CN113833715A - Hydraulic cylinder with explosion-proof buffering function - Google Patents
Hydraulic cylinder with explosion-proof buffering function Download PDFInfo
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- CN113833715A CN113833715A CN202111314102.7A CN202111314102A CN113833715A CN 113833715 A CN113833715 A CN 113833715A CN 202111314102 A CN202111314102 A CN 202111314102A CN 113833715 A CN113833715 A CN 113833715A
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- 230000003139 buffering effect Effects 0.000 title abstract description 12
- 239000000872 buffer Substances 0.000 claims abstract description 98
- 239000012530 fluid Substances 0.000 claims abstract description 9
- 238000007789 sealing Methods 0.000 claims description 45
- 239000012945 sealing adhesive Substances 0.000 claims description 3
- 238000000034 method Methods 0.000 abstract description 10
- 230000008569 process Effects 0.000 abstract description 9
- 238000004880 explosion Methods 0.000 abstract description 6
- 239000003921 oil Substances 0.000 description 155
- 239000007788 liquid Substances 0.000 description 63
- 230000000694 effects Effects 0.000 description 16
- 230000008602 contraction Effects 0.000 description 10
- 230000033001 locomotion Effects 0.000 description 8
- 230000000630 rising effect Effects 0.000 description 7
- 239000000428 dust Substances 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 4
- 230000000903 blocking effect Effects 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 238000013459 approach Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000002265 prevention Effects 0.000 description 2
- 230000009172 bursting Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1471—Guiding means other than in the end cap
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
- F15B20/005—Leakage; Spillage; Hose burst
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Actuator (AREA)
Abstract
A hydraulic cylinder with an explosion-proof buffer function comprises: the movable assembly that cylinder body subassembly and relatively cylinder body subassembly removed, the cylinder body subassembly has jar chamber and first hydraulic fluid port, first hydraulic fluid port and jar chamber intercommunication, and the movable assembly includes: the piston is located in the cylinder cavity and divides the cylinder cavity into a first cavity and a second cavity, the piston is provided with a plurality of buffer channels, and the first cavity is communicated with the second cavity through the buffer channels. When the hydraulic cylinder is used as a plunger type hydraulic cylinder, the hydraulic cylinder has an explosion-proof buffering function, and even if oil explosion happens in the process of bearing a heavy object, the heavy object can be prevented from rapidly falling, so that the hydraulic cylinder is protected, and safety accidents are prevented.
Description
Technical Field
The invention relates to the field of hydraulic cylinders, in particular to a hydraulic cylinder with an explosion-proof buffering function.
Background
The hydraulic cylinder is a hydraulic actuator which converts hydraulic energy into mechanical energy and makes linear reciprocating motion. It has simple structure and reliable operation. When it is used to implement reciprocating motion, it can omit speed-reducing device, and has no transmission gap, and its motion is stable, so that it can be extensively used in various mechanical hydraulic systems.
Hydraulic cylinders are generally classified into two types, ram and piston: the ram cylinder generally has an oil port, and when the plunger rod extends, the oil port inputs liquid (usually hydraulic oil) to push the plunger rod to advance; when the plunger rod is contracted, the oil port outputs liquid to drive the plunger rod to retreat. The piston type hydraulic cylinder generally has two oil ports, when a piston rod extends out, a first oil port inputs liquid, and a second oil port outputs liquid to push a piston to advance; when the piston rod contracts, the first oil port outputs liquid, and the second oil port inputs liquid, so that the piston is enabled to retreat.
However, the existing plunger-type hydraulic cylinder is often used for supporting a weight, if the weight of the weight is large, a situation (commonly called "oil explosion") that an oil pipe for conveying liquid bursts and explodes due to excessive hydraulic pressure may occur during the process of retracting the piston rod (i.e. during the process of descending the weight), when the oil explosion occurs, the hydraulic pressure in the hydraulic cylinder suddenly drops, the weight rapidly descends, and thus the hydraulic cylinder is damaged, or even a safety accident occurs.
At present, some manufacturers may set a buffer mechanism in the hydraulic cylinder to prevent the risk caused by oil explosion (refer to a hydraulic cylinder joint with an explosion-proof function disclosed in chinese utility model CN212028230U, and an explosion-proof hydraulic cylinder disclosed in chinese utility model CN 213064133U). However, the structure of the lift buffer mechanism is excessively complex, which increases the difficulty of the manufacturing process of the hydraulic cylinder and disadvantageously reduces the manufacturing cost of the hydraulic cylinder. In addition, the above-mentioned buffer mechanism mainly utilizes the spring to cushion, and the spring can appear the problem of mechanical fatigue along with the increase of number of times of using, loses elastic recovery ability gradually, and then can not realize the effect of buffering.
