Throttling type hydraulic damping adjusting device

Abstract

The invention belongs to the technical field of aero-engines, and particularly relates to a throttling type hydraulic damping adjusting device which comprises an actuator cylinder test piece, a piston rod is connected with a load mechanism through a strain gauge connecting rod, the actuator cylinder test piece is controlled through a servo valve, and a displacement sensor for measuring the telescopic length of the piston rod is installed on the actuator cylinder test piece; the load device comprises a load cylinder, a load mechanism piston rod, a pressure gauge, a one-way valve and a flow valve (5); the load mechanism piston rod is connected with the strain gauge connecting rod; the load cylinder is fixed to the support. The piston rod divides the load cylinder into a P2 cavity and a P1 cavity. The cavity P2 is provided with a port B, the cavity P1 is provided with a port A, the port B and the port A are respectively connected with a pressure gauge, the port B and the port A are connected in parallel through a first branch and a second branch, two opposite one-way valves are connected in series on the first branch, two opposite one-way valves are connected in series on the second branch, and flow valves are connected between the one-way valves of the first branch and between the one-way valves of the second branch.

Description

Technical Field

[0001] This application belongs to the field of aero-engine technology, and specifically relates to a throttling hydraulic damping adjustment device. Background Technology

[0002] The durability test of aircraft engine actuator cylinders is conducted to analyze the reciprocating extension and retraction motion of the actuator cylinder piston rod throughout its entire stroke range. Under the condition of being subjected to the load of the adjustable mechanism, the wear between the various parts of the actuator cylinder and the sealing condition at the joint surfaces are assessed as the number of cycles increases. This provides test data for the long-term and stable operation of the actuator cylinder within the engine.

[0003] In existing technology, the actuator cylinder test piece is connected to a load spring via a strain gauge connecting rod. Feedback from a displacement sensor controls a servo valve to cause the piston rod to reciprocate within the cavity, thus achieving the actuator cylinder durability test. The spring simulates the load of the adjustable mechanism. However, due to load and displacement constraints, the performance and parameters of the spring are extremely demanding when using it to simulate the loading test of the adjustable mechanism. Standard springs available on the market may not meet the test requirements, and even if they are available, their lifespan is questionable, potentially requiring frequent replacements during the test. This necessitates redesigning and reprocessing the materials and specifications of the springs used, resulting in a long cycle and difficulty in controlling the test stages. Another important factor is that this method can only apply positive loads, not negative loads.

[0004] When the engine actuator cylinder reciprocates, it compresses the oil in the P1 chamber of the load mechanism to simulate the loading and unloading of the adjustable mechanism. This method is time-saving, labor-saving, low-cost, and highly efficient. However, to achieve the purpose of simulating the load of the adjustable mechanism by changing the pressure in the P1 chamber, the following requirements must be met:

[0005] The volume of the load mechanism cavity should be comparable to that of the actuating cylinder cavity of the test piece.

[0006] The friction between the piston and cylinder of the load mechanism should be as small as possible, and there should be no external or internal leakage.

[0007] The amount of oil in chamber P1 needs to be adjusted repeatedly. Since the oil compression is very small, filling the chamber completely or not filling it too little will not work, and the test results will be the same as loading with weights.

[0008] In theory, it is possible to apply a negative load, but debugging is very difficult.

[0009] Disadvantages of existing technology:

[0010] Using springs to simulate the load of adjustable mechanisms requires high performance and parameter specifications. Purchased products require comparison and analysis of spring materials, specifications, and performance. If designed in-house, the cycle is long and different models of springs need to be designed and manufactured for different loads.

[0011] Using drag-and-drop weights to simulate the load of an adjustable mechanism has significant drawbacks. It cannot meet the waveform requirements of the test, and the loading frequency cannot be increased, resulting in poor waveform tracking.

[0012] The load of the adjustable mechanism can be simulated by compressing the volume inside the cavity of the load mechanism, which can meet the test requirements. However, the amount of liquid and gas mixture inside the cavity needs to be repeatedly adjusted, which is difficult and time-consuming.

