Closed hydrostatic guideway with adaptive high variable load and control method thereof

Abstract

This invention discloses a closed hydrostatic guide rail with adaptive high variable load and its control method, including an oil tank for storing hydraulic oil, the oil tank being connected to an oil circuit mechanism; the closed hydrostatic guide rail further includes: a guide rail mechanism, including a guide rail body, a slider controlled by a linear motor slidably connected to the guide rail body, the slider having multiple oil chambers communicating with the guide rail body; a pulsation damping mechanism, disposed on the pipeline of the oil circuit mechanism; the pulsation damping mechanism includes a spring, the lower end of the spring being connected to a diaphragm. The pulsation damping mechanism of this invention adjusts the preload of the spring by changing the oil pressure, thereby reducing oil pressure pulsation and thus maintaining stable oil pressure and uniform oil film in the oil circuit.

Description

Technical Field

[0001] This invention relates to a closed hydrostatic guide rail with adaptive high variable load and its control method, belonging to the field of hydrostatic guide rail technology. Background Technology

[0002] In the field of precision machining, closed hydrostatic guideways, with their frictionless support characteristics, have become a core functional component of high-precision machine tools. This technology delivers pressurized oil to the oil chamber between the guideway and moving parts through an external oil supply system, forming a load-bearing hydrostatic oil film that completely separates the relatively moving parts, thereby achieving ultra-high rigidity support, excellent vibration resistance, and an ultra-long service life. However, existing closed hydrostatic guideways face the challenge of precision stability caused by multi-physics coupling under complex working conditions. When heavy machine tools encounter sudden load changes, temperature fluctuations, or drastic changes in movement speed, traditional fixed-parameter oil supply systems and throttling structures cannot respond in real time. For example, in machining scenarios such as deep hole boring and high-speed milling, a sudden increase in axial load or a sudden change in the speed of moving parts can disrupt the oil film pressure balance, causing nonlinear fluctuations in oil pressure within the oil chamber. If the oil supply system cannot provide timely dynamic pressure compensation, the moving parts will experience instantaneous displacement or tilting due to uneven oil film thickness, directly causing increased workpiece machining tolerances, surface morphology distortion, and even a significant increase in scrap rate. This type of precision failure caused by multi-physics coupling essentially stems from the fact that the fixed throttling mode of existing guide rail systems cannot adjust the oil film stiffness and pressure distribution according to real-time operating conditions, resulting in a mismatch between the oil film's load-bearing capacity and external load requirements. Therefore, there is an urgent need to invent a self-adjusting closed hydrostatic guide rail to solve the above problems. Summary of the Invention

[0003] The purpose of this invention is to provide a closed hydrostatic guide rail with adaptive high variable load. The pulsation damping mechanism of this invention adjusts the preload of the spring by varying the oil pressure, thereby reducing oil pressure pulsation and maintaining stable oil pressure and uniform oil film in the oil circuit.

[0004] The technical solution of the present invention: A closed hydrostatic guide rail with adaptive high variable load, comprising an oil tank for storing hydraulic oil, the oil tank being connected to an oil circuit mechanism; the closed hydrostatic guide rail further comprises:

[0005] The guide rail mechanism includes a guide rail body, on which a slider controlled by a linear motor is slidably connected. The slider has multiple oil chambers communicating with the guide rail body. The hydraulic oil in the oil tank is delivered to the oil chambers through an oil circuit mechanism, so that an oil film is formed between the oil chambers and the guide rail body to support the slider and reduce the friction coefficient of the slider.

[0006] A pulsation damping mechanism is installed on the pipeline of the oil circuit mechanism; the pulsation damping mechanism is equipped with a spring, and the lower end of the spring is connected to a diaphragm; the pulsation damping mechanism adjusts the preload of the spring according to the hydraulic pressure pulsation, and the spring preload provides a reverse restoring force, so that the diaphragm counteracts the hydraulic pressure fluctuation, thereby stabilizing the output oil pressure of the oil circuit mechanism and ensuring the uniformity of the oil film.

[0007] The aforementioned closed hydrostatic guide rail with adaptive high variable load has a T-shaped guide rail body; the slider is wrapped around the outside of the guide rail body; multiple upper oil passages, side oil passages and lower oil passages are symmetrically arranged on both sides of the slider, and the inner ends of the upper oil passages, side oil passages and lower oil passages are respectively connected to the corresponding oil chambers; anti-collision blocks are provided at both ends of the guide rail body.

