CN117108584A - Hydraulic piston structure and hydraulic cylinder - Google Patents
Hydraulic piston structure and hydraulic cylinder Download PDFInfo
- Publication number
- CN117108584A CN117108584A CN202311267433.9A CN202311267433A CN117108584A CN 117108584 A CN117108584 A CN 117108584A CN 202311267433 A CN202311267433 A CN 202311267433A CN 117108584 A CN117108584 A CN 117108584A
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- piston
- piston rod
- sleeve
- hydraulic
- cylinder body
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- 238000007789 sealing Methods 0.000 claims abstract description 48
- 238000006073 displacement reaction Methods 0.000 claims abstract description 44
- 230000000903 blocking effect Effects 0.000 claims description 16
- 230000000087 stabilizing effect Effects 0.000 claims description 16
- 125000006850 spacer group Chemical group 0.000 claims description 10
- 238000009434 installation Methods 0.000 claims description 5
- 239000010720 hydraulic oil Substances 0.000 abstract description 33
- 230000000694 effects Effects 0.000 abstract description 3
- 230000006835 compression Effects 0.000 abstract description 2
- 238000007906 compression Methods 0.000 abstract description 2
- 230000008878 coupling Effects 0.000 abstract 1
- 238000010168 coupling process Methods 0.000 abstract 1
- 238000005859 coupling reaction Methods 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 50
- 238000010586 diagram Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 239000007788 liquid Substances 0.000 description 2
- 206010040007 Sense of oppression Diseases 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
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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
-
- 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
-
- 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
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Actuator (AREA)
Abstract
The application provides a hydraulic piston structure and a hydraulic oil cylinder, and relates to the technical field of hydraulic oil cylinders. The hydraulic piston structure comprises a large piston, wherein the large piston comprises a double-layer inner liner, a baffle ring capable of sliding in a sealing manner in the inner liner, an outer piston sleeve and an inner piston sleeve, wherein the outer piston sleeve and the inner piston sleeve are sleeved in the inner liner; the utility model provides a hydraulic cylinder, contains the cylinder body, sealed installs the uide bushing in the cylinder body, sealed slip has big piston rod in the uide bushing, big piston rod sealed rigid coupling in big piston, sealed slip grafting has little piston rod in the big piston rod, sealed grafting has the dabber in the little piston rod, utilizes the inside lining to reduce the compression area of two terminal surfaces of big piston and then reduces the deformation of big piston, utilizes the displacement of backing ring, makes the sealed effect of the piece of outer piston bush and cylinder body better, utilizes big piston rod to drive the displacement of little piston rod and big piston rod self in the cylinder body, forms the double stroke that is located the cylinder body with one side, has reduced occupation to the space.
Description
Technical Field
The application relates to the field of hydraulic cylinders, in particular to a hydraulic piston structure and a hydraulic cylinder.
Background
The traditional double-piston rod type hydraulic cylinder comprises a cylinder body, a piston and a piston rod, wherein cylinder covers are arranged at openings at the left end and the right end of the cylinder body, the piston is arranged in the cylinder body and can axially slide, an inner cavity of the cylinder body is divided into a left cavity and a right cavity which are independent of each other by the piston, a sealing structure is arranged between the piston, the cylinder cover and the inner peripheral wall of the cylinder body to form liquid seal, the piston rod penetrates through the piston and is fixed with the piston, the left end and the right end of the piston rod penetrate out of the cylinder covers at the left end and the right end of the cylinder body respectively and form liquid seal with the cylinder covers, and a left oil port communicated with the left cavity and a right oil port communicated with the right cavity are further arranged on the cylinder body.
Such a double piston rod hydraulic cylinder is disclosed in chinese patent publication No. CN 102493969B.
The piston rod both ends of this kind of pneumatic cylinder run through the cylinder body, can form relative displacement in the cylinder body both sides, but under the limited circumstances of installation space, this kind of pneumatic cylinder is not suitable for, and in this kind of pneumatic cylinder, its piston needs frequent reciprocating displacement, frequent friction between piston lateral wall and the cylinder body inner wall can cause the piston loss to aggravate, reduce the life of piston, and frequent piston receives the high pressure oppression of both ends hydraulic oil moreover to take place deformation, leads to the sealing performance between piston and the cylinder body to decline.
