A comprehensive test bench device for performance of a rotary engine

Abstract

This invention discloses a comprehensive performance testing bench for rotary engines, relating to the field of engine testing technology. It includes a support frame with a slide rail fixed to it. A fastenable connecting frame is mounted on the slide rail. First support plates are positioned above and below the connecting frame, and second support plates are positioned on both sides of the connecting frame. Pressure sensors are disposed in the first and second support plates. An eddy current brake is also fixed to the support frame, and a torque-speed sensor is positioned between the connecting frame and the eddy current brake. This invention can comprehensively, accurately, and safely test the performance parameters and dynamic stress characteristics of rotary engines under multiple operating conditions.

Description

Technical Field

[0001] This invention relates to the field of engine testing technology, specifically a comprehensive performance testing bench for rotary engines. Background Technology

[0002] During operation, the rotary engine exhibits significant differences from traditional reciprocating engines in terms of the seal between the rotor and cylinder, the radial force on the main shaft, and the overall vibration characteristics. Accurate performance testing is crucial for optimizing design and improving reliability. Therefore, developing a comprehensive performance testing bench capable of realistically simulating the actual installation boundaries and operating conditions of a rotary engine is of significant engineering importance.

[0003] Currently, existing rotary engine performance test benches mainly adopt the following implementation method: the engine is fixed on the base frame with rigid clamps, an eddy current dynamometer or an electric dynamometer is used as the load, and a torque and speed sensor is installed between the engine output shaft and the dynamometer to measure the engine torque and speed, thereby obtaining macroscopic performance parameters such as power and fuel consumption rate.

[0004] Existing test benches primarily use rigid clamping or simple rubber pads for engine fixation, which cannot accurately simulate the boundary constraints of a rotary engine in a real-world installation environment. In actual installation, the engine casing is subjected to multi-directional, pre-tightened elastic constraints, while rigid clamping alters the stress distribution and vibration modes of the casing, causing the measured force and vibration data to deviate from reality and affecting the accuracy of subsequent structural optimization and fault diagnosis.

[0005] Existing test benches typically rigidly connect the engine output shaft directly to the torque and speed sensor via a coupling, ignoring radial vibration, misalignment, or bending deformation that may occur in the spindle during actual operation. This rigid connection forces alignment, masking the true motion state of the spindle, resulting in the measured torque and speed not fully reflecting the actual output characteristics of the spindle under floating conditions.

[0006] Therefore, it is necessary to provide a comprehensive test bench for rotary engine performance to solve the problems mentioned in the background art. Summary of the Invention

[0007] To achieve the above objectives, the present invention provides the following technical solution: a comprehensive test bench device for rotor engine performance, comprising a support, a slide rail fixed on the support, a fastenable connecting frame provided on the slide rail, a first support plate provided above and below the connecting frame, a second support plate provided on each side of the connecting frame, and a pressure sensor provided in the first and second support plates; an eddy current brake is also fixed on the support, and a torque-speed sensor is provided between the connecting frame and the eddy current brake.

[0008] Furthermore, a coupling is provided between the torque and speed sensor, the eddy current brake, and the engine main shaft.

[0009] Furthermore, the slide rail is provided with a fastenable slide plate, the slide plate is provided with a third support plate, and the third support plate is provided with a pressure sensor.

[0010] Furthermore, a first lead screw penetrating the connecting frame is rotatably provided on the back of the first support plate, and a spring is provided between the first support plate and the first lead screw; a second lead screw penetrating the connecting frame is rotatably provided on the back of the second support plate, and a spring is provided between the second support plate and the second lead screw.

[0011] Furthermore, a third lead screw that passes through the slide plate is rotatably provided on the back of the third support plate, and a spring is provided between the third support plate and the third lead screw.

[0012] Furthermore, the connecting frame has a through hole on its front side, a sleeve is installed inside the through hole, a connecting plate is fixed around the sleeve, and multiple support springs are distributed circumferentially between the connecting plate and the connecting frame.

[0013] Furthermore, each of the support springs has a slider fixed at the end away from the connecting disc, and the slider is radially slidably connected to the connecting frame.

[0014] Furthermore, a concentric rotating ring is rotatably arranged around the through hole of the connecting frame, and each slider is hinged to the slider via a connecting rod.

[0015] Furthermore, a pressure sensor is installed between each slider and the support spring.

[0016] Furthermore, the outer wall of the rotating ring is threaded, and a screw that meshes with it is rotatably disposed inside the connecting frame.