[0008] The aforementioned closed hydrostatic guide rail with adaptive high variable load includes a pulsating damping mechanism comprising a housing, an oil inlet on the upper side of the housing, oil outlets on both sides of the lower end of the housing, and a damping adjustment mechanism at the upper end of the housing, the output end of which is connected to a spring.

[0009] The aforementioned closed hydrostatic guide rail with adaptive high variable load includes a damping adjustment mechanism comprising a motor mounted at the top of the housing, the motor's output end penetrating the housing and connected to a coupling, a planetary gear positioned below the coupling, and the lower end of the coupling connected to the sun gear of the planetary gear; a lead screw fixedly connected below the planet carrier of the planetary gear, and an internally threaded post connected below the lead screw, the thread on the inner side of the internally threaded post engaging with the lead screw; a diaphragm positioned below the internally threaded post, the edge of the diaphragm fixedly connected to the interior of the housing; the diaphragm being located above the oil inlet; a spring positioned between the diaphragm and the gear ring of the planetary gear; and the gear ring of the planetary gear being fixedly connected to the housing.

[0010] The aforementioned closed hydrostatic guide rail with adaptive high variable load has a sealing nut threadedly connected to the outer side of the oil outlet on one side.

[0011] The aforementioned closed hydrostatic guide rail with adaptive high variable load includes a hydraulic circuit mechanism comprising a hydraulic pump connected to an oil tank via a pipeline, a cooler connected to the oil outlet of the hydraulic pump via a pipeline, two filters connected to the oil outlet of the cooler via pipelines, and multiple parallel pulsation damping mechanisms connected to the oil outlet of each filter via pipelines. The oil outlet of each pulsation damping mechanism is connected to an upper oil passage, a side oil passage, and a lower oil passage on the same side of the slider via pipelines.

[0012] The aforementioned closed hydrostatic guide rail with adaptive high variable load has an energy storage device and a pressure gauge connected sequentially on the pipeline between the cooler and the filter.

[0013] The aforementioned closed hydrostatic guide rail with adaptive high variable load has an overflow valve connected to the oil outlet end of the filter; and a flow meter is installed on the oil inlet pipeline of the pulsating damping mechanism.

[0014] The aforementioned control method for a closed hydrostatic guide rail with adaptive high variable load involves using an oil circuit mechanism to deliver hydraulic oil from the tank to the oil chamber of the slider after adjustment by a pulsation damping mechanism. This creates an oil film between the oil chamber and the guide rail body, supporting the slider. When small oil pressure pulsations occur in the oil circuit, the pulsation damping mechanism stretches the spring, reducing its preload. Conversely, when large oil pressure pulsations occur, the pulsation damping mechanism contracts the spring, increasing its preload. The spring's preload provides a counteracting force, counteracting hydraulic pressure fluctuations. This allows for adjustment of the spring's preload through oil pressure changes, reducing oil pressure pulsations and maintaining stable oil pressure and a uniform oil film throughout the oil circuit.

[0015] Compared with the prior art, the present invention has the following beneficial effects:

[0016] 1. In this invention, the hydraulic oil in the tank is sent to the pulsation damping mechanism through the oil circuit system, and after being adjusted by the pulsation damping mechanism, it is sent to the oil chamber of the slider, so that an oil film is formed between the oil chamber and the guide rail body to support the slider; the pulsation damping mechanism adjusts the preload of the spring through the change of oil pressure pulsation, and provides a reverse restoring force through the preload of the spring to counteract the fluctuation of hydraulic pressure, thereby realizing the adjustment of the preload of the spring by the change of oil pressure, which can reduce the oil pressure pulsation, thereby always maintaining the stability of the oil circuit oil pressure and the uniformity of the oil film, and has the advantage of high stability.

[0017] 2. In this invention, the slider has multiple upper oil passages, side oil passages, and lower oil passages on both sides. When hydraulic oil is injected into the corresponding oil passages and enters the oil chamber, multiple independent oil films are simultaneously generated between the slider and the guide rail body. These oil films constitute a fully constrained support system. Through the natural coupling effect of hydrostatic pressure, the external load is evenly distributed to each bearing area, effectively avoiding single-point overload. The synergistic effect of multiple oil films can simultaneously resist vertical loads, lateral offsets, and overturning moments, enabling the slider to maintain consistent motion posture under complex working conditions, significantly improving guiding accuracy and operational stability, and providing reliable dynamic support performance for precision motion pairs.