Disclosure of Invention
The present application aims to solve at least one of the technical problems existing in the prior art. Therefore, the application provides a hydraulic piston structure which is arranged in a hydraulic oil cylinder and comprises:
the outer surface of the large piston is in sealing sliding fit with the inner wall of the hydraulic cylinder, and the large piston comprises a double-layer inner liner, a baffle ring capable of sliding in the inner liner in a sealing manner, an outer piston sleeve arranged on the outer side of the inner liner in a sealing manner and an inner piston sleeve arranged on the inner side of the inner liner in a sealing manner;
the outer layer of the lining is provided with a raised displacement cabin, and the outer wall of the baffle ring is in sealing sliding fit with the inner wall of the displacement cabin;
the displacement cabin is uniformly provided with first through holes along the axial direction;
the outer piston sleeve is provided with second through holes corresponding to the first through holes, and the second through holes and the first through holes are staggered;
and a supporting belt is sleeved on the position of the outer piston sleeve, which is provided with the second through hole.
In addition, the hydraulic piston structure and the hydraulic cylinder provided by the embodiment of the application have the following additional technical characteristics:
in some embodiments of the present application, a cavity is provided between the inner liners arranged in a double-layer manner, the cavity is communicated with the displacement cabin, and two ends of the inner liners arranged in a double-layer manner are fixedly connected through uniformly arranged connecting blocks.
In some embodiments of the present application, two sides of the baffle ring are fixedly connected with a blocking ring, and the blocking ring is in sealing sliding fit with the cavity between the inner lining in a double-layer arrangement.
In some embodiments of the present application, a stabilizing block is fixedly connected to a side of the blocking ring, which is far away from the blocking ring, and the stabilizing block is in sliding fit with the cavity seal between the lining in a double-layer arrangement.
In some embodiments of the present application, side grooves are symmetrically arranged on the outer surface of the outer piston sleeve, and a retainer ring is arranged on the side groove in a sealing sleeve manner.
In some embodiments of the present application, inner grooves are arranged between the side grooves which are symmetrically arranged, the second through holes are uniformly arranged on the inner grooves, and supporting belts are sealed and sleeved on the inner grooves.
In some embodiments of the present application, the inner side of the outer piston sleeve is uniformly provided with inner strip-shaped grooves along the axial direction, and the outer surface of the inner piston sleeve is uniformly provided with outer strip-shaped grooves along the axial direction.
In some embodiments of the present application, the inner liner is provided with a stabilizing component, and the stabilizing component includes plugging members symmetrically disposed at two ends of the inner liner and limiting strips uniformly disposed at two sides of the inner liner along an axial direction.
In some embodiments of the application, the closure comprises an annular protrusion fixedly attached to the outer wall of the liner and a side stop ring removably attached to the annular protrusion.
In some embodiments of the present application, the annular protrusion is disposed in an opening on a side facing the end surface of the liner, and an internal thread is disposed in the opening.
In some embodiments of the present application, an external thread portion is provided on a sidewall of the side stop ring, and the external thread portion is in threaded engagement with the internal thread.
In some embodiments of the application, the inner diameter of the side stop ring is no less than the inner diameter of the annular projection and the outer diameter of the side stop ring is no greater than the outer diameter of the outer piston sleeve.
In some embodiments of the present application, the limiting strips on the inner and outer sides of the liner are respectively matched with the inner strip-shaped groove and the outer strip-shaped groove.
On the other hand, the embodiment of the application further provides a hydraulic cylinder, which comprises the hydraulic piston structure and further comprises: the cylinder body, one end of the cylinder body is detachably provided with a cylinder head, the other end of the cylinder head is detachably provided with a cap, and the other end of the cylinder body is detachably provided with a flange;
a guide sleeve is arranged in the cylinder body towards one end of the flange in a sealing manner, a large piston rod is inserted in the guide sleeve in a sealing sliding manner, and one end of the large piston rod, which is far away from the guide sleeve, is fixedly connected with the large piston in a sealing manner;
a rear cover is connected in the large piston rod towards one end of the flange in a sealing way;
a small piston rod is inserted in the large piston rod in a sealing sliding manner;
the small piston rod is internally and hermetically inserted with a mandrel, and one end of the mandrel extends out of the cylinder head and is fixedly connected with the cap through a bolt.
In some specific embodiments of the application, the small piston rod is sealed and sleeved with a small piston towards the outer side of one end of the rear cover, and the small piston is in sealing sliding fit with the inner wall of the large piston rod;
the small piston rod is movably sleeved with a spacer bush towards the outer side of one end of the cylinder head, and the spacer bush is fixedly connected with the inner wall of the large piston rod.
