CN214063439U - Hydraulic cylinder and stacking machine - Google Patents
Hydraulic cylinder and stacking machine Download PDFInfo
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- CN214063439U CN214063439U CN202022730472.6U CN202022730472U CN214063439U CN 214063439 U CN214063439 U CN 214063439U CN 202022730472 U CN202022730472 U CN 202022730472U CN 214063439 U CN214063439 U CN 214063439U
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Abstract
The utility model relates to a pneumatic cylinder technical field, concretely relates to pneumatic cylinder and heap high machine. The hydraulic cylinder of the utility model comprises a cylinder barrel, a first piston rod, a first piston and a second piston, wherein the first piston is connected with the first piston rod, the cylinder barrel is divided into a first cavity and a second cavity by the first piston, and the first cavity is suitable for being communicated with a power element; the piston cavity is formed in the first piston rod, the second piston divides the piston cavity into a third cavity and a fourth cavity, the second piston can slide relative to the piston cavity, the third cavity is communicated with the first cavity, and the fourth cavity is provided with a first overflowing hole. Therefore, the effective action area of the first piston rod and the first piston is reduced, the pressure of the hydraulic cylinder is increased, the flow is reduced, and the instability phenomenon near the stroke end is relieved. And the outer diameter of the first piston rod is not reduced due to the reduction of the effective acting area, and the instability phenomenon of the hydraulic cylinder at the end part close to the stroke is not intensified.
Description
Technical Field
The utility model relates to a pneumatic cylinder technical field particularly, relates to a pneumatic cylinder and pile high machine.
Background
In the prior art, for a long-stroke lifting hydraulic cylinder, generally, the flow reduction and pressurization can be realized by reducing the diameter of a piston rod, but after the diameter of the piston rod is reduced, the lifting hydraulic cylinder is easy to be unstable at a position close to the stroke terminal.
SUMMERY OF THE UTILITY MODEL
The utility model provides a problem realize the pressure boost that subtracts of pneumatic cylinder under the prerequisite of the diameter of how guaranteeing the piston rod.
In order to solve the above problems, the present invention provides a hydraulic cylinder, including a cylinder barrel, a first piston rod, a first piston and a second piston, wherein the first piston is connected to the first piston rod, the cylinder barrel is divided into a first chamber and a second chamber by the first piston, and the first chamber is suitable for being communicated with a power element; the piston cavity is formed in the first piston rod, the second piston divides the piston cavity into a third cavity and a fourth cavity, the second piston can slide relative to the piston cavity, the third cavity is communicated with the first cavity, and a first overflowing hole is formed in the fourth cavity.
Therefore, when the pump pumps liquid into the first chamber, the liquid can push the first piston to move towards one side of the second chamber, and the liquid in the first chamber can flow into the third chamber of the first piston rod, so that the relative movement of the first piston rod and the second piston is realized; when the pump pumps the liquid out of the first chamber, the first piston moves to the first chamber side, and the liquid in the third chamber can also flow into the first chamber. Through inciting somebody to action first piston rod sets up to cavity structures, realized right first piston rod with the great reduction of the effective active area of first piston, thereby make the pressure of pneumatic cylinder grow by a wide margin, the flow diminishes by a wide margin for the unstability phenomenon near stroke end department is slowed down. However, the outer diameter of the first piston rod is not reduced by the reduction of the effective acting area, and the instability of the hydraulic cylinder near the stroke end is not so much aggravated.
Optionally, the piston further comprises a second piston rod, a through hole is formed in the first piston, the second piston rod is arranged in the through hole in a penetrating manner, and the first piston can slide relative to the second piston rod; and two ends of the second piston rod are respectively connected with the second piston and the cylinder barrel.
Therefore, the two ends of the second piston rod are respectively connected with the second piston and the cylinder barrel, the overall stability of the hydraulic cylinder can be improved, and the second piston is prevented from moving in the piston cavity in an unordered mode. The second piston may remain stationary as the first piston rod moves to the side of the second chamber, the first piston rod may move relative to the second piston, and the second piston rod may also guide the movement of the first piston rod.
