High-power, heavy-load planetary gear back-to-back test bench

Abstract

To solve the problem existing in a conventional planetary gear test bench that high machining cost of a transmission shaft prevents simulation of a test of a planetary gear box in a marine environment.SOLUTION: A driving device, a first coupling, a speed increasing machine, a second coupling, a rotating speed torque meter, and a planetary gear box back-to-back sealed power system are sequentially connected to each other. A clamping groove body is coaxially and externally fitted onto an axial positioning projection. A clamp assembly is internally fitted into an axial positioning recessed groove. A shaft segment is externally fitted onto the clamping groove body and clamps the clamping groove body and the axial positioning projection according to axial displacement provided by the clamping assembly. The clamping groove body generates radial displacement from the axial pushing effect of the clamping assembly, and is connected to an axial positioning recessed groove of another shaft segment in an expanded fitting state. A marine test assembly is installed onto an outer shell of a test planetary gear box to achieve simulation of a marine environment test. The present invention is used for a test of a planetary gear box with the full rotating speed and the full load.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a test bench, specifically to a heavy load planetary gear back-to-back test bench, which is used for full speed and full load testing of planetary gearboxes, and belongs to the field of planetary gear testing technology. [Background technology]

[0002] Planetary gear transmission is one of the important transmission forms of power transmission, and is relatively widely used in machines and mechanical equipment in the fields of automobiles, ships, space, aviation, petrochemicals, etc. Planetary gear transmission has the advantages of small volume, compact structure, high power density, large transmission ratio, high transmission efficiency, etc. Planetary gear transmission is not only applied to high rotation speed and high power, but also to low speed and large torque transmission devices, which can be applied to almost all power and rotation speed ranges, and has been increasingly widely used.

[0003] Since the gearbox is applied to various actual operating conditions after various tests and tests, each actual operating condition has its own characteristics, and these characteristics are also related to the service life and use effect of the gearbox. For example, in the marine field, the marine gearbox is the main propulsion transmission device of the marine power system, and has the functions of clutch, reduction and propeller thrust bearing. Especially in large marine equipment, the length of the transmission shaft of the transmission system is about 100 meters, about 200 meters, or even about 400 meters. Such a long main shaft is affected by the thrust between the propeller and seawater when transmitting power, and the main shaft and the gear of the gearbox need to withstand a heavy load. Therefore, the performance test of the transmission device is particularly important.

[0004] At present, in order to guarantee the coaxiality of such an extra-long transmission shaft during the production and processing process and to reduce the difficulty of processing, the transmission shaft is divided into multi-stage shafts, and the multi-stage shafts are connected by the method of spline insertion. For example, the disclosure number is CN102494886A, and the invention patent name is "Shaft penetration device for high-power planetary gearbox back-to-back experiment", and the multi-stage shafts in this invention patent are connected by spline. The spline teeth of the spline are uniformly distributed on the shaft, the force received is uniform, the weakening of the shaft is reduced, the stress concentration at the tooth root is relatively small, and the number of spline teeth makes the load capacity large and the neutrality and guiding properties relatively good, so that the spline connection method used between the multi-stage shafts can effectively solve the problem of the difficulty of processing the extra-long transmission shaft. However, since machining of the spline teeth and spline grooves requires the use of special equipment (e.g., spline shaft machining machine tools) and tools, the costs for both transmission testing and after the start of production of the transmission are very high.

[0005] In addition, in the testing process of the transmission used in large ships, the testing environment is only performed under normal operating conditions on land, and does not take into account that the ship is easily affected by salt fog in the seawater atmosphere when sailing on the ocean, and it is not possible to test the effect of salt fog on the planetary gear in the transmission. In the production process of the planetary gear, processing techniques such as anodizing, micro-arc oxidation, plating and coating have been used to improve the environmental adaptability of metal materials in the marine environment. However, even if the gears are treated as above, it is impossible to predict the adverse effects that may occur due to the synergistic effects of many factors during the actual sailing process of the transmission. For example, if the gearbox seal is not tight or there is a gap of 0.025-0.1 mm between the seal end cap and the case, fine gravel may enter the gearbox, affecting the meshing of the gears, causing seawater sputtering, raindrop erosion and other situations. After the corrosive medium enters and stays there (referring to the gear wheel tooth surface), its diffusion is restricted, which may lead to accelerated metal corrosion in the slits (referring to the tooth root or the area where tooth surface corrosion has already occurred). For example, if the service life of the gearbox is not timely discovered and accurately predicted, it will affect the safety of use of the transmission of the ship. Meanwhile, the traditional test bench cannot simulate the planetary gearbox test in the marine environment.

[0006] In summary, the conventional planetary gear test bench has problems such as the high machining cost of the transmission shaft and the inability to simulate the testing of the planetary gearbox in a marine environment. Summary of the Invention [Problem to be solved by the invention]

[0007] The present invention aims to solve the problems existing in the conventional planetary gear test bench, such as the high machining cost of the transmission shaft and the inability to simulate the test of the planetary gearbox in the marine environment, and further provides a high-power heavy-load planetary gear back-to-back test bench. [Means for solving the problem]

