Piston-through type hydraulic damping accumulator

Abstract

We provide a piston-through hydraulic damping accumulator that absorbs or reduces hydraulic shock in real time, thereby smoothing the pressure in the hydraulic system. [Solution] A piston-through type hydraulic damping accumulator comprising a cylinder block 10 having a hollow cavity, a first hydraulic oil hole and a second hydraulic oil hole provided at both ends of the cylinder block 10, a floating spacer 20 dividing the cylinder block 10 into a damping chamber 1011 and a hydraulic oil chamber 1012 that are sealed and isolated from each other, a communicating member 30 for connecting the first hydraulic oil hole, the second hydraulic oil hole and the hydraulic oil chamber, the communicating member provided inside the cylinder block 10 along the central axis direction of the cylinder block 10, and the floating spacer 20 fitted so as to slide and seal to the outside of the communicating member 30. The accumulator can be installed in series with the hydraulic system to immediately capture and absorb hydraulic shocks in the hydraulic system.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic accumulators, and particularly to piston-through type hydraulic damping accumulators.

Background Art

[0002] In a hydraulic transmission system, since the actuator needs to frequently start and stop and change directions, the hydraulic valve port suddenly closes and opens, causing a rapid change in the momentum of the hydraulic oil flowing through the pipeline, thereby causing intense pressure fluctuations. This phenomenon is called "hydraulic shock". Especially in a long pipeline (longer than 30 meters) system, this shock is expressed in the form of "water hammer effect", generating a very strong pressure peak with a destructive force, and its instantaneous value can exceed 40 MPa. Such high-frequency and high-pressure shock waves pose a serious hazard to the safety of the system, causing damage to precision components such as hydraulic valves, pipe joints, and sensors, leading to leakage, and reducing the stability and reliability of the overall operation of the equipment.

[0003] To suppress hydraulic shock, the prior art generally installs a capsule-type or diaphragm-type accumulator in parallel via a three-way joint on the pipeline near the actuator element that is prone to shock. Its operating principle is to utilize the flexibility of the compressible gas (usually nitrogen) in the accumulator to absorb the pressure pulsation of the pipeline. However, this parallel connection method has an inherent defect that when a hydraulic shock arrives, a shock wave is simultaneously transmitted to the accumulator connected in parallel with the hydraulic element. There is a certain response delay in the shock absorption effect of the accumulator, and it cannot completely block the initial shock of the shock wave to the element. More importantly, when dealing with extreme high-pressure shocks such as the "water hammer effect", the rubber diaphragm or capsule has limited shock fatigue strength, so it is easily broken through or torn instantaneously, leading to the failure of the accumulator.

[0004] Furthermore, some technical solutions have opted for conventional piston-type accumulators, which are more pressure-resistant, instead of capsule-type products. While piston structures can withstand higher pressures, their parallel mounting configuration fails to fundamentally solve the problems of "response delay" and "inability to block the initial shock." In high-frequency, high-pressure shock modes, while the reduced shock wave can lessen pipeline vibration, the hydraulic elements still withstand the initial shock force, which is not adequately damped, and the risk of damage remains high. [Overview of the Initiative] [Problems that the invention aims to solve]

[0005] To solve at least one of the above technical problems, the present invention proposes a piston-through type hydraulic damping accumulator, which solves the problem of parallel accumulators being delayed in response and destroyed under high-frequency high-pressure shocks. [Means for solving the problem]

[0006] To achieve the above objectives, the present invention employs the following technical means: A piston-through type hydraulic damping accumulator, Including the following, A cylinder block having a hollow cavity, and a first hydraulic oil hole and a second hydraulic oil hole are provided at both ends of the cylinder block to facilitate the entry and exit of hydraulic oil into and out of the hollow cavity. A floating spacer is provided in the hollow cavity along the central axis direction of the cylinder block and is slidably sealed against the inner wall of the cylinder block, and the floating spacer divides the cylinder block into a damping chamber and a hydraulic oil chamber that are sealed and isolated from each other. A connecting member for connecting the first hydraulic oil hole, the second hydraulic oil hole, and the hydraulic oil chamber, wherein the connecting member is provided within the cylinder block along the central axis direction of the cylinder block, and the floating spacer is fitted to the outside of the connecting member so as to slide and seal. During operation, the accumulator is mounted in series with the hydraulic system, and the floating spacer, in response to hydraulic shock, floats axially under the action of the damping medium in the damping chamber, absorbing or reducing hydraulic shock in real time.