Optionally, an end face of the second piston near one axial end of the second chamber is flush with an end face of one axial end of the cylinder.
Therefore, the stop of the first piston rod caused by the excessively high end surface of one end, close to the second chamber, of the second piston can be avoided, and the first piston rod cannot be completely reset.
Optionally, the first piston is provided with a second overflowing hole, and the second overflowing hole is suitable for communicating the first chamber with the second chamber.
Therefore, through the arrangement of the second overflowing hole, the fluid in the first chamber can flow into the second chamber, and the first piston rod can be prevented from retracting too fast.
Optionally, a third overflowing hole is formed in the third chamber, and the third overflowing hole is suitable for communicating the second chamber with the third chamber.
Thereby, through the setting of the third overflowing hole, the indirect communication between the first chamber and the third chamber is realized, so that the liquid in the first chamber and the liquid in the third chamber can be communicated.
Optionally, the cylinder further comprises a first sealing ring, the first sealing ring is sleeved on the circumferential outer surface of the first piston, and the first sealing ring is suitable for sealing between the first piston and the cylinder barrel.
Therefore, the first sealing ring is arranged to seal the space between the first piston and the cylinder barrel, and the first chamber and the second chamber are prevented from leaking at the joint of the first piston and the cylinder barrel.
Optionally, a first accommodating groove is formed in the circumferential surface of the first piston, and at least part of the first sealing ring is accommodated in the first accommodating groove.
Therefore, the first seal ring is axially positioned by the arrangement of the first accommodating groove, so that the first seal ring can be prevented from being loosened from the first piston.
Optionally, the piston further comprises a second sealing ring, the second sealing ring is sleeved on the circumferential outer surface of the second piston, and the second sealing ring is suitable for sealing between the second piston and the piston cavity.
Therefore, the second piston and the first piston rod are sealed through the arrangement of the second sealing ring, and the third chamber and the fourth chamber are prevented from leaking at the joint of the second piston and the first piston rod.
Optionally, a second accommodating groove is formed in the circumferential surface of the second piston, and at least part of the second sealing ring is accommodated in the second accommodating groove.
Therefore, the second seal ring is axially positioned by the second accommodating groove, so that the second seal ring can be prevented from loosening from the second piston.
The utility model also provides a pile high machine, include as above-mentioned arbitrary pneumatic cylinder. Compared with the prior art, the fork lift truck with the beneficial effect of pneumatic cylinder is the same, no longer gives unnecessary details here.
Drawings
Fig. 1 is a cross-sectional view of a hydraulic cylinder with a first piston rod retracted in an embodiment of the invention;
fig. 2 is a cross-sectional view of the hydraulic cylinder with the first piston rod extended in an embodiment of the present invention;
fig. 3 is a partial enlarged view of a portion a in fig. 2 according to the present invention;
fig. 4 is a partial enlarged view of the utility model at the point B in fig. 2;
fig. 5 is a partial enlarged view of the point C in fig. 2 according to the present invention.
Description of reference numerals:
1-a second piston rod, 2-a second piston, 3-a cylinder barrel, 4-a first piston rod, 5-a first piston, 6-a first sealing ring, 7-a second sealing ring, 21-a second containing groove, 31-a first chamber, 32-a second chamber, 41-a third chamber, 42-a fourth chamber, 43-a third overflowing hole, 311-a fourth overflowing hole, 421-a first overflowing hole, 51-a second overflowing hole, 52-a first containing groove and 53-a through hole.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention more comprehensible, embodiments accompanied with figures are described in detail below.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted", "connected" and "disposed" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; may be directly connected or indirectly connected through an intermediate. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the description herein, references to the description of the terms "an example," "one example," and "one implementation," etc., mean that a particular feature, structure, material, or characteristic described in connection with the example or implementation is included in at least one example or implementation of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or implementation. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or implementations.