[0008] The technical solution of the present invention is a high-power heavy-load planetary gear back-to-back test stand, which includes a drive unit, a first shaft coupling, a speed increaser, a second shaft coupling and a rotation speed torque meter, which are connected in sequence from left to right, and further includes a planetary gearbox back-to-back sealed power system and a marine test assembly, and the planetary gearbox back-to-back sealed power system includes a third shaft coupling, a test planetary gearbox, a first interlocking mechanism, a torsion shaft assembly, an associated test gearbox, a fourth shaft coupling, a second interlocking mechanism and a loader, and the third shaft coupling, the test planetary gearbox, the first interlocking mechanism, the torsion shaft assembly, the associated test gearbox, the fourth shaft coupling, the second interlocking mechanism and the loader are connected in sequence from left to right, and the torsion shaft assembly includes a clamping groove, a clamp assembly and a plurality of shaft segments, and the adjacent two shafts are connected in sequence from left to right, and the torsion shaft assembly includes a clamping groove, a clamp assembly and a plurality of shaft segments. An axial positioning protrusion is machined on the right side of the left shaft member of the segment, and an axial positioning groove is machined on one end face corresponding to the axial positioning protrusion on the right shaft member, the clamping groove body is coaxially externally fitted onto the axial positioning protrusion, the clamp assembly is internally fitted into the axial positioning groove, the right shaft member is coaxially externally fitted onto the clamping groove body, and the clamping groove body and the axial positioning protrusion are clamped by the axial displacement amount provided by the clamp assembly, the clamping groove body is expanded and connected with the axial positioning groove of the right shaft member by the axial pushing action of the clamp assembly, and the marine test assembly is attached to the outer shell of the test planetary gearbox, and corrosive medium and lubricating oil are provided into the test planetary gearbox to realize the simulation of marine environment test.

[0009] Furthermore, the sandwiching groove is a cylindrical groove having an inverted tapered groove, and the cylindrical groove has a plurality of elongated holes formed along its axial direction.

[0010] Further, the clamp assembly includes an upper clamp unit, a lower clamp unit and a clamp moving block, the upper clamp unit and the lower clamp unit are arranged on the left and right sides in the axial positioning groove in the axial direction, the lower clamp unit abuts against the bottom end surface of the axial positioning groove, a slope is machined on the corresponding one side of the upper clamp unit and the lower clamp unit, the slope of the upper clamp unit and the slope of the lower clamp unit form an inverted tapered space, the clamp moving block is slidably mounted in the inverted tapered space, and the outer walls of the clamp moving block contact the slope of the upper clamp unit and the slope of the lower clamp unit, respectively.

[0011] Furthermore, each of the upper clamp unit and the lower clamp unit includes two semicircular clamp blocks, the two semicircular clamp blocks are disposed opposite each other in the same plane, and a gap is left between the two semicircular clamp blocks.

[0012] The torsion shaft assembly further includes a removal device, which is fitted into the left shaft member and extends toward the axial positioning protrusion until it extends to push down the clamping groove body, where the removal device includes a screw, a removal nut, a driven bevel gear, a driving bevel gear, a wheel set and an end cap, the screw is horizontally rotatably attached in the axial opening of the left shaft member along the axial direction of the left shaft member, the wheel set is vertically rotatably attached in the longitudinal opening of the left shaft member along the radial direction of the left shaft member, and the axial opening and the longitudinal opening are connected, the drive bevel gear is externally fitted onto the wheel set, the driven bevel gear is externally fitted onto the head of the screw, the drive bevel gear and the driven bevel gear are meshed with each other, the removal nut is externally fitted onto the tail of the screw, and the end cap is attached onto the longitudinal opening.

[0013] Further, the marine test assembly includes a housing, a sealing cover, a corrosive medium introduction unit and a plurality of lubrication units, the housing is sealingly covered on the test planetary gearbox via the sealing cover, the plurality of lubrication units are vertically mounted in the housing and provide lubrication inside the test planetary gearbox in an oil-drop type lubrication manner, and the corrosive medium introduction unit is sealingly inserted into the lower part of the housing and provides the corrosive medium inside the test planetary gearbox.

[0014] Furthermore, each lubrication unit includes an annular cylinder, an annular magnet, an aluminum chute and a lubricating oil strainer, the aluminum chute is horizontally mounted at the bottom inside the housing, the housing is a case made of aluminum, the lubricating oil strainer is fitted inside the annular magnet, and the annular cylinder is vertically mounted on the annular magnet with a seal.

[0015] Preferably, the central portion of the lubricating oil strainer is downwardly convex.

[0016] Preferably, the mesh number of the lubricating oil strainer is 150-300 mesh.

[0017] Furthermore, the medium introduction pipe is sealingly inserted into the lower part of the housing and extends into the housing, and the medium nozzle is sealingly connected to the end of the medium introduction pipe located within the housing.

[0018] Preferably, the media nozzle includes a nozzle case and at least one set of helical vanes, the helical vanes being mounted within the nozzle case to provide turbulence to the introduction angle of the corrosive media. Effect of the Invention

[0019] The present invention has the following advantages over the conventional techniques.

[0020] 1. The present invention is applicable to the high-power planetary gearbox testing on ships. The test platform is a power sealed system, which does not require additional sealed associated test box and related transmission components. The power flow is sealed cycled in two planetary reducers (referring to the test planetary gearbox 7 and the associated test gearbox 10), so the power consumption of the driving device is much lower, and the power only needs to overcome the friction power consumption of the test platform. The power of the planetary gearbox testing is loaded by the loader in the mechanical power sealed system, which has a clear principle and is easy to implement.

[0021] 2. In the present invention, the loader passes the transmission shaft between the output ends through the test planetary gearbox and couples it to the inside of the associated test planetary gearbox to form a sealed state. During the test, the power source (referring to the drive device 1) drives the test stand, and the driving power only needs to overcome the friction power consumption of the gearbox sealing system, and the loader applies torque, which is applied to the test planetary gearbox and the associated test planetary gearbox by the torsion shaft assembly to form a sealed power flow, and the load is carried out in the manner of mechanical loading, ensuring that the test can be carried out under full load and other load operating conditions.

[0022] 3. The torsion shaft assembly of the present invention is also connected using a multi-stage shaft, but the multiple shaft segments of the present invention are connected as a single unit by the synergistic action of the clamping groove and the clamp assembly. There is no need to use special equipment for processing, and the axial positioning protrusion and the axial positioning groove can be directly processed when processing the shaft segments, which not only reduces the difficulty of processing, but also reduces the number of processing steps, and further effectively reduces the production cost of the torsion shaft assembly.