[0013] The common drawback of all three schemes is that the load cannot be applied at the zero point. Summary of the Invention

[0014] To address the aforementioned problems, this application provides a throttling hydraulic damping adjustment device, comprising:

[0015] The actuator cylinder test piece has a piston rod connected to the load mechanism via a strain gauge connecting rod. The actuator cylinder test piece is controlled by a servo valve and is equipped with a displacement sensor that measures the extension and retraction length of the piston rod.

[0016] The load device includes a load cylinder, a load mechanism piston rod, a pressure gauge, a check valve, and a flow valve (5).

[0017] The piston rod of the load mechanism is connected to the strain gauge connecting rod; the load cylinder is fixed on the bracket, and the piston rod divides the load cylinder into P2 cavity and P1 cavity; P2 cavity has port B, and P1 cavity has port A. Pressure gauges are connected to ports B and A respectively. Ports B and A are connected in parallel through the first branch and the second branch. Two opposing check valves are connected in series on the first branch, and two opposing check valves are connected in series on the second branch. Flow valves (5) are connected between the check valves of the first branch and between the check valves of the second branch.

[0018] Preferably, by adjusting the opening of the throttle valve (5), the flow rate of liquid from cavity P2 to cavity P1 and the flow rate of liquid from cavity P1 to cavity P2 are adjusted to achieve positive or negative loading on the actuator cylinder test piece.

[0019] Preferably, the throttle valve (5) is a manually adjustable valve, and the opening degree of the valve port is changed by rotating its handle.

[0020] Preferably, in the initial state, the opening of the throttle valve (5) is adjusted to the maximum;

[0021] The driven actuator test piece runs according to the preset waveform;

[0022] Slowly adjust the throttle valve (5) to reduce its opening, increase the hydraulic oil flow resistance, and observe the readings of the first pressure gauge (6) and / or the second pressure gauge (7);

[0023] When the pressure reading reaches the load value required for the test, stop adjusting the throttle valve (5).

[0024] Preferably, when adjusting the throttle valve (5), the change in its opening degree is matched with the loading frequency of the actuator test piece to achieve precise control of the load.

[0025] Preferably, when the test loading frequency changes, the opening of the throttle valve (5) needs to be readjusted accordingly to maintain load stability.

[0026] This application designs a device between the two chambers (P1, P2) of the load mechanism that allows for unidirectional flow and adjustable flow rate. By changing the oil flow rate between chambers P1 to P2 or P2 to P1 and matching it with the frequency of the loaded test specimen, the durability test of the actuator cylinder is completed. This scheme solves the problem of zero-crossing load and can apply loads in both forward and reverse directions. Attached Figure Description

[0027] Figure 1 It is a throttling hydraulic damping adjustment device;

[0028] Figure 2 This is a schematic diagram of the application of a throttling hydraulic damping device. Detailed Implementation

[0029] To make the objectives, technical solutions, and advantages of this application clearer, the technical solutions in the embodiments of this application will be described in more detail below with reference to the accompanying drawings. In the drawings, the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The described embodiments are only some, not all, of the embodiments of this application. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this application, and should not be construed as limiting this application. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the scope of protection of this application. The embodiments of this application will be described in detail below with reference to the accompanying drawings. Figures 1-2 As shown, the actuator cylinder test piece has a piston rod connected to the load mechanism via a strain gauge connecting rod. The actuator cylinder test piece is controlled by a servo valve and is equipped with a displacement sensor that measures the extension and retraction length of the piston rod.

[0030] The load device includes a load cylinder, a load mechanism piston rod, and a damping adjustment device; the load mechanism piston rod is connected to the strain gauge connecting rod; the load cylinder is fixed on the bracket, and the piston rod divides the load cylinder into a P2 cavity and a P1 cavity; the P2 cavity has a B port, and the P1 cavity has an A port. Pressure gauges are connected to the B port and the A port respectively. The B port and the A port are connected in parallel through a first branch and a second branch. Two opposing check valves are connected in series on the first branch, and two opposing check valves are connected in series on the second branch. Flow valves 5 are connected between the check valves of the first branch and between the check valves of the second branch.

