Heavy load impact rod hydrostatic bearing device and impact cylinder

Abstract

This application discloses a heavy-duty impact rod hydrostatic bearing device and impact cylinder, relating to the technical field of large impact equipment. It includes a hydrostatic bearing body with an even number of pressure oil chambers (not less than four) evenly distributed along the circumferential direction of the inner bore wall. The pressure oil chambers are symmetrically arranged along the axial center of the hydrostatic bearing body. A first return oil ring groove is provided at equal intervals on both sides of the pressure oil chamber along the axial direction. A damping ring gap is formed between the first return oil ring grooves, the pressure oil chambers, and the outer wall of the impact rod. The two first return oil ring grooves are connected to an external oil tank for oil storage via return oil channels. Each pressure oil chamber is connected to a damping structure with damping holes. The pressure oil chambers are connected to an external pressure oil source via the damping holes. When the impact rod is subjected to a radial load, the pressure oil chamber on the side with smaller gaps exerts a greater thrust on the impact rod, while the pressure oil chamber on the side with larger gaps exerts a less balanced thrust on the impact rod, thus achieving automatic repositioning of the impact rod to the center position.

Description

Technical Field

[0001] This application relates to the field of large impact equipment technology, and in particular to a heavy-duty impact rod hydrostatic bearing device and impact cylinder. Background Technology

[0002] For large, high-speed, heavy-duty impact equipment, the impact speed is much higher than that of ordinary impactors. The actuating element used for impact is the impact cylinder, which includes the cylinder body and the impact rod sliding inside the cylinder body. The radial load it bears during the impact process is also very large. The impact rod moves at high speed in the cylinder body. The piston rod of ordinary impact cylinders has high friction, which is not conducive to obtaining high impact speed. When subjected to radial impact load, the impact cylinder is very easy to be damaged. Especially when the impact rod and the impact head directly impact the impacted part, the impact rod bears severe axial and radial loads. Often, the impact rod will deform and scratch the surface inside the cylinder body guide sleeve, resulting in obstructed extension and contraction of the impact rod and sealing leakage. Severe damage can even lead to serious consequences such as bending and breaking of the impact rod.

[0003] If hydrostatic bearings can achieve fluid friction, they can greatly reduce operating friction resistance and wasted power consumption, and can withstand large loads. However, some hydrostatic bearings in conventional technology are only used for the rotational motion of the shaft. The shaft does not move axially within the bearing. The working position of the shaft and the bearing is relatively fixed, and they only bear loads in a definite direction on the circumference. Most large hydrostatic bearings are not closed complete circles in the circumferential direction. Such hydrostatic bearings cannot meet the working conditions of impact rods with loads in any circumferential direction.

[0004] For existing hydrostatic bearing schemes used in impactor design, the automatic centering adjustment scheme adopts diaphragm feedback. The feedback pressure-displacement mechanical parameters of the diaphragm are difficult to adapt to the oil pressure changes caused by the eccentricity of the impact rod. As a result, the feedback adjustment is difficult to achieve a stable equilibrium position. It is very likely that the adjustment oscillation phenomenon will occur, or the feedback centering effect will be insignificant, failing to achieve the preset control purpose, and failing to achieve the stable automatic centering adjustment function of the impact rod.

[0005] In summary, existing conventional technologies cannot meet the operational requirements of high-speed gas-liquid impact testing systems. Therefore, there is a need for an impact rod bearing that can withstand radially varying loads during the impact process of high-speed axial movement of the impact rod. This bearing should achieve stable liquid friction, reduce frictional resistance, prevent scratching of the impact rod, and possess the ability to automatically center itself against external radial loads when the impact rod deviates from the center and presses against the bearing wall due to radial load interference. Summary of the Invention

[0006] To help the impact rod withstand radial heavy loads during high-speed axial movement, this application provides a heavy-duty impact rod hydrostatic bearing device and an impact cylinder.

[0007] Firstly, this application provides a heavy-duty impact rod hydrostatic bearing device, which adopts the following technical solution:

[0008] A heavy-duty impact rod hydrostatic bearing device includes a hydrostatic bearing body. The hydrostatic bearing body has an even number of pressure oil chambers (not less than four) evenly distributed along its inner bore wall. The pressure oil chambers are symmetrically arranged along the axial center of the hydrostatic bearing body. A first oil return ring groove is provided at equal intervals on both sides of each pressure oil chamber along the axial direction. A damping ring gap is formed between the inner bore wall of the hydrostatic bearing body and the pressure oil chambers (not less than four), and between the two first oil return ring grooves and the outer wall of the impact rod used for impact, connecting the first oil return ring grooves and the pressure oil chambers. The two first oil return ring grooves are connected to an external oil tank for oil storage via oil return channels. Each of the four pressure oil chambers is connected to a damping structure with damping holes. Each of the four pressure oil chambers is connected to an external pressure oil source via the damping holes.

