A hydraulically driven valve-seat wear test device and method

Abstract

The present invention relates to a hydraulically driven valve-seat wear test device and method, the test device includes a frame, a loading device and a control device; the frame is provided with a simulated combustion chamber, and the simulated combustion chamber is provided with a matching valve and seat ring; a hydraulic driving device is provided on one side of the simulated combustion chamber, and the hydraulic driving device is connected to the valve through the loading device; the loading device is arranged corresponding to the valve, and is used to drive the valve to slide and impact the seat ring; a reset device is provided on the other side of the simulated combustion chamber, and is used to reset the valve; the control device is connected to the hydraulic driving device, and is used to control the hydraulic driving device to output various types of displacement curves. This test device can not only carry out experiments in various loading forms, but also provide a large loading force, which creates conditions for testing valve-seat rings under large explosion pressure, expands the test range, and completes the evaluation of valve-seat ring wear performance in a relatively short time.

Description

Technical Field

[0001] The invention relates to the technical field of valve-seat wear testing, and in particular to a hydraulically driven valve-seat wear testing device and method. Background Art

[0002] The valve-seat ring is a key friction pair in the engine valve train. The opening and closing of the valve-seat ring controls the entry of the fuel mixture and the discharge of the exhaust gas. The valve-seat ring not only has to withstand the scouring and corrosion of high-temperature combustion gas, but also the impact of explosion pressure. It is very easy to wear and fail, resulting in problems such as air leakage, low cylinder pressure, and insufficient engine power, affecting the output power and service life of the engine. With the continuous optimization of engine structure and the continuous improvement of performance indicators, the engine speed, the explosion pressure of the combustion chamber and the operating temperature of the valve are getting higher and higher, which makes the failure of the engine's valve-seat ring, especially the exhaust valve-seat ring, an increasingly serious problem.

[0003] At present, there are two main directions for the research on the wear performance of the engine valve-seat ring. The first is to test the material properties of the engine valve-seat ring contact pair. However, the material performance test only targets the characteristics of the material itself and cannot fully simulate the actual working conditions of the valve-seat ring; the second is to conduct direct wear tests on the valve-seat ring contact pair. The direct wear test of the contact pair can be divided into whole machine test and wear test bench test. The whole machine test cycle of the engine is long, the cost is high, and it is difficult to collect data. The test bench experiment requires equipment that can provide high temperature and large explosion pressure to simulate the real cylinder environment.

[0004] The prior art discloses a wear test bench driven by a cam, but the burst pressure that the cam can provide is very limited, and a large burst pressure and long-term experiments may cause wear and deformation of the cam. In addition, the operation of applying the burst pressure on the cam-driven test machine is relatively complicated and difficult to control. At the same time, the cam profile determines the lift mode of the valve, which is relatively fixed and single, and the range that can be tested is small. Summary of the invention

[0005] In view of the technical problems existing in the prior art, one of the purposes of the present invention is to provide a hydraulically driven valve-seat wear testing device, which can not only output various types of displacement curves for conducting experiments with various loading forms, but also provide a large loading force, thereby creating conditions for testing valve-seat rings that withstand large explosion pressures, expanding the testing range of existing testing machines, and providing a reliable basis for actual production.

[0006] In view of the technical problems existing in the prior art, the second purpose of the present invention is to provide a hydraulically driven valve-seat wear test method.

[0007] In order to achieve the above purpose, the design idea of ​​the present invention is to fix the seat ring and allow the valve to continuously contact and squeeze the seat ring under the action of the loading device and the reset device, so as to simulate the impact wear of the valve-seat ring under the explosion pressure in actual working conditions. The present invention adopts the following technical solutions:

[0008] A hydraulically driven valve-seat wear test device comprises a frame, a loading device and a control device;

[0009] The frame is provided with a simulated combustion chamber, and the simulated combustion chamber is provided with matching valves and seat rings;

[0010] A hydraulic drive device is provided on one side of the simulated combustion chamber, and the hydraulic drive device is connected to the valve through a loading device;

[0011] The loading device is arranged corresponding to the valve and is used to drive the valve to slide and impact toward the seat ring;

[0012] A reset device is provided on the other side of the simulated combustion chamber for resetting the valve;

[0013] The control device is connected to the hydraulic drive device and is used to control the hydraulic drive device to output various types of displacement curves.