In this embodiment, the hydraulic cylinder is a plunger cylinder, and assuming that the movement speed of the plunger cylinder is V and the load is F, the plunger cylinder pressure is P1 ═ F/S1, where S1 is the effective acting area of the first piston rod 4 and the first piston 5, the plunger cylinder flow rate is Q1 ═ S1 ═ V, and when S1 decreases, the plunger cylinder flow rate decreases and the plunger cylinder pressure increases; when S1 is increased, the flow rate of the plunger cylinder is increased, and the pressure of the plunger cylinder is decreased.
The utility model provides a hydraulic cylinder, as shown in fig. 1 and fig. 2, including cylinder 3, first piston rod 4, first piston 5 and second piston 2, first piston 5 with first piston rod 4 is connected, first piston 5 divides cylinder 3 into first cavity 31 and second cavity 32, first cavity 31 is suitable for and communicates with power component; the first piston rod 4 is internally provided with a piston cavity, the second piston 2 divides the piston cavity into a third cavity 41 and a fourth cavity 42, the second piston 2 can slide relative to the piston cavity, the third cavity 41 is communicated with the first cavity 31, and the fourth cavity 42 is provided with a first overflowing hole 421.
It should be noted that fig. 1 is a cross-sectional view of a longitudinal section at the axis of the first piston rod 4, which is a schematic diagram of the hydraulic cylinder when the first piston rod 4 is retracted; fig. 2 is a cross-sectional view of a longitudinal section at the axis of the first piston rod 4, which is a schematic view of the hydraulic cylinder when the first piston rod 4 is extended. The cylinder barrel 3 may be cylindrical, the piston cavity and the cylinder barrel 3 are coaxial, and the third cavity 41 is a cavity in the piston cavity, the cavity being close to one side of the first piston 5. The first piston rod 4 may also be a cylindrical structure, where the piston cavity is in contact with a surface of one axial end of the first piston 5, that is, the first piston 5 and the first piston rod 4 surround to form the piston cavity.
The first piston 5 and the first piston rod 4 are coaxial, a through hole is formed in one axial end of the cylinder barrel 3, the first piston rod 4 penetrates through the through hole, the diameter of the first piston rod 4 is the same as that of the through hole, and the first piston rod 4 can slide relative to the through hole. Here, the diameter of the through hole is the same as that of the first piston rod 4, which means the size of the through hole after dimensional tolerance is removed, and the diameter of the through hole is actually slightly larger than that of the first piston rod 4. The friction between the through hole and the first piston rod 4 can be reduced by smearing lubricating oil, and meanwhile, the sealing performance can be enhanced. In addition, a sealing ring may be additionally disposed between the through hole and the first piston rod 4 to seal the through hole and the first piston rod 4.
One end of the first piston rod 4 is connected with the first piston 5, and the other end extends out of the cylinder 3. When the first piston rod 4 moves towards the first chamber 31 relative to the second piston 2, the volume of the fourth chamber 42 decreases, the first overflowing hole 421 is communicated with the external environment, the first overflowing hole 421 can discharge the fluid in the fourth chamber 42, and the fluid in the fourth chamber 42 can be gas. When the first piston rod 4 moves towards the second chamber 32 relative to the second piston 2, the volume of the fourth chamber 42 is increased, and the first overflowing hole 421 can introduce fluid outside the hydraulic cylinder into the fourth chamber 42, so that the fourth chamber 42 is prevented from being blocked by vacuumizing to move the first piston 5. Here, the first overflowing hole 421 may be opened at one end of the first piston rod 4 in the axial direction, so as to avoid an influence on the stroke of the second piston 2. The first overflowing hole 421 may be an inlet or an outlet of the fluid.
The power element may be a pump by which liquid is pumped into the first chamber 31 or by which liquid is pumped out of the first chamber 31. Specifically, a fourth overflowing hole 311 is formed in the first chamber 31, and the outlet of the pump is communicated with the first chamber 31 through the fourth overflowing hole 311. Here, the fourth overflowing hole 311 may be an oil inlet or an oil outlet.