[0018] 3. In this invention, the motor of the damping adjustment mechanism drives the coupling to rotate, and the coupling drives the sun gear in the planetary gear to rotate. Because the gear ring in the planetary gear is fixedly connected to the housing and cannot rotate, the sun gear can only drive the planetary gear to rotate. When the planetary gear rotates, the planet carrier and the lead screw below it rotate accordingly. Because the edge of the diaphragm is fixedly connected to the inner wall of the housing, the internal threaded column cannot rotate, so that the internal threaded column rises or falls along the lead screw during the rotation of the lead screw. When it is necessary to reduce the spring preload, the motor rotates forward, causing the internal threaded column and the diaphragm to fall. When it is necessary to increase the spring preload, the motor rotates in reverse, causing the internal threaded column and the diaphragm to rise. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the oil circuit of the present invention;

[0020] Figure 2 This is a schematic diagram of the pulsation damping mechanism;

[0021] Figure 3 This is a schematic diagram of the internal structure of the pulsation damping mechanism;

[0022] Figure 4 This is a schematic diagram of the damping adjustment mechanism;

[0023] Figure 5 This is a schematic diagram of the guide rail mechanism;

[0024] Figure 6 This is a cross-sectional view of the guide rail mechanism.

[0025] The labels in the attached diagram are as follows: 1-oil tank, 2-oil circuit mechanism, 3-guide rail mechanism, 4-pulsation damping mechanism, 200-hydraulic pump, 201-cooler, 202-filter, 203-accumulator, 204-pressure gauge, 205-relief valve, 206-flow meter, 300-guide rail body, 301-linear motor, 302-slider, 303-oil chamber, 304-upper oil passage, 305-side oil passage, 306-lower oil passage, 307-anti-collision block, 400-housing, 401-oil inlet, 402-oil outlet, 403-damping adjustment mechanism, 404-spring, 405-motor, 406-coupling, 407-planetary gear, 408-lead screw, 409-internal threaded column, 410-diaphragm, 411-sealing nut. Detailed Implementation

[0026] The present invention will be further described below with reference to the accompanying drawings and embodiments, but this should not be construed as limiting the present invention.

[0027] Example: A closed hydrostatic guide rail with adaptive high variable load, configured as follows Figure 1-6As shown, it includes an oil tank 1 for storing hydraulic oil, and the oil tank 1 is connected to an oil circuit mechanism 2; the closed hydrostatic guide rail also includes:

[0028] Guide rail mechanism 3, such as Figure 5 and Figure 6 As shown, the system includes a guide rail body 300, which is T-shaped and has a surface hardened by quenching. A wear-resistant cast iron slider 302, controlled by a linear motor 301, is slidably connected to the guide rail body 300. The slider 302 has multiple oil cavities 303 communicating with the guide rail body 300. Hydraulic oil from the oil tank 1 is delivered to the oil cavities 303 via an oil circuit mechanism 2, forming an oil film between the oil cavities 303 and the guide rail body 300 to support the slider 302 and reduce its coefficient of friction. The slider 302 surrounds the outside of the guide rail body 300. Multiple upper oil passages 304, side oil passages 305, and lower oil passages 306 are symmetrically arranged on both sides of the slider 302. The inner ends of the upper oil passages 304, side oil passages 305, and lower oil passages 306 are respectively connected to... The corresponding oil chambers 303 are connected; both ends of the guide rail body 300 are provided with anti-collision blocks 307. The anti-collision blocks 307 are designed with elastic buffer to prevent the slider 302 from detaching from the guide rail body 300 and to buffer collisions when it moves to the end; the slider 302 is provided with multiple upper oil passages 304, side oil passages 305 and lower oil passages 306 on both sides. When hydraulic oil is injected into the corresponding oil passages and enters the oil chambers 303, multiple independent oil films are generated simultaneously between the slider 302 and the guide rail body 300. These oil films constitute a fully constrained support system. Through the natural coupling effect of hydrostatic pressure, the external load is evenly distributed to each bearing area, effectively avoiding single-point overload. The synergistic effect of multiple oil films can simultaneously resist vertical loads, lateral offsets and overturning moments, so that the slider 302 can still maintain the consistency of its motion posture under complex working conditions, significantly improving guiding accuracy and running stability, and providing reliable dynamic support performance for precision motion pairs. The guide rail mechanism 3 is applied to various parts of the machine tool that require linear movement. For example, in a CNC machine tool with a top adaptive dressing wheel, the dressing wheel table body is connected to the slider 302, and the guide rail body 300 is set on the machine tool housing. The CNC machine tool drives the lead screw mechanism through a corresponding motor to make the slider 302 on the dressing wheel table body move along the guide rail body 300, thereby adjusting the distance between the dressing wheel and the grinding wheel and dressing the grinding wheel. During this movement, the guide rail mechanism 3 maintains the consistency of the movement posture of the dressing wheel, improves the guiding accuracy and running stability, and thus improves the dressing accuracy.