In some embodiments of the present application, an oil port a is arranged at one end of the cylinder body near the guide sleeve, and an oil port B and an oil port C are symmetrically arranged on the cylinder head, wherein the oil port C and the oil port a are positioned at the same side of the cylinder body;
the side of the mandrel, which faces the rear cover, is hollow, and a hole communicated with the oil port C is formed in the side wall of the mandrel;
the oil duct of the oil port B is communicated with the interior of the cylinder body from the end face of the cylinder head towards one end of the inner side of the cylinder body.
According to the hydraulic piston structure and the hydraulic oil cylinder provided by the embodiment of the application, the beneficial effects are that:
the inner lining between the outer piston sleeve and the inner piston sleeve is used for reducing the areas of the two end surfaces of the large piston, so that the compression of the high pressure on the two ends of the large piston is reduced, and the deformation of the large piston possibly caused by the high pressure on the two ends of the large piston is reduced;
the hydraulic oil is input and output in the cylinder body, pressure difference is formed at two sides of the large piston, the baffle ring in the liner is forced to displace in the displacement cabin, so that the hydraulic oil at one side with high pressure is flushed from the displacement cabin to the outer piston sleeve, radial outward pressure is formed on the outer piston sleeve, and the supporting belt sleeved on the outer piston sleeve is forced to be in contact with the inner wall of the cylinder body, so that the sealing effect of the outer piston sleeve and a part of the cylinder body is better;
the large piston rod is utilized to drive the displacement of the small piston rod in the cylinder body to form one stroke, the displacement of the large piston rod in the cylinder body is utilized to form the other stroke, and the double strokes are positioned on the same side of the cylinder body, so that the occupation of space is reduced;
the displacement of the mandrel in the small piston rod can be utilized to adjust the two strokes of the hydraulic cylinder, so that the strokes are accurately controlled.
Additional aspects and advantages of the application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the application.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present application, the drawings that are needed in the embodiments will be briefly described below, it being understood that the following drawings only illustrate some examples of the present application and therefore should not be considered as limiting the scope, and other related drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a side view of a hydraulic ram according to an embodiment of the application at two angles;
FIG. 2 is a two-angle partial structural cross-sectional view of a hydraulic ram according to an embodiment of the application;
FIG. 3 is a front cross-sectional view of a hydraulic ram according to an embodiment of the application;
FIG. 4 is a schematic illustration of the position of a hydraulic piston structure according to an embodiment of the present application;
FIG. 5 is a structural exploded view of a hydraulic piston structure according to an embodiment of the present application;
FIG. 6 is a side view and exploded view of a liner and baffle ring according to an embodiment of the present application;
FIG. 7 is a schematic illustration of the position of a stabilizing assembly according to an embodiment of the present application;
FIG. 8 is an exploded view of the structure of a stabilization assembly in accordance with an embodiment of the present application;
FIG. 9 is a schematic illustration of two states of a stroke of a hydraulic ram according to an embodiment of the application;
fig. 10 is a schematic view of two states of another stroke of a hydraulic cylinder according to an embodiment of the present application.
Icon: 1. a cylinder; 11. a cylinder head; 12. capping; 13. a flange; 14. a guide sleeve; 15. a large piston rod; 16. a rear cover; 17. a small piston rod; 171. a small piston; 172. a spacer bush; 18. a mandrel; 2. a large piston; 21. a lining; 211. a connecting block; 212. a displacement cabin; 213. a first through hole; 22. a baffle ring; 221. blocking rings; 222. a stabilizing block; 23. an outer piston sleeve; 231. a side groove; 232. an inner groove; 233. a second through hole; 234. a retainer ring; 235. a support belt; 236. an inner bar-shaped groove; 24. an inner piston sleeve; 241. an outer bar-shaped groove; 3. a stabilizing assembly; 31. a blocking member; 311. an annular protrusion; 312. an internal thread; 313. a side baffle ring; 314. an external thread portion; 32. and a limit strip.
Detailed Description
The technical solutions in the embodiments of the present application will be described below with reference to the accompanying drawings in the embodiments of the present application.
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present application more apparent, the technical solutions of the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application, and it is apparent that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments, based on the embodiments of the application, which are apparent to those of ordinary skill in the art without inventive faculty, are intended to be within the scope of the application.
In a first aspect, a hydraulic piston structure according to an embodiment of the present application is installed in a hydraulic cylinder.
Specifically, as shown in fig. 1-10, the hydraulic piston structure comprises a large piston 2 with an outer surface in sealing sliding fit with the inner wall of a hydraulic cylinder, wherein the large piston 2 comprises a double-layer inner liner 21, a baffle ring 22 capable of sliding in a sealing manner in the inner liner 21, an outer piston sleeve 23 hermetically sleeved on the outer side of the inner liner 21, and an inner piston sleeve 24 hermetically sleeved on the inner side of the inner liner 21.
