An alternating current power generation loading test device and method

Abstract

The application discloses a kind of analog alternating current power generation loading test device and method, belong to engine test technical field, wherein device includes speed reducer assembly, support structure, screw member and elastic component, by with speed reducer assembly and adjusting assembly composition test device, can utilize the method of hydraulic loading power extraction equivalent alternating current power generation power extraction test, avoids high-power alternating current motor and engine adaptation and related problems of reformation, can consider the alternating current generator loading demand of multiple engines, wide application range, greatly save financial resources, also shorten the time of completing the test.

Description

Technical Field

[0001] This application belongs to the technical field of engine test, and particularly relates to a simulated AC power generation loading test device and method. Background Art

[0002] For an engine equipped with an AC generator accessory interface, there is a need for AC power generation loading during its AC power generation test, 60-hour or 150-hour endurance test, etc., to evaluate the engine's AC power generation loading ability.

[0003] Currently, the method to implement the engine AC power generation loading test is to perform power generation loading through an AC motor. This method requires an AC motor matching the engine and a loading cabinet system matching the test bench. However, an AC motor with a power generation power above 100 kVA often costs millions, and the price becomes higher as the power generation power increases. At the same time, if the loading cabinet system matching the test bench cannot meet the requirements of the AC motor's power generation power, it also needs to be modified, which also requires a significant amount of money. Moreover, AC motors matching some new engines have not been developed yet, and the progress is slow, but this engine urgently needs to verify its AC power generation loading function. Summary of the Invention

[0004] To solve the above problems, this application provides a simulated AC power generation loading test device and method to solve the technical problems raised in the background art.

[0005] A simulated AC power generation loading test device for the AC power generation test of an engine with an AC generator accessory interface, the test device includes: A reducer assembly, the input shaft of the reducer assembly is connected to the AC output end of the engine, and the output shaft of the reducer assembly is connected to the output shaft of the hydraulic motor; A support structure, including a support member and a frame member installed on the support member; A screw member, threadedly assembled on the frame member and extending in the vertical direction; An elastic member, extending in the vertical direction, one end of the elastic member is connected to the screw member, and the other end is connected to the reducer assembly.

[0006] Further, the support member includes a crossbeam portion extending in a first direction and a column portion supporting the crossbeam portion.

[0007] Further, the frame member is slidably installed on the crossbeam portion and extends in a second direction, and the first direction and the second direction are perpendicular to each other.

[0008] Further, the elastic member is a spring scale.

[0009] Furthermore, an over-torque protection device is provided between the AC output end of the engine and the input shaft of the reducer assembly.

[0010] Furthermore, the over-torque protection device is a double spline shaft.

[0011] Another aspect of this application discloses a simulated AC power generation loading test method, which is implemented based on the aforementioned test apparatus, and the test method includes: Determine the parameters of the reducer assembly, including the input speed and the output speed; Determine the target power output of the AC generator, as well as the overall efficiency and pressure difference of the hydraulic motor; The hydraulic motor flow rate and displacement are calculated based on the target power of AC power generation, the output speed of the reducer assembly, the total efficiency of the hydraulic motor, and the pressure difference, and then the hydraulic motor is selected. Connect the selected hydraulic motor, reducer assembly and elastic member, and make the center of mass of the reducer assembly and hydraulic motor as a whole lie on the axis of the elastic member. The tension of the elastic component is adjusted. After the tension of the elastic component is adjusted, the reducer assembly and the AC output terminal of the engine are connected and an AC power generation loading test is carried out.

[0012] Furthermore, the flow rate of the hydraulic motor Calculated based on the following formula:

[0013] In the formula, P is the target power generation. For pressure difference, For overall efficiency.

[0014] Furthermore, adjusting the tensile force of the elastic member includes: Position the reducer assembly at a set height, and control the rotation of the screw component to drive the end of the elastic component connected to the screw component to move vertically.

[0015] Furthermore, the test method also includes determining the hydraulic station parameters based on the reducer assembly and the selected hydraulic motor.

[0016] Compared with the prior art, this application has the following advantages: This application designs a test device consisting of a reducer assembly, a support structure, a screw component, and an elastic component. Through the transmission action of the reducer assembly, the engine torque load can be transmitted to the hydraulic motor, which then converts it into hydraulic energy. This allows for the equivalent AC generator load power extraction test using a hydraulic loading power extraction method. This avoids the problems related to the adaptation and modification of high-power AC motors and engines, and can accommodate the AC generator loading needs of various engines. It has a wide range of applications, greatly saves financial resources, and shortens the time required to complete the test.

