Ship bearing load measuring device

Abstract

The invention belongs to the field of ship bearing measurement, and discloses a ship bearing load measuring device which comprises a bearing, a dynamic supporting assembly and a rotating plate. The jack is used for supporting a ship bearing, and a pressure sensor is fixed at the upper end of the jack; the dynamic supporting assembly comprises a telescopic rod, a reset spring and a supporting rod, the telescopic rod is fixed to the inner wall of the supporting frame, the reset spring is fixed to the inner side of the telescopic rod, a displacement buffering space is provided for the bearing through the reset spring, and the rigid impact load between the bearing and the supporting frame can be reduced; a positioning ring is connected to the gravity center of the outer side of the bearing in a sleeving mode, a plurality of rotating plates are inserted under the positioning ring, self-locking assemblies are fixed among the rotating plates, and through the synergistic effect of the dynamic supporting assembly and the hydraulic oil flow channel system, instantaneous kinetic energy generated by sea wave impact is converted into heat energy and absorbed; rigid collision between the bearing and the supporting structure is reduced, and local deformation and measurement errors are avoided.

Description

Technical Field

[0001] The present disclosure belongs to the field of ship bearing measurement, and particularly relates to a ship bearing load measuring device. Background Art

[0002] Ship bearing load measurement is a key step in ship power system maintenance. Its accuracy directly affects bearing service life and navigation safety. Traditional measurement devices mostly use a rigid connection structure between the jack and the bearing, and directly obtain load data through a pressure sensor.

[0003] For example, the ship bearing load measuring device with publication number CN202433130U, by adjusting the position of the guide bracket on the guide shaft and the position of the jack on the slide rail, facilitates the coincidence of the center of the jack with the center of the ship's tail shaft, solving the problems of traditional jacks being laborious to move, difficult to accurately position, and having an uneven contact surface due to frequent movement. However, when the hull is hit by waves, if the bearing and the jack are rigidly connected, the impact force brought by the waves will be quickly transmitted through the hull to the connection between the bearing and the jack. Due to the constraint of the rigid connection, the stress in the connection part cannot be evenly dispersed, resulting in a sharp increase in local stress, which easily causes the bearing to deform. At this time, it is difficult for the bearing to automatically reset to the initial state where the center of the jack coincides with the center of the ship's tail shaft, causing the pressure sensor to produce a higher measurement error due to the edge effect. Summary of the Invention

[0004] In response to the deficiencies of the prior art, the purpose of the present disclosure is to provide a ship bearing load measuring device, which solves the problem in the prior art that due to the rigid connection between the jack and the bearing, when the impact force brought by the waves is transmitted to the rigid connection between the bearing and the jack behind the hull, stress concentration occurs at the connection due to the constraint of the rigid connection, causing the bearing to deform, the center of the jack to be offset from the center of the ship's tail shaft, and the pressure sensor detection working surface to be unevenly stressed, thereby resulting in large measurement errors.

[0005] The purpose of this disclosure can be achieved through the following technical solutions:

[0006] A ship bearing load measuring device comprising: a bearing, a dynamic support assembly and a rotating plate;

[0007] A jack for supporting a ship bearing, with a pressure sensor fixed to the upper end of the jack. The jack is located directly below the bearing, a support frame is provided between the jack and the bearing, and the center of gravity of the bearing, the center of gravity of the pressure sensor and the central axis of the jack coincide with each other. Multiple groups of dynamic support components are symmetrically provided on both sides of the bottom of the bearing;

[0008] The dynamic support assembly includes a telescopic rod, a return spring, and a support rod. The telescopic rod is fixed to the inner wall of the support frame, and the return spring is fixed to the inner side of the telescopic rod. The support rod is fixed on the side of the telescopic rod close to the bearing. The return spring provides a displacement buffer space for the bearing, which is conducive to reducing the rigid impact load between the bearing and the support frame.

