A method for cooperative simulation modeling of a hatch door movement mechanism system

Abstract

The application discloses a kind of cabin door movement mechanism system cooperative simulation modeling method, comprising: constructing parameterized entity model and importing engineering analysis software to extract physical property parameters;The physical property parameters extracted are imported into multi-body dynamics solver, and the multi-body dynamics model of the latch mechanism, lifting mechanism and pressure relief valve mechanism is constructed;Define the time-sequential movement stage of cabin door opening: a. Latch mechanism unlocking and cabin door pressure relief valve opening stage;B. Cabin door lifting stage;C. Cabin door rotation opening and positioning stage;Respectively for latch mechanism, lifting mechanism and pressure relief valve mechanism, analyze the motion characteristics;Extract key motion change curve, verify the motion function of the model.The application method realizes the dynamic performance simulation analysis of the whole process of cabin door opening / closing by constructing multi-body dynamics model, fusing spring boost, clearance friction and other influencing factors, to provide reliable basis for the design optimization and verification of cabin door mechanism.

Description

Technical Field

[0001] This application belongs to the field of simulation technology of door motion mechanism, specifically involving a collaborative simulation modeling method for a door motion mechanism system. Background Technology

[0002] As one of the main mechanical systems of an aircraft, the normal opening and closing function of the aircraft door mechanism plays a decisive role in the safety and maneuverability of the aircraft. Given the importance of the aircraft door mechanism, it is particularly crucial to conduct motion simulation to verify its functionality during the design process, as this directly relates to the rationality and reliability of the door mechanism design.

[0003] During the design phase of the hatch mechanism, a dynamic simulation model is typically constructed to ensure the rationality of the design. By performing dynamic simulations on the opening and closing processes of the hatch mechanism and obtaining output characteristic curves based on the simulation results, the motion function of the hatch mechanism can be verified. This process not only provides direction for the optimization and improvement of the hatch mechanism but also provides a strong basis for determining relevant parameters.

[0004] However, current patents related to aircraft door mechanisms cover relatively simple door motion patterns, applicable only to door mechanisms with a single motion mode. For door systems with multiple submechanisms, existing technologies cannot achieve collaborative simulation modeling. Actual aircraft door mechanisms often involve multiple subsystems such as latches, pressure relief valves, and lifting assistance systems. These subsystems work together to ensure the normal opening and closing of the door. However, the lack of collaborative simulation modeling technology for such complex door mechanisms results in a lack of systematic quantitative analysis methods when analyzing key performance aspects such as the motion coordination between components, clearance effects, and lifting assistance effects. This situation can easily lead to a series of problems, such as the door failing to open smoothly or serious malfunctions like unexpected unlocking during flight, posing a significant threat to flight safety. Therefore, developing a technology capable of collaborative simulation modeling and quantitative analysis of key performance aspects of aircraft door mechanisms with multiple submechanisms is of significant practical importance. Summary of the Invention

[0005] In view of this, in order to solve the problem of evaluating the motion function of complex hatch systems with multiple sub-mechanisms, this application provides a collaborative simulation modeling method for hatch motion mechanism systems. By constructing a multibody dynamics model of the latch lock mechanism, lifting mechanism and pressure relief valve mechanism, and integrating influencing factors such as spring assistance and clearance friction, the dynamic performance simulation analysis of the entire hatch opening / closing process is realized, providing a reliable basis for the design optimization and verification of the hatch mechanism.

[0006] To achieve the above technical objectives, this application specifically implements the following technical solution:

[0007] In one aspect of this application, a collaborative simulation modeling method for a hatch motion mechanism system is provided, comprising the following steps:

[0008] S1: Import the parametric solid model of the hatch system built by 3D modeling software into the engineering analysis software, analyze and extract the mass, moment of inertia, center of mass position and geometric dimension parameters of each component, and build a physical property database.

[0009] S2: Import the physical property database into the multibody dynamics solver, construct a coupled multibody dynamics model based on the topological relationship of the pin lock mechanism, lifting mechanism and pressure relief valve mechanism, and set the constraint pairs, driving functions and contact forces according to the actual motion relationship;

[0010] S3: Define the sequential motion stages of hatch opening: a. Locking mechanism unlocking and hatch pressure relief valve opening stage; b. Hatch lifting stage; c. Hatch rotation opening and positioning stage;

[0011] S4: Analysis of the coupled motion characteristics of multiple mechanisms:

[0012] For the bolt lock mechanism, a mapping model of the bolt movement trajectory, retraction stroke and wear clearance on the movement accuracy and contact force is established;

[0013] For the lifting mechanism, a coupled correlation model is constructed to determine the effect of the change in the elastic force of the assist spring and friction factors on the force characteristics of the main transmission rod.