[0014] Furthermore, the loading device includes an upper impact shaft, an impact reinforcement unit and a lower impact shaft. The two ends of the impact reinforcement unit are respectively abutted against the upper impact shaft and the lower impact shaft. The lower impact shaft is connected to the hydraulic drive device and is arranged corresponding to the valve.

[0015] Furthermore, the upper impact shaft and the lower impact shaft are coaxially arranged, and the impact reinforcement unit is provided with a guide device, and the guide device is parallel to the upper impact shaft and the lower impact shaft.

[0016] Furthermore, the lower impact shaft is provided with a pressure sensor, and the hydraulic drive device includes a hydraulic actuator, and the hydraulic actuator is connected to the pressure sensor and the control device respectively.

[0017] Furthermore, a push rod and a push disc are provided between the upper impact shaft and the valve. The push rod is connected to the upper impact shaft, and the push disc is interference fit with the push rod, and the other side is connected with the valve.

[0018] Furthermore, a detachable auxiliary positioning piece and a distance measuring device are provided between the push disc and the valve. The auxiliary positioning piece is wider than the valve face end of the valve, the auxiliary positioning piece abuts against the push disc, and the distance measuring device is used to measure the distance between the auxiliary positioning piece and the combustion chamber wall.

[0019] Furthermore, the auxiliary positioning member is provided with a positioning hole, and the positioning hole is located on one side of the valve.

[0020] Furthermore, the seat ring is located inside the simulated combustion chamber and is embedded in a seat ring fixture. The seat ring fixture is fixedly connected to the combustion chamber wall. A valve guide sleeve is fixed inside the combustion chamber wall, and the valve stem reciprocates up and down in the valve guide sleeve.

[0021] Furthermore, a cylinder gland is provided between the valve and the reset device, and the valve stem is passed through the cylinder gland, and the valve stem contacts and separates with the reset device through the cylinder gland in a cycle.

[0022] Furthermore, the reset device comprises a reset spring, one end of which is arranged corresponding to the gas cylinder gland, and the other end of which is fixedly connected to the frame.

[0023] A hydraulically driven valve-seat wear test method comprises the following steps:

[0024] S1, the control device controls the hydraulic driving device to output hydraulic forces with various types of displacement curves to the loading device;

[0025] S2, the loading device drives the valve to slide and impact toward the seat ring;

[0026] S3, after the valve completes sliding impact in the seat ring, the reset device resets the valve;

[0027] S4, repeat steps S1-S3.

[0028] Furthermore, the method includes the following steps: placing the auxiliary positioning member between the push disc and the valve, and using a distance measuring device to measure the distance between the auxiliary positioning member and the combustion chamber wall before and after a certain period of wear, and the difference is the circumferential cumulative wear and sinking of the valve-seat ring during this period. By measuring the entire experimental process of the valve-seat ring, a quantitative analysis of the entire wear process of the valve-seat ring can be made. Since the width of the auxiliary positioning member is greater than the valve face end of the valve, the auxiliary positioning member extends the horizontal plane of the valve, making it more convenient to measure the distance between the valve-seat ring. Preferably, the auxiliary positioning member can be a stainless steel plate with a parallelism of 0.01 mm, and the distance measuring device can be a depth gauge.

[0029] Furthermore, during the distance measurement process of the wear experiment, the auxiliary positioning member is positioned using the positioning hole of the auxiliary positioning member, ensuring that each experimental measurement is at the same position, thereby reducing measurement errors.

[0030] Furthermore, the circumferential cumulative sinking of the valve-seat ring before and after the experiment is the sum of the circumferential cumulative sinking measured at regular intervals, which is also the difference between the distance measurement results before and after the experiment. The circumferential cumulative sinking of the valve-seat ring is the cosine value of the circumferential cumulative sinking divided by the valve cone angle α.