[0017] Compared with the prior art, the advantages of this invention are as follows: the engine is clamped and fixed in the connecting frame by the first support plates on the upper and lower sides and the second support plates on the left and right sides, and each support plate is equipped with a spring-loaded lead screw on the back, which can precisely adjust the clamping force and use the spring to provide preload, avoiding damage to the engine housing caused by rigid clamping. The pressure sensor embedded in the support plate can monitor the clamping force and the force changes during engine operation in real time, ensuring that the test boundary conditions are highly consistent with the actual installation state.

[0018] By setting a movable slide plate and a third support plate on the slide rail, dynamic forces and vibrations of the engine along the output shaft direction are specifically collected, completing the measurement of the axial dimension. At the same time, multiple support springs and corresponding pressure sensors distributed circumferentially around the sleeve can accurately measure the magnitude and change of the radial force exerted by the main shaft on the sleeve in the 360° direction. This is used to analyze the centrifugal force, gyroscopic effect, imbalance, and radial impact of cylinder pressure fluctuations on the main shaft during high-speed rotor rotation. The multi-dimensional sensing layout makes the force analysis more complete and in-depth.

[0019] The engine main shaft is rotated and fitted inside a sleeve. The sleeve is connected to the connecting plate and connecting frame via circumferentially distributed support springs, forming a floating support structure. This structure can realistically simulate the radial vibration, misalignment, or bending deformation that the main shaft may experience during actual operation. By measuring the force changes of each support spring, the radial force exerted by the main shaft on the sleeve can be deduced, providing crucial data for rotor dynamic balance assessment, bearing condition diagnosis, and eccentric motion analysis.

[0020] By rotating the swivel, the connecting rod synchronously pushes each slider to slide the same distance radially, which can change the initial compression of all support springs. This allows for rapid and uniform adjustment of the overall radial support stiffness or simulation of bearing preload changes, ensuring that the spring preload around the sleeve is always symmetrical, avoiding off-center loading, and improving the repeatability and reliability of the test. Attached Figure Description

[0021] Figure 1 A schematic diagram of a comprehensive performance testing bench for a rotary engine;

[0022] Figure 2 This is a schematic diagram of the internal structure of the connecting frame in this invention;

[0023] Figure 3 This is a cross-sectional structural diagram of the present invention;

[0024] Figure 4 This is a schematic cross-sectional view of the sleeve portion of the connecting frame in this invention.

[0025] Figure 5 This is a schematic cross-sectional view of the first and second support plates of the connecting frame in this invention.

[0026] In the diagram: 1. Bracket; 2. Slide rail; 3. Connecting frame; 4. First support plate; 41. First lead screw; 5. Second support plate; 51. Second lead screw; 6. Sleeve; 61. Connecting disc; 62. Support spring; 63. Slider; 64. Rotary ring; 65. Connecting rod; 66. Screw; 7. Slide plate; 71. Third support plate; 72. Third lead screw; 8. Eddy current brake; 9. Torque-speed sensor. Detailed Implementation

[0027] Please see Figures 1-5 In this embodiment of the invention, a comprehensive performance test bench for a rotary engine includes a support 1, a slide rail 2 fixed on the support 1, a fastenable connecting frame 3 on the slide rail 2, a first support plate 4 at the top and bottom of the connecting frame 3, and a second support plate 5 on each side of the connecting frame 3. Pressure sensors are installed in the first support plate 4 and the second support plate 5. An eddy current brake 8 is also fixed on the support 1, and a torque-speed sensor 9 is installed between the connecting frame 3 and the eddy current brake 8.

[0028] The engine is clamped and fixed in the connecting frame 3 by the first support plates 4 on the upper and lower sides and the second support plates 5 on the left and right sides, simulating the actual installation boundary; the internal pressure sensor monitors the force and vibration of the engine in real time during operation; different loads are applied by controlling the eddy current brake 8 to simulate the actual working conditions; the torque and speed sensor 9 measures the torque and speed of the output shaft, thereby obtaining the performance parameters of the engine under different working conditions.

[0029] In this embodiment, a coupling is provided between the torque and speed sensor 9, the eddy current brake 8, and the engine main shaft.

[0030] In this embodiment, a fastenable slide plate 7 is provided on the slide rail 2, a third support plate 71 is provided on the slide plate 7, and a pressure sensor is provided in the third support plate 71.

[0031] The slide plate 7 can move and be secured on the slide rail 2. The third support plate 71 is located on the back of the engine. The pressure sensor inside it is specifically designed to collect the dynamic force and vibration of the engine along the output shaft direction, supplementing the axial dimension measurement and making the force analysis more complete.

[0032] In this embodiment, a first lead screw 41 is rotatably provided on the back of the first support plate 4, penetrating the connecting frame 3, and a spring is provided between the first support plate 4 and the first lead screw 41.