The first piston 5 is connected to the first piston rod 4, in one embodiment, an external thread is formed on the first piston rod 4, a threaded hole is formed in the first piston 5, and the first piston 5 and the first piston rod 4 can be connected through a threaded connection. Meanwhile, in order to avoid the looseness between the first piston rod 4 and the first piston 5, retaining washers may be provided at both axial ends of the first piston 5. In one embodiment, the first piston 5 and the first piston rod 4 may be connected by a snap key. In one embodiment, the first piston 5 and the first piston rod 4 may be connected by welding. In one embodiment, the first piston 5 is screwed to the first piston rod 4, and the first piston 5 is welded to the screwed portion of the first piston rod 4, so that the coaxiality of the first piston 5 and the first piston rod 4 can be ensured.
The third chamber 41 communicates with the first chamber 31. In one embodiment, the third chamber 41 may be in direct communication with the first chamber 31, for example, a damping hole may be formed in the first piston 5, and the communication between the third chamber 41 and the first chamber 31 is realized through the damping hole. In one embodiment, the third chamber 41 and the first chamber 31 may be indirectly communicated, that is, a transition chamber structure may be disposed between the third chamber 41 and the first chamber 31, and the third chamber 41 and the first chamber 31 are respectively communicated with the transition chamber structure, so that the third chamber 41 and the first chamber 31 are communicated.
This has the advantage that when the pump pumps fluid into the first chamber 31, the fluid can push the first piston 5 to move towards the second chamber 32, and the fluid in the first chamber 31 can flow towards the third chamber 41 of the first piston rod 4, so as to realize the relative movement of the first piston rod 4 and the second piston 2; when the pump pumps the liquid out of the first chamber 31, the first piston 5 moves to the first chamber 31 side, and the liquid in the third chamber 41 can also flow into the first chamber 31. Through inciting somebody to action first piston rod 4 sets up to cavity structures, realized right first piston rod 4 with the great reduction of effective active area of first piston 5, thereby make the pressure of pneumatic cylinder grow by a wide margin, the flow diminishes by a wide margin for the unstability phenomenon near stroke end department is slowed down. However, the outer diameter of the first piston rod 4 is not reduced by the reduction of the effective acting area, and the instability of the hydraulic cylinder near the end of the stroke is not so much aggravated.
As shown in fig. 1 to 5, the hydraulic cylinder further includes a second piston rod 1, a through hole 53 is formed in the first piston 5, the diameter of the through hole 53 is the same as that of the second piston rod 1, the second piston rod 1 is inserted into the through hole 53, and the first piston 5 can slide relative to the second piston rod 1; and two ends of the second piston rod 1 are respectively connected with the second piston 2 and the cylinder barrel 3.
It should be noted that the second piston rod 1 and the first piston rod 4 are coaxial, the other end of the second piston rod 1 is connected to one axial end of the cylinder 3, and the second piston rod 1 is connected to the inner side wall of the first chamber 31 of the cylinder 3. The diameter of the through hole 53 is the same as that of the second piston rod 1, which means the dimension of the through hole 53 and the second piston rod 1 after dimensional tolerance is taken out, and the diameter of the through hole 53 is actually slightly larger than that of the second piston rod 1. The friction between the through hole 53 and the second piston rod 1 can be reduced by applying lubricating oil, and the sealing performance can be enhanced. In addition, a seal ring may be additionally provided between the through hole 53 and the second piston rod 1 to seal the through hole 53 and the second piston rod 1.
One end of the second piston rod 1 is connected with the second piston 2. In one embodiment, the second piston rod 1 is provided with an external thread, the second piston 2 is provided with a threaded hole, and the second piston 2 and the second piston rod 1 can be connected through a threaded connection. Meanwhile, in order to avoid the second piston rod 1 and the second piston 2 from loosening, retaining washers may be disposed at two axial ends of the second piston 2. In one embodiment, the second piston 2 and the second piston rod 1 may be connected by a snap key. In one embodiment, the second piston 2 and the second piston rod 1 may be connected by welding. In one embodiment, the second piston 2 is screwed to the second piston rod 1, and the second piston 2 is welded to the second piston rod 1 at the screwed position, so that the coaxiality of the second piston 2 and the second piston rod 1 can be ensured.