In addition, the existing plunger type hydraulic cylinder generally only utilizes a guide sleeve to guide the plunger rod, and the single-point guide mode may cause the plunger rod to swing. Although some plunger type hydraulic cylinders lengthen the guide sleeve, the overlong guide sleeve can reduce the internal volume of the hydraulic cylinder, and limit the stroke of the plunger rod.
Disclosure of Invention
In order to solve the above problems, an aspect of the present invention provides a hydraulic cylinder having an explosion-proof cushion function, including: the cylinder body subassembly with can be relatively the movable assembly that the cylinder body subassembly removed, the cylinder body subassembly has cylinder chamber and first hydraulic fluid port, first hydraulic fluid port and cylinder chamber intercommunication, the movable assembly includes: piston and piston rod, the piston rod forms fixedly with the piston, the piston is located the inside of cylinder chamber, and the piston divides cylinder chamber into first cavity and second cavity, its characterized in that: the piston is provided with a plurality of buffer passages, and the first chamber and the second chamber are communicated through the buffer passages.
Further, the cross sections of the cylinder cavity and the buffer channel are circular, and the inner diameter of the cylinder cavity is more than 20 times of that of the buffer channel. The flow rate of the liquid can be effectively controlled by the arrangement, so that an ideal buffering effect is guaranteed.
Further, the buffer channel has a first port facing the first chamber and a second port facing the second chamber.
Further, the piston is also provided with a first oil path channel, the first oil path channel is communicated with the plurality of buffer channels, and when the piston is positioned at the rearmost end of the cylinder cavity, the first oil path channel is communicated with the first oil port. The first oil passage is arranged to control the liquid transmission flow rate of the first oil port, so that the buffer effect when the first oil port is extended and started and before the first oil port is contracted and reaches the limit is realized.
Further, the movable assembly further comprises: the sealing elements are used for respectively plugging the buffer channels. When the sealing piece is not installed on the movable assembly, the first cavity is communicated with the second cavity through the buffer channel, and after the sealing piece is installed on the movable assembly, the buffer channel is blocked, so that the first cavity is not communicated with the second cavity.
Further, the sealing member is a machine-meter screw, one or both of the two ports of the buffer channel are provided with internal threads, and the machine-meter screw is meshed with the internal threads in the ports of the buffer channel. The plugging is formed in a meshed mode, so that the plugging effect can be guaranteed, liquid circulation is prevented, and the plugging device is convenient to disassemble and assemble and convenient to operate.
Further, the cylinder body assembly is also provided with a second oil port which is more front than the first oil port; the piston is further provided with a second oil path channel which is more front than the first oil path channel and is communicated with a plurality of other buffer channels, when the piston is positioned at the foremost end of the cylinder cavity, the second oil path channel is communicated with a second oil port, a second port of the buffer channel communicated with the first oil path channel is blocked by a sealing element, and a first port of the buffer channel communicated with the second oil path channel is blocked by a sealing adhesive. The second oil passage is arranged to control the liquid transmission flow rate of the second oil port, so that the buffering effect during starting shrinkage and before reaching the limit is achieved.
Further, the cross sections of the first oil path channel and the second oil path channel are circular, the inner diameter of the cylinder cavity is more than 40 times of the inner diameter of the first oil path channel, and the inner diameters of the first oil path channel and the second oil path channel are equal.
Further, the movable assembly further comprises: the piston oil seal and the piston wear-resistant belt are arranged on the outer side wall of the piston in a surrounding mode, the piston oil seal and the inner side wall of the cylinder cavity form sealing, and the piston wear-resistant belt is in contact with the inner side wall of the cylinder cavity. Piston oil can obstruct liquid, and the wear-resistant belt of the piston can reduce friction force, thereby prolonging the service life.
Further, the cylinder block assembly further includes: and the sealing piece seals the second oil port. After the second port is blocked, the cylinder functions as a ram cylinder.
After the technical scheme is adopted, the invention has the effects that:
1. the hydraulic cylinder can be freely switched between a plunger type hydraulic cylinder and a piston type hydraulic cylinder, and the use freedom degree is high.
2. When the hydraulic cylinder is used as a plunger type hydraulic cylinder, the hydraulic cylinder has an explosion-proof buffering function, and even if oil explosion happens in the process of bearing a heavy object, the heavy object can be prevented from rapidly falling, so that the hydraulic cylinder is protected, and safety accidents are prevented.
3. When the hydraulic cylinder is used as a plunger type hydraulic cylinder, the flow rate of liquid can be accurately controlled, and the synchronism of a plurality of plunger type hydraulic cylinders is high.
4. The hydraulic cylinder can play a starting buffering function when being started in an extending mode and in a contracting mode, and the phenomenon that the hydraulic cylinder is too fast to start and is out of control is avoided.