[0014] For the pressure relief valve mechanism, we analyze its dynamic response characteristics during the opening process and the angular displacement input of the door handle.

[0015] S5: Parameter Response Verification:

[0016] Extract the dynamic response feature dataset during the multibody dynamics simulation, and verify the matching between the model's motion function and the target performance based on the dynamic response feature dataset and the error tolerance of the design parameters.

[0017] In one implementation, in step S1: a parametric solid model of the hatch system is created using the 3D modeling software UG, and imported into CATIA using the Parasolid intermediate format to build a physical property database.

[0018] In one implementation, the multibody dynamics solver in step S2 uses the ADAMS simulation platform.

[0019] In one embodiment, the bolt lock mechanism is a single-sided bolt linkage lock mechanism, including a bolt, a connecting arm, a double-headed rocker arm, and a handle, and uses a rotary joint and translational joint connection method to realize the transmission and coordinated action between the components.

[0020] In one implementation, during the unlocking phase of the bolt lock mechanism, the handle is rotated to unlock or lock the mechanism. When the bolt lock mechanism is in the closed state, the bolt is located in the lock hole of the lock seat. When the bolt lock mechanism is in the open state, the bolt retracts and disengages from the lock seat under the action of the handle.

[0021] In one implementation, the end of the pin is set as a motion characteristic measurement point.

[0022] In one embodiment, the lifting mechanism includes a main lifting mechanism and an auxiliary lifting mechanism; the main lifting mechanism includes an auxiliary lifting spring, and the auxiliary lifting mechanism includes a main lifting spring, the main lifting spring triggering the auxiliary lifting spring, and the auxiliary lifting spring providing a lifting force.

[0023] In one implementation, during the door lifting phase, after the latch lock mechanism is released, the lifting mechanism is activated, and the door is lifted under the combined action of the main assist spring and the auxiliary assist spring.

[0024] In one implementation, during the hatch rotation opening and positioning stage, after the hatch is raised to the position, the sliding door body rotates open to a predetermined angle and locks the hatch.

[0025] In one embodiment, the structural features of the pressure relief valve mechanism include a pressure relief valve, a pressure relief valve rocker arm, and a torsion spring; the opening pin locking mechanism drives the pressure relief valve rocker arm to rotate, so that the pressure relief valve opens synchronously under the action of the torsion spring.

[0026] In one implementation, the verification content in step S5 includes: the relationship between the distance the center of gravity of the bolt moves and the rotation angle of the door handle; the curve of the distance between the end of the bolt locking rod and the lock hole; and the response relationship between the opening angle of the pressure relief valve and the rotation angle of the door handle.

[0027] This application utilizes ADAMS to perform co-simulation modeling of the latch lock mechanism, pressure relief valve mechanism, and lifting mechanism in the hatch mechanism. It then conducts motion characteristic analysis of the hatch mechanism and obtains the key output responses of the hatch mechanism's motion, achieving the following significant results:

[0028] 1) It realizes collaborative modeling and motion analysis of multiple key sub-mechanisms of the hatch under ADAMS, and fully reflects the actual motion process of the hatch;

[0029] 2) Key influencing factors such as structural clearance, spring deformation, and friction were considered, and the analysis results are highly consistent with the actual situation;

[0030] 3) It can be used to predict the impact of different design parameters (such as spring stiffness and clearance) on motion performance, assisting designers in parameter optimization;

[0031] 4) This method is applicable to the modeling and simulation of various aircraft door motion mechanisms, and can also be extended to the dynamic performance evaluation of other complex multibody mechanisms. Attached Figure Description

[0032] Figure 1 This is the door movement mechanism in the embodiments of this application;

[0033] Figure 2 This is a schematic diagram of the process of unlocking the bolt lock and opening the pressure relief valve in an embodiment of this application; where a is and b is;

[0034] Figure 3 This is a schematic diagram of the operation of the hatch lifting mechanism according to an embodiment of this application; wherein, a is the process of the main assist spring lifting the hatch, and b is the operation process of the auxiliary lifting mechanism;