[0009] A positioning ring is sleeved at the center of gravity of the outer side of the bearing, and a plurality of rotating plates are inserted directly below the positioning ring, and a self-locking component is fixed between the plurality of rotating plates.

[0010] In some disclosures, a groove is provided on a side of the support rod close to the positioning ring, and the depth of the groove is adapted to the thickness of the positioning ring.

[0011] In some disclosures, the working end surface of the support rod forms a V-shaped support structure, and the symmetry axis of the support rod coincides with the vertical center line of the pressure sensor.

[0012] In some disclosures, a flow channel is opened on the inner side of the support frame, and one end of the flow channel close to the bearing is connected to the piston cavity of the telescopic rod, and the flow channel is filled with hydraulic oil.

[0013] In some disclosures, a support plate is fixed to one end of the flow channel away from the telescopic rod, and a thread groove is provided through the middle of the support plate, a piston plate is slidingly provided on the inner side of the flow channel, a screw rod adapted to the thread groove is fixed to one end of the piston plate close to the support plate, and the inner side of the thread groove is threadedly connected to the piston plate, and the moving path of the piston plate is the same as the path of the flow channel.

[0014] In some disclosures, a plurality of vertically downward rubber blocks are fixed directly below the positioning ring, and a plurality of rotating plates corresponding to the rubber blocks are opened in the middle of the upper end of the support frame, and the middle of the rotating plates are rotatably connected to the two ends of the support frame.

[0015] In some disclosures, a dial indicator is fixed directly above the support frame.

[0016] In some disclosures, a rotating shaft is fixed to the side wall of the support frame perpendicular to the central axis of the bearing, and extension plates are fixed to both ends of the rotating plate, and a rotating hole adapted to the rotating shaft is provided in the middle of the extension plate, and the rotating plate is rotatably connected to the support frame through the rotating hole and the rotating shaft.

[0017] In some disclosures, the self-locking assembly includes a support spring, a latch, a connecting rod, a block rod and a positioning hole. A connecting rod is rotatably connected between the two rotating plates. The upper end of the connecting rod is rotatably connected to the latch. A support spring is provided at the upper end of the latch. The block rod is fixed to one end of the latch close to the connecting rod. A positioning hole is provided at the upper end of the support frame, and the block rod is fixed to the inner side of the positioning hole by friction.

[0018] In some disclosures, guide grooves are provided on both sides of the positioning hole, and the paths of the guide grooves are the same as the moving paths of the latches when the rotating plate is deflected.

[0019] The nouns, conjunctions or adjectives involved in the above technical solution are explained as follows:

[0020] A fixed connection is a connection in which parts or components are fixed without any relative movement;

[0021] A rotational connection is a connection between parts that allows the parts to rotate relative to each other;

[0022] Threaded connection is a detachable fixed connection with the advantages of simple structure, reliable connection, and easy assembly and disassembly. It is widely used in mechanical engineering and connection structure fields.

[0023] A sliding connection is a connection between parts that allows the parts to slide relative to each other.

[0024] Beneficial effects of the present disclosure:

[0025] 1. Through the synergistic effect of the dynamic support assembly and the hydraulic oil flow system, the instantaneous kinetic energy generated by the impact of waves is converted into heat energy and absorbed, reducing the rigid collision between the bearing and the support structure, reducing the measurement error caused by the low gravity overlap between the pressure sensor and the bearing due to local deformation, and reducing the impact on the load test results of the ship's bearings;

[0026] 2. The elastic restoring force of the reset spring combined with the self-locking component ensures that the bearing automatically returns to its initial position after displacement, and uses the self-locking mechanism to limit overshoot or rebound, reduce the number of dynamic adjustments, and improve the accuracy of the bearing after reset. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] In order to more clearly illustrate the embodiments of the present disclosure or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, for ordinary technicians in this field, other drawings can be obtained based on these drawings without any creative work.