[0031] Furthermore, the valve and seat ring are removed, and the valve or seat ring before and after the experiment is placed in a 3D profilometer, and the sealing contact surface is placed horizontally. The appropriate parameters are adjusted so that the 3D profilometer starts from 2mm in front of the sealing surface, and the entire sealing surface cone of the valve or seat ring is scanned to obtain the contour curves before and after the experiment. Multiple positions before and after the experiment are selected to obtain multiple contour curves. In the drawing software, the first 2mm of the contour curves before and after the experiment are moved to overlap. The difference between the two curves on the sealing surface is the sinking amount of the valve or seat ring respectively, and the sum of the sinking amount of the valve and the seat ring is the cumulative sinking amount of the valve-seat ring.

[0032] Furthermore, the data obtained by comparing the two schemes do not differ by more than 15%, which proves the accuracy of the data measured by the distance measuring device. Therefore, the present invention can not only measure the cumulative sinking amount of the valve-seat ring before and after the experiment, but also perform quantitative analysis on the wear process of the valve-seat ring.

[0033] In general, the present invention has the following advantages:

[0034] The present invention has a reasonable design and is easy to operate. The higher frequency provided by the hydraulic equipment can ensure that the evaluation of the valve-seat wear performance is completed in a shorter time, solving the problems of long engine test cycle and high cost. In addition, the hydraulic drive device can provide a large loading force, and the control device can output various types of displacement curves, which creates conditions for the test of valve-seats with large explosion pressures and expands the test range of existing testing machines. The precise application of loading force and the precise control of the seating speed and experimental temperature provide a reliable basis for actual production. The test method for valve-seat wear is simple to operate, and has a clearer understanding of the entire wear process of the valve-seat, so as to facilitate the timely replacement of valves and seats in actual applications, extend the service life of the engine, and reduce the occurrence of accidents. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1 Schematic diagram of the planar structure of this embodiment.

[0036] Figure 2 It is a schematic diagram of the planar structure of the hydraulic drive device.

[0037] Figure 3 It is a schematic diagram of the planar structure of the loading device.

[0038] Figure 4 for Figure 3 An enlarged schematic diagram of point A.

[0039] Figure 5 It is a schematic diagram of the planar structure of the reset device.

[0040] Figure 6 A schematic diagram of the plane structure of the rack.

[0041] Figure 7 It is a schematic diagram of the three-dimensional structure of this embodiment.

[0042] Reference numerals:

[0043] 1- hydraulic drive device, 101- hydraulic actuator, 102- filter, 103- hydraulic oil tank, 104- three-phase asynchronous motor;

[0044] 2-loading device, 201-pressure sensor, 202-lower impact shaft, 203-carrying rod sleeve, 204-spring lower support plate, 205-impact spring, 206-guide shaft, 207-impact slider, 208-spring upper support plate, 209-T-plate, 2010-upper impact shaft, 2011-thrust rod, 2012-thrust disc, 2013-valve, 2014-seat ring, 2015-seat ring fixture, 2016-valve guide sleeve, 2017-combustion chamber wall, 2018-guide sleeve gland;

[0045] 3-reset device, 301-reset spring support rod, 302-reset spring lower plate, 303-reset spring, 304-reset spring upper plate, 305-rolling bearing, 306-screw fixing plate, 307-preload top shaft screw;

[0046] 401- all-solid-state heating equipment box, 402- induction heating coil, 403- thermocouple sensor;

[0047] 501-upper water jacket, 502-lower water jacket, 503-cooling water pipe, 504-cooling water tower, 505-adapter, 506-cooling pipeline, 507-pipeline booster pump;

[0048] 6-frame, 601-bottom plate, 602-lower supporting column, 603-lower supporting plate, 604-middle supporting column, 605-middle supporting plate, 606-upper supporting column, 607-upper supporting plate. DETAILED DESCRIPTION

[0049] The present invention will be described in further detail below.

[0050] like Figure 1 , Figure 7As shown, a hydraulically driven valve-seat wear testing device includes a frame 6, a control device, a heating device, a cooling device, a hydraulic driving device 1, a loading device 2, a valve 2013, a seat ring 2014 and a resetting device 3 for the valve 2013, wherein the heating device is used to form a simulated combustion chamber to simulate the high-temperature combustion chamber of the cylinder; the cooling device cools the hydraulic driving device 1 and the surrounding of the simulated combustion chamber respectively; the loading device 2 is used to simulate the explosion pressure generated by the cylinder; the hydraulic driving device 1 is used to drive the loading device 2 to push the valve 2013 to slide in the seat ring 2014 to complete the impact; the resetting device 3 of the valve 2013 is used to reset the valve 2013 after the impact is completed to ensure that the impact can be carried out continuously.