[0029] The pulsation damping mechanism 4 is installed on the pipeline of the oil circuit mechanism 2; for example... Figure 3As shown, the pulsation damping mechanism 4 is equipped with a spring 404, and the lower end of the spring 404 is connected to a diaphragm 410. The pulsation damping mechanism 4 adjusts the preload of the spring 404 according to the hydraulic pressure pulsation. The preload of the spring 404 provides a reverse restoring force, so that the diaphragm 410 counteracts the hydraulic pressure fluctuation, thereby stabilizing the output oil pressure of the oil circuit mechanism 2 and ensuring the uniformity of the oil film. The pulsation damping mechanism 4 includes a housing 400, with an oil inlet 401 on the upper side of the housing 400. Oil outlets 402 are respectively provided on both sides of the lower end of the housing 400. A damping adjustment mechanism 403 is provided at the upper end of the housing 400, and the output end of the damping adjustment mechanism 403 is connected to the spring 404. The damping adjustment mechanism 403 includes a motor 405 mounted at the top of the housing 400. The output end of the motor 405 passes through the interior of the housing 400 and is connected to a coupling 406. A planetary gear 407 is located below the coupling 406, and the lower end of the coupling 406 is connected to the sun gear of the planetary gear 407. A lead screw 408 is fixedly connected below the planet carrier of the planetary gear 407. An internally threaded post 409 is connected below the lead screw 408, and the thread on the inner side of the internally threaded post 409 is screwed into the lead screw 408. A diaphragm 410 is located below the internally threaded post 409, and the edge of the diaphragm 410 is fixedly connected to the interior of the housing 400 for sensing oil pressure changes and transmitting displacement. The diaphragm 410 is located above the oil inlet 401. A spring 404 is located between the diaphragm 410 and the gear ring of the planetary gear 407. The gear ring of the planetary gear 407 is fixedly connected to the housing 400. The motor 405 of the damping adjustment mechanism 403 drives the coupling 406 to rotate, and the coupling 406 drives the sun gear in the planetary gear 407 to rotate. Because the gear ring in the planetary gear 407 is fixedly connected to the housing 400 and cannot rotate, the sun gear can only drive the planetary gears to rotate. When the planetary gears rotate, the planet carrier and the lead screw 408 below them rotate accordingly. Because the edge of the diaphragm 410 is fixedly connected to the inner wall of the housing 400, the internal threaded column 409 cannot rotate, so that the internal threaded column 409 rises or falls along the lead screw 408 during the rotation of the lead screw 408. When it is necessary to reduce the preload of the spring 404, the motor 405 rotates forward, causing the internal threaded column 409 and the diaphragm 410 to fall. When it is necessary to increase the preload of the spring 404, the motor 405 rotates in reverse, causing the internal threaded column 409 and the diaphragm 410 to rise.

[0030] Preferably, such as Figure 2 As shown, a sealing nut is threadedly connected to the outer side of the oil outlet 402 on one side. When the oil outlet 402 on one side is not in use, it is sealed by screwing on the sealing nut. If the oil outlet 402 on the other side is blocked after use, the sealing nut can be removed and screwed onto the blocked oil outlet 402, and oil can be discharged through the unobstructed oil outlet 402 on the other side, ensuring that the oil circuit is redundant and ready for use.