[0031] Connect ports A and B to chambers P1 and P2 of the load mechanism. When the piston rod of the load mechanism exits the cylinder (moves to the left), the oil flows out through port A (in the direction indicated by the black arrow) to check valve 1, flow valve 5, and check valve 4, then flows into chamber P2 through port B. Observe pressure gauge 6 and adjust the flow valve 5 to control the oil flow rate, so that back pressure is generated in chamber P1, achieving the purpose of simulating the loading of the adjustable mechanism and completing the positive loading.

[0032] When the piston rod of the load mechanism retracts (moves to the right), the oil flows out through port B (in the direction indicated by the white arrow) to check valve 2, flow valve 5, and check valve 3, flowing into chamber P1 through port A. Observe pressure gauge 7, and control the oil outflow by adjusting flow valve 5 to generate back pressure in chamber P2, thereby simulating the loading of the adjustable mechanism and completing the negative loading.

[0033] This design is simple, easy to use, small in size, and easy to install. However, the dimensional tolerances between the mounting holes and components are small, and the surface roughness requirements for the sealing surfaces are high. Sharp edges must be smoothly transitioned. When processing smaller-sized components, the mounting hole diameter is small, and there are many transition points on the inner cylindrical surface. If the sharp edges are not treated, they are very easy to cut off, affecting the damping effect and sealing performance. When using this solution, it is best to select a load actuator with a volume comparable to the test specimen cavity, low friction, and minimal internal leakage.

[0034] Fully open the handle of flow valve 5 in the flow damping device. Connect port A to chamber P1 of the load mechanism and port B to chamber P2. Send a command signal to the servo valve via the servo controller to make the actuator cylinder test piece run according to the loading waveform (very small load). Slowly rotate the handle of flow valve 5 (closed direction) and observe the pressure gauge 6 or 7 to obtain the pressure in chamber P1 or P2 until the test load is reached. This method controls the flow velocity in the two chambers by changing the opening size of the flow valve, and it must match the loading frequency of the test piece. This allows for precise application of the test load to the actuator cylinder. If the test loading frequency is changed, the valve opening must also be adjusted accordingly.

[0035] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A throttling hydraulic damping adjustment device, characterized in that, include: The actuator cylinder test piece has a piston rod connected to the load mechanism via a strain gauge connecting rod. The actuator cylinder test piece is controlled by a servo valve and is equipped with a displacement sensor that measures the extension and retraction length of the piston rod. The load device includes a load cylinder, a load mechanism piston rod, a pressure gauge, a check valve, and a flow valve (5). The piston rod of the load mechanism is connected to the strain gauge connecting rod; the load cylinder is fixed on the bracket, and the piston rod divides the load cylinder into P2 cavity and P1 cavity; P2 cavity has port B, and P1 cavity has port A. Pressure gauges are connected to ports B and A respectively. Ports B and A are connected in parallel through the first branch and the second branch. Two opposing check valves are connected in series on the first branch, and two opposing check valves are connected in series on the second branch. Flow valves (5) are connected between the check valves of the first branch and between the check valves of the second branch.

2. The throttling hydraulic damping adjustment device as described in claim 1, characterized in that, By adjusting the opening of the throttle valve (5), the flow rate of liquid from cavity P2 to cavity P1 and the flow rate of liquid from cavity P1 to cavity P2 can be adjusted to achieve positive or negative loading on the actuator cylinder test piece.

3. The throttling hydraulic damping adjustment device as described in claim 1, characterized in that, The throttle valve (5) is a manually adjustable valve, and the opening degree of the valve port is changed by rotating its handle.

4. The throttling hydraulic damping adjustment device as described in claim 1, characterized in that, In the initial state, the opening of the throttle valve (5) is adjusted to the maximum; The driven actuator test piece runs according to the preset waveform; Slowly adjust the throttle valve (5) to reduce its opening, increase the hydraulic oil flow resistance, and observe the readings of the first pressure gauge (6) and / or the second pressure gauge (7); When the pressure reading reaches the load value required for the test, stop adjusting the throttle valve (5).

5. The throttling hydraulic damping adjustment device as described in claim 1, characterized in that, When adjusting the throttle valve (5), the change in its opening degree is matched with the loading frequency of the actuator test piece to achieve precise control of the load.

6. The throttling hydraulic damping adjustment device as described in claim 1, characterized in that, When the test loading frequency changes, the opening of the throttle valve (5) needs to be readjusted accordingly to maintain load stability.

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