[0017] Other features and advantages of this application will be set forth in the description which follows, and will be apparent in part from the description, or may be learned by practicing the application. The objectives and other advantages of this application may be realized and obtained by means of the structures pointed out in the description, claims and drawings. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A schematic diagram showing the connection between the reducer assembly and the hydraulic motor of this application is shown; Figure 2 A schematic diagram of the support structure of this application is shown; Figure 3 A schematic diagram of the overall experimental apparatus of this application is shown; Figure 4 A schematic diagram of the over-torsion protection device of this application is shown.

[0020] In the picture: 100. Reducer assembly; 101. Hydraulic motor; 200, Supporting component; 200a, Beam section; 200b, Column section; 201, Frame component; 202, Screw component; 203, Elastic component. Detailed Implementation

[0021] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0022] A simulated AC power generation loading test device (hereinafter referred to as the test device) is used for AC power generation testing of an engine with an AC generator accessory interface, i.e., the engine has an AC output terminal. In some embodiments, reference is made to... Figure 1 and Figure 3 The aforementioned test apparatus mainly consists of a reducer assembly 100 and an adjustment assembly. The input shaft of the reducer assembly 100 is connected to the AC output terminal of the engine, and the output shaft of the reducer assembly 100 is connected to the input terminal of the hydraulic motor 101. During the test, the AC output terminal (shaft) of the engine and the input shaft of the reducer assembly 100 are connected via internal and external splines, transmitting the engine torque load to the reducer assembly 100. After the reducer reduces the speed through its internal reduction gears, the torque load is transmitted to the hydraulic motor 101 via the connection between the output shaft of the reducer assembly 100 and the hydraulic motor 101. The hydraulic motor 101 ultimately converts this torque load into hydraulic energy to achieve… The conversion of engine mechanical energy and hydraulic motor 101 hydraulic energy, through an equivalent loading method of converting mechanical energy into hydraulic energy, eliminates the need to wait for the development of a matching AC generator. This allows for rapid verification of the engine's AC power generation loading function, significantly shortening the testing cycle. Furthermore, the reducer assembly 100 not only converts the high speed of the engine's AC output to the low speed required by the hydraulic motor 101, thus expanding the selection range of the hydraulic motor 101, reducing the procurement and customization costs of core components and improving compatibility with existing hydraulic stations, but also expands the installation space of the hydraulic motor 101, simplifying the installation operation, reducing assembly difficulty, and enhancing the compatibility with the test bench.

[0023] In some embodiments, refer to Figure 4 An over-torque protection device is configured between the AC output terminal of the aforementioned engine and the input shaft of the reducer assembly 100. When the torque exceeds the protection torque value for a certain period of time, the over-torque protection device is sheared to protect the engine and the reducer. In some examples, the over-torque protection device is a double spline shaft. By setting the over-torque protection device, the load transmission can be quickly cut off when the load fails, avoiding damage to the engine test piece and the loading device, significantly improving test safety, and reducing the test risk of high-value engines.

[0024] In some embodiments, refer to Figure 2 The aforementioned adjustment assembly includes a support structure, the main body of which is composed of a support member 200 and a frame member 201. The support member 200 generally forms a "gate"-shaped support. Specifically, the support member 200 has a beam portion 200a extending along a first direction and a column portion 200b supporting the beam portion 200a. The column portion 200b extends vertically, and correspondingly, the first direction is parallel to the horizontal direction. Continuing to refer to... Figure 2The aforementioned frame member 201 is mounted on the crossbeam portion 200a of the support member 200 and extends along a second direction, wherein the first and second directions are perpendicular. The frame member 201 is configured to move along the crossbeam portion 200a. In some examples, the support member is slidably mounted on the crossbeam portion 200a, i.e., the crossbeam is provided with a slide rail for the support member to slide on. In this case, the position of the frame member 201 on the crossbeam portion 200a can be adjusted by sliding the frame member 201. (Refer to...) Figure 3 The aforementioned adjustment assembly further includes an elastic member 203 and a screw member 202. The screw member 202 extends vertically and is threaded onto the frame member 201. When rotating, the screw member 202 can move linearly vertically. Correspondingly, the elastic member 203 also extends vertically, with one end connected to the reducer assembly 100. In some embodiments, one end of the elastic member 203 is connected to the reducer assembly 100 via a pull rod. Correspondingly, the other end of the elastic member 203 is connected to the screw member 202. When the position of the end of the elastic member 203 connected to the reducer assembly 100 is fixed, the end of the elastic member 203 connected to the screw member 202 can move linearly vertically with the rotation of the screw member 202, thereby realizing the linear movement of the elastic member 203. The adjustment of the tension amount allows for adjustment of the tension of the reducer assembly 100. Based on the setting of the adjustment component, the cantilever torque at the AC output end of the engine can be adjusted to balance part of the weight of the reducer assembly 100 and the hydraulic motor 101, thereby keeping the cantilever torque caused by the weight of the reducer assembly 100 and the hydraulic motor 101 within a set range. In some embodiments, the elastic member 203 is a spring scale, which allows for direct reading of the tension value after adjustment, i.e., obtaining the weight reduction. Based on the setting of the adjustment component, the cantilever torque can be compensated to meet the engine interface cantilever torque limit requirements and ensure engine operation stability. At the same time, by using an adjustable screw combined with a spring scale, the convenience of adjustment can be improved. During the adjustment process, the value can be directly read through the spring scale, thereby quickly completing the counterweight calibration and improving the efficiency of test preparation.