[0007] Preferably, the cylinder block includes the following: Cylinder body and An upper end cap is provided at one end of the cylinder body, and the first hydraulic oil hole is opened on the central axis of the upper end cap. A sealed and volume-variable damping chamber is formed between the upper end cap, the floating spacer, and the inner wall of the cylinder body. The cylinder body includes a lower end cap provided at one end away from the upper end cap, and the second hydraulic oil hole is opened on the central axis of the lower end cap, forming a sealed, variable-volume hydraulic oil chamber between the lower end cap, the floating spacer, and the inner wall of the cylinder body.

[0008] Preferably, the connecting member is a hollow steel pipe, and the ends of the upper end cap and the lower end cap are provided with a first mounting hole and a second mounting hole for accommodating the end of the hollow steel pipe, the central axes of the first mounting hole and the second mounting hole coincide with the central axes of the first hydraulic oil hole and / or the second hydraulic oil hole, and a third hydraulic oil hole communicating with the hydraulic oil chamber is provided around the end of the hollow steel pipe that is close to the lower end cap.

[0009] Preferably, the floating spacer is a piston, the central axis of the piston coincides with the central axis of the cylinder block and / or the central axis of the hollow steel pipe, and the piston is provided with a plug hole for fitting the communicating member along its central axis.

[0010] Preferably, the damping medium is a damping gas and / or an elastic damping material.

[0011] Preferably, if an elastic damping material is provided in the damping chamber, the elastic damping material is fitted to the outside of the hollow steel pipe and is located between the piston and the upper end cap, and the ends of the piston and the upper end cap that are close to each other are provided with a third mounting hole and an annular groove for accommodating the end of a mechanical spring, The annular groove is concentric with the first mounting hole, the inner diameter of the annular groove is larger than the inner diameter of the first mounting hole, and the diameter of the third mounting hole is larger than the diameter of the plug hole.

[0012] Preferably, the elastic damping material is a mechanical spring.

[0013] Preferably, when the damping chamber is filled with damping gas, the upper end cap is provided with a gas passage for injecting the damping gas into the damping chamber, and a one-way charge valve is provided at the intake port of the gas passage.

[0014] Preferably, the damping gas is nitrogen gas.

[0015] Preferably, the accumulator further includes a seal assembly. The seal assembly is A first sealing material fitted to the end of the upper end cap to seal the space between the upper end cap and the inner wall of the cylinder body, A second sealing material fitted to the end of the lower end cap to seal the space between the lower end cap and the inner wall of the cylinder body, A plurality of third sealing materials are fitted at intervals around the outer circumference of the piston to seal the space between the outer wall of the piston and the inner wall of the cylinder body, A plurality of fourth sealing materials are fitted at intervals on the inner wall of the piston to seal the space between the inner wall of the piston and the hollow steel pipe, The invention includes a fifth sealing material fitted to the hollow steel pipe and to the end near the upper end cap in order to seal the space between the hollow steel pipe and the first mounting hole. [Effects of the Invention]

[0016] Compared with the existing technology, the present invention has the following beneficial effects: 1. By installing a floating spacer inside the cylinder block, during operation, through the first hydraulic oil hole and the second hydraulic oil hole at both ends of the cylinder block and via a communication member, an accumulator is connected in series to the hydraulic system without changing the layout of the existing hydraulic pipeline. Thereby, the accumulator can immediately capture and absorb the hydraulic shock in the hydraulic system, avoiding the hydraulic shock from acting on the hydraulic components. The floating spacer floats axially under the action of the damping medium in the damping chamber in response to the hydraulic shock, absorbs or reduces the hydraulic shock in real time to smooth the pressure of the hydraulic system, and solves the problems of reaction delay and damage of the parallel accumulator under high-frequency high-pressure shock. 2. By installing an elastic damping material, when the pressure of the hydraulic system becomes excessive, the piston is rapidly pushed up to the upper end cap. At this time, the elastic damping material (mechanical spring) is compressed, absorbs the kinetic energy of the piston, and provides a buffering force by its own elasticity. When the system pressure fluctuates gently or is in a low-pressure state, the elastic damping material (mechanical spring) applies an upward pushing force on the piston by the damping chamber, enabling the piston to return to the balance state more quickly and stably. At the same time, the damping characteristics of the mechanical spring absorb the minute vibration at the piston balance position and stabilize the movement of the piston, thereby improving the stability of the pressure output of the hydraulic system.