[0035] Figure 4 This is a schematic diagram of the operation of the gust lock in an embodiment of this application;

[0036] Figure 5 This is a simulation model of the latch lock mechanism in the embodiments of this application;

[0037] Figure 6 These are the motion characteristics of the latch lock mechanism under different clearance conditions in the embodiments of this application;

[0038] Figure 7 This refers to the contact force at the spherical bearing under different wear clearance conditions in the embodiments of this application;

[0039] Figure 8 This is a simulation model of the main lifting mechanism and the auxiliary lifting mechanism of the hatch in the embodiments of this application;

[0040] Figure 9 This is the curve showing the change in the elastic force of the assist spring during the simulation of the door lifting mechanism in this embodiment of the application; where the solid red line corresponds to the auxiliary assist spring and the dashed blue line corresponds to the main assist spring.

[0041] Figure 10 The curves show the change in torque on the main transmission rod with and without the assist spring in the embodiments of this application; where the solid red line corresponds to the case with the assist spring and the dashed blue line corresponds to the case without the assist spring.

[0042] Figure 11 This is a curve showing the change in torque magnitude of the main transmission rod under varying frictional conditions according to an embodiment of this application; where the solid red line corresponds to a friction coefficient of 0.01, and the solid blue dashed line corresponds to a friction coefficient of 0.02.

[0043] Figure 12 This is a simulation model of the pressure relief valve mechanism in the embodiments of this application;

[0044] Figure 13These are simulation results of the hatch lifting process in the embodiments of this application;

[0045] Figure 14 This is a graph showing the change of the centroid ordinate of the rocker arm limiting bolt with the rotation angle of the inner door handle in an embodiment of this application;

[0046] Figure 15 This application describes the relationship between the opening angle of the pressure relief valve and the rotation angle of the inner door handle in the embodiments of this application.

[0047] Figure 16 This application describes the relationship between the distance the pin's center of gravity moves and the rotation angle of the inner door handle in this embodiment.

[0048] Figure 17 This application describes the relationship between the distance between the end of the latch rod and the latch hole as a function of the rotation angle of the inner door handle.

[0049] In the picture:

[0050] 1-Pin lock mechanism, 11-Pin, 12-Connecting arm, 13-Double-head rocker arm, 14-Threaded moving connecting rod, 15-Pin pressure relief valve shaft, 16-Connecting rod, 17-Cam connecting rod, 18-Cam, 19-Splined shaft, 20-Pull rod;

[0051] 2-Pressure relief valve mechanism, 21-Pressure relief valve, 22-Pressure relief valve rocker arm, 23-Adjustable stud, 24-Pressure relief valve bolt, 25-Bolt shaft, 26-Torsion spring, 27-Pressure relief valve support, 28-Rotating shaft, 29-Rotating shaft rocker arm, 30-Fixed support;

[0052] 3-Lifting mechanism, 31-Main assist spring, 32-Auxiliary assist spring, 33-Main transmission rod, 34-Lower lifting rocker arm, 35-Torque tube, 36-Upper rocker arm limit bolt, 37-C-type connecting rod, 38-Linkage shaft, 39-Upper lifting rocker arm;

[0053] 4-Inner handle; 5-Outer handle; 6-Main hinge; 7-Wind lock mechanism. Detailed Implementation

[0054] The technical solution of this application will be clearly and completely described below with reference to specific embodiments. However, those skilled in the art will understand that the embodiments described below are only some embodiments of this application, not all embodiments, and are only used to illustrate this application, and should not be regarded as limiting the scope of this application. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0055] In one embodiment, a collaborative simulation modeling method for a hatch motion mechanism system is provided, comprising the following steps:

[0056] S1: Import the parametric solid model of the hatch system built by 3D modeling software into the engineering analysis software, analyze and extract the mass, moment of inertia, center of mass position and geometric dimension parameters of each component, and build a physical property database.

[0057] This enables the standardized acquisition and cross-platform transmission of physical property data for the hatch system, providing an accurate initial parameter set for multibody dynamics simulation.

[0058] Specifically, the parametric solid model of the hatch system is constructed using the 3D modeling software UG. After the parametric solid model of the hatch system is completed, it is exported to a preset intermediate format. The selection of the intermediate format needs to consider universality and compatibility to ensure smooth transmission and parsing between different software platforms. This solution covers common formats such as Parasolid.