Drawings
FIG. 1 is a schematic structural diagram of a hydraulic cylinder according to the present invention;
FIG. 2 is a schematic view of a portion of a movable assembly according to the present invention;
FIG. 3 is a schematic end view of a piston according to the present invention;
FIG. 4 is a schematic structural view of a front cover assembly according to the present invention;
FIG. 5 is a schematic view of a guide sleeve assembly according to the present invention;
FIG. 6 is a schematic structural view of a rear cover assembly according to the present invention;
FIGS. 7a to 7e are views showing the operation state of a plunger type hydraulic cylinder according to embodiment 1 of the present invention;
FIGS. 8a to 8b are views showing the synchronous operation of two plunger-type hydraulic cylinders according to embodiment 2 of the present invention;
fig. 9a to 9h are operation state diagrams of the piston cylinder according to embodiment 3 of the present invention.
Detailed Description
It is specifically noted that, in the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise; the meaning of "several" is at least one. All directional indicators (such as up, down, left, right, front, and rear … …) in the embodiment of the present invention are only used to explain the relative positional relationship between the components, the movement, and the like in a certain posture, and if the certain posture is changed, the directional indicator is changed accordingly.
The technical solution of the present invention is further described by the following examples:
as shown in fig. 1, for the sake of understanding, the present invention defines the moving direction of the movable assembly 2 as a telescopic direction D, an end close to the extending direction as a front end, and an end close to the retracting direction as a rear end.
The invention provides a hydraulic cylinder with an explosion-proof buffering function, which comprises: cylinder body subassembly 1 and movable assembly 2 that can move relative to cylinder body 1 subassembly, cylinder body subassembly 1 has cylinder chamber 101 and first hydraulic fluid port 102, and first hydraulic fluid port 102 communicates with cylinder chamber 101, and movable assembly 2 includes: a piston 21 and a piston rod 22, the piston rod 22 being fixed to the piston 21, the piston 21 being located inside the cylinder chamber 101, and the piston 21 dividing the cylinder chamber 101 into a first chamber 101a and a second chamber 101 b. As shown in fig. 2 and 3, the piston 21 has a plurality of buffer passages 211, and the first chamber 101a and the second chamber 101b are communicated with each other through the buffer passages 211.
Specifically, the buffer channel 211 has a first port and a second port, the first port of the buffer channel 211 faces the first chamber 101a, and the second port of the buffer channel 211 faces the second chamber 101 b. When the hydraulic cylinder is used as a plunger type hydraulic cylinder, the liquid in the first chamber 101a and the liquid in the second chamber 101b can be communicated through the buffer passage 211 to achieve an explosion-proof buffer effect, which will be described later. It should be noted that the term "explosion-proof" in the present invention does not mean the prevention of a hydraulic cylinder or oil pipe from bursting, but means the prevention of the instant rapid movement of the movable assembly 2 caused by the loss of control after the oil pipe bursts.
The buffer passage 211 may be disposed at a middle position of the piston 21, or at an edge position of the piston 21. Specifically, when the buffer passage 211 is provided at the middle position of the piston 21, the buffer passage 211 is a through hole, and when the buffer passage 211 is provided at the edge position of the piston 21, the buffer passage 211 is a groove (i.e., a groove on the side wall of the piston 21). In addition, the buffer passage 211 may be a straight passage or a curved passage as long as the first chamber 101a and the second chamber 101b are communicated with each other.
Wherein, in the following embodiments, the movable assembly 2 is a single-rod movable assembly (i.e. only one piston rod 22); in other embodiments, the movable assembly 2 may be a dual-rod movable assembly, with the two piston rods 22 facing in opposite directions, and with the above-mentioned extending and retracting directions being referenced to one of the piston rods 22. In addition, the piston 21 and the piston rod 22 may be integrally formed or may be separately formed (i.e., may be detachable from each other), and the piston 21 and the piston rod 22 may be fixed by a threaded engagement or may be fixed by another method.
As a preferred solution, with continued reference to fig. 1, the cylinder chamber 101 and the buffer passage 211 are both of a uniform hollow structure, i.e., the inner diameters of the respective positions are equal (or constant, the same applies hereinafter). The cylinder chamber 101 is sectioned along a plane perpendicular to the telescopic direction D, the plane in the liquid flow direction and the buffer passage 211 are sectioned, hereinafter collectively referred to as a cross section, and the cross sectional area of the cylinder chamber 101 is 400 times or more the cross sectional area of the buffer passage 211.
More specifically, the cross-sections of the cylinder chamber 101 and the buffer passage 211 are circular, and the inner diameter of the cylinder chamber 101 is 20 times or more the inner diameter of the buffer passage 211. More preferably, the cross-sectional area of the cylinder chamber 101 is 576 times (i.e. the inner diameter ratio is 24: 1) the cross-sectional area of the buffer passage 211, and the above arrangement can effectively control the flow rate of the liquid to ensure that the desired buffer effect is achieved. Further, the cross-sectional area of the cylinder chamber 101 is generally 900 times or less the cross-sectional area of the buffer passage 211.
