CN215762570U

CN215762570U - Speed adjustable bidirectional buffer hydraulic cylinder

Info

Publication number: CN215762570U
Application number: CN202122074857.6U
Authority: CN
Inventors: 李江烨; 杨星辉
Original assignee: Sanhe Oil Cylinder Changzhou Co ltd
Current assignee: Sanhe Oil Cylinder Changzhou Co ltd
Priority date: 2021-08-30
Filing date: 2021-08-30
Publication date: 2022-02-08
Anticipated expiration: 2031-08-30

Abstract

The utility model relates to a speed-adjustable bidirectional buffer hydraulic cylinder which comprises a cylinder barrel, a front end cover, a rear end cover, a piston rod and a piston, wherein a buffer lantern ring attached to the front end surface of the piston and a buffer nut attached to the rear end surface of the piston are installed on the piston rod, a one-way valve for communicating a rear cavity with a rear buffer cavity when the piston rod moves forward and a throttle valve for adjusting the speed of the buffer nut entering the rear buffer cavity when the piston rod moves back are installed in the rear end cover in the radial direction, a throttle valve for adjusting the speed of the buffer lantern ring entering the front buffer cavity when the piston rod moves forward and a one-way valve for communicating the front cavity with the front buffer cavity when the piston rod moves back are installed in the front end cover in the radial direction. According to the utility model, the check valve and the throttle valve are respectively arranged in the front end cover and the rear end cover, the check valve is utilized to provide initial thrust at the moment of starting the piston rod, and the throttle valve is used to adjust the size of the oil return gap so as to realize control of the buffering speed, so that the practicability of the hydraulic cylinder is improved.

Description

Speed adjustable bidirectional buffer hydraulic cylinder

Technical Field

The utility model relates to the technical field of hydraulic oil cylinders, in particular to a speed-adjustable bidirectional buffer hydraulic cylinder.

Background

In order to reduce the impact on a cylinder body and a sealing element when a piston rod moves to a stroke end point, a buffer structure is generally arranged in a hydraulic cylinder, the existing hydraulic cylinder is mainly subjected to hole-shaft tolerance fit by manufacturing a buffer part and inner holes of front and rear cylinder covers, mechanical buffer is realized, and the situations of friction heating inside the cylinder body of the hydraulic cylinder, noise and sealing ring failure caused by internal temperature rise easily occur in actual application; and after a period of use, the materials of the internal parts are easily abraded due to friction, so that the buffering effect is not obvious.

The structure of the existing hydraulic cylinder with adjustable buffering speed is complex, more structural parts and accessories need to be added inside or outside the hydraulic cylinder, and the occupied space is large. The operation is more loaded down with trivial details when using, and is used limitedly in some special application occasions, for example die casting machine, injection molding machine etc. because the mould is complicated, and the space is limited, needs the more simple, compact pneumatic cylinder of structure.

Disclosure of Invention

The technical problem to be solved by the utility model is as follows: in order to overcome the defects in the prior art, the utility model provides the speed-adjustable bidirectional buffer hydraulic cylinder with a compact structure, and the buffer speed can be adjusted and controlled on the basis of realizing bidirectional buffering of the oil cylinder so as to meet the use under complex working conditions.

The technical scheme adopted by the utility model for solving the technical problems is as follows: the utility model provides a two-way buffering pneumatic cylinder with adjustable speed, includes cylinder, front end housing, rear end housing, piston rod and piston, the piston rod on install the cushion collar of laminating piston front end face, the cushion nut of laminating piston rear end face, the first hydraulic fluid port of intercommunication pneumatic cylinder front chamber is seted up to the outer wall on the front end housing, the second hydraulic fluid port of intercommunication pneumatic cylinder rear chamber is seted up to the rear end housing outer wall, front end housing center set up with cushion collar matched with preceding cushion chamber, rear end housing center set up with cushion nut matched with back cushion chamber, preceding cushion chamber intercommunication first hydraulic fluid port, back cushion chamber intercommunication second hydraulic fluid port, rear end housing in radially install the check valve of putting through back chamber and back cushion chamber when the piston rod moves forward, adjust the choke valve of the antedisplacement speed when the cushion nut gets into back cushion chamber when the piston rod moves back, the front end housing in radially install the choke valve of speed when the piston rod when adjusting the cushion collar and get into preceding cushion chamber, When the piston rod retracts, the check valve of the front cavity and the front buffer cavity is communicated.

