited, avoiding abnormal wear caused by force deviation. Meanwhile, the combination design of the spacer and multiple sets of adjusting shims can flexibly adjust the gap between the two bearings, which can not only compensate for assembly errors and dimensional changes caused by thermal expansion and contraction of components, but also ensure that the bearings are in the best working condition, reduce friction loss, and extend service life. The overall structure takes into account both the convenience of installation and the operability of later maintenance, providing a reliable guarantee for the long-term and efficient operation of the output shaft 20.

[0035] In some embodiments, such as Figure 2As shown, the reducer housing 18 is provided with a nameplate 15 for displaying parameter information, an oil level gauge 26 for monitoring oil level, and a vent cap 19 for balancing pressure. After adding lubricating oil, a gasket II 16 and a screw plug 17 are used for sealing. At the bottom of the housing, a gasket II 16 and a magnetic screw plug 27 are used to adsorb metal wear particles in the lubricating oil and keep the oil clean.

[0036] In some embodiments, such as Figure 3 As shown, the first-stage planetary carrier assembly 6 includes a first-stage sun gear 30, three first-stage planetary gears 31, a first-stage planetary carrier 33, a roller bearing without an outer ring I 29, and a retaining ring I 28. The first-stage sun gear 30 is arranged in the middle of the first-stage planetary carrier 33. The three first-stage planetary gears 31 are respectively mounted on the first-stage planetary carrier 33 and mesh with the first-stage sun gear 30. The use of three first-stage planetary gears 31 can evenly distribute the load, improving transmission stability and load-bearing capacity. The roller bearing without an outer ring I 29 is installed inside the first-stage planetary gears 31 to support the radial load of the first-stage planetary gears 31, while effectively saving installation space and making the overall structure more compact. The retaining ring I 28 is installed on the roller bearing without an outer ring I 29 to limit the axial movement of the roller bearing without an outer ring I 29, preventing bearing displacement due to vibration, etc., and ensuring transmission accuracy. The inner ring of the first-stage planetary carrier 33 and the gasket I... The 32-tight fit allows for precise adjustment of the axial distance between the gear and the second-stage sun gear 35, adapting to the connection with the second-stage planetary carrier assembly 7, ensuring smooth connection of each stage of transmission, reducing operational wear, and extending service life.

[0037] In some embodiments, such as Figure 4As shown, the secondary planetary carrier assembly 7 includes a secondary sun gear 35, four secondary planetary gears 38, a secondary planetary carrier 39, a roller bearing II without outer ring 36, and a retaining ring II 34. The secondary sun gear 35 is arranged in the middle of the secondary planetary carrier 39, and the four secondary planetary gears 38 mesh with the secondary sun gear 35 respectively. Compared with three primary planetary gears 31, the meshing of four secondary planetary gears 38 with the secondary sun gear 35 can further distribute the load during the transmission process, improve the load-bearing capacity of the secondary transmission, adapt to the increased torque demand after the primary reduction, and ensure more stable and reliable transmission. The roller bearing II without outer ring 36 is installed inside the secondary planetary gears 38, effectively supporting the diameter of the secondary planetary gears 38. While bearing the load, the outer ring structure is omitted, saving installation space and making the structure of the secondary planetary carrier assembly 7 more compact, adapting to the limited layout space inside the paver; the retaining ring II 34 is installed on the outer ringless roller bearing II 36, and the retaining ring II 34 can firmly restrict the axial movement of the outer ringless roller bearing II 36, preventing it from shifting in the vibration environment of the equipment operation, ensuring the meshing accuracy and operational stability of the secondary planetary gears; the inner ring of the secondary planetary gear carrier 39 is tightly fitted with the shim II 37, which can accurately adjust the axial distance between it and the output shaft 20, making the connection between the secondary planetary carrier assembly 7 and the output shaft 20 and other subsequent components smoother, reducing mechanical wear during operation, and extending the service life of the overall device.

[0038] In some embodiments, the transmission ratio i1 of the first-stage planetary carrier assembly 6 is Z1÷Z2+1, where Z1 is the total number of teeth of the three first-stage planetary gears 31 in the first-stage planetary carrier assembly 6, and Z2 is the number of teeth of the first-stage sun gear 30.

[0039] The transmission ratio i2 of the secondary planetary carrier assembly 7 is i2 = Z3 ÷ Z4 + 1, where Z3 is the total number of teeth on the four secondary planetary gears 38 in the secondary planetary carrier assembly 7, and Z4 is the number of teeth on the secondary sun gear 35; the total transmission ratio i of the reducer is i = i1 × i2. By clearly defining the transmission ratio i1 = Z1 ÷ Z2 + 1 of the primary planetary carrier assembly 6 and the transmission ratio i2 = Z3 ÷ Z4 + 1 of the secondary planetary carrier assembly 7, and then achieving precise superposition of the two-stage reduction using the total transmission ratio i = i1 × i2, the high speed and low torque output of the motor can be efficiently converted into the low speed and high torque required by the paver's working device, perfectly matching the power requirements of the material conveying and distributing system to overcome high resistance operations. Structurally, considering the different numbers of primary and secondary planetary gears (three and four respectively), the transmission ratio is calculated based on the proportion of their respective teeth, which can balance the force on each stage of the planetary gears, preventing premature wear of a certain stage due to excessive load, and extending the service life of the overall reducer.