[0033] The second support plate 5 is rotatably provided with a second lead screw 51 that passes through the connecting frame 3, and a spring is provided between the second support plate 5 and the second lead screw 51.

[0034] Rotating the first lead screw 41 and the second lead screw 51 can change the position of the corresponding first support plate 4 and the second support plate 5, thereby adapting to engines of different widths / heights; the spring provides preload force, so that the engine is clamped by pressure, while ensuring that the pressure sensor measures the actual change in contact force.

[0035] In this embodiment, a third lead screw 72 that passes through the slide plate 7 is rotatably provided on the back of the third support plate 71, and a spring is provided between the third support plate 71 and the third lead screw 72.

[0036] The position of the third support plate 71 can be adjusted by the third lead screw 72 to hold the back of the engine in place. This can eliminate axial clearance, simulate the axial constraint during actual installation, avoid rigid jamming that could cause housing deformation or measurement distortion, and buffer axial impact to protect the sensor.

[0037] In this embodiment, the front of the connecting frame 3 has a through hole, a sleeve 6 is provided in the through hole, a connecting plate 61 is fixed around the sleeve 6, and a plurality of support springs 62 are distributed circumferentially between the connecting plate 61 and the connecting frame 3.

[0038] The engine main shaft is rotated and fitted inside the sleeve 6. The sleeve 6 is connected to the connecting plate 61 and the connecting frame 3 by multiple circumferentially distributed support springs 62, forming a floating support. This can simulate the radial vibration, misalignment, or bending deformation that the main shaft may experience during actual operation. By measuring the force changes of the support springs 62, the radial force exerted by the main shaft on the sleeve 6 can be deduced, which can be used to analyze rotor dynamic balance, bearing condition, or eccentric motion.

[0039] In this embodiment, each of the support springs 62 has a slider 63 fixed at the end away from the connecting plate 61, and the slider 63 is radially slidably connected to the connecting frame 3.

[0040] In this embodiment, a concentric rotating ring 64 is rotatably arranged around the through hole of the connecting frame 3, and each slider 63 is hinged to the slider 63 by a connecting rod 65.

[0041] In other words, by rotating the swivel 64, each connecting rod 65 can synchronously push each slider 63 to slide radially, which can change the initial compression of the spring at that point; when rotating the swivel 64, all connecting rods 65 synchronously push each slider 63 to slide radially by the same distance, ensuring that the spring preload around the sleeve 6 is always symmetrical, avoiding uneven load, and quickly changing the overall radial support stiffness or simulating a uniform change in bearing preload.

[0042] In this embodiment, a pressure sensor is provided between each slider 63 and the support spring 62.

[0043] By using multiple pressure sensors distributed circumferentially, the magnitude and variation of the radial force exerted by the engine spindle on the sleeve 6 in the 360° direction can be accurately measured. This is used to analyze the radial impact of centrifugal force, gyroscopic effect, imbalance, and cylinder pressure fluctuations on the spindle during high-speed rotor rotation.

[0044] In this embodiment, the outer wall of the rotating ring 64 is threaded, and a screw 66 that meshes with it is rotatably disposed inside the connecting frame 3.

[0045] The screw 66 drive has a self-locking characteristic, and its position will not change due to vibration after adjustment. It can achieve fine adjustment of small angles, thereby precisely setting the preload of all support springs 62.

[0046] In practice, the rotor engine to be tested is placed in the connecting frame 3, with the main shaft roughly aligned with the center of the sleeve 6. Then, the first lead screws 41 on both the upper and lower sides are rotated to push the first support plate 4 closer to the engine. The spring between the first support plate 4 and the first lead screw 41 provides preload force, clamping the engine from the top and bottom. Similarly, the second lead screws 51 on both the left and right sides are rotated to push the second support plate 5 closer to the engine. The spring between the second support plate 5 and the second lead screw 51 provides preload force, clamping the engine from the left and right. During the clamping process, the readings of the pressure sensors installed inside the first support plate 4 and the second support plate 5 are continuously observed to ensure that the clamping force in all four directions is uniform and meets the requirements of simulating the actual installation boundary. The engine main shaft is then... The main shaft is rotated through the through hole on the front of the connecting frame 3 and fitted into the sleeve 6 inside the through hole. The coupling between the engine main shaft and the torque and speed sensor 9, and the coupling between the torque and speed sensor 9 and the eddy current brake 8 are installed in sequence. The slide plate 7 is moved to a suitable position on the back of the engine along the slide rail 2 on the bracket 1 and the slide plate 7 is tightened. The third lead screw 72 set on the slide plate 7 is rotated to push the third support plate 71 against the back of the engine. The spring between the third support plate 71 and the third lead screw 72 provides preload force to eliminate axial clearance and simulate axial constraint during actual installation. At the same time, it avoids rigid jamming that could cause housing deformation or measurement distortion. The third lead screw 72 is adjusted to make the preload force moderate to buffer axial impact and protect the sensor.