[0059] CATIA software was used for engineering analysis. The exported parametric solid model files of the hatch system in intermediate formats such as Parasolid were imported into CATIA. During the import process, CATIA automatically parsed the intermediate format files, identifying and reconstructing the geometric information and assembly relationships of the model. After the import was complete, the 3D model of the hatch system was viewed in the CATIA software interface to ensure that the model import was accurate.

[0060] S2: Import the physical property database into the multibody dynamics solver, construct a coupled multibody dynamics model based on the topological relationship of the pin lock mechanism, lifting mechanism and pressure relief valve mechanism, and set the constraint pairs, driving functions and contact forces according to the actual motion relationship.

[0061] By integrating multiple sub-mechanisms through a unified dynamics framework, this approach overcomes the limitations of existing technologies in the collaborative simulation of complex systems. It enables the unified construction of coupled dynamic models of multiple mechanisms, accurately simulating the collaborative motion behavior of the hatch system under actual operating conditions. Kinematic constraints and contact force modeling precisely reproduce the energy transfer path of the mechanical system.

[0062] Specifically, the multibody dynamics solver uses the ADAMS simulation platform.

[0063] Based on the actual opening and closing motion of the hatch in the ADAMS / View environment, corresponding connection constraints, kinematic pairs, driving functions, and contact relationships are added to each component of the model. Among them, kinematic pairs include, but are not limited to, revolute pairs and translational pairs.

[0064] S3: Define the sequential motion stages of hatch opening: the unlocking stage of the latch lock mechanism and the opening stage of the hatch pressure relief valve, the hatch lifting stage, and the hatch rotation opening and positioning stage.

[0065] During the unlocking of the bolt lock mechanism and the opening of the cabin door pressure relief valve: The bolt lock mechanism is manually locked or unlocked by rotating the handle from inside or outside the cabin. Simultaneously, the pressure relief valve mechanism works in conjunction to balance the pressure difference between the inside and outside of the cabin door. When the bolt lock mechanism is closed, the bolt is located within the lock hole of the lock seat. When the bolt lock mechanism is open, the bolt retracts and disengages from the lock seat under the action of the inner or outer handle.

[0066] During the door lifting phase: After the latch lock mechanism is released, the lifting mechanism is activated. Under the combined action of the main assist spring and the auxiliary assist spring, the door is lifted to a certain height, avoiding direct force to open and improving safety.

[0067] During the hatch rotation opening and positioning phase: After the hatch is raised to the position, push and pull the door body to make it rotate around the main hinge and finally open to the predetermined angle. The gust lock mechanism automatically locks the hatch during this phase to prevent accidental closure in strong wind or vibration environments.

[0068] S4: Multi-mechanism coupled motion characteristic analysis: For the latch lock mechanism, establish a mapping model of the latch movement trajectory, retraction stroke and wear gap on motion accuracy and contact force; for the lifting mechanism, construct a coupled correlation model of the change of spring force and friction factors on the force characteristics of the main transmission rod; for the pressure relief valve mechanism, analyze its opening process and the dynamic response characteristics of the door handle angular displacement input.

[0069] Motion characteristics analysis of the pin lock mechanism: The pin lock mechanism is a single-sided pin linkage lock mechanism, including a pin, connecting arm, double-headed rocker arm, threaded moving linkage, pin pressure relief valve shaft, linkage, cam linkage, cam, spline shaft, inner / outer handle linkage rod, and inner / outer handle mechanism. It adopts the connection method of rotary joint and translational joint to realize the transmission and coordinated action between components.

[0070] In some embodiments, for the latch linkage lock mechanism, the common concern is whether the latch can be inserted into the latch hole to prevent the hatch from opening accidentally when closed. Therefore, the left end point of the latch is selected as the motion characteristic measurement point.

[0071] Kinematic characteristics analysis of the pressure relief valve mechanism: The pressure relief valve mechanism includes, but is not limited to, components such as a pressure relief valve valve arm, adjustable stud, pressure relief valve bolt, bolt shaft, torsion spring, and pressure relief valve support. Rotating the inner / outer handle mechanism drives the rotating shaft to rotate via the splined shaft, cam, and connecting rod assembly. The rotating shaft rocker arm, rigidly connected to the rotating shaft, transmits the motion to the pressure relief valve rocker arm through a tie rod mechanism, causing it to rotate around the bolt shaft.

