Hydraulic cylinder independent floating balance stroke tail end bidirectional combined buffering device

Abstract

The invention discloses a hydraulic cylinder independent floating balance stroke tail end bidirectional combined buffering device, and belongs to the technical field of hydraulic cylinder buffering devices. Comprising a cylinder. An inner cavity is defined by the cylinder body, a piston is arranged in the inner cavity in a sliding mode, and the piston divides the inner cavity into a first cavity and a second cavity. A buffer hole is axially defined in the piston, and a first buffer assembly is arranged in the buffer hole in a floating and penetrating mode. The first buffering assembly comprises a buffering guide rod which is arranged in the buffering hole in a floating and penetrating mode, a curved sliding groove is defined by the buffering guide rod, a sealing block is arranged on the buffering guide rod, and the sealing block is located in the first cavity. The sealing block has a first position and a second position relative to the buffer hole, at the first position, the end face of the sealing block is in sealed connection with a port of the buffer hole to block the buffer hole, and the end, close to the second cavity, of the buffer guide rod protrudes out of the end face, located on the second cavity, of the piston. And at the second position, the sealing block is separated from the buffer hole, and the first cavity communicates with the second cavity through the curved sliding groove.

Description

Technical Field

[0001] This application relates to the technical field of hydraulic cylinder buffer devices, and particularly to an independent floating balance two-way combined buffer device for the end of the stroke of a hydraulic cylinder. Background Art

[0002] As an actuator of a hydraulic system, a hydraulic cylinder is used to convert fluid energy into kinetic energy, and has characteristics such as a simple transmission structure and flexible movement. It is widely used in fields with strict requirements for power control accuracy, such as construction machinery, automated production lines, and aerospace equipment. During the full-stroke movement of a hydraulic cylinder, the buffering performance at the end of the stroke directly determines the reliability, service life, and safety of the equipment operation.

[0003] In the related art, the buffer structure at the end of the stroke of a hydraulic cylinder generally uses a buffer sleeve or a buffer plunger, etc. These structures are generally relatively complex, have high requirements for the precision of parts, and have strict requirements for the matching precision with other parts, and the processing process is also relatively cumbersome. At the same time, the failure rate of the buffer plunger or buffer sleeve structure is relatively high, and it is easy for the plunger to be scratched or hit the bottom of the cylinder, causing structural damage, so that the buffering performance of the entire hydraulic cylinder cannot meet the requirements, and even the hydraulic cylinder itself is damaged and cannot be used continuously. In addition, these structures have poor applicability and are often difficult to apply to working conditions with relatively low telescopic frequencies or in hydraulic cylinders with relatively small cylinder diameters and rod diameters. Summary of the Invention

[0004] The purpose of this application is to provide an independent floating balance two-way combined buffer device for the end of the stroke of a hydraulic cylinder, which is used to solve the problems of high precision requirements and poor applicability of the hydraulic cylinder buffer structure in the prior art.

[0005] To solve the above technical problems, the following technical solutions are adopted in this application:

[0006] This application provides an independent floating balance two-way combined buffer device for the end of the stroke of a hydraulic cylinder, including: a cylinder body, the cylinder body defining an inner cavity;

[0007] a piston, the piston being slidably disposed in the inner cavity and separating the inner cavity into a first cavity and a second cavity, the piston defining a buffer hole;

[0008] The first buffer component includes a buffer guide rod that is floatingly disposed in the buffer hole. The buffer guide rod defines a curved chute. A sealing block is provided on the buffer guide rod, and the sealing block is located in the first chamber. The sealing block has a first position and a second position relative to the buffer hole. In the first position, the end face of the sealing block is sealingly connected to the port of the buffer hole to block the buffer hole, and the end of the buffer guide rod on the side close to the second chamber protrudes from the piston and is located on the end face on the second chamber side. In the second position, the sealing block is separated from the buffer hole, and the first chamber communicates with the second chamber through the curved chute.

[0009] In this solution, the first buffer component is used to achieve one-way secondary buffering of the hydraulic cylinder at the end of the stroke. Specifically, in response to the oil inlet in the first chamber, the piston moves towards the cylinder head on the second chamber side. At this time, under the action of the hydraulic oil pressure, the sealing block floats and moves to the first position. The end face of the sealing block is sealingly connected to the port of the buffer hole to block the buffer hole, and the first chamber is separated from the second chamber. At the same time, the end of the buffer guide rod on the side close to the second chamber protrudes from the piston and is located on the end face on the second chamber side, so that the buffer guide rod can contact the cylinder head relative to the piston first.