[0028] Figure 1 is a schematic diagram of the overall structure of an embodiment of the present disclosure;

[0029] Figure 2 is a schematic diagram of the connection structure of the bearing and the support frame according to an embodiment of the present disclosure;

[0030] Figure 3 is a schematic diagram of the connection structure between the support frame and the dynamic support assembly according to an embodiment of the present disclosure;

[0031] Figure 4 This is an embodiment of the present disclosure Figure 3 Schematic diagram of the internal structure;

[0032] Figure 5 is a schematic diagram of the overall structure of the support frame according to an embodiment of the present disclosure;

[0033] Figure 6 is a schematic diagram of the overall structure of the dynamic support assembly according to an embodiment of the present disclosure;

[0034] Figure 7 It is a schematic diagram of the overall structure of the self-locking component of an embodiment of the present disclosure.

[0035] In the figure: 1. bearing; 2. support frame; 21. flow channel; 22. rotating shaft; 3. dynamic support assembly; 31. telescopic rod; 32. return spring; 33. support rod; 331. groove; 4. jack; 5. pressure sensor; 6. rotating plate; 61. extension plate; 62. rotating hole; 7. self-locking assembly; 71. support spring; 72. latch; 73. connecting rod; 74. stop rod; 75. positioning hole; 751. guide groove; 8. positioning ring; 81. rubber block; 9. support plate; 91. threaded groove; 10. piston plate; 101. screw; 11. micrometer. DETAILED DESCRIPTION

[0036] The following will be combined with the accompanying drawings in the embodiments of the present disclosure to clearly and completely describe the technical solutions in the embodiments of the present disclosure. Obviously, the embodiments described are only part of the embodiments of the present disclosure, not all of the embodiments. Based on the embodiments of the present disclosure, all other embodiments obtained by ordinary technicians in this field without making any creative efforts are within the scope of protection of the present disclosure.

[0037] Please refer to Figures 1 to 7 , a ship bearing load measuring device, comprising: a bearing 1, a dynamic support assembly 3 and a rotating plate 6;

[0038] A jack 4 is used to support a ship bearing 1, and a pressure sensor 5 is fixed to the upper end of the jack 4. The jack 4 is located directly below the bearing 1. A support frame 2 is provided between the jack 4 and the bearing 1. The center of gravity of the bearing 1, the center of gravity of the pressure sensor 5, and the central axis of the jack 4 coincide. Multiple groups of dynamic support components 3 are symmetrically provided on both sides of the bottom of the bearing 1;

[0039] The dynamic support assembly 3 includes a telescopic rod 31, a return spring 32, and a support rod 33. The telescopic rod 31 is fixed to the inner wall of the support frame 2, and the return spring 32 is fixed to the inner side of the telescopic rod 31. The support rod 33 is fixed to the side of the telescopic rod 31 close to the bearing 1. The return spring 32 provides a displacement buffer space for the bearing 1, which helps to reduce the rigid impact load between the bearing 1 and the support frame 2.

[0040] A positioning ring 8 is sleeved at the center of gravity of the outer side of the bearing 1 , and a plurality of rotating plates 6 are inserted directly below the positioning ring 8 , and a self-locking assembly 7 is fixed between the plurality of rotating plates 6 .

[0041] When in use, the jack 4 is placed directly below the bearing 1, and a positioning ring 8 is provided on the outside of the center of gravity of the bearing 1. At the same time, to facilitate the installation of the positioning ring 8, the positioning ring 8 can be set in a clamp shape, which is convenient for sleeved on the outside of the bearing 1, and the lower end of the positioning ring 8 is engaged with the rotating plate 6. When the bearing 1 is located directly above the pressure sensor 5, the positioning ring 8 and the rotating plate 6 are set vertically. When the position of the bearing 1 is offset, the rotating plate 6 is deflected, and it is possible to directly observe whether the rotating plate 6 is in a vertical state to determine whether the position of the bearing 1 corresponds to the pressure sensor 5. By designing that the axes of the positioning ring 8 and the rotating plate 6 coincide with each other, combined with the verticality indicator mark, a three-dimensional spatial positioning reference is established, and the axial alignment of the bearing 1 and the pressure sensor 5 can be accurately determined to ensure the spatial reference consistency of the detection data, so as to reduce the problem caused by edge effects. When the pressure of the bearing 1 on the pressure sensor 5 is applied to the edge of the sensor, due to the asymmetry of the supporting structure or the deformation characteristics of the material, the output signal may deviate from the linear response when the center is subjected to force, resulting in measurement errors.