[0023] At the same time, after the clamping groove and clamp assembly used in the present invention are connected, the outer diameters of the two adjacent shaft segments are the same, which does not affect the fitting of transmission members such as bearings or gears on the torsion shaft, and the connection using the above connection method of the present invention is reliable. During the test of the torsion shaft, when the rotational speed of the torsion shaft is 3500 r / m or more, the large torque transmission is not affected, so the torsion shaft assembly of the present invention can also meet the demands of actual operating conditions under the premise of reducing production costs.

[0024] 4. The test stand of the present invention is further provided with an ocean test assembly, which can simulate various complex situations that a real large ship may encounter when traveling on the sea. For example, the gearbox may encounter situations such as high salt fog, gravel and seawater sputtering during long-term use. The present invention introduces the above-mentioned corrosive medium from the outside through the corrosive medium introduction unit. At the same time, the present invention adjusts the flow direction of the corrosive medium entering the nozzle by different numbers of spiral vanes, and further realizes the closest simulation to the situation encountered in real sea navigation. It provides convenience for the testing of transmissions for large ships, and especially under the action of comprehensive environmental factors, the accurate collection of gear failure data parameters is convenient for overhaul operators to provide relevant theories and data basis for research and judgment during the overhaul process. [Brief description of the drawings]

[0025] [Figure 1] 1 is a top schematic view of the overall structure of the test stand of the present invention. [Diagram 2] FIG. 1 is a principle diagram of the planetary gearbox back-to-back closed power system transmission, where the arrow represents the transmission direction of the closed power flow. [Diagram 3]FIG. 3 is an exploded schematic diagram of two adjacent shaft segments 9-1 before they are assembled, in which the arrows pointing to the left and right sides indicate the directions in which the clamping groove body 9-2 generates a radial displacement amount by the axial pushing action of the clamp assembly 9-3, and the two arrows pointing downward in FIG. 3 indicate the axial pushing direction of the clamp assembly 9-3. [Figure 4] FIG. 4 is a schematic diagram of the assembled state of FIG. [Diagram 5] FIG. 1 is a structural schematic diagram of the clamp assembly 9-3, in which the arrow pointing to the left represents the axial movement direction of the upper clamp unit 9-7, and the arrow pointing downward represents the movement direction when the clamp moving block 9-9 is subjected to a radial force. [Figure 6] 1 is a schematic diagram showing the structure of a grooved holding body 9-2. [Figure 7] FIG. 1 is a schematic structural diagram of a semicircular clamp block 9-10. [Figure 8] FIG. 2 is a structural schematic diagram of the marine test assembly. [Figure 9] FIG. 1 is a top schematic view of a marine test assembly. [Figure 10] FIG. 1 is a structural schematic diagram of the media nozzle 17-2 having a pair of spiral vanes 17-2-2. [Figure 11] FIG. 1 is a structural schematic diagram of a media nozzle 17-2 having two sets of spiral vanes 17-2-2. [Figure 12] 1 is an enlarged view of shaft segment 9-1, where arrows pointing up and down indicate the directions in which clamping groove 9-2 generates radial displacement due to the axial pushing action of clamp assembly 9-3. [Figure 13] FIG. 13 is a cross-sectional view taken along line AA in FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0026] 1 to 13, the present embodiment is described. The high-power heavy-load planetary gear back-to-back test stand of the present embodiment includes a drive unit 1, a first shaft coupling 2, a speed increaser 3, a second shaft coupling 4 and a rotation speed torque meter 5, the drive unit 1, the first shaft coupling 2, the speed increaser 3, the second shaft coupling 4 and the rotation speed torque meter 5 are sequentially connected from left to right, which further includes a planetary gear box back-to-back sealed power system 18 and a marine test assembly, the planetary gear box back-to-back The combined sealed power system 18 includes a third coupling 6, a test planetary gearbox 7, a first interlocking mechanism 8, a torsion shaft assembly 9, an associated test gearbox 10, a fourth coupling 11, a second interlocking mechanism 12, and a loader 13. The third coupling 6, the test planetary gearbox 7, the first interlocking mechanism 8, the torsion shaft assembly 9, the associated test gearbox 10, the fourth coupling 11, the second interlocking mechanism 12, and the loader 13 are connected in order from left to right. The torsion shaft assembly 9 includes a clamping groove body 9-2, a clutch 11, a clutch 12, and a loader 13. The device includes a clamp assembly 9-3 and a plurality of shaft segments 9-1, and an axial positioning protrusion 9-4 is machined on the right side of the left shaft member of two adjacent shaft segments 9-1, and an axial positioning groove 9-5 is machined on one end face of the right shaft member corresponding to the axial positioning protrusion 9-4. The clamping groove body 9-2 is coaxially fitted externally onto the axial positioning protrusion 9-4, and the clamp assembly 9-3 is fitted internally into the axial positioning groove 9-5, and the right shaft member is fitted with the clamping groove body 9- 2, and clamps the clamping groove 9-2 and the axial positioning protrusion 9-4 by the axial displacement provided by the clamping assembly 9-3. The clamping groove 9-2 is displaced radially by the axial pushing action of the clamping assembly 9-3, and is expanded and connected with the axial positioning groove 9-5 of the right shaft member. The marine test assembly is attached to the outer shell of the test planetary gearbox 7, and provides corrosive medium and lubricating oil into the test planetary gearbox 7 to simulate marine environment testing.

[0027] Here, in this embodiment, the transmission shaft 19 on the loader 13 and the torsion shaft assembly 9 are connected by a toothed shaft coupling or a spline. Also, a torque required for the test stand is provided.

[0028] The driving device 1 of the test stand in this embodiment provides the required rotation speed for the test stand, and its power is only used to overcome the friction power consumption of the entire test platform, which is related to the friction power consumption of each device in the test platform, and is generally 5-10% of the power of the test planetary gearbox 7. The driving device 1 pulls the entire test platform to reach the required test rotation speed for the test planetary gearbox 7, and the loader 13 provides the required torque for the test planetary gearbox 7, which can be loaded to any torque value in real time, and loaded smoothly without impact.