[0051] like Figure 2 As shown, the hydraulic drive device 1 includes a three-phase asynchronous motor 104, a hydraulic oil tank 103, a filter 102 and a hydraulic actuator 101. The three-phase asynchronous motor 104 is connected to the hydraulic oil tank 103, driving the hydraulic oil to enter the hydraulic actuator 101 through the filter 102. The hydraulic actuator 101 is connected to the control device and the loading device 2. The control device controls the hydraulic actuator 101 to output different types of displacement curves to achieve the loading of the explosion pressure through the loading device 2. The hydraulic actuator 101 is PID-regulated and controlled, and its output displacement accuracy can reach 0.01mm. The high accuracy ensures that the same load can be applied each time the distance measuring device is used for measurement, thereby ensuring that the difference measured at intervals is only the wear amount of the valve-seat ring, which provides a key basis for the implementation of the wear test method of the valve-seat ring. At the same time, the measurement of the circumferential cumulative sinking amount of the valve-seat ring at regular intervals can have a clearer understanding of the entire wear process of the valve-seat ring. The hydraulic actuator 101 can also select waveforms such as triangular wave, rectangular wave, square wave and sine wave, providing feasibility for experiments with various loading forms.

[0052] like Figure 3 , Figure 4As shown, the loading device 2 includes an upper impact shaft 2010, a lower impact shaft 202, and a reinforced impact unit. The reinforced impact unit is respectively abutted against the upper impact shaft 2010 and the lower impact shaft 202. The lower impact shaft 202 is provided with a pressure sensor 201. The pressure sensor 201 is connected to the hydraulic drive device 1 to transmit the pressure it bears to the control device in real time. The upper impact shaft 2010 is connected to a push rod 2011. The push disc 2012 is interference fit with the push rod 2011 and is connected to the valve 2013. The valve 2013 is in a simulated combustion chamber and is subjected to a relatively high temperature. The push rod 2011 and the push disc 2012 are located around the simulated combustion chamber and are prone to wear and deformation under a relatively high loading force. The push rod 2011 is mainly arranged to reduce the deformation of the upper impact shaft 2010, and the push rod 2011 and the upper impact shaft 2010 are threadedly connected to ensure coaxiality. The diameter of the push disc 2012 is slightly smaller than the diameter of the valve face end of the valve 2013. In order to prevent the push disc 2012 from deforming under a relatively large loading force, the force direction of the valve 2013 is changed.

[0053] The loading device 2 also includes a seat ring clamp 2015, a combustion chamber wall 2017, a valve guide sleeve 2016 and a guide sleeve cover 2018. The seat ring 2014 is interference fit with the seat ring fixture 2015 and is embedded in the seat ring fixture 2015. The seat ring fixture 2015 is in contact with the combustion chamber wall 2017. The valve guide sleeve 2016 is located inside the combustion chamber wall 2017. The rod of the valve 2013 moves up and down inside the valve guide sleeve 2016. The seat ring 2014, the seat ring fixture 2015, the valve guide sleeve 2016 and the valve 2013 rod have a high coaxiality to avoid eccentric wear of the valve 2013 and the seat ring 2014, as well as wear of the valve guide sleeve 2016 and the valve 2013 rod. The guide sleeve pressure cap 2018 is in contact with the combustion chamber wall 2017 and the upper end of the valve guide sleeve 2016 to avoid the movement of the valve guide sleeve 2016.

[0054] The reinforced impact unit includes a spring lower support plate 204, an impact spring 205 and a spring upper support plate 208. The two ends of the impact spring 205 are respectively abutted against the spring lower support plate 204 and the spring upper support plate 208. The two ends of the spring lower support plate 204 and the spring upper support plate 208 are provided with guide devices. The guide devices include an impact slider 207, a guide shaft 206, and a T-shaped plate 209. The impact slider 207 is fixed to the spring upper support plate 208 and the two ends of the spring lower support plate 204. The guide shaft 206 is parallel to the upper impact shaft 2010 and the lower impact shaft 202. The two ends of the guide shaft 206 are fixed to the T-shaped plate 209, and the T-shaped plate 209 is fixed to the frame 6. The guide device ensures the vertical loading of the force.