As shown in fig. 5 and 6, the outer layer of the double-layer inner liner 21 is provided with a raised displacement cabin 212, and the outer wall of the baffle ring 22 is in sealing sliding fit with the inner wall of the displacement cabin 212, and it can be understood that the baffle ring 22 forms a seal for both ends of the displacement cabin 212.
As shown in fig. 5, the displacement chamber 212 is provided with first through holes 213 uniformly in the axial direction.
Further, the outer piston sleeve 23 is provided with a second through hole 233 corresponding to the first through hole 213, and the second through hole 233 and the first through hole 213 are staggered, and it is understood that the first through hole 213 and the second through hole 233 are not communicated in an initial state.
Wherein, the outer piston sleeve 23 is provided with a second through hole 233 and a supporting belt 235.
As shown in fig. 6, a cavity is formed between the inner liners 21 arranged in a double-layer manner, the cavity is communicated with the displacement cabin 212, two ends of the inner liners 21 arranged in a double-layer manner are fixedly connected through uniformly arranged connecting blocks 211, it is understood that the inner liners 21 arranged in a double-layer manner are independent and integral, the cavity is formed between the inner layers and the outer layers of the inner liners, and the outer layers of the inner liners are provided with the bulge-shaped displacement cabin 212 communicated with the cavity.
Further, two sides of the baffle ring 22 are fixedly connected with a blocking ring 221, and a cavity between the blocking ring 221 and the double-layer lining 21 is in sealing sliding fit.
Wherein, the side of the blocking ring 221 away from the baffle ring 22 is uniformly fixedly connected with a stabilizing block 222, and the stabilizing block 222 is in sealing sliding fit with the cavity between the double-layer lining 21.
It will be appreciated that as can be seen in fig. 6, the sliding fit between the stopper ring 221 and the stabilizing block 222 and the cavity in the liner 21 provides support for the retainer ring 22 to prevent the retainer ring 22 from tipping under pressure within the displacement chamber 212, thereby disabling the closure of the liner 21.
It should be noted that, the lengths of the stabilizing blocks 222 at two sides of the baffle ring 22 are set such that, when the baffle ring 22 is displaced to the middle position of the displacement cabin 212, the stabilizing blocks 222 at two sides are located in the corresponding cavities to support the baffle ring 22, and at this time, the blocking ring 221 is located in the displacement cabin 212 to form communication between the cavities and the displacement cabin 212.
Further, as shown in fig. 5, side grooves 231 are symmetrically arranged on the outer surface of the outer piston sleeve 23, a retainer ring 234 is arranged on the side grooves 231 in a sealing sleeve manner, and the retainer ring 234 provides axial support for the outer piston sleeve 23.
Further, inner grooves 232 are arranged between the side grooves 231 symmetrically, second through holes 233 are uniformly formed in the inner grooves 232, and supporting bands 235 are arranged on the inner grooves 232 in a sealing sleeve mode.
Further, the inner side of the outer piston sleeve 23 is uniformly provided with an inner bar-shaped groove 236 in the axial direction, and the outer surface of the inner piston sleeve 24 is uniformly provided with an outer bar-shaped groove 241 in the axial direction.
The following describes a state change of a hydraulic piston structure in a hydraulic cylinder according to an embodiment of the present application with reference to the accompanying drawings:
when the pressure of hydraulic oil on one side (left side) of the large piston 2 is larger than that on the other side (right side), the large piston 2 is wholly displaced to one side with small pressure (right side) in the hydraulic cylinder, in order to facilitate understanding, in the embodiment of the application, the left side pressure is large, and the baffle ring 22 slides in the displacement cabin 212 in a sealing way, so the baffle ring 22 is displaced to the right side of the displacement cabin 212 under the action of pressure difference until the baffle ring 22 abuts against the right side of the displacement cabin 212, at this time, the left side cavity is communicated with the displacement cabin 212, the left side hydraulic oil enters the displacement cabin 212 from the cavity at the left end of the liner 21, and applies radial outward pressure to the outer piston sleeve 23 sleeved on the liner 21 through the first through holes 213 uniformly arranged on the displacement cabin 212 in the axial direction, and the position of the outer piston sleeve 23 corresponding to the first through holes 213 is provided with a supporting belt 235, the outer piston sleeve 23 is acted by hydraulic oil pressure to have radial outward deformation trend, so that radial outward expansion force is provided for the support belt 235, so that the support belt 235 has radial outward deformation force, meanwhile, because the outer piston sleeve 23 is provided with the second through holes 233 which are staggered with the first through holes 213, part of hydraulic oil passes through the second through holes 233 to provide radial outward pressure for the support belt 235, the support belt 235 is further promoted to have comprehensive radial outward deformation force, so that good sealing sliding fit is formed between the support belt 235 and the inner wall of the hydraulic cylinder, and because the support belt 235 is positioned in the inner groove 232 of the outer piston sleeve 23, the inner groove 232 has axial sealing performance with the support belt 235 when the end surface of the outer piston sleeve 23 is extruded by hydraulic oil, thereby integrally enhancing the sealing performance between the large piston 2 and the inner wall of the hydraulic cylinder, and the phenomenon that the sealing performance between the outer piston sleeve 23 and the inner wall of the hydraulic cylinder is reduced when the outer piston sleeve 23 and the inner wall of the hydraulic cylinder are worn due to frequent reciprocating displacement is avoided.