[0029] The test planetary gear box 7 of this embodiment includes a test two-stage sun gear 20, a test two-stage carrier 21, a test two-stage planetary gear 22, a test two-stage ring gear 23, a test first-stage sun gear 24, a test first-stage planetary gear 25, a test first-stage ring gear 26, a test first-stage carrier 27 and a test two-stage floating ring gear 28. The test first-stage sun gear 24 is fitted onto the torsion shaft assembly 9, the test first-stage planetary gear 25 is fitted onto the test first-stage carrier 27, the external teeth of the test first-stage planetary gear 25 and the external teeth of the test first-stage sun gear 24 are meshed with each other, and the test two-stage sun gear 20 is fitted onto the test The test two-stage planetary gear 22 is fitted onto the test two-stage carrier 21, and the external teeth of the test two-stage planetary gear 22 are meshed with the external teeth of the test two-stage sun gear 20. The test two-stage floating ring gear 28 is fitted onto the test two-stage planetary gear 22 and the test single-stage carrier 27, and the internal teeth of the test two-stage ring gear 23 of the test two-stage floating ring gear 28 are meshed with the external teeth of the test two-stage planetary gear 22 and the external teeth of the test single-stage carrier 27, respectively.

[0030] The first interlocking mechanism 8 of this embodiment includes a first connecting member 29, an intermediate shaft 30 and a second connecting member 31. The first connecting member 29, the intermediate shaft 30 and the second connecting member 31 are connected in order from left to right and are used to connect the test planetary gearbox 7 and the associated test gearbox 10.

[0031] The first connecting member 29 in this embodiment is connected to the test single stage carrier 27 of the test planetary gearbox 7 , and the second connecting member 31 is connected to the associated test single stage carrier 32 of the associated test gearbox 10 .

[0032] The accompanying test gear box 10 of this embodiment includes an accompanying test first stage carrier 32, an accompanying test first stage sun gear 33, an accompanying test second stage floating ring gear 34, an accompanying test first stage planetary gear 35, an accompanying test first stage ring gear 36, an accompanying test second stage sun gear 37, an accompanying test second stage planetary gear 38, an accompanying test second stage ring gear 39 and an accompanying test second stage carrier 40. The accompanying test first stage sun gear 33 is coaxially fitted on the torsion shaft assembly 9, the accompanying test first stage planetary gear 35 is fitted on the accompanying test first stage carrier 32, and the external teeth of the accompanying test first stage planetary gear 35 and the external teeth of the accompanying test first stage sun gear 33 are meshed with each other. The two-stage sun gear 37 is fitted onto the associated test single-stage planetary gear 35, and the internal teeth of the associated test single-stage ring gear 36 of the associated test two-stage sun gear 37 mesh with the external teeth of the associated test single-stage planetary gear 35, the associated test two-stage planetary gear 38 is fitted onto the associated test two-stage carrier 40, the associated test two-stage ring gear 39 is fitted onto the associated test single-stage carrier 32 and the associated test two-stage planetary gear 38, the internal teeth of the associated test two-stage floating ring gear 34 on the associated test two-stage ring gear 39 mesh with the external teeth of the associated test single-stage carrier 32, and the internal teeth of the associated test two-stage ring gear 39 mesh with the external teeth of the associated test two-stage planetary gear 38.

[0033] The accompanying test gearbox 10 in this embodiment further includes a third connecting member 41, and the accompanying test single-stage sun gear 33 and the loader 13 are connected via the third connecting member 41.

[0034] According to the difference in driving and loading methods, the test of planetary gearboxes can be divided into open test benches and closed power flow test benches. The open test bench is driven by a power source (motor), and the power of the test gearbox and the power consuming device must be equal to the power of the test gearbox. The closed power flow test bench connects the test planetary gearbox and the associated test planetary gearbox back to back (output end to output end) with a coupling mechanism, The present invention may be used for full speed and full load performance testing of planetary gearboxes, and is particularly applicable to dynamic balance testing of heavy load planetary gearboxes.

[0035] In particular, in the case of full-load long-term performance testing or reliability testing of a heavy-load planetary gearbox, the prominent problems of high test platform cost, high power consumption, and poor economy are encountered. In response to this problem, the input and output of the planetary gearbox are coaxially connected, and a back-to-back test method is used to realize full-speed and full-load performance testing of the planetary gearbox, while the set rotational speed torque meter is used to accurately measure the transmission efficiency.

[0036] The test platform of the present invention has a relatively small footprint. The loading is performed in the manner of mechanical sealed power. The driving device power is only the friction power consumption in the sealed system, and the power is relatively small. The loading device can be arbitrarily loaded in real time. It is applicable to planetary gearbox performance testing, especially for high-power planetary gearboxes.

[0037] 2. Description of the embodiment in conjunction with FIG. 3, FIG. 4 and FIG. 6. The clamping groove 9-2 of the embodiment is a cylindrical groove with a reverse tapered groove, and the cylindrical groove has a plurality of long holes 9-6 along its axial direction. When installed in this way, in actual use, the taper of the cylindrical groove with the reverse tapered groove engages with the outer circumferential surface of the axial positioning protrusion 9-4, and the outer circumferential taper of the axial positioning protrusion 9-4 is 1:15-1:20, which facilitates ensuring the realization of a reliable fit between the clamping groove 9-2 and the axial positioning protrusion 9-4, and the external expansion of the small displacement of the plurality of long holes 9-6 makes it easy to clamp the axial positioning protrusion 9-4 firmly in the axial positioning groove 9-5, and realizes accurate transmission by friction force. Other compositions and connection relationships are the same as those of the embodiment 1.

[0038] In this embodiment, the long holes 9-6 are arranged in a circular array along the circumferential direction, and the number of the holes is 4 to 8. In practical use, the number is preferably 4 or 6, for example, this setting can easily ensure the degree of clamping by the clamping groove 9-2, and the long holes can generate minute radial displacement when the cylindrical groove is subjected to pressing force, and can also play an expanding role for the axial positioning groove 9-5, which can ensure the reliability of the connection between the two adjacent shaft segments 9-1 and ensure accurate torque transmission.