[0055] The lower impact shaft 202 and the upper impact shaft 2010 are both sleeved with a rod-carrying sleeve 203 . The rod-carrying sleeve 203 is installed on the frame 6 and has a high degree of coaxiality with the lower impact shaft 202 and the upper impact shaft 2010 .

[0056] like Figure 6 As shown, the frame 6 includes three groups of support columns, namely a lower support column 602, a middle support column 604, and an upper support column 606, and four support plates, namely a bottom plate 601, a lower support plate 603, a middle support plate 605, and an upper support plate 607. The upper support plate 607 is in contact with the guide cylinder pressure cover 2018, and the middle positions of the middle support plate 605 and the lower support plate 603 are in contact with the carrier rod sleeve 203, and T-shaped plates 209 are fixed at both ends. The base plate 601 is connected to the hydraulic actuator 101. Each group of three support columns, namely the lower support column 602, the middle support column 604 and the upper support column 606, consists of four identical parts, which pass through the four support plates, namely the base plate 601, the lower support plate 603, the middle support plate 605 and the upper support plate 607 in sequence. The lower support column 602, the middle support column 604 and the upper support column 606 are internally provided with stepped shafts which are interlocked in sequence. In addition, there is a high degree of parallelism between the four support plates and between the central axes of the four parts of each group of the three groups of support columns, which enhances the stability of the overall structure and improves the reliability of the experiment.

[0057] like Figure 5 As shown, the reset device 3 includes, from top to bottom, a preloaded force top shaft screw 307, a screw fixing plate 306, a rolling bearing 305, a reset spring upper plate 304, a reset spring 303, a reset spring lower plate 302, and reset spring support rods 301 located parallel to both sides, one end of the reset spring support rod 301 contacts the combustion chamber wall 2017, passes through the reset spring lower plate 302, and the other end contacts the screw fixing plate 306, and the screw fixing plate 306 and the preloaded force top shaft screw 307 are respectively fixedly connected to the frame 6. The screw fixing plate 306, the reset spring upper plate 304, and the reset spring lower plate 302 have a high degree of parallelism.

[0058] When the loading device 2 rises, the stem of the valve 2013 pushes the return spring lower plate 302 upward through the center hole of the guide cylinder gland 2018, and the return spring 303 is compressed and stores energy. When the loading device 2 descends, the elastic potential energy of the return spring 303 pushes the return spring lower plate 302 downward, thereby separating the valve 2013 from the seat ring 2014, preparing for the next round of impact.

[0059] The heating device includes a fully solid-state heating device box 401, an induction heating coil 402 and a thermocouple sensor 403. One end of the induction heating coil 402 is connected to the fully solid-state induction heating device box 401, and the other end is wrapped around the valve 2013. The induction heating coil 402 wraps around the valve 2013 and the seat ring 2014 to form a simulated combustion chamber. The thermocouple sensor 403 is fixed inside the push rod 2011 and can instantly detect the temperature of the simulated combustion chamber.

[0060] The cooling device includes a cooling water tower 504, a pipeline booster pump 507, a cooling pipeline 506, an adapter 505, a cooling water pipe 503, an upper water jacket 501 and a lower water jacket 502. The pipeline booster pump 507 allows the water in the cooling water tower 504 to flow through the cooling pipeline 506 to cool the hydraulic oil. The adapter 505 is connected to the cooling pipeline 506. The water flows through the adapter 505 into the cooling water pipe 503, and flows through the upper water jacket 501 and the lower water jacket 502 in sequence to complete the cooling. The upper water jacket 501 contacts the valve guide 2016, and the lower water jacket 502 connects to the upper impact shaft 2010, so as to cool the parts around the simulated combustion chamber, extend the service life of the parts, and ensure the safety of the experiment.