[0072] Analysis of the motion characteristics of the lifting mechanism: The structural features of the lifting mechanism include a main lifting mechanism, a power-assisted lifting mechanism, and a guiding mechanism. The structural features of the power-assisted lifting mechanism include a main power-assisted spring and an auxiliary power-assisted spring. During the hatch lifting phase, the main power-assisted spring and the auxiliary power-assisted spring work together to drive the lifting mechanism. The main power-assisted spring triggers the auxiliary power-assisted spring, and the auxiliary power-assisted spring provides the main lifting force.

[0073] S5: Parameter Response Verification:

[0074] Extract the dynamic response feature dataset during the multibody dynamics simulation, and verify the matching between the model's motion function and the target performance based on the dynamic response feature dataset and the error tolerance of the design parameters.

[0075] Specifically, the verification content includes: the relationship between the distance the pin's center of gravity moves and the rotation angle of the door handle, the curve of the distance between the pin end and the key hole, and the response relationship between the opening angle of the pressure relief valve and the rotation angle of the door handle.

[0076] Example

[0077] This embodiment, combining the typical motion relationships and structural characteristics of the right hatch at the front of the cabin of a large amphibious aircraft, proposes a collaborative simulation modeling method for the door motion mechanism system. (Refer to...) Figure 1 As shown, the hatch motion mechanism system mainly includes three sub-mechanisms: the latch lock mechanism 1, the pressure relief valve mechanism 2, and the lifting mechanism 3, as well as the inner handle 4, the outer handle 5, the main hinge 6, and the gust lock mechanism 7. The specific modeling and simulation process is as follows:

[0078] Based on the geometry, assembly relationships, and motion characteristics of actual aircraft door components, a complete parametric solid model of the door system was created using the 3D modeling software UG. The completed parametric solid model was then exported as a Parasolid file, a universal intermediate format, enabling data exchange with a multibody dynamics simulation platform.

[0079] Key physical properties of each component are extracted in CATIA software, specifically including parameter data for key physical properties such as mass, moment of inertia, center of mass position, and geometric dimensions. The extracted parameter data is then imported into the ADAMS simulation platform as initial input data. In the ADAMS / View environment, based on the actual opening and closing motion of the hatch, corresponding connection constraints, kinematic pairs (such as revolute and translational pairs), driving functions, and contact relationships are added to each component of the model to ensure that the model accurately reflects the actual motion behavior of the hatch.

[0080] The hatch opening process consists of three stages:

[0081] 1) Initial unlocking and depressurization phase: When operating from inside the cabin, the operator raises the inner handle 4; when operating from outside, the operator rotates the outer handle 5 counterclockwise. This action drives the latch locking mechanism 1 and the depressurization valve mechanism 2 to work together, causing the latch 11 to retract and disengage from the lock hole. At the same time, the depressurization valve mechanism 2 opens, balancing the air pressure difference inside and outside the cabin (see...). Figure 2 ).

[0082] 2) Door Lifting Stage: After the latch lock mechanism 1 is released, the lifting mechanism 3 is activated. Under the combined action of the main assist spring 31 and the auxiliary assist spring 32, the door is lifted to a certain height, avoiding direct force to open and improving safety (see...). Figure 3 ).

[0083] 3) Door Rotation Opening and Positioning Stage: After the door is raised to the correct position, the operator can manually push or pull the door to rotate it around the main hinge 6 and finally open it to the predetermined angle. During this stage, the gust lock mechanism 7 automatically locks the door to prevent accidental closure in strong winds or vibrations (see...). Figure 4 ).

[0084] Motion characteristics analysis of bolt lock mechanism 1:

[0085] As the main locking device for the hatch, the bolt lock mechanism 1's motion characteristics directly affect the hatch's sealing and security. In the co-simulation model, the bolt lock mechanism 1 is a single-sided bolt linkage lock mechanism (e.g., Figure 5 As shown, it mainly consists of a pin 11, a connecting arm 12, a double-headed rocker arm 13, a threaded moving connecting rod 14, a pin-type pressure relief valve shaft 15, a connecting rod 16, a cam connecting rod 17, a cam 18, a splined shaft 19, and a pull rod 20. It uses a rotary joint and a translational joint connection method to realize the transmission and coordinated action between components.