[0009] By adopting the above technical solution, when the impact rod is not subjected to external radial load, the thrust of the oil in each pressure oil chamber on the impact rod is symmetrical and equal. The impact rod is in a dynamic equilibrium state at the center position of the hydrostatic bearing body. When the impact rod is subjected to radial load, the gap of the damping ring gap on the side bearing the load increases, and the gap on the opposite side decreases. The flow area of ​​the damping ring gap from the pressure oil chamber on the side with the smaller gap to the first return oil ring groove decreases, the flow resistance of the oil passage on this side of the damping ring gap increases, and the flow rate through the damping ring gap on this side decreases, resulting in a decrease in the flow rate through the damping structure of the oil passage. The pressure drop at both ends of the damping structure connected to this pressure oil chamber decreases, that is, the pressure oil chamber P L With oil supply pressure P P The oil pressure difference between them decreases, at the oil supply pressure P P Under the condition that the return oil pressure P0 remains constant, the oil pressure P in the pressure oil chamber will increase. L As the pressure increases, the thrust on the impact rod increases on the side with a smaller gap, resisting the load and causing the impact rod to return to its center position. Similarly, the flow area of ​​the damping annulus on the side with a larger gap increases, reducing the flow resistance of the oil passage in the damping annulus on this side and increasing the flow rate to the damping annulus on this side. This leads to an increase in the flow rate to the damping structure of the oil passage in the pressure oil chamber on this side, increasing the pressure drop across the damping structure, i.e., the pressure oil chamber P on this side... L With oil supply pressure P P The oil pressure difference between them increases, at the oil supply pressure P P Under the condition that the return oil pressure P0 remains constant, the oil pressure P in the pressure oil chamber on this side LThe pressure oil chamber on the side with a larger gap will inevitably decrease, reducing the balancing thrust on the impact rod. This will also cause the impact rod to return to the center position. Through the opposite changes in the thrust of the pressure oil chambers on both sides, the impact rod can resist radial load and achieve automatic centering control. This reliably ensures that the relative movement between the impact rod and the hydrostatic bearing body is non-contact fluid friction.

[0010] Preferably, the damping structure is an oil inlet passage disposed on the outer wall of the hydrostatic bearing body and communicating with the pressure oil chamber. A damping plug is installed on the oil inlet passage, and the damping plug is provided with the damping hole. A pressure oil ring groove is provided circumferentially along the outer wall of the hydrostatic bearing body at one end of the oil inlet passage away from the pressure oil chamber. The pressure oil ring groove is connected to a pressure oil passage on the impact cylinder body for mounting the hydrostatic bearing body and communicating with an external pressure oil source.

[0011] By adopting the above technical solution, a pressure oil ring groove is set on the outer wall of the hydrostatic bearing body, which helps to connect each oil inlet corresponding to the pressure oil chamber with the external pressure oil source. A damping plug is installed on the oil inlet, thereby better adjusting the pressure of the pressure oil chamber and realizing the reset of the impact rod to the center position.

[0012] Preferably, a reduced-diameter oil passage is provided at one end of the oil inlet passage near the pressure oil chamber, and a threaded hole is provided at the other end of the reduced-diameter oil passage away from the pressure oil chamber. The damping plug is sealed and fixed to the threaded hole, and the channel structure and diameter of the damping hole of each damping plug are the same.

[0013] By adopting the above technical solution, the reduced-diameter oil passage is located close to the pressure oil chamber and its diameter is smaller than that of the inlet oil passage. This facilitates the setting of threaded holes on the reduced-diameter oil passage, making it easier to install and remove the damping plug. This improves the convenience of installing, removing and maintaining the damping plug. The damping hole has the same channel structure and diameter, which helps to ensure that each pressure oil chamber has a consistent damping adjustment effect.

[0014] Preferably, the oil return channel is a first transverse oil return channel that is transversely connected to the first oil return ring groove, and a longitudinal oil return channel that is connected to the two first transverse oil return channels at both ends. The outer wall of the hydrostatic bearing body is provided with a second oil return ring groove. The second oil return ring groove is connected to the longitudinal oil return channel through the second transverse oil return channel. The second oil return ring groove is connected to the external oil tank through the transition oil return channel on the impact cylinder body.

[0015] By adopting the above technical solution, the return oil of the damping ring gap first flows through two first return oil ring grooves, then flows through the first transverse return oil channel to the longitudinal return oil channel, then flows from the longitudinal return oil channel through the second transverse return oil channel to the second return oil ring groove, and finally connects to the external oil tank through the transition return oil channel on the impact cylinder block. This enables the oil in the damping ring gap to flow back to the oil tank, realizing the flow circulation of the damping ring gap.