Specifically, with continued reference to fig. 2, the movable assembly 2 further includes: a number of seals 25, the number of seals 25 blocking the number of buffer channels 211. When the seal 25 is not installed on the movable assembly 2, the first chamber 101a and the second chamber 101b are communicated through the buffer passage 211, and when the seal 25 is installed on the movable assembly 2, the buffer passage 211 is blocked, and the communication between the first chamber 101a and the second chamber 101b is not performed.
Preferably, the sealing member 25 is a screw, and one or both of the ports of the buffer passage 211 are provided with an internal thread, and the screw is engaged with the internal thread in the port of the buffer passage 211. The plugging is formed in a meshed mode, so that the plugging effect can be guaranteed, liquid circulation is prevented, and the plugging device is convenient to disassemble and assemble and convenient to operate. Of course, in other embodiments, the seal 25 may also employ other types of elements, such as: rubber plugs, latches, etc.
It is worth mentioning that the cylinder of the invention can be switched between piston and ram cylinders by mounting and removing the seal 25. In addition, the buffer passage 211 and the sealing member 25 may be one or more, and preferably, the buffer passage 211 and the sealing member 25 are provided in plurality. In practical application, different numbers of buffer channels 211 can be selectively blocked according to the force borne by the hydraulic cylinder and the moving speed of the movable assembly 2, and the flexibility of use is stronger.
Specifically, as shown in fig. 1 and 2, the piston 21 further has a first oil passage 212, the first oil passage 212 communicates with the plurality of buffer passages 211, and when the piston 21 is located at the rearmost end of the cylinder chamber 101, the first oil passage 212 communicates with the first oil port 21. The first oil passage 212 is arranged to control the liquid transmission flow rate of the first oil port 102, so that the buffering effect during the extension starting and before the contraction reaches the limit is realized.
More specifically, one port of the first oil passage 212 faces the at least one relief passage 211, and the other port of the first oil passage 212 faces the inner side wall of the cylinder chamber 101.
More specifically, the cylinder block assembly 1 also has a second oil port 103, the second oil port 103 being more forward than the first oil port 102; the piston 21 is further provided with a second oil path channel 213, the second oil path channel 213 is more forward than the first oil path channel 212, the second oil path channel 213 is communicated with the other plurality of buffer channels 211 (namely the second oil path channel 213 is communicated with the other plurality of buffer channels 211 which are not communicated with the first oil path channel 212), when the piston 21 is positioned at the foremost end of the cylinder cavity 101, the other port of the second oil path channel 213 is communicated with the second oil port 103, the second port of the buffer channel 211 communicated with the first oil path channel 212 is blocked by a sealing element 25, and the first port of the buffer channel 211 communicated with the second oil path channel 213 is blocked by a sealing adhesive 25. The second oil passage 213 is provided to control the flow rate of the liquid delivered from the second port 103, thereby achieving a cushioning effect during the start of the contraction and before the expansion reaches the limit.
More specifically, one port of the second oil passage 213 faces the other at least one buffer passage 211, and the other port of the second oil passage 213 faces the inner side wall of the cylinder chamber 101.
The first oil passage 212 and the second oil passage 213 may be through-hole passages, that is, through holes are formed in the side surface of the piston 21, and the through holes communicate with the buffer passage 211; in other embodiments, the first oil passage 212 and the second oil passage 213 may be steps or grooves, as long as they communicate with the buffer passage 211 and respectively face the first oil port 102 and the second oil port 103 when the piston 21 moves to two limit positions (i.e., the contraction limit and the extension limit).
Preferably, the first oil passage 212 and the second oil passage 213 are both of a uniform hollow structure, the cross-sectional area of the cylinder cavity 101 is more than 1600 times of the cross-sectional area of the first oil passage 212, and the cross-sectional areas of the first oil passage 212 and the second oil passage 213 are equal.
More specifically, the cross sections of the cylinder chamber 101, the first oil passage 212 and the second oil passage 21 are all circular, the inner diameter of the cylinder chamber 101 is more than 40 times of the inner diameter of the first oil passage 212, and the inner diameters of the first oil passage 212 and the second oil passage 213 are equal. More preferably, the cross-sectional area of the cylinder chamber 101 is 2304 times (i.e. the inner diameter ratio is 48: 1) the cross-sectional area of the first oil passage 212, and the above arrangement can also effectively control the flow rate of the liquid to ensure the ideal buffering effect. The cross-sectional area of the cylinder chamber 101 is generally 3600 times or less the cross-sectional area of the first oil passage 212.