[0031] Preferably, such as Figure 1As shown, the oil circuit mechanism 2 includes a hydraulic pump 200 connected to the oil tank 1 via a pipeline. The hydraulic pump 200 provides a stable high-pressure oil source. The oil outlet of the hydraulic pump 200 is connected to a cooler 201 via a pipeline. The cooler 201 controls the temperature of the oil. The oil outlet of the cooler 201 is connected to two filters 202 via pipelines. The filters 202 remove impurities from the oil. The oil outlet of the filters 202 is connected to multiple parallel pulsation damping mechanisms 4 via pipelines. The oil outlet 402 of each pulsation damping mechanism 4 is connected via pipelines to the upper oil passage 304, the side oil passage 305, and the lower oil passage 306 on the same side of the slider 302. An energy storage device 203 and a pressure gauge 204 are connected sequentially on the pipeline between the cooler 201 and the filters 202. The energy storage device 203 is used to compensate for flow fluctuations and stabilize oil pressure, and the pressure gauge 204 displays the oil circuit pressure in real time. The oil outlet of the filter 202 is connected to an overflow valve 205 before the branch line to prevent system overload; the oil inlet pipe of the pulsation damping mechanism 4 is equipped with a flow meter 206 to monitor the oil flow in real time and feed it back to the control system.

[0032] The control method for the aforementioned closed hydrostatic guide rail with adaptive high variable load is described in the following steps:

[0033] Hydraulic oil is pressurized from oil tank 1 via oil circuit mechanism 2 and regulated by pulsation damping mechanism before being injected into corresponding oil chambers 303 through pipelines via upper oil passages 304, side oil passages 305, and lower oil passages 306 on both sides of slider 302. This forms multiple independent oil films between the upper, side, and lower contact surfaces of slider 302 and guide rail body 300. External loads are evenly distributed to the bearing areas of each oil film through hydrostatic pressure. The upper oil film resists vertical loads, the side oil films constrain lateral offset, and the lower oil film balances overturning moment, preventing oil film failure caused by single-point overload. The synergistic effect of multiple oil films forms dynamic support stiffness, compensating for load changes under complex working conditions such as off-center loading and impact in real time, ensuring the stability of slider 302's movement posture, and reducing vibration and offset.

[0034] A pulsation damping mechanism 4 is connected in series in the oil circuit. It suppresses oil pressure pulsation by dynamically adjusting the preload of the spring 404. When pressure pulsation occurs in the oil circuit, the diaphragm 410 at the oil inlet 401 undergoes a slight displacement due to pressure changes, triggering the damping adjustment mechanism 403. The motor 405 drives the sun gear of the coupling 406 and planetary gear 407 to rotate. Because the gear ring is fixed, the sun gear drives the planetary gears to rotate around the gear ring, thereby causing the lead screw 408 below the planetary carrier to rotate synchronously. When the lead screw 408 rotates, the internally threaded column 409, which is engaged with it, rises or falls axially. When a reduction in preload is needed, the motor 405 rotates forward, causing the internally threaded column 409 to fall, stretching the spring 404, reducing the preload, and allowing the diaphragm 410 to deform more significantly to absorb low-frequency pulsations. When a increase in preload is needed, the motor 405 rotates in reverse, causing the internally threaded column 409 to rise, compressing the spring 404, increasing the preload, and enhancing the stiffness of the diaphragm 410 to resist high-frequency, high-pressure pulsations. The reverse restoring force generated by the preload of spring 404 counteracts the hydraulic pressure fluctuations, and the pulsating energy is dissipated through the elastic deformation of diaphragm 410, so as to stabilize the output oil pressure and ensure uniform oil film thickness.

[0035] Therefore, the pulsation damping mechanism of the present invention can reduce oil pressure pulsation by adjusting the preload of the spring through changes in oil pressure, thereby maintaining the stability of oil pressure and the uniformity of oil film in the oil circuit.