Furthermore, two first axial oil ducts communicated with the front cavity are arranged in the front end cover, a first radial hole and a second radial hole are formed in the front end cover, the outer end portion of the front end cover is provided with an internal thread, the first axial oil ducts are vertically communicated with the first radial hole and the second radial hole respectively, and the inner ends of the first radial hole and the second radial hole are communicated with the front buffer cavity in a shrinkage mode.

Furthermore, two second axial oil ducts communicated with the rear cavity are arranged in the rear end cover, a first radial hole and a second radial hole are formed in the rear end cover, the outer end portion of the first radial hole and the outer end portion of the second radial hole are provided with internal threads, the second axial oil ducts are vertically communicated with the first radial hole and the second radial hole respectively, and the inner ends of the first radial hole and the second radial hole are communicated with the rear buffer cavity in a shrinkage mode.

Specifically, the check valve comprises a steel ball and a spring, the steel ball is arranged in the first radial hole and sealed with a conical hole line at the contraction position, the spring is arranged in the first radial hole, the inner end of the spring applies force to the steel ball, and the outer end part of the first radial hole is in threaded connection with an inner hexagonal plug which is pressed against the outer end of the spring.

Specifically speaking, the choke valve include the hexagon socket head cap taper valve, hexagon socket head cap taper valve and the radial outer end threaded connection in second, the pointed cone portion card of hexagon socket head cap taper valve is in the aperture after the second radial hole shrink, hexagon socket head cap taper valve outer end threaded connection has lock nut.

In order to better improve the initial force of the piston rod during retraction, the inner end face of the front end cover is provided with a first groove surrounding the periphery of the front buffer cavity, and the first axial oil duct is communicated with the first groove.

In order to better improve the initial force of the piston rod during extending, the inner end face of the rear end cover is provided with a second groove surrounding the periphery of the rear buffer cavity, and the second axial oil duct is communicated with the second groove.

The utility model has the beneficial effects that: according to the hydraulic cylinder, the check valve and the throttle valve are respectively arranged in the front end cover and the rear end cover, the check valve is used for providing initial thrust when the piston rod is started, the throttle valve is used for adjusting the size of an oil return gap to realize control of the buffering speed, the hydraulic cylinder is compact in internal structure, small in occupied space, more suitable for being used in occasions with limited installation and operation space, and the practicability of the hydraulic cylinder is improved.

Drawings

The utility model is further described with reference to the following figures and embodiments.

Fig. 1 is a schematic view of the piston rod of the present invention when it is not extended.

Fig. 2 is a schematic view of the piston rod of the present invention after it is extended.

Fig. 3 is an enlarged schematic view of a structure at a in fig. 1.

Fig. 4 is an enlarged schematic view of B in fig. 2.

In the figure: 1. the hydraulic cylinder comprises a cylinder barrel, 2, a front end cover, 3, a rear end cover, 4, a piston rod, 5, a piston, 6, a buffer lantern ring, 7, a buffer nut, 8, a front chamber, 9, a first oil port, 10, a rear chamber, 11, a second oil port, 12, a front buffer chamber, 13, a rear buffer chamber, 14, a first axial oil duct, 15, a first groove, 16, a first radial hole, 17, a second radial hole, 18, a second axial oil duct, 19, a second groove, 20, a steel ball, 21, a spring, 22, an inner hexagonal plug, 23, an inner hexagonal cone valve, 24, a locking nut, 25, a flange and 26.