[0010] As the piston continues to move closer to the end of the stroke, the buffer guide rod contacts the cylinder head first. The pressure of the hydraulic oil is first transmitted to the cylinder head through the buffer guide rod. Compared with the piston directly impacting the cylinder head, the impact force is effectively reduced, thus achieving the first buffering. As the hydraulic oil pushes the piston to continue moving, the sealing block will be separated from the buffer hole, and the sealing connection state between the end face of the sealing slider and the port of the buffer hole is broken, opening the buffer hole. At this time, the sealing block reaches the second position relative to the buffer hole. In the second position, the hydraulic oil in the first chamber can enter the second chamber through the curved chute, and a back pressure is formed in the second chamber, generating resistance to the movement of the piston rod, thereby slowing down the piston movement speed and achieving secondary buffering.

[0011] In this solution, by changing the depth and angle of the curved chute, the flow rate and flow resistance of the hydraulic oil passing through the curved chute can be changed, thereby achieving different buffering effects. In addition, the buffer guide rod can achieve floating balance according to the hydraulic oil pressure difference between the first chamber and the second chamber during movement, change the relative position of the curved chute, and then change the size of the throttling to adjust the buffering effect.

[0012] Optionally, the buffer hole is a stepped hole, including a first hole section on the side of the second chamber and a second hole section on the side of the first chamber. The diameter of the second hole section is larger than that of the first hole section. A front guide is provided on the buffer guide rod, and the front guide is located in the second hole section.

[0013] Optionally, the sealing block has a third position relative to the buffer hole. In the third position, the sealing block is separated from the buffer hole, and the end face of the leading member is sealingly connected to the port of the first hole section to block the first hole section.

[0014] In this solution, a leading member is provided on the buffer guide rod. The buffer guide rod contacts the cylinder head through the leading member, thereby increasing the contact area with the cylinder head and reducing the impact damage at the contact part between the cylinder head and the buffer guide rod. In addition, the movement range of the buffer guide rod in the buffer hole can be limited by the leading member and the sealing block, preventing the buffer guide rod from moving out of the buffer hole. As the piston continues to move closer to the end of the stroke, the leading member first contacts the cylinder head. When the piston continues to move to the end of the stroke, the leading member can completely enter the second hole section, thus not affecting the stroke of the hydraulic cylinder.

[0015] In response to the oil inlet of the second chamber, the piston moves towards the cylinder head on the first chamber side. At this time, the leading member can move towards the first hole section under the action of the hydraulic oil pressure, and the end face of the leading member is sealingly connected to the port of the first hole section to block the first hole section, thereby separating the first chamber from the second chamber.

[0016] Optionally, the leading member is a round nut threadedly connected to the buffer guide rod, and the diameter of the round nut is larger than the first hole section and smaller than the second hole section.

[0017] In this solution, the leading member is a round nut, and the round nut is threadedly connected to the buffer guide rod. By adjusting the position of the leading nut on the buffer guide rod, the buffer guide rod can be adapted to pistons of different lengths.

[0018] Optionally, the buffer hole has a first sealing conical surface at the port on the first chamber side, and the sealing block has a second sealing conical surface. The first sealing conical surface can be fitted with the second sealing conical surface to form a sealing structure.

[0019] A first sealing conical surface is provided at the port on the first chamber side of the buffer hole, and a corresponding second sealing conical surface is provided on the sealing block. The conical surface contact has a larger contact area and better fit, ensuring the reliability of the seal. When the hydraulic oil enters the first chamber, the oil pressure will act on the sealing block. Under the action of the hydraulic oil pressure, the sealing block is subjected to a force towards the port of the buffer hole, pushing the second sealing conical surface to closely fit with the first sealing conical surface, effectively preventing the leakage of hydraulic oil between the first chamber and the second chamber.