Claims

1. A closed hydrostatic guide rail with adaptive high variable load, comprising an oil tank (1) for storing hydraulic oil, the oil tank (1) being connected to an oil circuit mechanism (2); characterized in that: The closed hydrostatic guide rail also includes: The guide rail mechanism (3) includes a guide rail body (300), on which a slider (302) controlled by a linear motor (301) is slidably connected. The slider (302) has multiple oil chambers (303) communicating with the guide rail body (300). The hydraulic oil in the oil tank (1) is sent to the oil chambers (303) through the oil circuit mechanism (2), so that an oil film is formed between the oil chambers (303) and the guide rail body (300) to support the slider (302) and reduce the friction coefficient of the slider (302). A pulsation damping mechanism (4) is installed on the pipeline of the oil circuit mechanism (2); the pulsation damping mechanism (4) is provided with a spring (404), and the lower end of the spring (404) is connected to a diaphragm (410); the pulsation damping mechanism (4) adjusts the preload of the spring (404) according to the hydraulic pressure pulsation, and the preload of the spring (404) provides a reverse restoring force, so that the diaphragm (410) counteracts the hydraulic pressure fluctuation, so as to stabilize the output oil pressure and make the oil film of the oil circuit mechanism (2) stable; The pulsating damping mechanism (4) includes a housing (400), with an oil inlet (401) on the upper side of the housing (400); oil outlets (402) are respectively provided on both sides of the lower end of the housing (400); a damping adjustment mechanism (403) is provided at the upper end of the housing (400), and a spring (404) is connected to the output end of the damping adjustment mechanism (403). A sealing nut (411) is threadedly connected to the outer side of the oil outlet (402) on one side.

2. The closed hydrostatic guide rail with adaptive high variable load according to claim 1, characterized in that: The guide rail body (300) is T-shaped; the slider (302) surrounds the outside of the guide rail body (300); multiple upper oil passages (304), side oil passages (305) and lower oil passages (306) are symmetrically arranged on both sides of the slider (302), and the inner ends of the upper oil passages (304), side oil passages (305) and lower oil passages (306) are respectively connected to the corresponding oil cavities (303); anti-collision blocks (307) are provided at both ends of the guide rail body (300).

3. The closed hydrostatic guide rail with adaptive high variable load according to claim 1, characterized in that: The damping adjustment mechanism (403) includes a motor (405) mounted on the top of the housing (400). The output end of the motor (405) is inserted into the housing (400) and connected to a coupling (406). A planetary gear (407) is located below the coupling (406), and the lower end of the coupling (406) is connected to the sun gear of the planetary gear (407). A lead screw (408) is fixedly connected below the planet carrier of the planetary gear (407), and an internal thread is connected below the lead screw (408). The internal thread of the internal threaded column (409) is screwed into the lead screw (408); a diaphragm (410) is provided below the internal threaded column (409), and the edge of the diaphragm (410) is fixedly connected to the inside of the housing (400); the diaphragm (410) is located above the oil inlet (401); the spring (404) is disposed between the diaphragm (410) and the gear ring of the planetary gear (407); the gear ring of the planetary gear (407) is fixedly connected to the housing (400).

4. The closed hydrostatic guide rail with adaptive high variable load as described in claim 1, characterized in that: The oil circuit mechanism (2) includes a hydraulic pump (200) connected to the oil tank (1) via a pipeline. The oil outlet of the hydraulic pump (200) is connected to a cooler (201) via a pipeline. The oil outlet of the cooler (201) is connected to two filters (202) via a pipeline. The oil outlet of the filter (202) is connected to multiple parallel pulsation damping mechanisms (4) via a pipeline. The oil outlet (402) of each pulsation damping mechanism (4) is connected to the upper oil passage (304), side oil passage (305) and lower oil passage (306) on the same side of the slider (302) via a pipeline.

5. The closed hydrostatic guide rail with adaptive high variable load according to claim 4, characterized in that: An energy storage device (203) and a pressure gauge (204) are connected in sequence on the pipeline between the cooler (201) and the filter (202).

6. The closed hydrostatic guide rail with adaptive high variable load according to claim 5, characterized in that: The filter (202) is connected to an overflow valve (205) at the oil outlet end; a flow meter (206) is provided on the oil inlet pipe of the pulsation damping mechanism (4).

7. The control method for a closed hydrostatic guide rail with adaptive high variable load according to any one of claims 1-6, characterized in that: The hydraulic oil in the tank is regulated by a pulsation damping mechanism and then delivered to the oil chamber of the slider. This creates an oil film between the oil chamber and the guide rail body, supporting the slider. When small oil pressure pulsations occur in the oil circuit, the pulsation damping mechanism stretches the spring, reducing its preload. When large oil pressure pulsations occur, the pulsation damping mechanism contracts the spring, increasing its preload. The preload provides a counter-recovery force to counteract hydraulic pressure fluctuations, thus adjusting the spring preload based on oil pressure changes, reducing oil pressure pulsations, and maintaining stable oil pressure and a uniform oil film throughout the oil circuit.

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