[0025] This application also discloses a simulated AC power generation loading test method, which is implemented based on the above-mentioned test device. Specifically, the test method includes: Determine the parameters of the reducer assembly 100, which include the input speed and the output speed; Determine the target power output of the AC power generation, as well as the overall efficiency and pressure difference of the hydraulic motor 101; Based on the target power of AC power generation, the output speed of reducer assembly 100, the total efficiency of hydraulic motor 101 and the pressure difference, the flow rate and displacement of hydraulic motor 101 are calculated, and hydraulic motor 101 is selected. Connect the selected hydraulic motor 101, reducer assembly 100 and elastic member 203, and make the center of mass of the reducer assembly 100 and hydraulic motor 101 as a whole lie on the axis of elastic member 203. The tension of the elastic member 203 is adjusted. After the tension of the elastic member 203 is adjusted, the reducer assembly 100 and the AC output terminal of the engine are connected and an AC power generation loading test is carried out.

[0026] The adjustment of the tension in the elastic member 203 includes: The reducer assembly 100 is positioned at a set height, and the screw component 202 is rotated to drive the end of the elastic component 203 connected to the screw component 202 to move vertically.

[0027] Specifically, in the test method, the target power output of the engine simulated AC power generation load test is P (unit: kW), that is, the target power output is P, and the rotational speed N1 (unit: r / min) of the engine's AC output terminal (shaft) is a known value, that is, the rotational speed of the input shaft of the reducer assembly 100 is a known value N1. The output rotational speed N2 of the reducer assembly 100 is a manually selected value, mainly considering that the cantilever torque caused by the installation space of the reducer assembly 100 on the engine and its own weight should be minimized and not exceed the allowable value of the engine's cantilever torque. After the input and output rotational speeds of the reducer assembly 100 are determined, the reduction ratio i (i.e., transmission ratio) of the reducer assembly 100 can be determined, and the reducer assembly 100 can be selected accordingly, that is: (1); Wherein, Z1 is the number of teeth on the input gear of the reducer assembly 100, and Z2 is the number of teeth on the output gear of the reducer assembly 100.

[0028] Furthermore, the flow rate calculation formula for hydraulic motor 101 is as follows (2): (2) In formula (2), The flow rate of hydraulic motor 101 is expressed in L / min. The displacement per revolution of hydraulic motor 101 is expressed in cm. 3 ; For volumetric efficiency.

[0029] Equation (2) is transformed to obtain equation (3): (3) In formula (3), N2 is the output speed of reducer assembly 100, that is, the input speed of hydraulic motor 101 (unit: r / min).

[0030] Meanwhile, the formula (4) for calculating the output torque of the hydraulic motor 101 is as follows: (4) In formula (4), T is the output torque of hydraulic motor 101, in N·m; For mechanical and hydraulic efficiency; Pressure differential, unit: bar, selected by the user.

[0031] The formula (5) for calculating the overall efficiency of hydraulic motor 101 is as follows: (5) In formula (5), For overall efficiency.

[0032] The power calculation formula for hydraulic motor 101 is as follows: (6) In formula (6), P is the target power of the generator (i.e., the power of the hydraulic motor 101), in kW.

[0033] From formulas (2) to (6): (7) In actual testing, it is necessary to pre-select the hydraulic motor 101. For a specific type of hydraulic motor 101, the volumetric efficiency is... Given that its overall efficiency range is a fixed value, in this application, the lowest value is selected for calculation. Therefore, according to formula (7), it can be seen that the overall efficiency... Given, pressure difference Given that the target power generation P is known, the flow rate of hydraulic motor 101 can be calculated. At the same time, volumetric efficiency Given that the rotational speed N2 is known, the displacement can be calculated according to formula (2), and the hydraulic motor 101 can be selected accordingly. Specifically, in the selection process of the hydraulic motor 101, in addition to considering the displacement, In addition to considering the rotational speed N2, we also need to consider minimizing its own size (considering installation space) and minimizing its weight (considering the cantilever torque on the engine caused by its weight).