[0039] 3. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 3: This embodiment will be described in conjunction with Figures 3, 4 and 5. The clamp assembly 9-3 of this embodiment includes an upper clamp unit 9-7, a lower clamp unit 9-8 and a clamp moving block 9-9. The upper clamp unit 9-7 and the lower clamp unit 9-8 are arranged on the left and right sides of the axial positioning groove 9-5 in the axial direction. The lower clamp unit 9-8 abuts against the bottom end surface of the axial positioning groove 9-5. The upper clamp unit 9-7 and the lower clamp unit 9-8 have a slope machined on the corresponding one side. The slope of the upper clamp unit 9-7 and the slope of the lower clamp unit 9-8 form an inverted tapered space. The clamp moving block 9-9 is slidably mounted in the inverted tapered space. The outer wall of the clamp moving block 9-9 contacts the slope of the upper clamp unit 9-7 and the slope of the lower clamp unit 9-8, respectively.

[0040] When installed in this manner, the end face of the lower clamping unit 9-8 abuts against the groove of the axial positioning groove 9-5, so that when the clamp moving block 9-9 generates an acting force on the lower clamping unit 9-8, the lower clamping unit 9-8 does not undergo a slight displacement, and the upper clamping unit 9-7 undergoes a slight displacement toward the axial positioning groove 9-5, which causes the clamping groove 9-2 to move axially and expand outward, and the inner wall of the axial positioning groove 9-5 clamps the clamping groove 9-2, and further realizes the connection between the two adjacent shaft segments 9-1. Other compositions and connection relationships are the same as those in the first or second embodiment of the present invention.

[0041] In this embodiment, in actual use, a number of counterbores are opened on the outer periphery of the shaft segment 9-1 in which the axial positioning groove 9-5 is opened, an internal hexagonal hole is machined on the upper part of the clamp moving block 9-9, and the lower end face of the bolt of the vertical segment of the "L" shaped bolt wrench for external screwing and removal is machined into an external hexagon. The bolt is screwed into the counterbore, and during the downward movement of the bolt, the external hexagon of the bolt is inserted into the internal hexagonal hole of the clamp moving block 9-9. During the rotation of the "L" shaped bolt wrench, it pulls the clamp moving block 9-9 to move downward, and further provides driving force for the axial movement of the upper clamp unit 9-7. When removing, the reverse operation is performed.

[0042] EMBODIMENT 4 FOR CARRYING OUT THEINVENTION: Referring to Figures 3 to 6, this embodiment will be described. Each of the upper clamp unit 9-7 and the lower clamp unit 9-8 in this embodiment includes two semicircular clamp blocks 9-10, which are arranged opposite each other in the same plane, and a gap is left between the two semicircular clamp blocks 9-10.

[0043] When installed in this way, the gap is used to realize the positioning of the clamping groove 9-2, the range of the gap is 3mm-10mm, and a positioning post is machined on the outer end surface of the clamping groove 9-2, which can be accurately inserted into the gap during assembly, and further ensures the concentricity of the connection between the two adjacent shaft segments 9-1. Other compositions and connection relationships are the same as those of the first, second or third embodiment of the invention.

[0044] 5. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS: Referring to FIG. 3, FIG. 4, FIG. 12 and FIG. 13, the torsion shaft assembly 9 of the present embodiment further includes a removal device, which is fitted into the left shaft member and extends to the axial positioning protrusion 9-4 side until it extends and pushes down the clamping groove body 9-2. Here, the removal device includes a screw 9-11, a removal nut 9-12, a driven bevel gear 9-13, a driving bevel gear 9-14, a wheel axle 9-15 and an end cap 9-16. The screw 9-11 is inserted in the axial direction of the left shaft member. The left axle member is horizontally rotatably mounted in the axial opening of the left axle member along the radial direction of the left axle member, the wheel axle 9-15 is vertically rotatably mounted in the vertical opening of the left axle member along the radial direction of the left axle member, and the axial opening and the vertical opening are connected, the drive bevel gear 9-14 is externally fitted onto the wheel axle 9-15, the driven bevel gear 9-13 is externally fitted onto the head of the screw 9-11, the drive bevel gear 9-14 and the driven bevel gear 9-13 are meshed with each other, the removal nut 9-12 is externally fitted onto the tail of the screw 9-11, and the end cap 9-16 is attached onto the vertical opening.

[0045] When the super long shaft system is installed in this way, if it is necessary to remove the super long shaft system, first remove the end cap 9-16, and then use an external hexagonal wrench to insert it into the tail of the axle 9-15, rotate the wrench, and the wrench will pull the axle 9-15, the driving bevel gear 9-14, the driven bevel gear 9-13 and the screw 9-11, and the removal nut 9-12 located on the screw 9-11 will contact the bottom end face of the clamping groove 9-2 to apply axial force, and move horizontally to the right along the screw until the clamping groove 9-2 is pushed down, and the removal is completed at the axial positioning protrusion 9-4 of the clamping groove 9-2. Other compositions and connection relationships are the same as those in the first, second, third or fourth embodiment of the invention.

[0046] It should be noted that in order to ensure that the removal nut 9-12 can realize horizontal axial movement, a guide groove is opened on the outer circumferential direction of the removal nut 9-12, the guide groove is installed coaxially with the removal nut 9-12, and a guide boss that slides into and engages with the guide groove is machined in the axial opening of the axial positioning protrusion 9-4, so that the guide boss is positioned in the guide groove to realize the removal nut 9-12 to slide horizontally along its axial direction.