Brief Description of the Drawings

[0017] [Figure 1] is a cross-sectional view of a piston-through hydraulic damping accumulator. [Figure 2] is a structural diagram of the cylinder block of the present invention. [Figure 3] is a cross-sectional view of a piston-through hydraulic damping accumulator having an elastic damping material. [Figure 4] is a structural diagram of the cylinder body of the present invention. [Figure 5] is a structural diagram of the upper end cap of the present invention. [Figure 6] is a plan view of the upper end cap of the present invention. [Figure 7] is a structural view of the piston structure of the present invention. [Figure 8] is a structural view of the lower end cap of the present invention. [Figure 9] is a structural view of the communication member of the present invention.

Embodiments for Carrying out the Invention

[0018] In order for those skilled in the art to better understand the technical aspects of the present invention, the technical aspects in the embodiments of the present invention will be clearly and completely described below in connection with the drawings of the embodiments of the present invention. However, it is clear that the described embodiments are only part of the embodiments of the present invention and not all embodiments of the present invention.

[0019] (Example 1) As shown in FIGS. 1 to 9, a piston-through type hydraulic accumulator, including the following, a cylinder block 10 having a hollow cavity, and at both ends of the cylinder block 10, a first hydraulic oil hole 1021 and a second hydraulic oil hole 1031 are provided to facilitate the entry and outflow of hydraulic oil into the hollow cavity, a floating spacer 20 provided in the hollow cavity along the central axis direction of the cylinder block 10 and slidably sealed to the inner wall of the cylinder block 10. The floating spacer 20 divides the cylinder block 10 into a damping chamber 1011 and a hydraulic oil chamber 1012 that are sealed and isolated from each other, a communication member 30 for communicating the first hydraulic oil hole 1021, the second hydraulic oil hole 1031 and the hydraulic oil chamber 1012. The communication member 30 is provided in the cylinder block 10 along the central axis direction of the cylinder block 10, and the floating spacer 20 is fitted so as to slidably seal outside the communication member 30.

[0020] In this embodiment, by installing a floating spacer 20 within the cylinder block 10, the accumulator is connected in series to the hydraulic system via the first hydraulic oil holes 1021 and the second hydraulic oil holes 1031 at both ends of the cylinder block 10 during operation, without changing the existing hydraulic pipeline layout through the communicating member 30. This allows the accumulator to immediately capture and absorb hydraulic shocks in the hydraulic system, preventing the hydraulic shocks from acting on hydraulic components. The floating spacer 20 floats axially in response to hydraulic shocks under the action of the damping medium in the damping chamber 1011, absorbing or reducing hydraulic shocks in real time, thereby smoothing the pressure in the hydraulic system and solving the problem of delayed response or damage to parallel accumulators under high-frequency, high-pressure shocks.

[0021] As shown in Figures 1 to 3, in a preferred embodiment, the cylinder block 10 includes the following: It is preferable to use a cylinder body 101, specifically a hollow cylinder with a constant inner diameter. An upper end cap 102 is provided at one end of the cylinder body 101, and the first hydraulic oil hole 1021 is opened on the central axis of the upper end cap 102. A sealed and volume-variable damping chamber 1011 is formed between the upper end cap 102, the floating spacer 20, and the inner wall of the cylinder body 101. A lower end cap 103 is provided on the cylinder body 101 at one end away from the upper end cap 102, and a second hydraulic oil hole 1031 is opened on the central axis of the lower end cap 103. A sealed, variable-volume hydraulic oil chamber 1012 is formed between the lower end cap 103, a floating spacer, and the inner wall of the cylinder body 101.

[0022] To facilitate the installation of the upper end cap 102 and the lower end cap 103, in this embodiment, female threads are provided on the inside of both ends of the cylinder body 101, and male threads corresponding to the female threads are provided on the ends of the upper end cap 102 and the lower end cap 103. The upper end cap 102, the lower end cap 103, and the cylinder body 101 are detachably connected using screw connections to form a separate structure. If a part of the structure is damaged, it can be replaced, improving the maintainability and service life of the accumulator. At the same time, the separable design reduces the difficulty of processing a single part, making it convenient for manufacturing and widespread implementation.