Detailed Description

The present invention will now be described in further detail with reference to the accompanying drawings. These drawings are simplified schematic views illustrating only the basic structure of the present invention in a schematic manner, and thus show only the constitution related to the present invention.

As shown in fig. 1 to 4, the speed-adjustable bidirectional buffer hydraulic cylinder comprises a cylinder barrel 1, a front end cover 2 fixed on the front end face of the cylinder barrel 1, a rear end cover 3 fixed on the rear end face of the cylinder barrel 1, a piston rod 4 and a piston 5, wherein the piston 5 of the front end cover 2 is fixedly connected with the piston rod 4, the periphery of the piston 5 is in sliding fit with the inner wall of the cylinder barrel 1, a flange 25 is fixed on the outer end face of the front end cover 2, and a guide sleeve 26 in sliding fit with the piston rod 4 is installed in an inner hole of the flange 25.

Piston rod 4 on install the cushion collar 6 of laminating piston 5 preceding terminal surface, the cushion nut 7 of laminating piston 5 rear end face, set up the first hydraulic fluid port 9 of intercommunication pneumatic cylinder front chamber 8 on 2 perisporium of front end housing, set up the second hydraulic fluid port 11 of intercommunication pneumatic cylinder rear chamber 10 on 3 perisporium of rear end housing, 2 interior terminal surface centers of front end housing set up with cushion collar 6 matched with preceding

cushion chamber

12, 3 interior terminal surface centers of rear end housing set up with cushion nut 7 matched with back cushion chamber 13, the outer face of cylinder of cushion collar 6 and cushion nut 7 on all be equipped with the circular conical surface of one end circular arc transition to be favorable to more that cushion collar 6 gets into preceding cushion chamber 12, cushion nut 7 gets into back cushion chamber 13, avoid producing collision and impact. The front buffer cavity 12 is communicated with the first oil port 9, and the rear buffer cavity 13 is communicated with the second oil port 11.

The rear end cover 3 is internally and radially provided with a one-way valve which is used for connecting the rear cavity 10 with the rear buffer cavity 13 when the piston rod 4 moves forwards and stretches out, and a throttle valve which is used for adjusting the speed of the buffer nut 7 entering the rear buffer cavity 13 when the piston rod 4 returns, and the front end cover 2 is internally and radially provided with a throttle valve which is used for adjusting the speed of the buffer sleeve ring 6 entering the front buffer cavity 12 when the piston rod 4 moves forwards and a one-way valve which is used for connecting the front cavity 8 with the front buffer cavity 12 when the piston rod 4 returns.

Specifically, two first axial oil passages 14 communicated with the front cavity 8 are arranged in the front end cover 2, a first groove 15 surrounding the periphery of the front buffer cavity 12 is formed in the inner end surface of the front end cover 2, and the first axial oil passages 14 are communicated with the first groove 15; a first radial hole 16 and a second radial hole 17 with internal threads at the outer end parts are formed in the front end cover 2, the first axial oil passage 14 is vertically communicated with the first radial hole 16 and the second radial hole 17 respectively, and the inner ends of the first radial hole 16 and the second radial hole 17 are communicated with the front buffer cavity 12 in a shrinkage mode.

The rear end cover 3 is internally provided with two second axial oil channels 18 communicated with the rear cavity 10, the inner end surface of the rear end cover 3 is provided with a second groove 19 surrounding the periphery of the rear buffer cavity 13, and the second axial oil channels 1 are communicated with the second groove 19; a first radial hole 16 and a second radial hole 17 with internal threads at the outer end part are formed in the rear end cover 3, a second axial oil passage 18 is vertically communicated with the first radial hole 16 and the second radial hole 17 respectively, and the inner ends of the first radial hole 16 and the second radial hole 17 are communicated with the rear buffer cavity 13 in a shrinkage mode.