[0020] Optionally, a piston rod is connected to the piston. The first chamber is the rodless chamber, and the second chamber is the rod chamber. The cylinder block includes a cylinder barrel, and a guide sleeve and a cylinder bottom that are hermetically connected to both sides of the cylinder barrel respectively. An assembly hole is defined in the guide sleeve to accommodate the piston rod. The cylinder bottom defines a first oil passage communicating with the rodless chamber, and the guide sleeve defines a second oil passage communicating with the rod chamber.

[0021] In this solution, the first chamber is the rodless chamber and the second chamber is the rod chamber. In response to the oil inlet of the first oil passage, the piston rod extends, and the piston moves towards the guide sleeve. The first buffer assembly can secondarily reduce the impact of the piston on the guide sleeve when the piston rod extends.

[0022] Optionally, a second buffer assembly is provided on one side of the piston rod located in the rodless chamber. The second buffer assembly includes: a guide rod axially arranged on one side of the piston rod located in the rodless chamber. A throttle slider is slidably sleeved on the guide rod. A spring is provided between the throttle slider and the piston rod. The first oil passage has a guide hole for accommodating the guide rod. The end face of the throttle slider can be hermetically connected to the port on the rodless chamber side of the guide hole. A throttle hole is provided on the throttle slider. When the throttle slider is connected to the guide hole, the hydraulic oil in the rodless chamber can enter the guide hole through the throttle hole.

[0023] In response to the oil inlet of the second oil passage, the piston rod retracts, and the piston moves towards the cylinder bottom. As the piston moves closer to the end of the stroke, the guide rod enters the guide hole, and the end face of the throttle slider contacts and forms a sealed connection with the port on the rodless chamber side of the guide hole. The hydraulic oil in the rodless chamber will enter the guide hole through the throttle hole and be discharged. Since the cross-sectional area of the oil inlet of the guide hole decreases, the discharge flow rate of the hydraulic oil will be throttled, causing the pressure in the rodless chamber to increase and form a back pressure. Thus, the acting force in the moving direction of the piston increases, and primary buffering is achieved. At the same time, as the piston continues to move, the guide rod gradually penetrates into the guide hole, and the throttle slider will compress the spring. Under the action of the spring force, the movement of the piston will slow down, achieving secondary buffering.

[0024] Optionally, a spring groove is axially defined in the piston rod. The guide rod is arranged in the spring groove and one end protrudes from the end face of the opening side of the spring groove. The spring groove can accommodate the throttle slider.

[0025] When the piston rod or the piston moves into contact with the cylinder bottom, the spring and the throttle slider can be completely received into the spring groove, thus having no impact on the stroke of the hydraulic cylinder.

[0026] Compared with the prior art, the beneficial effects achieved by this application are as follows: In this application, in response to the oil inlet of the first chamber, the piston moves towards the cylinder head on the side of the second chamber. At this time, the sealing block moves to the first position under the action of the hydraulic oil pressure, isolating the first chamber from the second chamber. As the piston continues to move closer to the end of the stroke, the buffer guide rod first comes into contact with the cylinder head, and the pressure of the hydraulic oil is first transmitted to the cylinder head through the buffer guide rod. Compared with the piston directly impacting the cylinder head, the impact force is effectively reduced, thus achieving the first buffering. As the hydraulic oil pushes the piston to continue moving, the sealing block reaches the second position relative to the buffer hole, and the hydraulic oil in the first chamber can enter the second chamber through the curved chute, forming a back pressure in the second chamber, generating resistance to the movement of the piston rod, thereby slowing down the movement speed of the piston and achieving secondary buffering.

[0027] This application ensures the stability and reliability of the buffering at the extreme displacement state at the end of the stroke of the hydraulic cylinder through two-stage buffering, prevents the piston from colliding violently with the cylinder head and causing damage, and can be applied to various buffering requirements of hydraulic cylinders. By changing the depth and angle of the curved chute, the flow rate and flow resistance of the hydraulic oil passing through the curved chute can be changed, thereby achieving different buffering effects. Different from the commonly used buffer sleeve or buffer plunger structures on the market, the structure of this application is simple, the requirement for the fitting accuracy of parts is relatively low, the requirement for the machining precision of parts is not high, and the machining difficulty is greatly reduced. Description of the Drawings

[0028] In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present disclosure. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0029] Figure 1 It is a schematic diagram of the overall structure of some embodiments provided by this application;

[0030] Figure 2 It is an enlarged schematic diagram of the first buffer assembly of some embodiments provided by this application;

[0031] Figure 3 It is a schematic diagram of the buffer hole structure of some embodiments provided by this application;

[0032] Figure 4 It is a schematic diagram of the cylinder block structure of some embodiments provided by this application;

[0033] Figure 5 It is a schematic diagram of the second buffer assembly structure of some embodiments provided by this application.