[0047] In the present embodiment, the removal device further includes a bearing seat 9-17, an axle fixing seat 9-18, an axle mounting seat 9-19 and a screw aligning seat 9-20 in practical use. The head of the screw 9-11 is an axle and is used to fit the driven bevel gear 9-13, where the head of the screw 9-11 and the driven bevel gear 9-13 are keyed together. The screw aligning seat 9-20 is installed in the axial mouth. The screw aligning seat 9-20 is arranged coaxially with the shaft segment 9-1. The screw 9-11 is installed in the screw aligning seat 9-20 by the bearing rotation. The screw aligning seat 9-20 is connected to the shaft segment 9-1 by the shaft segment 9-1. The tail of the screw 9-11 is a male thread, and the screw 9-11 and the removal nut 9-12 are engaged with each other to form a nut thread, the axle mounting seat 9-19 is fixedly mounted in the longitudinal opening, the axle 9-15 is rotated and inserted onto the axle mounting seat 9-19, and the upper part of the axle 9-15 is externally fitted into the axle fixing seat 9-18 located in the longitudinal opening through a bearing, which is used to limit the axial degree of the axle 9-15 and can also ensure that the axle segment 9-1 maintains structural stability during high-speed rotation, and the driving bevel gear 9-14 and the axle 9-15 are keyed together.

[0048] It should be further explained that, during installation, the removal device of this embodiment has a give-away groove opened on the screw aligning seat 9-20, which engages with a guide boss machined into the axial opening of the axial positioning protrusion 9-4. After the screw 9-11 is installed, the give-away groove facilitates the screw aligning seat 9-20 to be smoothly installed into the axial opening of the axial positioning protrusion 9-4, not only facilitating installation, but also avoiding the problem of installation being difficult due to the opening of the guide boss.

[0049] In this embodiment, a removal device is used, which can be removed after the experiment is completed to avoid wasting the shaft segment 9-1, and can also be reused, further saving costs.

[0050] 6. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS: Referring to FIG. 7 and FIG. 8, the marine test assembly of the present embodiment includes a housing 14, a sealing cover 15, a corrosive medium introduction unit 17 and a plurality of lubrication units 16. The housing 14 is sealed and covered on the test planetary gearbox 7 via the sealing cover 15. The plurality of lubrication units 16 are vertically mounted in the housing 14 and provide lubrication to the inside of the test planetary gearbox 7 in an oil-drop lubrication manner. The corrosive medium introduction unit 17 is sealed and inserted into the lower part of the housing 14 and provides the corrosive medium to the inside of the test planetary gearbox 7.

[0051] When installed in this manner, an oil drain hole is opened on the case of the test planetary gearbox 7, and the present embodiment uses a lubrication unit 16 to realize lubrication of the test planetary gearbox 7. The corrosive medium introduction unit 17 is connected to an external marine operating condition simulator, and the number of the corrosive medium introduction units 17 is multiple and is mainly used to provide environmental simulation such as salt fog, raindrops, and gravel. The external marine operating condition simulator is a conventional technology and will not be described further here. Other compositions and connection relationships are the same as any one of the first to fifth embodiments of the present invention.

[0052] In addition, this embodiment also simulates high temperature and high humidity environments during actual use, and the simulated high temperature can be achieved by adding a heating coil to the case, and the high humidity environment can be achieved by introducing salt mist and increasing it in proportion to the humidity of seawater. No further explanation will be given here.

[0053] 7 to 8, each lubrication unit 16 of the present embodiment includes an annular cylinder 16-1, an annular magnet 16-2, an aluminum chute 16-3 and a lubricating oil strainer 16-4. The aluminum chute 16-3 is mounted horizontally at the bottom of the housing 14, which is a case made of aluminum. The lubricating oil strainer 16-4 is fitted onto the annular magnet 16-2, and the annular cylinder 16-1 is mounted vertically and sealed onto the annular magnet 16-2.

[0054] When installed in this manner, the lubrication method of this embodiment drips lubricant mainly by vibration generated when the test planetary gearbox 7 operates, and the lubrication units 16 themselves can drip by the vibration generated by the same magnetic repulsion and vibration synergy on the chute. Other compositions and connections are the same as any one of the first to sixth embodiments of the present invention.

[0055] In this embodiment, neither the aluminum chute nor the aluminum case body has any attraction with the annular magnet 16-2, and the annular magnet 16-2 can slide at any position within the aluminum chute 16-3, and the magnetic properties of the annular magnets 16-2 in two adjacent lubrication units 16 are the same. Furthermore, the distance between the multiple lubrication units 16 is guaranteed, and oil is dropped at different positions to achieve lubrication.

[0056] Lubrication is one of the basic operations of gearbox management, so a good lubrication condition is beneficial to ensure reliable operation of the gearbox, reduce friction power consumption, reduce temperature rise and wear, and reduce the consumption of lubricant, and avoid transient wear of gears and bearings. Meanwhile, the present invention uses drip lubrication to effectively utilize the vibration of the gearbox and save the consumption of lubricant.

[0057] 8th embodiment of the present invention: Explaining this embodiment in conjunction with Fig. 7 and Fig. 8, the center of the lubricating oil strainer 16-4 of this embodiment is convex downward. Installed in this manner, it is easy to drip the lubricating oil accurately. The other composition and connection relationship are the same as any one of the 1st to 7th embodiments of the present invention.

[0058] 9th embodiment of the invention: This embodiment is explained in conjunction with FIG. 8. The mesh number of the lubricating oil strainer 16-4 of this embodiment is 150-300 mesh. When installed in this way, it can ensure that the lubricating oil drips by the synergistic action of vibration and shaking, and it can easily control the amount of dripping of the lubricating oil, and it can also filter impurities in the lubricating oil. The other compositions and connections are the same as any one of the 1st to 8th embodiments of the invention.

[0059] 10. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS: Referring to FIG. 7, FIG. 10 and FIG. 11, the corrosive medium introduction unit 17 of the present embodiment includes a medium introduction pipe 17-1 and a medium nozzle 17-2. The medium introduction pipe 17-1 is sealed and inserted into the lower part of the housing 14 and extends into the housing 14. The medium nozzle 17-2 is sealed and connected to the end of the medium introduction pipe 17-1 located inside the housing 14.

[0060] When installed in this manner, the medium introduction pipe 17-1 is made of a corrosion-resistant material. The other compositions and connections are the same as any one of the first to ninth embodiments of the present invention.