[0016] Preferably, the hydrostatic bearing device further includes a fixed sealing assembly, which includes a first fixed seal, a second fixed seal, and a third fixed seal. A first sealing groove and a second sealing groove are provided on both sides of the pressure oil ring groove, and a third sealing groove is provided on the side of the second sealing groove away from the first sealing groove. The second return oil ring groove is provided between the second sealing groove and the third sealing groove. The first fixed seal, the second fixed seal, and the third fixed seal are sequentially installed in the first sealing groove, the second sealing groove, and the third sealing groove.

[0017] By adopting the above technical solution, by installing the first fixed seal and the second fixed seal in the first sealing groove and the second sealing groove respectively, it helps to reduce the leakage of hydraulic oil in the pressure oil ring groove from the first fixed seal and the second fixed seal to both ends. By installing the third fixed seal in the third sealing groove, it helps to reduce the leakage of hydraulic oil in the second return oil ring groove from the second fixed seal and the third fixed seal to both ends, thus ensuring the normal operation of the hydraulic oil circuit.

[0018] Preferably, the hydrostatic bearing device further includes a sliding seal assembly, which includes two sliding seals. Each sliding seal groove is provided on the inner wall of the first oil return ring groove near the end of the hydrostatic bearing body, and the sliding seal is installed in the sliding seal groove.

[0019] By adopting the above technical solution, the sliding sealing groove is set on the side of the first return oil ring groove near the end of the hydrostatic bearing body, which helps to prevent the hydraulic oil in the rod chamber of the impact cylinder from leaking into the first return oil ring groove, or the hydraulic oil in the first return oil ring groove from leaking out from the end of the hydrostatic bearing body, thereby improving the stability of the hydraulic oil operation in the first return oil ring groove.

[0020] Secondly, this application provides an impact cylinder, which adopts the following technical solution:

[0021] An impact cylinder includes an impact cylinder body, an impact rod, and the aforementioned heavy-duty impact rod hydrostatic bearing device located between the impact cylinder body and the impact rod, and further includes a fixing assembly for fixing the hydrostatic bearing body to the impact cylinder body.

[0022] By adopting the above technical solution, the impact cylinder fixes the hydrostatic bearing body and the impact cylinder body together through the fixing component, which helps to prevent the hydrostatic bearing body from moving axially along the impact rod and improves the reliability of the hydrostatic bearing device.

[0023] Preferably, the fixing component includes a cylinder head, the cylinder head having a through hole through which the impact rod passes, one end of the cylinder head near the impact cylinder body being fixedly connected to the end of the impact cylinder body, and the hydrostatic bearing body being fixedly connected to the cylinder head.

[0024] By adopting the above technical solution, the fixing assembly helps to improve the stability of the hydrostatic bearing body installation by installing the cylinder head at one end of the impact cylinder and then fixing the hydrostatic bearing body to the cylinder head.

[0025] Preferably, the fixing assembly further includes a plurality of retaining keys. The impact cylinder body has an annular keyway at one end near the cylinder head, and the plurality of retaining keys are installed in the annular keyway. The hydrostatic bearing body has a reduced diameter section at one end near the cylinder head. The reduced diameter section forms a step with the outer wall of the hydrostatic bearing body. The retaining key abuts against the step at one end away from the cylinder head. A thrust ring is integrally provided on the side of the cylinder head near the retaining key. The thrust ring abuts against the end of the retaining key near the cylinder head.

[0026] By adopting the above technical solution, the fixing component installs several locking keys in the annular keyway of the impact cylinder. One end of the locking key abuts against the step of the hydrostatic bearing body, which increases the impact force that the hydrostatic bearing body can withstand along the axial direction of the impact rod. In addition, the thrust ring set on the cylinder head abuts against the lower end face of the locking key, which further increases the axial force that the hydrostatic bearing body can withstand, thereby improving the reliability of the hydrostatic bearing body.

[0027] In summary, this application includes at least one of the following beneficial technical effects:

[0028] 1. This application has the function of ensuring good alignment between the impact rod and the hydrostatic bearing body, and has the effect of resisting the interference of radial load on the alignment position of the impact rod. It can reliably ensure that the relative motion between the impact rod and the hydrostatic bearing body achieves fluid friction, greatly reducing motion friction resistance and waste power consumption, reducing the wear of the impact rod and bearing, extending the service life of the equipment, reducing the probability of equipment damage, and has a simple structure, stable performance, reliability, durability, and long service life. It provides a beneficial solution for the design and manufacture of heavy-duty rod-type motion mechanisms.