[0086] The bolt lock mechanism 1 is manually locked and unlocked. Operators can unlock and lock the bolt lock mechanism 1 by rotating the handle from inside or outside the cabin. When the bolt lock mechanism 1 is closed, the bolt 11 extends and enters the lock seat's keyhole, restricting the door's inward movement and preventing it from opening, thus locking the door. To open the bolt lock mechanism 1, the outer handle 5 should be pushed upward to rotate it around its axis. Under the action of the lever assembly, the bolt 11 retracts, disengaging from the lock seat's restriction, thus opening the bolt lock mechanism 1. At this point, the door can be opened outward. The locking process is the reverse of the unlocking process, and the principle is the same.

[0087] For the bolt lock mechanism 1, the usual concern is whether the bolt 11 can be inserted into the lock seat hole to prevent the hatch from being opened accidentally when closed. Therefore, the left end point of the bolt 11 is selected as the motion characteristic measurement point.

[0088] The latching mechanism 1 completes one working stroke, which involves a cycle of unlocking and locking. The entire simulation process takes 1 second, with the first 0.5 seconds being the unlocking process and the last 0.5 seconds being the locking process.

[0089] Figure 6 The figure shows the positional changes of the characteristic points of the pin lock under different wear clearances. It can be seen that the smaller the error at the joint bearing in the pin lock mechanism 1, the smoother and more accurate the movement of pin 11. Conversely, the larger the error, the more significant the oscillation of pin 11, and the lower the movement accuracy. The simulation results are consistent with the actual situation.

[0090] Figure 7 The figure shows the magnitude of the contact force at the spherical plain bearing under different clearance conditions. The figure shows that the smaller the clearance at the spherical plain bearing, the smaller the contact force. Conversely, the larger the clearance at the spherical plain bearing, the greater the contact force, which further aggravates the wear of the spherical plain bearing.

[0091] Motion characteristic analysis of lifting mechanism 3:

[0092] The lifting mechanism 3 is used to smoothly raise the door from its closed state to the position to be opened after the door is unlocked. The lifting mechanism 3 consists of a main lifting mechanism and an auxiliary lifting mechanism, which are driven by the main transmission rod 33. Its structural diagram is shown below. Figure 8 As shown. The lifting mechanism 3 is equipped with two main assist springs: a main assist spring 31 and an auxiliary assist spring 32. The trend of their output spring force changing with the hatch opening angle is as follows. Figure 9 As shown. The main assist spring 31 is mainly used to activate the auxiliary assist spring 32. Its own output is relatively small, while the auxiliary assist spring 32 provides the main lifting force during the movement of the mechanism, which can effectively maintain the stability of the hatch within a specific height range.

[0093] Figure 10 The simulation compares the torque changes of the main transmission rod 33 with and without the assist spring. The solid red line represents the torque curve with the spring, while the dashed blue line corresponds to the case without the spring. At 70 seconds of simulation (corresponding to the door handle rotating 70 degrees), the assist spring begins to function. The torque of the main transmission rod 33 reaches its peak at approximately 90 degrees, representing the maximum manual force required to open the door. The assist effect is most significant after approximately 120 degrees, allowing the door to remain open. Without the assist spring, as the door rises, the torque of the main transmission rod 33 continuously increases, reaching its maximum value (approximately 37000 N·mm) at a specific height. If the external force is removed at this point, the door will fall due to its own weight, failing to achieve its opening and holding functions.

[0094] In addition, friction at each hinge point and at the sequence controller in the mechanism also has a significant impact on motion performance. Figure 11The figure shows a comparison of the torque variation on the main transmission rod 33 under different friction coefficients (0.01 and 0.02). The results indicate that as the friction coefficient increases, the torque on the main transmission rod 33 increases significantly, meaning the operator needs to apply a larger torque to lift the hatch, which is highly consistent with actual operating experience. This demonstrates that friction has a significant impact on the performance of the main transmission rod 33 and must be fully considered in the design and analysis.