[0042] The bottom of the bearing 1 contacts the support rods 33 on the multiple dynamic support components 3. At the same time, the multiple dynamic support components 3 are symmetrically arranged on both sides of the bearing 1 with respect to the vertical center line of the support frame 2, and the contact surfaces of the multiple support rods 33 and the bearing 1 form a V shape. At the same time, the weight of the support frame 2 and the dynamic support component 3 are calibrated to zero in advance, and the jack 4 is used to drive the pressure sensor 5 and the support frame 2 to move upward until the support rods 33 on the multiple dynamic support components 3 are in contact with the outer wall of the bearing 1. At this time, the reset spring on the dynamic support component 3 is used to The spring 32 applies a horizontal thrust to the bearing 1. At the same time, since the bottom surface of the bearing 1 is arc-shaped, the multiple support rods 33 use the elastic restoring force of the return spring 32 to push the support rods 33 to fit the side wall of the bearing 1. When the weight of the ship bearing 1 is 10 kg, the spring coefficient of the return spring 32 is selected to be an alloy spring steel of 150N / m-200N / m. If it is used in a large ship, a return spring 32 with a larger spring coefficient is selected to ensure that the elastic restoring force of the return spring 32 can push the bearing 1 to move after the bearing 1 deviates. , and thereby limit the position of the bearing 1. At the same time, when the ship is hit by waves and tilts, the bearing 1 deflects to one side, driving the support rod 33 to contract inward and compressing the return spring 32 on one side. At this time, since the bearing 1 and the support frame 2 are not fixedly connected, the inward contraction of the return spring 32 provides displacement space for the bearing 1, thereby offsetting the instantaneous impact force caused by the waves and reducing the rigid collision between the hydraulic jack 4 and the bearing 1. The symmetrically distributed dynamic support assembly 3 provides displacement buffer space for the bearing 1 while ensuring lateral restraint force, which is conducive to reducing the rigid impact load between the bearing 1 and the support frame 2. In some embodiments, the bearing 1 is reset only by elastic members. However, due to the large weight of the bearing, oscillation (overshoot or rebound) occurs at the initial position during the reset process, requiring multiple adjustments to stabilize, thereby reducing dynamic accuracy. At the same time, the return spring 32 will suffer elastic fatigue after long-term use. The user should lubricate and maintain the return spring 32 after each measurement and replace it promptly if the return spring 32 is deformed or damaged.

[0043] At the same time, when the force of the waves weakens, according to Hooke's law, the elastic force of the restoring spring 32 increases with the compressed length, and drives the bearing 1 to move close to the initial position before the bearing 1 moves until the bearing 1 is reset. At the moment the bearing 1 is reset, a self-locking component 7 is set between multiple rotating plates 6. When the rotating plate 6 is deflected, the self-locking component 7 is triggered and enters the waiting state for self-locking. When the rotating plate 6 rotates to a vertical state, the self-locking component 7 enters the self-locking state and limits the rotation of the rotating plate 6, thereby limiting the overshoot of the bearing 1.

[0044] Please refer to Figure 3 、 Figure 4 and Figure 6A groove 331 is formed on one side of the support rod 33 close to the positioning ring 8 , and the depth of the groove 331 is adapted to the thickness of the positioning ring 8 .

[0045] During use, the positioning ring 8 is embedded in the groove 331 on the support rod 33 . At this time, the working surface of the support rod 33 is in linear contact with the outer wall of the bearing 1 , thereby improving the fit between the support rod 33 and the bearing 1 .