The second piston rod 1 is connected with the cylinder 3. In one embodiment, the second piston rod 1 is provided with an external thread, the cylinder 3 is provided with a threaded hole, and the second piston 2 and the cylinder 3 can be connected through threaded connection. Meanwhile, in order to avoid the loosening between the cylinder 3 and the second piston 2, retaining washers may be provided at both axial ends of the cylinder 3. In one embodiment, the second piston 2 and the cylinder 3 may be connected by a snap-in key. In one embodiment, the second piston 2 and the cylinder 3 may be connected by welding. In one embodiment, the second piston 2 is screwed into the cylinder 3 and welded at the screwed position of the second piston 2 and the cylinder 3, so that the coaxiality of the second piston 2 and the cylinder 3 can be ensured.
The advantage that sets up like this is that through 1 both ends of second piston rod respectively with second piston 2 with cylinder 3 is connected, can improve the holistic stability of pneumatic cylinder, avoid second piston 2 in unordered motion in the piston chamber. When the first piston rod 4 moves towards the side of the second chamber 32, the second piston 2 can remain stationary, the first piston rod 4 can move relative to the second piston 2, and the second piston rod 1 can also guide the movement of the first piston rod 4.
When the end of the second piston 2 close to the second chamber 32 is higher than the outer end face of the axial end of the cylinder 3, the first piston rod 4 cannot be effectively reset due to the stop of the second piston 2. As shown in fig. 1 and 2, one axial end of the second piston 2 close to the second chamber 32 is flush with the outer end face of one axial end of the cylinder 3, and the inner surface of the other axial end of the cylinder 3 is connected to the second piston rod 1. Thus, it is avoided that the end surface of the second piston 2 near the end of the second chamber 32 is too high to form a stop for the first piston rod 4, thereby avoiding that the first piston rod 4 cannot be completely reset.
When the end of the second piston 2 close to the first chamber 31 is lower than the inner end face of the axial end of the cylinder 3, the first piston rod 4 will cause the effective stroke to be shortened due to the stop of the second piston 2. As shown in fig. 1 and 2, a distance between an axial end surface of the second piston 2 close to the first chamber 31 and an inner end surface of one axial end of the cylinder 3 is 5-25mm, and an inner surface of the other axial end of the cylinder 3 is connected to the second piston rod 1. Therefore, the end surface of the end of the second piston 2 close to the first chamber 31 is made to be as close as possible to the inner end surface of the axial end of the cylinder 3, so that the stop of the first piston rod 4 due to the excessively low end surface of the end of the second piston 2 close to the first chamber 31 can be reduced, and the influence on the shortening of the effective stroke of the first piston rod 4 is reduced.
As shown in fig. 1 to 3, the first piston 5 is provided with a second overflowing hole 51, and the second overflowing hole 51 is suitable for communicating the first chamber 31 with the second chamber 32.
It should be noted that the second overflowing hole 51 may be a damping hole, the axial line of the second overflowing hole 51 is parallel to the axial line of the first piston 5, and the diameter of the second overflowing hole 51 may be between 0.2mm and 2.5mm, so as to prevent the damping hole from being too large and increasing the pressure loss. When the first piston rod 4 moves towards the first chamber 31 relative to the second piston 2, the volume of the first chamber 31 is reduced, the volume of the second chamber 32 is increased, and the liquid in the first chamber 31 flows into the second chamber 32 through the second overflowing hole 51; when the first piston rod 4 moves towards the second chamber 32 relative to the second piston 2, the volume of the second chamber 32 is reduced, the volume of the first chamber 31 is increased, and the liquid in the second chamber 32 flows into the first chamber 31 through the second overflowing hole 51. Thus, by the arrangement of the second overflowing hole 51, the fluid in the first chamber 31 can flow into the second chamber 32, so that the first piston rod 4 can be prevented from being retracted too fast.
As shown in fig. 1 to 5, a third overflowing hole 43 is formed in the third chamber 41, and the third overflowing hole 43 is suitable for communicating the second chamber 32 with the third chamber 41.