[0023] In a preferred embodiment, as shown in Figures 1, 3, and 9, the communicating member 30 is a hollow steel pipe, and the ends of the upper end cap 102 and the lower end cap 103 are provided with a first mounting hole 1024 and a second mounting hole 1032 for accommodating the ends of the hollow steel pipe, the central axes of the first mounting hole 1024 and the second mounting hole 1032 coincide with the central axes of the first hydraulic oil hole 1021 and / or the second hydraulic oil hole 1031, and a third hydraulic oil hole 301 communicating with the hydraulic oil chamber 1012 is provided around the end of the hollow steel pipe that is close to the lower end cap 103.

[0024] What can be understood is that the first hydraulic oil holes 1021 and the second hydraulic oil holes 1031 at both ends of the upper end cap 102 and the lower end cap 103 are in communication with the hydraulic pipeline of the hydraulic system, the hydraulic elements and hydraulic pipe fittings, and when the hydraulic oil in the hydraulic system enters the hydraulic oil chamber 1012 through the third hydraulic oil hole 301, the pressure in the hydraulic oil chamber 1012 becomes the same as the pressure of the hydraulic system, and under the floating adjustment of the floating spacer 20, the damping chamber 1011 and the hydraulic oil chamber 1012 become in a pull-out balance state.

[0025] Furthermore, the third hydraulic oil hole 301 is opened in the radial direction of the hollow steel pipe, and in order to prevent the third hydraulic oil hole 301 from being located inside the second mounting hole 1032 after installation, the hydraulic oil enters the narrow slit region first, forming a flow "dead zone" or vortex, increasing the flow resistance and reducing the response speed.

[0026] In this embodiment, the third hydraulic oil hole 301 is positioned above the second mounting hole 1032 in order to allow hydraulic oil to smoothly enter the hydraulic oil chamber 1012 from the third hydraulic oil hole 301 and improve the response speed.

[0027] At the same time, opening the holes circumferentially ensures that the hydraulic oil enters the hydraulic oil chamber 1012 synchronously from the center outwards, ensuring uniform pressure within the cavity and avoiding situations where the hollow steel pipe receives support from one side, resulting in instantaneous uneven loading and reduced response speed.

[0028] As shown in Figures 1, 3, and 7, the floating spacer 20 in this embodiment is a piston, the central axis of the piston coincides with the central axis of the cylinder block 10 and / or the central axis of the hollow steel pipe, and the piston is provided with a plug hole 201 for fitting the communication member 30 along its central axis direction.

[0029] In this embodiment, the damping medium may be a damping gas and / or an elastic damping material. That is, the damping of the damping accumulator can be achieved by filling the damping chamber with damping gas, by installing an elastic damping material in the damping chamber, or by simultaneously filling the damping chamber with damping gas and installing an elastic damping material. Next, the operating principle of the damping accumulator will be specifically explained with reference to the drawings.

[0030] As shown in Figures 1 and 2, when the damping chamber is filled with damping gas, in this embodiment, to facilitate filling the damping chamber 1011 with damping gas at a constant pressure, the upper end cap 102 is provided with a gas passage 1022 for injecting damping gas into the damping chamber 1011, and a one-way charge valve 1023 is provided at the intake port of the gas passage 1022.

[0031] Specifically, when a hydraulic shock is present in the hydraulic system, the hydraulic oil enters the hydraulic oil chamber 1012 via the communicating member 30, and under the action of the hydraulic oil pressure, the floating spacer 20 compresses the gas in the damping chamber 1011 along the axial direction of the cylinder block 10 without delay, converting the kinetic energy of the hydraulic shock into gas potential (internal energy).

[0032] When the hydraulic system pressure drops, the pressure in the hydraulic oil chamber 1012 becomes lower than the gas pressure in the damping chamber 1011. At this time, the compressed gas expands, pushing the floating spacer 20 and moving in the reverse direction axially of the cylinder block 10 without delay, returning the stored gas potential to the system and compensating for the pressure loss in the hydraulic system.