The check valve comprises a steel ball 20 and a spring 21, the steel ball 20 is arranged in the first radial hole 16 and sealed with a conical hole line at the contraction position, the spring 21 is arranged in the first radial hole 16, the inner end of the spring 21 applies force on the steel ball 20, and the outer end part of the first radial hole 16 is in threaded connection with an inner hexagonal plug 22 which is pressed against the outer end of the spring 21.

The throttling valve comprises an inner hexagonal cone valve 23, the inner hexagonal cone valve 23 is in threaded connection with the outer end of the second radial hole 17, a sharp cone portion of the inner hexagonal cone valve 23 is clamped in a small hole formed after the second radial hole 17 is contracted, and the outer end of the inner hexagonal cone valve 23 is in threaded connection with a locking nut 24. The screwing depth of the external thread of the inner hexagonal cone valve 23 is adjusted, the gap between the pointed cone part of the inner hexagonal cone valve 23 and the small hole after the second radial hole 17 is shrunk can be controlled, the flow of the hydraulic oil flowing from the first axial oil passage 14 to the front buffer cavity 12 and the flow of the hydraulic oil flowing from the second axial oil passage 18 to the rear buffer cavity 13 are adjusted, and the locking nut 24 is screwed down after the adjustment is finished to lock the inner hexagonal cone valve 23.

The working principle is briefly described as follows:

when the piston rod 4 is in an initial state, the initial pressure in the rear cavity 10 is zero and the area is about zero, hydraulic oil enters from the second oil port 11 to fill the rear buffer cavity 13, the pressure of the rear buffer cavity 13 rises, when the pressure is greater than the pressure of a spring 21 of a check valve in the rear end cover 3, the steel ball 20 is jacked open, the check valve in the rear end cover 3 is opened, the hydraulic oil enters the rear cavity 10 through the second axial oil passage 18 through the second groove 19, and the initial force is provided for pushing the piston rod 4 to extend outwards through the areas of the rear buffer cavity 13 and the second groove 19; when the pressure in the rear chamber 10 is equal to that in the rear buffer chamber 13, the steel ball 20 is reset under the action of the spring 21, the one-way valve is closed, and the one-way valve only plays a role at the moment when the piston rod 4 extends and starts.

In the process that the piston rod 4 extends out, hydraulic oil in the front cavity 8 is discharged from the first oil port 9 through the front buffer cavity 12, when the buffer lantern ring 6 enters the front buffer cavity 12 of the front end cover 2, an oil return path is blocked, the hydraulic oil in the front cavity 8 can only enter the front buffer cavity 12 through the first axial oil duct 14 and then is discharged through the first oil port 9, and the throttling buffer effect is realized by adjusting an oil return gap between the inner hexagonal cone valve 23 of the throttling valve and the first axial oil duct 14, so that the hydraulic oil generates a force resisting against the output force of the piston rod 4 in the front cavity 8; the control of the buffering speed can be realized by adjusting the size of the oil return gap, the larger the gap is, the less obvious the buffering effect is, and the larger the buffering speed is; on the contrary, the smaller the gap, the better the buffering effect and the smaller the buffering speed. When the front end face of the piston 5 contacts the inner end face of the front end cover 2, the extending process of the piston rod 4 is stopped.

When the piston rod 4 retracts, hydraulic oil enters from the first oil port 9, the check valve in the front end cover 2 is opened, the initial area is increased, the retraction process of the piston rod 4 starts, the hydraulic oil in the rear cavity 10 is discharged from the second oil port 11 through the rear buffer cavity 13, when the buffer nut 7 enters the rear buffer cavity 13, an oil return path is blocked, the hydraulic oil in the rear cavity 10 can only enter the rear buffer cavity 13 through the second axial oil duct 18 and then is discharged through the second oil port 11, at the moment, the oil return gap between the inner hexagonal cone valve 23 in the rear end cover 3 and the second axial oil duct 18 is adjusted, so that the hydraulic oil generates a force resisting against the output force of the piston rod 4 in the rear cavity 10 to achieve throttling buffering, and the buffering speed is controlled by adjusting the size of the oil return gap.