In a second aspect, an embodiment of the present application further provides a hydraulic cylinder, including the hydraulic piston structure described above.
In the related art, the two ends of the piston rod of the existing double-piston rod hydraulic cylinder penetrate the hydraulic cylinder, and relative displacement is formed at the two ends of the hydraulic cylinder, however, the mode is not suitable for the environment with limited installation space, and the specific displacement stroke cannot be adjusted.
According to some embodiments of the present application, as shown in fig. 1-3 and fig. 9-10, the hydraulic ram comprises:
the cylinder body 1, one end of the cylinder body 1 is detachably provided with a cylinder head 11, the other end of the cylinder head 11 is detachably provided with a cap 12, and the other end of the cylinder body 1 is detachably provided with a flange 13;
a guide sleeve 14 is arranged at one end, facing the flange 13, of the cylinder body 1, a large piston rod 15 is inserted in the guide sleeve 14 in a sealing sliding manner, and one end, far away from the guide sleeve 14, of the large piston rod 15 is fixedly connected with the large piston 2 in a sealing manner.
The large piston rod 15 is hollow.
Wherein, one end of the large piston rod 15 facing the flange 13 is hermetically connected with a rear cover 16, and one end of the large piston rod 15 is plugged;
as shown in fig. 2-3, the large piston rod 15 is internally and slidably connected with the small piston rod 17 in a sealing manner, and it is understood that a sealing cavity is formed between the small piston rod 17 and the end of the large piston rod 15 where the rear cover 16 is mounted.
A mandrel 18 is inserted in the small piston rod 17 in a sealing manner, one end of the mandrel 18 extends out of the cylinder head 11 and is fixedly connected to the cap 12 through a bolt, and it should be noted that the bolt is in threaded fit with the mandrel 18, so that when the bolt is rotated, the mandrel 18 is enabled to displace corresponding to the cap 12.
The small piston rod 17 and the mandrel 18 slide in a limited manner.
Wherein, the small piston rod 17 is sealed and sleeved with a small piston 171 towards the outer side of one end of the rear cover 16, and the small piston 171 is in sealed sliding fit with the inner wall of the large piston rod 15;
the outer side of one end of the small piston rod 17 facing the cylinder head 11 is movably sleeved with a spacer 172, and the spacer 172 is fixedly connected with the inner wall of the large piston rod 15.
Further, an oil port A is arranged at one end, close to the guide sleeve 14, of the cylinder body 1, an oil port B and an oil port C are symmetrically arranged on the cylinder head 11, and the oil port C and the oil port A are positioned at the same side of the cylinder body 1;
the side of the mandrel 18 facing the rear cover 16 is hollow, wherein a hole communicated with the oil port C is arranged on the side wall of the mandrel 18;
the oil passage of the oil port B communicates with the interior of the cylinder 1 from the end surface of the cylinder head 11 toward the inner end of the cylinder 1.
As shown in fig. 3, the distance between the spacer 172 and the small piston 171 is smaller than the distance between the large piston 2 and the guide sleeve 14.
It should be further noted that the connection position of the oil port a on the cylinder 1 is not blocked by the guide sleeve 14.
It should be further noted that the small piston 171 has the same structure as the large piston 2, and only has a different size to enhance the service life of the small piston 171.