[0029] 2. A pressure oil ring groove is provided on the outer wall of the hydrostatic bearing body, which helps each pressure oil chamber to connect with the external pressure oil source through the oil inlet. A damping plug is installed on the oil inlet to better adjust the pressure of the pressure oil chamber and realize the reset of the impact rod to the center position.

[0030] 3. The oil at both ends of the damping ring gap first flows through the first return oil ring groove, then through the first transverse return oil channel to the longitudinal return oil channel, and then through the longitudinal return oil channel to the second return oil ring groove via the second transverse return oil channel. Finally, it is connected to the external oil tank through the transition return oil channel on the impact cylinder block, which enables the oil at both ends of the damping ring gap to flow back to the oil tank.

[0031] 4. The fixing component installs several locking keys in the annular keyway of the impact cylinder. One end of each locking key abuts against the step of the hydrostatic bearing body, which increases the impact force that the hydrostatic bearing body can withstand along the axial direction of the impact rod. In addition, the thrust ring integrally set on the cylinder head abuts against the lower end face of the locking keys, which further increases the axial force that the hydrostatic bearing body can withstand, thereby improving the reliability of the hydrostatic bearing body. Attached Figure Description

[0032] Figure 1 This is a cross-sectional view of a heavy-duty impact rod hydrostatic bearing device disclosed in this application, with the cross-section passing through the pressure oil chamber.

[0033] Figure 2 This is a cross-sectional view of a heavy-duty impact rod hydrostatic bearing device disclosed in this application, with the cross-section passing through the oil return channel.

[0034] Figure 3 For along Figure 1 A cross-sectional view along line AA in the middle.

[0035] Figure 4 for Figure 3 A magnified view of the area at position I.

[0036] Figure 5 For along Figure 2 A cross-sectional view along the BB line.

[0037] Explanation of reference numerals in the attached figures:

[0038] 1. Hydrostatic bearing housing; 11. Pressure oil chamber; 12. Pressure oil ring groove; 13. First return oil ring groove; 14. Oil inlet passage; 141. Reduced diameter oil passage; 1411. Threaded hole; 142. Damping plug; 1421. Damping hole; 15. Return oil channel; 151. First transverse return oil channel; 152. Longitudinal return oil channel; 153. Second return oil ring groove; 154. Second transverse return oil channel; 161. First sealing groove; 162. Second sealing groove; 163. 17. Third sealing groove; 18. Sliding sealing groove; 2. Step; 3. Damping annular seam; 4. Fixed sealing assembly; 5. First fixed seal; 6. Second fixed seal; 7. Third fixed seal; 8. Sliding sealing assembly; 9. Sliding seal; 10. Impact cylinder; 11. Pressure oil passage; 12. Transition return oil passage; 13. Annular keyway; 14. Impact rod; 15. Fixed assembly; 16. Cylinder head; 17. Thrust ring; 18. Locking key. Detailed Implementation

[0039] The following combination Figures 1 to 5 This application will be described in further detail.

[0040] This application discloses a heavy-duty impact bar hydrostatic bearing device.

[0041] A heavy-duty impact rod hydrostatic bearing device. (Refer to...) Figure 1 and Figure 2 The bearing includes a hydrostatic bearing body 1. The hydrostatic bearing body 1 has an even number of pressure oil chambers 11, not less than four, evenly distributed along the circumferential direction of its inner bore wall. In this embodiment, the number of pressure oil chambers 11 is four; in other embodiments, the number is six or eight. The number of pressure oil chambers 11 is related to the inner bore diameter of the hydrostatic bearing; a larger diameter allows for a greater number of pressure oil chambers 11. The pressure oil chambers 11 are symmetrically arranged along the axial center of the hydrostatic bearing body 1. A first oil return ring groove 13 is provided at equal intervals on both sides of each pressure oil chamber 11 along the axial direction. The two first oil return ring grooves 13 communicate with the inner bore wall of the hydrostatic bearing body 1 between the two pressure oil chambers 11 and the even number of pressure oil chambers 11, and with the outer wall of the impact rod 6 used for impact. The first return oil ring groove 13 and the damping ring gap 2 of the pressure oil chamber 11 are connected to the external oil tank for oil storage through the return oil channel 15. The pressure oil chambers 11, which are not less than 4, are respectively connected to a damping structure. The damping structure is provided with a damping hole 1421. The pressure oil chambers 11, which are not less than 4, are respectively connected to an external pressure oil source through the damping hole 1421. It should be noted that the shape of the pressure oil chamber 11 along the circumferential direction can be rectangular or circular, and the axial section can be rectangular or crescent-shaped. The pressure oil chamber 11 has a certain thickness in the radial direction. The pressure oil can flow freely in the pressure oil chamber 11. The size of the damping ring gap 2 and the size of the damping hole 1421 are related to the radial load, oil supply pressure and flow rate.