[0034] Description of the reference numerals: 1 - cylinder block; 2 - piston; 3 - first buffer assembly; 4 - second buffer assembly; 5 - piston rod; 11 - first chamber; 12 - second chamber; 13 - cylinder barrel; 14 - guide sleeve; 15 - cylinder bottom; 16 - first oil passage; 17 - second oil passage; 161 - guide hole; 1611 - third sealing conical surface; 21 - buffer hole; 211 - first hole section; 212 - second hole section; 213 - first sealing conical surface; 31 - buffer guide rod; 32 - sealing block; 33 - front guide; 311 - curved chute; 321 - second sealing conical surface; 41 - guide rod; 42 - spring; 43 - throttle slider; 44 - limiting part; 431 - throttle hole; 432 - fourth sealing conical surface; 51 - spring groove. Detailed implementation manners

[0035] Next, the technical solutions in the embodiments of the present application will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only a part of the embodiments of the present disclosure / the present application, rather than all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and in no way constitutes a limitation on the present application and its application or use.

[0036] Embodiment 1

[0037] This embodiment introduces a two-way combined buffer device for the end of the independent floating balance stroke of a hydraulic cylinder. Refer to Figure 1 and Figure 2 , the two-way combined buffer device for the end of the independent floating balance stroke of the hydraulic cylinder in this embodiment includes a cylinder block 1. The cylinder block 1 defines an inner cavity, and a piston 2 is slidably arranged in the inner cavity. The piston 2 divides the inner cavity into a first chamber 11 and a second chamber 12. A buffer hole 21 is axially defined on the piston 2, and a first buffer assembly 3 is floatingly inserted into the buffer hole 21. Through the first buffer assembly 3, one-way secondary buffering of the hydraulic cylinder at the end of the stroke can be achieved.

[0038] Specifically, the first buffer assembly 3 includes a buffer guide rod 31 floatingly inserted into the buffer hole 21. The buffer guide rod 31 defines a curved chute 311. A sealing block 32 is arranged on the buffer guide rod 31, and the sealing block 32 is located in the first chamber 11. The sealing block 32 has a first position and a second position relative to the buffer hole 21. In the first position, the end face of the sealing block 32 is sealingly connected to the port of the buffer hole 21 to block the buffer hole 21, and the end of the buffer guide rod 31 close to the second chamber 12 protrudes from the end face of the piston 2 on the side of the second chamber 12. In the second position, the sealing block 32 is separated from the buffer hole 21, and the first chamber 11 is communicated with the second chamber 12 through the curved chute 311.

[0039] In response to the oil inlet of the first chamber 11, the piston 2 moves towards the cylinder head on the side of the second chamber 12. At this time, under the action of the hydraulic oil pressure, the sealing block 32 floats and moves to the first position, and the end face of the sealing block 32 is hermetically connected to the port of the buffer hole 21, blocking the buffer hole 21, and isolating the first chamber 11 from the second chamber 12. At the same time, the end of the buffer guide rod 31 on the side close to the second chamber 12 protrudes from the end face of the piston 2 on the side of the second chamber 12, so that the buffer guide rod 31 can contact the cylinder head first relative to the piston 2. As the piston 2 continues to move closer to the end of the stroke, the buffer guide rod 31 first contacts the cylinder head, and the pressure of the hydraulic oil is first transmitted to the cylinder head through the buffer guide rod 31. Compared with the piston 2 directly impacting the cylinder head, the impact force is effectively reduced, thus realizing the first buffering. As the hydraulic oil pushes the piston 2 to continue moving, the sealing block 32 will separate from the buffer hole 21, and the sealed connection state between the end face of the sealing slider and the port of the buffer hole 21 is broken, opening the buffer hole 21. At this time, the sealing block 32 reaches the second position relative to the buffer hole 21. At the second position, the hydraulic oil in the first chamber 11 can enter the second chamber 12 through the curved chute 311, and a back pressure is formed in the second chamber 12, generating resistance to the movement of the piston rod 5, thereby slowing down the movement speed of the piston 2 and realizing secondary buffering.