Specifically, with continued reference to fig. 2, the movable assembly 2 further includes: piston oil seal 23 and piston wear-resisting area 24, piston oil seal 23 and piston wear-resisting area 24 all encircle the lateral wall of piston 21 (i.e. set up on the lateral wall in annular mode, the same below), and piston oil seal 23 forms the sealed (i.e. liquid can not pass through) with the inside wall of cylinder chamber 101, and piston wear-resisting area 24 contacts with the inside wall of cylinder chamber 101. More specifically, there are two piston oil seals 23, the two piston oil seals 23 are separated from each other in the telescopic direction D, and the piston wear strip 24 is located between the two piston oil seals 24.
Specifically, with continued reference to fig. 1, the cylinder assembly 1 includes: the cylinder barrel 11, the front cover assembly 12, the guide sleeve assembly 13, the rear cover assembly 14 and the flange 15, wherein the front cover assembly 12, the guide sleeve assembly 13 and the rear cover assembly 14 are sealed with the inner side wall of the cylinder barrel 11, the guide sleeve assembly 13 is located between the front cover assembly 12 and the rear cover assembly 14 along the extension direction D, the flange 15 is fixed on the outer side wall of the cylinder barrel 11, the cylinder cavity 101, the first oil port 102 and the second oil port 103 are all arranged on the cylinder barrel 11, and the front cover assembly 12 and the guide sleeve assembly 13 are sealed with the side wall of the piston rod 22. The front cover assembly 12, the guide bush assembly 13, and the rear cover assembly 14 seal against the inner side wall of the cylinder tube 11, thereby preventing liquid from leaking out of the cylinder chamber 101, and similarly, the guide bush assembly 13 seals against the side wall of the piston rod 22, thereby preventing liquid from leaking out of the cylinder chamber 101. Further, dust can be prevented from entering the cylinder chamber 101 by the sealing action of the front cover assembly 12 and the side wall of the piston rod 22. The flange 15 is mainly used for fixing the hydraulic cylinder.
More specifically, as shown in fig. 7a, the cylinder block assembly 1 further includes: and the sealing piece 16 seals the second oil port 103 by the sealing piece 16. The sealing member 16 may be a rubber plug, a bolt, or the like having a sealing function. Before the hydraulic cylinder is used as a plunger type hydraulic cylinder, the sealing piece 16 can be loosened, then the air in the cylinder cavity 101 is exhausted, and the cylinder cavity 101 is filled with liquid; when the hydraulic cylinder is used as a ram-type hydraulic cylinder, the second oil port 103 is blocked with the closure 16.
More specifically, as shown in fig. 4, the front cover assembly 12 includes: the front cover 121, the front cover sealing ring 122 and the dust ring 123, the front cover 121 is a hollow structure, the front cover sealing ring 122 is arranged on the outer side wall of the front cover 121 in a surrounding mode, the dust ring 123 is arranged on the inner side wall of the front cover 121 in a surrounding mode, the front cover sealing ring 122 and the inner side wall of the cylinder 11 form sealing, and the dust ring 123 and the side wall of the piston rod 22 form sealing.
More specifically, as shown in fig. 5, the guide bush assembly 13 includes: the guide sleeve 131, the guide sleeve outer sealing ring 132, the guide sleeve oil seal 133, the guide sleeve wear-resistant band 134 and the guide sleeve inner sealing ring 135 are of a hollow structure, the guide sleeve 131 is arranged on the outer side wall of the guide sleeve 131 in a surrounding mode, the guide sleeve oil seal 133, the guide sleeve wear-resistant band 134 and the guide sleeve inner sealing ring 135 are arranged on the inner side wall of the guide sleeve 131 in a surrounding mode, the guide sleeve outer sealing ring 132 and the inner side wall of the cylinder 11 form sealing, the guide sleeve oil seal 133 and the guide sleeve inner sealing ring 135 form sealing with the side wall of the piston rod 22, and the guide sleeve wear-resistant band 134 is in contact with the side wall of the piston rod 22. More specifically, the number of the guide sleeve outer sealing rings 132 and the number of the guide sleeve oil seals 133 are two, the two guide sleeve outer sealing rings 132 are separated from each other in the telescopic direction D, and the two guide sleeve oil seals 133 are also separated from each other in the telescopic direction D.
Due to the guiding function between the piston 21 and the cylinder 11 and the guiding function between the guide sleeve 131 and the piston rod 22, the two-point guiding effect can be realized, so that the piston rod 22 moves more stably without shaking.
More specifically, as shown in fig. 6, the rear cover assembly 14 includes: the rear cover 141 and the rear cover sealing ring 142, the rear cover sealing ring 142 is annularly arranged on the outer side wall of the rear cover 141, and the rear cover sealing ring 142 forms a seal with the inner side wall of the cylinder 11. More specifically, the back cover sealing rings 142 are two, and the two back cover sealing rings 142 are separated from each other in the expansion and contraction direction D.