[0047] When it is necessary to change the radial support stiffness of the main shaft or simulate the change in bearing preload, the rotating screw 66 drives the rotating ring 64 to rotate. The rotating ring 64 is hinged to each slider 63 through the connecting rod 65, and simultaneously pushes all sliders 63 to slide radially. Each slider 63 is equipped with a pressure sensor between itself and the support spring 62. During the adjustment process, the readings of multiple pressure sensors in the circumferential direction are read to make the spring preload uniform and symmetrical in the 360° direction. This can quickly change the overall radial support stiffness and simulate uniform changes in bearing preload. Moreover, the screw 66 drive has a self-locking characteristic, and the position is stable after adjustment.

[0048] The rotor engine is started, and testing begins after it warms up and stabilizes. Different loads are applied by controlling the eddy current brake 8 to simulate actual working conditions, while the torque and speed sensor 9 measures the torque and speed of the output shaft in real time. During the test, all pressure sensors work continuously. The pressure sensors in the first support plate 4 and the second support plate 5 monitor the forces and vibrations of the engine during operation. The pressure sensor in the third support plate 71 specifically collects the dynamic forces and vibrations of the engine along the output shaft direction. The pressure sensors between each slider 63 around the sleeve 6 and the support spring 62 accurately measure the magnitude and changes of the radial force of the main shaft in the 360° direction, which are used to analyze the centrifugal force, gyroscopic effect, imbalance, and radial impact of cylinder pressure fluctuations on the main shaft when the rotor rotates at high speed.

[0049] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A rotor engine performance comprehensive test bench device comprising a support (1), characterized in that, The bracket (1) is fixed with a slide rail (2), and the slide rail (2) is provided with a fastening connecting frame (3). The connecting frame (3) is provided with a first support plate (4) at the top and bottom, and a second support plate (5) is provided on each side of the connecting frame (3). Pressure sensors are provided in the first support plate (4) and the second support plate (5). An eddy current brake (8) is also fixed on the bracket (1), and a torque speed sensor (9) is provided between the connecting frame (3) and the eddy current brake (8).

2. A performance comprehensive test bench device for a rotary engine according to claim 1, characterized in that, A coupling is provided between the torque and speed sensor (9), the eddy current brake (8), and the engine main shaft.

3. The performance comprehensive test bench device of a rotary engine according to claim 1, characterized in that, The slide rail (2) is provided with a fastenable slide plate (7), the slide plate (7) is provided with a third support plate (71), and the third support plate (71) is provided with a pressure sensor.

4. The performance comprehensive test bench device of a rotary engine according to claim 1, characterized in that, The first support plate (4) is rotatably provided with a first lead screw (41) that passes through the connecting frame (3) on its back side, and a spring is provided between the first support plate (4) and the first lead screw (41); The second support plate (5) is rotatably provided with a second lead screw (51) that passes through the connecting frame (3) on its back side, and a spring is provided between the second support plate (5) and the second lead screw (51).

5. The rotary engine performance comprehensive test bench device according to claim 3, characterized in that, The third support plate (71) is rotatably provided with a third lead screw (72) that passes through the slide plate (7) on its back side, and a spring is provided between the third support plate (71) and the third lead screw (72).

6. The rotary engine performance comprehensive test bench device according to claim 1, characterized in that, The connecting frame (3) has a through hole on its front side, and a sleeve (6) is provided in the through hole. A connecting plate (61) is fixed around the sleeve (6). Multiple support springs (62) are distributed circumferentially between the connecting plate (61) and the connecting frame (3).

7. The rotary engine performance comprehensive test bench device according to claim 6, characterized in that, Each of the support springs (62) has a slider (63) fixed at one end away from the connecting plate (61), and the slider (63) is radially slidably connected to the connecting frame (3).

8. The rotary engine performance comprehensive test bench device according to claim 7, characterized in that, The connecting frame (3) is rotatably provided with a concentric rotating ring (64) around the through hole, and each slider (63) is hinged to the slider (63) by a connecting rod (65).

9. The rotary engine performance comprehensive test bench device according to claim 7, characterized in that, A pressure sensor is provided between each slider (63) and the support spring (62).

10. The rotary engine performance comprehensive test bench device according to claim 8, characterized in that, The outer wall of the swivel ring (64) is threaded, and a screw (66) that meshes with it is rotatably provided inside the connecting frame (3).

Images