Thus, in the first embodiment, as shown in the upper diagram of fig. 9, the oil port C is closed by the external device, the oil port a and the oil port B are opened, and hydraulic oil is injected into the oil port a, at this time, the oil pressure at the oil port a is greater than the oil pressure at the oil port B, so that under the pressure effect of the hydraulic oil, the large piston 2 will drive the large piston rod 15 to displace in the right direction, and the hydraulic oil in the cavity where the right side of the large piston 2 is communicated with the oil port B is discharged from the oil port B, whereas, as shown in the lower diagram of fig. 9, when hydraulic oil is injected into the cylinder 1 from the oil port B, at this time, the oil pressure at the oil port B is greater than the oil pressure at the oil port a, the hydraulic oil will provide a pressure pushing to the large piston 2 to the left side, and the hydraulic oil in the cavity at the right side of the large piston 2 will rush into the large piston rod 15 from the gap between the spacer 172 and the small piston rod 17, and the small piston 171 will provide a pressure displacing to the left side, and it is necessary to say that, at this time, the pressure value of the pressure applied to the right end face of the small piston 171 is greater than the negative pressure value formed inside the small piston rods 17 and 18 when they displace to the left side, and the small piston rod 17 and 18, at this time, the small piston rod 17 and the right end face and the piston rod 15 will be displaced to the left side and the piston rod end face and the piston rod 2 will be further displaced to the piston rod 2 is more and the piston rod end face to the piston side;
in the second embodiment, as shown in fig. 10, the oil port a is an oil filling port, the oil port B is closed, the oil port C is an oil outlet, the cavity of the cylinder body 1 on the right end face of the large piston 2 is in a vacuum state at this time, and negative pressure is provided, so that the left end faces of the small piston rod 17 and the small piston 171 are subjected to the pressure of the hydraulic oil in the cavity of the large piston rod 15 near one end of the rear cover 16 to provide rightward displacement, and simultaneously the right end face of the small piston 171 is subjected to the negative pressure in the cavity of the right side of the large piston 2 to receive the suction force of rightward displacement, so that the small piston rod 17 is positioned at the extreme right end of the self stroke, at this time, the oil port a is filled with hydraulic oil, the large piston 2 is subjected to the action of the left hydraulic oil, the large piston 2 drives the large piston rod 15 to displace rightward, during the displacement, the cavity of the large piston rod 15 is reduced in volume on the side of the large piston rod 15 where the rear cover 16 is installed, the hydraulic oil in the cavity is discharged to the oil port C via the small piston rod 17 and the mandrel 18, and the hydraulic oil is discharged from the oil port C, whereas when the oil port C is an oil filling port, the oil port A is an oil outlet, and hydraulic oil is injected into the cylinder body 1, the hydraulic oil is conveyed into a cavity on one side of the large piston rod 15, where the rear cover 16 is arranged, through the mandrel 18 and the small piston rod 17, under the action of the oil pressure, the large piston rod 15 is pushed to drive the large piston 2 to move leftwards, and the hydraulic oil on the left end face of the large piston 2 is discharged from the oil port A, in the process, the left end faces of the small piston rod 17 and the small piston 171 are subjected to the pressure exerted by the hydraulic oil, and the small piston rod 17 is kept to be always positioned at the rightmost end of the stroke.
In sum, through the opening, closing, input and output changes of the three oil ports, the hydraulic oil cylinder can have two different strokes on the same side;
as shown in the upper diagram of fig. 10, it should be noted that, the small piston rod 17 and the mandrel 18 slide in a limited manner, that is, when the small piston rod 17 is located at the rightmost end of the stroke of the small piston rod 17 and the mandrel 18 in the diagram form, the small piston rod 17 is driven to change the position of the small piston rod 17 in the cylinder 1 by rotating the bolt on the cap 12 to adjust the position of the mandrel 18 in the cylinder 1, it is understood that, as shown in fig. 10, when the mandrel 18 is displaced leftwards, the small piston rod 17 is driven to be displaced leftwards, and then the distance between the spacer 172 and the small piston 171 is increased, that is, in the second embodiment, the displacement stroke of the large piston rod 15 is increased, and in the first embodiment, the distance between the large piston 2 and the guide sleeve 14 is reduced due to the leftwards displacement of the small piston rod 17, and then the displacement stroke of the large piston rod 15 is reduced, so that, it is understood that the stroke adjustable design of the hydraulic cylinder is realized by adjusting the specific position of the mandrel 18 and the on-off change of three oil ports.
In the related art, in the hydraulic piston structure, due to the design of matching the double-layer piston sleeve with the inner liner 21, the influence of the pressure caused by hydraulic oil on the end face of the outer piston sleeve 23 is reduced, and the radially outward pressure is provided for the outer piston sleeve 23, so that the tightness between the large piston 2 and the inner wall of the cylinder body 1 is enhanced, but due to the reduction of the end face area, the thickness of the end face of the outer piston sleeve 23 is reduced, and deformation is more easily caused by the end face pressure, so that stronger abrasion can be generated between the end face and the cylinder body 1, and the service life of the outer piston sleeve 23 is reduced.