[0040] Finally, in a second aspect, this utility model also provides a paver equipped with the aforementioned electric drive transmission device. The two-stage precision reduction design of the electric drive transmission device can stably output the low speed and high torque required for paving operations, ensuring that the material conveying and distribution system maintains a uniform conveying speed and paving force when handling different materials such as asphalt and water-stabilized materials. This reduces road surface smoothness deviations caused by power fluctuations and improves construction quality. Replacing the traditional hydraulic drive system eliminates energy losses from components such as hydraulic pumps and pipelines, improving transmission efficiency and reducing overall machine fuel consumption. It also eliminates the risk of hydraulic oil leakage, reduces pollution at construction sites, meets green engineering standards, and is suitable for municipal and highway projects with stringent environmental requirements. Maintenance is more convenient, component lifespan is longer, and downtime and maintenance costs are reduced. Furthermore, it better adapts to intelligent development, making the equipment more advantageous.

[0041] Furthermore, those skilled in the art will understand that although some embodiments described herein include certain features found in other embodiments but not others, combinations of features from different embodiments are also within the scope of protection of this utility model and form different embodiments. For example, in the embodiments described above, those skilled in the art can use them in combination based on known technical solutions and the technical problems to be solved by this application.

Claims

1. An electric drive transmission device for a paver, characterized in that, It includes a motor (1), a connecting plate (4), a reducer housing (18), a first-stage planetary carrier assembly (6), a second-stage planetary carrier assembly (7), and an output shaft (20); the motor (1) is connected to the front end of the reducer housing (18) through the connecting plate (4), the spline shaft of the motor (1) meshes with the first-stage planetary carrier assembly (6) to achieve the first stage of transmission, the first-stage planetary carrier assembly (6) is connected to the second-stage planetary carrier assembly (7) to achieve the second stage of transmission, the second-stage planetary carrier assembly (7) is connected to the front end of the output shaft (20), and the end of the output shaft (20) is used to connect to the sprocket of the working device.

2. The electric drive transmission device for a paver according to claim 1, characterized in that, The connecting disc (4) is provided with multiple O-rings for sealing.

3. The electric drive transmission device for a paver according to claim 1, characterized in that, The end of the reducer housing (18) is connected to the output end cover (24) by bolts (25), and the output end cover (24) is provided with a lip seal (22) and an O-ring for sealing.

4. The electric drive transmission device for a paver according to claim 1, characterized in that, The middle section of the output shaft (20) is provided with bearing I (10) and bearing II (21). Bearing I (10) is fixed by nut (8) and washer I (9). Bearing II (21) is close to the output end cover (24). A spacer (14) and multiple adjusting shims are provided between bearing I (10) and bearing II (21) to adjust the gap between the two bearings.

5. The electric drive transmission device for a paver according to claim 1, characterized in that, The reducer housing (18) is provided with a nameplate (15), an oil level indicator (26) and a vent cap (19); the reducer housing (18) is provided with a screw plug (17) and a washer II (16) at the lubricating oil addition position to achieve sealing; the reducer housing (18) is provided with a magnetic screw plug (27) and a washer II (16) at the bottom to adsorb metal wear particles in the lubricating oil.

6. The electric drive transmission device for a paver according to claim 1, characterized in that, The primary planetary carrier assembly (6) includes a primary sun gear (30), three primary planetary gears (31), a primary planetary carrier (33), a roller bearing without an outer ring I (29), and a retaining ring I (28); The first-stage sun gear (30) is arranged in the middle of the first-stage planetary gear carrier (33), and the three first-stage planetary gears (31) mesh with the first-stage sun gear (30) respectively; the outer ringless roller bearing I (29) is installed inside the first-stage planetary gear (31) to support the radial load of the first-stage planetary gear (31), and the retaining ring I (28) is installed on the outer ringless roller bearing I (29) to restrict the axial movement of the outer ringless roller bearing I (29); The inner ring of the first-stage planetary gear carrier (33) is tightly fitted with the gasket I (32).

7. The paver electric drive transmission device according to claim 1, characterized in that, The secondary planetary carrier assembly (7) includes a secondary sun gear (35), four secondary planetary gears (38), a secondary planetary carrier (39), a roller bearing without an outer ring II (36), and a retaining ring II (34); The secondary sun gear (35) is arranged in the middle of the secondary planetary gear carrier (39), and the four secondary planetary gears (38) mesh with the secondary sun gear (35) respectively; the outer ringless roller bearing II (36) is installed in the secondary planetary gear (38) to support the radial load of the secondary planetary gear (38), and the retaining ring II (34) is installed on the outer ringless roller bearing II (36) to restrict the axial movement of the outer ringless roller bearing II (36); The inner ring of the secondary planetary gear carrier (39) is tightly fitted with the gasket II (37).

8. A paver, characterized in that, The paver is equipped with the paver electric drive transmission device according to any one of claims 1-7.

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