[0033] Furthermore, during operation, the floating spacer 20 reciprocates via the central guide shaft of the connecting member 30, effectively preventing deflection and locking during the floating process of the floating spacer 20. This ensures the linearity of the floating spacer 20's movement and the reliability of the seal, thereby ensuring stable operation of the accumulator.

[0034] In this embodiment, an inert gas can be used as the damping gas in the damping chamber 1011 as an elastic medium. Specifically, nitrogen gas can be used. By utilizing the characteristics of nitrogen gas, which is non-flammable and easily explosive when compressed, chemical reactions between the hydraulic oil and the sealing material are effectively avoided, and the stability of the internal environment of the accumulator under high-pressure conditions is ensured.

[0035] What can be understood is that, during specific operations, the initial state (initial pressure) of the accumulator damping chamber 1011 can be set according to the operating pressure of the hydraulic system, improving the effectiveness of the accumulator's hydraulic shock absorption and pressure compensation, and expanding the accumulator's applicable range. At the same time, the one-way charge valve 1023 can prevent gas backflow, ensuring long-term stability of the pressure in the damping chamber 1011, and making it easy to replenish the damping chamber 1011 with air in the event of a pressure drop due to minor leakage.

[0036] As shown in Figure 3, when an elastic damping material is provided in the damping chamber and filled with damping gas, specifically, the elastic damping material 40 used in this embodiment is a mechanical spring. The mechanical spring is fitted to the outside of the hollow steel pipe and is located between the upper end cap 102 and the piston.

[0037] To facilitate the installation of the mechanical spring, the ends of the piston and the upper end cap 102 that are close to each other are provided with a third mounting hole 202 and an annular groove 1025 for accommodating the end of the mechanical spring, respectively. The annular groove 1025 is concentric with the first mounting hole 1024, and the inner diameter of the annular groove 1025 is larger than the inner diameter of the first mounting hole 1024, and the diameter of the third mounting hole 202 is larger than the diameter of the plug hole 201.

[0038] It can be understood that when the hydraulic system pressure is too high and the piston is rapidly pushed out against the upper end cap 102, the mechanical spring is compressed, absorbing the piston's kinetic energy and providing a damping force through its own elasticity. When the system pressure fluctuations are gradual or the pressure is low, the mechanical spring adds a damping chamber 1011 to the piston, applying a force that pushes the piston, allowing it to return to the balanced position more quickly and stably. Furthermore, the damping characteristics of the mechanical spring absorb minute vibrations in the piston's balanced position, ensuring stable piston motion and thereby increasing the stability of the hydraulic system's pressure output.

[0039] Furthermore, in extreme cases, if the damping chamber 1011 is depressurized, the mechanical spring can, to some extent, substitute for the function of the damping chamber 1011, maintaining a seesaw balance between the damping chamber 1011 and the hydraulic oil chamber 1012. This provides a mechanical protective barrier to the accumulator and improves the safety redundancy of the device.

[0040] Furthermore, when only an elastic damping material, i.e., a mechanical spring, is installed in the damping chamber, the operating principle is the same as when both an elastic damping material and damping gas are installed in the damping chamber, and this will not be explained further in this application.

[0041] As shown in Figures 1 and 3, in order to improve the overall sealing performance of the accumulator, the accumulator of this embodiment further includes a seal assembly 50. The seal assembly 50 is A first sealing material 501 is fitted to the end of the upper end cap 102 to seal the space between the upper end cap 102 and the inner wall of the cylinder body 101, A second sealing material 502 is fitted to the end of the lower end cap 103 to seal the space between the lower end cap 103 and the inner wall of the cylinder body 101, Multiple third sealing materials 503 are fitted at intervals around the outer circumference of the piston to seal the space between the outer wall of the piston and the inner wall of the cylinder body 101, Multiple fourth sealing materials 504 are fitted at intervals on the inner wall of the piston to seal the space between the inner wall of the piston and the hollow steel pipe, The invention includes a fifth sealing material 505 fitted to the end of the hollow steel pipe near the upper end cap 102 in order to seal the space between the hollow steel pipe and the first mounting hole 1024.

[0042] What can be understood is that the first seal material 501 and the second seal material 502 provide a static seal between the upper end cap 102, the lower end cap 103, and the cylinder body 101, and the fifth seal material 505 provides a static seal between the hollow steel pipe and the upper end cap 102, thereby effectively preventing hydraulic oil from leaking out of the accumulator and avoiding system failure due to oil loss.