It should be noted that the third overflowing hole 43 is opened in the side wall of the third chamber 41, the third overflowing hole 43 is disposed along the radial direction of the first piston rod 4, the third overflowing hole 43 may be a damping hole, and the diameter of the second overflowing hole 51 may be between 0.2mm and 2.5mm, so as to prevent the pressure loss from increasing due to the too large damping hole. When the first piston rod 4 moves towards the first chamber 31 relative to the second piston 2, the volumes of the second chamber 32 and the third chamber 41 increase, the volumes of the first chamber 31 and the fourth chamber 42 decrease, the liquid in the first chamber 31 firstly flows into the second chamber 32 through the second overflowing hole 51, then flows into the third chamber 41 from the second chamber 32 through the third overflowing hole 43, the second piston 2 moves towards the fourth chamber 42, and the fluid in the fourth chamber 42 flows out through the first overflowing hole 421; when the first piston rod 4 moves towards the second chamber 32 relative to the second piston 2, the volumes of the second chamber 32 and the third chamber 41 are reduced, the volumes of the first chamber 31 and the fourth chamber 42 are increased, fluid flows into the fourth chamber 42 from the outside of the hydraulic cylinder, the second piston 2 moves towards the third chamber 41, liquid flows into the second chamber 32 from the third chamber 41 through the third overflowing hole 43, and the liquid in the second chamber 32 flows into the first chamber 31 through the second overflowing hole 51. Thereby, by the arrangement of the third overflowing hole 43, the first chamber 31 is indirectly communicated with the third chamber 41, so that the liquid in the first chamber 31 and the third chamber 41 can be communicated.
As shown in fig. 1 to 5, the hydraulic cylinder further includes a first sealing ring 6, the first sealing ring 6 is sleeved on the circumferential outer surface of the first piston 5, and the first sealing ring 6 is suitable for sealing between the first piston 5 and the cylinder barrel 3. The first sealing ring 6 is coaxial with the first piston 5 and the cylinder 3, and when the first piston 5 moves along the cylinder 3, the first sealing ring 6 moves together with the first piston 5. Thus, the first seal ring 6 seals between the first piston 5 and the cylinder 3, and the first chamber 31 and the second chamber 32 are prevented from leaking at the joint between the first piston 5 and the cylinder 3.
Preferably, a first receiving groove 52 is formed in a circumferential outer surface of the first piston 5, and at least a portion of the first sealing ring 6 is received in the first receiving groove 52. The first receiving groove 52 is an annular groove, the first receiving groove 52 and the first piston 5 are coaxial, and the first seal ring 6 is partially embedded in the first receiving groove 52. Therefore, the first seal ring 6 is axially positioned by the arrangement of the first receiving groove 52, so that the first seal ring 6 can be prevented from being released from the first piston 5.
As shown in fig. 1 to 5, the hydraulic cylinder further includes a second sealing ring 7, the second sealing ring 7 is sleeved on the circumferential outer surface of the second piston 2, and the second sealing ring 7 is suitable for sealing between the second piston 2 and the piston cavity. The second sealing ring 7 is coaxial with the second piston 2 and the first piston rod 4, and when the second piston 2 moves relative to the first piston rod 4, the second sealing ring 7 and the second piston 2 are kept static. Thus, the second seal ring 7 seals between the second piston 2 and the first piston rod 4, and leakage of the third chamber 41 and the fourth chamber 42 at the joint between the second piston 2 and the first piston rod 4 is avoided.
Preferably, a second receiving groove 21 is formed in a circumferential surface of the second piston 2, and at least a portion of the second sealing ring 7 is received in the second receiving groove 21. The second receiving groove 21 is an annular groove, the second receiving groove 21 and the second piston 2 are coaxial, and the second sealing ring 7 is partially embedded in the second receiving groove 21. Therefore, the second seal ring 7 is axially positioned by the second receiving groove 21, so that the second seal ring 7 can be prevented from being loosened from the second piston 2.
The utility model also provides a pile high machine, include as above-mentioned arbitrary pneumatic cylinder. The stacking machine comprises a gantry hydraulic system, the gantry hydraulic system comprises a pump and a hydraulic cylinder, and an outlet of the pump is communicated with a fourth overflowing hole 311 of the hydraulic cylinder. The hydraulic cylinder is a plunger cylinder. Compared with the prior art, the fork lift truck with the beneficial effect of pneumatic cylinder is the same, no longer gives unnecessary details here.