[0061] A hydraulically driven valve-seat wear test method comprises the following steps:

[0062] S1, the control device controls the hydraulic driving device 1 to output a hydraulic force having various types of displacement curves to the loading device 2;

[0063] S2, the loading device 2 drives the valve 2013 to slide and impact the seat ring 2014;

[0064] S3, after the valve 2013 completes the sliding impact in the seat ring 2014, the resetting device 3 resets the valve 2013;

[0065] S4, repeat steps S1-S3.

[0066] Through this test method, the hydraulic drive device 1 can output various types of displacement curves to conduct experiments with various loading forms, can provide a larger loading force, expand the test range of the existing testing machine, create conditions for testing the valve 2013 and the seat ring 2014 that withstand a larger explosion pressure, and provide a reliable basis for actual production.

[0067] Working process:

[0068] The three-phase asynchronous motor 104 drives the hydraulic oil into the hydraulic actuator 101, causing it to output a variable displacement, thereby pushing the entire impact loading rod upward, causing the valve 2013 to contact and wear the seat ring 2014. When the valve 2013 reaches the highest point of displacement, the loading device 2 moves downward, and the valve 2013 moves away from the seat ring 2014 under the action of the reset device 3 and resets to the initial position, and this cycle repeats. According to needs, the PID control device controls the hydraulic actuator 101 to output different types of displacement curves to achieve force loading.

[0069] Measuring the circumferential cumulative sinking of the valve 2013 and the seat ring 2014: At room temperature, place the detachable auxiliary positioning part under the valve 2013, start the hydraulic equipment, set appropriate parameters for the control device to control the hydraulic actuator 101 to rise, so as to apply a certain load force to the valve 2013 and the seat ring 2014. Use a distance measuring device to measure the distance from the bottom of the auxiliary positioning part to the combustion chamber wall 2017 from the positioning hole of the auxiliary positioning part, and measure multiple sets of data from multiple positioning holes. Then set appropriate parameters for the control device to control the hydraulic actuator 101 to descend, remove the auxiliary positioning part, and then control the hydraulic actuator 101 to rise again, so that the valve 2013 just contacts the seat ring 2014, and then turn on the cooling device and the heating device in turn. When the temperature transmitted by the thermocouple sensor 403 reaches the specified reading, set appropriate stroke and frequency parameters for the control device to start the valve-seat wear experiment. After a period of experiment, turn off the heating equipment, wait until the temperature drops to room temperature, and repeat the above steps to measure the distance from the bottom of the auxiliary positioning part to the combustion chamber wall 2017. The difference between the two data is the cumulative circumferential sinking of the valve 2013 and the seat ring 2014 during this period.

[0070] This measurement method can be completed by simple disassembly and assembly, and can make quantitative analysis of the wear condition at any stage of the experimental process, thereby clarifying the entire wear process of the valve-seat ring.

[0071] The cone angle α of the valve 2013 or the seat ring 2014 is measured by an angle measuring instrument, and the cumulative sinking amount of the valve 2013 and the seat ring 2014 is the cosine value of the circumferential cumulative sinking amount divided by the cone angle α.

[0072] In addition, the valve 2013 or the seat ring 2014 before and after the experiment is placed in a 3D profiler to ensure that the sealing contact surface is placed horizontally, and the appropriate parameters are adjusted so that the 3D profiler starts from the position 2mm in front of the sealing surface, and completely scans the entire sealing surface cone of the valve 2013 or the seat ring 2014 to obtain the contour curves before and after the experiment. Select multiple positions before and after the experiment to obtain multiple contour curves. In the drawing software, the first 2mm of the contour curves before and after the experiment are moved to overlap, and the difference between the two curves on the sealing surface is the sinking amount of the valve 2013 or the seat ring 2014, and the sum of the sinking amounts of the valve 2013 and the seat ring 2014 is the cumulative sinking amount of the valve 2013 and the seat ring 2014. The data obtained by comparing the two schemes do not differ by more than 15%, which proves the accuracy of the measurement data of the distance measuring device. Therefore, the present invention can not only measure the cumulative sinking amount of the valve 2013 and the seat ring 2014 before and after the experiment, but also can quantitatively analyze the wear process of the valve-seat ring.