[0042] In this embodiment, an impact rod 6 is installed inside the hydrostatic bearing housing 1. One end of the impact rod 6, installed inside the impact cylinder 5, is connected to an impact piston, and the other end is fitted with an impact head for impact. In other embodiments of this application, a piston rod is used. The impact rod 6 or the piston rod can withstand heavy axial forces along the axial direction, with loads exceeding one hundred tons. During the impact process, when the impact rod 6 is not subjected to external radial loads, the thrust of the oil in each pressure oil chamber 11 on the impact rod 6 is symmetrical and equal. The impact rod 6 is located at the center of the hydrostatic bearing housing 1. In a dynamic equilibrium state, when the impact rod 6 is subjected to a radial load during its movement, the gap of the damping ring slit 2 on the side bearing the load increases, while the gap on the opposite side decreases. The flow area of ​​the damping ring slit 2 leading from the pressure oil chamber 11 on the side with the smaller gap to the first return oil ring groove 13 decreases, increasing the flow resistance of the oil passage in this side of the damping ring slit 2. This reduces the flow rate through the damping structure, resulting in a decrease in the flow rate through the damping structure. Consequently, the pressure drop across the damping structure connected to this pressure oil chamber 11 decreases, meaning the oil pressure P in the pressure oil chamber 11 decreases. L With oil supply pressure P P The oil pressure difference between them decreases, at the oil supply pressure P P Under the condition that the return oil pressure P0 remains constant, the oil pressure P in the pressure oil chamber 11 will increase. LAs the pressure increases, the thrust on the impact rod 6 increases on the side of the pressure oil chamber 11 with a smaller gap, resisting the load and causing the impact rod 6 to return to its center position. Similarly, the flow area of ​​the damping annular gap 2 increases on the side with a larger gap, reducing the flow resistance of the oil passage in the damping annular gap 2 on this side. This increases the flow rate to the damping structure of the oil passage in the pressure oil chamber 11 on this side, increasing the pressure drop across the damping structure. In other words, the oil pressure P in the pressure oil chamber 11 on this side increases. L With oil supply pressure P P The oil pressure difference between them increases, at the oil supply pressure P P Under the condition that the return oil pressure P0 remains constant, the oil pressure P in the pressure oil chamber 11 on this side L The pressure oil chamber 11 on the side with larger gap will inevitably decrease, reducing the balancing thrust of the impact rod 6. This will also cause the impact rod 6 to return to the center position. Through the opposite changes in the thrust of the pressure oil chambers 11 on both sides, the impact rod 6 can resist radial load and achieve automatic centering control function. This reliably ensures that the relative movement between the impact rod 6 and the hydrostatic bearing body 1 is non-contact liquid friction.

[0043] Reference Figure 3 and Figure 4 The damping structure is an oil inlet channel 14 on the outer wall of the hydrostatic bearing body 1, which communicates with the pressure oil chamber 11. A damping plug 142 is installed on the oil inlet channel 14, and a damping hole 1421 is provided on the damping plug 142. A pressure oil ring groove 12 is provided circumferentially along the outer wall of the hydrostatic bearing body 1 at the end of the oil inlet channel 14 away from the pressure oil chamber 11. The pressure oil ring groove 12 is connected to the pressure oil channel 51 on the impact cylinder 5 used to install the hydrostatic bearing body 1, which is connected to an external pressure oil source. The pressure oil ring groove 12 on the outer wall of the hydrostatic bearing body 1 helps each oil inlet channel 14 corresponding to the pressure oil chamber 11 to communicate with the external pressure oil source. The damping plug 142 is installed on the oil inlet channel 14, which can better adjust the pressure of the pressure oil chamber 11 and realize the automatic reset of the impact rod 6 to the center position.

[0044] Reference Figure 4 A reduced-diameter oil passage 141 is provided at one end of the oil inlet passage 14 near the pressure oil chamber 11, and a threaded hole 1411 is provided at the other end of the reduced-diameter oil passage 141 away from the pressure oil chamber 11. The damping plug 142 is sealed and fixed to the threaded hole 1411. The channel structure and diameter of the damping holes 1421 of each damping plug 142 are the same. The reduced-diameter oil passage 141 is located near the pressure oil chamber 11 and its diameter is smaller than that of the oil inlet passage 14, which helps to provide the threaded hole 1411 on the reduced-diameter oil passage 141, making it convenient to install and remove the damping plug 142, and improving the convenience of installation, removal and maintenance of the damping plug 142. The channel structure and diameter of the damping holes 1421 are the same, which helps to make each pressure oil chamber 11 have a consistent damping adjustment effect.