Wherein the dust ring 123 can prevent the entry of dust. The piston oil seal 23 and the guide sleeve oil seal 133 can block liquid. The front cover sealing ring 122, the guide sleeve outer sealing ring 132, the guide sleeve inner sealing ring 135 and the rear cover sealing ring 142 can prevent the leakage of liquid. The piston wear strips 24 and the guide sleeve wear strips 134 reduce friction and thus prolong service life.
[ example 1 ]
In this embodiment, the hydraulic cylinder is used as a ram-type hydraulic cylinder, all or part of the buffer passage 211 is not blocked by the screw 25, and the second oil port 103 is blocked by the closure 16. Specifically, the piston 21 has four buffer passages 211, the four buffer passages 211 are arranged in a matrix, the cross sections of the cylinder chamber 101, the buffer passages 211 and the first oil passage 212 are all circular, the diameter of the cylinder chamber 101 is 120mm, the diameter of the buffer passages 211 is 5mm, and the diameter of the first oil passage 212 is 2.5 mm. The working process of the plunger type hydraulic cylinder is as follows:
as shown in fig. 7a (in the figure, a large arrow indicates a moving direction of a piston, a small arrow indicates a flowing direction of a liquid, and the same is applied below), when the ram-type hydraulic cylinder is extended and started, the first oil port 102 inputs the liquid into the first chamber 101a, at this time, the piston 21 is located at the rearmost end of the cylinder cavity 101, the first chamber 101a has almost no liquid, the other port of the first oil passage 212 faces the first oil port 102, since the liquid input from the first oil port 102 needs to pass through the first oil passage 212 and the at least one buffer passage 211 to reach the first chamber 101a, the flow rate is slow, the buffer effect can effectively avoid the hydraulic pressure from rising to cause that the hydraulic cylinder is extended and started too fast, in addition, the second chamber 101b is originally filled with the liquid, and the liquid can have a certain blocking effect on the piston 21 when the plunger-type hydraulic cylinder is extended and started, and the problem of the hydraulic pressure rising can also be avoided; as shown in fig. 7b, in the extending process of the plunger-type hydraulic cylinder, the liquid input from the first oil port 102 pushes the piston 21 (when the piston is standing, the movable assembly 2 is still under the action of its own gravity and buoyancy, the same applies below), and along with the movement of the piston 21, the liquid in the second chamber 101b is also transferred to the first chamber 101a through the buffer channel 211, and since the liquid in the second chamber 101b continues to have a certain blocking effect on the piston 21, the problem of hydraulic pressure surge can be continuously avoided, and it is worth mentioning that, compared to the whole cylinder chamber 101, the liquid in the second chamber 101b hardly moves actually, and only the relative movement of the piston 21 changes the volumes of the first chamber 101a and the second chamber 101b, so that the liquid originally located in the second chamber 101b is converted into the first chamber 101 a; as shown in fig. 7c, when the ram cylinder extends to the limit, the first port 102 stops inputting the liquid into the first chamber 101a, the piston 21 is located at the foremost end of the cylinder cavity 101, and the second chamber 101b has almost no liquid; as shown in fig. 7d, when the plunger hydraulic cylinder contracts, the first oil port 102 draws the liquid from the first chamber 101a, the piston 21 moves in the reverse direction, and at this time, the internal pressure of the second chamber 101b is smaller than the internal pressure of the first chamber 101a (i.e., the second chamber 101b is in a relatively vacuum negative pressure state), and the liquid in the first chamber 101a is drawn out and simultaneously filled into the second chamber 101b, so that the piston 21 moves in the contraction direction, which hinders the drawing of the liquid, and buffers the movement of the piston 21 in the contraction direction, thereby avoiding the situation that the hydraulic pressure of the first chamber 101a drops suddenly. In addition, as shown in fig. 7e, when the plunger type hydraulic cylinder is contracted to the limit, the other port of the first oil passage 212 faces the first oil port 102, and the remaining liquid in the first chamber 101a needs to pass through the buffer passage 211 and at least one first oil passage 212 to be extracted from the first oil port 102, so that the flow rate is slow, and the buffer effect can effectively avoid hydraulic pressure from rising to cause the hydraulic cylinder to be contracted and stopped too fast.
More importantly, even if the oil explosion happens due to the overload bearing in the contraction process of the plunger type hydraulic cylinder, the liquid in the first chamber 101a can be prevented from being drawn out instantaneously through the negative pressure effect of the second chamber 101b, so that the hydraulic pressure of the first chamber 101a can not drop suddenly, and the problem that the hydraulic cylinder is damaged or a safety accident happens due to the sudden drop of the hydraulic pressure is avoided.