[0040] In this embodiment, by changing the depth and angle of the curved chute 311, the flow rate and flow resistance of the hydraulic oil passing through the curved chute 311 can be changed, thereby realizing different buffering effects. For example, increasing the depth of the curved chute 311 can increase the passing flow rate of the hydraulic oil, making the formation of the back pressure relatively slow and the buffering process relatively gentle; conversely, decreasing the depth of the curved chute 311 can decrease the passing flow rate of the hydraulic oil, making the formation of the back pressure relatively fast and the buffering process relatively rapid. In addition, the buffer guide rod 31 can achieve floating balance according to the hydraulic oil pressure difference between the first chamber 11 and the second chamber 12 during movement, change the relative position of the curved chute 311, and then change the size of the throttling to adjust the buffering effect.

[0041] In this embodiment, the buffer hole 21 has a first sealing conical surface 213 at the port on the side of the first chamber 11, and the sealing block 32 has a second sealing conical surface 321. The first sealing conical surface 213 can fit with the second sealing conical surface 321 to form a sealing structure. The conical surface contact has a larger contact area and better fit, ensuring the reliability of the seal. When the hydraulic oil enters the first chamber 11, the oil pressure will act on the sealing block 32. Under the action of the hydraulic oil pressure, the sealing block 32 receives a force towards the port of the buffer hole 21, pushing the second sealing conical surface 321 to closely fit with the first sealing conical surface 213, effectively preventing the leakage of the hydraulic oil between the first chamber 11 and the second chamber 12.

[0042] Embodiment 2:

[0043] Based on the same inventive concept as Embodiment 1, refer to Figures 1 to 3, in this embodiment, the buffer hole 21 is a stepped hole, including a first hole section 211 on one side of the second chamber 12 and a second hole section 212 on one side of the first chamber 11. Among them, the diameter of the second hole section 212 is larger than that of the first hole section 211. Further, a front guide 33 is provided on the buffer guide rod 31, and the front guide 33 is located in the second hole section 212. The buffer guide rod 31 contacts the cylinder head through the front guide 33, thereby increasing the contact area with the cylinder head and reducing the impact damage at the contact part between the cylinder head and the buffer guide rod 31. In addition, the movement range of the buffer guide rod 31 in the buffer hole 21 can be limited by the front guide 33 and the sealing block 32, preventing the buffer guide rod 31 from moving out of the buffer hole 21. In this embodiment, the front guide 33 is a round nut threadedly connected to the buffer guide rod 31, and the diameter of the round nut is larger than that of the first hole section 211 and smaller than that of the second hole section 212. By adjusting the position of the front guide nut on the buffer guide rod 31, the buffer guide rod 31 can be adapted to pistons 2 of different lengths. As the piston 2 continues to move closer to the end of the stroke, the round nut can come into contact with the cylinder head first. When the piston 2 continues to move to the end of the stroke, the round nut can completely enter the second hole section 212, thus not affecting the stroke of the hydraulic cylinder.

[0044] Further, in response to the second chamber 12 being filled with oil, the piston 2 moves towards the cylinder head on the side of the first chamber 11. The sealing block 32 has a third position relative to the buffer hole 21. In the third position, the sealing block 32 is separated from the buffer hole 21. At this time, the front guide 33 can move towards the first hole section 211 under the action of the hydraulic oil pressure, and the end face of the front guide 33 is sealingly connected to the port of the first hole section 211 to block the first hole section 211, thereby separating the first chamber 11 from the second chamber 12.

[0045] Embodiment Three:

[0046] Based on the same inventive concept as Embodiment One, referring to Figure 1 , Figure 4 and Figure 5 , in this embodiment, a piston rod 5 is inserted through the piston 2. The first chamber 11 is a rodless chamber, and the second chamber 12 is a rod chamber. The cylinder block 1 includes a cylinder barrel 13 and a guide sleeve 14 and a cylinder bottom 15 that are respectively sealingly connected to both sides of the cylinder barrel 13. An assembly hole is defined on the guide sleeve 14 to accommodate the piston rod 5. The cylinder bottom 15 defines a first oil passage 16 communicating with the rodless chamber, and the guide sleeve 14 defines a second oil passage 17 communicating with the rod chamber. In response to the first oil passage 16 being filled with oil, the piston rod 5 extends, and the piston 2 moves towards the guide sleeve 14. The first buffer assembly 3 is used to prevent the piston 2 from causing a high-speed impact on the guide sleeve 14 when the piston rod 5 extends.