[0046] Please refer to Figures 1 to 3 The working end surface of support rod 33 forms a V-shaped support structure, and the symmetry axis of support rod 33 coincides with the vertical centerline of pressure sensor 5. During use, the inclined surface formed by the V-shaped support structure can guide the movement path of bearing 1 when it is reset, causing bearing 1 to move closer to the original symmetry axis of support rod 33.

[0047] Please refer to Figures 4 and 5 A flow channel 21 is opened on the inner side of the support frame 2, and one end of the flow channel 21 close to the bearing 1 is connected to the piston cavity of the telescopic rod 31, and the flow channel 21 is filled with hydraulic oil.

[0048] When in use, hydraulic oil is blocked between the return spring 32 and the telescopic rod 31, and the hydraulic oil converts the instantaneous impact force of the bearing 1 moving due to the waves into heat energy, thereby further reducing the kinetic energy generated by the movement of the bearing 1 and buffering the bearing 1.

[0049] Please refer to Figures 3 to 5 A support plate 9 is fixed to the end of the flow channel 21 away from the telescopic rod 31, and a thread groove 91 is provided through the middle of the support plate 9. A piston plate 10 is slidingly provided on the inner side of the flow channel 21. A screw 101 adapted to the thread groove 91 is fixed to the end of the piston plate 10 close to the support plate 9, and the inner side of the thread groove 91 is threadedly connected to the piston plate 10, and the moving path of the piston plate 10 is the same as the path of the flow channel 21.

[0050] During use, the piston plate 10 is first inserted into the flow channel 21, and the support plate 9 is blocked at the end of the flow channel 21 away from the telescopic rod 31, and the support plate 9 is fixed to the side wall of the support frame 2 by bolts. Then, by rotating the screw 101, the circumferential restriction imposed on the piston plate 10 by the flow channel 21 is utilized to move the piston plate 10 along the flow channel 21 to the side close to the bearing 1, thereby pushing the return spring 32 to undergo elastic deformation, thereby adjusting the pressure of the support rod 33 on the bearing 1 and improving the adaptability to bearings 1 of different diameters.

[0051] Please refer to Figures 3 and 4 , a plurality of vertically downward rubber blocks 81 are fixed directly below the positioning ring 8, and a plurality of rotating plates 6 corresponding to the rubber blocks 81 are opened in the middle of the upper end of the support frame 2, and the middle of the rotating plate 6 is rotatably connected to the two ends of the support frame 2;

[0052] When in use, the positioning ring 8 is sleeved on the outside of the bearing 1, and the rubber block 81 at the bottom of the positioning ring 8 is embedded between multiple rotating plates 6. When the bearing 1 deviates, the rubber block 81 is twisted and deformed, and the rubber block 81 will deflect to one side. At this time, the twisting force of the rubber block 81 is used to drive the rotating plate 6 to rotate. Compared with the rigid connection between the rotating plate 6 and the positioning ring 8, it directly rotates when the bearing 1 deviates. Since the rotating plate 6 is made of rigid material and the offset of the bearing 1 is unstable, the triggering of the rubber block 81 can reduce the wear at the connection between the rotating plate 6 and the positioning ring 8, which is beneficial to increase the service life of the rotating plate 6.

[0053] Please refer to Figure 1 A micrometer 11 is fixed just above the support frame 2.

[0054] The support frame 2 and the bearing 1 are moved upward by the jack 4 , the displacement of the bearing 1 is measured by the dial gauge 11 , and the load on the bearing 1 is recorded by the pressure sensor 5 , thereby detecting the load condition of the bearing 1 .