[0095] Kinematic characteristics analysis of pressure relief valve mechanism 2:

[0096] Before opening the hatch, to prevent the pressure difference between the inside and outside of the cabin from affecting the structure and personnel safety, pre-pressure relief valve mechanism 2 is required for depressurization. (Refer to...) Figure 12 As shown, the pressure relief valve mechanism 2 mainly includes a pressure relief valve 21, a pressure relief valve rocker arm 22, an adjustable stud 23, a pressure relief valve bolt 24, a bolt shaft 25, a torsion spring 26, a pressure relief valve support 27, a rotating shaft 28, a rotating shaft rocker arm 29, a fixed support 30, and other components. Its multibody dynamics simulation model is as follows: Figure 12 As shown. Its working process is as follows: Rotating the inner / outer handle mechanism drives the rotating shaft 28 to rotate via the splined shaft 19, cam 18, and connecting rod assembly. The rotating shaft rocker arm 29, rigidly connected to the rotating shaft 28, transmits the motion to the pressure relief valve rocker arm 22 through a pull rod mechanism, causing it to rotate around the bolt shaft 25. Since a torsion spring 26 is provided between the pressure relief valve 21 and the fixed support 30, this rotational action will further cause the pressure relief valve 21 to open synchronously under the action of the elastic force, realizing the pressure relief function.

[0097] Analysis of the motion characteristics of the hatch lifting system:

[0098] Simulation results of the hatch lifting process are as follows: Figure 13 , Figure 13 (a) This represents the initial state of the hatch lifting process, where both the auxiliary and main assist springs are in an untriggered state. Rotating the inner / outer handle of the hatch first triggers the pressure relief valve mechanism 2 and the latch lock mechanism 1, completing the opening process of the pressure relief valve mechanism 1 and the unlocking process of the latch lock mechanism 1. Continuing to rotate the inner / outer handle of the hatch, the movement is transmitted to the linkage shaft 38 via the spline shaft 19. The C-shaped connecting rod 37 rotates with the linkage shaft 38 and exerts a squeezing force on the lifting rocker arm 39, using the cross hinge on the main hinge 6 as a fulcrum, driving the hatch to lift upwards. As the hatch continues to lift, the rotation of the linkage shaft 20 activates the auxiliary assist spring 32, at which point the hatch movement is as follows: Figure 13 As shown in (b), the activation of the auxiliary spring 32 lays the foundation for and provides power to trigger the main spring 31. As the hatch continues to lift, the rotation of the lower lifting rocker arm 34 triggers the main spring 31 via the torque tube 35. Subsequently, under the combined action of the main spring 31 and the auxiliary spring 32, the hatch moves upwards and reaches the desired position. Figure 13 (c) shows the state

[0099] After the cabin door is fully opened, it will be locked by the gust lock mechanism 7. The closing process of the cabin door is the reverse process of the opening process. When the cabin door lifting height cannot meet the minimum height required for the guide rollers to move out of or slide into the guide groove smoothly, the cabin door will not be able to open or close smoothly. Therefore, the cabin door lifting system plays a crucial role in the normal operation of the cabin door. Since there is a fixed constraint between the upper rocker arm limit bolt 36 and the aircraft cabin door frame structure in the simulation model of the aircraft cabin door lifting system, the change in the position of the center of mass of the upper rocker arm limit bolt 36 can be used to represent the change in the position of the center of mass of the aircraft cabin door. Figure 14 The graph shows the change of the longitudinal coordinate of the center of mass of the upper rocker arm limit bolt 36 with the rotation angle of the inner door handle. The difference between the final value and the initial value of the longitudinal coordinate of the center of mass of the upper rocker arm limit bolt 36 is the effective lifting height of the hatch.

[0100] Through simulation analysis, the deformation of the main assist spring 31 and the auxiliary assist spring 32, as well as the change curves of the spring force during the door lifting process, can be obtained, such as... Figure 15 As shown, the horizontal axis represents the rotation angle of the inner door handle. The opening angle of the pressure relief valve can be indirectly obtained by setting three marker points at different positions. The measurement results of the pressure relief valve opening angle are shown in [reference needed]. Figure 15 The horizontal axis represents the rotation angle of the door handle inside the hatch. When the bolt lock mechanism 1 is unlocked, the bolt 11 retracts inward under the action of the linkage. When the bolt 11 retracts inward into the door frame and is released from the lock seat restriction, the bolt lock mechanism 1 is in the open state.

[0101] The relationship between the distance the center of mass of latch 11 moves and the rotation angle of the inner door handle during the opening of the hatch is shown in the figure. Figure 16 When the bolt lock mechanism 1 is fully open, the bolt 11 can be fully retracted, and at this time the distance between the end of the bolt 11 and the lock hole should be less than 0.