[ example 2 ]
In this embodiment, the hydraulic cylinder is also used as a ram cylinder, and the same structure as the ram cylinder of embodiment 1 is used except that two ram cylinders are used for simultaneous expansion and contraction in this embodiment. In the practical application process, the hydraulic pressures input and output by the two plunger type hydraulic cylinders are difficult to keep completely consistent, so the problem that the two plunger type hydraulic cylinders are not synchronous in extension and retraction frequently occurs.
As shown in fig. 8a, when the two ram cylinders are simultaneously extended, the first ports 102 of the two ram cylinders simultaneously input the fluid, and the pistons 21 of the two ram cylinders simultaneously move. Because the piston 21 is provided with the buffer channel 211, the flow rate of liquid can be controlled by opening the number (namely, the number which is not blocked) of the buffer channel 211, thereby ensuring the extending synchronism of the two plunger type hydraulic cylinders; similarly, as shown in fig. 8b, when the two plunger cylinders are contracted simultaneously, the synchronism of the contraction of the two plunger cylinders is ensured by the above-described setting of the number of the opening buffer passages 211.
It should be noted that, since the cross-sectional area of the buffer channel 211 is very small relative to the cylinder cavity 101, the flow rate of the liquid is mainly determined by the number of the opened buffer channels 211, and therefore, in the practical application process, if the cross-sectional areas of the buffer channels 211 of the two ram hydraulic cylinders are ensured to be within the tolerance range, as long as the two ram hydraulic cylinders open the same number of buffer channels 211, the expansion and contraction of the two ram hydraulic cylinders can be synchronized.
In addition, since the piston wear strips 24 are all arranged around the outer side wall of the piston 21 and the guide bush wear strips 134 are arranged around the inner side wall of the guide bush 131, and the positions where the friction force is generated when the movable assembly 2 moves are mainly the two positions, the friction force generated inside the two hydraulic cylinders is basically equal under the condition that the friction coefficients of the wear strips of the two hydraulic cylinders are the same, and the synchronism is further maintained.
[ example 3 ]
Unlike embodiment 1, in the present embodiment, the hydraulic cylinder is used as a piston type hydraulic cylinder, all the buffer passages 211 are closed by the screw 25, and the second oil ports 103 are not closed by the closure 16. The cross sections of the first oil channel 212 and the second oil channel 213 are circular, and the diameters of the first oil channel 212 and the second oil channel 213 are 2.5 mm.
As shown in fig. 9a to 9d, when the piston-type hydraulic cylinder is started to extend, the first oil port 102 inputs liquid into the first chamber 101a, the second oil port 103 extracts the liquid from the second chamber 101b, at this time, the piston 21 is located at the rearmost end of the cylinder cavity 101, the first chamber 101a has almost no liquid, the other port of the first oil passage 212 faces the first oil port 102, and the liquid input from the first oil port 102 needs to pass through the first oil passage 212 and the at least one buffer passage 211 to reach the first chamber 101a, so that the flow rate is slow, and the buffer effect can effectively prevent the hydraulic cylinder from extending and starting too fast due to hydraulic pressure rising; when the other port of the first oil passage 212 leaves the first oil port 102, the liquid input from the first oil port 102 directly reaches the first chamber 101a and continues to push the piston 21 to move; as the piston moves, the second oil passage 213 gradually approaches the second oil port 103; when the piston 21 reaches the foremost end of the cylinder cavity 101, the first oil port 102 stops inputting liquid into the first chamber 101a, the second oil port 103 stops extracting liquid from the second chamber 101b, at this time, the other port of the second oil passage 213 faces the second oil port 103, and the remaining liquid in the second chamber 101b needs to pass through at least one buffer passage 211 and the second oil passage 213 to be extracted from the second oil port 103, so that the flow rate is slow, and the buffer effect can effectively avoid the hydraulic pressure from rising to cause the hydraulic cylinder to extend and stop too fast.
As shown in fig. 9e to 9h, when the piston-type hydraulic cylinder is started to contract, the second oil port 103 inputs liquid into the second chamber 101b, the first oil port 102 draws the liquid from the first chamber 101a, at this time, the piston 21 is located at the foremost end of the cylinder cavity 101, the second chamber 101b has almost no liquid, the other port of the second oil passage 213 faces the second oil port 103, and the liquid input by the second oil port 103 needs to pass through the second oil passage 213 and the at least one buffer passage 211 to reach the second chamber 101b, so that the flow rate is slow, and the buffer effect can effectively avoid hydraulic pressure from rising suddenly to cause the hydraulic cylinder to start to contract too fast; when the other port of the second oil passage 213 leaves the second oil port 103, the liquid input from the second oil port 103 directly reaches the second chamber 101b, and continues to push the piston 21 to move; as the piston moves, the first oil port 102 gradually approaches the first oil port 102; when the piston 21 reaches the rearmost end of the cylinder cavity 101, the second oil port 103 stops inputting liquid into the second chamber 101b, the first oil port 102 stops extracting liquid from the first chamber 101a, at this time, the other port of the first oil passage 212 faces the first oil port 102, and the remaining liquid in the first chamber 101a needs to pass through at least one buffer passage 211 and the first oil passage 212 to be extracted from the first oil port 102, so that the flow rate is slow, and the buffer effect can effectively avoid hydraulic pressure from rising suddenly to cause the hydraulic cylinder to contract and stop too fast.