[0045] Reference Figure 2 and Figure 5 The return oil channel 15 consists of a first transverse return oil channel 151 that is transversely connected to the first return oil ring groove 13, and a longitudinal return oil channel 152 that is connected to the two first transverse return oil channels 151 at both ends. A second return oil ring groove 153 is provided on the outer wall of the hydrostatic bearing body 1. The second return oil ring groove 153 is connected to the longitudinal return oil channel 152 through a second transverse return oil channel 154. The second return oil ring groove 153 is connected to the external oil tank through the transition return oil channel 52 on the impact cylinder body 5. The return oil of the damping ring gap 2 first flows through the two first return oil ring grooves 13, then flows through the first transverse return oil channel 151 to the longitudinal return oil channel 152, and then flows through the longitudinal return oil channel 152. The oil flows through the second transverse return oil passage 154 to the second return oil ring groove 153, and finally connects to the external oil tank through the transition return oil passage 52 on the impact cylinder 5. This allows the oil in the damping ring gap 2 to flow back to the oil tank, realizing the flow circulation of the damping ring gap 2. It should be noted that, during the processing of the first transverse return oil passage 151, for ease of processing, the first transverse return oil passage 151 can be drilled along the radial direction of the hydrostatic bearing body 1, and then the inlet end of the drilled hole can be sealed with a plug. Similarly, to facilitate the processing of the longitudinal return oil passage 152, the longitudinal return oil passage 152 can be drilled along the axial direction of the hydrostatic bearing body 1, and then the inlet end of the drilled hole can be sealed with a plug.

[0046] Reference Figure 1 and Figure 2 The hydrostatic bearing device also includes a fixed sealing assembly 3, which includes a first fixed seal 31, a second fixed seal 32, and a third fixed seal 33. The three fixed seals have identical structures. A first sealing groove 161 and a second sealing groove 162 are provided on both sides of the pressure oil ring groove 12. A third sealing groove 163 is provided on the side of the second sealing groove 162 away from the first sealing groove 161. A second return oil ring groove 153 is located between the second sealing groove 162 and the third sealing groove 163. The first fixed seal 31, the second fixed seal 32, and the third fixed seal 33 are sequentially installed... Within the first sealing groove 161, the second sealing groove 162, and the third sealing groove 163, by installing the first fixed seal 31 and the second fixed seal 32 in the first sealing groove 161 and the second sealing groove 162 respectively, it helps to reduce the leakage of hydraulic oil in the pressure oil ring groove 12 from the first fixed seal 31 and the second fixed seal 32 to both ends. By installing the third fixed seal 33 in the third sealing groove 163, it helps to reduce the leakage of hydraulic oil in the second return oil ring groove 153 from the second fixed seal 32 and the third fixed seal 33 to both ends, thus ensuring the normal operation of the hydraulic oil circuit.

[0047] Reference Figure 1The hydrostatic bearing device also includes a sliding seal assembly 4, which includes two sliding seals 41. Each sliding seal groove 17 is provided on the inner wall of the first return oil ring groove 13 near the end of the hydrostatic bearing body 1. The sliding seals 41 are installed in the sliding seal grooves 17. The sliding seals 41 are allowed to have a small radial elastic displacement with the impact rod 6 in the sealing groove. The sliding seal grooves 17 are located on the side of the first return oil ring groove 13 near the end of the hydrostatic bearing body 1, which helps to prevent the hydraulic oil in the rod cavity of the impact cylinder 5 from leaking into the first return oil ring groove 13, or the hydraulic oil in the first return oil ring groove 13 from leaking out from the end of the hydrostatic bearing body 1, thereby improving the stability of the hydraulic oil operation in the first return oil ring groove 13.

[0048] This application also discloses an impact cylinder.

[0049] An impact cylinder, reference Figure 2 The device includes an impact cylinder 5, an impact rod 6, and the aforementioned heavy-duty impact rod hydrostatic bearing device located between the impact cylinder 5 and the impact rod 6. It also includes a fixing assembly 7 for fixing the hydrostatic bearing body 1 and the impact cylinder 5. The impact cylinder fixes the hydrostatic bearing body 1 and the impact cylinder 5 together through the fixing assembly 7, which helps to prevent the hydrostatic bearing body 1 from moving axially along the impact rod 6 and improves the reliability of the hydrostatic bearing device.

[0050] Reference Figure 2 The fixing assembly 7 includes a cylinder head 71, which has a through hole through which the impact rod 6 passes. The end of the cylinder head 71 near the impact cylinder body 5 is fixedly connected to the end of the impact cylinder body 5. The hydrostatic bearing body 1 is fixedly connected to the cylinder head 71. The fixing assembly 7 fixes the cylinder head 71 to one end of the impact cylinder body 5 with screws, and then fixes the hydrostatic bearing body 1 to the cylinder head 71 together with screws, which helps to improve the firmness of the installation of the hydrostatic bearing body 1.