[0047] In this embodiment, when the piston rod 5 retracts, the piston 2 or the piston rod 5 impacts the guide sleeve 14 at a high speed through the second buffer assembly 4. Specifically, a spring groove 42 is axially defined on the side of the piston rod 5 located in the rodless cavity. The second buffer assembly 4 includes a guide rod 41 disposed in the spring groove 42, and one end of the guide rod 41 protrudes from the end face of the opening side of the spring groove 42.

[0048] Furthermore, a throttle slider 43 is slidably sleeved on the guide rod 41, and the end of the guide rod 41 has a limiting portion 44 for restricting the sliding of the throttle slider 43. A spring 42 is provided between the throttle slider 43 and the piston rod 5. The first oil passage 16 has a guide hole 161 for accommodating the guide rod 41. The end face of the throttle slider 43 can be hermetically connected to the port of the guide hole 161 on the side of the rodless cavity. Further, a throttle hole 431 is provided on the throttle slider 43. When the throttle slider 43 is connected to the guide hole 161, the hydraulic oil in the rodless cavity can enter the guide hole 161 through the throttle hole 431.

[0049] In response to the oil inlet of the second oil passage 17, the piston rod 5 retracts, and the piston 2 moves towards the bottom 15 of the cylinder. As the piston 2 moves closer to the end of the stroke, the guide rod 41 enters the guide hole 161, and the end face of the throttle slider 43 contacts the port of the guide hole 161 on the side of the rodless cavity to form a sealed connection. The hydraulic oil in the rodless cavity will enter the guide hole 161 through the throttle hole 431 and be discharged. Since the cross-sectional area of the oil inlet of the guide hole 161 decreases, the discharge flow rate of the hydraulic oil will be throttled, causing the pressure in the rodless cavity to increase and form a back pressure. Thus, the directional force acting in the moving direction of the piston 2 increases, and a primary buffer is achieved. At the same time, as the piston 2 continues to move, the guide rod 41 gradually penetrates into the guide hole 161, and the throttle slider 43 will compress the spring 42. Under the elastic force of the spring 42, the movement of the piston 2 will slow down, achieving a secondary buffer. When the piston rod 5 or the piston 2 moves to contact the bottom 15 of the cylinder, the spring 42 and the throttle slider 43 can be completely received into the spring groove 42, so as not to affect the stroke of the hydraulic cylinder.

[0050] In this embodiment, the port of the guide hole 161 on the side of the rodless cavity has a third sealing cone surface 1611, and the throttle slider 43 has a fourth sealing cone surface 432. The third sealing cone surface 1611 can be fitted with the fourth sealing cone surface 432 to form a sealing structure.

[0051] The above are only the preferred embodiments of the present application. It should be noted that for those of ordinary skill in the art, without departing from the technical principles of the present disclosure / the present application, several improvements and deformations can still be made, and these improvements and deformations should also be regarded as the protection scope of the present disclosure / the present application.

Claims

1. A two-way combined buffer device for the independent floating balance of the end stroke of a hydraulic cylinder, characterized in that, Comprising: A cylinder block (1), the cylinder block (1) defining an inner cavity; A piston (2), the piston (2) being slidably disposed in the inner cavity and dividing the inner cavity into a first chamber (11) and a second chamber (12), the piston (2) defining a buffer hole (21); A first buffer assembly (3), including a buffer guide rod (31) floatingly disposed in the buffer hole (21), the buffer guide rod (31) defining a curved chute (311), a sealing block (32) being disposed on the buffer guide rod (31), the sealing block (32) being located in the first chamber (11); the sealing block (32) has a first position and a second position relative to the buffer hole (21), in the first position, the end face of the sealing block (32) is sealingly connected to the port of the buffer hole (21) to block the buffer hole (21), and the end of the buffer guide rod (31) close to the second chamber (12) protrudes from the piston (2) and is located on the end face of the second chamber (12) side; in the second position, the sealing block (32) is separated from the buffer hole (21), and the first chamber (11) communicates with the second chamber (12) through the curved chute (311).