[0043] The third seal material 503 and the fourth seal material 504 form a dynamic seal between the piston and the hollow steel pipe and cylinder body 101, preventing damping gas in the damping chamber 1011 from leaking through the gap to the hydraulic oil chamber 1012 and / or hydraulic oil in the hydraulic oil chamber 1012 from leaking through the gap to the damping chamber 1011, thereby preventing the accumulator from becoming sluggish in its response to hydraulic shocks and reducing work efficiency.

[0044] As shown in Figures 1 and 3, the seal between the piston, the hollow steel pipe, and the cylinder body 101 is a dynamic seal. To improve the reliability of the seal, in this embodiment, both the third seal material 503 and the fourth seal material 504 employ a combination seal. Specifically, a combination seal refers to a combination of two or more sealing elements of different materials and shapes, such as the commonly seen "GlydRing + StepSeal" or "O-ring + retaining ring".

[0045] It is understood that the coefficient of friction between the main sealing material (e.g., the PTFE wear-resistant ring in a glailing) and the metal surface in a combination seal is extremely low. This avoids the high friction and startup delay caused by the "stick-slip effect" of conventional rubber seals (e.g., O-rings), allowing the accumulator to respond immediately to high frequencies and minute pressure pulsations.

[0046] At the same time, the combined and sealed wear-resistant ring (e.g., PTFE material) itself is self-lubricating, has better wear resistance, and converts traditional "surface contact" friction to "line contact" or "strip contact." Because the contact area is small, the specific pressure is high and uniform, the sealing effect is guaranteed, and the friction work and wear rate are greatly reduced.

[0047] Furthermore, in combination seals, the elastic element (O-ring) is solely responsible for providing elastic force without direct friction with the metal surface, thus significantly reducing its aging rate.

[0048] Furthermore, in this embodiment, the third seal 503 and the fourth seal 504 are arranged in multiple sets with spacing between them so that the piston has classification pressure resistance and sealing safety redundancy. Specifically, the multiple combination seals form a "pressure step," meaning that the first seal (the highest pressure side) absorbs most of the pressure drop and reduces the pressure to an intermediate value, while the pressure drop on the second seal and subsequent seals decreases in stages. As a result, the overall differential pressure is distributed among the multiple seals, and each seal is kept within its optimal operating pressure range, thereby doubling the overall pressure resistance capacity.

[0049] At the same time, in extreme cases, if the outermost first combination seal fails due to unforeseen damage, the second seal inside it can still perform its primary sealing function, preventing serious internal leakage of the system. Thus, it provides sealing safety redundancy to the accumulator.

[0050] The accumulator provided by this invention has a compact structure, fast response, reliable sealing, is easy to maintain, and has a wide range of applications.

[0051] The above are specific embodiments of the present invention, and it should be noted that general articulators in the field can make several improvements and refinements without departing from the principles of the present invention, and these improvements and refinements should also be considered within the scope of protection of this application. [Explanation of Symbols]

[0052] 10. Cylinder block; 101. Cylinder body; 1011. Damping chamber; 1012. Hydraulic oil chamber; 102. Upper end cap; 1021. First hydraulic oil hole; 1022. Gas passage; 1023. One-way charge valve; 1024. First mounting hole; 1025. Annular groove; 103. Lower end cap; 1031. Second hydraulic oil hole; 1032. Second mounting hole; 20. Floating spacer; 201. Plug hole; 202. Third mounting hole; 30. Communicating member; 301. Third hydraulic oil hole; 40. Elastic damping material; 50. Seal assembly; 501. First seal material; 502. Second seal material; 503. Third seal material; 504. Fourth seal material; 505. Fifth seal material.