[0061] In the present embodiment, the mounting angle of the media nozzle 17-2 can be adjusted arbitrarily during actual use, but the media nozzle 17-2 has an angle toward the housing 14 and forms an angle with the housing 14, which makes it easier to ensure randomness of the injected medium and is more suited to the uncertainty in the marine environment.

[0062] EMBODIMENT 11 FOR CARRYING OUT THE PRESENTINFERENCE POINT: Referring to FIG. 10 and FIG. 11, the present embodiment will be described. The media nozzle 17-2 of the present embodiment includes a nozzle case 17-2-1 and at least one set of helical blades 17-2-2, and the helical blades 17-2-2 are mounted within the nozzle case 17-2-1 to realize turbulence with respect to the introduction angle of the corrosive medium.

[0063] When installed in this manner, the different numbers of spiral blades cause the entering medium to undergo a spiral action and generate different introduction angles. The other compositions and connection relationships are the same as any one of the first to tenth embodiments of the present invention.

[0064] The operating principle of the present invention will be explained by combining Figs. 1 to 13. The drive device of the present invention provides the required rotational speed for the test stand, and its power is only used to overcome the friction power consumption of the entire test platform, which is related to the friction power consumption of each equipment in the test platform, generally 5-10% of the power of the test planetary gearbox, and the loader provides the required torque for the test stand.

[0065] The testing principle of the present invention: the high-power planetary gear back-to-back test stand is loaded by mechanically sealed power method; when testing, the driving device pulls the entire test platform to reach the required test rotation speed of the test planetary gearbox, and the loader provides the required torque for the test planetary gearbox, which can be loaded to any torque value in real time, and is loaded smoothly without impact.

[0066] The ocean simulation principle of the present invention: by connecting an external ocean operating condition simulator with a corrosive medium introduction unit 17, according to the actual usage environment and the needs of test data collection, salt fog, raindrops, gravel, high humidity and other media can be introduced separately or simultaneously for a certain period of time to realize multi-operating condition simulation.

[0067] Although the present invention has been disclosed above in a better embodiment, it is not intended to limit the present invention, and those skilled in the art may make other modifications within the spirit of the present invention and use the present invention in fields not mentioned herein, and of course, any modifications made based on the spirit of the present invention should be included within the scope of protection claimed by the present invention. [Explanation of symbols]

[0068] Here, 1 is a driving device, 2 is a first shaft coupling, 3 is a speed increaser, 4 is a second shaft coupling, 5 is a rotational speed torque meter, 6 is a third shaft coupling, 7 is a test planetary gear box, 8 is a first interlocking mechanism, 9 is a torsion shaft assembly, 9-1 is a shaft segment, 9-2 is a clamping groove body, 9-3 is a clamp assembly, 9-4 is an axial positioning protrusion, 9-5 is an axial positioning groove, 9-6 is an elongated hole, 9-7 is an upper clamp unit, 9-8 is a lower clamp unit, 9-9 is a clamp moving block, 9-10 is a semicircular arc clamp block, 9-11 is a screw, 9-12 is a removal nut, 9-13 is a driven bevel gear, and 9-14 is a driving bevel gear. , 9-15 is a wheel set, 9-16 is an end cap, 9-17 is a bearing seat, 9-18 is a wheel set fixing seat, 9-19 is a wheel set mounting seat, 9-20 is a screw aligning seat, 10 is an associated test gear box, 11 is a fourth shaft coupling, 12 is a second interlocking mechanism, 13 is a loader, 14 is a housing, 15 is a seal cover body, and 16 is a lubricant. unit, 16-1 is an annular cylinder, 16-2 is an annular magnet, 16-3 is an aluminum chute, 16-4 is a lubricating oil strainer, 17 is a corrosion medium introduction unit, 17-1 is a medium introduction pipe, 17-2 is a medium nozzle, 17-2-1 is a nozzle case, 17-2-2 is a spiral vane, 18 is a planetary gear box back-to-back sealed power system, Also, 19 is a transmission shaft, 20 is a test two-stage sun gear, 21 is a test two-stage carrier, 22 is a test two-stage planetary gear, 23 is a test two-stage ring gear, 24 is a test single-stage sun gear, 25 is a test single-stage planetary gear, 26 is a test single-stage ring gear, 27 is a test single-stage carrier, 28 is a test two-stage floating ring gear, 29 is a first connecting member, 30 is an intermediate shaft, and 31 is a 3 is a second connecting member, 32 is an associated test single stage carrier, 33 is an associated test single stage sun gear, 34 is an associated test two stage floating ring gear, 35 is an associated test single stage planetary gear, 36 is an associated test single stage ring gear, 37 is an associated test two stage sun gear, 38 is an associated test two stage planetary gear, 39 is an associated test two stage ring gear, 40 is an associated test two stage carrier, and 41 is a third connecting member.