According to some embodiments of the present application, as shown in fig. 7 and 8, the inner liner 21 is provided with a stabilizing assembly 3, and the stabilizing assembly 3 includes blocking members 31 symmetrically disposed at two ends of the inner liner 21 and limiting bars 32 uniformly disposed at two inner and outer sides of the inner liner 21 in an axial direction.
Wherein, the blocking member 31 comprises an annular protrusion 311 fixedly connected to the outer wall of the liner 21 and a side blocking ring 313 detachably connected to the annular protrusion 311, so as to facilitate the installation and replacement of the outer piston sleeve 23 on the liner 21.
Specifically, the annular protrusion 311 is disposed in an opening on a side facing the end surface of the liner 21, and an internal thread 312 is disposed in the opening.
Further, an external thread portion 314 is provided on a side wall of the side stopper 313, and the external thread portion 314 is screw-engaged with the internal thread 312.
In this way, fixing and detachment between the side fence 313 and the annular projection 311 can be achieved.
Wherein the inner diameter of the side stopper ring 313 is not smaller than the inner diameter of the annular projection 311, and the outer diameter of the side stopper ring 313 is not larger than the outer diameter of the outer piston sleeve 23, it will be understood that the side stopper ring 313 covers the end face of the outer piston sleeve 23.
Further, the limiting strips 32 on the inner side and the outer side of the liner 21 are respectively matched with the inner strip-shaped groove 236 and the outer strip-shaped groove 241, and it can be understood that the limiting strips 32 play a role in axially positioning the outer piston sleeve 23 and the inner piston sleeve 24, so that the two sealing sleeves are prevented from rotating on the liner 21, and the sealing performance and the original dislocation relation between the first through hole 213 and the second through hole 233 are prevented from being influenced.
Therefore, when the piston is specifically used, through the threaded matching relationship between the side baffle rings 313 and the corresponding annular protrusions 311 on two sides, the two side baffle rings 313 can be installed and detached, so that the installation or replacement of the outer piston sleeve 23 is more convenient, meanwhile, it can be understood that when hydraulic oil on two sides of the large piston 2 presses two end faces of the large piston 2 respectively, the pressure of the hydraulic oil is directly applied to the side baffle rings 313, the rear side baffle rings 313 transmit the pressure to the large piston rod 15 through the inner piston sleeve 24, and then the large piston rod 15 is driven to displace, specifically, the side baffle rings 313 can be designed to cover the inner piston sleeve 24, and through holes are formed at the positions of cavities at two ends of the covering inner liner 21, so that the hydraulic oil does not influence the hydraulic oil to enter the displacement cabin 212, and meanwhile, the inner piston sleeve 24 and the end faces of the outer piston sleeve 23 can be better prevented from being pressed, and the inner piston sleeve 24 and the outer piston sleeve 23 can be prevented from rotating axially by the plurality of limiting bars 32 arranged on the inner surface and the outer surface of the inner liner 21, and the inner piston sleeve 24 and the outer piston sleeve 23 can be prevented from being influenced by the wear and the first through holes 233 and the second through holes 213.
It should be noted that, specific model specifications of the cylinder body 1, the cylinder head 11, the cap 12, the flange 13, the guide sleeve 14, the rear cover 16 and the mandrel 18 need to be determined by selecting a model according to actual specifications of the device, and a specific model selection calculation method adopts the prior art in the field, so detailed description is omitted.
The foregoing is merely illustrative embodiments of the present application, but the scope of the present application is not limited thereto, and any person skilled in the art can easily think about variations or substitutions within the technical scope of the present application, and the application should be covered. Therefore, the protection scope of the application is subject to the protection scope of the claims.
Claims (10)
1. A hydraulic piston structure for installation in a hydraulic ram, comprising:
the outer surface of the large piston (2) is in sealing sliding fit with the inner wall of the hydraulic cylinder, the large piston (2) comprises a double-layer inner liner (21), a baffle ring (22) capable of sliding in the inner liner (21), an outer piston sleeve (23) hermetically sleeved on the outer side of the inner liner (21) and an inner piston sleeve (24) hermetically sleeved on the inner side of the inner liner (21);
wherein, the outer layer of the lining (21) is provided with a raised displacement cabin (212), and the outer wall of the baffle ring (22) is in sealed sliding fit with the inner wall of the displacement cabin (212);
the displacement cabin (212) is uniformly provided with first through holes (213) along the axial direction;
the outer piston sleeve (23) is provided with a second through hole (233) corresponding to the first through hole (213), and the second through hole (233) and the first through hole (213) are arranged in a staggered manner;
and a supporting belt (235) is sleeved at the position of the outer piston sleeve (23) provided with the second through hole (233).