[0051] Reference Figure 2The fixing component 7 also includes several retaining keys 72. An annular keyway 53 is provided at one end of the impact cylinder body 5 near the cylinder head 71, and several retaining keys 72 are installed within the annular keyway 53. A reduced-diameter section is provided at one end of the hydrostatic bearing body 1 near the cylinder head 71, forming a step 18 with the outer wall of the hydrostatic bearing body 1. The end of the retaining key 72 away from the cylinder head 71 abuts against the step 18. A thrust ring 711 is integrally provided on the side of the cylinder head 71 near the retaining key 72, and the end of the thrust ring 711 near the retaining key 72 abuts against the step 18. The retaining key 72 abuts against one end of the cylinder head 71; the fixing assembly 7 installs several retaining keys 72 in the annular keyway 53 of the impact cylinder 5, with one end of the retaining key 72 abutting against the step 18 of the hydrostatic bearing body 1, thereby increasing the impact force borne by the hydrostatic bearing body 1 along the axial direction of the impact rod 6. In addition, the thrust ring 711 provided on the cylinder head 71 abuts against the lower end face of the retaining key 72, further increasing the axial force borne by the hydrostatic bearing body 1, thereby improving the reliability of the operation of the hydrostatic bearing body 1.

[0052] The working principle of an impact cylinder according to an embodiment of this application is as follows: the pressure oil passage 51 on the impact cylinder body 5 is connected to an external pressure oil source, and the transition return oil passage 52 is connected to an external oil tank. During the impact process, when the impact rod 6 is not subjected to an external radial load, the thrust of the oil in each pressure oil chamber 11 on the impact rod 6 is symmetrical and equal. The impact rod 6 is in a dynamic equilibrium state at the center position of the hydrostatic bearing body 1. When the impact rod 6 is subjected to a radial load during the impact process, the gap of the damping ring slit 2 on the side bearing the load increases, and the gap on the opposite side decreases. The flow area of ​​the damping ring slit 2 leading to the first return oil ring groove 13 of the pressure oil chamber 11 with the smaller gap decreases, the flow resistance of the oil passage of the damping ring slit 2 on this side increases, and the flow rate through the damping ring slit 2 on this side decreases, resulting in a decrease in the flow rate through the damping hole 1421 of the oil passage. The pressure drop at both ends of the damping hole 1421 connected to this pressure oil chamber 11 decreases, that is, the oil pressure P of the pressure oil chamber 11 decreases. L With oil supply pressure P P The oil pressure difference between them decreases, at the oil supply pressure P P Under the condition that the return oil pressure P0 remains constant, the oil pressure P in the pressure oil chamber 11 will increase. L As the pressure increases, the thrust of the impact rod 6 on the pressure oil chamber 11 on the side with smaller gap increases, resisting the load and causing the impact rod 6 to return to its center position. Similarly, the flow area of ​​the damping annular gap 2 on the side with larger gap increases, the flow resistance of the oil passage in the damping annular gap 2 on this side decreases, and the flow rate to the damping annular gap 2 on this side increases, resulting in an increase in the flow rate to the damping orifice 1421 of the oil passage in the pressure oil chamber 11 on this side. The pressure drop across the damping orifice 1421 increases, that is, the oil pressure P of the pressure oil chamber 11 on this side increases. L With oil supply pressure P P The oil pressure difference between them increases, at the oil supply pressure P P Under the condition that the return oil pressure P0 remains constant, the oil pressure P in the pressure oil chamber 11 on this sideL The pressure oil chamber 11 on the side with larger gap will inevitably decrease, reducing the balancing thrust of the impact rod 6. This will also cause the impact rod 6 to return to the center position. Through the opposite changes in the thrust of the pressure oil chambers 11 on both sides, the impact rod 6 can resist radial load and achieve automatic centering control of the impact rod 6. This reliably ensures that the relative movement between the impact rod 6 and the hydrostatic bearing body 1 is non-contact liquid friction.

[0053] The above are all preferred embodiments of this application, and are not intended to limit the scope of protection of this application. Therefore, all equivalent changes made in accordance with the structure, shape and principle of this application should be covered within the scope of protection of this application.