Although the present disclosure has been described above, the scope of the present disclosure is not limited thereto. Various changes and modifications may be made by those skilled in the art without departing from the spirit and scope of the present disclosure, and these changes and modifications are intended to fall within the scope of the present disclosure.
Claims (10)
1. A hydraulic cylinder, characterized by comprising a cylinder barrel (3), a first piston rod (4), a first piston (5) and a second piston (2), said first piston (5) being connected to said first piston rod (4), said first piston (5) dividing said cylinder barrel (3) into a first chamber (31) and a second chamber (32), said first chamber (31) being adapted to communicate with a power element; the piston cavity is formed in the first piston rod (4), the second piston (2) separates the piston cavity into a third cavity (41) and a fourth cavity (42), the second piston (2) can slide relative to the piston cavity, the third cavity (41) is communicated with the first cavity (31), and a first overflowing hole (421) is formed in the fourth cavity (42).
2. The hydraulic cylinder according to claim 1, further comprising a second piston rod (1), the second piston rod (1) being parallel to the axis of the first piston rod (4); a through hole (53) is formed in the first piston (5), the second piston rod (1) is arranged in the through hole (53) in a penetrating mode, and the first piston (5) can slide relative to the second piston rod (1); and two ends of the second piston rod (1) are respectively connected with the second piston (2) and the cylinder barrel (3).
3. Hydraulic cylinder according to claim 1, characterized in that the end face of the second piston (2) close to the axial end of the second chamber (32) is flush with the outer end face of the axial end of the cylinder tube (3).
4. Hydraulic cylinder according to claim 1, characterized in that the first piston (5) is provided with a second through-flow aperture (51), the second through-flow aperture (51) being adapted to communicate the first chamber (31) with the second chamber (32).
5. Hydraulic cylinder according to claim 1, characterized in that the third chamber (41) is provided with a third flow aperture (43), the third flow aperture (43) being adapted to communicate the second chamber (32) with the third chamber (41).
6. The hydraulic cylinder according to claim 1, further comprising a first sealing ring (6), wherein the first sealing ring (6) is sleeved on the circumferential outer surface of the first piston (5), and the first sealing ring (6) is adapted to seal between the first piston (5) and the cylinder tube (3).
7. The hydraulic cylinder according to claim 6, wherein the circumferential surface of the first piston (5) defines a first receiving groove (52), and the first seal ring (6) is at least partially received in the first receiving groove (52).
8. The hydraulic cylinder according to claim 1, further comprising a second sealing ring (7), the second sealing ring (7) being fitted around a circumferential outer surface of the second piston (2), the second sealing ring (7) being adapted to seal between the second piston (2) and the piston cavity.
9. The hydraulic cylinder according to claim 8, wherein the second piston (2) has a circumferential surface defining a second receiving groove (21), and wherein the second seal ring (7) is at least partially received in the second receiving groove (21).
10. A fork lift truck comprising a hydraulic cylinder according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022730472.6U CN214063439U (en) | 2020-11-23 | 2020-11-23 | Hydraulic cylinder and stacking machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022730472.6U CN214063439U (en) | 2020-11-23 | 2020-11-23 | Hydraulic cylinder and stacking machine |
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| Publication Number | Publication Date |
|---|---|
| CN214063439U true CN214063439U (en) | 2021-08-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202022730472.6U Active CN214063439U (en) | 2020-11-23 | 2020-11-23 | Hydraulic cylinder and stacking machine |
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| CN (1) | CN214063439U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023207294A1 (en) * | 2022-04-25 | 2023-11-02 | 三一重机有限公司 | Hydraulic control system and operation machine |
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- 2020-11-23 CN CN202022730472.6U patent/CN214063439U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023207294A1 (en) * | 2022-04-25 | 2023-11-02 | 三一重机有限公司 | Hydraulic control system and operation machine |
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