[0073] After the experiment, a cross-shaped steel plate matching the seat ring 2014 is placed on the seat ring fixture 2015, and the seat ring 2014 is removed by a hydraulic press. Due to the interference fit, the mass of the seat ring 2014 is slightly lost during the disassembly and assembly process. If the wear mass of the seat ring 2014 is to be measured, the total mass of the seat ring 2014 and the seat ring fixture 2015 before and after the experiment can be weighed and the difference can be calculated.

[0074] The above embodiments are preferred implementation modes of the present invention, but the implementation modes of the present invention are not limited to the above embodiments. Any other changes, modifications, substitutions, combinations, and simplifications that do not deviate from the spirit and principles of the present invention should be equivalent replacement methods and are included in the protection scope of the present invention.

Claims

1. A hydraulically driven valve-seat wear test device, characterized in that: It includes a frame, a loading device and a control device; The frame is provided with a simulated combustion chamber, and the simulated combustion chamber is provided with matching valves and seat rings; A hydraulic drive device is provided on one side of the simulated combustion chamber, and the hydraulic drive device is connected to the valve through a loading device; The loading device is arranged corresponding to the valve and is used to drive the valve to slide and impact toward the seat ring; A reset device is provided on the other side of the simulated combustion chamber for resetting the valve; The control device is connected to the hydraulic drive device and is used to control the hydraulic drive device to output various types of displacement curves; The loading device includes an upper impact shaft, an impact reinforcement unit and a lower impact shaft, the two ends of the impact reinforcement unit are respectively abutted against the upper impact shaft and the lower impact shaft, and the lower impact shaft is connected to the hydraulic drive device and is arranged corresponding to the valve; A push disc is provided between the upper impact shaft and the valve, a detachable auxiliary positioning piece and a distance measuring device are provided between the push disc and the valve, the width of the auxiliary positioning piece is greater than the valve face end of the valve, the auxiliary positioning piece abuts against the push disc, the simulated combustion chamber is provided with a combustion chamber wall, and the distance measuring device is used to measure the distance between the auxiliary positioning piece and the combustion chamber wall; A cylinder gland is arranged between the valve and the reset device, and the valve stem is passed through the cylinder gland, and the valve stem contacts and separates with the reset device through the cylinder gland in a cycle.

2. A hydraulically driven valve-seat wear testing device according to claim 1, characterized in that: The upper impact shaft and the lower impact shaft are coaxially arranged, and the impact reinforcement unit is provided with a guide device, which is parallel to the upper impact shaft and the lower impact shaft.

3. A hydraulically driven valve-seat wear testing device according to claim 1, characterized in that: The lower impact shaft is provided with a pressure sensor, and the hydraulic drive device comprises a hydraulic actuator, and the hydraulic actuator is respectively connected with the pressure sensor and the control device.

4. A hydraulically driven valve-seat wear testing device according to claim 1, characterized in that: The auxiliary positioning piece is provided with a positioning hole, and the positioning hole is located on one side of the valve.

5. A hydraulically driven valve-seat wear testing device according to claim 1, characterized in that: The reset device comprises a reset spring, one end of which is arranged corresponding to the gas cylinder gland, and the other end of which is fixedly connected to the frame.

6. A hydraulically driven valve-seat wear test method, characterized in that: The hydraulically driven valve-seat wear test device according to any one of claims 1 to 5 comprises the following steps: S1, the control device controls the hydraulic driving device to output hydraulic forces with various types of displacement curves to the loading device; S2, the loading device drives the valve to slide and impact toward the seat ring; S3, after the valve completes sliding impact in the seat ring, the reset device resets the valve; S4, repeat steps S1-S3.

7. A hydraulically driven valve-seat wear test method according to claim 6, characterized in that: The following steps are included: The valve or seat ring before and after the experiment is placed in the 3D profiler successively, so that the sealing contact surface of the valve and the seat ring is placed horizontally, and the conical surface of the sealing contact surface of the valve or the seat ring is scanned by the 3D profiler to obtain the contour curves before and after the experiment; Move the starting positions of the contour curves before and after the experiment until they overlap. The difference between the two curves on the conical surface of the sealing contact surface is the sinking amount of the valve or seat ring respectively, and the sum of the sinking amounts of the valve and seat ring is the cumulative sinking amount of the valve-seat ring.

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