Claims

1. A heavy-duty impact rod hydrostatic bearing device, characterized in that: The system includes a hydrostatic bearing body (1), which has an even number of pressure oil chambers (11) of not less than 4 evenly distributed along the circumferential direction of its inner bore wall. The pressure oil chambers (11) are symmetrically arranged along the axial center of the hydrostatic bearing body (1). A first oil return ring groove (13) is provided at equal intervals on both sides of the pressure oil chamber (11) along the axial direction. The inner bore wall of the hydrostatic bearing body (1) between the two first oil return ring grooves (13) and the even number of pressure oil chambers (11) of not less than 4, and the grooves are used for impact. A damping annular groove (2) is formed between the outer walls of the impact rod (6) to connect the first return oil annular groove (13) and the pressure oil chamber (11). The two first return oil annular grooves (13) are connected to an external oil tank for oil storage through the return oil channel (15). A damping structure is provided for each of the even number of pressure oil chambers (11) not less than 4. The damping structure is provided with a damping hole (1421). A damping hole (1421) is provided for each of the even number of pressure oil chambers (11) not less than 4. The external pressure oil source is connected through the damping hole (1421). The damping structure is an oil inlet channel (14) connected to the pressure oil chamber (11) on the outer wall of the hydrostatic bearing body (1). A damping plug (142) is installed on the oil inlet channel (14). The damping plug (142) is provided with the damping hole (1421). A pressure oil ring groove (12) is provided circumferentially along the outer wall of the hydrostatic bearing body (1) at one end of the oil inlet channel (14) away from the pressure oil chamber (11). The pressure oil ring groove (12) is connected to the pressure oil channel (51) connected to the external pressure oil source on the impact cylinder (5) used to install the hydrostatic bearing body (1). The oil inlet channel (14) is provided with a reduced diameter oil channel (141) at one end near the pressure oil chamber (11), and a threaded hole (1411) is provided at the other end of the reduced diameter oil channel (141) away from the pressure oil chamber (11). The damping plug (142) is sealed and fixed to the threaded hole (1411). The damping hole (1421) of each damping plug (142) has the same channel structure and diameter. The oil return channel (15) is a first transverse oil return channel (151) that is transversely connected to the first oil return ring groove (13), and a longitudinal oil return channel (152) that is connected to the two first transverse oil return channels (151) at both ends. The outer wall of the hydrostatic bearing body (1) is provided with a second oil return ring groove (153). The second oil return ring groove (153) is connected to the longitudinal oil return channel (152) through a second transverse oil return channel (154). The second oil return ring groove (153) is connected to the external oil tank through a transition oil return channel (52) on the impact cylinder body (5).

2. The heavy-duty impact rod hydrostatic bearing device according to claim 1, characterized in that: The hydrostatic bearing device further includes a fixed sealing assembly (3), which includes a first fixed seal (31), a second fixed seal (32), and a third fixed seal (33). A first sealing groove (161) and a second sealing groove (162) are provided on both sides of the pressure oil ring groove (12). A third sealing groove (163) is provided on the side of the second sealing groove (162) away from the first sealing groove (161). A second return oil ring groove (153) is provided between the second sealing groove (162) and the third sealing groove (163). The first fixed seal (31), the second fixed seal (32), and the third fixed seal (33) are installed in the first sealing groove (161), the second sealing groove (162), and the third sealing groove (163) in sequence.

3. The heavy-duty impact rod hydrostatic bearing device according to claim 2, characterized in that: The hydrostatic bearing device further includes a sliding seal assembly (4), which includes two sliding seals (41). Each of the inner walls of the first oil return ring groove (13) near the end of the hydrostatic bearing body (1) is provided with a sliding seal groove (17), and the sliding seals (41) are installed in the sliding seal grooves (17).

4. An impact cylinder, characterized in that, The device includes an impact cylinder (5), an impact rod (6), and a heavy-duty impact rod hydrostatic bearing device according to any one of claims 1-3 located between the impact cylinder (5) and the impact rod (6), and further includes a fixing assembly (7) for fixing the hydrostatic bearing body (1) to the impact cylinder (5).

5. An impact cylinder according to claim 4, characterized in that: The fixing component (7) includes a cylinder head (71), which has a through hole through which the impact rod (6) passes. The end of the cylinder head (71) near the impact cylinder body (5) is in contact with and fixed to the end of the impact cylinder body (5). The hydrostatic bearing body (1) is fixedly connected to the cylinder head (71).

6. An impact cylinder according to claim 5, characterized in that: The fixing component (7) also includes several locking keys (72). The impact cylinder (5) has an annular keyway (53) at one end near the cylinder head (71). Several locking keys (72) are installed in the annular keyway (53). The hydrostatic bearing body (1) has a reduced diameter section at one end near the cylinder head (71). The reduced diameter section forms a step (18) with the outer wall of the hydrostatic bearing body (1). The end of the locking key (72) away from the cylinder head (71) abuts against the step (18). The side of the cylinder head (71) near the locking key (72) is integrally provided with a thrust ring (711). The end of the thrust ring (711) near the locking key (72) abuts against the end of the locking key (72) near the cylinder head (71).

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