[0055] Please refer to Figure 3 and Figure 5 A rotating shaft 22 is fixed to the side wall of the support frame 2 perpendicular to the central axis of the bearing 1, and an extension plate 61 is fixed to both ends of the rotating plate 6, and a rotating hole 62 adapted to the rotating shaft 22 is provided in the middle of the extension plate 61, and the rotating plate 6 is rotatably connected to the support frame 2 through the rotating hole 62 and the rotating shaft 22.

[0056] During use, the rotating hole 62 on the rotating plate 6 is sleeved on the rotating shaft 22. At this time, the rotating plate 6 can rotate with the rotating shaft 22 as the center, and the rubber block 81 is inserted between multiple rotating plates 6. Before the rubber block 81 is twisted, the rubber block 81 is in a vertical state. At this time, the side of the rubber block 81 is in contact with the side of the rotating plate 6. The rubber block 81 remains in a vertical state when it is not loaded, and its side is tightly fitted with the rotating plate 6, forming a preload force on the initial contact surface, which can not only buffer small vibrations, but also actively trigger the synchronous deflection of the rotating plate 6 through the twisting deformation (energy storage-release) of the rubber block 81 when the bearing 1 is offset, thereby realizing sensitive transmission of the offset signal.

[0057] Please refer to Figure 1 and Figure 7 The self-locking assembly 7 includes a support spring 71, a latch 72, a connecting rod 73, a blocking rod 74 and a positioning hole 75. A connecting rod 73 is rotatably connected between the two rotating plates 6. The upper end of the connecting rod 73 is rotatably connected to the latch 72. The upper end of the latch 72 is provided with a support spring 71. The end of the latch 72 close to the connecting rod 73 fixes the blocking rod 74. A positioning hole 75 is opened at the upper end of the support frame 2, and the blocking rod 74 is fixed to the inner side of the positioning hole 75 by friction.

[0058] When the support frame 2 is in a horizontal state, the latch 72, the blocking rod 74 and the positioning hole 75 are coaxially arranged. When the bearing 1 is offset, the rubber block 81 is deformed and bent, and the rotating plate 6 and the connecting rod 73 are rotated, so that the blocking rod 74 and the latch 72 are misaligned and automatically unlocked from the self-locking state, so that the elastic potential energy of the support spring 71 is released. When the reset spring 32 on the dynamic support assembly 3 pushes the bearing 1 to reset, it drives the bearing 1 to move toward the middle of the two dynamic support assemblies 3. During the movement, the bearing 1 drives the rotating plate 6 to reverse. When the bearing 1 moves to the initial position The central axis of the latch 72 coincides with the central axis of the positioning hole 75. At this time, the latch 72 is reset by the elastic support force of the hand support spring 71, and then inserted into the corresponding positioning hole 75, thereby locking. At this time, since the kinetic energy of the bearing 1 is weak when it is reset, the rotating plate 6 is self-locked, which is conducive to reducing the overshoot of the bearing 1. The depth of the positioning hole 75 is 1-1.5 cm, and the length of the blocking rod 74 is 2-3 cm. Since the length of the blocking rod 74 is much greater than the depth of the positioning hole 75, the blocking rod 74 can be moved out of the positioning hole 75 when the force is unbalanced. When the latch 72 and the blocking rod 74 are relatively offset due to external loads or position changes, the central axes of the two no longer coincide, and the force direction of the top end of the blocking rod 74 changes, breaking the original equilibrium state, so that the radial component of the force on the bottom end of the blocking rod 74 exceeds the restraining capacity of the positioning hole 75, and then moves out of the positioning hole 75, realizing the change of the connection state.

[0059] Please refer to Figure 5 Guide grooves 751 are formed on both sides of the positioning hole 75, and the path of the guide grooves 751 is the same as the movement path of the latch 72 when the rotating plate 6 is deflected. The guide grooves 751 limit the movement path of the latch 72. When the bearing 1 returns to its initial position, the latch 72 moves into the positioning hole 75. The support spring 71 applies downward pressure to the latch 72 so that its bottom end abuts against the inner wall of the positioning hole 75, thereby achieving self-locking. The positioning hole 75 is located in the middle of the inner side of the guide grooves 751. No matter which section the latch 72 slides from to the middle, it can achieve self-locking when it moves to the position of the positioning hole 75. At the same time, because the path of the guide grooves 751 is the same as the movement path of the latch 72 when the rotating plate 6 is deflected, the latch 72 is always in the same plane as the guide grooves 751. When the latch 72 is extended, it can move into the guide grooves 751.