2. A hydraulic piston structure as defined in claim 1, wherein: a cavity is arranged between the inner liners (21) which are arranged in a double-layer mode, the cavity is communicated with the displacement cabin (212), and two ends of the inner liners (21) which are arranged in a double-layer mode are fixedly connected through connecting blocks (211) which are uniformly arranged.
3. A hydraulic piston structure as defined in claim 2, wherein: the two sides of the baffle ring (22) are fixedly connected with blocking rings (221), and the cavity between the blocking rings (221) and the lining (21) which is arranged in a double-layer manner is in sealing sliding fit.
4. A hydraulic piston structure as claimed in claim 3, wherein: one side of the blocking ring (221) far away from the baffle ring (22) is uniformly fixedly connected with a stabilizing block (222), and the stabilizing block (222) is in sealing sliding fit with a cavity between the lining (21) which is arranged in a double-layer manner.
5. A hydraulic piston structure as defined in claim 1, wherein: side grooves (231) are symmetrically formed in the outer surface of the outer piston sleeve (23), and check rings (234) are arranged on the side grooves (231) in a sealing sleeve mode.
6. A hydraulic piston structure as defined in claim 5, wherein: an inner groove (232) is formed between the side grooves (231) which are symmetrically arranged, the second through holes (233) are uniformly formed in the inner groove (232), and a supporting belt (235) is arranged on the inner groove (232) in a sealing sleeve mode.
7. A hydraulic piston structure as defined in claim 1, wherein: an inner strip-shaped groove (236) is uniformly arranged on the inner side of the outer piston sleeve (23) along the axial direction, and an outer strip-shaped groove (241) is uniformly arranged on the outer surface of the inner piston sleeve (24) along the axial direction.
8. A hydraulic ram comprising a hydraulic piston structure according to any one of claims 1-7, further comprising:
the cylinder comprises a cylinder body (1), wherein a cylinder head (11) is detachably arranged at one end of the cylinder body (1), a cap (12) is detachably arranged at the other end of the cylinder head (11), and a flange (13) is detachably arranged at the other end of the cylinder body (1);
a guide sleeve (14) is arranged in the cylinder body (1) towards one end of the flange (13) in a sealing manner, a large piston rod (15) is inserted in the guide sleeve (14) in a sealing sliding manner, and one end, away from the guide sleeve (14), of the large piston rod (15) is fixedly connected with the large piston (2) in a sealing manner;
a rear cover (16) is connected in the large piston rod (15) towards one end of the flange (13) in a sealing way;
a small piston rod (17) is inserted in the large piston rod (15) in a sealing sliding manner;
a mandrel (18) is inserted in the small piston rod (17) in a sealing way, and one end of the mandrel (18) extends out of the cylinder head (11) and is fixedly connected to the cap (12) through a bolt.
9. A hydraulic ram as defined in claim 8, wherein: a small piston (171) is arranged on the outer side of one end, facing the rear cover (16), of the small piston rod (17) in a sealing and sliding fit with the inner wall of the large piston rod (15);
the small piston rod (17) is movably sleeved with a spacer sleeve (172) towards the outer side of one end of the cylinder head (11), and the spacer sleeve (172) is fixedly connected with the inner wall of the large piston rod (15).
10. A hydraulic ram as defined in claim 8, wherein: an oil port A is formed in one end, close to the guide sleeve (14), of the cylinder body (1), an oil port B and an oil port C are symmetrically formed in the cylinder head (11), and the oil port C and the oil port A are located on the same side of the cylinder body (1);
the side of the mandrel (18) facing the rear cover (16) is hollow, and a hole communicated with the oil port C is formed in the side wall of the mandrel (18);
the oil passage of the oil port B is communicated with the interior of the cylinder body (1) from the end face of the cylinder head (11) facing the inner side end of the cylinder body (1).
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| CN202311267433.9A CN117108584B (en) | 2023-09-28 | 2023-09-28 | Hydraulic piston structure and hydraulic cylinder |
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| CN202311267433.9A CN117108584B (en) | 2023-09-28 | 2023-09-28 | Hydraulic piston structure and hydraulic cylinder |
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| CN117108584B (en) | 2024-02-27 |
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