Claims

1. A high-power heavy-load planetary gear back-to-back test bench including a drive unit (1), a first shaft coupling (2), a speed increaser (3), a second shaft coupling (4) and a rotational speed torque meter (5) connected in sequence from left to right, a back-to-back planetary gearbox sealed power system (18) and a marine test assembly; The planetary gearbox back-to-back sealed power system (18) includes a third coupling (6), a test planetary gearbox (7), a first interlocking mechanism (8), a torsion shaft assembly (9), an associated test gearbox (10), a fourth coupling (11), a second interlocking mechanism (12) and a loader (13), and the rotational speed torque meter (5) and one end of the test planetary gearbox (7) are connected via the third coupling (6), and the other end of the test planetary gearbox (7) and the associated test gearbox (14) are connected via the loader (13). a first interlocking mechanism (8) mounted on the torsion shaft assembly (9) between the other end of the test planetary gearbox (7) and one end of the associated test gearbox (10); a second interlocking mechanism (12) is fitted onto the fourth coupling (11) between the other end of the test planetary gearbox (7) and one end of the associated test gearbox (10); a third interlocking mechanism (13) mounted on the loader (12) and connected to the loader (13) through a fourth coupling (11); The torsion shaft assembly (9) includes a clamping groove body (9-2), a clamp assembly (9-3), and a plurality of shaft segments (9-1). An axial positioning protrusion (9-4) is machined on the right side of the left shaft member of the two adjacent shaft segments (9-1), and an axial positioning groove (9-5) is machined on the end face on one side corresponding to the axial positioning protrusion (9-4) on the right shaft member. The clamping groove body (9-2) is coaxially disposed on the axial positioning protrusion (9-4). the clamp assembly (9-3) is fitted inside the axial positioning groove (9-5); the right shaft member is fitted coaxially onto the clamping groove (9-2), and the clamping groove (9-2) and the axial positioning protrusion (9-4) are clamped by the axial displacement provided by the clamping assembly (9-3); the clamping groove (9-2) is displaced radially by the axial pushing action of the clamping assembly (9-3), and is expanded and connected to the axial positioning groove (9-5) of the right shaft member; The clamping groove body (9-2) is a cylindrical groove body having an inverted tapered groove, and the cylindrical groove body has a plurality of elongated holes (9-6) formed along its axial direction. The clamp assembly (9-3) includes an upper clamp unit (9-7), a lower clamp unit (9-8) and a clamp moving block (9-9), the upper clamp unit (9-7) and the lower clamp unit (9-8) are arranged on the left and right sides in the axial positioning groove (9-5) in the axial direction, the lower clamp unit (9-8) abuts against the groove bottom end surface of the axial positioning groove (9-5), a slope is machined on one corresponding side of the upper clamp unit (9-7) and the lower clamp unit (9-8), the slope of the upper clamp unit (9-7) and the slope of the lower clamp unit (9-8) form an inverted tapered space, the clamp moving block (9-9) is slidably mounted in the inverted tapered space, and the outer walls of the clamp moving block (9-9) respectively contact the slope of the upper clamp unit (9-7) and the slope of the lower clamp unit (9-8); A high power heavy load planetary gear back to back test stand, characterized in that the marine test assembly is mounted on the outer shell of the test planetary gear box (7) and provides corrosive medium and lubricating oil within the test planetary gear box (7).

2. The high-power heavy-load planetary gear back-to-back test stand as claimed in claim 1, characterized in that the upper clamping unit (9-7) and the lower clamping unit (9-8) each include two semicircular clamping blocks (9-10), the two semicircular clamping blocks (9-10) are arranged opposite to each other in the same plane, and a gap is left between the two semicircular clamping blocks (9-10).

3. The torsion shaft assembly (9) further includes a removal device, which is fitted into the left shaft member and extends toward the axial positioning protrusion (9-4) until it extends and pushes down the clamping groove body (9-2), where the removal device includes a screw (9-11), a removal nut (9-12), a driven bevel gear (9-13), a driving bevel gear (9-14), a wheel axle (9-15) and an end cap (9-16), and the screw (9-11) is horizontally rotatably attached in the axial opening of the left shaft member along the axial direction of the left shaft member, and the wheel axle (9-15) is a screw (9-11) that is attached to the left shaft member so as to be horizontally rotatable in the axial opening of the left shaft member along the axial direction of the left shaft member. The high-power heavy-load planetary gear back-to-back test bench of claim 1, characterized in that: the left shaft member is mounted in the vertical opening of the left shaft member along the radial direction so as to be vertically rotatable, and the axial opening and the vertical opening are communicated with each other; the driving bevel gear (9-14) is fitted onto the wheel axle (9-15), the driven bevel gear (9-13) is fitted onto the head of the screw (9-11), the driving bevel gear (9-14) and the driven bevel gear (9-13) are meshed with each other; the removal nut (9-12) is fitted onto the tail of the screw (9-11), and the end cap (9-16) is mounted on the vertical opening.

4. The high-power heavy-load planetary gear back-to-back test stand according to claim 3, characterized in that the marine test assembly includes a housing (14), a sealing cover (15), a corrosive medium introduction unit (17) and a plurality of lubrication units (16), the housing (14) is sealingly covered on the test planetary gearbox (7) through the sealing cover (15), the plurality of lubrication units (16) are vertically mounted in the housing (14) and provide lubrication inside the test planetary gearbox (7) in a manner of oil-drop lubrication, and the corrosive medium introduction unit (17) is sealingly inserted into the lower part of the housing (14) and provides the corrosive medium inside the test planetary gearbox (7).

5. The high-power heavy-load planetary gear back-to-back test bench of claim 4, characterized in that each lubrication unit (16) includes an annular cylinder (16-1), an annular magnet (16-2), an aluminum chute (16-3) and an oil strainer (16-4), the aluminum chute (16-3) is horizontally mounted at the bottom of the housing (14), the housing (14) is a case made of aluminum material, the oil strainer (16-4) is fitted on the annular magnet (16-2), and the annular cylinder (16-1) is vertically mounted on the annular magnet (16-2) with a seal.

6. The high-power heavy-load planetary gear back-to-back test stand according to claim 5, characterized in that the central part of the lubricating oil strainer (16-4) is convex downward, and the mesh number of the lubricating oil strainer (16-4) is 150-300 mesh.

7. The high-power heavy-load planetary gear back-to-back test stand according to claim 6, characterized in that the corrosive medium introduction unit (17) includes a medium introduction pipe (17-1) and a medium nozzle (17-2), the medium introduction pipe (17-1) is sealedly inserted into the lower part of the housing (14) and extends into the housing (14), and the medium nozzle (17-2) is sealedly connected to the end of the medium introduction pipe (17-1) located inside the housing (14).

8. The high-power heavy-load planetary gear back-to-back test stand according to claim 7, characterized in that the medium nozzle (17-2) includes a nozzle case (17-2-1) and at least one set of helical vanes (17-2-2), the helical vanes (17-2-2) are mounted in the nozzle case (17-2-1) to realize turbulence to the introduction angle of the corrosive medium.

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