[0060] The ship bearing load measuring device provided by the present invention will be further described below with reference to the accompanying drawings and implementation examples.

[0061] When in use, place the jack 4 directly under the bearing 1, and put the positioning ring 8 on the outside of the bearing 1, and move the clamp so that it is located on the side of the bearing 1 close to the center of gravity. At the same time, the rubber block 81 at the bottom end of the positioning ring 8 is inserted between multiple rotating plates 6. At this time, the rubber block 81 and the rotating plates 6 are both vertically downward. At this time, the pin 72 applies a tightening force to the baffle rod 74 along the axial direction, and the bottom end of the baffle rod 74 is tightly matched with the inner wall of the positioning hole 75 to form a stable positioning connection.

[0062] At this time, the pressure sensor 5 and the support frame 2 are driven to move vertically upward by the jack 4, and the displacement of the bearing 1 is recorded by the dial gauge 11 to detect the load of the bearing 1;

[0063] When the waves hit the hull and the hull tilts, the position of the bearing 1 is offset, for example, it offsets to the right. During the offset process of the bearing 1, the right dynamic support assembly 3 is driven to retract inward, and the return spring 32 is compressed by the telescopic rod 31. The return spring 32 and the hydraulic oil are used to buffer the instantaneous kinetic energy of the bearing 1 when it offsets. At the same time, the rubber block 81 is driven to twist and deform when the bearing 1 offsets, causing the rubber block 81 to deflect to the right. At this time, the twisting force of the rubber block 81 is used to drive the rotating plate 6 and the connecting rod 73 to rotate, thereby offsetting the position of the latch 72 and the stop rod 74. The force direction of the top end of the stop rod 74 changes, breaking the original equilibrium state, so that the radial component of force on the bottom end of the stop rod 74 exceeds the restraining capacity of the positioning hole 75, and then moves out of the positioning hole 75. At the same time, the latch 72 is driven downward by the elastic restoring force of the support spring 71 and fits into the guide groove 751.

[0064] After the force of the waves weakens, the elastic force of the return spring 32 drives the bearing 1 to move to the left until the bearing 1 is reset. During the resetting movement of the bearing 1, the rubber block 81 and the rotating plate 6 are driven to reverse. At this time, the connecting rod 73 drives the pin 72 to slide along the guide groove 751. When the bearing 1 is reset, the pin 72 is inserted into the positioning hole 75 to form a self-locking function and fix the position of the bearing 1, thereby limiting the position of the bearing 1.

[0065] Throughout this specification, references to terms such as "one embodiment," "example," or "specific example" indicate that a specific feature, structure, material, or characteristic described in conjunction with that embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, schematic representations of these terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0066] The above shows and describes the basic principles, main features and advantages of the present disclosure. Those skilled in the art should understand that the present disclosure is not limited to the above embodiments. The above embodiments and descriptions are merely illustrative of the principles of the present disclosure. Various changes and improvements may be made to the present disclosure without departing from the spirit and scope of the present disclosure, and such changes and improvements shall fall within the scope of the present disclosure.