In light of the foregoing description of the preferred embodiment of the present invention, many modifications and variations can be made by the worker in the light of the above teachings without departing from the spirit of the utility model. The technical scope of the present invention is not limited to the content of the specification, and must be determined according to the scope of the claims.

Claims

1. The utility model provides a two-way buffer hydraulic cylinder with adjustable speed, includes cylinder, front end housing, rear end housing, piston rod and piston, the piston rod on install the cushion lantern ring of terminal surface before the laminating piston, the buffer nut of laminating piston rear end face, the first hydraulic fluid port of intercommunication pneumatic cylinder front chamber is seted up to the outer wall on the front end housing, the second hydraulic fluid port of intercommunication pneumatic cylinder rear chamber, characterized by are seted up to the rear end housing outer wall: the front end housing center seted up with the preceding cushion chamber of buffering lantern ring matched with, the back cushion chamber with buffer nut matched with is seted up at the back end housing center, preceding cushion chamber intercommunication first hydraulic fluid port, back cushion chamber intercommunication second hydraulic fluid port, back end housing internal diameter install when the piston rod antedisplacement switch-on back cavity and back cushion chamber check valve, the choke valve of speed when the piston rod returns to adjust buffer nut and get into back cushion chamber, the front end housing internal diameter install when the piston rod antedisplacement adjust the speed when the buffering lantern ring gets into preceding cushion chamber the choke valve, when the piston rod returns to switch-on front cavity and preceding cushion chamber check valve.

2. The adjustable speed bi-directional damping cylinder as claimed in claim 1, wherein: the front end cover is internally provided with two first axial oil ducts communicated with the front cavity, a first radial hole and a second radial hole are arranged in the front end cover, the outer end part of the front end cover is provided with an internal thread, the first axial oil ducts are vertically communicated with the first radial hole and the second radial hole respectively, and the inner ends of the first radial hole and the second radial hole are contracted and communicated with the front buffer cavity.

3. The adjustable speed bi-directional damping cylinder as claimed in claim 1, wherein: the rear end cover is internally provided with two second axial oil ducts communicated with the rear cavity, a first radial hole and a second radial hole are arranged in the rear end cover, the outer end part of the first radial hole and the outer end part of the second radial hole are provided with internal threads, the second axial oil ducts are respectively vertically communicated with the first radial hole and the second radial hole, and the inner ends of the first radial hole and the second radial hole are communicated with the rear buffer cavity in a shrinkage mode.

4. The adjustable speed bi-directional damping cylinder according to claim 2 or 3, wherein: the check valve comprises a steel ball and a spring, the steel ball is arranged in the first radial hole and sealed with a conical hole line at the contraction position, the spring is arranged in the first radial hole, the inner end of the spring applies force on the steel ball, and the outer end part of the first radial hole is in threaded connection with an inner hexagonal plug which is pressed against the outer end of the spring.

5. The adjustable speed bi-directional damping cylinder according to claim 2 or 3, wherein: the throttling valve comprises an inner hexagonal cone valve, the inner hexagonal cone valve is in threaded connection with the outer end of the second radial hole, a sharp cone portion of the inner hexagonal cone valve is clamped in a small hole formed after the second radial hole is contracted, and the outer end of the inner hexagonal cone valve is in threaded connection with a locking nut.

6. The adjustable speed bi-directional damping cylinder as claimed in claim 2, wherein: the inner end face of the front end cover is provided with a first groove surrounding the periphery of the front buffer cavity, and the first axial oil duct is communicated with the first groove.

7. The adjustable speed bi-directional damping cylinder according to claim 3, wherein: the inner end face of the rear end cover is provided with a second groove surrounding the periphery of the rear buffer cavity, and the second axial oil duct is communicated with the second groove.