The above-described embodiments are merely preferred examples of the present invention, and not intended to limit the scope of the invention, so that equivalent changes or modifications in the structure, features and principles of the invention described in the claims should be included in the claims.
Claims (10)
1. A hydraulic cylinder with an explosion-proof buffer function comprises: the cylinder body subassembly with can be relatively the movable assembly that the cylinder body subassembly removed, the cylinder body subassembly has cylinder chamber and first hydraulic fluid port, first hydraulic fluid port and cylinder chamber intercommunication, the movable assembly includes: piston and piston rod, the piston rod forms fixedly with the piston, the piston is located the inside of cylinder chamber, and the piston divides cylinder chamber into first cavity and second cavity, its characterized in that: the piston is provided with a plurality of buffer passages, and the first chamber and the second chamber are communicated through the buffer passages.
2. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 1, characterized in that: the cross sections of the cylinder cavity and the buffer channel are circular, and the inner diameter of the cylinder cavity is more than 20 times of that of the buffer channel.
3. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 1, characterized in that: the buffer channel has a first port facing the first chamber and a second port facing the second chamber.
4. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 3, characterized in that: the piston is also provided with a first oil path channel which is communicated with the plurality of buffer channels, and when the piston is positioned at the rearmost end of the cylinder cavity, the first oil path channel is communicated with the first oil port.
5. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 4, wherein: the movable assembly further comprises: the sealing elements are used for respectively plugging the buffer channels.
6. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 5, characterized in that: the sealing element is a machine meter screw, one or two of the two ports of the buffer channel are provided with internal threads, and the machine meter screw is meshed with the internal threads in the ports of the buffer channel.
7. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 5, characterized in that: the cylinder body assembly is also provided with a second oil port which is more front than the first oil port; the piston is further provided with a second oil path channel which is more front than the first oil path channel and is communicated with a plurality of other buffer channels, when the piston is positioned at the foremost end of the cylinder cavity, the second oil path channel is communicated with a second oil port, a second port of the buffer channel communicated with the first oil path channel is blocked by a sealing element, and a first port of the buffer channel communicated with the second oil path channel is blocked by a sealing adhesive.
8. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 7, characterized in that: the cross sections of the first oil path channel and the second oil path channel are circular, the inner diameter of the cylinder cavity is more than 40 times of the inner diameter of the first oil path channel, and the inner diameters of the first oil path channel and the second oil path channel are equal.
9. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 1, characterized in that: the movable assembly further comprises: the piston oil seal and the piston wear-resistant belt are arranged on the outer side wall of the piston in a surrounding mode, the piston oil seal and the inner side wall of the cylinder cavity form sealing, and the piston wear-resistant belt is in contact with the inner side wall of the cylinder cavity.
10. The hydraulic cylinder with an explosion-proof and shock-absorbing function according to claim 9, characterized in that: the cylinder block assembly further includes: and the sealing piece seals the second oil port.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111314102.7A CN113833715A (en) | 2021-11-08 | 2021-11-08 | Hydraulic cylinder with explosion-proof buffering function |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111314102.7A CN113833715A (en) | 2021-11-08 | 2021-11-08 | Hydraulic cylinder with explosion-proof buffering function |
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| CN113833715A true CN113833715A (en) | 2021-12-24 |
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| CN110307192A (en) * | 2019-07-31 | 2019-10-08 | 娄底市中兴液压件有限公司 | Pressurize oil cylinder |
| CN216077799U (en) * | 2021-11-08 | 2022-03-18 | 东莞市通兴液压科技有限公司 | Hydraulic cylinder with explosion-proof buffering function |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4493659A (en) * | 1980-12-03 | 1985-01-15 | Yamaha Hatsudoki Kabushiki Kaisha | Tilt-lock mechanism |
| JP2004225737A (en) * | 2003-01-20 | 2004-08-12 | Shin Meiwa Ind Co Ltd | Hydraulic cylinder |
| CN201166022Y (en) * | 2008-02-27 | 2008-12-17 | 长沙中联重工科技发展股份有限公司 | Hydraulic pressure accumulator oil cylinder for crane |
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| CN110307192A (en) * | 2019-07-31 | 2019-10-08 | 娄底市中兴液压件有限公司 | Pressurize oil cylinder |
| CN216077799U (en) * | 2021-11-08 | 2022-03-18 | 东莞市通兴液压科技有限公司 | Hydraulic cylinder with explosion-proof buffering function |
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