Claims

1. A ship bearing load measuring device, characterized in that: include: Bearing (1), dynamic support assembly (3) and rotating plate (6); A jack (4) for supporting a ship bearing (1), wherein a pressure sensor (5) is fixed to the upper end of the jack (4), the jack (4) is located directly below the bearing (1), a support frame (2) is provided between the jack (4) and the bearing (1), and the center of gravity of the bearing (1), the center of gravity of the pressure sensor (5) and the central axis of the jack (4) coincide with each other, and a plurality of groups of dynamic support components (3) are symmetrically provided on both sides of the bottom of the bearing (1); The dynamic support assembly (3) comprises a telescopic rod (31), a return spring (32) and a support rod (33); the telescopic rod (31) is fixed to the inner wall of the support frame (2), and the return spring (32) is fixed to the inner side of the telescopic rod (31); the support rod (33) is fixed on the side of the telescopic rod (31) close to the bearing (1); the return spring (32) is used to provide a displacement buffer space for the bearing (1), which is conducive to reducing the rigid impact load between the bearing (1) and the support frame (2); A positioning ring (8) is sleeved at the center of gravity of the outer side of the bearing (1), and a plurality of rotating plates (6) are inserted directly below the positioning ring (8), and a self-locking component (7) is fixed between the plurality of rotating plates (6).

2. The ship bearing load measuring device according to claim 1, characterized in that: A groove (331) is provided on one side of the support rod (33) close to the positioning ring (8), and the depth of the groove (331) is adapted to the thickness of the positioning ring (8).

3. The ship bearing load measuring device according to claim 2, characterized in that: The working end surface of the support rod (33) forms a V-shaped support structure, and the symmetry axis of the support rod (33) coincides with the vertical center line of the pressure sensor (5).

4. The ship bearing load measuring device according to claim 3, characterized in that: A flow channel (21) is provided on the inner side of the support frame (2), and one end of the flow channel (21) close to the bearing (1) is connected to the piston cavity of the telescopic rod (31), and the flow channel (21) is filled with hydraulic oil.

5. The ship bearing load measuring device according to claim 1, characterized in that: A support plate (9) is fixed to one end of the flow channel (21) away from the telescopic rod (31), and a thread groove (91) is provided through the middle of the support plate (9). A piston plate (10) is slidably provided on the inner side of the flow channel (21), and a screw (101) adapted to the thread groove (91) is fixed to one end of the piston plate (10) close to the support plate (9), and the moving path of the piston plate (10) is the same as the path of the flow channel (21).

6. The ship bearing load measuring device according to claim 2, characterized in that: A plurality of rubber blocks (81) pointing vertically downward are fixed directly below the positioning ring (8), and a plurality of rotating plates (6) corresponding to the rubber blocks (81) are provided in the middle of the upper end of the support frame (2), and the middle of the rotating plates (6) are rotatably connected to the two ends of the support frame (2).

7. The ship bearing load measuring device according to claim 1, characterized in that: A micrometer (11) is fixed directly above the support frame (2).

8. The ship bearing load measuring device according to claim 6, characterized in that: A rotating shaft (22) is fixed to the side wall of the support frame (2) perpendicular to the central axis of the bearing (1), and extension plates (61) are fixed to both ends of the rotating plate (6), and a rotating hole (62) adapted to the rotating shaft (22) is provided in the middle of the extension plate (61), and the rotating plate (6) is rotatably connected to the support frame (2) through the rotating hole (62) and the rotating shaft (22).

9. The ship bearing load measuring device according to claim 1, characterized in that: The self-locking assembly (7) comprises a supporting spring (71), a latch (72), a connecting rod (73), a blocking rod (74) and a positioning hole (75); a connecting rod (73) is rotatably connected between the two rotating plates (6); the upper end of the connecting rod (73) is rotatably connected to the latch (72); the upper end of the latch (72) is provided with a supporting spring (71); the latch (72) is close to one end of the connecting rod (73) to fix the blocking rod (74); a positioning hole (75) is provided at the upper end of the support frame (2); the blocking rod (74) is fixed to the inner side of the positioning hole (75) by friction.

10. The ship bearing load measuring device according to claim 9, characterized in that: Guide grooves (751) are provided on both sides of the positioning hole (75), and the paths of the guide grooves (751) are the same as the moving paths of the latch pins (72) when the rotating plate (6) is deflected.

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