[0102] Figure 17 The change curve of the distance between the end of the latch 11 and the lock hole of the lock seat during the opening of the hatch was measured. The simulation results show that the latch 11 has good motion accuracy throughout the entire movement process and can meet the structural clearance requirements for unlocking.

[0103] Although the embodiments of this application have been described above in conjunction with the accompanying drawings, this application is not limited to the specific embodiments and application fields described above. The specific embodiments described above are merely illustrative and instructive, not restrictive. Those skilled in the art can make many other forms based on the guidance of this specification and without departing from the scope of protection of the claims of this application, and these are all within the scope of protection of this application.

Claims

1. A collaborative simulation modeling method for a hatch motion mechanism system, characterized in that, include: S1: Import the parametric solid model of the hatch system built by 3D modeling software into the engineering analysis software, analyze and extract the mass, moment of inertia, center of mass position and geometric dimension parameters of each component, and build a physical property database. S2: Import the physical property database into the multibody dynamics solver, construct a coupled multibody dynamics model based on the topological relationship of the pin lock mechanism, lifting mechanism and pressure relief valve mechanism, and set the constraint pairs, driving functions and contact forces according to the actual motion relationship; S3: Define the sequential movement stages of hatch opening: a. Locking mechanism unlocking and pressure relief valve mechanism opening stage; b. Hatch opening stage; c. Door rotation, opening, and positioning stage; S4: Analysis of the coupled motion characteristics of multiple mechanisms: For the bolt lock mechanism, a mapping model of the bolt movement trajectory, retraction stroke and wear clearance on the movement accuracy and contact force is established; For the lifting mechanism, a coupled correlation model is constructed to determine the effect of the change in the elastic force of the assist spring and friction factors on the force characteristics of the main transmission rod. For the pressure relief valve mechanism, we analyze its dynamic response characteristics during the opening process and the door handle rotation angle input; S5: Parameter Response Verification: Extract the dynamic response feature dataset during the multibody dynamics simulation, and verify the matching between the model's motion function and the target performance based on the dynamic response feature dataset and the error tolerance of the design parameters. The pin lock mechanism is a single-sided pin linkage lock mechanism, including a pin, a connecting arm, a double-headed rocker arm, and a handle. It uses a rotary joint and a translational joint connection method to realize the transmission and coordinated action between the components; the end of the pin is set as a motion characteristic measurement point. The lifting mechanism includes a main lifting mechanism and a booster lifting mechanism; the main lifting mechanism includes an auxiliary booster spring, the booster lifting mechanism includes a main booster spring, the main booster spring triggers the auxiliary booster spring, and the auxiliary booster spring provides lifting force. The structural features of the pressure relief valve mechanism include a pressure relief valve, a pressure relief valve rocker arm, and a torsion spring; the opening pin locking mechanism drives the pressure relief valve rocker arm to rotate, so that the pressure relief valve opens synchronously under the action of the torsion spring; The verification content in step S5 includes: the curve of the change in distance between the end of the pin and the lock seat of the pin lock mechanism.

2. The collaborative simulation modeling method according to claim 1, characterized in that, In step S1: A parametric solid model of the hatch system is created using the 3D modeling software UG, and the Parasolid intermediate format is used to import it into CATIA to build a physical property database.

3. The collaborative simulation modeling method according to claim 1, characterized in that, During the unlocking phase of the bolt lock mechanism, pushing the handle to rotate completes the unlocking or locking of the bolt lock mechanism. When the bolt lock mechanism is in the closed state, the bolt is located in the lock hole of the lock seat. When the bolt lock mechanism is in the open state, the bolt retracts and disengages from the lock seat under the action of the handle.

4. The collaborative simulation modeling method according to claim 1, characterized in that, During the door lifting phase, after the latch lock mechanism is released, the lifting mechanism is activated, and the door is lifted under the combined action of the main assist spring and the auxiliary assist spring.

5. The collaborative simulation modeling method according to claim 1, characterized in that, During the hatch rotation opening and positioning phase, after the hatch is raised to the correct position, the sliding door rotates open to the predetermined angle and locks the hatch.

6. The collaborative simulation modeling method according to claim 1, characterized in that, The verification content in step S5 includes: the relationship between the distance the pin's center of gravity moves and the rotation angle of the door handle; and the response relationship between the opening angle of the pressure relief valve mechanism and the rotation angle of the door handle.

Images