Claims

1. A piston-through type hydraulic damping accumulator, Including the following, A cylinder block (10) having a hollow cavity, and at both ends of the cylinder block (10) are provided a first hydraulic oil hole (1021) and a second hydraulic oil hole (1031) to facilitate the entry and exit of hydraulic oil into and out of the hollow cavity. A floating spacer (20) is provided in the hollow cavity along the central axis direction of the cylinder block (10) and is slidably sealed against the inner wall of the cylinder block (10), and the floating spacer (20) divides the cylinder block (10) into a damping chamber (1011) and a hydraulic oil chamber (1012) that are sealed and isolated from each other. A connecting member (30) for connecting the first hydraulic oil hole (1021), the second hydraulic oil hole (1031), and the hydraulic oil chamber (1012), wherein the connecting member (30) is provided inside the cylinder block (10) along the central axis direction of the cylinder block (10), and the floating spacer (20) is fitted to the outside of the connecting member (30) so as to slide and seal. During operation, the accumulator is mounted in series with the hydraulic system, and the floating spacer (20) floats axially in response to hydraulic shock under the action of the damping medium in the damping chamber (1011), absorbing or reducing hydraulic shock in real time. The cylinder block (10) includes the following: Cylinder body (101) and An upper end cap (102) is provided at one end of the cylinder body (101), and the first hydraulic oil hole (1021) is opened on the central axis of the upper end cap (102). A sealed and volume-variable damping chamber (1011) is formed between the upper end cap (102), the floating spacer (20), and the inner wall of the cylinder body (101). A lower end cap (103) is provided at one end of the cylinder body (101) away from the upper end cap (102), and the second hydraulic oil hole (1031) is opened on the central axis of the lower end cap (103), and a sealed, variable-volume hydraulic oil chamber (1012) is formed between the lower end cap (103), the floating spacer (20), and the inner wall of the cylinder body (101). The connecting member (30) is a hollow steel pipe, and the ends of the upper end cap (102) and the lower end cap (103) are provided with a first mounting hole (1024) and a second mounting hole (1032) for accommodating the ends of the hollow steel pipe, the central axes of the first mounting hole (1024) and the second mounting hole (1032) coincide with the central axis of the first hydraulic oil hole (1021) and / or the second hydraulic oil hole (1031), and a third hydraulic oil hole (301) communicating with the hydraulic oil chamber (1012) is provided around the end of the hollow steel pipe that is close to the lower end cap (103). The floating spacer (20) is a piston, the central axis of the piston coincides with the central axis of the cylinder block (10) and / or the central axis of the hollow steel pipe, and the piston is provided with a plug hole (201) along its central axis for fitting the communicating member (30). The damping medium is a damping gas and / or an elastic damping material (40), If an elastic damping material is provided in the damping chamber, the elastic damping material is fitted to the outside of the hollow steel pipe and is located between the piston and the upper end cap, and at the ends where the piston and the upper end cap (102) are close to each other, a third mounting hole (202) and an annular groove (1025) for accommodating the end of a mechanical spring are provided, A piston-through type hydraulic damping accumulator characterized in that the annular groove (1025) is concentric with the first mounting hole (1024), the inner diameter of the annular groove (1025) is larger than the inner diameter of the first mounting hole (1024), and the diameter of the third mounting hole (202) is larger than the diameter of the plug hole (201).

2. The piston-through type hydraulic damping accumulator according to claim 1, characterized in that the elastic damping material (40) is a mechanical spring.

3. The piston-through type hydraulic damping accumulator according to claim 1, characterized in that when damping gas is filled into the damping chamber, the upper end cap (102) is provided with a gas passage (1022) for injecting damping gas into the damping chamber (1011), and a one-way charge valve (1023) is provided at the intake port of the gas passage (1022).

4. The piston-through type hydraulic damping accumulator according to claim 3, characterized in that the damping gas is nitrogen gas.

5. The accumulator further includes a seal assembly (50), The seal assembly (50) is A first sealing material (501) is fitted to the end of the upper end cap (102) to seal the space between the upper end cap (102) and the inner wall of the cylinder body (101), A second sealing material (502) is fitted to the end of the lower end cap (103) to seal the space between the lower end cap (103) and the inner wall of the cylinder body (101), A plurality of third sealing materials (503) are fitted at intervals around the outer circumference of the piston to seal the space between the outer wall of the piston and the inner wall of the cylinder body (101), A plurality of fourth sealing materials (504) are fitted at intervals on the inner wall of the piston to seal the space between the inner wall of the piston and the hollow steel pipe, A piston-through type hydraulic damping accumulator according to any one of claims 1 to 4, characterized in that it includes a fifth sealing material (505) fitted to the hollow steel pipe and the end near the upper end cap (102) in order to seal the space between the hollow steel pipe and the first mounting hole (1024).

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