[0034] In some embodiments, after the reducer assembly 100 and the hydraulic motor 101 are determined, the oil tank volume and control requirements of the hydraulic oil station are finally determined based on the input and output pressure, flow rate, heat dissipation and other requirements of the reducer assembly 100 and the hydraulic motor 101. That is, the hydraulic oil station parameters are determined based on the reducer assembly 100 and the selected hydraulic motor 101.

[0035] Based on the above method, hydraulic power extraction can be used to equivalently replace AC power generation loading, enabling engine power generation loading verification under conditions without a real generator. This fills a gap in related domestic testing technologies. Furthermore, by selecting the appropriate hydraulic motor model, it can be adapted to engines of various models, power levels, and interface types, offering high reusability and long service life. This significantly reduces equipment investment and modification costs for parallel development of multiple projects, meeting the testing needs of all scenarios, including short-term verification tests, long-term continuous testing, and variable operating condition assessments. This significantly improves engine development efficiency and test success rate. Simultaneously, this method provides a new technical route and engineering implementation scheme for subsequent AC power generation testing of new engines, possessing significant engineering application value and promotional significance for improving engine accessory system testing capabilities, shortening model development cycles, and reducing development costs.

[0036] In the description of this invention, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of the invention. In this invention, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. Moreover, those skilled in the art can combine different embodiments or examples and features of different embodiments or examples described in this invention without contradiction.

[0037] Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A simulated AC power generation loading test device, characterized in that, AC power generation test for an engine with an AC generator accessory interface, the test apparatus comprising: A speed reducer assembly (100) has its input shaft connected to the AC output of the engine and its output shaft connected to the output shaft of the hydraulic motor (101). The support structure includes a support member (200) and a frame member (201) mounted on the support member (200). The screw component (202) is threadedly assembled onto the frame component (201) and extends vertically. An elastic member (203) extends vertically, with one end of the elastic member (203) connected to the screw member (202) and the other end connected to the reducer assembly (100).

2. The simulated AC power generation loading test device according to claim 1, characterized in that, The support member (200) includes a beam portion (200a) extending along a first direction and a column portion (200b) supporting the beam portion (200a).

3. The simulated AC power generation loading test device according to claim 2, characterized in that, The frame component (201) is slidably mounted on the crossbeam (200a) and extends along the second direction, which is perpendicular to the first direction.

4. The simulated AC power generation loading test device according to claim 1, characterized in that, The elastic component (203) is a spring scale.

5. The simulated AC power generation loading test device according to claim 1, characterized in that, An over-torque protection device is provided between the AC output end of the engine and the input shaft of the reducer assembly (100).

6. The simulated AC power generation loading test device according to claim 5, characterized in that, The over-torque protection device is a double spline shaft.

7. A method for simulating AC power generation loading test, characterized in that, The test method is implemented based on the test apparatus according to any one of claims 1 to 6, and the test method includes: Determine the parameters of the reducer assembly (100), which include the input speed and the output speed; Determine the target power of AC power generation and the overall efficiency and pressure difference of the hydraulic motor (101); The flow rate and displacement of the hydraulic motor (101) are calculated based on the target power of AC power generation, the output speed of the reducer assembly (100), the total efficiency of the hydraulic motor (101) and the pressure difference, and the hydraulic motor (101) is selected. Connect the selected hydraulic motor (101), reducer assembly (100) and elastic member (203), and make the center of mass of the reducer assembly (100) and hydraulic motor (101) as a whole lie on the axis of elastic member (203); The tension of the elastic member (203) is adjusted. After the tension of the elastic member (203) is adjusted, the reducer assembly (100) and the AC output terminal of the engine are connected and an AC power generation loading test is carried out.

8. The simulated AC power generation loading test method according to claim 7, characterized in that, Flow rate of hydraulic motor (101) Calculated based on the following formula: In the formula, P is the target power generation; It is the pressure difference; For overall efficiency.

9. The simulated AC power generation loading test method according to claim 7, characterized in that, Adjusting the tension of the elastic member (203) includes: The reducer assembly (100) is positioned at a set height. By controlling the rotation of the screw component (202), the end of the elastic component (203) connected to the screw component (202) is moved vertically.

10. The simulated AC power generation loading test method according to claim 7, characterized in that, The test method also includes determining hydraulic station parameters based on the reducer assembly (100) and the selected hydraulic motor (101).

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