2. The bidirectional combined buffer device for the independent floating balance of the hydraulic cylinder at the end of the stroke according to claim 1, characterized in that, The buffer hole (21) is a stepped hole, including a first hole section (211) on the side of the second chamber (12) and a second hole section (212) on the side of the first chamber (11), the diameter of the second hole section (212) being larger than the diameter of the first hole section (211), and a leading member (33) being disposed on the buffer guide rod (31), the leading member (33) being located in the second hole section (212).

3. The two-way combined buffer device for the independent floating balance of the hydraulic cylinder at the end of the stroke according to claim 2, characterized in that, The sealing block (32) has a third position relative to the buffer hole (21), in the third position, the sealing block (32) is separated from the buffer hole (21), and the end face of the leading member (33) is sealingly connected to the port of the first hole section (211) to block the first hole section (211).

4. The two-way combined buffer device for the independent floating balance of the hydraulic cylinder at the end of the stroke according to claim 2, characterized in that, The leading member (33) is a round nut threadedly connected to the buffer guide rod (31), the diameter of the round nut being larger than the first hole section (211) and smaller than the second hole section (212).

5. The two-way combined buffer device for the independent floating balance of the hydraulic cylinder at the end of the stroke according to claim 1, characterized in that, The port of the buffer hole (21) on the side of the first chamber (11) has a first sealing cone surface (213), and the sealing block (32) has a second sealing cone surface (321), and the first sealing cone surface (213) can be fitted with the second sealing cone surface (321) to form a sealing structure.

6. The double-direction combined buffer device for the independent floating balance of the hydraulic cylinder at the end of the stroke according to claim 1, characterized in that, A piston rod (5) is disposed through the piston (2), the first chamber (11) is a rodless chamber, the second chamber (12) is a rod chamber, the cylinder block (1) includes a cylinder barrel (13) and a guide sleeve (14) and a cylinder bottom (15) respectively sealingly connected to both sides of the cylinder barrel (13), the guide sleeve (14) defining a fitting hole to accommodate the piston rod (5), the cylinder bottom (15) defining a first oil passage (16) communicating with the rodless chamber, and the guide sleeve (14) defining a second oil passage (17) communicating with the rod chamber.

7. The two-way combined buffer device for the independent floating balance of the hydraulic cylinder at the end of the stroke according to claim 6, characterized in that, A second buffer assembly (4) is provided on one side of the piston rod (5) located in the rodless cavity. The second buffer assembly (4) includes: a guide rod (41) axially arranged on one side of the piston rod (5) located in the rodless cavity. A throttle slider (43) is slidably sleeved on the guide rod (41). A spring (42) is provided between the throttle slider (43) and the piston rod (5). The first oil passage (16) has a guide hole (161) for accommodating the guide rod (41). The end face of the throttle slider (43) can be sealingly connected to the port on the side of the rodless cavity of the guide hole (161). A throttle hole (431) is provided on the throttle slider (43). When the throttle slider (43) is connected to the guide hole (161), the hydraulic oil in the rodless cavity can enter the guide hole (161) through the throttle hole (431).

8. The independent floating balance two-way combined buffer device for the end of the hydraulic cylinder stroke according to claim 7, wherein, A spring groove (51) is axially defined in the piston rod (5). The guide rod (41) is arranged in the spring groove (51) and one end protrudes from the end face of the opening side of the spring groove (51). The spring groove (51) can accommodate the throttle slider (43).

9. The two-way combined buffer device for the independent floating balance of the hydraulic cylinder at the end of the stroke according to claim 6, characterized in that, One end of the guide rod (41) has a limiting portion (44), and the limiting portion (44) is used to limit the sliding of the throttle slider (43).

10. The independent floating balance two-way combined buffer device for the end of the hydraulic cylinder stroke according to claim 6, characterized in that, The port on the side of the rodless cavity of the guide hole (161) has a third sealing cone surface (1611). The throttle slider (43) has a fourth sealing cone surface (432). The third sealing cone surface (1611) can be fitted with the fourth sealing cone surface (432) to form a sealing structure.

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